Heat exchanger and battery thermal management system

Abstract

The application relates to a heat exchanger and a battery thermal management system. The heat exchanger is provided with a heat inlet collecting channel, a plurality of heat flow circulation channel layers and a heat outlet collecting channel which are sequentially communicated. The heat exchanger is also provided with a cold inlet collecting channel, a plurality of cold flow circulation channel layers and a cold outlet collecting channel which are sequentially communicated. The heat flow circulation channel layers and the cold flow circulation channel layers are cross-laminated. A first flow guide part is arranged at the opening of the cold inlet collecting channel. The first flow guide part is provided with a first flow guide channel which is communicated with the cold inlet collecting channel. The refrigerant can enter the cold inlet collecting channel through the first flow guide channel. The cross-sectional area of the first flow guide channel is smaller than that of the cold inlet collecting channel. The projection of the first flow guide channel on the cross section of the cold inlet collecting channel along the center line of the cold inlet collecting channel is located at the end of the cross section of the cold inlet collecting channel which is far away from the cold outlet collecting channel. The heat exchanger and the battery thermal management system provided by the application improve the heat exchange efficiency of the heat exchanger without increasing the volume of the heat exchanger.

Description

Technical Field

[0001] This application relates to the field of new energy vehicle technology, and in particular to a heat exchanger and battery thermal management system. Background Technology

[0002] Typically, when heat exchangers are used in battery thermal management systems, they are used for heat exchange between refrigerant and coolant. The coolant cools the battery module through the loop, and at the same time, the temperature of the coolant rises. Then, the coolant exchanges heat with the refrigerant in the heat exchanger, causing the temperature of the coolant to drop, so that the coolant can cool the battery module in the next cycle.

[0003] Furthermore, in the prior art, the heat exchange efficiency of refrigerant and coolant in heat exchangers is relatively low. In order to increase the heat exchange efficiency of refrigerant and coolant in heat exchangers, the common approach is to increase the volume of the heat exchanger. However, heat exchangers are usually used in automotive battery thermal management systems, and the space available for the battery thermal management system is limited. Therefore, an excessively large heat exchanger will lead to difficulties in assembling the battery thermal management system. Summary of the Invention

[0004] Therefore, it is necessary to provide a heat exchanger and a battery thermal management system to improve the heat exchange efficiency of the heat exchanger without increasing its size.

[0005] The heat exchanger provided in this application has a heat inlet collection channel, a multi-layer heat flow circulation channel layer, and a heat outlet collection channel connected in sequence. The heat exchanger also has a cold inlet collection channel, a multi-layer cold flow circulation channel layer, and a cold outlet collection channel connected in sequence, with the heat flow circulation channel layer and the cold flow circulation channel layer arranged in an alternating stacked manner. A first guide section is provided at the opening of the cold inlet collection channel, and the first guide section has a first guide channel connected to the cold inlet collection channel. The refrigerant can enter the cold inlet collection channel through the first guide channel. The cross-sectional area of ​​the first guide channel is smaller than that of the cold inlet collection channel, and the projection of the first guide channel along the center line of the cold inlet collection channel onto the cross-section of the cold inlet collection channel is located at the end of the cross-section of the cold inlet collection channel away from the cold outlet collection channel.

[0006] In one embodiment, the centerline of the first flow guide channel, the centerline of the inlet cold flow collector channel, and the centerline of the outlet cold flow collector channel are located in the same plane. It is understood that this arrangement further extends the contact time between the refrigerant and the coolant within the heat exchanger, thereby improving the heat exchanger's efficiency.

[0007] In one embodiment, a first guide hole is provided at one end of the first guide channel that connects to the cold inlet manifold channel. The inner wall of the first guide hole on the side away from the cold outlet manifold channel is expanded, and the inner wall of the first guide hole on the side closer to the cold outlet manifold channel is contracted. It can be understood that this arrangement facilitates the entry of most of the refrigerant into the cold flow circulation channel layer on the side of the cold inlet manifold channel away from the cold outlet manifold channel.

