Heat exchanger and heat management system

Abstract

The invention provides a heat exchanger and a heat management system. The heat exchanger comprises a plurality of first plates and second plates, the first plates and the second plates are alternately arranged, adjacent first plates and second plates form plate pairs, and refrigerant heat exchange channels are defined between the first plates and the second plates of each plate pair or between every two adjacent plate pairs; the refrigerant inlet flow collecting channel communicates with the multiple refrigerant heat exchange channels; the refrigerant inlet flow collecting channel is communicated with the refrigerant heat exchange channels, the refrigerant outlet flow collecting channel is communicated with the refrigerant heat exchange channels, the heat exchanger further comprises a distribution structure, and the distribution structure is arranged in the refrigerant inlet flow collecting channel. According to the heat exchanger, the distribution structure is arranged in the refrigerant inlet flow collecting channel, so that the gas-liquid two-phase refrigerant can be uniformly distributed in the heat exchanger, and the heat exchange efficiency of the heat exchanger is effectively improved.

Description

TECHNICAL FIELD

[0001] The present disclosure relates to a heat exchanger and a heat management system comprising the same, in particular to a heat exchanger with a distribution structure. BACKGROUND

[0002] In a heat management system, a plate heat exchanger is usually employed 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, low-temperature refrigerant absorbs heat from high-temperature coolant, so that the coolant is cooled down, the refrigerant absorbs heat and changes phase (e.g. from liquid phase to gas phase), and then flows out of the plate heat exchanger.

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

[0004] Therefore, those skilled in the art are committed to developing a new type of heat exchanger to solve the above-mentioned defects of the prior art. SUMMARY

[0005] The purpose of the present disclosure is to provide a heat exchanger that can uniformly distribute gas-liquid two-phase refrigerant. By providing a distribution structure inside the refrigerant inlet manifold channel 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 can facilitate manufacturing and avoid separate installation of the distribution structure, thereby saving installation time.

[0006] The present disclosure provides a heat exchanger, comprising: a plurality of first plates and second plates arranged alternately, adjacent first plates and second plates forming a plate pair, 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 manifold channel communicating with a plurality of refrigerant heat exchange channels; and a refrigerant outlet manifold channel communicating with the plurality of refrigerant heat exchange channels, wherein the heat exchanger further comprises a distribution structure arranged in the refrigerant inlet manifold channel.

[0007] The heat exchanger according to the present disclosure can also have one or more of the following features, alone or in combination.

[0008] In one or more embodiments, the distribution structure comprises: a middle blocking portion; a peripheral blocking portion connected to the middle blocking portion; and a hole portion arranged around the middle blocking portion and alternating with the peripheral blocking portion.

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

[0011] In one or more embodiments, when a refrigerant heat exchange passage is defined between the first plate and the second plate of each plate pair, a coolant heat exchange passage is defined between two adjacent plate pairs; when a refrigerant heat exchange passage is defined between two adjacent plate pairs, a coolant heat exchange passage is defined between the first plate and the second plate of each plate pair, and a plurality of the coolant heat exchange passages and a plurality of the refrigerant heat exchange passages are alternately and layeringly arranged.

[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 arranged between the first plate and the second plate.

[0014] In one or more embodiments, the distribution structure comprises a plurality of peripheral blocking portions and a plurality of hole portions arranged alternately.

[0015] In one or more embodiments, a total of cross-sectional areas of the plurality of hole portions is less than a cross-sectional area of the refrigerant inlet header passage.

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

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

[0018] In one or more embodiments, the heat exchanger further comprises a first inlet and a first outlet, so that the refrigerant can flow into the refrigerant inlet header passage via the first inlet and flow out of the refrigerant outlet header passage via the first outlet.

[0019] The present disclosure also provides a heat management system comprising the aforementioned heat exchanger. BRIEF DESCRIPTION OF DRAWINGS

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

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

[0022] Figure 3 A sectional view of a heat exchanger according to an embodiment of the present disclosure, in which a refrigerant inlet header channel and a refrigerant outlet header channel are shown;

[0023] Figure 4 A perspective view of Figure 3 A partial enlarged view of the refrigerant inlet header channel shown at a distribution structure;

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

[0025] Figure 6 A perspective view of Figure 5 A partial enlarged view of the first plate or the second plate shown at a distribution structure. DETAILED DESCRIPTION

[0026] Other advantages and effects of the present disclosure can be easily understood by those skilled in the art from the content disclosed in the present specification.

