Heat exchanger and thermal management system

Abstract

The present disclosure provides a heat exchanger and a thermal management system. The heat exchanger provided by the present disclosure comprises: a plurality of first plates and second plates which are alternately arranged, adjacent first plates and second plates forming plate pairs, and a refrigerant heat exchange channel being defined between the first plate and the second plate of each plate pair or between two adjacent plate pairs; a refrigerant inlet collection channel, which is in communication with the plurality of refrigerant heat exchange channels; and a refrigerant outlet collection channel, which is in communication with the plurality of refrigerant heat exchange channels. The heat exchanger further comprises a distribution structure, and the distribution structure is provided in the refrigerant inlet collection channel. According to the present disclosure, by means of providing the distribution structure in the interior of the refrigerant inlet collection channel, a gas-liquid two-phase refrigerant can be evenly distributed in the heat exchanger, thereby effectively improving the heat exchange efficiency of the heat exchanger.

Description

Heat exchangers and thermal management systems Technical Field

[0001] This disclosure relates to a heat exchanger and a thermal management system including the heat exchanger, and more particularly to a heat exchanger having a distribution structure. Background Technology

[0002] In thermal management systems, plate heat exchangers are typically used to achieve heat exchange between refrigerant and coolant. The refrigerant enters the plate heat exchanger and exchanges heat with the coolant flowing into the plate heat exchanger. For example, the low-temperature refrigerant absorbs heat from the high-temperature coolant, causing the coolant to cool down. The refrigerant absorbs heat and changes phase (e.g., from liquid to gas) and flows out of the plate heat exchanger.

[0003] However, when a gas-liquid two-phase refrigerant enters a plate heat exchanger, for example, when the gas-liquid two-phase refrigerant enters the refrigerant inlet manifold of the plate heat exchanger, only a small amount of refrigerant will flow into the heat exchange channel near the beginning of the manifold, while a larger amount of refrigerant will flow into the heat exchange channel near the end of the manifold. This results in uneven distribution of refrigerant within the heat exchanger, affecting the heat exchange efficiency of the heat exchanger and making it difficult to maximize its heat exchange performance.

[0004] Therefore, those skilled in the art are dedicated to developing a novel heat exchanger to overcome the aforementioned deficiencies of the prior art. Summary of the Invention

[0005] The purpose of this disclosure is to provide a heat exchanger that can uniformly distribute gas-liquid two-phase refrigerant. By setting a distribution structure inside the refrigerant inlet manifold of the heat exchanger, the gas-liquid two-phase refrigerant can be uniformly distributed in the heat exchanger, thereby effectively improving the heat exchange efficiency of the heat exchanger. Moreover, the distribution structure can be integrally formed with the heat exchange plate (e.g., the first plate or the second plate), which facilitates manufacturing and avoids the need to install the distribution structure separately, thus saving installation time.

[0006] This disclosure provides a heat exchanger comprising: a plurality of alternately arranged first plates and second plates, adjacent first plates and second plates forming plate pairs, wherein the first plate and second plate of each plate pair or between two adjacent plate pairs defines a refrigerant heat exchange channel; a refrigerant inlet manifold connecting the plurality of refrigerant heat exchange channels; and a refrigerant outlet manifold connecting the plurality of refrigerant heat exchange channels, wherein the heat exchanger further comprises a distribution structure disposed within the refrigerant inlet manifold.

[0007] The heat exchanger according to this disclosure may also have one or more of the following features, individually or in combination.

[0008] In one or more embodiments, the dispensing structure includes: a central blocking portion; a peripheral blocking portion connected to the central blocking portion; and a hole portion disposed alternately around the central blocking portion and the peripheral blocking portion.

[0009] In one or more embodiments, the refrigerant inlet manifold has a first end and a second end in its extending direction, the distance between the first end and the second end is L, and the distance from the distribution structure to the first end (21) is between L / 3 and 2L / 3.

[0010] In one or more embodiments, the distance from the allocation structure to the first end is L / 2.