[0008] In one embodiment, a first baffle is provided at the end of the inlet cold flow collector channel near the outlet cold flow collector channel. The first baffle has a first baffle surface facing the inner wall of the inlet cold flow collector channel away from the outlet cold flow collector channel. The end of the inlet cold flow collector channel near the first guide channel is defined as the first end, and the end of the inlet cold flow collector channel away from the first guide channel is defined as the second end. The first baffle surface extends from the first end near the outlet cold flow collector channel towards the second end away from the outlet cold flow collector channel. It is understood that this arrangement helps improve the uniformity of refrigerant distribution in different cold flow circulation channel layers, thereby further improving the overall heat exchange efficiency of the heat exchanger.

[0009] In one embodiment, the first flow-blocking surface is a plane, a concave surface, or a convex surface.

[0010] In one embodiment, the first baffle surface extends from one end of the first guide channel near the cold outlet collector channel toward the second end away from the cold outlet collector channel. It is understood that this arrangement increases the slope of the first baffle surface, thereby improving the refrigerant distribution effect of the first baffle surface.

[0011] In one embodiment, a first partition is provided on the inner wall of the outlet cold flow manifold near the inlet cold flow manifold, so that the refrigerant in the cold flow circulation channel layer can enter the outlet cold flow manifold from the inner wall of the outlet cold flow manifold away from the inlet cold flow manifold. It can be understood that this arrangement further increases the travel distance of the refrigerant within the cold flow circulation channel layer.

[0012] In one embodiment, the inner wall of the cold outlet manifold near the cold inlet manifold is closed to form a first partition.

[0013] In one embodiment, a second guide portion is provided at the opening of the heat inlet manifold channel. This second guide portion has a second guide channel connecting to the heat inlet manifold channel, allowing coolant to enter the channel. The cross-sectional area of ​​the second guide channel is smaller than that of the heat inlet manifold channel, and the projection of the second guide channel along the centerline of the heat inlet manifold channel onto its cross-section is located at the end of the cross-section furthest from the heat outlet manifold channel. It is understood that this configuration increases the travel distance of the coolant within the heat flow circulation channel layer, further extending the heat exchange time between the refrigerant and the coolant, thereby improving the heat exchange efficiency of the heat exchanger during a single cycle.

[0014] This application also provides a battery thermal management system, which includes the heat exchanger described in any of the above embodiments.

[0015] Compared with the prior art, the heat exchanger and battery thermal management system provided in this application typically has an inlet heat collector channel, an outlet heat collector channel, an inlet cold collector channel, and an outlet cold collector channel respectively located at the four corners of the heat exchanger. Furthermore, to improve the structural strength of the heat exchanger, a certain width is reserved at the edges of the inlet heat collector channel, outlet heat collector channel, inlet cold collector channel, outlet cold collector channel, and the heat exchanger itself. Therefore, when the cross-sectional area of ​​the first guide channel is smaller than the cross-sectional area of ​​the inlet cold collector channel, and the projection of the first guide channel along the centerline of the inlet cold collector channel onto the cross-section of the inlet cold collector channel is located at the end of the inlet cold collector channel away from the outlet cold collector channel, the refrigerant entering from the first guide channel can flow along the inner wall of the end of the inlet cold collector channel away from the outlet cold collector channel. Further, the refrigerant can enter the cold flow circulation channel layer on the side of the inlet cold collector channel away from the outlet cold collector channel. Compared to existing technologies where most refrigerant enters the cold flow circulation channel layer between the inlet and outlet cold flow channels directly from the inlet cold flow channel, the solution in this application significantly increases the travel distance of the refrigerant within the cold flow circulation channel layer, thereby extending the contact time between the refrigerant and the coolant in the heat exchanger and thus improving the heat exchange efficiency of the heat exchanger.

[0016] It should be noted that the refrigerant velocity in the cold flow circulation channel layer is greater than that in the hot flow circulation channel layer. Therefore, by increasing the refrigerant's travel distance in the cold flow circulation channel layer, the residence time of the refrigerant and the residence time of the coolant in the heat exchanger can be made to be more equal during one heat exchange process, thereby ensuring sufficient heat exchange between the refrigerant and the coolant.

