Three-dimensional stereoscopic flow channel heat dissipation device utilizing inlet section effect

Abstract

This invention discloses a three-dimensional flow channel heat dissipation device utilizing the inlet section effect, relating to the field of single-phase liquid cooling technology. It includes a heat sink in a heat dissipation cavity and a heat dissipation flow channel. The heat sink has an inlet and an outlet. The heat dissipation flow channel is located within the heat sink and includes an inlet pipe, an outlet pipe, and a flow distribution section. The flow distribution section includes a pair of flow distribution plates and multiple flow distribution pipes. The two flow distribution plates are arranged parallel and spaced apart. The flow distribution pipes are vertically sandwiched between the two flow distribution plates, with both ends connected to the two flow distribution plates. One end of the inlet pipe and the outlet pipe are connected to the two flow distribution plates, and the other end is connected to the inlet and outlet, respectively. The flow distribution plates have multiple horizontal and vertical pipes connected in series or parallel, and both horizontal and vertical pipes are square tubes. This invention can solve the problem of unsatisfactory liquid cooling effect for high-power, miniaturized high-heat-flux devices, which affects the device's lifespan.

Description

Technical Field

[0001] This invention relates to the field of single-phase liquid cooling technology, specifically to a three-dimensional flow channel heat dissipation device utilizing the inlet section effect. Background Technology

[0002] In recent years, single-phase liquid cooling technology has been widely used, typically in airborne electronic chassis, radar equipment, and liquid-cooled flow channel cold plates in automotive batteries. Compared to traditional air cooling, liquid cooling has significant performance advantages, with a heat dissipation efficiency up to 50 times that of air cooling. With the rapid development of electronic information technology, high-performance electronic devices are widely used in advanced engineering fields such as aerospace, energy, transportation, communications, and AI computing. To meet the ever-increasing demands for data processing and functionality, these devices are rapidly evolving towards higher power, miniaturization, and integration. While high integration improves component performance, it also brings the challenge of dissipating high heat flux. Research shows that if the heat generated by power chips cannot be dissipated in time, the device will operate under high-temperature conditions for extended periods, directly affecting its lifespan and even causing it to fail.

[0003] Therefore, this application is hereby submitted. Summary of the Invention

[0004] The purpose of this invention is to provide a three-dimensional flow channel heat dissipation device that utilizes the inlet section effect to solve the problem of unsatisfactory liquid cooling effect for high-power, miniaturized high heat flux devices, which affects the service life of the devices.

[0005] This invention is achieved through the following technical solution: A three-dimensional heat dissipation device utilizing the inlet section effect includes: a heat sink with an inlet and an outlet; a heat dissipation channel disposed within the heat sink, comprising an inlet pipe, an outlet pipe, and a flow distribution section; the flow distribution section includes a pair of flow distribution plates and multiple flow distribution pipes, the two flow distribution plates being arranged parallel and spaced apart, the flow distribution pipes being vertically sandwiched between the two flow distribution plates and having both ends connected to the two flow distribution plates respectively, one end of the inlet pipe and the outlet pipe being connected to the two flow distribution plates respectively, and the other end being connected to the inlet and the outlet respectively; the flow distribution plates are provided with multiple horizontal and vertical pipes connected in series or parallel, and both the horizontal and vertical pipes are square tubes.

[0006] In another preferred embodiment, the heat sink of the heat dissipation cavity is in the shape of a cuboid box to form a first heat dissipation surface and a second heat dissipation surface, a third heat dissipation surface and a fourth heat dissipation surface, and a fifth surface and a sixth surface, which are arranged opposite to each other; the two diversion plates are arranged parallel to the first heat dissipation surface and the second heat dissipation surface, respectively, and exchange heat; all the diversion pipes are located on the same plane, and the plane they are located on is parallel to the third heat dissipation surface and the fourth heat dissipation surface, respectively, and exchange heat, and is located on the midpoint plane between the third heat dissipation surface and the fourth heat dissipation surface; the inlet and the outlet are respectively located on the fifth surface and the sixth surface.

[0007] In another preferred embodiment, the heat sink of the heat dissipation cavity has dimensions of 100mm×100mm×100mm; the cross-sectional dimensions of the horizontal tube and the vertical tube are a×b, where a≥0.5mm and b≥0.5mm.

[0008] In another preferred embodiment, the diverter plate includes three horizontal pipes and multiple vertical pipes; the three horizontal pipes are arranged in parallel and spaced apart; the multiple vertical pipes are arranged in parallel and spaced apart, and are all vertically sandwiched between two adjacent horizontal pipes, with both ends connected to the two horizontal pipes respectively; the inner ends of the inlet pipe and the outlet pipe are respectively connected to the opposite ends of a pair of horizontal pipes located in the middle; the two ends of the diverter pipe are respectively connected to the side walls of the pair of horizontal pipes located in the middle.

[0009] In another preferred embodiment, the diverter plate includes nine longitudinal tubes; two horizontal tubes located at the top and middle are of the same length and are longer than the horizontal tube located at the bottom; five longitudinal tubes are arranged in parallel and spaced apart, and are all vertically sandwiched between the two horizontal tubes at the top and middle, with both ends connected to the two horizontal tubes respectively; four longitudinal tubes are arranged in parallel and spaced apart, and are all vertically sandwiched between the two horizontal tubes at the middle and bottom, with both ends connected to the two horizontal tubes respectively.

