CN118943573A

CN118943573A - Heat exchange plate and battery module

Info

Publication number: CN118943573A
Application number: CN202411000147.0A
Authority: CN
Inventors: 汪朝晖; 熊肖; 张博文; 周子杨; 高全杰; 王红霞
Original assignee: Wuhan University of Science and Technology WHUST; Hubei University of Automotive Technology
Current assignee: Wuhan University of Science and Technology WHUST; Hubei University of Automotive Technology
Priority date: 2024-07-24
Filing date: 2024-07-24
Publication date: 2024-11-12

Abstract

The invention provides a heat exchange plate and a battery module, which relate to the technical field of batteries, and comprise a runner plate and a cover plate, wherein a liquid cavity is concavely formed on the surface of the runner plate, a plurality of honeycomb-shaped arranged turbulence structures are fixedly arranged in the liquid cavity, each turbulence structure consists of a central turbulence column and at least one ring-shaped bulge concentrically surrounding the outer side of the turbulence column, each turbulence column and each ring-shaped bulge are of a regular hexagon structure, the annular bulges and the edges of the turbulence columns are arranged in parallel, a first flow passage is arranged between the annular bulges and the turbulence columns and between the annular bulges, a second flow passage is arranged between the annular bulges of the outermost ring of each two adjacent turbulence structures, and flow guide ports communicated with the first flow passage and the second flow passage are respectively arranged at two end points of each annular bulge in the horizontal direction. The invention not only reduces the pressure loss when the liquid enters and exits, but also ensures the consistency of the temperature field in the liquid cavity of the whole heat exchange plate, and effectively improves the heat exchange quality and the stability of the system.

Description

Heat exchange plate and battery module

Technical Field

The invention relates to the technical field of battery thermal management, in particular to a heat exchange plate and a battery module.

Background

The lithium ion battery has the advantages of long cycle life, low self-discharge rate, high energy density and the like, and is widely used as a power source of an electric automobile. However, lithium ion batteries are very sensitive to temperature, and related literature indicates that the optimal operating temperature of lithium ion batteries is 20-40 ℃ and the temperature differential of the battery pack is controlled below 5 ℃. The excessive temperature of the battery can cause thermal runaway, and lithium dendrite can be formed when the temperature is too low, so that the safety, reliability and effectiveness of the battery are seriously affected. Therefore, in order to accommodate a complex vehicle environment, a battery thermal management system is urgently required to maintain the optimal operating temperature and temperature uniformity of the battery module.

Different types of battery thermal management systems have been developed, mainly divided into active and passive systems, including air cooling, liquid cooling, phase change material cooling, and heat pipe cooling. The air cooling is widely applied to the electric automobile due to the simple design, low cost and simple maintenance requirement. But air cooling does not meet thermal management requirements at high discharge rates and or high operating temperatures. The phase change material cooling is widely focused and studied because of the advantages of good economy, simple structure, no additional energy consumption and the like, but the heat conductivity of the working medium is still too low to realize effective heat transfer and heat management, and the phase change material cooling is expensive and is not widely applied to a battery heat management system. The heat pipe cooling has high heat conducting performance to realize efficient heat dissipation and accurate temperature control, but has higher design and maintenance cost and is limited by working temperature. In contrast, liquid cooling not only has efficient heat dissipation capability, but also can be applied in high-temperature working environments. Can provide a better solution for the great requirement of high-rate charge and discharge of the electric automobile at present.

At present, in the process of designing a battery thermal management system, the power consumption required by solving the heat dissipation problem is often needed to be considered, so that the endurance mileage of the electric automobile is increased. The liquid cooling system realizes the circulation flow of the heat exchange medium through the water pump, and the power consumption of the water pump has great influence on the endurance mileage of the electric automobile. At present, the heat exchange plate mode adopted in the traditional liquid cooling battery thermal management system mostly can not simultaneously meet the double-layer function requirements of heat dissipation and pumping power consumption of the liquid cooling system due to the limitation of a runner structure, namely, on one hand, the heat exchange uniformity of heat exchange of the battery module can not be realized by the heat exchange plate, and on the other hand, the overall pressure drop of the heat exchange plate is larger, so that the power consumption of a water pump in the thermal management system is increased, and the requirements of low energy consumption and balanced temperature control of the battery thermal management system can not be met.

Disclosure of Invention

In view of the above, the invention provides a heat exchange plate and a battery module, which can reduce the inlet and outlet pressure drops of the heat exchange plate while keeping the temperature consistency in the battery module, thereby saving the power consumption of a water pump for driving the cooling liquid to circularly flow and further improving the effective utilization efficiency of energy.

