Non-uniform integrated heat dissipation unit

Abstract

The invention relates to the technical field of heat exchange, in particular to a non-uniform integrated heat dissipation unit. Comprising a plurality of non-uniform fin core body units which are integrated and arranged in a heat dissipation shell side by side; each non-uniform fin core body unit comprises a partition plate, an air side fin set and a working medium channel arranged between the partition plate and the air side fin set. And the air side fin group at least comprises a low-temperature side non-uniform fin group corresponding to the first working medium channel and a high-temperature side non-uniform fin group corresponding to the second working medium channel. Through differentiated fin spacing and length design, flow resistance is reduced through sparse arrangement of low-temperature sides, and heat exchange efficiency is improved through dense arrangement of high-temperature sides; the high-temperature and low-temperature waterway isolation design ensures temperature gradient optimization in the heat exchange process; the overall structure is compact, and the device is suitable for space-limited heat dissipation scenes. Through an innovative non-uniform fin arrangement scheme, collaborative optimization of heat exchange in high and low temperature areas is achieved, and the overall performance of the heat dissipation unit is remarkably improved.

Description

Technical Field

[0001] The present invention relates to the field of heat exchange technology, and in particular to a non-uniform integrated heat dissipation unit. Background Art

[0002] Conventional As the power density of modern vehicles and electronic equipment continues to increase, the heat load generated has increased significantly, which has placed higher demands on the heat dissipation capacity of the thermal management system. In a limited space such as the vehicle's power compartment, it is usually necessary to arrange multiple cooling circuits such as the engine cooling system, the power electronic equipment cooling system, and the battery thermal management system at the same time, which makes the design of the heat dissipation structure face severe space constraint challenges. In this context, the integrated heat dissipation unit has become an effective solution to improve space utilization due to its compactness and modularity. However, how to achieve efficient heat dissipation in a highly integrated structure and meet the differentiated cooling needs of different heat sources remains a technical problem that needs to be solved urgently.

[0003] In a vehicle's thermal management system, the cooling requirements of different components vary significantly. For example, the engine cooling system typically maintains a coolant operating temperature above 100°C, while the coolant temperature of power electronics devices such as IGBT modules must be kept below 80°C to ensure reliable operation. This temperature difference results in distinct heat dissipation characteristics within the cooling system: high-temperature coolant utilizes a large vapor-liquid temperature gradient for efficient heat transfer, while low-temperature coolant requires more precise temperature control to avoid overcooling or local boiling.

[0004] Currently, most common integrated cooling units use a parallel flow channel design, in which each cooling circuit operates independently and performs heat exchange through evenly distributed heat dissipation fins. However, this design approach has obvious limitations in practical applications. For low-temperature cooling circuits, if a dense fin arrangement is used to enhance the heat dissipation effect, the flow channel resistance will increase significantly, thereby increasing pump power loss; if a sparse fin arrangement is used, the cooling requirements of electronic equipment may not be met due to insufficient heat exchange capacity. At the same time, this design approach fails to fully consider the coordinated optimization of high and low temperature cooling circuits. When the coolant in the low-temperature circuit undergoes excessive heat exchange, the vapor-liquid temperature difference when entering the high-temperature circuit will decrease, thereby reducing the heat dissipation efficiency of the high-temperature circuit.

[0005] Therefore, a new integrated cooling unit design is urgently needed. This design, through the serial arrangement of high and low temperature circuits and a differentiated fin layout strategy, can achieve the synergistic optimization of low flow resistance in the low-temperature circuit and efficient heat exchange in the high-temperature circuit. This design requires ensuring a sparse fin layout in the low-temperature circuit to control pressure drop and heat exchange, thereby maintaining a large vapor-liquid temperature difference for the coolant entering the high-temperature circuit. At the same time, an optimized fin layout in the high-temperature circuit is used to fully utilize its heat dissipation potential, ultimately achieving improved overall heat dissipation performance. Summary of the Invention

[0006] The purpose of the present invention is to provide a non-uniform integrated heat dissipation unit to solve the technical problems of uneven heat exchange efficiency in high and low temperature areas and large air-side flow resistance in existing heat dissipation units.

[0007] In order to solve the above technical problems, the present invention adopts the following technical solutions:

[0008] The present invention provides a non-uniform integrated heat dissipation unit, comprising a plurality of non-uniform fin core units integrated and arranged in parallel in a heat dissipation housing;

[0009] The non-uniform fin core unit includes a partition plate, an air-side fin group, and a working medium channel arranged between the partition plate and the air-side fin group;

[0010] The working fluid channel includes at least a first working fluid channel and a second working fluid channel;

[0011] The temperature of the working fluid flowing through the first working fluid channel is lower than the temperature of the working fluid flowing through the second working fluid channel;

[0012] The gas-side fin group includes at least a low-temperature-side non-uniform fin group corresponding to the first working medium channel and a high-temperature-side non-uniform fin group corresponding to the second working medium channel.