[0010] In another preferred embodiment, the two ends of the two horizontal pipes located between the two horizontal pipes at the top and middle and on both sides are connected in series with the two horizontal pipes respectively; the bottom ends of the two vertical pipes located between the two horizontal pipes at the middle and lower and on both sides are connected in series with the two ends of the horizontal pipe located at the lower; the hydraulic radius of the heat dissipation channel is 3.5 mm.

[0011] In another preferred embodiment, it further includes one of the flow dividers and multiple flow dividers; the three flow dividers are arranged in parallel and spaced apart, the third flow divider is sandwiched between the first flow divider and shares the second flow divider, and is connected to the second flow divider through the flow dividers; the third flow divider is connected to a second inlet pipe, and the fifth side has a second inlet, and the second inlet pipe is connected to the second inlet.

[0012] In another preferred embodiment, the diverter plate includes eighteen longitudinal pipes; nine longitudinal pipes are arranged in parallel at intervals and are all vertically sandwiched between two horizontal pipes in the upper and middle sections, and both ends are respectively connected to the two horizontal pipes; nine longitudinal pipes are arranged in parallel at intervals and are all vertically sandwiched between two horizontal pipes in the middle and lower sections, and both ends are respectively connected to the two horizontal pipes.

[0013] In another preferred embodiment, the two ends of the longitudinal pipe located on the outer side are connected in series with two transverse pipes respectively; the hydraulic radius of the heat dissipation channel is 1.8 mm.

[0014] In another preferred embodiment, the outer walls of the first, second, third, and fourth heat dissipation surfaces are all covered with printed circuit boards, and the inner walls of the printed circuit boards are covered with heating element groups. Each heating element group includes a large heating element and multiple small heating elements. The large heating element has dimensions of 40 mm × 40 mm × 2 mm, and the small heating elements have dimensions of 20 mm × 20 mm × 2 mm. The heating element groups corresponding to the first and second heat dissipation surfaces include 8 small heating elements, and the heating element groups corresponding to the third and fourth heat dissipation surfaces include 4 small heating elements.

[0015] The present invention, by adopting the above-mentioned technical solution, has the following positive effects compared with the prior art: This invention discloses a three-dimensional heat dissipation device utilizing the inlet section effect. By setting up a heat sink within a heat dissipation cavity and heat dissipation channels, with the channels located within the heat sink, the heat sink is continuously liquid-cooled, thus enabling the entire device to dissipate heat. Furthermore, the heat dissipation channels include inlet pipes, outlet pipes, and a distribution section. The distribution section further includes a pair of distribution plates and multiple distribution pipes. Each distribution plate has multiple horizontal and vertical pipes connected in series or parallel, forming an H-shaped symmetrical heat dissipation channel structure with two distribution plates sandwiching multiple distribution pipes. This structure utilizes a symmetrical power distribution. This design initially improves heat dissipation. Building upon this, by using square tubes for both the horizontal and vertical sections, the turbulence generated by the flow diversion is enhanced. Furthermore, by altering the cross-sectional length and width of the square tubes, flow resistance matching is achieved, ensuring a uniform flow distribution throughout the H-shaped heat dissipation channel. This utilizes the inlet section effect to amplify the asymmetric distribution of heat dissipation power at the inlet surface. Combined with the symmetrical H-shaped heat dissipation channel structure, this further effectively improves the device's heat dissipation efficiency and performance. Through the synergy of these features, this three-dimensional flow channel heat dissipation device utilizing the inlet section effect can effectively solve the problem of unsatisfactory liquid cooling performance for high-power, miniaturized, high-heat-flux devices, thus affecting device lifespan. Attached Figure Description

[0016] The accompanying drawings, which are included to provide a further understanding of embodiments of the invention and form part of this application, do not constitute a limitation thereof. In the drawings: Figure 1 This is a schematic diagram of a three-dimensional flow channel heat dissipation device utilizing the inlet section effect, provided in Embodiment 1 of the present invention. Figure 2 This is a schematic diagram of the heat dissipation channel of a three-dimensional flow channel heat dissipation device utilizing the inlet section effect, provided in Embodiment 1 of the present invention. Figure 3 A perspective view of a printed circuit board laid out with a three-dimensional heat dissipation device utilizing the inlet section effect, as provided in Embodiment 1 of the present invention. Figure 4 and Figure 5 A turbulence intensity distribution diagram of the splitter pipe of a three-dimensional flow channel heat dissipation device utilizing the inlet section effect, provided in Embodiment 1 of the present invention; Figure 6 A turbulence intensity distribution diagram of a flow divider plate of a three-dimensional flow channel heat dissipation device utilizing the inlet section effect, provided in Embodiment 1 of the present invention; Figure 7 This is a temperature change graph of the test points during the verification phase of Embodiment 1 of the present invention; Figure 8 This is a temperature change graph of the test points during the verification phase of Embodiment 1 of the present invention; Figure 9 This is a temperature distribution diagram of the entire module under maximum power conditions during the verification phase of Embodiment 1 of the present invention; Figure 10 This is a temperature distribution diagram on the heating element during the maximum power state in the verification phase of Embodiment 1 of the present invention; Figure 11 This is a temperature variation graph of each heating element at a flow rate of 1.8 L / min during the verification phase of Embodiment 1 of the present invention; Figure 12 This is a temperature distribution diagram of the entire module when the flow rate is 1.8 L / min during the verification phase of Embodiment 1 of the present invention. Figure 13 This is a temperature distribution diagram on the heating element when the flow rate is 1.8 L / min during the verification phase of Embodiment 1 of the present invention; Figure 14 This is a schematic diagram of a three-dimensional flow channel heat dissipation device utilizing the inlet section effect, provided in Embodiment 2 of the present invention. Figure 15 The diagram shows the turbulence intensity distribution of the splitter pipe of a three-dimensional flow channel heat dissipation device utilizing the inlet section effect, as provided in Embodiment 2 of the present invention.