[0017] Furthermore, compared to existing technologies, the cross-sectional area of ​​the first guide channel is smaller than that of the cold inlet collector channel, which effectively increases the flow velocity of the refrigerant in the first guide channel. This, in turn, helps to increase the spray distance of the refrigerant in the cold inlet collector channel, preventing the refrigerant from concentrating in the cold flow circulation channel layer near the opening of the cold inlet collector channel, thus preventing uneven heat exchange in different cold flow circulation channel layers. In other words, it improves the heat exchange uniformity of the entire heat exchanger. Attached Figure Description

[0018] To more clearly illustrate the technical solutions in the embodiments of this application or the conventional technology, the drawings used in the description of the embodiments or the conventional technology will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1 A schematic diagram of the structure of a heat exchanger according to an embodiment of this application;

[0020] Figure 2 A planar projection schematic diagram of a heat exchanger according to an embodiment of this application;

[0021] Figure 3 A cross-sectional view of a heat exchanger according to an embodiment provided in this application;

[0022] Figure 4 Partial cross-sectional view of a heat exchanger according to another embodiment provided in this application. Figure 1 ;

[0023] Figure 5 Partial cross-sectional view of a heat exchanger according to another embodiment provided in this application. Figure 1 ;

[0024] Figure 6 Partial cross-sectional view of a heat exchanger according to another embodiment provided in this application. Figure 3 ;

[0025] Figure 7 A partial cross-sectional view of a heat exchanger according to another embodiment provided in this application. Figure 4 .

[0026] Reference numerals: 100, Inlet heat collection channel; 110, Second guide section; 111, Second guide channel; 112, Second guide hole; 120, Second baffle section; 121, Second baffle surface; 130, Third end; 140, Fourth end; 200, Outlet heat collection channel; 300, Heat flow circulation channel layer; 400, Inlet cold collection channel; 410, First guide section; 411, First guide channel; 412, First guide hole; 420, First baffle section; 421, First baffle surface; 430, First end; 440, Second end; 500, Outlet cold collection channel; 600, Cold flow circulation channel layer. Detailed Implementation

[0027] In the description of this application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0028] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this application, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0029] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise expressly limited. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0030] In this application, unless otherwise expressly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0031] It should be noted that when an element is referred to as being "fixed to" or "set on" another element, it can be directly on the other element or there may be an intervening element. When an element is considered to be "connected to" another element, it can be directly connected to the other element or there may be an intervening element. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only possible implementation.

[0032] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terminology used herein in the specification of this application is for the purpose of describing particular embodiments only and is not intended to be limiting of the application. The term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

[0033] Typically, when heat exchangers are used in battery thermal management systems, they are used for heat exchange between refrigerant and coolant. The coolant cools the battery module through the loop, and at the same time, the temperature of the coolant rises. Then, the coolant exchanges heat with the refrigerant in the heat exchanger, causing the temperature of the coolant to drop, so that the coolant can cool the battery module in the next cycle.

[0034] Furthermore, in the prior art, the heat exchange efficiency of refrigerant and coolant in heat exchangers is relatively low. In order to increase the heat exchange efficiency of refrigerant and coolant in heat exchangers, the common approach is to increase the volume of the heat exchanger. However, heat exchangers are usually used in automotive battery thermal management systems, and the space available for the battery thermal management system is limited. Therefore, an excessively large heat exchanger will lead to difficulties in assembling the battery thermal management system.

[0035] Please see Figures 1-3 In order to improve the heat exchange efficiency of the heat exchanger without increasing its volume, this application provides a heat exchanger having a heat inlet collection channel 100, a multi-layer heat flow circulation channel layer 300 and a heat outlet collection channel 200 connected in sequence. The heat exchanger also has a cold inlet collection channel 400, a multi-layer cold flow circulation channel layer 600 and a cold outlet collection channel 500 connected in sequence, with the heat flow circulation channel layer 300 and the cold flow circulation channel layer 600 arranged in a cross-layered manner. Furthermore, a first guide section 410 is provided at the opening of the cold inlet manifold 400. The first guide section 410 is provided with a first guide channel 411 that connects to the cold inlet manifold 400. The refrigerant can enter the cold inlet manifold 400 through the first guide channel 411. The cross-sectional area of ​​the first guide channel 411 is smaller than the cross-sectional area of ​​the cold inlet manifold 400. The projection of the first guide channel 411 along the center line of the cold inlet manifold 400 onto the cross-section of the cold inlet manifold 400 is located at the end of the cross-section of the cold inlet manifold 400 that is far away from the cold outlet manifold 500.