The technical scheme of the invention is realized as follows:

in one aspect, the invention provides a heat exchange plate, which comprises a runner plate and a cover plate, wherein a liquid cavity is concavely formed on the surface of the runner plate, the cover plate is arranged on the surface of the runner plate and forms a seal with the periphery of the liquid cavity, and the runner plate or the cover plate is provided with a liquid inlet and a liquid outlet which are communicated with the liquid cavity along the liquid flowing direction;

The liquid cavity is internally and fixedly provided with a plurality of honeycomb-shaped arranged turbulent flow structures, the top of each turbulent flow structure is contacted with the bottom surface of the cover plate, each turbulent flow structure is formed by a central turbulent flow column and at least one ring of annular protrusions concentrically surrounding the outer side of the turbulent flow column, each ring of annular protrusions is of a regular hexagon structure, the edges of each ring of annular protrusions and the turbulent flow column are kept in edge-to-edge parallel arrangement, first flow channels are arranged between each annular protrusion and each turbulent flow column and between the corresponding ring of annular protrusions, second flow channels are arranged between the annular protrusions of the outermost ring of each two adjacent turbulent flow structures, flow guide ports are respectively arranged at two end points of each annular protrusion in the horizontal direction, and the flow guide ports are communicated with the first flow channels and the second flow channels.

On the basis of the above technical solution, preferably, the wall thickness of each annular protrusion is the same.

On the basis of the above technical solution, preferably, the opening direction of each flow guiding port is parallel to the flowing direction of the liquid and corresponds to the second flow passage between the adjacent turbulence structures.

Further, preferably, the widths of the diversion port and the second flow passage are the same.

Still further, preferably, the first flow channel and the second flow channel have the same width.

On the basis of the technical scheme, preferably, an upward inclination angle is arranged on the surface, connected with the cover plate, of the flow channel plate along the liquid flowing direction, and the bottom surface of the cover plate is obliquely matched with the surface of the flow channel plate.

Preferably, the inclination angle is 0.1 ° to 1 °.

On the basis of the technical scheme, preferably, the liquid cavity comprises a liquid inlet cavity, a flow distribution cavity and a liquid outlet cavity which are sequentially arranged along the flowing direction of liquid, the liquid inlet and the liquid inlet cavity are communicated, the liquid outlet and the liquid outlet cavity are communicated, and a plurality of honeycomb-shaped distributed turbulence structures are arranged in the flow distribution cavity.

Preferably, a third flow passage is arranged between the inner wall of the flow distribution cavity and the adjacent turbulence structure, and the widths of the third flow passage and the first flow passage are the same.

In a second aspect, the invention also discloses a battery module, which comprises a plurality of single batteries and the heat exchange plate, wherein the single batteries are stacked and arranged on the surface of the cover plate of the heat exchange plate.

Compared with the prior art, the invention has the following beneficial effects:

(1) The heat exchange plate disclosed by the invention combines a streamline flow passage plane and a honeycomb structure, creates a complex and ordered flow path, improves the turbulence degree of the contact surface of fluid and the heat exchange plate, promotes heat transfer along a high-efficiency path, and improves the overall heat exchange efficiency. On the basis, the annular protrusions of each turbulence structure are arranged in parallel with the turbulence columns and concentrically arranged so that the distances between the first flow passages are equal, the uniform fluid flow velocity is facilitated, the occurrence of velocity peaks or valleys is avoided, the formation probability of a heat concentration area is reduced, and more uniform temperature distribution is realized. At the same time, this configuration is advantageous in that the pressure drop can be further reduced by a smooth transition of the carefully designed second flow path when the fluid moves between the turbulence structures, since the continuous and equal flow path reduces the resistance in the flow and controls the acceleration of the fluid, avoiding additional pressure losses due to abrupt changes in the fluid flow conditions. In addition, the fluid can be switched between different flow passages more flexibly due to the existence of the flow guide port of each annular bulge end point, so that the dynamic coordination of the liquid inlet and outlet is maintained. The comprehensive design not only reduces the pressure loss during the liquid inlet and outlet, but also ensures the consistency of the temperature field in the liquid cavity of the whole heat exchange plate, and effectively improves the heat exchange quality and the system stability.

(2) The annular protrusions with the same wall thickness provide structural uniformity and thermal management balance for the heat exchange plate, so that the heat exchange plate can effectively improve thermal stability and energy efficiency in heat exchange occasions.

(3) The consistency of the parallel design of the flow guide openings and the fluid flow direction and the direct corresponding layout of the flow guide openings and the second flow channels enhance the hydrodynamic efficiency and the heat exchange balance of the heat exchange plate, so that the overall performance of the heat exchange plate is optimized.

(4) The uniformity of the widths of the first flow channel and the second flow channel is beneficial to realizing efficient, stable and uniform fluid flow and heat exchange, pressure drop and uneven heat distribution caused by improper flow channel design are reduced, and the overall performance of the heat exchange plate in the use process is improved.