[0027] It should be noted that the structures, proportions, sizes, etc. shown in the accompanying drawings of the present specification are only used to cooperate with the content disclosed in the present specification for the understanding and reading of those skilled in the art, and do not have technical significance in defining the conditions for implementing the present disclosure, so any modification of the structure, change of the proportional relationship or adjustment of the size, without affecting the effects and purposes that can be achieved by the present disclosure, should still fall within the scope of the technology disclosed by the present disclosure. At the same time, the terms such as "upper" and "one" used in the present specification are only for the convenience of clear description, and not to limit the scope of the present disclosure, and the change or adjustment of the relative relationship without substantially changing the technical content is also considered as the scope of the present disclosure.

[0028] The present disclosure provides a heat exchanger with a distribution structure. The specific embodiments of the present disclosure are specifically described below in conjunction with the accompanying drawings.

[0029] Please refer to Figures 1 to 4The heat exchanger 1 comprises a plurality of plate pairs 10 arranged in a stack, each plate pair 10 is formed by a first plate 11 (may also be referred to as a first heat exchange plate) and a second plate 12 (may also be referred to as a second heat exchange plate) arranged in a stack, wherein a refrigerant heat exchange passage is defined between two plate pairs 10, and a coolant heat exchange passage is defined between the first plate 11 and the second plate 12 of each plate pair 10, that is, two sides of each heat exchange plate (for example, the first plate and the second plate) are formed with heat exchange passages of different fluids, so that the plurality of refrigerant heat exchange passages and the plurality of coolant heat exchange passages are arranged in an alternating stack in the heat exchanger 1, thereby increasing the heat exchange area of the refrigerant and the coolant. Of course, the present disclosure is not limited to the above-mentioned arrangement positions of the refrigerant heat exchange passages and the coolant heat exchange passages. For example, the coolant heat exchange passages can be defined between two plate pairs 10, and the refrigerant heat exchange passages can be defined between the first plate 11 and the second plate 12 of each plate pair 10, as long as the plurality of refrigerant heat exchange passages and the plurality of coolant heat exchange passages are arranged in an alternating stack.

[0030] Please continue to see Figures 1 to 3 The heat exchanger 1 can have a generally cuboid shape, and refrigerant inlet and outlet manifold passages 20, 30, coolant inlet and outlet manifold passages (not shown) are arranged in the interior of the cuboid near the four corners, respectively, and pass through each plate pair 10. The refrigerant inlet and outlet manifold passages 20, 30 are arranged near two adjacent corners (for example, arranged near the two corners of the front side shown in Figure 1 , and are in fluid communication with the refrigerant heat exchange passages, so that the refrigerant can flow into the refrigerant heat exchange passages through the refrigerant inlet manifold passage 20, and flow out of the refrigerant heat exchange passages through the refrigerant outlet manifold passage 30. Correspondingly, the coolant inlet and outlet manifold passages can be arranged near the other two adjacent corners (for example, arranged near the two corners of the rear side shown in Figure 1 ), and are in fluid communication with the coolant heat exchange passages, so that the coolant can flow into the coolant heat exchange passages through the coolant inlet manifold passage, and flow out of the coolant heat exchange passages through the coolant outlet manifold passage, wherein the refrigerant and the coolant can be fully exchanged when flowing through their corresponding heat exchange passages.