[0036] It should be noted that, in this embodiment, when the cross-section of the cold inlet manifold 400 is circular, the projection of the first guide channel 411 along the center line of the cold inlet manifold 400 onto the cross-section of the cold inlet manifold 400 is located at the end of the cross-section of the cold inlet manifold 400 away from the cold outlet manifold 500. This means that the projection of the first guide channel 411 along the center line of the cold inlet manifold 400 onto the cross-section of the cold inlet manifold 400 is located in the semi-circular region of the cross-section of the cold inlet manifold 400 away from the cold outlet manifold 500. Similarly, when the cross-section of the cold inlet manifold 400 is square, the projection of the first guide channel 411 along the center line of the cold inlet manifold 400 onto the cross-section of the cold inlet manifold 400 is located at the end of the cross-section of the cold inlet manifold 400 away from the cold outlet manifold 500. This means that the projection of the first guide channel 411 along the center line of the cold inlet manifold 400 onto the cross-section of the cold inlet manifold 400 is located in the triangular region of the cross-section of the cold inlet manifold 400 away from the cold outlet manifold 500.

[0037] Typically, the heat inlet manifold 100, heat outlet manifold 200, cold inlet manifold 400, and cold outlet manifold 500 are located at the four corners of the heat exchanger. In order to improve the structural strength of the heat exchanger, a certain width is reserved for the heat inlet manifold 100, heat outlet manifold 200, cold inlet manifold 400, cold outlet manifold 500, and the edges of the heat exchanger. Therefore, when the cross-sectional area of ​​the first guide channel 411 is smaller than the cross-sectional area of ​​the cold inlet manifold 400, and the projection of the first guide channel 411 along the center line of the cold inlet manifold 400 onto the cross-section of the cold inlet manifold 400 is located at the end of the cross-section of the cold inlet manifold 400 away from the cold outlet manifold 500, the refrigerant entering from the first guide channel 411 can flow along the inner wall of the end of the cold inlet manifold 400 away from the cold outlet manifold 500. Furthermore, the refrigerant can enter the cold flow circulation channel layer 600 on the side of the cold inlet manifold 400 away from the cold outlet manifold 500. Compared to the prior art, in which most of the refrigerant enters the cold flow circulation channel layer 600 between the cold inlet manifold 400 and the cold outlet manifold 500 directly from the cold inlet manifold 400, the solution of this application significantly increases the travel distance of the refrigerant in the cold flow circulation channel layer 600, thereby prolonging the contact time between the refrigerant and the coolant in the heat exchanger, and thus improving the heat exchange efficiency of the heat exchanger.

[0038] It should be noted that the refrigerant velocity in the cold flow circulation channel layer 600 is greater than the coolant velocity in the hot flow circulation channel layer 300. Therefore, by increasing the refrigerant's travel distance in the cold flow circulation channel layer 600, the residence time of the refrigerant in the heat exchanger during one heat exchange process can be made to be more equal, thereby ensuring sufficient heat exchange between the refrigerant and the coolant.

[0039] Furthermore, compared to the prior art, the cross-sectional area of ​​the first guide channel 411 is smaller than that of the cold inlet collection channel 400, which effectively increases the flow velocity of the refrigerant in the first guide channel 411. This, in turn, helps to increase the spray distance of the refrigerant in the cold inlet collection channel 400, and prevents the refrigerant from concentrating into the cold flow circulation channel layer 600 near the opening of the cold inlet collection channel 400, which would lead to uneven heat exchange in different cold flow circulation channel layers 600. In other words, it improves the heat exchange uniformity of the entire heat exchanger.

[0040] Furthermore, in one embodiment, as Figure 2 As shown, the centerline of the first flow guide channel 411, the centerline of the inlet cooling flow collection channel 400, and the centerline of the outlet cooling flow collection channel 500 are located in the same plane.

[0041] Thus, the projection of the first guide channel 411 along the center line of the inlet cooling manifold 400 onto the cross-section of the inlet cooling manifold 400 is located at the position furthest from the outlet cooling manifold 500 on the cross-section of the inlet cooling manifold 400. This is beneficial for the refrigerant to travel the longest distance from the inlet cooling manifold 400 to the outlet cooling manifold 500, that is, to further extend the contact time between the refrigerant and the coolant in the heat exchanger, thereby improving the heat exchange efficiency of the heat exchanger.

