Heat exchanger and automotive thermal management system

Abstract

The utility model relates to heat exchanger technical field especially relates to a heat exchanger and car heat management system. The heat exchanger includes first medium flow channel and second medium flow channel. Among them, the continuous gradual change spiral baffle is provided in the first medium flow channel, and the pitch of continuous gradual change spiral baffle gradually increases along the flow direction of medium in the first medium flow channel, and the first medium flow channel is adapted to the medium of phase change. The continuous fixed spiral baffle is provided in the second medium flow channel, and the pitch of continuous fixed spiral baffle is equal, and the second medium flow channel is adapted to the medium without phase change. The outer peripheral wall of first medium flow channel and the outer peripheral wall of second medium flow channel contact and form the heat exchange surface, so that the medium in the first medium flow channel and the medium in the second medium flow channel exchange heat. The refrigerant side flow channel of the heat exchanger can adapt to the dryness change of refrigerant in the heat absorption phase change process, improve the heat exchange efficiency, and save the energy consumption of car heat management system.

Description

Technical Field

[0001] This utility model relates to the field of heat exchanger technology, and in particular to a heat exchanger and an automotive thermal management system. Background Technology

[0002] As a core device for energy transfer and exchange, the performance of a heat exchanger directly determines the energy efficiency, space utilization, and operational reliability of an automotive thermal management system. However, in existing technologies, the refrigerant-side flow channels of heat exchangers cannot adapt to the characteristics of refrigerant such as dryness changes and volume expansion during the heat absorption phase change process, thus reducing the heat exchanger's heat exchange efficiency and increasing system energy consumption.

[0003] Therefore, there is an urgent need to design a heat exchanger and automotive thermal management system to solve the above technical problems. Utility Model Content

[0004] The purpose of this invention is to propose a heat exchanger and an automotive thermal management system. The refrigerant side flow channel of the heat exchanger can adapt to the dryness change of the refrigerant during the heat absorption phase change process, thereby improving heat exchange efficiency and saving energy consumption of the automotive thermal management system.

[0005] To achieve this objective, the present invention adopts the following technical solution:

[0006] On the one hand, this utility model provides a heat exchanger, comprising:

[0007] A first medium flow channel is provided, in which a continuously tapered spiral baffle is provided, the pitch of which gradually increases along the flow direction of the medium in the first medium flow channel; the first medium flow channel is adapted to a phase-change medium.

[0008] The second medium flow channel is provided with a continuous fixed spiral baffle plate, the spiral baffle plate having an equal pitch, and the second medium flow channel is adapted to media without phase change;

[0009] The outer peripheral wall of the first medium flow channel contacts the outer peripheral wall of the second medium flow channel to form a heat exchange surface, so as to exchange heat between the medium in the first medium flow channel and the medium in the second medium flow channel.

[0010] As an optional technical solution for a heat exchanger, both the first medium flow channel and the second medium flow channel are configured as multiple, with adjacent first medium flow channels and second medium flow channels arranged alternately in a matrix, and at least four second medium flow channels are distributed around each first medium flow channel, and at least four first medium flow channels are distributed around each second medium flow channel.

[0011] As an optional technical solution for heat exchangers, the flow direction of the medium in the first medium flow channel is set to be 180° counter-current to the flow direction of the medium in the second medium flow channel.

[0012] As an optional technical solution for the heat exchanger, an inner fin is also provided in the first medium flow channel. The inner fin has a continuously tapered spiral structure, and the pitch of the inner fin changes synchronously with the pitch of the continuously tapered spiral baffle.

[0013] As an optional technical solution for heat exchangers, the inner fins are arranged at a preset angle to the continuous, gradually changing spiral baffles on the inner wall of the first medium flow channel.

[0014] As an optional technical solution for heat exchangers, the preset angle is set to 30°-90°.

[0015] As an optional technical solution for a heat exchanger, the two ends of the first medium flow channel have a first inlet and a first outlet, and the two ends of the second medium flow channel have a second inlet and a second outlet, respectively. The first inlet and the first outlet are used to connect the two ends of the refrigerant circulation loop, and the second inlet and the second outlet are used to connect the two ends of the water circulation loop.

[0016] As an optional technical solution for a heat exchanger, the pitch of the continuously variable spiral baffle at the first inlet is set to 2mm-20mm, and the pitch of the continuously variable spiral baffle at the first outlet is set to 4mm-40mm, with a pitch gradient step of 0.5mm-10mm per revolution.

