Soaking structure, battery and electric device

Abstract

The utility model relates to a soaking structure, a battery and a power utilization device, the soaking structure comprises a soaking main body and a liquid cooling layer, a soaking runner is formed in the soaking main body, and the surface of one side of the soaking main body in the thickness direction is a heat exchange surface for exchanging heat with a battery cell. The liquid cooling layer is arranged on the side, away from the heat exchange face, of the soaking body and forms a liquid cooling flow channel used for exchanging heat with the soaking body, and at least part of the projection of the liquid cooling flow channel in the thickness direction covers the soaking flow channel. According to the technical scheme, the soaking effect of the soaking structure can be improved.

Description

Technical Field

[0001] The present application relates to the field of battery technology, and in particular to a heat distribution structure, a battery and an electrical device. Background Art

[0002] When the battery is under fast charge / discharge conditions, a violent conversion of chemical energy and electrical energy will occur, which will generate a large amount of heat and cause the temperature of the battery cells to rise sharply. Excessive temperature will lead to a decrease in the cycle life and safety of the battery cells. The industry generally adopts air cooling, liquid cooling plate cooling and other methods to dissipate heat from the battery cells. The liquid cooling plate has a high heat dissipation efficiency, but it has many pipe joints and a large system pressure drop. Using a heat spreader instead of part of the liquid cooling plate can help achieve large-area heat exchange, effectively reduce the system pressure drop and reduce the number of pipes, but how to improve the heat spreader's heat spread effect is a topic worth further study. Utility Model Content

[0003] Based on this, in order to improve the heat dissipation effect of the heat dissipation plate, a heat dissipation structure, a battery and an electrical device are provided.

[0004] In a first aspect, an embodiment of the present application provides a heat distribution structure, characterized in that the heat distribution structure comprises:

[0005] A heat-scaling body is formed with a heat-scaling flow channel, and one side surface of the heat-scaling body in the thickness direction is a heat exchange surface for exchanging heat with the battery core; and

[0006] The liquid cooling layer is arranged on a side of the heat equalizing body away from the heat exchange surface and forms a liquid cooling channel for exchanging heat with the heat equalizing body. The projection of the liquid cooling channel along the thickness direction at least partially covers the heat equalizing channel.

[0007] In some embodiments, the heat-saturating body is arranged vertically, and the liquid cooling layer is arranged at the upper end of the heat-saturating body;

[0008] The liquid cooling channel is arranged to extend in a horizontal straight line.

[0009] In some embodiments, the heat-spreading structure also includes a cooling plate, and the cooling plate and the heat-spreading body are respectively used for heat exchange with different side surfaces intersecting with the battery cell; the cooling plate is heat-conductingly arranged at the lower end of the heat-spreading body, and a cooling channel for circulating coolant is arranged therein.

[0010] In some embodiments, the liquid cooling layer and the heat equalizing body are jointly enclosed to form the liquid cooling channel.

[0011] In some embodiments, a boss is protruding from the inner wall of the heat-dissipating channel.

[0012] In some embodiments, the heat-sparing body includes a heat exchange layer and a heat-sparing layer, and the liquid cooling layer is disposed in the heat-sparing layer;

[0013] The heat-averaging layer is provided with a first convex portion protruding away from the heat exchange layer, the first convex portion encloses a flow channel space, and the heat exchange layer closes the flow channel space of the first convex portion to form the heat-averaging flow channel together;

[0014] Wherein, a groove portion sunken toward the heat exchange layer is arranged on the first convex portion, and the groove portion extends into the heat equalizing flow channel to form the boss.

[0015] In some embodiments, the groove portion extends into the heat-averaging channel and abuts against the heat exchange layer; and / or,

[0016] At least some of the groove portions satisfy the requirement that every two of the groove portions adjacent to each other in the vertical direction are staggered in the length direction of the heat-saturating body.

[0017] In some embodiments, the heat-sparing body has protruding ears at both ends in the length direction, and the ears are provided with connecting joints connected to the liquid cooling channel, and the liquid cooling layer extends to the area where the ears are located.

[0018] In a second aspect, an embodiment of the present application provides a battery, comprising:

[0019] Battery cells; and

[0020] As for the heat distribution structure described in the above embodiment, the heat exchange surface of the heat distribution structure is in thermal contact with the battery core.

[0021] In a third aspect, an embodiment of the present application provides an electrical device, comprising the battery described in the above embodiment, wherein the battery is used for supplying power.