[0011] In one or more embodiments, when the first plate and the second plate of each plate pair define the refrigerant heat exchange channel, then the adjacent two plate pairs define the coolant heat exchange channel; when the adjacent two plate pairs define the refrigerant heat exchange channel, then the first plate and the second plate of each plate pair define the coolant heat exchange channel, wherein a plurality of coolant heat exchange channels and a plurality of refrigerant heat exchange channel layers are alternately stacked.

[0012] In one or more embodiments, the distribution structure is integrally formed with the first plate or the second plate.

[0013] In one or more embodiments, the distribution structure is disposed between adjacent first and second plates.

[0014] In one or more embodiments, the distribution structure includes a plurality of peripheral barriers and a plurality of holes arranged alternately.

[0015] In one or more embodiments, the sum of the cross-sectional areas of the plurality of holes is less than the cross-sectional area of ​​the refrigerant inlet manifold.

[0016] In one or more embodiments, the intermediate blocking portion is circular, polygonal, or elliptical, and the blocking portion is a plurality of legs extending outward from the intermediate blocking portion, the plurality of legs being evenly distributed around the intermediate blocking portion.

[0017] In one or more embodiments, the allocation structure is at least one.

[0018] In one or more embodiments, the heat exchanger further includes a first inlet and a first outlet, allowing the refrigerant to flow into the refrigerant inlet manifold via the first inlet and out of the refrigerant outlet manifold via the first outlet.

[0019] This disclosure also provides a thermal management system, which includes the aforementioned heat exchanger. Attached Figure Description

[0020] Figure 1 is a perspective view of a heat exchanger according to an embodiment of the present disclosure;

[0021] Figure 2 is a perspective view of a heat exchanger according to an embodiment of the present disclosure from another angle;

[0022] Figure 3 is a cross-sectional view of a heat exchanger according to an embodiment of the present disclosure, showing a refrigerant inlet manifold and a refrigerant outlet manifold.

[0023] Figure 4 is a partial enlarged view of the refrigerant inlet manifold shown in Figure 3 at the distribution structure;

[0024] Figure 5 is a perspective view of a first plate or a second plate according to an embodiment of the present disclosure, wherein the first plate or the second plate is provided with a distribution structure;

[0025] Figure 6 is a partial enlarged view of the first or second plate shown in Figure 5 at the distribution structure. Detailed Implementation

[0026] The following specific embodiments illustrate the implementation of this disclosure. Those skilled in the art can easily understand other advantages and effects of this disclosure from the content disclosed in this specification.

[0027] It should be understood that the structures, proportions, sizes, etc., depicted in the accompanying drawings are merely for illustrative purposes to aid those skilled in the art in understanding and reading the content disclosed herein, and are not intended to limit the implementation conditions of this disclosure. Therefore, they have no substantial technical significance. Any modifications to the structure, changes in proportions, or adjustments to the size, without affecting the effectiveness and purpose of this disclosure, should still fall within the scope of the technical content disclosed herein. Furthermore, the terms such as "above" and "a" used in this specification are merely for clarity of description and are not intended to limit the scope of this disclosure. Changes or adjustments to their relative relationships, without substantially altering the technical content, should also be considered within the scope of this disclosure's implementation.

[0028] This disclosure provides a heat exchanger with a distribution structure. Specific embodiments of this disclosure are described below with reference to the accompanying drawings.

