Heat exchangers and thermal management systems

Abstract

This application relates to a heat exchanger and a thermal management system. The heat exchanger includes a flow guide plate with first flow guide grooves. Adjacent first flow guide grooves form multiple flow splitting gaps. The first flow guide groove is formed by either a straight groove segment or a curved groove segment alone, or by alternating arrangements of both. The straight groove segment includes multiple staggered channels connected sequentially along its own centerline, with adjacent staggered channels arranged in a direction perpendicular to the centerline of the straight groove segment. The flow guide plate also has multiple second flow guide grooves and flow guide protrusions. The flow guide protrusions divide the area of ​​the cold flow channel layer between the first and second flow guide grooves into multiple flow guide channels. The flow area of ​​the flow guide channels, the flow area of ​​the first flow guide groove, and the flow area of ​​the second flow guide groove are all equal. The heat exchanger and thermal management system provided by this application solve the problem of thermal stress concentration in the heat exchanger caused by inconsistent heat exchange effects at different locations in the cold flow channel layer.

Description

[0001] This application is a divisional application of the patent application filed on December 28, 2022, with application number 202211692896.5 and invention title "Heat Exchanger and Thermal Management System". Technical Field

[0002] This application relates to the field of heat exchanger technology, and in particular to a heat exchanger and thermal management system. Background Technology

[0003] Typically, a heat exchanger has a series of interconnected inlet hot flow collector channels, multiple layers of hot flow channels, and an outlet hot flow collector channel. It also has a series of interconnected inlet cold flow collector channels, multiple layers of cold flow channels, and an outlet cold flow collector channel. To facilitate rapid heat dissipation from the high-temperature medium within the hot flow channel layers, the hot and cold flow channel layers are alternately stacked. When the low-temperature medium enters the cold flow channel layer, turbulence can easily occur within it. This turbulence increases the flow resistance of the low-temperature medium within the cold flow channel layer, thus affecting the heat exchanger's heat exchange efficiency.

[0004] To address the issue of excessive flow resistance in the cold flow channel layer for cryogenic media, a common technique is to install multiple flow channels within the cold flow channel layer. However, conventional flow channels cannot resolve the problem of inconsistent heat exchange effects of the cryogenic media at different locations within the cold flow channel layer, which can lead to thermal stress concentration in the heat exchanger. Summary of the Invention

[0005] Therefore, it is necessary to provide a heat exchanger and thermal management system to solve the problem of inconsistent heat exchange effect of low temperature medium in different parts of the cold flow channel layer, which leads to the heat exchanger being prone to thermal stress concentration.

[0006] The heat exchanger provided in this application has a heat inlet collection channel, a multi-layer heat flow 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 channel layer, and a cold outlet collection channel connected in sequence, with the heat flow channel layer and cold flow channel layer alternately stacked. The heat exchanger includes a flow guide plate disposed within the cold flow channel layer, and the flow guide plate has multiple first flow guide grooves connecting the cold inlet collection channel and the cold outlet collection channel. Adjacent first flow guide grooves are spaced apart to form multiple flow split gaps, so that the low-temperature medium in the cold flow channel layer can flow from the cold inlet collection channel into the cold outlet collection channel along the first flow guide grooves and flow split gaps, respectively. Furthermore, the first diversion channel includes straight channel segments and curved channel segments. The first diversion channel is formed by either a single straight channel segment or a curved channel segment, or by alternating arrangements of both. The sidewalls of the curved channel segments are smoothly extending curves, while the centerline of the straight channel segments is straight. Each straight channel segment includes multiple staggered channels connected sequentially along its own centerline. Adjacent staggered channels are arranged in a direction perpendicular to the centerline of the straight channel segment, so that each staggered channel can connect to an adjacent staggered channel and a flow divider gap located on one side of the straight channel segment. The cold inlet and cold outlet channels are diagonally distributed, as are the hot inlet and hot outlet channels. The first diversion channel is located between the hot inlet and hot outlet channels. The flow guide plate also has multiple second flow guide channels. A portion of the second flow guide channels are located on the side of the heat inlet collection channel opposite to the heat outlet collection channel, while another portion are located on the side of the heat outlet collection channel opposite to the heat inlet collection channel. The flow guide plate also has flow guide protrusions located in the area between the first and second flow guide channels to divide the area of ​​the cold flow channel layer between the first and second flow guide channels into multiple flow guide channels. Furthermore, the flow area of ​​each flow guide channel, the flow area of ​​the first flow guide channel, and the flow area of ​​the second flow guide channel are all equal.