[0022] The above-mentioned heat-equalizing structure, battery and electrical device, when in actual application, contact the battery cell through the heat exchange surface, and the heat of the battery cell is transferred to the refrigerant in the heat-equalizing channel through the heat exchange surface. After the refrigerant that absorbs the heat of the heat exchange surface is vaporized, it is condensed and reliquefied under the cooling of the coolant in the liquid cooling channel. The refrigerant can circulate in the vapor-liquid two-phase in the heat-equalizing channel, and its equivalent thermal conductivity is much higher than that of metal materials, so that the heat-equalizing structure has a good heat-equalizing effect. Moreover, the liquid cooling channel is not in direct contact with the heat exchange surface, but is in contact with the heat exchange surface with a larger surface area through the refrigerant, which not only reduces the space occupied by the liquid cooling layer for heat exchange with the battery cell, but also makes the temperature of the heat exchange surface more uniform, and the heat-equalizing structure has a good heat-equalizing effect. In addition, the projection of the liquid cooling channel along the thickness direction of the heat-equalizing body at least partially covers the heat-equalizing channel, and the liquid cooling channel can directly exchange heat with the heat-equalizing channel, with high heat exchange efficiency, so that the heat-equalizing structure has a better heat-equalizing effect. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Various other advantages and benefits will become apparent to those of ordinary skill in the art by reading the detailed description of the preferred embodiments below. The accompanying drawings are only for the purpose of illustrating the preferred embodiments and are not to be considered as limiting the present application. Moreover, the same reference numerals are used throughout the drawings to represent the same components. In the drawings:

[0024] Figure 1 Schematic diagram of the heat distribution structure of some embodiments.

[0025] Figure 2 for Figure 1 Schematic diagram of the exploded view of the heat-isolating structure shown.

[0026] Figure 3 for Figure 1 Another exploded schematic diagram of the heat-saturating structure shown.

[0027] Figure 4 Schematic diagram of the structure of batteries in some embodiments.

[0028] Figure 5 for Figure 4 An exploded schematic diagram of the battery is shown.

[0029] Figure 6 Graph showing pressure drop simulation results of liquid cooling channels in some embodiments.

[0030] The reference numerals in the specific implementation manner are as follows:

[0031] 100, heat-scaling structure; x, thickness direction; z, vertical direction; y, length direction; 100a, heat-scaling body; a1, lug; 10, heat exchange layer; 10a, heat exchange surface; 20, heat-scaling layer; s1, heat-scaling channel; T, boss; 21, first convex part; 22, groove part; q1, first zone; q2, second zone; q3, third zone; 30, liquid-cooling layer; s2, liquid-cooling channel; 31, second convex part; 40, connecting joint; 1000, battery; 200, battery cell; 200A, battery cell group; 100a, heat-scaling group; 300, liquid inlet main pipe; 400, liquid outlet main pipe. DETAILED DESCRIPTION

[0032] In order to make the above-mentioned purposes, features and advantages of the present application more obvious and easy to understand, the specific implementation methods of the present application are described in detail below in conjunction with the accompanying drawings. In the following description, many specific details are set forth to facilitate a full understanding of the present application. However, the present application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar improvements without violating the connotation of the present application, so the present application is not limited by the specific embodiments disclosed below.

[0033] In the description of the present application, it should be understood that terms such as “center”, “longitudinal”, “lateral”, “length”, “width”, “thickness”, “up”, “down”, “front”, “back”, “left”, “right”, “vertical”, “horizontal”, “top”, “bottom”, “inside”, “outside”, “clockwise”, “counterclockwise”, “axial”, “radial”, “circumferential”, etc., indicating orientations or positional relationships, if any, are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present application.

[0034] In addition, if present, the terms "first" and "second" are used for descriptive purposes only and are not to be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of the features. In the description of this application, "plurality" means at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0035] In this application, unless otherwise clearly specified and limited, if any, the terms "installed", "connected", "connected", "fixed" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0036] In the present application, if it appears, unless otherwise clearly specified and limited, a first feature “above” or “below” a second feature may mean that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. Moreover, a first feature “above”, “above” and “above” a second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. A first feature “below”, “below” and “below” a second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0037] It should be noted that, if present, when an element is referred to as being "fixed to" or "disposed on" another element, it may be directly on the other element or there may be a central element. When an element is considered to be "connected to" another element, it may be directly connected to the other element or there may be a central element at the same time. The terms "vertical", "horizontal", "upper", "lower", "left", "right" and similar expressions used herein are for illustrative purposes only and are not intended to be the only implementation method.

[0038] In order to improve the heat dissipation effect of the heat dissipation plate, the embodiment of the present application provides a heat dissipation structure, a battery and an electrical device. First, the heat dissipation structure is introduced in detail.

[0039] According to some embodiments of the present application, referring to Figures 1 to 3 The heat-scaling structure 100 provided in the embodiment of the present application includes a heat-scaling body 100a and a liquid cooling layer 30. The heat-scaling body 100a is formed with a heat-scaling flow channel s1. One side surface of the heat-scaling body 100a in the thickness direction x is a heat exchange surface 10a for exchanging heat with the battery cell. The liquid cooling layer 30 is arranged on the side of the heat-scaling body 100a away from the heat exchange surface 10a, and forms a liquid cooling flow channel s2 for exchanging heat with the heat-scaling body 100a. The projection of the liquid cooling flow channel s2 along the thickness direction x at least partially covers the heat-scaling flow channel s1.