[0029] Please refer to Figures 1 to 4. The heat exchanger 1 includes multiple stacked plate pairs 10. Each plate pair 10 consists of a stacked first plate 11 (also referred to as a first heat exchange plate) and a second plate 12 (also referred to as a second heat exchange plate). The space between the two plate pairs 10 defines a refrigerant heat exchange channel, and the space between the first plate 11 and the second plate 12 of each plate pair 10 defines a coolant heat exchange channel. That is, heat exchange channels for different fluids are formed on both sides of each heat exchange plate (e.g., the first plate and the second plate), so that the multiple refrigerant heat exchange channels and multiple coolant heat exchange channels in the heat exchanger 1 are alternately stacked, increasing the heat exchange area of ​​the refrigerant and coolant. Of course, this disclosure is not limited to the above-mentioned arrangement of the refrigerant heat exchange channels and coolant heat exchange channels. For example, the space between the two plate pairs 10 can also be defined as a coolant heat exchange channel, and the space between the first plate 11 and the second plate 12 of each plate pair 10 can also be defined as a refrigerant heat exchange channel, as long as the multiple refrigerant heat exchange channels and multiple coolant heat exchange channels are alternately stacked.

[0030] Please refer to Figures 1 to 3. The heat exchanger 1 can be roughly rectangular in shape. Inside the cuboid, near the four corners, there are refrigerant inlet manifolds 20, refrigerant outlet manifolds 30, coolant inlet manifolds (not shown), and coolant outlet manifolds (not shown), which penetrate each plate pair 10. The refrigerant inlet manifolds 20 and 30 are located near two adjacent corners (for example, near the two corners on the front side shown in Figure 1), and are both in fluid communication with the refrigerant heat exchange channel, allowing the refrigerant to pass through the refrigerant inlet manifold. The refrigerant flows into the refrigerant heat exchange channel through the inlet manifold 20 and out of the refrigerant heat exchange channel through the refrigerant outlet manifold 30. Correspondingly, the coolant inlet manifold and the coolant outlet manifold can be located near two other adjacent corners (for example, near the two corners on the rear side as shown in Figure 1), and both are in fluid communication with the coolant heat exchange channel, so that the coolant can flow into the coolant heat exchange channel through the coolant inlet manifold and out of the coolant heat exchange channel through the coolant outlet manifold, wherein the refrigerant and the coolant can fully exchange heat when flowing through their corresponding heat exchange channels.

[0031] Please refer to Figures 1 and 2. The heat exchanger 1 also includes a first inlet 110, a first outlet 120, a second inlet 210, and a second outlet 220. The first inlet 110 and the first outlet 120 can be located on a first side of the heat exchanger 1 (e.g., the upper side shown in Figure 1) and are in fluid communication with the refrigerant inlet manifold 20 and the refrigerant outlet manifold 30, respectively, so that the refrigerant can flow into the refrigerant inlet manifold 20 through the first inlet (110) and flow out of the refrigerant outlet manifold 30 through the first outlet 120. Correspondingly, the second inlet 210 and the second outlet 220 can be located on a second side of the heat exchanger 1 opposite to the first side (e.g., the lower side shown in Figure 1) and are in fluid communication with the coolant inlet manifold and the coolant outlet manifold, respectively, so that the coolant can flow into the coolant inlet manifold through the second inlet 210 and flow out of the coolant outlet manifold through the second outlet 220.

[0032] When the gas-liquid two-phase refrigerant enters the refrigerant inlet manifold 20 through the first inlet 110, the gas phase refrigerant is more likely to flow into the refrigerant heat exchange channel at the beginning end (i.e., the refrigerant heat exchange channel near the first inlet 110) than the liquid phase refrigerant due to the higher linear velocity and lower dynamic viscosity of the gas. Furthermore, due to the strong cohesiveness and adsorption properties of liquids, the liquid phase refrigerant is more likely to adsorb onto the pipe wall of the manifold and form a liquid film. A portion of the liquid phase refrigerant is impacted by the high-speed gas phase refrigerant and enters the refrigerant heat exchange channel at the beginning end, but more liquid refrigerant accumulates along the extension direction of the refrigerant inlet manifold 20 to the end of the manifold and flows into the refrigerant heat exchange channel at the end (i.e., the refrigerant heat exchange channel away from the first inlet 110). Furthermore, since the density of liquid refrigerant is greater than that of gaseous refrigerant, the refrigerant in heat exchanger 1 ultimately exhibits the following behavior: a smaller mass flow rate of refrigerant flows into the refrigerant heat exchange channel at the beginning, while a larger mass flow rate of refrigerant flows into the refrigerant heat exchange channel at the end. In other words, the refrigerant is unevenly distributed in heat exchanger 1, resulting in a lower heat exchange efficiency of heat exchanger 1.