[0017] The attached diagram shows the markings and corresponding component names: 10-Heat sink in heat dissipation cavity; 11-First heat dissipation surface; 12-Second heat dissipation surface; 13-Third heat dissipation surface; 14-Fourth heat dissipation surface; 15-Fifth surface; 16-Sixth surface; 17-Printed circuit board; 20-Heat dissipation channel; 21-Inlet pipe; 22-Pipeline; 23-Distributor plate; 231-Horizontal pipe; 232-Vertical pipe; 24-Distributor pipe; 25-Second inlet pipe. Detailed Implementation

[0018] The technical solution of the present invention will now be clearly and completely described with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0019] In the description of this invention, it should be understood that the orientation or positional relationship indicated by terms such as "upper", "lower", "left", "right", "inner", "outer", "front", "rear", "lateral", and "vertical" are based on the orientation or positional relationship shown in the accompanying drawings and are only for the convenience of describing this invention, and are not intended to indicate or imply that the device or component referred to must have a specific orientation, and therefore should not be construed as a limitation of this invention.

[0020] It should be noted that the terms "horizontal" and "vertical" in this invention are used to describe approximate positional relationships, and not strictly "horizontal plane" or "vertical plane". Example

[0021] Please refer to Figures 1 to 3 As shown, this embodiment provides a three-dimensional flow channel heat dissipation device utilizing the inlet section effect, including: a heat sink 10 with an inlet and an outlet; a second heat dissipation flow channel 20 disposed within the heat sink 10, comprising an inlet pipe 21, a drain pipe 22, and a diversion section; a third diversion section comprising a pair of diversion plates 23 and multiple diversion pipes 24, the two diversion plates 23 being arranged parallel and spaced apart, the diversion pipes 24 being vertically sandwiched between the two diversion plates 23 and having both ends connected to the two diversion plates 23 respectively, one end of the inlet pipe 21 and the drain pipe 22 being connected to the two diversion plates 23 respectively, and the other end being connected to the inlet and the outlet respectively; a fourth diversion plate 23 having multiple horizontal pipes 231 and vertical pipes 232 connected in series or in parallel, the horizontal pipes 231 and the vertical pipes 232 being square pipes.

[0022] This embodiment discloses a three-dimensional flow channel heat dissipation device utilizing the inlet section effect. By setting up a heat sink 10 and a heat dissipation flow channel 20 within the heat sink 10, the heat sink 10 is continuously liquid-cooled via the flow channel 20, thus enabling the entire device to dissipate heat. Furthermore, the heat dissipation flow channel 20 includes an inlet pipe 21, an outlet pipe 22, and a flow branch. The flow branch further includes a pair of flow branch plates 23 and multiple flow branch pipes 24. The flow branch plates 23 are equipped with multiple horizontal pipes 231 and vertical pipes 232 connected in series or parallel, forming an H-shaped symmetrical heat dissipation flow channel 24 with two flow branch plates 23 sandwiching multiple flow branch pipes 24. The H-shaped heat dissipation channel 20 initially improves heat dissipation by adopting a symmetrical power distribution. Building upon this, by setting the horizontal tube 231 and vertical tube 232 as square tubes, the turbulence generated by the flow split is enhanced. Furthermore, by changing the cross-sectional length and width of the square tubes, flow resistance matching is achieved, ensuring uniform flow distribution throughout the entire H-shaped heat dissipation channel 20. This utilizes the inlet section effect to amplify the asymmetrical distribution of heat dissipation power at the inlet surface. Combined with the H-shaped symmetrical heat dissipation channel 20 structure, the heat dissipation efficiency and effect of the device are further effectively improved. Through the synergy of these features, this three-dimensional heat dissipation device utilizing the inlet section effect can effectively solve the problem of unsatisfactory liquid cooling performance for high-power, miniaturized, high-heat-flux devices, thus affecting device lifespan.

