Thermal management assembly

Abstract

This application discloses a thermal management component, comprising a heat exchanger, a flow channel, and a damper. The heat exchanger is fixedly connected to the flow channel and has an inlet. The flow channel includes a first sub-flow channel with a first sub-flow channel. At least a portion of the damper is located at the inlet or the first sub-flow channel and is connected to either the inlet or the flow channel. The damper includes a first through-hole with a first through-hole. The inlet communicates with the first through-hole, and the first through-hole communicates with the first sub-flow channel. The hydraulic diameter of the first through-hole is smaller than that of the first sub-flow channel. Because the hydraulic diameter of the first through-hole is smaller than that of the first sub-flow channel, the damper generates greater resistance in the hydraulic diameter variation section, thereby reducing the pressure entering the heat exchanger and improving the pressure control accuracy of the thermal management component.

Description

Technical Field

[0001] This application relates to the field of thermal management technology, and more particularly to a thermal management component for energy storage. Background Technology

[0002] In related technologies, thermal management components include heat exchangers, flow channels, and throttling valves. The throttling valve is installed at the inlet of the heat exchanger to regulate the pressure entering the regenerator. The throttling valve needs to collect and calculate signals before it can act, resulting in a time delay when regulating the pressure. It cannot adjust the pressure instantaneously, which makes the pressure control accuracy of the thermal management components poor. Summary of the Invention

[0003] The purpose of this application is to provide a thermal management component that improves the accuracy of pressure control.

[0004] To achieve the above objectives, this application adopts the following technical solution:

[0005] A thermal management component is provided, comprising: a heat exchanger, a flow channel, and a damper, wherein the heat exchanger is fixedly connected to the flow channel, the heat exchanger has an inlet, the inlet has an inlet, the flow channel includes a first sub-flow channel, the first sub-flow channel has a first sub-flow channel; at least a portion of the damper is located at the inlet or the first sub-flow channel, at least a portion of the damper is connected to the inlet or the flow channel, the damper includes a first through-hole, the first through-hole has a first through-hole, the inlet communicates with the first through-hole, the first through-hole communicates with the first sub-flow channel, and the hydraulic diameter of the first through-hole is smaller than the hydraulic diameter of the first sub-flow channel.

[0006] In this application, the hydraulic diameter of the first through hole is smaller than that of the first sub-channel, causing the damper to generate greater resistance in the hydraulic diameter change section, thereby reducing the pressure entering the heat exchanger and improving the pressure control accuracy of the thermal management component. Attached Figure Description

[0007] Figure 1 A schematic diagram of a structural embodiment of the thermal management component of this application;

[0008] Figure 2 yes Figure 1 The diagram shows a structural schematic of the thermal management component from one perspective.

[0009] Figure 3 yes Figure 1 This is a schematic diagram of the thermal management component from another perspective;

[0010] Figure 4 This is a cross-sectional schematic diagram of an embodiment of the thermal management component of this application;

[0011] Figure 5 yes Figure 4 An enlarged schematic diagram of the thermal management component at point Q is shown;

[0012] Figure 6 yes Figure 1 A schematic diagram of the damper structure of the thermal management component is shown;

[0013] Figure 7 This is a cross-sectional schematic diagram of another embodiment of the thermal management component of this application;

[0014] Figure 8 yes Figure 7 An enlarged schematic diagram of the thermal management component at point R;

[0015] Figure 9 yes Figure 1 or Figure 7 A block diagram of the thermal management system shown. Detailed Implementation

[0016] It should be understood that the terms "first," "second," and similar terms used in this application specification and claims do not indicate any order, quantity, or importance, but are merely used to distinguish different components. Similarly, "a" or "one," and similar terms do not indicate a quantity limitation, but rather indicate the presence of at least one; "multiple" indicates two or more. Unless otherwise stated, terms such as "front," "rear," "lower," and / or "upper" are for illustrative purposes only and are not limited to a location or spatial orientation. Terms such as "comprising" or "including" indicate that the elements or objects preceding "comprising" or "including" encompass the elements or objects listed following "comprising" or "including" and their equivalents, but do not exclude other elements or objects.