[0031] Please continue to see Figure 1 and Figure 2 The heat exchanger 1 further comprises 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 arranged on the first side of the heat exchanger 1 (for example, the front side shown in Figure 1the first side (e.g. the upper side as shown) of the heat exchanger 1, and are respectively in fluid communication with the refrigerant inlet header channel 20 and the refrigerant outlet header channel 30, so that the refrigerant can flow into the refrigerant inlet header channel 20 via the first inlet 110, and flow out of the refrigerant outlet header channel 30 via the first outlet 120; correspondingly, the second inlet 210 and the second outlet 220 can be provided at the second side (e.g. the lower side as shown) of the heat exchanger 1 opposite to the first side, and are respectively in fluid communication with the coolant inlet header channel and the coolant outlet header channel, so that the coolant can flow into the coolant inlet header channel via the second inlet 210, and flow out of the coolant outlet header channel via the second outlet 220. Figure 1 the first side (e.g. the upper side as shown) of the heat exchanger 1, and are respectively in fluid communication with the refrigerant inlet header channel 20 and the refrigerant outlet header channel 30, so that the refrigerant can flow into the refrigerant inlet header channel 20 via the first inlet 110, and flow out of the refrigerant outlet header channel 30 via the first outlet 120; correspondingly, the second inlet 210 and the second outlet 220 can be provided at the second side (e.g. the lower side as shown) of the heat exchanger 1 opposite to the first side, and are respectively in fluid communication with the coolant inlet header channel and the coolant outlet header channel, so that the coolant can flow into the coolant inlet header channel via the second inlet 210, and flow out of the coolant outlet header channel via the second outlet 220.

[0032] When the gas-liquid two-phase refrigerant enters the refrigerant inlet header channel 20 via the first inlet 110, due to the higher linear flow velocity and lower dynamic viscosity of the gas phase, the gas phase refrigerant is more likely to flow into the refrigerant heat exchange channels at the start end (i.e. the refrigerant heat exchange channels close to the first inlet 110) than the liquid phase refrigerant; and due to the stronger cohesion and adsorption of the liquid, the liquid phase refrigerant is more likely to be adsorbed on the pipe wall of the header channel and form a liquid film, and a part of the liquid phase refrigerant will be impacted by the high-speed gas phase refrigerant and enter the refrigerant heat exchange channels at the start end, but more liquid refrigerant will accumulate to the end of the refrigerant inlet header channel 20 along the extension direction and flow into the refrigerant heat exchange channels at the end (i.e. the refrigerant heat exchange channels far away from the first inlet 110). Since the density of the liquid phase refrigerant is greater than that of the gas phase refrigerant, the final performance of the refrigerant in the heat exchanger 1 is that less mass flow of the refrigerant flows into the refrigerant heat exchange channels at the start end, and more mass flow of the refrigerant flows into the refrigerant heat exchange channels at the end, i.e. the refrigerant is unevenly distributed in the heat exchanger 1, resulting in lower heat exchange efficiency of the heat exchanger 1.

[0033] To overcome the above problems, the heat exchanger 1 of the present disclosure is provided with a distribution structure 40 in the refrigerant inlet header channel 20, as shown in Figure 3 The distribution structure 40 is arranged to evenly distribute the gas-liquid two-phase refrigerant in the heat exchanger 1, thereby effectively improving the heat exchange efficiency of the heat exchanger 1.

[0034] Specifically, please refer to Figure 5 and Figure 6The distribution structure 40 can include an intermediate barrier 41, a peripheral barrier 42 connected to the intermediate barrier 41, and a hole portion 43 arranged around the intermediate barrier 41 and alternating with the peripheral barrier 42. In an embodiment, the intermediate barrier 41 can be substantially circular, and the intermediate barrier 41 is mainly used to reduce the linear flow rate of the gas-phase refrigerant, reduce the linear flow rate difference between the gas-phase refrigerant and the liquid-phase refrigerant, weaken the slippage of the gas-liquid two-phase refrigerant, enhance the following effect of the liquid-phase refrigerant with the gas-phase refrigerant, and thus improve the probability of the liquid-phase refrigerant and the gas-phase refrigerant being evenly distributed in the refrigerant inlet manifold 20. Meanwhile, the intermediate barrier 41 can stop the refrigerant, and can avoid too much refrigerant flowing into the end of the refrigerant inlet manifold 20. Of course, the present disclosure is not limited to the shape of the intermediate barrier 41 described above. For example, the intermediate barrier 41 can also be set as a polygon, an oval, or other regular or irregular shapes, as long as it can reduce the linear flow rate of the gas-phase refrigerant and avoid too much refrigerant flowing into the end of the refrigerant inlet manifold.