(5) The inclined angle is arranged on the surface of the flow passage plate along the flowing direction of the liquid, so that a design combining hydrodynamic force and thermodynamics is provided, and the potential energy and the kinetic energy of the fluid can be regulated by increasing the sectional area of the flow passage while the liquid is gradually heated and the potential energy is increased along with the gradual increase of the turbulence structure in the flowing direction of the liquid, so that the hydrodynamic pressure drop is reduced, and meanwhile, the local heat distribution nonuniformity caused by the difference of flow velocity is reduced.

Drawings

In order to more clearly illustrate the embodiments of the invention or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, it being obvious that the drawings in the following description are only some embodiments of the invention, and that other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.

FIG. 1 is a schematic perspective view of a heat exchanger plate according to the present disclosure;

FIG. 2 is a schematic perspective view of a flow field plate according to the present disclosure;

FIG. 3 is a schematic plan view of a heat exchanger plate of the present disclosure;

fig. 4 is a schematic perspective view of a battery module according to the present disclosure;

Reference numerals:

1. A flow channel plate; 2. a cover plate; 10. a liquid chamber; 12. a liquid inlet; 13. a liquid outlet; 14. a turbulence structure; 141. a turbulent flow column; 142. an annular protrusion; l1, a first runner; l2, a second runner; 1421. a diversion port; 101. a liquid inlet cavity; 102. a shunt cavity; 103. a liquid outlet cavity; l3, a third runner; 3. and (3) a single battery.

Detailed Description

The following description of the embodiments of the present invention will clearly and fully describe the technical aspects of the embodiments of the present invention, and it is apparent that the described embodiments are only some embodiments of the present invention, not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the present invention without making any inventive effort, are intended to fall within the scope of the present invention.

As shown in fig. 1 and 2, the embodiment of the invention discloses a heat exchange plate, which comprises a flow channel plate 1 and a cover plate 2, wherein a liquid cavity 10 is concavely formed on the surface of the flow channel plate 1, the liquid cavity 10 is used for cooling liquid to flow through, and the cover plate 2 is arranged on the surface of the flow channel plate 1 and forms a seal with the periphery of the liquid cavity 10, so that the cooling liquid can be ensured not to leak when flowing in the liquid cavity 10, and a closed environment is provided for efficient heat exchange. The flow channel plate 1 or the cover plate 2 is provided with a liquid inlet 12 and a liquid outlet 13 which are communicated with the liquid cavity 10 in the liquid flow direction, and the liquid inlet 12 and the liquid outlet 13 are respectively connected through a cooling liquid pipeline and a liquid cooling liquid circulating system, so that the cooling liquid can circulate through the liquid cavity 10, and heat exchange is realized on a battery arranged on the heat exchange plate.

In order to realize the formation of a flow channel structure in the liquid cavity 10, heat exchange and temperature equalization can be realized in the process of flowing the cooling liquid in the liquid cavity 10, and meanwhile, the pressure drop of an inlet and an outlet is reduced, and the flow channel plate 1 is structurally arranged in the embodiment.

Specifically, the liquid chamber 10 internal fixation is provided with a plurality of honeycomb vortex structures 14 of arranging, the top of vortex structure 14 contacts with the bottom surface of apron 2, every vortex structure 14 comprises central vortex post 141 and the annular protruding 142 of at least one circle concentric ring in the vortex post 141 outside, vortex post 141 and annular protruding 142 are regular hexagon structure, adopt such structure setting, honeycomb vortex structure 14's arrangement has increased the turbulence of coolant liquid and heat exchanger plate contact surface on the one hand, on the other hand has promoted the even distribution of coolant liquid in liquid chamber 10, the heat exchange area has been increased to the regular hexagon design of vortex post 141 and annular protruding 142 for the temperature is more even, reduces the formation of local hot spot, improves the efficiency of heat exchange.

The annular bulges 142 of each circle are arranged in parallel with the edges of the turbulent flow column 141 in an edge-to-edge manner, and first flow passages L1 are arranged between the annular bulges 142 and the turbulent flow column 141 and between the annular bulges 142 of each circle, so that the arrangement is that the surface area of liquid in contact with the heat exchange plate can be increased by the first flow passages L1 in the turbulent flow structure 14, heat conduction is more uniform, and better uniform temperature effect is realized. All the annular protrusions 142 and the edges of the corresponding turbulence columns 141 are aligned in parallel on each ring layer to form a regular honeycomb shape, and the parallel arrangement ensures that liquid can flow more uniformly in the first flow channels L1 of each ring stage, local high-speed flow or blocking phenomenon is avoided, and pressure drop generated by fluid flow is stabilized. Due to the regular arrangement of the first flow channels L1, the hydrodynamic characteristics are uniform, the heat distribution in the heat exchange plate is balanced, and the formation of hot spots is prevented.