[0023] To further explain the specific structure of the heat sink 10 of the heat dissipation wall and its positional relationship with the heat dissipation channel 20, the heat sink 10 of the heat dissipation cavity is in the shape of a cuboid box, forming a first heat dissipation surface 11 and a second heat dissipation surface 12, a third heat dissipation surface 13 and a fourth heat dissipation surface 14, and a fifth surface 15 and a sixth surface 16 arranged opposite to each other; the two diversion plates 23 are arranged parallel to the first heat dissipation surface 11 and the second heat dissipation surface 12 respectively and exchange heat; all the diversion pipes 24 are located on the same plane, and the planes they are located on are parallel to the third heat dissipation surface 13 and the fourth heat dissipation surface 14 respectively and exchange heat, and are located on the mid-plane of the third heat dissipation surface 13 and the fourth heat dissipation surface 14; the inlet and the outlet are respectively located on the fifth surface 15 and the sixth surface 16.

[0024] To provide a specific explanation of the dimensions of the heat sink 10 in the heat dissipation cavity and the dimensions of the horizontal tube 231 and the vertical tube 232, the dimensions of the heat sink 10 in the heat dissipation cavity are 100mm×100mm×100mm; the cross-sectional dimensions of the horizontal tube 231 and the vertical tube 232 are a×b, where: a≥0.5mm, b≥0.5mm.

[0025] To further explain the specific shape of the diverter plate 23, the diverter plate 23 includes three horizontal pipes 231 and multiple vertical pipes 232; the three horizontal pipes 231 are arranged in parallel and spaced apart; the multiple vertical pipes 232 are arranged in parallel and spaced apart, and are all vertically sandwiched between two adjacent horizontal pipes 231, and their two ends are respectively connected to the two horizontal pipes 231; the inner ends of the inlet pipe 21 and the outlet pipe 22 are respectively connected to the opposite ends of a pair of horizontal pipes 231 located in the middle; the two ends of the diverter pipe 24 are respectively connected to the side walls of a pair of horizontal pipes 231 located in the middle.

[0026] To further optimize the specific structure of the diverter plate 23 and further utilize the inlet end effect, the diverter plate 23 includes nine longitudinal pipes 232; two transverse pipes 231 located at the top and middle have the same length and are longer than the transverse pipe 231 located at the bottom; five longitudinal pipes 232 are arranged in parallel and spaced apart, and are all vertically sandwiched between the two transverse pipes 231 located at the top and middle, and are connected to the two transverse pipes 231 at both ends respectively; four longitudinal pipes 232 are arranged in parallel and spaced apart, and are all vertically sandwiched between the two transverse pipes 231 located at the middle and bottom, and are connected to the two transverse pipes 231 at both ends respectively.

[0027] To further prevent the coolant from losing kinetic energy, the two ends of the two horizontal pipes 231 located at the top and middle and the two vertical pipes 232 located on both sides are connected in series with the two horizontal pipes 231 respectively; the bottom ends of the two horizontal pipes 231 located at the middle and lower and the two vertical pipes 232 located on both sides are connected in series with the two ends of the horizontal pipe 231 located below; the hydraulic radius of the heat dissipation channel 20 is 3.5mm.

[0028] To further explain the heat exchange structure of the heat dissipation channel 20 and the heat sink 10 of the heat dissipation cavity, the outer walls of the first heat dissipation surface 11, the second heat dissipation surface 12, the third heat dissipation surface 13 and the fourth heat dissipation surface 14 are all covered with printed circuit boards 17, and the inner walls of the printed circuit boards 17 are covered with heating element groups; the heating element group includes one large heating element and multiple small heating elements, the size of the large heating element is 40 mm × 40 mm × 2 mm; the size of the small heating elements is 20 mm × 20 mm × 2 mm; the heating element group corresponding to the first heat dissipation surface 11 and the second heat dissipation surface 12 includes 8 of the small heating elements; the heating element group corresponding to the third heat dissipation surface 13 and the fourth heat dissipation surface 14 includes 4 of the small heating elements.

[0029] I. Mechanism analysis of the entrance segment effect: Under the condition of symmetrical power consumption distribution, the temperature of the heating element on the first heat dissipation surface 11 is significantly lower than that on other surfaces. When the coolant flows into the diverter plate 23, an "inlet section effect" will appear in its inlet section. This effect is manifested in that the turbulence intensity in the heat dissipation pipe at the inlet surface is significantly higher than that in other areas, and the velocity in the heat dissipation pipe at the inlet surface is significantly faster than that in other areas, resulting in a significantly higher heat dissipation efficiency in the inlet section than on other surfaces. The core principle is that when the coolant just enters the heat dissipation channel 20, the velocity boundary layer and temperature boundary layer of the fluid are relatively thin, resulting in a lower thermal resistance during heat transfer, thus exhibiting a strong heat transfer capacity in the inlet section region of the fluid. Therefore, how to extend the inlet section effect and how to effectively utilize the inlet section effect are key factors in solving the problem of limited space and limited heat dissipation resources for airborne electronic equipment. The following formulas (1)-(3) give the influence length of the inlet section effect of a smooth pipe under normal circumstances.