[0035] The distribution structure 40 can include a plurality of peripheral barriers 42 and a plurality of hole portions 43 arranged around the intermediate barrier 41 alternately, such as three peripheral barriers 42 and three hole portions 43 shown in FIGS. 1 and 2. Figure 4 and Figure 5 The peripheral barrier 42 can be a plurality of legs extending outward from the intermediate barrier 41, and the plurality of legs can be uniformly distributed around the intermediate barrier 41 to uniformly fix the intermediate barrier 41 inside the refrigerant inlet manifold 20. In an embodiment, the peripheral barrier 42 can be substantially trapezoidal, and the upper base of the trapezoid is connected to the intermediate barrier 41. The peripheral barrier 42 can break the liquid film adsorbed on the pipe wall of the refrigerant inlet manifold 20, i.e., the liquid film is broken into small droplets and dispersed in the gas-phase refrigerant to generate a uniformly mixed gas-liquid two-phase refrigerant spray jet. The part between two adjacent peripheral barriers 42 is the hole portion 43. In an embodiment, the hole portion 43 can be substantially a fan ring, and the sum of the cross-sectional areas of the plurality of hole portions 43 is less than the cross-sectional area of the refrigerant inlet manifold 20. In this way, the average linear flow rate of the refrigerant can be increased, and the gas-phase refrigerant and the liquid-phase refrigerant can be more easily mixed uniformly. Of course, the present disclosure is not limited to the shapes of the peripheral barrier 42 and the hole portion 43 described above, and the plurality of legs can not be uniformly distributed around the intermediate barrier 41 (i.e., the distribution can be uneven), as long as the peripheral barrier 42 and the hole portion 43 are arranged around the intermediate barrier 41 alternately.

[0036] Please refer to Figure 3The distribution structure 40 of the present application is arranged inside the refrigerant inlet manifold 20. Specifically, the refrigerant inlet manifold 20 can have a first end 21 and a second end 22 oppositely arranged in the extending direction thereof, and the distance between the first end 21 and the second end 22 is L (i.e. the extending length of the refrigerant inlet manifold 20 is L). In the present embodiment, the first end 21 is close to the first inlet 110, and the second end 22 is away from the first inlet 110, but the present disclosure is not limited thereto. The distribution structure 40 is arranged between the first end 21 and the second end 22, for example, the distance between the distribution structure 41 and the first end 21 can be approximately between L / 3 and 2L / 3, preferably, the distance between the distribution structure 41 and the first end 21 can be approximately L / 2, i.e. the distribution structure 40 can be arranged at the middle position of the refrigerant inlet manifold 20. Arranging the distribution structure 40 at the above-mentioned position can maximize the mixing of the gas-phase refrigerant and the liquid-phase refrigerant, so that the gas-liquid two-phase refrigerant is evenly distributed in the heat exchanger 1.

[0037] Please refer to Figure 5 and Figure 6 In an embodiment, the distribution structure 40 can be integrally formed with a heat exchange plate (e.g. the first plate 11 or the second plate 12), so that the manufacturing process is facilitated and the separate installation of the distribution structure 40 is avoided, i.e. 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 as in the prior art. It should be noted that the operator only needs to arrange the heat exchange plate having the distribution structure 40 according to the position where the distribution structure 40 is to be arranged. Of course, the present disclosure is not limited to the above-mentioned 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 (e.g. sandwiched between two plate pairs 10 or sandwiched between the first plate 11 and the second plate 12 of a plate pair 10), as long as the middle blocking portion 41, the peripheral blocking portion 42 and the hole portion 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 inside 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 of the present disclosure will be described below in combination with Figure 3 and Figure 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 gaseous refrigerant and the stronger cohesion and adsorption of the liquid refrigerant, most of the gaseous 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 refrigerant flows around the gaseous 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 will stop the gaseous refrigerant and reduce its linear velocity (e.g., Figure 4 (The large arrow shown becomes a small arrow), reducing the linear velocity difference between the gaseous and liquid refrigerants, weakening the slippage phenomenon of the gas-liquid two-phase refrigerants, enhancing the following effect of the liquid refrigerant with the gaseous refrigerant, improving the mixing degree of the liquid and gaseous refrigerants, and the intermediate barrier 41 can prevent excessive refrigerant from flowing into the end of the refrigerant inlet manifold 20, and allow 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, dispersing it in the gaseous refrigerant, generating a uniformly mixed gas-liquid two-phase refrigerant spray jet, and the refrigerant can increase its average linear velocity when passing through the orifice 43, making it easier for the gaseous 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 110 (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 110 (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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