[0017] like Figure 1As shown, this embodiment proposes a thermal management component, which includes a heat exchanger 100, a flow channel section 200, and a damper 300. The heat exchanger 100 is fixedly connected to the flow channel section 200. The heat exchanger 100 has an inlet section 110 with an inlet 111. The flow channel section 200 includes a first sub-flow channel section 210 with a first sub-flow channel 211. This embodiment's thermal management component achieves a compact structural design by fixedly connecting the heat exchanger 100 to the flow channel section 200, reducing piping connections, effectively lowering the overall equipment size, saving space, and reducing the risk of leakage. The connection between the inlet 111 and the first sub-flow channel 211 creates an integrated flow field, significantly improving heat exchange efficiency and reducing flow resistance. The modular connection between the heat exchanger 100 and the flow channel section 200 simplifies the assembly process and reduces manufacturing and maintenance costs. The synergistic effect between the components enables the thermal management assembly to adapt to complex operating conditions such as high frequency and large temperature differences, exhibiting excellent performance in energy recovery and temperature control. Heat exchanger 100 can be a regenerator.

[0018] At least a portion of the damper 300 is located at the inlet 111 or the first sub-channel 211, and is connected to the inlet portion 110 or the channel portion 200. The damper 300 includes a first through-hole portion 310 with a first through-hole 311. The inlet 111 communicates with the first through-hole 311, and the first through-hole 311 communicates with the first sub-channel 211. The hydraulic diameter of the first through-hole portion 310 is smaller than that of the first sub-channel portion 210. This connection method ensures a reliable connection between the damper 300 and the inlet portion 110 or the channel portion 200, facilitating disassembly and maintenance while maintaining structural stability. The first through-hole portion 310 and the first sub-channel portion 210 employ a design with differentiated hydraulic diameters, creating a gradient throttling effect as the fluid flows through them, effectively reducing the impact of fluid pulsation on the thermal management components. This structure allows for flexible switching of the hydraulic diameter ratio between the first through-hole section 310 and the first sub-flow channel section 210 according to operating conditions, enabling proactive adaptation to different flow velocities and pressures, and significantly improving flow regulation accuracy. In this application, by making the hydraulic diameter of the first through-hole section 310 smaller than that of the first sub-flow channel section 210, the damper 300 generates greater resistance in the hydraulic diameter variation section, thereby reducing the pressure entering the heat exchanger 100 and improving the pressure control accuracy of the thermal management components.

[0019] The damper 300 also includes a second through-hole section 320, which has a second through-hole 321. The first through-hole 311 communicates with the second through-hole 321. The hydraulic diameter of the first through-hole section 310 is smaller or larger than the hydraulic diameter of the second through-hole section 320. This arrangement of the first through-hole 311 and the second through-hole 321 forms a multi-stage buffering mechanism, enhancing the absorption capacity of pressure fluctuations while maintaining fluid flow, enabling the thermal management component to maintain efficient and stable energy transfer characteristics under varying operating conditions. The first through-hole section 310 and the second through-hole section 320 employ a design with differentiated hydraulic diameters, creating a gradient throttling effect as the fluid flows through them, effectively reducing the impact of fluid pulsation on the thermal management component. This structure allows for flexible switching of the hydraulic diameter ratio of the first through-hole section 310 and the second through-hole section 320 according to operating conditions, enabling proactive adaptation to different flow velocities and pressures, and significantly improving flow regulation accuracy.

