Recessed type flow guide reinforced transmission refrigerant direct cooling plate

Abstract

The utility model discloses a sunken type flow guide enhanced transmission refrigerant direct cooling plate which comprises a plate body and a heat exchange runner arranged in the plate body, one side of the plate body is an outer heat exchange face, and the outer heat exchange face is used for conducting heat exchange with the outside; the face, opposite to the outer heat exchange face, in the heat exchange runner is an inner heat exchange face, and the inner heat exchange face is used for heat exchange between the plate body and a refrigerant working medium. A plurality of concave turbulent flow structures are arranged in the heat exchange flow channel at intervals and used for guiding a liquid refrigerant working medium in the flow channel to generate turbulent flow, and the contact frequency and efficiency of the refrigerant working medium and the inner heat exchange face are improved. The direct cooling plate can effectively promote turbulent flow formation of refrigerant working media. The contact efficiency of the refrigerant and the heat exchange surface can be remarkably improved through generation of turbulent flow, and then the utilization rate and the heat exchange efficiency of the refrigerant are improved.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of battery temperature control, and in particular to a concave flow guide reinforced transmission refrigerant direct cooling plate. BACKGROUND

[0002] With the transformation of global energy structure and the improvement of environmental protection consciousness, the market demand for new energy vehicles, especially electric vehicles, is rapidly growing. In this context, the performance and safety of batteries, as the core components of electric vehicles, directly affect the performance of the whole vehicle and the driving experience of users. A large amount of heat is generated during the charging and discharging process of the battery. If this heat cannot be effectively dissipated, not only will the service life of the battery be shortened, but also safety accidents such as thermal runaway may occur. Therefore, designing an efficient battery thermal management system is of great importance. This not only relates to the improvement of battery life and performance, but also involves the safety of the vehicle and the trust of users in new energy vehicles.

[0003] At present, the refrigerant direct cooling plate widely used in the market mainly relies on the flow of refrigerant to take away the heat generated by the battery. The design is simple, and the manufacturing cost is relatively low, so it has been widely used in the heat dissipation system of new energy vehicle batteries. However, with the increase of battery capacity and the development of fast charging technology in electric vehicles, the traditional refrigerant direct cooling plate gradually exposes its shortcomings. Especially under high load working conditions, the refrigerant working medium in the heat exchange channel of the traditional refrigerant direct cooling plate mainly flows in the form of laminar flow, resulting in low contact efficiency of the refrigerant with the heat exchange surface. Due to the small volume of refrigerant working medium participating in heat exchange in the flow channel, the refrigerant utilization rate is low, and its heat conduction capacity cannot be fully utilized, thereby affecting the heat dissipation effect.

[0004] This problem of laminar flow of refrigerant working medium is particularly significant in practical application, especially in high temperature and high power density environments. The heat exchange effect of the traditional refrigerant direct cooling plate is obviously insufficient. The contact area between the refrigerant and the heat exchange surface is limited, which cannot effectively absorb the heat generated by the battery, leading to easy overheating in local areas. With the increasing demand for efficient heat dissipation of electric vehicles, the limitations of traditional refrigerant direct cooling plates are increasingly prominent, and they cannot meet the high-efficiency heat dissipation requirements of modern electric vehicle batteries. This not only affects the performance of the battery, but also may cause safety hazards to the vehicle, especially when working for a long time at high power.

[0005] Therefore, it is particularly necessary to develop a new type of refrigerant direct cooling plate that can effectively improve the contact efficiency of the refrigerant working medium with the heat exchange surface. CONTENT OF THE INVENTION

[0006] The purpose of the present application is to overcome at least one deficiency in the prior art, and to provide a concave flow guide reinforced transmission refrigerant direct cooling plate. The direct cooling plate can effectively promote the formation of turbulent flow of refrigerant working medium. The generation of turbulent flow can significantly increase the contact efficiency of the refrigerant with the heat exchange surface, thereby improving the utilization rate of the refrigerant and the heat exchange efficiency.