[0007] In one embodiment, the sidewall of the curved groove section has a connecting hole for connecting the flow divider gap at the position where its curvature is the greatest.

[0008] In one embodiment, the misaligned channel is continuous along the centerline of the straight groove segment.

[0009] In one embodiment, the drain plate is a stamped part.

[0010] In one embodiment, the drain plate is a welded component.

[0011] In one embodiment, the drainage plate is a 3D printed part.

[0012] In one embodiment, the flow area at the inlet of any first flow channel near the end of the cold inlet and the flow area at the inlet of any split gap near the end of the cold inlet and the flow channel are equal.

[0013] In one embodiment, the flow area at the inlet of any first drainage channel near the end of the cold collection channel is equal to the flow area at the inlet of any diversion gap near the end of the cold collection channel.

[0014] In one embodiment, adjacent partitions are respectively arranged to form a cold flow channel layer and a hot flow channel layer, and the flow guide plate is fixedly connected to the adjacent partition.

[0015] This application also provides a thermal management system, which includes the heat exchanger described in any of the above embodiments.

[0016] Compared to existing technologies, the heat exchanger and thermal management system provided in this application have a relatively large area of ​​the entire cold flow channel layer relative to the cross-sectional areas of the inlet and outlet cold flow channels. Therefore, to connect the inlet and outlet cold flow channels and to ensure a more uniform distribution of the cryogenic medium within the cold flow channel layer, the first guide channel typically cannot be directly connected to the inlet and outlet cold flow channels. That is, a portion of the first guide channel must extend towards both sides of the center line connecting the inlet and outlet cold flow channels. Compared to using a zigzag-shaped first guide channel, using a combination of straight and curved channel segments to form the first guide channel maximizes the smooth flow of the cryogenic medium within the first guide channel, preventing a sudden change in flow direction that would cause a sharp increase in flow resistance. In other words, this design minimizes the flow resistance of the cryogenic medium within the cold flow channel layer. Furthermore, designing the sidewalls of the curved groove section as a smoothly extending curve helps reduce the flow resistance of the cryogenic medium within the curved groove section, thereby increasing the flow velocity of the cryogenic medium within the curved groove section. Moreover, by setting straight groove sections, and with adjacent staggered channels arranged in a direction perpendicular to the centerline of the straight groove section, the cryogenic medium can continuously switch flow paths between the staggered channels and the flow dividers. This reduces the flow velocity of the cryogenic medium, ensuring that the flow velocity of the cryogenic medium in the straight groove section region (including the flow dividers between straight groove sections) remains consistent with its flow velocity in the curved groove section region (including the flow dividers between curved groove sections). Furthermore, each staggered channel can connect adjacent staggered channels and the flow divider located on one side of the straight groove section, enabling continuous redistribution of the cryogenic medium between the straight groove section and the flow divider. This allows the hydraulic pressure of the cryogenic medium in the straight groove section region to tend towards equilibrium, thereby making the flow velocity of the cryogenic medium in the straight groove section region also tend towards uniformity, thus achieving a uniform flow effect for the cryogenic medium. In summary, by balancing the flow velocity of the cryogenic medium at different locations within the cold flow channel layer, the heat transfer effect of the cryogenic medium at these locations can be kept consistent. This effectively solves the problem of inconsistent heat transfer effects of the cryogenic medium at various points within the cold flow channel layer, which can lead to thermal stress concentration in the heat exchanger. Furthermore, this design further reduces the flow resistance of the cryogenic medium within the cold flow channel layer, thereby reducing the pressure drop of the cryogenic medium within the cold flow channel layer. Attached Figure Description

[0017] 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.