[0042] In one embodiment, such as Figure 4 As shown, the first guide channel 411 is connected to the end of the cold inlet collection channel 400 and is provided with a first guide hole 412. The inner wall of the first guide hole 412 on the side away from the cold outlet collection channel 500 is expanded, and the inner wall of the first guide hole 412 on the side close to the cold outlet collection channel 500 is contracted.

[0043] Thus, by setting the first guide hole 412, the refrigerant can flow directly toward the side of the inlet cold flow manifold 400 away from the outlet cold flow manifold 500, so that most of the refrigerant can enter the cold flow circulation channel layer 600 on the side of the inlet cold flow manifold 400 away from the outlet cold flow manifold 500.

[0044] In one embodiment, such as Figure 5 As shown, a first baffle 420 is provided at one end of the cold inlet manifold 400 near the cold outlet manifold 500. The first baffle 420 is provided with a first baffle surface 421 facing the inner wall of the cold inlet manifold 400 away from the cold outlet manifold 500. The end of the cold inlet manifold 400 near the first guide channel 411 is defined as the first end 430, and the end of the cold inlet manifold 400 away from the first guide channel 411 is defined as the second end 440. The first baffle surface 421 extends from the end of the first end 430 near the cold outlet manifold 500 toward the end of the second end 440 away from the cold outlet manifold 500.

[0045] Thus, after the refrigerant enters the cold air inlet and outlet channel 400 from the first guide channel 411, it directly impacts the first baffle surface 421. Furthermore, under the reflection effect of the first baffle surface 421, the refrigerant is evenly dispersed into different cold air circulation channel layers 600. Therefore, this arrangement helps improve the uniformity of refrigerant distribution in different cold air circulation channel layers 600, thereby further improving the overall heat exchange efficiency of the heat exchanger.

[0046] Specifically, in one embodiment, the first baffle surface 421 is a plane, a concave surface, or a convex surface. When the first baffle surface 421 is concave, it has a converging effect, which facilitates the refrigerant to concentrate and enter different cold flow circulation channel layers 600. When the first baffle surface 421 is convex, it has a diverging effect, which facilitates the refrigerant to disperse and enter different cold flow circulation channel layers 600.

[0047] Furthermore, in one embodiment, as Figure 5 As shown, the first baffle surface 421 extends from the end of the first guide channel 411 near the outlet cold collection channel 500 toward the second end 440 away from the outlet cold collection channel 500.

[0048] This increases the slope of the first baffle surface 421, thereby improving the distribution effect of the first baffle surface 421 on the refrigerant.

[0049] In order to maximize the travel of the refrigerant in the cold flow circulation channel layer 600, in one embodiment, a first partition (not shown) is provided on the inner wall of the outlet cold flow manifold 500 near the inlet cold flow manifold 400, so that the refrigerant in the cold flow circulation channel layer 600 can enter the outlet cold flow manifold 500 from the inner wall of the outlet cold flow manifold 500 away from the inlet cold flow manifold 400.

[0050] This further increases the travel distance of the refrigerant within the cold flow circulation channel layer 600.

[0051] Specifically, in one embodiment, the inner wall of the cold outlet manifold 500 near the cold inlet manifold 400 is closed to form a first partition. In other embodiments, the inner wall of the cold outlet manifold 500 near the cold inlet manifold 400 is provided with other partitions to form the first partition.

[0052] Correspondingly, in one embodiment, such as Figure 2 , Figure 6 and Figure 7As shown, a second guide section 110 is provided at the opening of the heat inlet collection channel 100. The second guide section 110 is provided with a second guide channel 111 that connects to the heat inlet collection channel 100. Coolant can enter the heat inlet collection channel 100 through the second guide channel 111. The cross-sectional area of ​​the second guide channel 111 is smaller than the cross-sectional area of ​​the heat inlet collection channel 100. The projection of the second guide channel 111 along the center line of the heat inlet collection channel 100 onto the cross-section of the heat inlet collection channel 100 is located at the end of the cross-section of the heat inlet collection channel 100 that is away from the heat outlet collection channel 200.