The second flow passage L2 is arranged between the annular protrusions of the outermost rings of the two adjacent turbulence structures 14, and the second flow passage L2 enables fluid to be transferred between the turbulence structures 14 freely. The adjacent turbulence structures 14 are connected through the second flow passage L2, so that the contact area and time between the fluid and the heat exchange plate are increased, and the heat exchange efficiency is improved.

Each annular projection 142 is provided with a diversion port 1421 at two end points in the horizontal direction, and the diversion port 1421 is communicated with the first flow passage L1 and the second flow passage L2. With this structural arrangement, the flow-directing port 1421 acts as an interface between the first and second flow paths L1, L2, allowing a smooth transition of fluid between the two flow paths, minimizing pressure variations and turbulence that may occur as the direction of fluid flow changes. In addition, the presence of the flow directing ports 1421 reduces kinetic energy loss as fluid is transferred from one flow channel to another, helping to maintain a lower overall system pressure drop while promoting a more uniform temperature profile.

The heat exchange plate disclosed by the invention combines a streamline flow passage plane and a honeycomb structure, creates a complex and ordered flow path, improves the turbulence degree of the contact surface of fluid and the heat exchange plate, promotes heat transfer along a high-efficiency path, and improves the overall heat exchange efficiency. On this basis, the parallel arrangement and concentric arrangement of the annular protrusion 142 of each turbulence structure 14 and the turbulence column 141 make the distance between the first flow passages L1 equal, which is conducive to unifying the fluid flow rate, and avoids occurrence of speed peaks or valleys, thereby reducing the formation probability of the heat concentration area and realizing more uniform temperature distribution. At the same time, this configuration is advantageous in that the pressure drop can be further reduced by a smooth transition of the carefully designed second flow path L2 as the fluid moves between the turbulence structures 14, since the continuous and equal flow path reduces the resistance in the flow and controls the acceleration of the fluid, avoiding additional pressure losses due to abrupt changes in the fluid flow conditions. In addition, the fluid can be switched between different channels more flexibly due to the existence of the flow guiding ports 1421 at the end points of each annular bulge 142, so that the dynamic coordination of the liquid inlet and outlet is maintained. The comprehensive design not only reduces the pressure loss during the liquid inlet and outlet, but also ensures the consistency of the temperature field in the liquid cavity 10 of the whole heat exchange plate, and effectively improves the heat exchange quality and the stability of the system.

In the above embodiment, the wall thickness of each of the annular projections 142 is the same. The annular protrusion 142 of uniform wall thickness helps achieve several key thermal management properties:

1) Uniformity of structural strength and heat conduction: the uniform wall thickness of the annular projection 142 provides for uniform structural strength of these components throughout the heat exchange plate and a uniform distribution of internal liquid pressure that is tolerated, thereby avoiding uneven expansion, contraction or thermal stress build-up due to non-uniform wall thickness. In addition, the annular projections 142 of the same wall thickness ensure uniformity and stability in conduction of heat within the material.

2) Balanced heat distribution: since the wall thickness of all the annular protrusions 142 is the same, their thermal response characteristics during heat exchange are comparable, which helps to provide a smooth and uniform heat flow distribution, so that the temperatures of the parts of the heat exchange plate are more uniform, and thermal stress caused by temperature differences is effectively reduced.

3) Control of pressure drop: the annular projection 142 of equal wall thickness facilitates maintaining pressure uniformity of the fluid as it passes through the flow channels during fluid flow, as the geometric uniformity of the flow channels reduces localized flow rate variations due to abrupt structural changes. This reduces not only the power loss of the liquid in the flow, but also the vortex generation at the flow passage junction, thereby controlling the overall pressure drop.

In summary, annular protrusions 142 having the same wall thickness provide structural uniformity and thermal management balance to the heat exchanger plate, enabling effective thermal stability and energy efficiency enhancement in heat exchange applications, particularly in demanding temperature and pressure drop management scenarios.

Notably, the turbulence structures 14 of the plurality of annular projections 142 may gradually slow the increase in liquid velocity. As the liquid passes each ring of annular projections 142, it undergoes a series of expansion and compression processes, increasing surface contact and turbulence without creating excessive velocity, which can help to avoid significant pressure loss of the liquid during flow.

Second, the different levels of flow passages formed by the plurality of annular projections 142 allow the liquid to flow in a wider area distribution, thereby reducing the fluid flow rate and corresponding resistance within a single first flow passage L1. Dispersing the fluid makes the flow rate of each first flow path L1 more controllable, and thus the overall pressure drop due to the acceleration of the fluid can be reduced.