[0007] To achieve the above-mentioned objectives, the present application discloses a refrigerant direct cooling plate with a recessed flow-guiding and enhanced transmission, the direct cooling plate comprising a plate body and a heat exchange channel arranged in the plate body, wherein one side of the plate body is an external heat exchange surface, and the external heat exchange surface is used for heat exchange with the outside world; the side of the heat exchange channel opposite to the external heat exchange surface is an internal heat exchange surface, and the internal heat exchange surface is used for heat exchange between the plate body and the refrigerant; a number of recessed flow-disturbing structures are arranged at intervals in the heat exchange channel to guide the liquid refrigerant in the channel to produce turbulence, thereby improving the contact frequency and efficiency of the refrigerant with the internal heat exchange surface.

[0008] As an optional technical solution, the plate body includes a bottom plate provided with a groove and a panel for sealing an opening of the bottom plate.

[0009] As an optional technical solution, the cross-section of the heat exchange channel is trapezoidal or rectangular.

[0010] As an optional technical solution, diffusion grooves are provided on the inner heat exchange surface. During the flow of the refrigerant, the refrigerant can diffuse evenly along the inner heat exchange surface through the grooves, thereby further increasing the contact area with the inner heat exchange surface and improving the heat exchange efficiency.

[0011] Preferably, the diffusion groove includes a groove in the same direction as the heat exchange channel and located in the center, and branch grooves extending from the main groove in a branch-like manner.

[0012] As an optional technical solution, the concave spoiler structure includes an uphill section, a flat slope section and an uphill section.

[0013] As an optional technical solution, in the heat exchange flow channel, the shape of the concave groove of the single concave flow-disturbing structure is one of an arc shape, a diamond shape, a rectangle, a circle, and a triangle.

[0014] As an optional technical solution, the recessed flow-disturbing structure can be arranged in a variety of regular or irregular forms in the heat exchange flow channel.

[0015] As an optional technical solution, the distribution, size and shape of the plurality of concave flow-disturbing structures in different positions in the heat exchange flow channel are the same / different, so as to optimize the flow characteristics and enhance the local turbulence effect, thereby improving the overall heat exchange efficiency.

[0016] As an optional technical solution, the angle between the branch groove and the main groove is 1-90 degrees.

[0017] Compared with the prior art, this application has at least one of the following beneficial effects:

[0018] 1. Improve heat exchange efficiency: By setting a concave turbulent flow structure in the heat exchange flow channel, the turbulent flow of the refrigerant is effectively promoted, and the contact frequency between the refrigerant and the internal heat exchange surface is increased, thereby significantly improving the heat exchange efficiency.

[0019] 2. Enhanced refrigerant utilization: The concave guide design makes the refrigerant flow more uniform in the flow channel, expands the contact area between the refrigerant and the heat exchange surface, improves the refrigerant utilization rate, and solves the refrigerant waste problem caused by the laminar flow effect of traditional refrigerant direct cooling plates.

[0020] 3. Improve local heat dissipation effect: By rationally distributing and designing the shape and size of the concave spoiler structure, the turbulence effect in the local area can be enhanced, local overheating can be prevented, and the heat dissipation effect in high power density environments can be improved.

[0021] 4. Adapt to different working conditions: This design can adjust the layout, size and shape of the concave spoiler structure according to actual working conditions, flexibly respond to cooling requirements under various working conditions, and improve the applicability of the device and the reliability of the heat dissipation effect.

[0022] 5. Simple structure and low manufacturing cost: The board design with base plate and panel packaging makes the whole device simple in structure, easy to manufacture, with low manufacturing cost, suitable for large-scale production and wide application.

[0023] The above-listed beneficial effects are not exhaustive and other potential beneficial effects and detailed technical implementations will be further disclosed in the examples or other description sections of this application. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] After reading the following detailed description in conjunction with the accompanying drawings, you will better understand the various aspects of the present disclosure. The positions, sizes, and ranges of various structures shown in the drawings and the like sometimes do not represent the actual positions, sizes, and ranges. In the drawings:

[0025] Figure 1 It is a structural diagram of an embodiment disclosed in this application.