[0040] The heat-scaling body 100a has the smallest size in its thickness direction x, and exchanges heat with the battery cell 200 through the heat exchange surface 10a. The length direction y of the heat-scaling body 100a is roughly perpendicular to its vertical direction z and its thickness direction x. In actual application, the vertical direction z of the heat-scaling body 100a corresponds to the direction of gravity, and the length direction y corresponds to the horizontal direction. That is, in actual application, the heat-scaling body 100a is usually set vertically. The heat exchange surface 10a is usually but not limited to a plane. The heat exchange surface 10a is located on one side of the heat-scaling body 100a in the thickness direction x, and it usually has a larger surface area.

[0041] The heat equalizing channel s1 can be filled with a phase-changing refrigerant. In the embodiment of the present application, a phase-changing refrigerant refers to a substance that can undergo a phase change between vapor and liquid with temperature changes. The phase-changing refrigerant may be, but is not limited to, Freon. At a lower temperature, the refrigerant releases heat and changes to a liquid phase, and at a higher temperature, the refrigerant absorbs heat and changes to a vapor phase. Optionally, an injection hole is provided on the heat equalizing body 100a, and the refrigerant is injected into the heat equalizing channel s1 through the injection hole. When in use, the injection hole remains sealed to prevent leakage.

[0042] The liquid cooling layer 30 forms a liquid cooling channel s2, and an external coolant circulates in the liquid cooling channel s2. The coolant may be, but is not limited to, cooling water. Understandably, in the use state, the heat equalizing channel s1 is not connected to the outside world, and the refrigerant phase change occurs in the heat equalizing channel s1. The liquid cooling channel s2 is connected to the outside world to circulate the coolant. The projection of the liquid cooling channel s2 along the thickness direction x of the heat equalizing body 100a at least partially covers the heat equalizing channel s1. At this time, the heat conduction path between the liquid cooling channel s2 and the heat equalizing channel s1 is short, and the heat exchange efficiency is high.

[0043] In actual application, the heat-equalizing structure 100 contacts the battery cell 200 through the heat exchange surface 10a, and the heat of the battery cell 200 is transferred to the refrigerant in the heat-equalizing channel s1 through the heat exchange surface 10a. After the refrigerant that absorbs the heat of the heat exchange surface 10a is vaporized, it is condensed and reliquefied under the cooling of the coolant in the liquid cooling channel s2. The refrigerant can circulate in the vapor-liquid two-phase in the heat-equalizing channel s1, and its equivalent thermal conductivity is much higher than that of metal materials, so that the heat-equalizing structure 100 has a good heat-equalizing effect. Moreover, the liquid cooling channel s2 is not in direct contact with the heat exchange surface 10a, but is in contact with the heat exchange surface 10a through the refrigerant, which can not only reduce the space occupied by the liquid cooling layer 30 for heat exchange with the battery cell, but also make the temperature of the heat exchange surface 10a more uniform, and the heat-equalizing structure 100 has a good heat-equalizing effect. In addition, the projection of the liquid cooling channel s2 along the thickness direction x of the heat equalizing body 100a at least partially covers the heat equalizing channel s1. The liquid cooling channel s2 can directly exchange heat with the heat equalizing channel s1, and the heat exchange efficiency is high, so that the heat equalizing structure 100 has a better heat equalizing effect.

[0044] In some embodiments, the heat-sinking body 100a is vertically disposed, and the liquid cooling layer 30 is arranged at the upper end of the heat-sinking body 100a.

[0045] The vapor phase refrigerant is lighter than the liquid phase refrigerant, and the vapor phase refrigerant is easy to float in the heat equalizing flow channel s1. At this time, the liquid cooling layer 30 is arranged at the upper end of the heat equalizing body 100a, that is, the liquid cooling flow channel s2 is located at the upper end of the heat equalizing body 100a, which can effectively exchange heat with the vapor phase refrigerant, help improve the condensation efficiency of the vapor phase refrigerant, and then improve the circulation of the vapor-liquid two-phase of the refrigerant, which helps to improve the heat equalizing effect of the heat equalizing structure.

[0046] In some embodiments, the liquid cooling channel s2 is arranged to extend in a horizontal straight line. In this case, the liquid cooling channel s2 is short and extends in a straight line, and the cooling liquid circulation resistance is small, which helps to reduce the pressure drop of the cooling liquid in the liquid cooling channel s2, thereby reducing the energy consumption of the power device (such as a pump) that causes the cooling liquid to flow.

[0047] It is also worth noting that the use of a linear liquid cooling channel s2 overcomes the existing technical bias, because the existing technology tends to use a serpentine flow path to cover more heat dissipation area, while the present invention uses a heat spreader to make the liquid cooling channel s2 no longer need to consider the heat dissipation area index, but only the heat dissipation efficiency and flow resistance index, thereby obtaining a heat dissipation capacity with smaller flow resistance and higher efficiency. This ability can play its greatest value when the battery cells are grouped. Figure 6 The pressure drop simulation results of the linear horizontally extending liquid cooling channel s2 of some embodiments of the present application are shown. Figure 6 It can be seen that the pressure drop of the liquid-cooling flow channel s2 is stable, that is, the liquid-cooling flow channel s2 extending horizontally and straightly has a small flow resistance, which can effectively reduce the pressure drop.