[0017] On the other hand, this utility model also provides an automotive thermal management system, which includes a heat exchanger as described in any of the above optional technical solutions, a refrigerant circulation loop for circulating a phase-change medium, and a water circulation loop for circulating a non-phase-change medium; the refrigerant circulation loop is connected to a first medium flow channel of the heat exchanger; and the water circulation loop is connected to a second medium flow channel of the heat exchanger.

[0018] As an optional technical solution for automotive thermal management systems, the refrigerant circulation loop includes a compressor, a receiver, and a throttling component. The exhaust port of the compressor is connected to the first inlet of the first medium flow channel, the first outlet of the first medium flow channel is connected to the inlet of the receiver, and the outlet of the receiver is connected to the suction port of the compressor after passing through the throttling component, forming a closed-loop refrigerant circulation.

[0019] The water circulation loop includes a water pump and a heat dissipation component. The outlet of the water pump is connected to the second inlet of the second medium flow channel, the second outlet of the second medium flow channel is connected to the heat dissipation component, and the outlet of the heat dissipation component is connected to the inlet of the water pump, forming a closed-loop water circulation.

[0020] The beneficial effects of this utility model include at least the following:

[0021] This invention provides a heat exchanger comprising a first medium flow channel and a second medium flow channel. The first medium flow channel contains continuously varying spiral baffles with a pitch that gradually increases along the flow direction of the medium within the channel; the first medium flow channel is suitable for media undergoing phase change. The second medium flow channel contains continuously fixed spiral baffles with equal pitch; the second medium flow channel is suitable for media without phase change. The outer peripheral walls of the first and second medium flow channels contact each other to form a heat exchange surface, enabling heat exchange between the media in the first and second medium flow channels.

[0022] In the first medium flow channel, the phase-change medium (such as refrigerant) transforms from a liquid to a gaseous state during flow, gradually expanding in volume and increasing in dryness. The pitch of the continuously tapered spiral baffles increases with the flow direction, dynamically adapting to the medium's volume expansion requirements. This avoids sudden increases in local velocity or eddies caused by insufficient space in the first medium flow channel, thereby reducing flow resistance and system drive energy consumption. Simultaneously, the spiral structure forces the medium to flow spirally along the first medium flow channel, increasing the contact time and disturbance intensity between the medium and the inner wall of the first medium flow channel, enhancing heat transfer. In the second medium flow channel, the flow state of the non-phase-change medium (such as coolant) is stable. The equal pitch of the continuously fixed spiral baffles ensures sufficient disturbance of the medium while maintaining stable flow resistance, avoiding energy consumption fluctuations caused by structural changes, and thus saving energy in the automotive thermal management system.

[0023] This utility model also provides an automotive thermal management system, which has high heat exchange performance, can realize rapid heat exchange between refrigerant and coolant, improve heat exchange efficiency, and save energy consumption of the automotive thermal management system. Attached Figure Description

[0024] To more clearly illustrate the technical solutions in the embodiments of this utility model, the drawings used in the description of the embodiments of this utility model will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on the content of the embodiments of this utility model and these drawings without creative effort.

[0025] Figure 1This is a schematic diagram of the heat exchanger provided in an embodiment of the present invention;

[0026] Figure 2 This is a side view of the heat exchanger provided in an embodiment of the present invention;

[0027] Figure 3 This is a flow field simulation diagram of the first medium flow channel provided in this embodiment of the utility model.

[0028] Figure Labels

[0029] 10. First medium flow channel; 11. Continuously tapered spiral baffle; 12. Inner fins;

[0030] 20. Second medium flow channel; 21. Continuously fixed spiral baffle;

[0031] 30. First import; 40. First export; 50. Second import; 60. Second export. Detailed Implementation

[0032] To make the objectives, technical solutions, and advantages of the embodiments of this utility model clearer, the technical solutions of the embodiments of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, and not all embodiments. The components of the embodiments of this utility model described and shown in the accompanying drawings can generally be arranged and designed in various different configurations.

[0033] Therefore, the following detailed description of the embodiments of the present invention provided in the accompanying drawings is not intended to limit the scope of the claimed invention, but merely to illustrate selected embodiments of the invention. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without inventive effort are within the scope of protection of the present invention.

[0034] It should be noted that similar labels and letters in the following figures indicate similar items. Therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures.