[0020] In some embodiments, the hydraulic diameter of the first through-hole 310 is smaller than that of the second through-hole 320. The first through-hole 311 is a circular through-hole, and the second through-hole 321 is an internal hexagonal through-hole, which can serve as an internal hexagonal wrench mounting groove. This embodiment forms a two-stage fluid control structure through the combination of differentiated hydraulic diameters and irregularly shaped through-holes. The circular first through-hole 311 first implements precise throttling of the fluid, and then the internal hexagonal second through-hole 321 uses its edge structure to generate controllable vortices, reducing the flow velocity while enhancing the turbulent mixing effect. This structure causes a gradual pressure gradient change in the fluid during expansion, effectively suppressing cavitation and improving energy conversion efficiency. The unique corner flow separation characteristics of the internal hexagonal through-hole complement the symmetrical flow of the circular through-hole, ensuring stable transport of the main body while enhancing local heat transfer through corner vortices. This composite through-hole structure achieves active control of flow field distribution and pressure pulsation while maintaining low pressure loss of the thermal management component, significantly improving the adaptability of the thermal management component to dynamic operating conditions.

[0021] In some embodiments, the hydraulic diameter of the first through-hole 310 is larger than that of the second through-hole 320, and the connection surface 350 between the first through-hole 310 and the second through-hole 320 is an inclined surface. This embodiment achieves an adaptive fluid rectification structure through the synergistic design of a reverse hydraulic diameter gradient and an inclined surface transition. When fluid flows from the large-diameter first through-hole 310 along the inclined surface to the small-diameter second through-hole 320, the inclined surface generates a gradual contraction effect, achieving a smooth increase in flow velocity while avoiding boundary layer separation caused by abrupt channel contraction. This inclined transition interface guides the fluid to form wall-attached flow, significantly reducing the eddy generation region and enabling pressure energy to be converted into kinetic energy more efficiently. The combination of the reverse diameter gradient and the inclined surface angle establishes a reverse pressure gradient field within the damper 300, effectively suppressing the initiation and collapse of cavitation bubbles. The sloping connecting surface 350 also functions as a rectifier grid, achieving multi-stage dissipation of fluid pulsation energy while maintaining overall low pressure loss characteristics, thus enhancing the thermal management component's resistance to disturbances under variable flow conditions. This composite transition structure enables the thermal management component to possess both high flow efficiency and excellent cavitation protection characteristics.

[0022] In some embodiments, such as Figure 5 and Figure 6 As shown, the damper 300 includes an external threaded portion 330, and the flow channel portion 200 includes an insert 220 connected to the first sub-flow channel portion 210. The insert 220 includes a third through-hole portion 221, which has a third through-hole 2211. At least a portion of the damper 300 is located in the third through-hole 2211. The third through-hole portion 221 includes an internal threaded portion 2212, which is threadedly connected to the external threaded portion 330. This embodiment achieves a precise fit between the damper 300 and the flow channel portion 200 through a threaded connection. The meshing structure of the external threaded portion 330 and the internal threaded portion 2212 forms a self-aligning connection mechanism, ensuring assembly coaxiality while providing reliable radial constraint force. The integral molding design of the insert 220 and the first sub-flow channel portion 210 enhances the structural integrity of the flow channel portion 200, avoids the cumulative errors caused by split assembly, and effectively improves the sealing performance of the thermal management component. The adjustable screw depth of the threaded pair allows for fine-tuning of the axial position of the damper 300, meeting the assembly requirements of dampers with different strengths. The third through-hole 221 serves as both a connection carrier and an auxiliary flow channel, forming a double-layer sealed interface with the damper 300, maintaining a stable connection even under high-pressure conditions. This structure, through a composite design of mechanical interlocking and fluid channels, significantly improves the vibration fatigue resistance of the thermal management components while ensuring quick disassembly and maintenance.