[0053] This configuration increases the travel distance of the coolant within the heat flow circulation channel layer 300, further extending the heat exchange time between the refrigerant and the coolant, thereby improving the heat exchange efficiency of the heat exchanger during one cycle.

[0054] Furthermore, in one embodiment, as Figure 2 As shown, the centerline of the second flow guide channel 111, the centerline of the heat inlet collection channel 100, and the centerline of the heat outlet collection channel 200 are located in the same plane.

[0055] Thus, the projection of the second guide channel 111 along the center line of the heat inlet collector channel 100 onto the cross-section of the heat inlet collector channel 100 is located at the position furthest from the heat outlet collector channel 200 on the cross-section of the heat inlet collector channel 100. This is beneficial for the coolant to travel the longest distance from the heat inlet collector channel 100 to the heat outlet collector channel 200, that is, to further extend the contact time between the coolant and the refrigerant in the heat exchanger, thereby improving the heat exchange efficiency of the heat exchanger.

[0056] In one embodiment, such as Figure 6 As shown, the second guide channel 111 is connected to the heat collection channel 100 at one end and is provided with a second guide hole 112. The inner wall of the second guide hole 112 on the side away from the heat collection channel 200 is expanded, and the inner wall of the second guide hole 112 on the side close to the heat collection channel 200 is contracted.

[0057] Thus, by providing the second guide hole 112, the coolant can flow directly toward the side of the inlet heat collection channel 100 away from the outlet heat collection channel 200, so that most of the coolant can enter the heat flow circulation channel layer 300 on the side of the inlet heat collection channel 100 away from the outlet heat collection channel 200.

[0058] In one embodiment, such as Figure 7As shown, a second baffle 120 is provided at one end of the heat inlet collector channel 100 near the heat outlet collector channel 200. The second baffle 120 is provided with a second baffle surface 121 facing the inner wall of the side of the heat inlet collector channel 100 away from the heat outlet collector channel 200. The end of the heat inlet collector channel 100 near the second guide channel 111 is defined as the third end 130, and the end of the heat inlet collector channel 100 away from the second guide channel 111 is defined as the fourth end 140. The second baffle surface 121 extends from the end of the third end 130 near the heat outlet collector channel 200 toward the end of the fourth end 140 away from the heat outlet collector channel 200.

[0059] Thus, after the coolant enters the heat inlet and collector channel 100 from the second guide channel 111, it directly impacts the second baffle surface 121. Furthermore, under the reflection effect of the second baffle surface 121, the coolant is evenly dispersed into different heat flow circulation channel layers 300. Therefore, this arrangement helps improve the uniformity of coolant distribution in different heat flow circulation channel layers 300, thereby further improving the overall heat exchanger efficiency.

[0060] Specifically, in one embodiment, the second baffle surface 121 is a plane, a concave surface, or a convex surface. When the second baffle surface 121 is concave, it has a converging effect, which facilitates the coolant to concentrate and enter different heat flow circulation channel layers 300. When the second baffle surface 121 is convex, it has a diverging effect, which facilitates the coolant to disperse and enter different heat flow circulation channel layers 300.

[0061] Furthermore, in one embodiment, as Figure 7 As shown, the second baffle surface 121 extends from one end of the second guide channel 111 near the heat collection channel 200 toward the second end 440 away from the heat collection channel 200.

[0062] This increases the slope of the second baffle surface 121, thereby improving the distribution effect of the second baffle surface 121 on the coolant.

[0063] In order to maximize the travel of the coolant within the heat flow circulation channel layer 300, in one embodiment, a second partition (not shown) is provided on the inner wall of the heat outlet collection channel 200 near the heat inlet collection channel 100, so that the coolant in the heat flow circulation channel layer 300 can enter the heat outlet collection channel 200 from the inner wall of the heat outlet collection channel 200 away from the heat inlet collection channel 100.

[0064] This further increases the travel distance of the coolant within the heat flow circulation channel layer 300.

[0065] Specifically, in one embodiment, the inner wall of the heat outlet collecting channel 200 near the heat inlet collecting channel 100 is closed to form a second partition. In other embodiments, other partitions are provided on the inner wall of the heat outlet collecting channel 200 near the heat inlet collecting channel 100 to form a second partition.