[0026] Figure 2 It is a structural schematic diagram of a base plate in an embodiment disclosed in this application.

[0027] Figure 3 This is a structural schematic diagram of the base plate in another embodiment disclosed in the present application from another perspective.

[0028] Figure 4 It is a structural schematic diagram of a panel in an embodiment disclosed in this application. DETAILED DESCRIPTION

[0029] The present disclosure will be described with reference to the attached drawings, which are presented for the purpose of illustration and description. It is to be understood that the present disclosure can be presented in a multitude of different forms and that the present disclosure is not limited to the embodiments set forth herein and illustrated in the drawings. Rather, the embodiments presented herein are meant to provide a more complete and enabling disclosure of the present disclosure as defined by the appended claims. It should be understood that the embodiments disclosed herein can be combined in a variety of ways to provide additional embodiments.

[0030] It is to be understood that like numerals refer to like elements throughout the drawings. In the drawings, the size of some of the features can be exaggerated for clarity.

[0031] It is to be understood that the phraseology and terminology used herein is for the purpose of description and not of limitation. All technical and scientific terms used herein are to be interpreted according to their ordinary meaning unless otherwise defined. For the purposes of the present disclosure, the singular forms "a", "an" and "the" include plural referents unless the context clearly dictates otherwise. For the purposes of the present disclosure, the terms "comprises", "comprising", "includes", "including" and the like are to be construed in an inclusive, rather than an exclusive, sense unless otherwise indicated.

[0032] As used herein, the singular forms "a", "an" and "the" include plural referents unless the context clearly dictates otherwise. As used herein, the terms "comprises", "comprising", "includes", "including" and the like are to be construed in an inclusive, rather than an exclusive, sense unless otherwise indicated. Embodiments

[0033] As Figure 1-4 shown, the present embodiment describes a recessed flow-guided enhanced transmission refrigerant direct cooling plate, which comprises a plate body and a heat exchange channel 3 arranged inside the plate body. One side of the plate body is an outer heat exchange surface for heat exchange with the external environment. The surface inside the heat exchange channel 3 opposite to the outer heat exchange surface is called an inner heat exchange surface, which directly exchanges heat with the refrigerant working medium. A plurality of recessed turbulence structures 4 are arranged in the heat exchange channel 3, which are used to guide the refrigerant working medium in the channel to generate turbulent flow, thereby increasing the contact frequency and efficiency of the refrigerant and the inner heat exchange surface, and further optimizing the overall heat exchange performance.

[0034] The plate body is composed of a bottom plate 1 and a face plate 2, wherein the bottom plate 1 is provided with a plurality of grooves, and the face plate 2 is used to close the open part of the bottom plate 1 to form an internal heat exchange flow channel 3. Both the bottom plate 1 and the face plate 2 are made of metal materials with excellent heat conduction performance, such as copper or aluminum, to maximize the heat conduction efficiency. This plate body structure not only ensures the complete sealing of the refrigerant flow channel, but also has high mechanical strength, facilitating subsequent installation and maintenance. The close combination between the bottom plate 1 and the face plate 2 significantly enhances the overall structural strength and effectively avoids the risk of refrigerant leakage, further improving the stability and safety of the system.

[0035] The cross section of the heat exchange flow channel 3 can be designed as a trapezoidal or rectangular shape, which helps to optimize the flow characteristics of the fluid in the flow channel, reduce flow dead zones, and improve the uniformity of heat transfer. In particular, the trapezoidal cross section can effectively guide the liquid refrigerant to gradually spread at the inlet of the flow channel, thereby improving the overall flow efficiency of the fluid. To further enhance the contact area between the refrigerant and the inner heat exchange surface, diffusion grooves 5 are provided on the inner heat exchange surface. The refrigerant uniformly spreads to the entire inner heat exchange surface through these grooves during the flow process, thereby increasing the contact area and improving the heat exchange efficiency. The diffusion grooves 5 include a main groove along the direction of the heat exchange flow channel 3, located at the center of the inner heat exchange surface, and a plurality of branch grooves branching from the main groove. The design of these branch grooves helps the refrigerant to uniformly cover the entire inner heat exchange surface, thereby significantly improving the flow efficiency of the refrigerant and the heat exchange effect.