[0018] Figure 1A schematic diagram of the structure of a heat exchanger according to an embodiment of this application;

[0019] Figure 2 A partial exploded view of a heat exchanger according to an embodiment provided in this application;

[0020] Figure 3 A schematic diagram of the structure of a drainage plate according to an embodiment of this application.

[0021] Reference numerals: 110, Low-temperature medium inlet pipe; 120, Low-temperature medium outlet pipe; 130, High-temperature medium inlet pipe; 140, High-temperature medium outlet pipe; 200, Heat exchange core; 210, Heat inlet collection channel; 230, Heat outlet collection channel; 240, Cold inlet collection channel; 260, Cold outlet collection channel; 300, Drain plate; 310, First drainage groove; 311, Straight groove section; 312, Offset channel; 313, Curved groove section; 314, Connecting hole; 320, Dividing gap; 330, Drain protrusion; 331, Drain channel; 340, Second drainage groove; 400, Partition plate. Detailed Implementation

[0022] 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.

[0023] 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.

[0024] 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.

[0025] 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.

[0026] 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.

[0027] 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.

[0028] Typically, a heat exchanger has a series of interconnected inlet hot flow collector channels, multiple layers of hot flow channels, and an outlet hot flow collector channel. It also has a series of interconnected inlet cold flow collector channels, multiple layers of cold flow channels, and an outlet cold flow collector channel. To facilitate rapid heat dissipation from the high-temperature medium within the hot flow channel layers, the hot and cold flow channel layers are alternately stacked. When the low-temperature medium enters the cold flow channel layer, turbulence can easily occur within it. This turbulence increases the flow resistance of the low-temperature medium within the cold flow channel layer, thus affecting the heat exchanger's heat exchange efficiency.

[0029] To address the issue of excessive flow resistance in the cold flow channel layer for cryogenic media, a common technique is to install multiple flow channels within the cold flow channel layer. However, conventional flow channels cannot resolve the problem of inconsistent heat exchange effects of the cryogenic media at different locations within the cold flow channel layer, which can lead to thermal stress concentration in the heat exchanger.

[0030] Please see Figures 1-3 To address the problem of inconsistent heat exchange effects of the low-temperature medium at different locations in the cold flow channel layer, which can lead to thermal stress concentration in the heat exchanger, this application provides a heat exchanger comprising a low-temperature medium inlet pipe 110, a low-temperature medium outlet pipe 120, a high-temperature medium inlet pipe 130, a high-temperature medium outlet pipe 140, and a heat exchange core 200. The low-temperature medium enters the heat exchange core 200 through the low-temperature medium inlet pipe 110 and exits through the low-temperature medium outlet pipe 120. The high-temperature medium enters the heat exchange core 200 through the high-temperature medium inlet pipe 130 and exits through the high-temperature medium outlet pipe 140. Furthermore, heat exchange occurs between the low-temperature medium and the high-temperature medium within the heat exchange core 200. The heat exchanger is provided with a sequentially connected inlet heat flow channel 210, a multi-layer heat flow channel layer (not shown), and an outlet heat flow channel 230. The heat exchanger also has a sequentially connected inlet cold flow channel 240, a multi-layer cold flow channel layer (not shown), and an outlet cold flow channel 260, with the heat flow channel layers and cold flow channel layers alternately stacked. Furthermore, the low-temperature medium inlet pipe 110 is connected to the inlet cold flow channel 240, the low-temperature medium outlet pipe 120 is connected to the outlet cold flow channel 260, the high-temperature medium inlet pipe 130 is connected to the inlet heat flow channel 210, and the high-temperature medium outlet pipe 140 is connected to the outlet heat flow channel 230. Both the cold flow channel layer and the heat flow channel layer are located within the heat exchange core 200.