[0066] This application also provides a battery thermal management system, which includes the heat exchanger described in any of the above embodiments.

[0067] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above 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.

[0068] The embodiments described above are merely illustrative of several implementation methods of this application, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the patent application. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this application, and these all fall within the scope of protection of this application. Therefore, the patent protection scope of this application should be determined by the appended claims.

Claims

1. A heat exchanger, characterized in that, The heat exchanger is provided with a heat inlet collection channel (100), a multi-layer heat flow circulation channel layer (300), and a heat outlet collection channel (200) connected in sequence. The heat exchanger is also provided with a cold inlet collection channel (400), a multi-layer cold flow circulation channel layer (600), and a cold outlet collection channel (500) connected in sequence. The heat flow circulation channel layer (300) and the cold flow circulation channel layer (600) are arranged in a cross-stacked manner. The opening of the cold inlet manifold (400) is provided with a first guide section (410), and the first guide section (410) is provided with a first guide channel (411) that connects to the cold inlet manifold (400). The refrigerant can enter the cold inlet manifold (400) through the first guide channel (411). The cross-sectional area of ​​the first guide channel (411) is smaller than the cross-sectional area of ​​the cold inlet manifold (400), and the projection of the first guide channel (411) along the center line of the cold inlet manifold (400) onto the cross-section of the cold inlet manifold (400) is located at the end of the cross-section of the cold inlet manifold (400) away from the cold outlet manifold (500).

2. The heat exchanger according to claim 1, characterized in that, The centerline of the first flow guide channel (411), the centerline of the cold inlet flow collector channel (400), and the centerline of the cold outlet flow collector channel (500) are located in the same plane.

3. The heat exchanger according to claim 1, characterized in that, The first guide channel (411) is connected to the end of the cold inlet collection channel (400) and is provided with a first guide hole (412). The inner wall of the first guide hole (412) away from the cold outlet collection channel (500) is expanded, and the inner wall of the first guide hole (412) close to the cold outlet collection channel (500) is contracted.

4. The heat exchanger according to claim 1, characterized in that, The inlet cooling manifold (400) has a first baffle (420) at one end near the outlet cooling manifold (500). The first baffle (420) has a first baffle surface (421) facing the inner wall of the inlet cooling manifold (400) away from the outlet cooling manifold (500). The end of the inlet cooling manifold (400) near the first guide channel (411) is defined as the first end (430), and the end of the inlet cooling manifold (400) away from the first guide channel (411) is defined as the second end (440). The first baffle surface (421) extends from the end of the first end (430) near the outlet cooling manifold (500) toward the end of the second end (440) away from the outlet cooling manifold (500).

5. The heat exchanger according to claim 4, characterized in that, The first flow-blocking surface (421) is a plane, a concave surface, or a convex surface.

6. The heat exchanger according to claim 4, characterized in that, The first baffle surface (421) extends from one end of the first guide channel (411) near the cold outlet collection channel (500) toward the second end (440) away from the cold outlet collection channel (500).

7. The heat exchanger according to claim 1, characterized in that, The cold outlet manifold (500) has a first partition on the inner wall of the side of the cold inlet manifold (400) so that the refrigerant in the cold flow circulation channel layer (600) can enter the cold outlet manifold (500) from the inner wall of the side of the cold outlet manifold (500) away from the cold inlet manifold (400).

8. The heat exchanger according to claim 7, characterized in that, The first partition is formed by sealing the inner wall of the outlet cooling collection channel (500) near the inlet cooling collection channel (400).

9. The heat exchanger according to claim 1, characterized in that, The heat inlet collection channel (100) has a second guide section (110) at its opening. The second guide section (110) has a second guide channel (111) that connects to the heat inlet collection channel (100). Coolant can enter the heat inlet collection channel (100) through the second guide channel (111). The cross-sectional area of ​​the second guide channel (111) is smaller than the cross-sectional area of ​​the heat inlet collection channel (100). The projection of the second guide channel (111) along the center line of the heat inlet collection channel (100) onto the cross-section of the heat inlet collection channel (100) is located at the end of the cross-section of the heat inlet collection channel (100) away from the heat outlet collection channel (200).

10. A battery thermal management system, characterized in that, Including the heat exchanger as described in any one of claims 1-9.

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