[0023] In some embodiments, such as Figure 8As shown, the damper 300 includes a first boss 340, and the heat exchanger 100 includes a second boss 120, with the first boss 340 and the second boss 120 engaging. This embodiment achieves tool-free rapid assembly of the damper 300 and the heat exchanger 100 through the interlocking engagement structure of the first boss 340 and the second boss 120. The three-dimensional constraint mechanism formed by the engagement of the first boss 340 and the second boss 120 provides simultaneous limiting in the left-right, front-back, and up-down directions, preventing axial movement and eliminating the risk of radial displacement. The elastic deformation space generated at the engagement interface of the first boss 340 and the second boss 120 can absorb high-frequency vibration energy during equipment operation, reducing the probability of fatigue damage at the connection points. This design replaces traditional welding or threaded connections with mechanical interlocking, ensuring structural strength while avoiding material performance degradation caused by heat input. The self-sealing characteristics of the engagement surfaces of the first boss 340 and the second boss 120 conformally match the heat exchanger flow channel, effectively improving the boundary layer integrity of the fluid channel. This structure is suitable for thermal cycling conditions, allowing for adaptive compensation of minute deformations between components caused by temperature differences, thereby enhancing the long-term operational reliability of thermal management components.

[0024] In some embodiments, the hydraulic diameter of the smaller of the first through-hole portion 310 and the second through-hole portion 320 is between 0.1 mm and 5 mm, for example, 0.1 mm, 0.5 mm, 1 mm, 1.5 mm, 2 mm, 2.5 mm, 3 mm, 3.5 mm, 4 mm, 4.5 mm, and 5 mm. This range of hydraulic diameters allows either the first through-hole portion 310 or the second through-hole portion 320 to function as a flow guide, thus guiding the flow. This embodiment constructs multi-stage fluid control capabilities by defining a range of through-hole sizes with a minimum hydraulic diameter. The micron- to millimeter-scale aperture span allows the damper 300 to implement precise microflow control while also handling high-fluidity media transport. This size threshold ensures fluid flow within the critical Reynolds number range, balancing laminar stability and turbulent mixing efficiency. The specific aperture range effectively balances the effects of surface tension and inertial forces, suppressing cavitation exacerbation caused by microbubble aggregation and preventing channel blockage caused by particulate matter retention. The lower limit of the dimensions ensures the feasibility of precision casting or machining, while the upper limit maintains the mechanical reliability of the thin-walled structure. This precise matching of the through-hole dimensions enables the damper 300 to adapt to a wide range of operating conditions, achieving active shaping of the fluid energy spectrum while maintaining low pressure loss characteristics.

[0025] In some embodiments, the flow channel 200 includes a first flow channel plate 230 and a second flow channel plate 240. The first flow channel plate 230 is made of plastic, and the second flow channel plate 240 is also made of plastic. The first flow channel plate 230 and the second flow channel plate 240 are welded together. This embodiment forms a fluid channel with intrinsic sealing characteristics through the welding integration of homogeneous plastic flow channel plates. The thermoplastic compatibility of the plastic material enables molecular-level fusion at the welding interface, reducing the risk of leakage caused by the aging of traditional sealing rings. The symmetrical structure of the first flow channel plate 230 and the second flow channel plate 240 undergoes coordinated deformation when heated, effectively compensating for internal stress caused by differences in thermal expansion of the materials. The continuous fusion line formed by the welding process replaces mechanical fastening points, keeping the inner wall of the flow channel smooth and avoiding turbulent losses caused by raised step surfaces. This design fully utilizes the corrosion resistance of engineering plastics and is suitable for handling chemically corrosive fluids. The homogeneous material welded joint also has vibration damping characteristics, which can absorb the pressure pulsation energy during the operation of the thermal management components and improve the fatigue resistance of the thermal management components. This one-piece flow channel structure achieves an optimized balance between lightweight and reliability, making it suitable for compact thermal management components with complex spatial layouts.