[0031] Furthermore, the heat exchanger includes a flow guide plate 300, which is disposed within the cold flow channel layer. The flow guide plate 300 is provided with multiple first flow guide grooves 310 that can connect the inlet cold flow collection channel 240 and the outlet cold flow collection channel 260. Adjacent first flow guide grooves 310 are spaced apart to form multiple flow split gaps 320, so that the low-temperature medium in the cold flow channel layer can flow from the inlet cold flow collection channel 240 into the outlet cold flow collection channel 260 along the first flow guide grooves 310 and the flow split gaps 320 respectively. Furthermore, the first drainage channel 310 is formed by either a straight channel segment 311 or a curved channel segment 313 alone, or by alternating arrangements of both straight channel segments 311 and curved channel segments 313. The sidewalls of the curved channel segment 313 are smoothly extending curves, and the centerline of the straight channel segment 311 is straight. Each straight channel segment 311 includes multiple staggered channels 312 that are sequentially connected along its own centerline. Adjacent staggered channels 312 are staggered along a direction perpendicular to the centerline of the straight channel segment 311, so that each staggered channel 312 can connect to the adjacent staggered channel 312 and the diversion gap 320 located on one side of the straight channel segment 311.

[0032] It should be noted that each misaligned channel 312 is continuous along the center line of the straight groove segment 311.

[0033] It is understandable that the area of ​​the entire cold flow channel layer is relatively large compared to the cross-sectional areas of the inlet cold flow channel 240 and the outlet cold flow channel 260. Therefore, in order to connect the inlet cold flow channel 240 and the outlet cold flow channel 260, and to ensure a more uniform distribution of the cryogenic medium within the cold flow channel layer, the first guide groove 310 typically cannot be connected to the inlet cold flow channel 240 and the outlet cold flow channel 260 in a straight line. That is, part of the first guide groove 310 must extend towards both sides of the center line connecting the inlet cold flow channel 240 and the outlet cold flow channel 260. Compared to using a zigzag-shaped first guide groove 310, using a combination of straight groove segments 311 and curved groove segments 313 to form the first guide groove 310 can maximize the smooth flow of the cryogenic medium within the first guide groove 310, avoiding a sudden change in the flow direction of the cryogenic medium that would cause a sharp increase in flow resistance. In other words, this design can minimize the flow resistance of the cryogenic medium within the cold flow channel layer.

[0034] Furthermore, by setting the sidewalls of the curved groove section 313 to a smoothly extending curve, it is beneficial to reduce the flow resistance of the cryogenic medium within the curved groove section 313, thereby increasing the flow velocity of the cryogenic medium within the curved groove section 313. Moreover, by setting straight groove sections 311, and by arranging adjacent staggered channels 312 in a direction perpendicular to the centerline of the straight groove sections 311, the cryogenic medium can continuously switch flow paths between the staggered channels 312 and the flow divider gaps 320. This reduces the flow velocity of the cryogenic medium, ensuring that the flow velocity of the cryogenic medium in the region of the straight groove sections 311 (including the flow divider gaps 320 between the straight groove sections 311) remains consistent with the flow velocity in the region of the curved groove sections (including the flow divider gaps 320 between the curved groove sections 313).

[0035] Furthermore, each misaligned channel 312 can connect to adjacent misaligned channels 312 and the flow divider gap 320 located on one side of the straight groove section 311, thereby enabling the continuous redistribution of the cryogenic medium between the straight groove section 311 and the flow divider gap 320, so that the hydraulic pressure of the cryogenic medium in the region of the straight groove section 311 tends to be balanced, and thus the flow velocity of the cryogenic medium in the region of the straight groove section 311 tends to be the same, thereby achieving the effect of uniform flow of the cryogenic medium.

[0036] In summary, by balancing the flow velocity of the cryogenic medium at different locations in the cold flow channel layer, the heat exchange effect of the cryogenic medium at different locations in the cold flow channel layer can be kept consistent. This effectively solves the problem of inconsistent heat exchange effect of the cryogenic medium at different locations in the cold flow channel layer, which leads to the heat exchanger being prone to thermal stress concentration.