[0030] Re=ρvL / u (1) L=2ab / (a+b) (2) Le=1.36Re (1 / 4) L (3) In the formula, Re is the Reynolds number during the flow process; ρ is the coolant density, kg / m3; v is the coolant velocity, m / s; L is the hydraulic radius of the flow channel, m; a is the length of the rectangular flow channel, m; b is the width of the rectangular flow channel, m; u is the dynamic viscosity, Pa·s; and Le is the length affected by the smooth pipe inlet section effect, m.

[0031] According to formulas (1)-(3), under the condition of 65# aviation coolant with a flow rate of 2.5L / min, the distance affected by the effect of the smooth pipe inlet section should be 35.62mm. Figures 4 to 6 The figures show the turbulence intensity distribution at the middle section of the flow channel, as well as the velocity distribution at the middle section and the inlet section. As can be seen from the three figures above, if... Figure 5 The region with a flow velocity ≥ 2.62 m / s is defined as the high-speed flow region. It can be observed that from the inlet end of the pipe to the bottom, the high-speed flow region extends from the inlet section to the bottom of the H-shaped heat dissipation channel 20, and shows a continuous downward trend. Even after turning 90° from the bottom of the inlet pipe, the fast-flow region in the pipe continues for a period of medium to high speed. This indicates that in the H-shaped channel structure, the length of the inlet section effect... L e > The inlet pipe length is 89.75 mm. This indicates that the H-shaped flow channel structure effectively extends the length of the inlet section effect, enhances the intensity of the inlet section effect, and increases the heat dissipation efficiency of the fifth surface 15 of the inlet section.

[0032] The reason for the above phenomenon is that in the structural design of the H-shaped heat dissipation channel 20 in this embodiment, the horizontal pipe 231 in the middle of the diversion plate 23 is diverted 9 times in the middle section and 9 times in the vertical direction, that is, it is diverted a total of 18 times on the main inlet pipe. When the coolant flows in the H-shaped heat dissipation channel 20, the flow boundary layer and velocity boundary layer of the horizontal pipe 231 in the middle section will be repeatedly destroyed and repeatedly regenerated. In this process, the influence distance of the inlet section effect is extended, and the intensity of the inlet section effect is enhanced, thereby strengthening the heat dissipation efficiency of the first heat dissipation surface 11. In addition, as Figure 5 It can be observed that each time the flow is split in the middle horizontal pipe 231, a turbulent region with locally enhanced velocity appears on the right side of the pipe. This indicates that the velocity boundary layer and temperature boundary layer are disrupted at this point, confirming the above analysis. Figure 4 As shown, the turbulence intensity at the diversion point of the diversion pipe 24 is significantly enhanced, with a large area of ​​bright highlights. This indicates that the continuous interruption and diversion of the horizontal pipe 231 in the middle effectively enhances the turbulence intensity on the entire inlet pipe, achieving the goal of enhancing the inlet section effect.

[0033] II. Verification of the heat dissipation effect after the enhancement of the inlet section effect of the above-mentioned H-type heat dissipation channel 20: During the experiment, it was found that the highest temperature on the heating element at the coolant inlet section, i.e., the first heat dissipation surface 11, was only 51.27℃, while the temperature on the opposite second heat dissipation surface 12 was 65.25℃, exceeding the required 60℃. At the inlet of the liquid-cooled manifold 23, due to insufficient flow development and a thinner thermal boundary layer, the local heat transfer coefficient was significantly higher than that in the fully developed stage. In particular, when the flow was laminar, the heat transfer coefficient at the inlet section could reach 1.5-3 times that of the fully developed section.

[0034] To address the issue that the H-shaped heat dissipation channel 20 cannot meet chip heat dissipation requirements at a power consumption of 1000W, the heat dissipation power of the chip at the inlet surface is increased, i.e., the heat dissipation power of the first heat dissipation surface 11 is increased. For example... Figure 7As shown, the total power on the first heat dissipation surface 11 is increased from 320W to 40×4+35.06×7.51=423W, while the power consumption of other heat dissipation surfaces is reduced. The highest temperature on the heating element on the first heat dissipation surface 11 will increase from 51.27℃ to 57.67℃ < 60℃. Since the total power is a fixed 1000W, increasing the power of the first heat dissipation surface 11 correspondingly reduces the total power on the second heat dissipation surface 12, making the highest temperature of the heating element on the second heat dissipation surface 12 also lower than 57.67℃. At this time, the highest temperature of the heating element on the entire H-shaped heat dissipation channel 20 is 57.67℃. When the inlet liquid temperature of the H-shaped heat dissipation channel 20 is 30℃ and the inlet liquid is 65# aviation coolant, the temperature rise of the heating element on the module does not exceed 30℃, the highest temperature is 57.67℃, and the temperature rise is 27.67℃, which meets the requirements of GJB / Z 35-1993 "Component Derating Guidelines".