[0035] In the description of this utility model, it should be noted that the terms "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, or the orientation or positional relationship commonly used when the product of this utility model is in use. They are used only for the convenience of describing this utility model and for 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. Therefore, they should not be construed as limitations on this utility model. Furthermore, the terms "first," "second," and "third," etc., are used only to distinguish descriptions and should not be construed as indicating or implying relative importance. In the description of this utility model, unless otherwise stated, "a plurality of" means two or more.

[0036] In the description of this utility model, it should also be noted that, unless otherwise explicitly specified and limited, the terms "set" and "connection" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0037] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0038] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this utility model, and should not be construed as limiting this utility model.

[0039] The technical solution of this utility model will be further described below with reference to the accompanying drawings and specific embodiments.

[0040] This embodiment provides a heat exchanger whose refrigerant-side flow channel can adapt to the dryness change of the refrigerant during the heat absorption phase change process, thereby improving heat exchange efficiency and saving energy consumption of the vehicle's thermal management system.

[0041] like Figures 1-2As shown, the heat exchanger mainly includes a first medium flow channel 10 and a second medium flow channel 20. The first medium flow channel 10 is equipped with continuously tapered spiral baffles 11, the pitch of which gradually increases along the flow direction of the medium within the first medium flow channel 10; the first medium flow channel 10 is suitable for media undergoing phase change. The second medium flow channel 20 is equipped with continuously fixed spiral baffles 21, the pitch of which is equal; the second medium flow channel 20 is suitable for media without phase change. The outer peripheral wall of the first medium flow channel 10 contacts the outer peripheral wall of the second medium flow channel 20, forming a heat exchange surface to facilitate heat exchange between the medium in the first medium flow channel 10 and the medium in the second medium flow channel 20.

[0042] Based on the above design, in this embodiment, in the first medium flow channel 10, the phase-change medium (such as refrigerant) transforms from liquid to gas during flow, gradually expanding in volume and increasing in dryness. The pitch of the continuously tapered spiral baffle 11 increases with the flow direction, dynamically adapting to the medium's volume expansion requirements. This avoids sudden increases in local flow velocity or eddies caused by insufficient space in the first medium flow channel 10, thereby reducing flow resistance and system drive energy consumption. Simultaneously, the spiral structure forces the medium to flow spirally along the first medium flow channel 10, increasing the contact time and disturbance intensity between the medium and the inner wall of the first medium flow channel 10, enhancing heat transfer. In the second medium flow channel 20, the flow state of the non-phase-change medium (such as coolant) is stable. The pitch of the continuously fixed spiral baffle 21 is equal, ensuring sufficient disturbance of the medium while maintaining stable flow resistance, avoiding energy consumption fluctuations caused by structural changes, and thus saving energy consumption in the automotive thermal management system.

[0043] Optionally, in this embodiment, the phase change medium can be set as R134a refrigerant, and the non-phase change medium can be set as a 50% ethylene glycol aqueous solution.

[0044] like Figures 1-2 As shown, in this embodiment, the first medium flow channel 10 and the second medium flow channel 20 are both configured as multiple adjacent first medium flow channels 10 and second medium flow channels 20 arranged alternately in a matrix, and at least four second medium flow channels 20 are distributed around any one first medium flow channel 10, and at least four first medium flow channels 10 are distributed around any one second medium flow channel 20.

[0045] The matrix-style alternating arrangement allows the outer peripheral wall of each first medium flow channel 10 to contact multiple adjacent second medium flow channels 20, which greatly increases the overall heat exchange area, reduces local overheating or undercooling caused by concentrated flow, and improves the overall heat exchange stability of the heat exchanger.

[0046] For example, the matrix alternating arrangement of the first medium flow channel 10 and the second medium flow channel 20 is specifically a 5×5 arrangement (a total of 25 channels), wherein the first medium flow channel 10 and the second medium flow channel 20 are distributed according to the rule of alternating rows and columns.

[0047] In this embodiment, the flow direction of the medium in the first medium flow channel 10 is 180° counter-current to the flow direction of the medium in the second medium flow channel 20. During counter-current flow, the temperature difference between the phase-change medium (e.g., refrigerant, from low to high temperature) and the non-phase-change medium (e.g., coolant, from high to low temperature) is more uniform and larger overall along the entire flow channel length. This larger average temperature difference enhances the driving force for heat transfer, increasing the amount of heat transferred per unit time and thus improving the heat exchanger's efficiency. Furthermore, the uniform temperature distribution avoids localized overheating, such as preventing heat exchange stagnation caused by a small temperature difference at the outlet during co-current flow, thus extending the heat exchanger's service life.