Due to the design between each annular projection 142 and the first flow path L1, the fluid will create more turbulence during the flow. The appropriate amount of turbulence can improve the heat exchange efficiency, and simultaneously, because a plurality of contact points of the edge of the first flow channel L1 and the liquid are uniformly distributed, the mixing degree is higher, the resistance to the liquid is more evenly dispersed, and the pressure gradient along the flowing direction is reduced. While turbulence is typically associated with energy losses, the multi-turn structure ensures that the turbulent energy generated is accelerating heat transfer rather than being wasted, which allows the energy of the fluid to be effectively utilized for heat exchange rather than the inefficient loss of kinetic energy due to the too high flow rate.

In summary, the provision of the plurality of annular projections 142 achieves a combination of reducing the pressure drop across the system during fluid flow by decelerating the fluid, dispersing the flow path resistance, increasing the amount of turbulence, and optimizing energy utilization.

As some preferred embodiments, the opening direction of each diversion opening 1421 is parallel to the liquid flow direction and corresponds to the second flow path L2 between the adjacent turbulence structures 14.

With the above technical solution, the opening direction of the flow guiding port 1421 is set parallel to the liquid flow direction so that the liquid can directly flow into or out of the flow guiding port 1421 without significant change in direction. This is critical to minimize hydrodynamic losses. When the fluid does not need to turn sharply, it can flow more smoothly, thereby reducing the generation of vortex and friction with the flow passage wall surface.

Second, because the flow-directing port 1421 is parallel to the direction of liquid flow, the fluid does not encounter too much resistance in entering and exiting the second flow path L2. This helps to maintain a low pressure drop and high fluid flow efficiency, particularly where rapid heat removal is desired, such as in battery cooling or high performance heat exchange devices, which can significantly improve the overall thermal efficiency of the system.

By the corresponding arrangement with the second flow channels L2, the flow guiding ports 1421 ensure that fluid directly flows into or out of these flow channels, assisting in achieving an even distribution of heat over the heat exchanger plate. Since such geometric designs allow for uniform dispersion of the hot fluid from the spoiler structure 14, they help reduce local temperature gradients, thereby maintaining uniform temperatures throughout the various parts of the device, preventing the creation of overheated or undercooled areas.

In summary, the consistency of the parallel design of the flow guiding ports 1421 with the fluid flow direction and the direct corresponding layout with the second flow channels L2 enhances the hydrodynamic efficiency and heat exchange balance of the heat exchanger plate. This allows the overall performance of the heat exchange plate to be optimized, and the benefits of these design improvements are particularly pronounced in battery field applications where there are severe demands on temperature control and pressure drop management.

As some preferred embodiments, the diversion port 1421 and the second flow path L2 have the same width. By adopting the technical scheme, the device has the following technical effects:

1) Fluid ingress and egress smoothness: the flow-directing port 1421 is the same width as the second flow channel L2 such that the cross-sectional area of the flow channel remains uniform as fluid enters the second flow channel L2 from the flow-directing port 1421 or exits the second flow channel L2. Such a design reduces liquid velocity changes and possible pressure fluctuations due to abrupt flow path cross-section, thereby making the ingress and egress of liquid smoother and helping to maintain consistent flow rates and pressure levels.

2) Reducing the local pressure drop: the uniformity of the flow-directing ports 1421 of the same width with the flow channels reduces the localized pressure drop as liquid passes through these regions. Pressure losses are typically experienced when the liquid passes through the compressed or expanded region in the flow passage, but this is significantly reduced by the matching of the width of the flow-directing port 1421 to the second flow passage L2.

3) Optimizing flow channel fluid dynamics: this design helps to optimize the fluid dynamics within the flow channel and avoids the formation of unstable flows and turbulence due to the variation in the cross-sectional area of the flow channel. The fluid is more stable when flowing in channels of the same width, reducing the occurrence of eddy currents, which is critical for reducing energy losses and improving heat exchange efficiency.

4) Enhancing heat exchange efficiency: the uniformity of the widths of the flow guiding ports 1421 and the second flow passages L2 also contributes to the uniform distribution of the liquid in the heat exchange plate, thereby enhancing the heat exchange efficiency. The fluid can cover the whole heat exchange plate more evenly, so that the overall heat transfer balance is improved, and the maintenance of the temperature uniformity of the whole system is facilitated.

In summary, the consistent design of the flow-directing ports 1421 and the second flow path L2 simplifies the complexity of the hydrodynamic system, helping to achieve efficient thermal management and fluid control, which is critical to improving the energy transfer of the working medium in the heat exchanger plates and reducing the cost of system operation.

As some preferred embodiments, the widths of the first flow channel L1 and the second flow channel L2 are the same, and the above technical scheme is adopted, which has the following technical effects:

1) Fluid flow consistency: the widths of the first flow channel L1 and the second flow channel L2 are the same, so that the consistency of the flow conditions of the fluid in the two flow channels is ensured, and the flow speed change caused by the difference of the widths of the flow channels is reduced, thereby reducing the possibility of causing liquid turbulence and power loss. The fluid is smoothly transferred between different flow channels, so that the stability of the flow is maintained.