[0035] III. Verification of the effect of square tubes on the inlet section: The inlet horizontal pipe 231 and vertical pipe 232 have been optimized from circular to rectangular. This is mainly because the coolant flows out of the H-shaped cooling channel 20 through the distributor plate 23, and its flow path is necessarily equal to L. T2 =2Ls+Lm+Lh. If the pipe diameters in each heat dissipation surface are equal, there will inevitably be virtually no coolant in the distribution plate 23. Therefore, it is necessary to reduce the hydraulic radius in the horizontal pipe 231 and the vertical pipe 232, optimizing the circular pipe into a rectangular pipe. By adjusting the values ​​of the cross-sectional length and width (a, b), the flow resistance of the coolant through the distribution pipe 24 is matched, so that although the flow rate in the distribution plate 23 is larger than that in the distribution pipe 24, the flow resistance of the two is the same, thus ensuring the uniformity of the flow rate in the entire H-shaped heat dissipation channel 20. Another reason for optimizing the circular channel into a rectangular channel is that the velocity boundary layer and temperature boundary layer are significantly different. When transitioning from a rectangular pipe to a circular pipe, the turbulence intensity generated is significantly greater than when transitioning from a circular pipe to a circular pipe.

[0036] (1) Verification of the ultimate heat dissipation power of the H-type heat dissipation channel 20 at a flow rate of 2.5 L / min: Adjusting the power of the heating element on the module, we explored the maximum heat dissipation at a flow rate of 2.5 L / min, an inlet liquid temperature of 30°C, an ambient temperature of 25°C, and 65# aviation coolant. Based on the above, the inlet surface of the H-shaped heat dissipation channel 20, i.e., the first heat dissipation surface 11, has the best heat dissipation effect due to the inlet section effect. Therefore, we increased the heat dissipation power of the first heat dissipation surface 11, adjusting it to 414.28 W. Figure 8As shown, when the total power of the other three heat dissipation surfaces is 700W, the heat dissipation power of the entire H-shaped heat dissipation channel is 1114.28W. The H-shaped heat dissipation channel 20 only requires 2.5L / min of cooling medium to ensure that the maximum temperature rise of all heating elements on the heat dissipation channel 20 is <30℃. Figure 9 It can be seen that the highest temperature of the thermocouple on the heating element is 59.62℃, and the maximum temperature rise is 29.39℃. Tests show that the flow resistance on the H-type heat dissipation channel 20 under this condition is 21.90kPa < 100kPa, which meets the task requirements.

[0037] A fluid-structure interaction simulation analysis was performed on the 1114.28W power state. Figure 10 Simulation analysis shows that the highest temperature on the heating element is the highest temperature of the entire module. The highest temperature occurs on the large heating element in the middle of the first heat dissipation surface 11, reaching 60.50℃. The simulated highest temperature of 60.50℃ differs from the experimental highest temperature of 59.62℃ by only 0.88℃, with an error of only 1.47%. Simulation also reveals that the flow resistance of the entire channel at this temperature is 23.58 kPa, which differs from the experimentally measured flow resistance of 22.10 kPa by 1.48 kPa. The error between the two values ​​is 6.7% < 15%, meeting the requirements.

[0038] As shown above, simulation and experimental analysis of the H-type flow channel reveal that the error in the highest temperature is only 1.47%, and the error in the maximum flow resistance is 6.7%, both meeting design requirements. It can be concluded that at a flow rate of 2.5 L / min, the maximum heat dissipation of the H-type flow channel module is 1114.28 W, and the flow resistance is only 22.10 kPa, both of which match the simulation and experimental results.

[0039] (2) Verification of the minimum heat dissipation flow rate of the H-type flow channel at 1000W power: like Figure 11 At a flow rate of 1.8 L / min, the maximum power that the H-type heat dissipation channel 20 can withstand is 1004.63 W. Figure 12 It can be seen that the highest temperature of the thermocouple on the ceramic heating element is 61.08℃, and the maximum temperature rise is 31.08℃. Tests show that the flow resistance at this point is also 14.2 kPa.

[0040] like Figure 13It can be seen that the highest temperature on the entire module is 63.1℃, and the highest temperature occurs on the large heating plate in the middle of the first heat dissipation surface 11, with a maximum temperature rise of 33.1℃. From the above, it can be seen that the highest temperature in the experimental state is 61.08℃, while the highest temperature in the simulation state is 63.1℃, a difference of 2.02℃, with an error of only 3.3%, indicating a good match between the simulation and the experiment. The simulated flow resistance value is 13.575kPa, which differs from the experimental value of 14.2kPa by 0.625kPa, with an error of only 4.4%, showing a high degree of agreement between the experiment and the simulation.

[0041] Based on the above analysis, it can be seen that without considering the inlet section effect, the H-shaped flow channel cannot meet the design requirements with a temperature rise of <30℃ when the inlet heat dissipation flow rate is 2.5L / min. However, considering the inlet section effect, increasing the heat dissipation power of the first heat dissipation surface 11 at the inlet section can effectively improve the heat dissipation efficiency of the entire H-shaped flow channel. According to the above, considering the inlet section effect, the heat dissipation of the entire H-shaped flow channel can reach 1114.28W at a flow rate of 2.5L / min. Meanwhile, when the heat dissipation power applied to the H-shaped flow channel is 1000W, the actual required heat dissipation flow rate is only 1.8L / min when considering the inlet section effect. Therefore, it can be demonstrated that the inlet section effect has a significant effect on enhancing the heat dissipation capacity of the equipment.