[0037] Furthermore, the sidewalls of the curved groove section are designed as smoothly extending curves, which is beneficial for the mold opening and processing of the flow guide plate 300.

[0038] Specifically, in one embodiment, the diversion plate 300 is processed into a plurality of first diversion grooves 310 by stamping.

[0039] However, this is not the only one. In other embodiments, the diversion plate 300 can also be processed by welding to form multiple first diversion grooves 310, or the diversion plate 300 can also be processed by 3D printing. These are not limited to one method here.

[0040] In one embodiment, such as Figure 3 As shown, when the first drainage channel 310 is formed by alternating straight channel segments 311 and curved channel segments 313, the width of the misaligned channel 312 tends to increase along the direction perpendicular to the center line of the straight channel segment 311, from away from the curved channel segment 313 to near the curved channel segment 313.

[0041] This configuration facilitates the entry of the cryogenic medium into the misaligned channel 312 near the curved groove section 313, thereby increasing the flow rate of the cryogenic medium in the misaligned channel 312 near the curved groove section 313.

[0042] In one embodiment, such as Figure 3 As shown, the flow area at the inlet of any first flow channel 310 near the end of the cold inlet collection channel 240 is equal to the flow area at the inlet of any split gap 320 near the end of the cold inlet collection channel 240.

[0043] It should be noted that the flow area at the inlet of any first flow channel 310 near the end of the cold inlet collection channel 240 and the flow area at the inlet of any branch gap 320 near the end of the cold inlet collection channel 240 are equal. This means that the flow area at the inlet of each first flow channel 310 near the end of the cold inlet collection channel 240 is equal, the flow area at the inlet of each branch gap 320 near the end of the cold inlet collection channel 240 is equal, and the flow area at the inlet of the first flow channel 310 near the end of the cold inlet collection channel 240 and the flow area at the inlet of the branch gap 320 near the end of the cold inlet collection channel 240 are also equal.

[0044] In this way, the low-temperature medium flowing out of the cold flow channel 240 can uniformly enter each of the first flow channels 310 and the flow divider gaps 320, so that the flow rate of the low-temperature medium in each of the first flow channels 310 and the flow divider gaps 320 is equal, thereby ensuring that the total heat exchange of the low-temperature medium in each of the first flow channels 310 and each flow divider gap 320 is consistent. Combined with the fact that the flow velocity of the low-temperature medium in the straight channel section 311 region and the curved channel section region is also consistent, it can be seen that this arrangement ensures that the flow rate and velocity of the low-temperature medium are consistent throughout the cold flow channel layer, further ensuring that the heat exchange effect is consistent throughout the cold flow channel layer, thereby avoiding the effect of thermal stress concentration in the heat exchanger.

[0045] Specifically, in one embodiment, when the distance between the two first diversion channels 310 tends to increase or decrease along the flow direction of the low-temperature medium, the flow area at the inlet of any first diversion channel 310 near the end of the cold inlet channel 240 can be equal to the flow area at the inlet of any diversion gap 320 near the end of the cold inlet channel 240 by adjusting the distance between the first diversion channel 310 and the cold inlet channel 240.

[0046] In one embodiment, such as Figure 3 As shown, the flow area at the inlet of any first flow channel 310 near the end of the cold flow collection channel 260 is equal to the flow area at the inlet of any split gap 320 near the end of the cold flow collection channel 260.

[0047] In this way, the different flow rates of the low-temperature medium flowing out from different first flow channels 310 and different flow dividers 320 can be avoided, which would cause turbulence in the low-temperature medium at the cold flow collection channel 260, thereby avoiding an increase in the flow resistance of the low-temperature medium in the cold flow channel layer.

[0048] In one embodiment, such as Figure 3 As shown, the sidewall of the curved groove section 313 is provided with a connecting hole 314 for connecting the flow splitting gap 320 at the position where its curvature is the largest.