[0048] like Figures 1-2 As shown, in this embodiment, an inner fin 12 is also provided in the first medium flow channel 10. The inner fin 12 has a continuous gradient spiral structure, and the pitch of the inner fin 12 changes synchronously with the pitch of the continuous gradient spiral baffle 11.

[0049] The internal fins 12 increase the contact area between the phase-change medium and the flow channel, thereby improving heat transfer efficiency. The continuously varying spiral structure of the internal fins 12 and the synchronously changing pitch of the continuously varying spiral baffles 11 allow for dynamic adjustment of the spatial distribution within the flow channel as the phase-change medium expands, preventing localized blockages caused by the fixed structure of the internal fins 12. This ensures that when the gaseous medium expands after phase change, the increased pitch of the internal fins 12 provides sufficient flow space for the gaseous medium. Furthermore, the combination of the continuously varying spiral structure of the internal fins 12 and the continuously varying spiral baffles 11 makes it easier for the medium to form turbulent flow rather than laminar flow during flow, further enhancing the disturbance to the medium and improving the heat transfer coefficient.

[0050] Furthermore, in this embodiment, the inner fins 12 and the continuous gradient spiral baffles 11 on the inner wall of the first medium flow channel 10 are arranged at a preset angle. The preset angle between the two causes the inner fins 12 and the continuous gradient spiral baffles 11 to form an intersecting structure. When the medium flows, it must simultaneously bypass both of them, forming more complex turbulence (such as eddies and secondary flows), which increases the collision frequency between the medium and the inner fins 12 and the continuous gradient spiral baffles 11, thereby improving the heat transfer coefficient.

[0051] For example, the preset angle in this embodiment can be set to 30°-90°. When the preset angle is <30°, the inner fins 12 are nearly parallel to the continuous gradient spiral baffles 11, resulting in weak disturbance and making it difficult to significantly improve the heat transfer coefficient; when the angle is >90°, although the disturbance is strong, the flow resistance increases sharply, which will increase the system drive energy consumption and increase the cost.

[0052] For example, the preset angle between the two in this embodiment can be set to 30°, 45°, 60°, 90°, etc.

[0053] like Figure 3 As shown, Figure 3 The simulation diagram shows the flow field of the first medium channel 10. This simulation diagram intuitively presents the fluid motion state within the first medium channel 10 of the heat exchanger. It can be clearly observed in the diagram that there are a large number of irregular vortices within the first medium channel 10. These vortices are continuously distributed along the extension direction of the first medium channel 10, effectively breaking the laminar boundary layer formed by the medium on the channel wall, avoiding the heat transfer efficiency decay caused by the thickening of the boundary layer. The enhanced heat transfer effect of the inner fins 12 and the continuous gradient spiral baffles 11 is verified from the perspective of flow field characteristics.

[0054] Optionally, the flow field simulation diagram of the first medium flow channel 10 can be drawn using commonly used computational fluid dynamics (CFD) software in the industry, such as ANSYS Fluent, COMSOL, or STAR-CCM+, etc.

[0055] In this embodiment, the heat exchanger is integrally formed using metal 3D printing technology. Specifically, high thermal conductivity metal materials such as aluminum alloy and copper alloy can be selected. The overall structure is precisely manufactured using selective laser melting (SLM) technology. Metal 3D printing technology can accurately reproduce the continuous gradient spiral baffle 11 and synchronously gradient inner fins 12 in the first medium flow channel 10, as well as the continuous fixed spiral baffle 21 in the second medium flow channel 20. At the same time, it ensures that the outer peripheral walls of each flow channel in the matrix-alternating flow channel layout are tightly fitted to form a complete heat exchange surface.

[0056] Compared to traditional splicing or casting processes, metal 3D printing technology eliminates the need for segmented processing or assembly of complex spiral structures. It can complete the integrated molding of the flow channel inner wall, baffles, and inner fins 12 in one go, completely eliminating the thermal resistance risks such as weld seams and assembly gaps caused by splicing multiple parts, and significantly improving the heat transfer efficiency of the heat exchange surface. At the same time, its layered stacking manufacturing characteristics can precisely control the pitch change accuracy of the continuously gradually changing spiral baffles 11, ensuring the dynamic adaptability of the flow channel space and volume expansion during the phase change medium flow. In addition, metal 3D printing can flexibly adjust the flow channel wall thickness and the distribution density of the inner fins 12, maximizing the heat exchange area while meeting structural strength requirements, and further enhancing heat exchange performance.