[0033] To overcome the above problems, the heat exchanger 1 of this disclosure is provided with a distribution structure 40 in the refrigerant inlet manifold 20, as shown in Figure 3. This arrangement allows the gas-liquid two-phase refrigerant to be evenly distributed in the heat exchanger 1, thereby effectively improving the heat exchange efficiency of the heat exchanger 1.

[0034] Specifically, referring to Figures 5 and 6, the distribution structure 40 may include an intermediate blocking portion 41, a peripheral blocking portion 42 connected to the intermediate blocking portion 41, and a hole portion 43 arranged around the intermediate blocking portion 41 and alternately with the peripheral blocking portion 42. In one embodiment, the intermediate blocking portion 41 may be generally circular, and the intermediate blocking portion 41 is mainly used to reduce the linear flow rate of the gaseous refrigerant, reduce the difference in linear flow rate between the gaseous and liquid refrigerants, weaken the slippage phenomenon of the gaseous and liquid refrigerants, enhance the following effect of the liquid refrigerant with the gaseous refrigerant, and thus improve the even distribution probability of the liquid and gaseous refrigerants in the refrigerant inlet manifold 20; at the same time, the intermediate blocking portion 41 can stop the refrigerant, which can prevent excessive refrigerant from flowing into the end of the refrigerant inlet manifold 20. Of course, this disclosure is not limited to the shape of the intermediate blocking part 41. For example, the intermediate blocking part 41 can also be configured as a polygon, an ellipse or other regular or irregular shape, as long as it can reduce the linear flow rate of the gaseous refrigerant and prevent too much refrigerant from flowing into the end of the refrigerant inlet manifold.

[0035] The distribution structure 40 may include a plurality of peripheral blocking portions 42 and a plurality of orifices 43 arranged alternately around the intermediate blocking portion 41, such as the three peripheral blocking portions 42 and three orifices 43 shown in Figures 4 and 5. The peripheral blocking portions 42 may be a plurality of legs extending outward from the intermediate blocking portion 41, which may be evenly distributed around the intermediate blocking portion 41 to uniformly fix the intermediate blocking portion 41 inside the refrigerant inlet manifold 20. In one embodiment, the peripheral blocking portions 42 may be generally trapezoidal, with the upper base of the trapezoid connected to the intermediate blocking portion 41. The arrangement of the peripheral blocking portions 42 can disrupt the liquid film adsorbed on the pipe wall of the refrigerant inlet manifold 20, breaking the liquid film into small droplets and dispersing it in the gaseous refrigerant to generate a uniformly mixed gas-liquid two-phase refrigerant spray jet. The portion between two adjacent peripheral blocking portions 42 constitutes the orifice 43. In one embodiment, the orifice 43 may be approximately fan-shaped, and the sum of the cross-sectional areas of the plurality of orifices 43 is less than the cross-sectional area of ​​the refrigerant inlet manifold 20. This arrangement can increase the average linear flow velocity of the refrigerant, making it easier for the gaseous and liquid refrigerants to mix uniformly. Of course, this disclosure is not limited to the above-described shapes of the peripheral blocking portion 42 and the orifice 43, nor is it limited to the plurality of legs being evenly distributed around the central blocking portion 41 (i.e., the distribution may be uneven), as long as the peripheral blocking portion 42 and the orifice 43 are arranged alternately around the central blocking portion 41.