2) System pressure drop minimization: the uniform width of the flow channels helps to avoid additional pressure drop due to abrupt cross-sectional changes during fluid flow from the first flow channel L1 into the second flow channel L2 or back. This allows the liquid to flow at nearly constant pressure conditions, minimizing system pressure losses and ensuring efficient use of pumping energy.

3) Uniform temperature distribution: ensuring uniformity of the widths of the first and second flow channels L1 and L2 helps to achieve the same heat exchange conditions at different locations, thereby maintaining a uniform temperature distribution across the heat exchange plate. Such uniform temperature control is important, particularly in applications requiring tight temperature control (e.g., battery cooling systems), to improve device performance and lifetime.

4) And the heat exchange efficiency is improved: the equal-width design of the first flow channel L1 and the second flow channel L2 optimizes the heat transfer path of the liquid, and the equal-width flow channels can more fully utilize a given space to perform heat exchange, so that the operation efficiency is improved.

In general, the consistency of the widths of the first flow channel L1 and the second flow channel L2 is beneficial to realizing efficient, stable and uniform fluid flow and heat exchange, reducing pressure drop and uneven heat distribution caused by improper flow channel design, and improving the overall performance of the heat exchange plate in the use process.

Since the temperature of the outlet is higher than that of the inlet end in the flow of the cooling liquid in the flow channel plate 1 in the flowing direction of the liquid, the temperature difference is larger. For this reason, the scheme adopted in this embodiment is: the surface of the runner plate 1 connected with the cover plate 2 is provided with an upward inclination angle along the liquid flowing direction, and the bottom surface of the cover plate 2 is obliquely matched with the surface of the runner plate 1.

By adopting the technical scheme, the surface of the runner plate 1 is arranged in an upward inclined manner from the liquid inlet 12 to the liquid outlet 13, so that the depth of the liquid cavity 10 is gradually increased along the liquid flowing direction, and correspondingly, the height of the turbulence structure 14 is also increased. This design helps to gradually adjust the volume within the liquid chamber 10 over long distances of flow, providing further room for heat to spread. As the liquid gradually increases in temperature from the liquid inlet end to the liquid outlet end, the increased volume of the liquid chamber 10 may partially alleviate the temperature increase at the end of the liquid chamber 10, since given the same heat input, the enlarged space allows the heat to be dispersed over a larger area, thereby reducing the local temperature gradient.

Second, as the depth of the liquid chamber 10 increases gradually in the liquid flow direction, the heights of the first and second flow passages L1 and L2 also increase in the liquid flow direction, and the liquid has a larger cross-sectional area during the flow. The larger flow channels can reduce the flow rate per unit area of liquid, thereby reducing pressure losses due to too fast flow rates. This design allows the liquid to have a lower fluid velocity in the high temperature region near the liquid outlet end, helping to reduce the pressure drop effect of fluid expansion due to temperature rise.

In general, by providing the surface of the flow channel plate 1 with an inclination angle along the flow direction of the liquid, a design of combining hydrodynamic force and thermodynamics is provided, and as the turbulence structure 14 gradually increases in the flow direction of the liquid, potential energy and kinetic energy of the liquid can be adjusted by increasing the sectional area of the flow channel while the liquid is gradually heated and the potential energy increases, so that hydrodynamic pressure drop is reduced, and local heat distribution non-uniformity caused by flow velocity difference is reduced.

Preferably, the inclination angle is 0.1 ° to 1 °. The relatively small tilt angle (0.1 deg. to 1 deg.) provides subtle temperature gradient regulation in long distance liquid flows. Due to the gradual absorption of heat during the flow of the liquid, a suitable inclination prevents the liquid from having too high a temperature at the liquid outlet end, since the enlarged cavity space provides a higher tolerance in respect of heat accumulation. This helps to achieve a more uniform temperature profile from the liquid inlet end to the liquid outlet end, reducing the temperature peaks due to localized area heat accumulation.

The slope of 0.1 deg. to 1 deg. neither makes the liquid chamber 10 too steep (which may cause fluid flow to be difficult to control) nor too gentle (which may not be effective in assisting the liquid flow by gravity). As the depth of the fluid chamber 10 increases, the cross-sectional areas of the first and second flow channels L1, L2 increase, and the fluid flow rate decreases accordingly, which helps to reduce the overall pressure drop of the system, especially in the region of the fluid outlet end where the fluid naturally expands due to heating.

In summary, the range of tilt angles creates a gradual thermodynamic field as the liquid flows through the turbulator structure 14, with increasing depth of the liquid chamber 10, increasing heat carrying capacity of the liquid, while the increasing height of the turbulator structure 14 dynamically allows the fluid to contact the heat exchange plates at a relatively high location for a long period of time, improving heat exchange efficiency, while reducing pressure loss at the liquid outlet end.