[0057] Heat exchanger models formed by metal 3D printing have no dead corners or suspended structures, resulting in excellent forming quality and minimizing the formation of defective areas. All suspended angles are greater than 45°, demonstrating superior printing performance. Furthermore, metal 3D printing is a one-piece molding process, simplifying assembly and eliminating intermediate welding structures, thereby improving the reliability of the heat exchanger.

[0058] like Figures 1-2 As shown, in this embodiment, the first medium flow channel 10 has a first inlet 30 and a first outlet 40 at its opposite ends, and the second medium flow channel 20 has a second inlet 50 and a second outlet 60 at its opposite ends. The first inlet 30 and the first outlet 40 are used to connect the two ends of the refrigerant circulation loop, and the second inlet 50 and the second outlet 60 are used to connect the two ends of the water circulation loop.

[0059] In some alternative embodiments, the first inlet 30 and the first outlet 40 adopt a quick-connect structure to accommodate the copper pipes of the refrigerant circulation loop. The second inlet 50 and the second outlet 60 adopt a flange connection to accommodate the aluminum pipes of the water circulation loop.

[0060] In this embodiment, the pitch of the continuously variable spiral baffle 11 at the first inlet 30 is set to 2mm-20mm, and the pitch of the continuously variable spiral baffle 11 at the first outlet 40 is set to 4mm-40mm, with the pitch change step being 0.5mm-10mm per revolution.

[0061] Specifically, the pitch at the first inlet 30 (where the refrigerant is initially liquid) is 2mm-20mm. Since the liquid refrigerant has a small volume, a smaller pitch increases the density of the continuously tapered spiral baffles 11, enhancing turbulence and improving heat exchange efficiency in the liquid section. The pitch at the first outlet 40 (where the refrigerant becomes gaseous) is 4mm-40mm. Since the gaseous refrigerant expands, a larger pitch accommodates the volume change and prevents flow channel blockage. The gradual transition step size is 0.5mm-10mm per revolution, ensuring a smooth transition from the first inlet 30 to the first outlet 40, rather than an abrupt change, avoiding sudden increases in local eddies and flow resistance caused by structural abrupt changes.

[0062] For example, the refrigerant is R134a, the pitch of the continuous gradient spiral baffle 11 at the first inlet 30 is set to 5mm, the pitch at the first outlet 40 is set to 15mm, and the gradient step of the pitch is 1mm per revolution.

[0063] This embodiment also provides an automotive thermal management system, which includes the aforementioned heat exchanger, a refrigerant circulation loop for flowing a phase-change medium, and a water circulation loop for flowing a non-phase-change medium. The refrigerant circulation loop is connected to the first medium flow channel 10 of the heat exchanger; the water circulation loop is connected to the second medium flow channel 20 of the heat exchanger.

[0064] Because the automotive thermal management system has the aforementioned heat exchanger, it has high heat exchange performance, enabling rapid heat exchange between the refrigerant and coolant, improving heat exchange efficiency, and saving energy consumption.

[0065] Specifically, the refrigerant circulation loop includes a compressor, a receiver, and a throttling device. The compressor's discharge port is connected to the first inlet 30 of the first medium flow channel 10, and the first outlet 40 of the first medium flow channel 10 is connected to the inlet of the receiver. The outlet of the receiver, after passing through the throttling device, is connected to the compressor's suction port, forming a closed-loop refrigerant circulation. The compressor provides power, the receiver stabilizes the refrigerant flow (avoiding gas-liquid mixing), and the throttling device (such as an electronic expansion valve) precisely controls the flow of refrigerant into the heat exchanger, ensuring a stable phase change process.

[0066] The water circulation loop includes a water pump and a heat dissipation component. The outlet of the water pump is connected to the second inlet 50 of the second medium flow channel 20, and the second outlet 60 of the second medium flow channel 20 is connected to the heat dissipation component. The outlet of the heat dissipation component is connected to the inlet of the water pump, forming a closed-loop water circulation. The water pump drives the coolant to flow, and the heat dissipation component (such as a radiator) releases the absorbed heat into the environment, ensuring efficient coolant circulation.