[0013] Furthermore, in this embodiment, the low-temperature side non-uniform fin group and the high-temperature side non-uniform fin group both include multiple non-uniform fins arranged at predetermined intervals; the non-uniform fin spacing of the low-temperature side non-uniform fin group is greater than the non-uniform fin spacing of the high-temperature side non-uniform fin group.

[0014] Furthermore, in this embodiment, the non-uniform fin spacing of the low-temperature side non-uniform fin group is 3-4 mm; the non-uniform fin spacing of the high-temperature side non-uniform fin group is 1.5-2.5 mm.

[0015] Furthermore, in this embodiment, the non-uniform fin lengths of the low-temperature side non-uniform fin group and the non-uniform fin lengths of the high-temperature side non-uniform fin group are both gradually changed along the air flow direction to optimize the heat dissipation performance at different positions.

[0016] Furthermore, in this embodiment, strengthening fins are further provided in the non-uniform fin arrangement region of the low-temperature side non-uniform fin group.

[0017] Furthermore, in this embodiment, the fin types of the low-temperature side non-uniform fin group and the high-temperature side non-uniform fin group include serrated fins and corrugated fins.

[0018] Furthermore, in this embodiment, the first working medium channel and the second working medium channel are isolated by high and low temperature water side seals provided on the partition plate.

[0019] Furthermore, in this embodiment, a high-temperature side inlet seal and a low-temperature side inlet seal are provided on one end side of the heat dissipation housing; a low-temperature side outlet seal and a high-temperature side outlet seal are provided on the other end side;

[0020] The working medium inlet end of each of the first working medium channels is connected to the low-temperature side inlet head, and the working medium discharge end thereof is connected to the low-temperature side outlet head;

[0021] The working medium inlet end of each of the second working medium channels is communicated with the high-temperature side inlet head, and the working medium discharge end thereof is communicated with the high-temperature side outlet head.

[0022] Furthermore, in this embodiment, a high-temperature side water inlet is provided on the high-temperature side inlet head; a low-temperature side water inlet is provided on the low-temperature side inlet head; a high-temperature side water outlet is provided on the high-temperature side outlet head; and a low-temperature side water outlet is provided on the low-temperature side outlet head.

[0023] Compared with the prior art, the present invention has the following beneficial technical effects:

[0024] In the present invention, differentiated fin spacing and length designs are adopted, with sparse arrangement on the low-temperature side to reduce flow resistance and dense arrangement on the high-temperature side to improve heat exchange efficiency; the high and low temperature water channel isolation design ensures the optimization of the temperature gradient during the heat exchange process; the overall structure is compact and suitable for heat dissipation scenarios with limited space.

[0025] The present invention achieves coordinated optimization of heat exchange in high and low temperature areas through an innovative non-uniform fin arrangement scheme, significantly improving the overall performance of the heat dissipation unit. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] The present invention will be further described below with reference to the accompanying drawings.

[0027] Figure 1 The present invention is an assembly of a non-uniform integrated heat dissipation unit;

[0028] Figure 2 This is a schematic diagram of the core axial side of a non-uniform integrated heat dissipation unit of the present invention;

[0029] Figure 3 This is a schematic side view of the core end face of a non-uniform integrated heat dissipation unit of the present invention;

[0030] Figure 4 This is a detailed structural diagram of the core of a non-uniform integrated heat dissipation unit of the present invention;

[0031] Figure 5 The core temperature contour map and velocity scalar contour map of the present invention are shown;

[0032] Figure 6 This is the contour diagram of the core velocity scalar of the present invention.