[0042] As can be seen from the above verification, the three-dimensional flow channel heat dissipation device utilizing the inlet section effect provided in Example 1 can effectively solve the problem of unsatisfactory liquid cooling effect for high-power, miniaturized high heat flux devices, which affects the service life of the devices.

[0043] Example 2 Please refer to Figures 14 to 15 As shown, this embodiment provides a three-dimensional flow channel heat dissipation device utilizing the inlet section effect, which is a further improvement of Embodiment 1. The only difference between it and Embodiment 1 is that: To maximize the use of the inlet section effect, this embodiment provides a three-dimensional flow channel heat dissipation device utilizing the inlet section effect, which further includes a flow divider plate 23 and multiple flow divider pipes 24; the three flow dividers 23 are arranged in parallel and spaced apart, the third flow divider plate 23 is sandwiched between the first flow divider plate 23 and shares the second flow divider plate 23, and is connected to the second flow divider plate 23 through the flow divider pipes 24; the third flow divider plate 23 is connected to a second inlet pipe 25, the fifth surface 15 has a second inlet, and the second inlet pipe 25 is connected to the second inlet.

[0044] It should be noted that the dimensions of the heat sink 10 of the heat dissipation cavity of the three-dimensional flow channel heat dissipation device utilizing the inlet section effect are still 100mm×100mm×100mm. The dimensions of the heat dissipation flow channel 20 (mainly the dimensions parallel to the length direction of the split pipe 24) should be adjusted accordingly to make the two match.

[0045] Through the above configuration, the coolant in the horizontal pipe 231 located in the middle is repeatedly interrupted by the connected flow channels, so that the coolant continuously generates turbulence, thereby achieving the purpose of extending the effect of the flow channel inlet section.

[0046] Furthermore, through the above configuration, a second inlet pipe 25 is added to the inlet pipe 21 of the heat dissipation channel 20. At this time, the parts with stronger heat dissipation capacity are the first heat dissipation surface 11 and the second heat dissipation surface 12.

[0047] To further optimize heat dissipation, the diversion plate 23 includes eighteen longitudinal pipes 232; nine longitudinal pipes 232 are arranged in parallel and spaced apart, and are all vertically sandwiched between two horizontal pipes 231 at the top and middle, with both ends connected to the two horizontal pipes 231 respectively; nine longitudinal pipes 232 are arranged in parallel and spaced apart, and are all vertically sandwiched between two horizontal pipes 231 at the middle and bottom, with both ends connected to the two horizontal pipes 231 respectively. The two ends of the longitudinal pipes 232 located on the outer side are connected in series with the two horizontal pipes 231 respectively; the hydraulic radius of the heat dissipation channel 20 is 1.8 mm.

[0048] As the hydraulic radius decreases, the flow velocity increases. Simultaneously, the continuous disturbance of the main flow channels on the left and right end heat dissipation surfaces by the diverter plate 23 and diverter pipe 24 causes the flow velocity at the inlet sections of the inlet pipe 21 and the second inlet pipe 25 to increase from 4.19 m / s in the structure of Example 1 to 16.8 m / s, an increase of approximately four times. Comparing the flow velocity in the deep region of the horizontal pipe 231 located in the middle of the two diverter plates 23 on both sides, the initial structure's deep region flow velocity was between 0.4 m / s and 2.1 m / s, while the improved structure's deep region flow velocity was between 3.36 and 10.1 m / s, an increase of approximately 5 to 10 times. This stable increase in flow velocity effectively enhances the heat dissipation effect of the heat dissipation surface.

[0049] The above description is merely a preferred embodiment of the present invention and does not limit the implementation and protection scope of the present invention. Those skilled in the art should realize that any equivalent substitutions and obvious changes made based on the description and illustrations of the present invention should be included within the protection scope of the present invention.

Claims

1. A three-dimensional flow channel heat dissipation device utilizing the inlet section effect, characterized in that, include: The heat sink (10) of the heat dissipation cavity has an inlet and an outlet; The heat dissipation channel (20) is located inside the heat sink (10) of the heat dissipation cavity. The heat dissipation channel (20) includes an inlet pipe (21), an outlet pipe (22), and a flow distribution section. The diversion section includes a pair of diversion plates (23) and multiple diversion pipes (24). The two diversion plates (23) are arranged in parallel and spaced apart. The diversion pipes (24) are vertically sandwiched between the two diversion plates (23) and their two ends are respectively connected to the two diversion plates (23). One end of the inlet pipe (21) and the outlet pipe (22) are respectively connected to the two diversion plates (23), and the other end is respectively connected to the inlet and the outlet. The diversion plate (23) is provided with multiple horizontal pipes (231) and vertical pipes (232) connected in series or in parallel. Both the horizontal pipes (231) and the vertical pipes (232) are square pipes.