[0026] In some embodiments, the first flow channel plate 230 is made of a mixture of polypropylene and glass fiber, and the second flow channel plate 240 is made of a mixture of polypropylene and glass fiber. This embodiment constructs a reinforced flow channel structure with isotropic characteristics through the symmetrical application of composite materials with the same formulation. The polypropylene matrix provides an intrinsic corrosion-resistant barrier, while the network reinforcement phase of glass fiber forms a three-dimensional stress-transfer skeleton, simultaneously improving the creep resistance and dimensional stability of both the first and second flow channel plates 230 and 240. The consistent thermal expansion of the homogeneous composite material eliminates the tendency for interfacial microcracks during welding of dissimilar materials, ensuring the reliability of the medium barrier in the fusion line region. The controlled orientation distribution of glass fiber allows for gradient modulus design in the flow channel wall thickness direction, enhancing the structural rigidity of the pressure-bearing side while maintaining the smoothness of the fluid contact surface. This material system enables the thermal management component to combine the molding advantages of plastics with the mechanical properties of metals, making it suitable for alternating thermal load conditions. The micro-damping structure formed at the glass fiber-polypropylene matrix interface can also effectively attenuate broadband vibrations caused by fluid pulsation, improving the operational stability of the thermal management component in resonant sensitive regions.

[0027] In some embodiments, such as Figure 7As shown, the thermal management assembly also includes a heater 410, a first filter 420, a second filter 430, and a first evaporator 440. The heater 410, first filter 420, second filter 430, and first evaporator 440 are connected to the flow channel section 200. The heater 410, first filter 420, and heat exchanger 100 are fixed to the first surface 251 of the flow channel section 200, and the second filter 430 and first evaporator 440 are fixed to the second surface 252 of the flow channel section 200. This embodiment achieves compact integration of a multi-functional thermal management system through a double-sided layout. The double-sided arrangement strategy forms thermal circulation units on both sides of the flow channel section 200, constructing a bidirectional energy exchange channel. The layered positioning of the heater 410 and the second filter 430 decouples the temperature control and media purification processes, avoiding interference from heat load on filtration accuracy. The surface fixing method forms a mechanical-thermal composite isolation interface, ensuring the vibration stability of the assembly while reducing thermal bridging effects. The first filter 420 and the second filter 430 are configured upstream and downstream to form a multi-level protection, implementing differentiated interception for different pollution forms during the phase change process. The cross-surface layout of the first evaporator 440 and the heat exchanger 100 enables the synergistic recovery of sensible and latent heat, improving the system's energy efficiency density. This thermal management component achieves topology optimization of functional elements through the flow channel section 200 carrier, integrating the entire process of heating, purification, and phase change within a limited space, making it particularly suitable for mobile thermal management components that switch between multiple operating conditions.

[0028] In some embodiments, such as Figure 4 As shown, the thermal management component also includes a second evaporator 450 and a pipe 460. The first evaporator 440 and the second evaporator 450 are arranged side by side and connected by the pipe 460. In this embodiment, an adaptive phase change system is formed through the topological interconnection of the first evaporator 440 and the second evaporator 450, constructing a multi-modal heat exchange capability. The side-by-side layout achieves spatial coupling between the first evaporator 440 and the second evaporator 450, maintaining independent operational freedom while enabling synergistic efficiency. The pipe 460, which connects to the first evaporator 440 and the second evaporator 450, forms a dynamic medium balance channel, automatically eliminating uneven evaporation caused by refrigerant flow deviation through the siphon effect. The dual evaporation interface formed by the first evaporator 440 and the second evaporator 450 can flexibly switch operating modes according to load requirements. Under low load, staged evaporation increases subcooling, while under high load, parallel operation expands the heat exchange area. The U-shaped siphon structure formed by pipe 460 also utilizes gravity to achieve self-draining, preventing refrigerant migration caused by liquid refrigerant retention during shutdown. This design maintains a compact layout while doubling the functionality of the first evaporator 440 and the second evaporator 450, making it particularly suitable for energy storage temperature control scenarios with intermittent load characteristics. The combination of redundant evaporation units and a self-balancing mechanism significantly improves the system's robustness to complex operating conditions.