As some embodiments, the liquid chamber 10 includes a liquid inlet chamber 101, a flow dividing chamber 102 and a liquid outlet chamber 103 sequentially arranged along the flowing direction of the liquid, the liquid inlet 12 is communicated with the liquid inlet chamber 101, the liquid outlet 13 is communicated with the liquid outlet chamber 103, and a plurality of turbulence structures 14 arranged in a honeycomb shape are arranged in the flow dividing chamber 102.

The inlet 12 opens directly into the inlet chamber 101, which is the starting point for liquid to enter the heat exchanger plate. The inlet chamber 101 is typically the lowest temperature part of the liquid chamber 10, since it is first contacted by the cooling liquid, and the design here is focused on ensuring that the liquid can smoothly enter the heat exchanger plate from the liquid supply system. The diversion cavity 102 is located between the liquid inlet cavity 101 and the liquid outlet cavity 103, and a plurality of honeycomb-shaped flow-around structures are arranged in the diversion cavity. The function of these structures is to break up the fluid flow lines, increase the contact area and contact time of the fluid and the heat exchange plate surface, thereby improving the heat exchange efficiency. The honeycomb design also helps to disperse the kinetic energy generated by the fluid flow, balance the fluid velocity, and reduce pressure fluctuations within the fluid chamber 10. The liquid outlet chamber 103 serves as the last region of the liquid chamber 10, guiding the heat exchanged liquid to the liquid outlet 13 and finally away from the heat exchanger plate. After efficient heat exchange, the fluid is typically at a higher temperature, so the design of the outlet chamber 103 needs to take into account how efficiently the hot fluid is guided to reduce energy losses.

By adopting the technical scheme, the method has the following technical effects:

1) And (3) sequencing temperature control: by separating the fluid chambers 10, sequential management of temperature changes of the fluid is facilitated. The fluid may be warmed up stepwise as it passes through the three different chambers, which helps to avoid abrupt changes in temperature during heat exchange.

2) Improving heat exchange efficiency: the honeycomb structure creates a complex flow path in the shunt cavity 102 that not only increases turbulence of the fluid with the heat exchanger plate surface, but also disperses shock waves caused by the fluid flow, acting together to improve the uniformity and efficiency of heat exchange.

3) Reducing inlet and outlet pressure drops: by rationally designing the volumes of the liquid inlet and outlet cavities 103 and interfacing with the respective flow channels, hydrodynamic losses can be minimized at the liquid inlet 12 and outlet 13. Particularly at the high Wen Chuye port 13, proper cavity design helps to relieve the extra pressure due to expansion and contraction of the liquid.

In general, the heat exchanger plate design fully accounts for the temperature and pressure variations of the fluid from inlet to outlet within the liquid chamber 10. The use of a separate design of the chambers and honeycomb structure provides a more complex flow path for the liquid, which is advantageous for improving heat exchange efficiency, maintaining the balance of the fluid power system, and for efficient heat management.

In the above embodiment, the third flow path L3 is provided between the inner wall of the distribution chamber 102 and the adjacent turbulence structure 14, the third flow path L3 and the coolant flow direction are the same, and the widths of the third flow path L3 and the first flow path L1 are the same.

The technical effect of the technical scheme is that:

1) Enhancing flow uniformity: the presence of the third flow path L3 helps create a boundary layer that reduces turbulence and eddies created by the edges of the spoiler 14, making the fluid smoother as it passes over the sides of the spoiler 14. This design improves the uniformity of fluid distribution within the distribution chamber 102 and effectively reduces the pressure loss due to the circuitous flow of fluid.

2) Balance control of fluid temperature: since the third flow path L3 has the same width as the first flow path L1, it can more smoothly adjust the temperature gradient of the fluid, and avoid the excessive local temperature difference caused by the change of the flow paths. This helps to achieve a more stable and uniform temperature distribution inside the liquid chamber 10, especially in applications where high fluid flows cause rapid changes in temperature.

3) Reducing pressure fluctuations: maintaining the third flow path L3 consistent with the width of the first flow path L1 helps to maintain pressure consistency as the fluid flows within the heat exchange plates. The matching of the widths of the flow passages ensures that the flow velocity of the liquid does not generate severe fluctuation due to the narrowing or the expanding of the flow passages in the transmission process, thereby reducing the hydrodynamic loss and the pumping load.

4) And the overall performance of the heat exchange plate is improved: the addition of the third flow channel L3 to the inner wall of the distribution chamber 102 is a design that combines both fluid dynamics and heat exchange, and this optimization helps to ensure the overall operating efficiency of the heat exchanger plate, maximizing the heat transfer performance of the heat exchanger plate by balancing the fluid flow and temperature distribution.