[0033] Explanation of the accompanying drawings: 1-high-temperature side inlet head, 2-high-temperature side water inlet, 3-low-temperature side water inlet, 4-low-temperature side inlet head, 5-non-uniform fin core unit, 51-partition, 52-first working medium channel, 53-high and low-temperature water side seals, 54-second working medium channel, 55-gas side fin group, 551-low-temperature side non-uniform fin group, 552-high-temperature side non-uniform fin group, 553-reinforced fins, 6-low-temperature side outlet head, 7-low-temperature side water outlet, 8-high-temperature side water outlet, 9-high-temperature side outlet head, 10-heat dissipation shell. DETAILED DESCRIPTION

[0034] In this example, a non-uniform integrated heat dissipation unit is provided, comprising a plurality of non-uniform fin core units 5 integrated and arranged in parallel in a heat dissipation housing 10; the non-uniform fin core unit 5 comprises a partition 51, an air-side fin group 55, and a working fluid channel designed and formed between the partition 51 and the air-side fin group 55; the air-side fin group 55 comprises a low-temperature side non-uniform fin group 551 corresponding to the first working fluid channel 52, and a high-temperature side non-uniform fin group 552 corresponding to the second working fluid channel 54; ventilation is performed by means of the air-side fin gaps of the air-side fin group 55, thereby achieving heat dissipation and cooling of the working fluid flowing through the working fluid channel.

[0035] The plurality of non-uniform fin core units 5 can be designed by splitting and splicing; the plurality of non-uniform fin core units 5 can also be designed by welding to form an integral structure that is adapted to the inner size of the heat dissipation housing 10 .

[0036] As an embodiment, the non-uniform fin core unit 5 includes two opposing partitions 51, an air-side fin group 55 installed between the two partitions 51, and a working fluid channel; wherein the air-side fin group 55 and the working fluid channel are independent and isolated from each other; specifically, the separation is performed by a heat-conducting partition.

[0037] In specific implementation, when designing the working fluid channel, multiple working fluid channels may be designed according to different working fluids that need to be used for heat dissipation.

[0038] refer to Figure 1 and Figure 2In this embodiment, the working fluid channel includes a first working fluid channel 52 and a second working fluid channel 54; the temperature of the working fluid flowing in the first working fluid channel 52 is lower than the temperature of the working fluid flowing in the second working fluid channel 54 (taking the engine cooling system as an example, the operating temperature of the coolant is usually maintained above 100°C, while the coolant temperature of power electronic equipment such as IGBT modules needs to be controlled below 80°C to ensure reliable operation); when using this embodiment for synchronous heat dissipation, the temperature of the working fluid flowing in the first working fluid channel 52 is below 80°C, and the temperature of the working fluid flowing in the second working fluid channel 54 is maintained above 100°C.

[0039] The first working fluid channel 52 and the second working fluid channel 54 are isolated by the high and low temperature water side seals 53 installed on the partition 51. The non-uniform fin core unit 5 achieves physical isolation of the high and low temperature side water flows through the partition 51 and the high and low temperature water side seals 53 arranged inside it, and at the same time uses the air side fin group 55 to perform efficient heat exchange with the forced convection air. Specifically, under the action of the negative pressure of the fan, the ambient air flows through the surface of the air side fin group 55, taking away the heat absorbed by the fins from the water side, thereby achieving continuous heat dissipation of the system. Among them, the differentiated arrangement of the low temperature side non-uniform fin group 551 and the high temperature side non-uniform fin group 552 is used for heat exchange with the forced convection air, ensuring that the heat exchange efficiency of the air flow in different temperature zones is optimized.

[0040] As another implementation, a fan may be directly used to provide positive wind pressure or compressed air may be used for blowing, and the fins may absorb the heat from the water side and take it away, thereby achieving continuous heat dissipation of the system.

[0041] refer to Figure 1 In this example, a high-temperature side inlet head 1 and a low-temperature side inlet head 4 are installed on one end of the heat dissipation housing 10; a low-temperature side outlet head 6 and a high-temperature side outlet head 9 are installed on the other end; wherein the working medium inlet end of each first working medium channel 52 is connected to the low-temperature side inlet head 4, and the working medium outlet end thereof is connected to the low-temperature side outlet head 6; the working medium inlet end of each second working medium channel 54 is connected to the high-temperature side inlet head 1, and the working medium outlet end thereof is connected to the high-temperature side outlet head 9. A high-temperature side water inlet 2 is installed on the high-temperature side inlet head 1; a low-temperature side water inlet 3 is installed on the low-temperature side inlet head 4; a high-temperature side water outlet 8 is installed on the high-temperature side outlet head 9; and a low-temperature side water outlet 7 is installed on the low-temperature side outlet head 6.

[0042] As an embodiment, the cooling medium with a temperature of about 80°C can be provided to the low-temperature side inlet head 4 through the low-temperature side water inlet 3. After entering each of the first working medium channels 52, the cooling medium is ventilated and dissipated by the air side fin group 55 outside the first working medium channel 52, and then discharged through the low-temperature side outlet head 6 and the low-temperature side water outlet 7.