[0036] The recessed turbulence structure 4 arranged in the heat exchange flow channel 3 is designed to guide the flow of liquid refrigerant and enhance the turbulence effect, thereby improving the heat exchange efficiency. Each recessed turbulence structure 4 can present a circular arc shape, a diamond shape, a rectangular shape, a circular shape, or a triangular shape, and the specific shape is selected according to the design requirements of the heat exchange flow channel 3. The turbulence structures can be arranged in a regular or irregular manner, such as periodic arrangement or random distribution, to further optimize the flow characteristics inside the flow channel. By selecting different shapes of turbulence structures, the heat exchange performance can be customized and optimized according to different application conditions. For example, circular arc and diamond structures are suitable for low flow rate scenarios, while rectangular and triangular structures exhibit better turbulence effect under high flow rate conditions, thereby further improving the overall heat exchange performance.

[0037] The recessed turbulence structure 4 is composed of an uphill section, a flat section, and a downhill section, wherein the uphill section and the downhill section can introduce momentum changes during the flow of the refrigerant, causing significant turbulence effects when the refrigerant flows through the turbulence structure, increasing the contact efficiency between the refrigerant and the inner heat exchange surface. This design enhances the degree of turbulence by changing the flow direction and flow rate of the refrigerant, thereby further improving the heat exchange effect. In addition, the height and angle of the uphill section and the downhill section can be adjusted according to specific heat exchange requirements to ensure that the refrigerant achieves maximum disturbance effect when flowing through these structures, enhancing the overall heat exchange efficiency.

[0038] The multiple recessed flow-disturbing structures 4 in the heat exchange channel 3 can be arranged in different positions with the same or different sizes, shapes and distribution patterns. Through this arrangement design, the local turbulence effect can be enhanced according to the local flow characteristics of the refrigerant, and ultimately the overall heat exchange efficiency can be improved. For example, in areas with higher refrigerant flow rates, larger flow-disturbing structures can effectively increase fluid disturbances, while in areas with lower flow rates, smaller flow-disturbing structures help maintain a stable turbulent state. In addition, the arrangement of the recessed flow-disturbing structures 4 can also be optimized according to the temperature gradient of the refrigerant to ensure a uniform distribution of temperature inside the channel, thereby improving the operational stability and reliability of the entire system.

[0039] The angle between the main groove and the branch groove in the diffusion groove 5 is between 1 and 90 degrees. The specific angle range can be selected according to the actual application scenario to achieve the best diffusion effect of the refrigerant inside the flow channel. In high heat flux density application scenarios, the angle should be selected larger to promote the rapid diffusion of the refrigerant, thereby effectively reducing the surface temperature of the inner heat exchange surface and improving the overall heat exchange efficiency. Under low heat flux density conditions, a smaller angle helps to ensure uniform diffusion of the refrigerant on the inner heat exchange surface, avoid local overheating or insufficient cooling, and ensure long-term stable operation of the system.

[0040] During use, the refrigerant flows from the inlet into the heat exchange channel 3, where it undergoes efficient heat exchange with the plate body through the inner heat exchange surface. As the refrigerant flows through the recessed turbulent structure 4 within the channel, its flow state gradually changes from laminar to turbulent, increasing the contact frequency between the refrigerant and the inner heat exchange surface, thereby effectively improving the overall heat exchange efficiency. The refrigerant is ultimately further evenly diffused throughout the entire inner heat exchange surface through the diffusion grooves 5, ensuring uniformity and efficiency of the heat exchange process. The entire heat exchange process not only has a high heat transfer efficiency, but also effectively reduces the system's energy loss through reasonable structural design.