[0036] Please refer back to Figure 3. The distribution structure 40 of this application is disposed inside the refrigerant inlet manifold 20. Specifically, the refrigerant inlet manifold 20 may have a first end 21 and a second end 22 disposed opposite to each other in its extension direction, and the distance between the first end 21 and the second end 22 is L (that is, the extension length of the refrigerant inlet manifold 20 is L). In this embodiment, the first end 21 is close to the first inlet 110, and the second end 22 is far from the first inlet 110, but this disclosure is not limited to this. The distribution structure 40 is disposed between the first end 21 and the second end 22. For example, the distance from the distribution structure 41 to the first end 21 may be approximately between L / 3 and 2L / 3. Preferably, the distance from the distribution structure 41 to the first end 21 may be approximately L / 2, that is, the distribution structure 40 may be disposed approximately in the middle position of the refrigerant inlet manifold 20. By disposing the distribution structure 40 in the above position, the gaseous refrigerant and the liquid refrigerant can be mixed to the greatest extent, so that the gaseous and liquid refrigerants are uniformly distributed in the heat exchanger 1.

[0037] Referring to Figures 5 and 6, in one embodiment, the distribution structure 40 can be integrally formed with a heat exchange plate (e.g., a first plate 11 or a second plate 12). This facilitates manufacturing and avoids the need for separate installation of the distribution structure 40. As in the prior art, the first plate 11 and the second plate 12 are first stacked to form a plate pair 10, and then the plate pair 10 is stacked to form the heat exchanger 1. It should be noted that the operator only needs to set the position of the heat exchange plate with the distribution structure 40 according to the desired location. Of course, this disclosure is not limited to the above-described arrangement of the distribution structure 40. For example, the distribution structure 40 can also be a separate structure sandwiched between adjacent first plates 11 and second plates 12 (for example, it can be sandwiched between two plate pairs 10 or between the first plate 11 and the second plate 12 of a certain plate pair 10), as long as the intermediate blocking part 41, the peripheral blocking part 42 and the hole part 43 of the distribution structure 40 are exposed inside the refrigerant inlet manifold 20; for another example, the distribution structure 40 can also be a separate structure welded to the corresponding position in the refrigerant inlet manifold 20.

[0038] The movement of the gas-liquid two-phase refrigerant after entering the refrigerant inlet manifold 20 of the heat exchanger 1 described herein will be explained below with reference to Figures 3 and 4.

[0039] When the gas-liquid two-phase refrigerant enters the refrigerant inlet manifold 20 through the first inlet 110, due to the higher linear velocity and lower viscosity of the gas phase refrigerant and the stronger cohesion and adsorption of the liquid phase refrigerant, most of the gas phase refrigerant flows in the middle of the cross-section of the refrigerant inlet manifold 20 (close to the axis of the refrigerant inlet manifold 20), while most of the liquid phase refrigerant flows around the gas phase refrigerant and adsorbs onto the pipe wall of the refrigerant inlet manifold 20. When the gas-liquid two-phase refrigerant flows to the distribution structure 40, the intermediate blocking part 41 stops the gas phase refrigerant, reducing its linear velocity (for example, the large arrow in Figure 4 becomes a small arrow), narrowing the linear flow between the gas phase refrigerant and the liquid phase refrigerant. The velocity difference weakens the slippage phenomenon of the gas-liquid two-phase refrigerant, enhances the following effect of the liquid refrigerant with the gas refrigerant, and improves the mixing degree of the liquid and gas refrigerants. Moreover, the intermediate barrier 41 can prevent excessive refrigerant from flowing into the end of the refrigerant inlet manifold 20, and allows more gas-liquid two-phase refrigerant to flow into the refrigerant heat exchange channel at the beginning. At the same time, the peripheral barrier 42 of the distribution structure 40 can destroy the liquid film adsorbed on the pipe wall of the refrigerant inlet manifold 20, breaking the liquid film into small droplets, which are dispersed in the gas refrigerant to generate a uniformly mixed gas-liquid two-phase refrigerant spray jet. Furthermore, the average linear velocity of the refrigerant can be increased when it passes through the orifice 43, making it easier for the gas and liquid refrigerants to mix evenly. This allows the gas-liquid two-phase refrigerant entering the refrigerant inlet manifold 20 to be distributed approximately evenly in each refrigerant heat exchange channel of the heat exchanger 1 under the action of the distribution structure 40 (i.e., the refrigerant can be evenly distributed in the refrigerant heat exchange channels at the beginning and end). It then exchanges heat with the coolant entering the coolant heat exchange channel via the second inlet 210 and the coolant inlet manifold, increasing the heat exchange area between the refrigerant and coolant and improving the heat exchange efficiency of the heat exchanger 1. Subsequently, the refrigerant flows out of the heat exchanger 1 via the refrigerant outlet manifold 30 and the first outlet 120, and the coolant flows out of the heat exchanger via the coolant outlet manifold and the second outlet 220, completing the heat exchange between the refrigerant and coolant. Therefore, the heat exchanger 1 equipped with the distribution structure 40 in this application can evenly distribute the gas-liquid two-phase refrigerant, effectively improving the heat exchange efficiency of the heat exchanger 1.