In summary, the present embodiment sets the third flow path L3 to be uniform in width with the first flow path L1, and by improving the hydrodynamic and heat exchange conditions, more optimal flow control and more uniform heat distribution are achieved inside the liquid chamber 10. The runner arrangement helps to improve the performance of the heat exchange plate, and is particularly suitable for application environments with high requirements on temperature uniformity and fluid pressure stability.

In the actual working process of the heat exchange plate, the cooling liquid with lower temperature can be introduced to realize the cooling and heat dissipation functions, and the cooling liquid with higher temperature can also be introduced to realize the temperature rising function.

The invention also discloses a battery module, which comprises a plurality of single batteries 3 and the heat exchange plate, wherein the single batteries 3 are stacked and arranged on the surface of the cover plate 2 of the heat exchange plate. Because the battery module adopts the heat exchange plate disclosed above, the turbulent flow structure 14 and the flow channel design provided in the heat exchange plate ensure that the fluid in the heat exchange plate can uniformly distribute heat, so that the temperature balance between the single batteries 3 in the battery module is realized, and adverse effects on the battery performance or service life caused by overlarge temperature difference are prevented. Through honeycomb structure and runner design of heat exchange plate, reduced the pressure drop of liquid in the battery module, help guaranteeing the high-efficient operation of liquid cooling circulation system, reduce the energy consumption simultaneously.

The foregoing description of the preferred embodiments of the invention is not intended to be limiting, but rather is intended to cover all modifications, equivalents, alternatives, and improvements that fall within the spirit and scope of the invention.

Claims

1. A heat exchange plate, comprising a flow channel plate (1) and a cover plate (2), wherein the surface of the flow channel plate (1) is recessed to form a liquid cavity (10), the cover plate (2) is arranged on the surface of the flow channel plate (1) and forms a seal with the outer periphery of the liquid cavity (10), and the flow channel plate (1) or the cover plate (2) is provided with a liquid inlet (12) and a liquid outlet (13) connected to the liquid cavity (10) along the liquid flow direction;

The invention is characterized in that: a plurality of honeycomb-arranged spoiler structures (14) are fixedly arranged in the liquid chamber (10), the top of the spoiler structure (14) is in contact with the bottom surface of the cover plate (2), each spoiler structure (14) is composed of a central spoiler column (141) and at least one circle of annular protrusions (142) concentrically surrounding the spoiler column (141), the spoiler column (141) and the annular protrusions (142) are both regular hexagonal structures, and each circle of annular protrusions (142) is the same as the spoiler column (141). 1) The edges are arranged in parallel side by side, a first flow channel (L1) is provided between the annular protrusion (142) and the spoiler column (141) and between multiple circles of annular protrusions (142), a second flow channel (L2) is provided between the annular protrusions of the outermost circles of two adjacent spoiler structures (14), and each annular protrusion (142) is provided with a guide port (1421) at two end points in a horizontal direction, and the guide port (1421) is connected to the first flow channel (L1) and the second flow channel (L2).

2. The heat exchange plate according to claim 1, characterized in that the wall thickness of each of the annular protrusions (142) is the same.

3. The heat exchange plate according to claim 2, characterized in that the opening direction of each of the guide ports (1421) is parallel to the liquid flow direction and corresponds to the second flow channel (L2) between adjacent spoiler structures (14).

4. The heat exchange plate according to claim 3, characterized in that the guide port (1421) and the second flow channel (L2) have the same width.

5. The heat exchange plate according to claim 4, characterized in that the first flow channel (L1) and the second flow channel (L2) have the same width.

6. The heat exchange plate according to claim 5, characterized in that: a surface of the flow channel plate (1) connected to the cover plate (2) is provided with an upward inclination angle along the liquid flow direction, and the bottom surface of the cover plate (2) is matched with the surface of the flow channel plate (1) in an inclined manner.

7. The heat exchange plate according to claim 6, characterized in that the inclination angle is 0.1° to 1°.

8. The heat exchange plate according to claim 5 or 7, characterized in that: the liquid chamber (10) comprises a liquid inlet chamber (101), a diverter chamber (102) and a liquid outlet chamber (103) arranged in sequence along the liquid flow direction, the liquid inlet (12) is connected to the liquid inlet chamber (101), the liquid outlet (13) is connected to the liquid outlet chamber (103), and a plurality of honeycomb-shaped turbulent structures (14) are arranged in the diverter chamber (102).

9. The heat exchange plate according to claim 8, characterized in that: a third flow channel (L3) is provided between the inner wall of the flow dividing cavity (102) and the adjacent flow disturbing structure (14), and the third flow channel (L3) has the same width as the first flow channel (L1).

10. A battery module, characterized in that it comprises a plurality of single cells (3) and a heat exchange plate as claimed in any one of claims 1 to 9, wherein the plurality of single cells (3) are stacked and arranged on the surface of a cover plate (2) of the heat exchange plate.