[0048] In some embodiments, in order to achieve a better heat dissipation effect of the liquid cooling channel s2, the size of the liquid cooling channel s2 in the thickness direction x can be between 3.5 mm and 4.0 mm, specifically 3.6 mm, 3.7 mm, 3.8 mm, 3.9 mm, 4.0 mm, etc., and the average height of the liquid cooling channel s2 in the vertical direction z can be between 20 mm and 25 mm. The liquid cooling channel s2 can be a trapezoidal channel, a square channel, etc.

[0049] In some embodiments, the heat-spreading structure 100 also includes a cooling plate (not shown), which exchanges heat with the different side surfaces of the heat-spreading body 100a that intersect with the battery cell respectively. The cooling plate is heat-conductingly arranged at the lower end of the heat-spreading body 100a, and a cooling channel for circulating coolant is arranged therein.

[0050] Generally, the heat exchange surface 10a of the heat spreader 100a is used to exchange heat with the vertical side of the battery cell, and the cooling plate exchanges heat with the bottom of the battery cell. A cooling channel for circulating coolant can be set in the cooling plate to remove the heat on the heat spreader 100a through the coolant.

[0051] At this time, the upper and lower ends of the heat equalizer body 100a exchange heat through the liquid cooling channel s2 and the cooling plate respectively, which helps to reduce the temperature difference between the two ends of the heat equalizer body 100a and improve the temperature equalization effect of the heat equalizer body 100a.

[0052] In some embodiments, the liquid cooling layer s1 and the heat-saturating body 100a are jointly enclosed to form a liquid cooling channel s2.

[0053] Specifically, the liquid cooling layer s1 protrudes away from the heat equalizing body 100a to form a second protrusion 22a, and the second protrusion 22a encloses the flow channel space of the liquid cooling channel s2, and the heat equalizing body 100a closes the flow channel space. Specifically, the liquid cooling layer s1 is plate-shaped, and the second protrusion 31 is formed on the liquid cooling layer s1 by stamping or the like. The wall thickness of the second protrusion 31 is generally equal to the wall thickness of the rest of the liquid cooling layer 30. At this time, the internal space of the liquid cooling channel s2 is formed by the second protrusion 31 on the liquid cooling layer 30, which has a simple structure and is easy to form, which can simplify the structure of the heat equalizing body 100a and reduce the overall processing cost.

[0054] Specifically, the heat-sparing body 100a may be recessed away from the liquid cooling layer s1 to form a flow channel space of the liquid cooling flow channel s2. Of course, partial flow channel space of the liquid cooling flow channel s2 may also be constructed on both the liquid cooling layer s1 and the heat-sparing body 100a.

[0055] At this time, the liquid cooling layer s1 and the heat equalizing body 100a together form a liquid cooling channel s2, that is, the heat equalizing channel s1 and the liquid cooling channel s2 form the wall of the heat equalizing body 100a. The heat conduction speed between the cooling liquid and the refrigerant is faster, the heat exchange efficiency is higher, and the heat equalizing effect of the heat equalizing structure 100 is better.

[0056] Of course, in other embodiments, the liquid-cooling channel s2 can be independently formed by the liquid-cooling layer 30 .

[0057] In some embodiments, a boss T is protrudingly provided on the inner wall of the heat-averaging channel s1.

[0058] Specifically, the boss T may be disposed on an inner wall of the heat-averaging channel s1 that is away from the liquid cooling layer 30 , or may be disposed on an inner wall of the heat-averaging channel s1 that is close to the liquid cooling layer 30 .

[0059] The boss T can act as a spoiler structure, increase the cross-mixing of the refrigerant along the inner wall of the boss T, and increase the temperature uniformity of the heat-equalizing flow channel s1. In addition, the boss T increases the contact area between the vapor-phase refrigerant and the heat-equalizing structure 100, improves the condensation efficiency of the vapor-phase refrigerant and the circulation efficiency between the vapor and liquid phases of the refrigerant, and helps to improve the heat exchange efficiency of the heat-equalizing structure 100.

[0060] There are a plurality of bosses, and the bosses T are arranged at intervals. Usually, convex parts T are arranged at intervals in the longitudinal direction y and the vertical direction z of the heat-averaging runner s1.

[0061] Preferably, the boss T is connected to the inner walls on both sides of the heat equalizing channel s1 in the thickness direction x of the heat equalizing body 100a. At this time, the heat exchange area of ​​the boss T is large, and the probability of contacting with the vapor-phase refrigerant is high, which can improve the condensation efficiency of the vapor-phase refrigerant.

[0062] In some embodiments, the heat-averaging body 100a includes a heat exchange layer 10 and a heat-averaging layer 20, and the liquid cooling layer 30 is disposed on the heat-averaging layer 20. The heat-averaging layer 20 is provided with a first convex portion 21 protruding from the back of the heat exchange layer 10, and the first convex portion 21 encloses a flow channel space, and the heat exchange layer 10 closes the flow channel space of the first convex portion 21 to form a heat-averaging flow channel s1 together. Among them, the first convex portion 21 is provided with a groove portion 22 that is recessed toward the heat exchange layer 10, and the groove portion 22 extends into the heat-averaging flow channel s1 and forms a boss T.