[0040] Although the above embodiments of this disclosure are illustrated by taking the example of setting one distribution structure 40 in the refrigerant inlet manifold 20, this disclosure is not limited to this. For example, multiple distribution structures 40 may also be set in the refrigerant inlet manifold 20, which can further improve the heat exchange efficiency of the heat exchanger.

[0041] The above embodiments of this disclosure are illustrated using multiple peripheral blocking portions 42 and multiple hole portions 43 as examples. However, this disclosure is not limited to this. For example, the peripheral blocking portion 42 and the hole portion 43 may also be one. The specific configuration can be changed according to actual needs.

[0042] The above embodiments of this disclosure are illustrated by taking the distribution structure 40 as an example, which includes three parts: a middle blocking part 41, a peripheral blocking part 42, and a hole part 30. However, this disclosure is not limited to this. For example, the distribution structure 40 may also include only two parts: the blocking part and the hole part, as long as the cross-sectional area of ​​the hole part is smaller than the cross-sectional area of ​​the refrigerant inlet manifold channel and can prevent excessive refrigerant from flowing into the end of the refrigerant inlet manifold channel 20.

[0043] The above embodiments of this disclosure are illustrated with the example of the first inlet 110 and the second inlet 120 being located on the first side of the heat exchanger 1, and the second inlet 210 and the second outlet 220 being located on the second side of the heat exchanger 1. However, this disclosure is not limited to this. For example, the first inlet 110 and the first outlet 120, as well as the second inlet 210 and the second outlet 220, may also be located on the same side of the heat exchanger 1, as long as refrigerant and coolant are allowed to flow into and out of the heat exchanger 1.

[0044] Furthermore, the above embodiments of this disclosure are mainly illustrated by taking the example of a gas-liquid two-phase refrigerant entering the heat exchanger 1 through the first inlet 11O (at which time the heat exchanger 1 can act as a chiller). However, this disclosure is not limited to this. For example, a pure gaseous refrigerant can also enter the heat exchanger 1 through the first inlet 11O (at which time the heat exchanger 1 can act as a water-cooled condenser). During the flow of the pure gaseous refrigerant (for example, when it flows through a certain section of the refrigerant inlet manifold 20 and / or the refrigerant heat exchange channel), it will also become a gas-liquid two-phase state, that is, the problem of uneven refrigerant distribution also exists. Therefore, the heat exchanger 1 also needs to be provided with a distribution structure 40 in the refrigerant inlet manifold 20.

[0045] This disclosure provides a heat exchanger in which a distribution structure is provided inside the refrigerant inlet manifold, enabling uniform distribution of the gas-liquid two-phase refrigerant within the heat exchanger, thereby effectively improving the heat exchange efficiency. Furthermore, the distribution structure can be integrally formed with the heat exchange plates (e.g., the first plate or the second plate), facilitating manufacturing and avoiding the need for separate installation of the distribution structure, thus saving installation time.