[0067] Obviously, the above description is merely a preferred embodiment of the present invention and the technical principles employed. Those skilled in the art will understand that the present invention is not limited to the specific embodiments described herein, and various obvious changes, readjustments, and substitutions can be made without departing from the protection scope of the present invention. Therefore, although the present invention has been described in detail through the above embodiments, the present invention is not limited to the above embodiments. Many other equivalent embodiments may be included without departing from the concept of the present invention, and the scope of the present invention is determined by the scope of the appended claims.

[0068] Note that in the description of this specification, the references to terms such as "some embodiments," "other embodiments," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this utility model. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

Claims

1. A heat exchanger, characterized in that, include: A first medium flow channel (10) is provided in which a continuously tapered spiral baffle (11) is provided. The pitch of the continuously tapered spiral baffle (11) gradually increases along the flow direction of the medium in the first medium flow channel (10). The first medium flow channel (10) is adapted to a phase-change medium. The second medium flow channel (20) is provided with a continuous fixed spiral baffle (21) with equal pitch. The second medium flow channel (20) is adapted to a medium without phase change. The outer peripheral wall of the first medium flow channel (10) contacts the outer peripheral wall of the second medium flow channel (20) and forms a heat exchange surface, so that the medium in the first medium flow channel (10) exchanges heat with the medium in the second medium flow channel (20).

2. The heat exchanger according to claim 1, characterized in that, The first medium flow channel (10) and the second medium flow channel (20) are both configured as multiple, and the adjacent first medium flow channels (10) and second medium flow channels (20) are arranged alternately in a matrix, and at least four second medium flow channels (20) are distributed around any one of the first medium flow channels (10), and at least four first medium flow channels (10) are distributed around any one of the second medium flow channels (20).

3. The heat exchanger according to claim 1, characterized in that, The flow direction of the medium in the first medium flow channel (10) is set to be 180° opposite to the flow direction of the medium in the second medium flow channel (20).

4. The heat exchanger according to claim 1, characterized in that, The first medium flow channel (10) is also provided with an inner fin (12), which is a continuous gradual spiral structure. The pitch of the inner fin (12) is synchronously gradual with the pitch of the continuous gradual spiral baffle (11).

5. The heat exchanger according to claim 4, characterized in that, The inner fins (12) are arranged at a preset angle to the continuous gradient spiral baffles (11) on the inner wall of the first medium flow channel (10).

6. The heat exchanger according to claim 5, characterized in that, The preset angle is set to 30°-90°.

7. The heat exchanger according to claim 1, characterized in that, The first medium flow channel (10) has a first inlet (30) and a first outlet (40) at its opposite ends, and the second medium flow channel (20) has a second inlet (50) and a second outlet (60) at its opposite ends. The first inlet (30) and the first outlet (40) are used to connect the two ends of the refrigerant circulation loop, and the second inlet (50) and the second outlet (60) are used to connect the two ends of the water circulation loop.

8. The heat exchanger according to claim 7, characterized in that, The pitch of the continuously tapered spiral baffle (11) at the first inlet (30) is set to 2mm-20mm, and the pitch of the continuously tapered spiral baffle (11) at the first outlet (40) is set to 4mm-40mm, and the pitch gradient step is 0.5mm-10mm per turn.

9. An automotive thermal management system, characterized in that, The automotive thermal management system includes a heat exchanger as described in any one of claims 1-8, a refrigerant circulation loop for circulating a medium undergoing phase change, and a water circulation loop for circulating a medium without phase change; the refrigerant circulation loop is connected to the first medium flow channel (10) of the heat exchanger; and the water circulation loop is connected to the second medium flow channel (20) of the heat exchanger.

10. The automotive thermal management system according to claim 9, characterized in that, The refrigerant circulation loop includes a compressor, a liquid receiver and a throttling component. The exhaust port of the compressor is connected to the first inlet (30) of the first medium flow channel (10), the first outlet (40) of the first medium flow channel (10) is connected to the inlet of the liquid receiver, and the outlet of the liquid receiver is connected to the suction port of the compressor after passing through the throttling component, forming a closed-loop refrigerant circulation. The water circulation loop includes a water pump and a heat dissipation component. The outlet of the water pump is connected to the second inlet (50) of the second medium flow channel (20), and the second outlet (60) of the second medium flow channel (20) is connected to the heat dissipation component. The outlet of the heat dissipation component is connected to the inlet of the water pump, forming a closed-loop water circulation.

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