[0049] Since the adjacent first diversion channels 310 form a flow divider gap 320, when the cryogenic medium passes through the position with the maximum curvature of the curved channel segment 313, the curvature of the cryogenic medium at the flow divider gap 320 is also the maximum. It can be understood that at this point, the cryogenic medium experiences the greatest resistance from the sidewall of the curved channel segment 313. By providing the connecting hole 314, not only can the cryogenic medium at this location flow between the curved channel segment 313 and the flow divider gap 320, achieving a uniform flow of the cryogenic medium within the curved channel segment 313 region, but the cryogenic medium within the flow divider gap 320 can also act as a sidewall of the curved channel segment 313 under hydraulic pressure, allowing the cryogenic medium within the curved channel segment 313 to pass through the position with the maximum curvature within the curved channel segment 313 with less resistance. Similarly, the cryogenic medium within the curved channel segment 313 can also act as a sidewall of the flow divider gap 320 under hydraulic pressure, allowing the cryogenic medium within the flow divider gap 320 to pass through the position with the maximum curvature within the flow divider gap 320 with less resistance.

[0050] In one embodiment, such as Figure 3 As shown, the cold inlet collector channel 240 and the cold outlet collector channel 260 are diagonally distributed, and the hot inlet collector channel 210 and the hot outlet collector channel 230 are also diagonally distributed. The first diversion groove 310 is located between the hot inlet collector channel 210 and the hot outlet collector channel 230.

[0051] It is understandable that the low-temperature medium mainly enters the cold-flow-collecting channel 260 from the cold-flow-collecting channel 240 through the area between the hot-flow-collecting channel 210 and the hot-flow-collecting channel 230. Therefore, placing the first flow channel 310 between the hot-flow-collecting channel 210 and the hot-flow-collecting channel 230 can ensure that the flow rate of most of the low-temperature medium in the cold flow channel layer remains consistent.

[0052] Furthermore, in one embodiment, as Figure 3 As shown, the diversion plate 300 is also provided with a plurality of second diversion grooves 340. A portion of the second diversion grooves 340 are located on the side of the heat inlet collection channel 210 away from the heat outlet collection channel 230, and another portion of the second diversion grooves 340 are located on the side of the heat outlet collection channel 230 away from the heat inlet collection channel 210.

[0053] In this way, the low-temperature medium can smoothly pass through the side of the inlet heat collector channel 210 away from the outlet heat collector channel 230 and the side of the outlet heat collector channel 230 away from the inlet heat collector channel 210, thereby further effectively reducing the flow resistance of the low-temperature medium in the cold flow channel layer, and thus reducing the pressure drop of the low-temperature medium in the cold flow channel layer.

[0054] Furthermore, in one embodiment, as Figure 3 As shown, the flow guide plate 300 is also provided with a flow guide protrusion 330, which is located in the area between the first flow guide groove 310 and the second flow guide groove 340, so as to divide the area of ​​the cold flow channel layer between the first flow guide groove 310 and the second flow guide groove 340 into a plurality of flow guide channels 331. Furthermore, the flow area of ​​the flow guide channel 331, the flow area of ​​the first flow guide groove 310, and the flow area of ​​the second flow guide groove 340 are all equal.

[0055] This further reduces the flow resistance of the low-temperature medium in the cold flow channel layer, thereby reducing the pressure drop of the low-temperature medium in the cold flow channel layer.

[0056] In one embodiment, such as Figure 3 As shown, the heat exchanger includes multiple partition plates 400, with adjacent partition plates 400 forming a cold flow channel layer and a hot flow channel layer, respectively, and the flow guide plate 300 is fixedly connected to the adjacent partition plate 400.

[0057] This helps to improve the connection strength of the drainage plate 300.

[0058] This application also provides a thermal management system, which includes the heat exchanger described in any of the above embodiments.

[0059] 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.