[0046] This disclosure also provides a thermal management system, which includes the aforementioned heat exchanger 1 having a distribution structure 40.

[0047] The foregoing description of exemplary embodiments of the heat exchanger and thermal management system provided by this disclosure refers to preferred embodiments. However, those skilled in the art will understand that various modifications and alterations can be made to the above specific embodiments without departing from the spirit of this disclosure, and various combinations can be made to the various technical features and structures proposed in this disclosure without exceeding the protection scope of this disclosure, which is determined by the appended claims.

Claims

1. A heat exchanger (1), characterized in that, The heat exchanger (1) includes: Multiple alternating first plates (11) and second plates (12) are provided, with adjacent first plates (11) and second plates (12) forming plate pairs (10), and each plate pair (10) is defined as a refrigerant heat exchange channel between the first plate (11) and the second plate (12) or between two adjacent plate pairs (10); The refrigerant inlet manifold (20) connects to multiple refrigerant heat exchange channels; and The refrigerant outlet manifold (30) connects to the plurality of refrigerant heat exchange channels. The heat exchanger (1) further includes a distribution structure (40), which is disposed within the refrigerant inlet manifold (20).

2. The heat exchanger (1) as claimed in claim 1, characterized in that, The allocation structure (40) includes: Intermediate blocking part (41); A peripheral blocking portion (42) is connected to the intermediate blocking portion (41); and The hole (43) is arranged alternately around the intermediate blocking portion (41) and the peripheral blocking portion (42).

3. The heat exchanger (1) as described in claim 2, characterized in that, The refrigerant inlet manifold (20) has a first end (21) and a second end (22) in its extending direction, the distance between the first end (21) and the second end (22) is L, and the distance from the distribution structure (40) to the first end (21) is between L / 3 and 2L / 3.

4. The heat exchanger (1) as described in claim 3, characterized in that, The distance from the distribution structure (40) to the first end (21) is L / 2.

5. The heat exchanger (1) as claimed in claim 1, characterized in that, When the first plate (11) and the second plate (12) of each plate pair (10) define the refrigerant heat exchange channel, then the adjacent two plate pairs (10) define the coolant heat exchange channel. When the space between two adjacent plate pairs (10) defines the refrigerant heat exchange channel, then the space between the first plate (11) and the second plate (12) of each plate pair (10) defines the coolant heat exchange channel. The plurality of coolant heat exchange channels are alternately stacked with the plurality of refrigerant heat exchange channel layers.

6. The heat exchanger (1) as claimed in claim 1, characterized in that, The distribution structure (40) is integrally formed with the first plate (11) or the second plate (12).

7. The heat exchanger (1) as claimed in claim 1, characterized in that, The distribution structure (40) is disposed between adjacent first plates (11) and second plates (20).

8. The heat exchanger (1) as described in any one of claims 2-7, characterized in that, The distribution structure (40) includes a plurality of peripheral blocking portions (42) and a plurality of holes (43) arranged alternately.

9. The heat exchanger (1) as claimed in claim 8, characterized in that, The sum of the cross-sectional areas of the plurality of holes (43) is less than the cross-sectional area of ​​the refrigerant inlet manifold (20).

10. The heat exchanger (1) as claimed in claim 9, characterized in that, The intermediate blocking part (41) is circular, polygonal or elliptical, and the blocking part (42) is a plurality of legs extending outward from the intermediate blocking part (41), and the plurality of legs are evenly distributed around the intermediate blocking part (41).

11. The heat exchanger (1) as claimed in claim 1, characterized in that, The allocation structure (40) is at least one.

12. The heat exchanger (1) as claimed in claim 1, characterized in that, The heat exchanger (1) further includes a first inlet (110) and a first outlet (120) so that the refrigerant can flow into the refrigerant inlet manifold (20) via the first inlet (110) and flow out of the refrigerant outlet manifold (30) via the first outlet (120).

13. A thermal management system, characterized in that, The thermal management system includes a heat exchanger (1) as described in any one of claims 1-11.

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