[0063] The protruding direction of the first protrusion 21 is roughly along the thickness direction x of the heat equalizing body 100a. Usually but not limited to, the heat exchange layer 10 is flat, and the flow channel space formed by the first protrusion 21 is closed by the heat exchange layer 10 to form the heat equalizing flow channel s1. Of course, the heat exchange layer 10 can also be provided with a groove structure that forms part of the flow channel space of the heat equalizing flow channel s1.

[0064] The protruding size of the first protrusion 21 is usually small, and can be between 2 mm and 4 mm (specifically, the selected values ​​can be 2.5 mm, 3 mm, 3.5 mm, etc. If the heat exchange layer 10 does not constitute part of the flow channel space of the heat-averaging flow channel s1, the protruding size of the first protrusion 21 is equivalent to the depth dimension of the heat-averaging flow channel s1 in the thickness direction x of the heat-averaging structure 100.

[0065] The recessed direction of the groove portion 22 is roughly along the thickness direction x of the heat equalizing body 100a. The groove portion 22 extends into the heat equalizing channel s1, that is, the bottom of the groove portion 22 extends into the heat equalizing channel s1, so that a boss T is formed on the inner wall of the heat equalizing channel s1.

[0066] In practical applications, the heat-averaging layer 20 can be a plate-like structure obtained by punching out the first convex portion 21 on a flat plate. The wall thickness of the first convex portion 21 is usually equal to the wall thickness of the rest of the heat-averaging layer 20. Usually, the thickness of the first convex portion 21 is usually thinner. During the stamping process, the first convex portion 21 is more likely to deform during the molding process, and the groove portion 22 is formed on the first convex portion 21. The setting of the groove portion 22 can strengthen the structural strength of the first convex portion 21, so that the first convex portion 21 can bear a greater plastic force without being easily deformed, and it is easier to mold to obtain the heat-averaging runner s1.

[0067] That is to say, the provision of the groove portion 22 can not only increase the molding capability of the first convex portion 21 , but also form the boss T, thus achieving multiple goals at one stroke.

[0068] The groove portion 22 can be formed on the first convex portion 21 by stamping or the like. In the actual processing process, the first convex portion 21 and the groove portion 22 can be stamped synchronously, and the forming directions of the two are opposite.

[0069] In some embodiments, the groove portion 22 extends into the heat-averaging channel s1 and abuts against the heat exchange layer 10 .

[0070] At this time, the boss T formed by the groove portion 22 is connected to the inner walls on both sides of the heat equalizing channel s1 located in the thickness direction x of the heat equalizing body 100a. The heat exchange area of ​​the boss T is large and the probability of contact with the vapor-phase refrigerant is high, which can improve the condensation efficiency of the vapor-phase refrigerant.

[0071] In some embodiments, at least some of the groove portions 22 satisfy the following requirement: every two adjacent groove portions 22 in the vertical direction z are staggered in the length direction y of the heat-saturating body 100 a .

[0072] Every two adjacent grooves 22 in the vertical direction z are staggered in the length direction y of the heat-saturating body 100a, which means that the projections of every two adjacent grooves 22 in the vertical direction z do not overlap in the length direction y of the heat-saturating body 100a. The "non-overlap" here can refer to either complete staggering or partial staggering.

[0073] It can be understood that the length direction y of the heat equalizing body 100a corresponds to the horizontal direction. There are multiple groove portions 22, and multiple groove portions 22 are arranged at intervals in the vertical direction z and the length direction y. At this time, the projections of the groove portions 22 located at different positions in the length direction y along the vertical direction z can fall at different positions on the same horizontal plane. That is, for the heat equalizing flow channels s1 located at different heights, the bosses T thereon can promote the mixing of refrigerants at different horizontal positions. In this way, it is helpful to improve the uniformity of the distribution of the refrigerant in the horizontal direction, thereby improving the uniformity of the temperature distribution of the heat equalizing body 100a in the horizontal direction, and helping to improve the heat equalizing effect of the heat equalizing structure 100.

[0074] In some embodiments, refer to Figure 2 The heat-spreading layer 20 includes a first zone q1, a second zone q2, and a third zone q3 sequentially arranged along the vertical direction z, and the second zone q2 and the third zone q3 are both provided with a plurality of grooves 22. The grooves 22 located in the second zone q2 extend in a strip shape in the length direction y of the heat-spreading structure 100, and the liquid cooling layer 30 is arranged in the third zone q3 and covers the grooves 22 located in the third zone q3.

[0075] The groove portion 22 of the first zone q1 and the third zone q3 may be a strip groove extending in a strip shape, or a circular groove, or even other shapes. The groove portion 22 of the second zone q2 is a strip groove extending in a strip shape. The liquid cooling layer 30 is arranged in the third zone q3. The groove portion 22 is arranged in the third zone q3, which is equivalent to forming an arch structure in the heat-averaging flow channel s1 corresponding to the third zone q3, increasing the contact area between the refrigerant and the inner wall of the heat-averaging flow channel s1, and the coolant can flow through the groove portion 22, thereby increasing the heat exchange efficiency between the refrigerant and the coolant, accelerating the condensation of the vapor-phase refrigerant, and then accelerating the circulation of the vapor-liquid two-phase refrigerant in the heat-averaging flow channel s1, thereby improving the heat exchange efficiency.