[0043] Similarly, after passing through the high-temperature side water inlet 2 and the high-temperature side inlet head 1 to each second working medium channel 54, the cooled working medium is ventilated and dissipated by the gas side fin group 55 outside the first working medium channel 52, and then discharged through the high-temperature side outlet head 9 and the high-temperature side water outlet 8.

[0044] Specifically, when ventilation and heat dissipation are performed through the air-side fin group 55, under the action of the negative pressure of the fan, the ambient air flows through the surface of the air-side fin group 55, and takes away the heat absorbed by the fins from the water side, thereby achieving continuous heat dissipation of the system; and the heat dissipation air preferentially passes through the air-side fins on the outer wall of the second working fluid channel 54 with a higher temperature, so as to improve the heat dissipation efficiency and meet the heat dissipation requirements of each working fluid channel.

[0045] In this embodiment, the low-temperature side non-uniform fin group 551 and the high-temperature side non-uniform fin group 552 both include multiple non-uniform fins arranged at predetermined intervals; the non-uniform fin spacing of the low-temperature side non-uniform fin group 551 is greater than the non-uniform fin spacing of the high-temperature side non-uniform fin group 552.

[0046] As an embodiment, the non-uniform fin pitch of the low-temperature side non-uniform fin group 551 is 3.5 mm; the non-uniform fin pitch of the high-temperature side non-uniform fin group 552 is 2 mm.

[0047] This design, based on the thermodynamic characteristics of a large temperature difference between the air and water sides during the initial heat exchange phase, reduces air flow resistance through a relatively sparse fin arrangement, allowing air to enter the heat exchange area with a low pressure drop, ensuring efficient heat transfer during the initial heat exchange phase. This design addresses the fact that the air temperature rises after heat exchange on the low-temperature side and the temperature difference with the water side decreases. By increasing the fin density, the heat exchange area is increased, fully tapping the remaining heat exchange potential on the high-temperature side.

[0048] Specifically, according to the actual temperature difference of the working fluid flowing through the first working fluid channel 52 and the second working fluid channel 54, the non-uniform fin spacing of the low-temperature side non-uniform fin group 551 needs to be set to 3.0 mm; the non-uniform fin spacing of the high-temperature side non-uniform fin group 552 needs to be set to 1.5 mm, or the non-uniform fin spacing of the low-temperature side non-uniform fin group 551 needs to be set to 4.0 mm; the non-uniform fin spacing of the high-temperature side non-uniform fin group 552 needs to be set to 2.5 mm.

[0049] In this embodiment, the length of the non-uniform fins of the low-temperature side non-uniform fin group 551 and the length of the non-uniform fins of the high-temperature side non-uniform fin group 552 are gradually shortened along the air flow direction to optimize the heat dissipation performance at different positions.

[0050] refer to Figure 4 Preferably, a plurality of strengthening fins 553 are installed in the significantly thickened area of ​​the heat transfer boundary layer of the low-temperature side non-uniform fin group 551. The strengthening fins 553 destroy the stable development of the air thermal boundary layer through the surface turbulence structure.

[0051] In specific implementation, the fin types of the low-temperature side non-uniform fin group 551 and the high-temperature side non-uniform fin group 552 include serrated fins, corrugated fins, or a combination of the two. In addition, the fins of the non-uniform fin core 5 are made of a good thermal conductive metal, preferably aluminum alloy.

[0052] The heat dissipation channels have a highly symmetrical structure, so the flow rate entering each channel can be assumed to be the same. To simplify the simulation, four channels were selected, the geometry was constructed, and symmetrical boundaries were set on both sides for numerical simulation to analyze the flow and heat transfer performance of a non-uniform integrated heat dissipation unit.

[0053] CFD simulation software was used to simulate a non-uniform integrated heat dissipation unit. The heat dissipation unit is made of aluminum, with air as the heat exchange medium on the cold side and water as the heat exchange medium on the hot side. Considering the comprehensive performance impact of flow resistance, PEC was set as the response indicator, and the evaluation index was:

[0054] PEC=Q / P 1 / 3 .

[0055] Where Q is the heat transfer capacity on the cold side, and P is the pressure drop on the cold side. A larger PEC indicates better overall flow and heat transfer performance.

[0056] The boundaries are set based on the operating conditions of the cooling unit. The cold side heat exchange medium inlet temperature is set to 35°C and the flow rate is set to 10.91 m / s. The low temperature side heat exchange medium inlet 52 is set to 90°C and the flow rate is set to 1 m / s. The high temperature side heat exchange medium inlet 54 is set to 125°C and the flow rate is set to 1 m / s.

[0057] Simulation results:

[0058] Table 1 shows the performance comparison between the common heat dissipation unit design and the non-uniform design.