[0029] In some embodiments, such as Figures 1 to 3 As shown, the interfaces are distributed on both sides of the flow channel section 200. The first evaporator 440 has a reagent-side inlet 501, and the second evaporator 450 has a reagent-side outlet 502. The first pump inlet 503, battery return port 504, second water inlet 505, DC liquid supply port 506, gun liquid supply port 507, first water inlet 508, DC return port 509, first dry cooling inlet 510, second dry cooling inlet 511, gun return port 512, first vent 513, and second vent 514 are arranged on the first surface 251 of the flow channel section 200. The second pump inlet 515, second pump outlet 516, first dry cooling outlet 517, and second dry cooling outlet 518 are arranged on the second surface 252 of the flow channel section 200. The first water inlet 508 and second water inlet 505 are arranged at the bottom of the flow channel section 200, and the first vent 513 and second vent 514 are arranged at the top of the flow channel section 200.

[0030] In natural cooling mode, the coolant needs to cool both the charging gun 604 and the DC-to-DC converter 605 (DCDC). Considering that natural cooling of the charging gun 604 alone through the dry cooler 601 is ineffective, heat exchange is achieved through the heat exchanger 100 and the battery circuit to achieve a cooling effect. The charging gun 604 has a narrow pipe, for example, a rated flow rate of 1 Lpm, while the rated flow rate of the DC-to-DC converter 605 circuit is 30 Lpm. The coolant needs to be divided into two branches after passing through the second water pump 603. Considering the large difference in flow rate between the branches, a damper 300 is installed on the flow channel plate to distribute the flow between the two branches. The damper 300 is located directly below the heat exchanger 100. By installing the damper 300 at the bottom of the heat exchanger 100, the flow rate entering the heat exchanger is controlled, achieving flow diversion, reducing pressure loss in the gun line circuit, and lowering the power consumption of the water pump. The filling valve 609 replenishes the coolant, and the expansion tank 610 is used for pressure regulation.

[0031] like Figure 9 The system diagram shown shows that the water-side integrated assembly integrates two evaporator side heat exchangers, two filters, and one electric heater through a water-side flow channel plate. The dashed boxes in the diagram represent external, non-integrated components.

[0032] The water-side integrated assembly forms two coolant circulation loops via a water-side flow channel plate and external hoses: one for the battery and AC / DC switching power supply 607 (ACDC), and the other for the charging gun 604 and DC-DC converter 605. The two loops exchange heat through a heat exchanger 100. In the figure, arrows indicate the direction of coolant flow.

[0033] In compressor cooling mode, the battery and AC / DC power supply 607 circuit works as follows: coolant exits from the first evaporator 440 and the second evaporator 450, then enters the battery and AC / DC power supply 607 via the first water pump 606 to dissipate heat from the battery and AC / DC power supply 607. After exiting the battery and AC / DC power supply 607, coolant enters the heat exchanger 100, then the heater 410 (the heater 410 is not in operation), exits the heater 410, enters the first filter 420, and then exits the first filter 420 and returns to the first evaporator 440 and the second evaporator 450, forming a complete cycle.

[0034] In natural cooling mode, the circuit of charging gun 604 and DC-DC converter 605 is as follows: coolant flows out from dry cooler 601, enters second filter 430, and then passes through first exhaust valve 602 and second water pump 603. It then splits into two paths: one path enters heat exchanger 100 for heat dissipation and further cooling before entering charging gun 604 to absorb the heat emitted by charging gun 604 and cool it down; the other path enters DC-DC converter 605 to cool it down. The two coolant paths merge after exiting charging gun 604 and DC-DC converter 605 and then enter dry cooler 601. The fan cools dry cooler 601 and removes the heat absorbed by the coolant, forming a complete cycle.

[0035] In heating mode, the battery and AC / DC switching power supply 607 circuit: At this time, the refrigerant side circuit does not work. After the coolant comes out of the heater 410, it enters the battery and AC / DC switching power supply 607 through the first filter 420, the second exhaust valve 608, the first evaporator 440, the second evaporator 450 and the first water pump 606, heating the battery and AC / DC 607 switching power supply. Then it returns to the heater 410 through the heat exchanger 100, forming a complete cycle.

[0036] In this application, the "connection" between two components can be a direct connection or a connection via a pipeline. The two components may only have a pipeline between them, or they may have a valve or other component in addition to a pipeline. Similarly, the "connection" between two components in this application can be a direct connection or a connection via a pipeline. The two components may only have a pipeline connection, or they may have a valve or other component in addition to a pipeline connection.