[0076] The liquid cooling layer 30 and the heat-averaging layer 20 are usually connected by welding. The groove portion 22 of the second zone q2 is arranged in a strip shape. On the basis of increasing the wall area of ​​the same arch structure, the number of groove portions 22 in the second zone q2 can be reduced, which helps to increase the spacing distance between adjacent groove portions 22, thereby increasing the welding operation space of the liquid cooling layer 30 and the heat-averaging layer 20.

[0077] Regarding the arrangement of the groove portions 22 in the first zone q1, the second zone q2, and the third zone q3. In the illustrated embodiment, the plurality of groove portions 22 in the first zone q1 are arranged in multiple rows along the vertical direction z, the groove portions 22 in the second zone q2 are arranged in a row along the length direction y, and the groove portions 22 in the third zone q3 are arranged in a row along the length direction y. At this time, the groove portions 22 are arranged in an orderly manner.

[0078] In some embodiments, a capillary structure (not shown) is constructed on the inner wall of the heat-spreading channel s1 , and the capillary structure is used to guide the liquid refrigerant to flow toward one end of the heat-spreading layer 20 away from the liquid cooling layer 30 .

[0079] The capillary structure forms a capillary channel, and the liquid refrigerant quickly refluxes along the capillary channel under the action of capillary force. Specifically, the capillary structure can be composed of a sintered texture sintered on the inner wall of the heat-averaging channel s1, and the sintered texture can form a capillary channel. The capillary structure can also be composed of a liquid-absorbing core structure arranged on the inner wall of the heat-averaging channel s1, and the liquid-absorbing core structure is similar to a sponge structure, and has a plurality of capillary channels interconnected therein.

[0080] At this time, the design of the capillary structure can speed up the reflux rate of the condensed liquid-phase refrigerant, thereby speeding up the circulation of the vapor-liquid two-phase refrigerant, which helps to improve the heat exchange efficiency of the heat equalizing structure 100.

[0081] Understandably, referring to Figures 1 to 3 The heat-saturating structure 100 includes a connection joint 40, which is connected to the liquid cooling channel s2. The external cooling liquid can enter and exit the liquid cooling channel s2 through the connection joint 40. It can be understood that there are at least two connection joints 40, some of which are used for cooling liquid to flow in, and some of which are used for cooling liquid to flow out.

[0082] In some embodiments, reference Figures 1 to 3The liquid cooling channel s2 is extended along the length direction y of the heat equalizing body 100a, and a connecting joint 40 is provided at both ends of the liquid cooling channel s2 in the extending direction. Usually, a connecting joint 40 is provided at both ends of the liquid cooling channel s2, one of which is for the coolant to flow in, and the other is for the coolant to flow out. At this time, the coolant can effectively flow through the liquid cooling channel s2 between the inflow and outflow connecting joints 40, and the coolant can fully exchange heat in the liquid cooling channel s2, which can improve the energy utilization rate of the coolant, and thus improve the heat exchange efficiency of the heat equalizing structure 100.

[0083] In some embodiments, reference Figure 1 The heat-saturating body 100a has protruding ears a1 at both ends in the length direction y, and a connecting joint (40) connected to the liquid cooling channel s2 is provided at the protruding ear a1, and the liquid cooling layer 30 extends to the area where the protruding ear a1 is located.

[0084] It can be understood that the lug a1 is formed by a portion of the heat exchange layer 10 and a portion of the heat-averaging layer 20. The liquid cooling layer 30 extends to the lug a1, so that the connection joint 40 provided at the lug a1 is connected to the liquid cooling channel s2. Specifically, the heat-averaging channel s1 can be extended to the area where the lug a1 is located to increase the area 10b of the heat-averaging channel s1 and improve the heat exchange efficiency.

[0085] In practical application, combined with Figure 4 It is understood that the lug a1 is arranged beyond the battery cell 200 to facilitate the connection of the connector 40 to the pipeline. Moreover, since the lug a1 is arranged protrudingly, the space below the lug a1 can be used to arrange the pipeline, which facilitates the layout of the pipeline.

[0086] In some embodiments, the heat-spreading structure 100 further includes a heating element (not shown), which is disposed on the outer surface of the heat-spreading layer 20 and / or the heat exchange surface 10a. Specifically, the heating element may be a heating wire disposed on the outer surface of the first convex portion 21. The heating wire may be embedded in the groove portion 22. Specifically, the heating element may be a heating film disposed on the heat exchange surface 10a, and the heating film is usually spread over the entire heat exchange surface 10a for uniform heating.

[0087] At this time, a heating element is provided on the heat-spreading structure 100 , and the heating structure can also be used to heat the battery cell 200 , so that the heat-spreading structure 100 has more functions.