[0041] The design principle of this embodiment and the coordination between the various structures ensure that the refrigerant is always in an efficient heat exchange state in the heat exchange channel 3, significantly improving the heat transfer efficiency. This refrigerant direct cooling plate is particularly suitable for cooling needs in high heat flux density environments, especially for battery heat dissipation and heat dissipation systems of high-power electronic equipment. Through efficient heat exchange design, this direct cooling plate can significantly improve the overall performance and reliability of the system. In addition, the structural design in this embodiment is also highly flexible and can adapt to different cooling needs. The best cooling effect is achieved through the flexible combination of the plate body, heat exchange channel 3, recessed turbulence structure 4 and diffusion groove 5. The flexibility of this design enables the refrigerant direct cooling plate to exhibit good adaptability and excellent performance in a variety of application scenarios, thereby meeting the needs of industrial and civilian fields for efficient heat dissipation.

[0042] While exemplary embodiments of the present disclosure have been described, it is to be understood that the exemplary embodiments of the present disclosure are provided by way of illustration only. Therefore, various changes and modifications can be suggested to those skilled in the art without departing from the spirit and scope of the present disclosure. Thus, all changes and modifications are intended to be included within the scope of the present disclosure as defined by the appended claims. The present disclosure is defined by the appended claims and their equivalents.

Claims

1. A concave-type refrigerant direct cooling plate with enhanced flow transmission, characterized in that: The direct cooling plate includes: a plate body and a heat exchange channel arranged in the plate body, wherein one side of the plate body is an external heat exchange surface, which is used for heat exchange with the outside world; the side of the heat exchange channel opposite to the external heat exchange surface is an internal heat exchange surface, which is used for heat exchange between the plate body and the refrigerant; a number of concave turbulent flow structures are arranged at intervals in the heat exchange channel to guide the liquid refrigerant in the channel to produce turbulent flow, thereby improving the contact frequency and efficiency of the refrigerant and the internal heat exchange surface.

2. A concave-type refrigerant direct cooling plate with enhanced flow transmission as claimed in claim 1, characterized in that: The plate body comprises a bottom plate provided with a groove and a panel for sealing an opening of the bottom plate.

3. A concave-type refrigerant direct cooling plate with enhanced flow transmission as claimed in claim 1, characterized in that: The cross section of the heat exchange channel is trapezoidal or rectangular.

4. The concave-type refrigerant direct cooling plate with enhanced flow transmission as claimed in claim 1, characterized in that: The inner heat exchange surface is provided with diffusion grooves, and the refrigerant can be evenly diffused along the inner heat exchange surface through the grooves during the flow process, thereby further increasing the contact area with the inner heat exchange surface and improving the heat exchange efficiency.

5. A concave-type refrigerant direct cooling plate with enhanced flow transmission as claimed in claim 4, characterized in that: The diffusion groove includes a groove in the same direction as the heat exchange flow channel and located in the center, and a branch groove extending from the main groove in a branch shape.

6. The concave-type refrigerant direct cooling plate with enhanced flow transmission as claimed in claim 1, characterized in that: The concave spoiler structure includes an uphill section, a flat slope section and an uphill section.

7. The refrigerant direct cooling plate with a concave flow-guiding and enhanced transmission as claimed in claim 1, characterized in that: In the heat exchange flow channel, the shape of the concave groove of a single concave flow-disturbing structure is one of an arc shape, a diamond shape, a rectangle, a circle, and a triangle.

8. The refrigerant direct cooling plate with a concave flow-guiding and enhanced transmission as claimed in claim 1, characterized in that: The recessed flow-disturbing structures can be arranged in various regular or irregular forms within the heat exchange channel.

9. The concave-type refrigerant direct cooling plate with enhanced flow transmission as claimed in claim 1, characterized in that: The distribution, size and shape of the plurality of concave flow-disturbing structures at different positions in the heat exchange flow channel are the same / different, so as to optimize the flow characteristics and enhance the local turbulence effect, thereby improving the overall heat exchange efficiency.

10. The refrigerant direct cooling plate with a concave flow-guiding and enhanced transmission as claimed in claim 5, characterized in that: The angle between the branch groove and the main groove is 1-90 degrees.

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