[0060] 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 (210), a multi-layer heat flow channel layer and a heat outlet collection channel (230) connected in sequence. The heat exchanger is also provided with a cold inlet collection channel (240), a multi-layer cold flow channel layer and a cold outlet collection channel (260) connected in sequence. The heat flow channel layer and the cold flow channel layer are stacked alternately. The heat exchanger includes a flow guide plate (300), which is disposed in the cold flow channel layer. The flow guide plate (300) is provided with a plurality of first flow guide grooves (310) that can connect the cold inlet collection channel (240) and the cold outlet collection channel (260). Adjacent first flow guide grooves (310) are spaced apart to form a plurality of flow split gaps (320), so that the low temperature medium in the cold flow channel layer can flow from the cold inlet collection channel (240) into the cold outlet collection channel (260) along the first flow guide grooves (310) and the flow split gaps (320), respectively. Furthermore, the first drainage channel (310) includes a straight channel segment (311) and a curved channel segment (313). The first drainage channel (310) is formed by either the straight channel segment (311) or the curved channel segment (313) alone, or by alternating arrangements of the straight channel segment (311) and the curved channel segment (313). The sidewall of the curved channel segment (313) is a smoothly extending curve, and the centerline of the straight channel segment (311) is a straight line. Each straight channel segment (311) includes a plurality of staggered channels (312) that are sequentially connected along its own centerline. Adjacent staggered channels (312) are staggered along a direction perpendicular to the centerline of the straight channel segment (311) so that each staggered channel (312) can connect to the adjacent staggered channel (312) and the diversion gap (320) located on one side of the straight channel segment (311). The inlet cooling collector channel (240) and the outlet cooling collector channel (260) are diagonally distributed, and the inlet heating collector channel (210) and the outlet heating collector channel (230) are also diagonally distributed. The first diversion groove (310) is located between the inlet heating collector channel (210) and the outlet heating collector channel (230). The diversion plate (300) is also provided with a plurality of second diversion grooves (340), a portion of which are located on the side of the heat inlet collection channel (210) away from the heat outlet collection channel (230), and another portion of which are located on the side of the heat outlet collection channel (230) away from the heat inlet collection channel (210). The drainage plate (300) is also provided with a drainage protrusion (330), which is located in the area between the first drainage groove (310) and the second drainage groove (340) to divide the area of ​​the cold flow channel layer between the first drainage groove (310) and the second drainage groove (340) into a plurality of drainage channels (331). The flow area of ​​the drainage channel (331), the flow area of ​​the first drainage groove (310) and the flow area of ​​the second drainage groove (340) are all equal.

2. The heat exchanger according to claim 1, characterized in that, The sidewall of the curved groove section (313) is provided with a connecting hole (314) that connects to the flow divider gap (320) at the position where its curvature is the greatest.

3. The heat exchanger according to claim 1, characterized in that, The misaligned channel (312) is continuous along the center line of the straight groove segment (311).

4. The heat exchanger according to claim 1, characterized in that, The diversion plate (300) is a stamped part.

5. The heat exchanger according to claim 1, characterized in that, The diversion plate (300) is a welded component.

6. The heat exchanger according to claim 1, characterized in that, The diversion plate (300) is a 3D printed part.

7. The heat exchanger according to claim 1, characterized in that, The flow area at the inlet of any of the first flow channels (310) near the end of the cold inlet collection channel (240) is equal to the flow area at the inlet of any of the flow dividers (320) near the end of the cold inlet collection channel (240).

8. The heat exchanger according to claim 7, characterized in that, The flow area at the inlet of any of the first diversion channels (310) near the end of the cold outlet collection channel (260) is equal to the flow area at the inlet of any of the diversion gaps (320) near the end of the cold outlet collection channel (260).

9. The heat exchanger according to claim 1, characterized in that, It also includes a plurality of partition plates (400), adjacent partition plates (400) respectively enclosing to form the cold flow channel layer and the hot flow channel layer, and the flow guide plate (300) is fixedly connected to the adjacent partition plate (400).

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

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