[0088] In one embodiment of the present application, refer to Figure 1 Place Figure 3The heat-sparing structure 100 includes a heat exchange layer 10, a heat-sparing layer 20 and a liquid cooling layer 30 which are welded and connected in sequence. The heat-sparing layer 20 protrudes away from the heat exchange layer 10 to form a first protrusion 21, the first protrusion 21 encloses the flow space of the heat-sparing flow channel s1, and the heat exchange layer 10 closes the flow space of the first protrusion 21. The liquid cooling layer 30 protrudes away from the heat-sparing layer 20 to form a second protrusion 31, the second protrusion 31 encloses the flow space of the liquid cooling flow channel s2, and the heat-sparing layer 20 closes the flow space of the second protrusion 31. A groove portion 22 is provided on the first protrusion 21. The liquid cooling layer 30 is arranged at the upper end of the heat-sparing layer 20, and extends straight from one end of the heat-sparing layer 20 to the other end.

[0089] In addition, refer to Figure 4 The embodiment of the present application further provides a battery 1000, comprising a battery cell 200 and the heat distribution structure 100 in the above embodiment, wherein the heat exchange surface 10a of the heat distribution structure 100 is in thermal contact with the battery cell 200.

[0090] The battery cell 200 is the smallest charging and discharging unit in the battery pack 1000. The battery cell 200 can be a secondary battery or a primary battery. The battery cell 200 can be a lithium-sulfur battery, a sodium-ion battery or a magnesium-ion battery, but is not limited thereto. The battery cell 200 can be cylindrical, flat, rectangular or other shapes. The battery cell 200 usually includes a battery shell, an electrode assembly contained between the battery shells, and an electrolyte disposed in the battery shell. The electrolyte can be solid or liquid. The electrode assembly is the smallest unit for electrochemical reaction in the battery cell 200, which realizes the charging and discharging of the battery cell 200, and usually includes a positive electrode sheet, a negative electrode sheet, and a separator separating the positive electrode sheet and the negative electrode sheet. The battery cell 200 usually also includes an explosion-proof structure, which is arranged on the battery shell. The explosion-proof structure can explode when the internal pressure of the battery cell 200 reaches a relevant threshold, and the battery cell 200 is connected inside and outside to relieve pressure. The explosion-proof structure can be an explosion-proof valve, a notch, and other structures. The battery cell 200 generally further includes a positive electrode column and a negative electrode column, which are used to connect the battery cell 200 to an external circuit. Regarding the specific structure of the battery cell 200, please refer to the conventional configuration in the art.

[0091] The heat exchange surface 10a of the heat-spreading structure 100 is in thermal contact with the battery cell 200. Specifically, the heat exchange surface 10a of the heat-spreading structure 100 is in surface contact with the side surface (extending in the vertical direction z when in use) of the battery cell 200. A thermal conductive adhesive may be provided between the heat exchange surface 10a and the side surface of the battery cell 200 to strengthen the connection strength between the two and improve the heat exchange reliability.

[0092] The battery 1000 has the beneficial effects described in the above embodiments, which will not be described in detail here.

[0093] Generally, the battery 1000 also includes a box body, which mainly protects the internal battery cell 200 and other structures. The box body generally includes a box shell and a box cover, the battery cell 200, the heat distribution structure 100, etc. are arranged in the box shell, and the box cover can cover the box shell.

[0094] In some embodiments, reference Figure 4 , multiple battery cells 200 are arranged along the length direction y of the heat-spreading structure 100 to form a battery cell group 200A, and multiple battery cell groups 200A are arranged at intervals along the thickness direction x of the heat-spreading decoupling strand. Multiple heat-spreading structures 100 are configured, and the side surface of each battery cell group 200A in the thickness direction x of the heat-spreading structure 100 is in thermal contact with the heat exchange surface 10a of a heat-spreading structure 100.

[0095] At this time, each heat distribution structure 100 can dissipate heat for multiple battery cells 200 in the battery cell group 200A at the same time, and the utilization rate is high. In addition, the battery 1000 includes multiple battery cell groups 200A, which has a large capacity and a long driving range.

[0096] Understandably, both sides of each battery cell group 200A in the thickness direction x of the heat distribution structure 100 are independently in thermal contact with the heat exchange surface 10a of a heat distribution structure 100. The thickness directions x of the heat distribution structures 100 are arranged in parallel, that is, the heat distribution structures 100 are arranged parallel to each other along the thickness direction x.

[0097] In some embodiments, reference Figure 5 , along the thickness direction x of the heat-sparing structure 100, all the heat-sparing structures 100 are divided into multiple heat-sparing groups 100a, each heat-sparing group 100a includes multiple heat-sparing structures 100 arranged adjacent to each other in sequence, and the battery 1000 includes a liquid inlet manifold 300 and a liquid outlet manifold 400. The liquid cooling channels s2 of the heat-sparing structures 100 in each heat-sparing group 100a are connected in series via pipelines, and the liquid cooling channels s2 of the heat-sparing structures 100 in different heat-sparing groups 100a are independently connected between the liquid inlet manifold 300 and the liquid outlet manifold 400.