2. The three-dimensional flow channel heat dissipation device utilizing the inlet section effect according to claim 1, characterized in that, The heat sink (10) of the heat dissipation cavity is in the shape of a cuboid box to form a first heat dissipation surface (11) and a second heat dissipation surface (12), a third heat dissipation surface (13) and a fourth heat dissipation surface (14) arranged opposite to each other, and a fifth surface (15) and a sixth surface (16) arranged opposite to each other. The two heat exchange plates (23) are arranged parallel to the first heat dissipation surface (11) and the second heat dissipation surface (12) respectively and exchange heat. All the aforementioned shunt pipes (24) are located on the same plane, and the plane they are located on is parallel to and exchanges heat with the third heat dissipation surface (13) and the fourth heat dissipation surface (14) respectively, and is located at the midpoint of the third heat dissipation surface (13) and the fourth heat dissipation surface (14); The entrance and the exit are respectively located on the fifth side (15) and the sixth side (16).

3. The three-dimensional flow channel heat dissipation device utilizing the inlet section effect according to claim 2, characterized in that, The dimensions of the heat sink (10) in the heat dissipation cavity are 100mm×100mm×100mm; The cross-sectional dimensions of the horizontal tube (231) and the vertical tube (232) are a×b, where a≥0.5mm and b≥0.5mm.

4. The three-dimensional flow channel heat dissipation device utilizing the inlet section effect according to claim 2, characterized in that, The diversion plate (23) includes three horizontal pipes (231) and multiple vertical pipes (232); The three horizontal tubes (231) are arranged in parallel at intervals; Multiple longitudinal tubes (232) are arranged in parallel at intervals and are all vertically sandwiched between two adjacent transverse tubes (231), and both ends are connected to the two transverse tubes (231) respectively; The inner ends of the inlet pipe (21) and the outlet pipe (22) are respectively connected to the opposite ends of a pair of horizontal pipes (231) located in the middle; The two ends of the diversion pipe (24) are respectively connected to the side walls of a pair of horizontal pipes (231) located in the middle.

5. The three-dimensional flow channel heat dissipation device utilizing the inlet section effect according to claim 4, characterized in that, The diverter plate (23) includes nine of the longitudinal tubes (232); The two horizontal tubes (231) located at the top and middle are of the same length and are longer than the horizontal tube (231) located at the bottom. The five longitudinal tubes (232) are arranged in parallel and spaced apart, and are all vertically sandwiched between the two transverse tubes (231) at the top and middle, and are connected at both ends to the two transverse tubes (231); The four longitudinal tubes (232) are arranged in parallel and spaced apart, and are all vertically sandwiched between the two transverse tubes (231) in the middle and below, and their two ends are respectively connected to the two transverse tubes (231).

6. The three-dimensional flow channel heat dissipation device utilizing the inlet section effect according to claim 5, characterized in that, The two ends of the two longitudinal tubes (232) located between the two horizontal tubes (231) at the top and middle and on both sides are connected in series with the two horizontal tubes (231); The bottom ends of the two horizontal tubes (231) located between the middle and lower sections and the two vertical tubes (232) located on both sides are connected in series with the two ends of the horizontal tubes (231) located below. The hydraulic radius of the heat dissipation channel (20) is 3.5 mm.

7. The three-dimensional flow channel heat dissipation device utilizing the inlet section effect according to claim 4, characterized in that, It also includes a flow divider plate (23) and multiple flow divider pipes (24); The three diversion plates (23) are arranged in parallel and spaced apart. The third diversion plate (23) is sandwiched between the first diversion plate (23) and shares the second diversion plate (23), and is connected to the second diversion plate (23) through the diversion pipe (24). The third diverter plate (23) is connected to the second inlet pipe (25), and the fifth surface (15) has a second inlet, which is connected to the second inlet pipe (25).

8. The three-dimensional flow channel heat dissipation device utilizing the inlet section effect according to claim 7, characterized in that, The diversion plate (23) includes eighteen of the longitudinal pipes (232); The nine longitudinal tubes (232) are arranged in parallel at intervals and are all vertically sandwiched between the two transverse tubes (231) at the top and middle, and their two ends are respectively connected to the two transverse tubes (231); The nine longitudinal tubes (232) are arranged in parallel and spaced apart, and are all vertically sandwiched between the two transverse tubes (231) in the middle and below, and their two ends are respectively connected to the two transverse tubes (231).

9. The three-dimensional flow channel heat dissipation device utilizing the inlet section effect according to claim 8, characterized in that, The two ends of the longitudinal tube (232) located on the outside are connected in series with the two transverse tubes (231); The hydraulic radius of the heat dissipation channel (20) is 1.8 mm.

10. The three-dimensional flow channel heat dissipation device utilizing the inlet section effect according to claim 3, characterized in that, The outer walls of the first heat dissipation surface (11), the second heat dissipation surface (12), the third heat dissipation surface (13) and the fourth heat dissipation surface (14) are all covered with printed circuit boards (17), and the inner walls of the printed circuit boards (17) are covered with heating element groups. The heating element assembly includes a large heating element and multiple small heating elements. The large heating element measures 40 mm × 40 mm × 2 mm, and the small heating elements measure 20 mm × 20 mm × 2 mm. The heating element group corresponding to the first heat dissipation surface (11) and the second heat dissipation surface (12) includes 8 small heating elements; The heating element group corresponding to the third heat dissipation surface (13) and the fourth heat dissipation surface (14) includes 4 small heating elements.

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