[0037] The above examples illustrate the principles and implementation methods of the present invention. These embodiments are merely illustrative and intended to aid in understanding the method and core concepts of the present invention. It should be noted that those skilled in the art can make various improvements and modifications to the present invention without departing from its principles, and these improvements and modifications also fall within the scope of protection of the present invention.

Claims

1. A thermal management assembly, characterized by, include: The heat exchanger (100), the flow channel section (200), and the damper (300) are fixedly connected. The heat exchanger (100) has an inlet section (110) and an inlet (111). The flow channel section (200) includes a first sub-flow channel section (210) and the first sub-flow channel section (210) has a first sub-flow channel (211). At least a portion of the damper (300) is located at the inlet (111) or the first sub-channel (211), and at least a portion of the damper (300) is connected to the inlet portion (110) or the channel portion (200). The damper (300) includes a first through-hole portion (310) having a first through-hole (311). The inlet (111) communicates with the first through-hole (311), and the first through-hole (311) communicates with the first sub-channel (211). The hydraulic diameter of the first through-hole portion (310) is smaller than the hydraulic diameter of the first sub-channel portion (210).

2. The thermal management assembly of claim 1, wherein, The damper (300) further includes a second through hole (320), the second through hole (320) having a second through hole (321), the first through hole (311) communicating with the second through hole (321), and the hydraulic diameter of the first through hole (310) being smaller or larger than the hydraulic diameter of the second through hole (320).

3. The thermal management component as described in claim 2, characterized in that, The hydraulic diameter of the first through hole (310) is smaller than that of the second through hole (320). The first through hole (311) is a circular through hole, and the second through hole (321) is an inner hexagonal through hole.

4. The thermal management component as described in claim 2, characterized in that, The hydraulic diameter of the first through hole (310) is greater than that of the second through hole (320), and the connecting surface (350) between the first through hole (310) and the second through hole (320) is an inclined surface.

5. The thermal management component as claimed in claim 1, characterized in that, The damper (300) includes an external thread portion (330), the flow channel portion (200) includes an insert (220), the insert (220) is connected to the first sub-flow channel portion (210), the insert (220) includes a third through hole portion (221), the third through hole portion (221) has a third through hole (2211), at least a portion of the damper (300) is located in the third through hole (2211), the third through hole portion (221) includes an internal thread portion (2212), the internal thread portion (2212) is threadedly connected to the external thread portion (330).

6. The thermal management component according to any one of claims 1 to 5, characterized in that, The damper (300) includes a first boss (340), and the heat exchanger (100) includes a second boss (120), the first boss (340) and the second boss (120) being engaged.

7. The thermal management component according to any one of claims 1 to 5, characterized in that, The flow channel section (200) includes a first flow channel plate (230) and a second flow channel plate (240). The first flow channel plate (230) is made of plastic, and the second flow channel plate (240) is made of plastic. The first flow channel plate (230) and the second flow channel plate (240) are welded together.

8. The thermal management component as claimed in claim 7, characterized in that, The first flow channel plate (230) is made of a mixture of polypropylene and glass fiber, and the second flow channel plate (240) is made of a mixture of polypropylene and glass fiber.

9. The thermal management component according to any one of claims 1 to 5, characterized in that, It also includes a heater (410), a first filter (420), a second filter (430), and a first evaporator (440). The heater (410), the first filter (420), the second filter (430), and the first evaporator (440) are in communication with the flow channel (200). The flow channel (200) includes a first surface (251) and a second surface (252). The heater (410), the first filter (420), and the heat exchanger (100) are fixed to the first surface (251), and the second filter (430) and the first evaporator (440) are fixed to the second surface (252).

10. The thermal management component as claimed in claim 9, characterized in that, It also includes a second evaporator (450) and a pipe (460), wherein the first evaporator (440) and the second evaporator (450) are arranged side by side and are connected by the pipe (460).

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