[0098] That is, the liquid cooling channels s2 of the heat-sparing structures 100 in each heat-sparing group 100a are connected in series to form an integral channel, and then are arranged in parallel with the integral channels formed by the heat-sparing structures 100 in other heat-sparing groups 100a. In this way, the pipeline layout can be simplified. In addition, the coolant flowing out of the liquid inlet main pipe is first connected to the heat-sparing structure located in the middle position, and then connected to the heat-sparing structure located at the edge position. Since the battery cell in the middle position is heated by the battery cells on both sides while self-heating, the temperature is relatively high. Therefore, this method of middle liquid inlet allows the low-temperature coolant to cool the highest temperature part first, which helps to evenly cool each battery cell group.

[0099] Specifically, the battery 1000 may include two heat absorbing groups 100 a .

[0100] In addition, the embodiment of the present application further provides an electric device, including the above-mentioned battery 1000, and the battery 1000 is used to supply power. The electric device may be, but is not limited to, a mobile phone, a tablet, a laptop computer, an electric toy, an electric tool, a battery car, an electric car, a ship, etc. Taking the electric device as a vehicle as an example, the battery 1000 may be arranged at the rear, the front or the bottom of the vehicle, and the battery 1000 may provide power for the drive of the vehicle, and may also provide power for the control system of the vehicle.

[0101] The technical features of the above-described embodiments may be arbitrarily combined. To make the description concise, not all possible combinations of the technical features in the above-described embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0102] The above-mentioned embodiments only express several implementation methods of the present application, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the present application. It should be pointed out that, for a person of ordinary skill in the art, several variations and improvements can be made without departing from the concept of the present application, and these all belong to the protection scope of the present application. Therefore, the protection scope of the present application shall be subject to the attached claims.

Claims

1. A heat-dissipating structure, characterized in that: The heat-saturating structure comprises: A heat-scaling body (100a) is formed with a heat-scaling flow channel (s1), and a surface of one side of the heat-scaling body (100a) in the thickness direction (x) thereof is a heat-exchanging surface (10a) for exchanging heat with a battery core; and The liquid cooling layer (30) is arranged on a side of the heat equalizing body (100a) away from the heat exchange surface (10a), and forms a liquid cooling channel (s2) for exchanging heat with the heat equalizing body (100a), wherein the projection of the liquid cooling channel (s2) along the thickness direction (x) at least partially covers the heat equalizing channel (s1).

2. The heat distribution structure according to claim 1, characterized in that: The heat-saturating body (100a) is arranged vertically, and the liquid cooling layer (30) is arranged at the upper end of the heat-saturating body (100a); The liquid cooling channel (s2) is arranged to extend in a horizontal straight line.

3. The heat distribution structure according to claim 2, characterized in that: The heat-spreading structure also includes a cooling plate, and the cooling plate and the heat-spreading body (100a) are respectively used for heat exchange with different two side surfaces intersecting with the battery core; the cooling plate is heat-conductingly arranged at the lower end of the heat-spreading body (100a), and a cooling channel for circulating a coolant is arranged therein.

4. The heat distribution structure according to claim 1, characterized in that: The liquid cooling layer (30) and the heat equalizing body (100a) are jointly enclosed to form the liquid cooling channel (s2).

5. The heat distribution structure according to claim 1, characterized in that: A boss (T) is protruding from the inner wall of the heat-equalizing channel (s1).

6. The heat distribution structure according to claim 5, characterized in that: The heat-averaging body (100a) comprises a heat exchange layer (10) and a heat-averaging layer (20), and a liquid cooling layer (30) is arranged on the heat-averaging layer (20); The heat-averaging layer (20) is provided with a first convex portion (21) protruding away from the heat exchange layer (10), the first convex portion (21) encloses a flow channel space, and the heat exchange layer (10) closes the flow channel space of the first convex portion (21) to jointly form the heat-averaging flow channel (s1); Wherein, a groove portion (22) recessed toward the heat exchange layer (10) is provided on the first convex portion (21), and the groove portion (22) extends into the heat equalizing channel (s1) to form the boss (T).

7. The heat distribution structure according to claim 6, characterized in that: The groove portion (22) extends into the heat-averaging channel (s1) and abuts against the heat exchange layer (10); and / or, At least part of the groove portions (22) satisfy the condition that every two adjacent groove portions (22) in the vertical direction (z) are staggered in the length direction (y) of the heat-balancing body (100a).

8. The heat distribution structure according to claim 1, characterized in that: The heat equalizing body (100a) has protruding ears (a1) at both ends in the length direction (y), and a connecting joint (40) connected to the liquid cooling channel (s2) is provided at the protruding ear (a1), and the liquid cooling layer (30) extends to the area where the protruding ear (a1) is located.

9. A battery, characterized in that: The battery comprises: A battery cell (200); and The heat distribution structure according to any one of claims 1 to 8, wherein the heat exchange surface (10a) of the heat distribution structure is in thermal contact with the battery core (200).

10. An electrical device, characterized in that: The invention comprises a battery as claimed in claim 9, wherein the battery is used for supplying power.

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