[0059] Cooling unit design Pressure drop (Pa) Heat dissipation (W) PEC Non-uniform design 1086.36 121.04 11.77 Uniform encryption design 2396.74 133.66 9.99 Uniformly sparse design 315.76 75.98 11.16

[0060] The flow velocity and temperature distribution inside the heat dissipation channel are as follows: Figure 5 and Figure 6As shown in the figure, on the high-temperature side, the non-uniform fins disrupt boundary layer growth multiple times through denser finning, increasing local flow velocity and enhancing overall heat transfer performance. On the low-temperature side, the sparser fins reduce flow resistance. These characteristics result in the best overall performance of the non-uniform heat dissipation channel, improving overall performance by 17.82% compared to a denser design and 5.47% compared to a sparser design.

[0061] The above embodiments are merely descriptions of preferred embodiments of the present invention and are not intended to limit the scope of the present invention. Without departing from the spirit of the present invention, various modifications and improvements made to the technical solutions of the present invention by persons skilled in the art shall fall within the scope of protection defined by the claims of the present invention.

Claims

1. A non-uniform integrated heat dissipation unit, characterized in that: It comprises a plurality of non-uniform fin core units (5) integrated and arranged in parallel in a heat dissipation housing (10); The non-uniform fin core unit (5) comprises a partition plate (51), an air-side fin group (55), and a working medium channel arranged between the partition plate (51) and the air-side fin group (55); The working fluid channel comprises at least a first working fluid channel (52) and a second working fluid channel (54); The temperature of the working fluid flowing through the first working fluid channel (52) is lower than the temperature of the working fluid flowing through the second working fluid channel (54); The gas-side fin group (55) comprises at least a low-temperature-side non-uniform fin group (551) corresponding to the first working medium channel (52) and a high-temperature-side non-uniform fin group (552) corresponding to the second working medium channel (54).

2. The non-uniform integrated heat dissipation unit according to claim 1, characterized in that: The low-temperature side non-uniform fin group (551) and the high-temperature side non-uniform fin group (552) both include a plurality of non-uniform fins arranged at a predetermined spacing; the non-uniform fin spacing of the low-temperature side non-uniform fin group (551) is greater than the non-uniform fin spacing of the high-temperature side non-uniform fin group (552).

3. The non-uniform integrated heat dissipation unit according to claim 2, wherein: The non-uniform fin spacing of the low-temperature side non-uniform fin group (551) is 3.0-4.0 mm; the non-uniform fin spacing of the high-temperature side non-uniform fin group (552) is 1.5-2.5 mm.

4. The non-uniform integrated heat dissipation unit according to claim 3, wherein: The non-uniform fin lengths of the low-temperature side non-uniform fin group (551) and the non-uniform fin lengths of the high-temperature side non-uniform fin group (552) are both gradually changed along the air flow direction to optimize heat dissipation performance at different positions.

5. The non-uniform integrated heat dissipation unit according to claim 4, characterized in that: Strengthening fins (553) are further provided in the non-uniform fin arrangement area of ​​the low-temperature side non-uniform fin group (551).

6. The non-uniform integrated heat dissipation unit according to claim 5, characterized in that: The fin types of the low-temperature side non-uniform fin group (551) and the high-temperature side non-uniform fin group (552) include serrated fins and corrugated fins.

7. The non-uniform integrated heat dissipation unit according to claim 1, characterized in that: The first working medium channel (52) and the second working medium channel (54) are isolated by a high and low temperature water side seal (53) provided on the partition plate (51).

8. The non-uniform integrated heat dissipation unit according to claim 1, characterized in that: A high-temperature side inlet seal (1) and a low-temperature side inlet seal (4) are provided on one end side of the heat dissipation housing (10); a low-temperature side outlet seal (6) and a high-temperature side outlet seal (9) are provided on the other end side thereof; The working medium inlet end of each of the first working medium channels (52) is in communication with the low-temperature side inlet head (4), and the working medium discharge end thereof is in communication with the low-temperature side outlet head (6); The working medium inlet end of each second working medium channel (54) is in communication with the high-temperature side inlet head (1), and the working medium discharge end thereof is in communication with the high-temperature side outlet head (9).

9. The non-uniform integrated heat dissipation unit according to claim 8, characterized in that: The high-temperature side inlet seal (1) is provided with a high-temperature side water inlet (2); the low-temperature side inlet seal (4) is provided with a low-temperature side water inlet (3); the high-temperature side outlet seal (9) is provided with a high-temperature side water outlet (8); and the low-temperature side outlet seal (6) is provided with a low-temperature side water outlet (7).

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