Evaporator, thermal management system and vehicle

Abstract

The utility model discloses an evaporator, a heat management system and a vehicle, and relates to the technical field of heat exchange. The evaporator comprises a body and a plurality of refrigerant distribution structures, first heat exchange flow channels are formed between adjacent heat exchange plate sets of the body, and refrigerant flow channels are formed in the heat exchange plate sets. A first annular part of the refrigerant distribution structure is provided with a distribution cavity and a first refrigerant outlet, a refrigerant annular channel is formed between the first annular part and a second annular part, and the second annular part is provided with a second refrigerant outlet. Due to the fact that the first refrigerant outlet is located below the second refrigerant outlet, when the flow of the refrigerant is low, part of the liquid refrigerant is accumulated in the refrigerant annular channel and seals the first refrigerant outlet in a liquid mode, the resistance of the refrigerant passing through the first refrigerant outlet is increased, the refrigerant can flow to the first refrigerant outlet which is not sealed in the liquid mode, the uniformity of refrigerant distribution is improved, and the service life of the refrigerant is prolonged. The heat exchange efficiency of the evaporator is improved. When the flow of the refrigerant is high, the refrigerant in the refrigerant loop is in a gas-liquid mixed mist shape, no liquid seal exists at the first refrigerant outlet, and the influence on flowing of the refrigerant is small.

Description

Technical Field

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

[0002] Vehicles typically require a thermal management system to regulate the temperature of the passenger compartment or battery. This system includes a compressor, condenser, receiver-dryer, expansion valve, and evaporator. Refrigerant discharged from the compressor passes through the condenser, receiver-dryer, expansion valve, and evaporator before returning to the compressor. Because the refrigerant flow rate varies under different operating conditions, at low flow rates, the refrigerant is prone to gas-liquid separation after passing through the expansion valve. This results in uneven distribution of the refrigerant throughout the evaporator's flow channels, leading to reduced heat exchange efficiency. Utility Model Content

[0003] This invention aims to solve at least one of the technical problems existing in the prior art. To this end, this invention proposes an evaporator that can improve the uniformity of refrigerant distribution within the evaporator and improve heat exchange efficiency.

[0004] This utility model also proposes a thermal management system and a vehicle having the above-mentioned evaporator.

[0005] An evaporator according to a first aspect embodiment of the present invention includes: a body comprising a plurality of perimeters and a plurality of heat exchange plate assemblies arranged along a first direction, wherein the plurality of perimeters are correspondingly connected between two adjacent heat exchange plate assemblies, at least a portion of the structures of two adjacent heat exchange plate assemblies are spaced apart within the perimeters, and a first heat exchange channel for supplying heat exchange medium is formed within the perimeters; a refrigerant channel is provided within each heat exchange plate assembly, and the refrigerant channel is isolated from the first heat exchange channel; and a plurality of refrigerant distribution structures, respectively connected to corresponding heat exchange plate assemblies, wherein each refrigerant distribution structure includes a first annular portion and a second annular portion, the first annular portion being located within the second annular portion. The first annular portion is disposed inside the second annular portion and spaced apart from it. The first annular portion encloses and forms a distribution cavity. The first annular portion has a first refrigerant outlet that communicates with the distribution cavity. A refrigerant loop is formed between the first annular portion and the second annular portion that communicates with the first refrigerant outlet. The second annular portion has a second refrigerant outlet. The refrigerant loop communicates with the refrigerant flow channel through the second refrigerant outlet, so that the refrigerant enters the refrigerant loop in the distribution cavity through the first refrigerant outlet and is discharged to the refrigerant flow channel through the second refrigerant outlet. In the vertical direction, the first refrigerant outlet is located below the second refrigerant outlet.

[0006] The evaporator according to the embodiment of this utility model has at least the following beneficial effects:

[0007] The main body comprises multiple heat exchange plate assemblies, with a first heat exchange channel formed between adjacent heat exchange plate assemblies and a refrigerant channel formed within each heat exchange plate assembly. A refrigerant distribution structure is connected to the heat exchange plate assemblies. The first annular portion of the refrigerant distribution structure has a distribution chamber and a first refrigerant outlet. A refrigerant loop is formed between the first and second annular portions, and the second annular portion has a second refrigerant outlet. Therefore, the refrigerant enters from the distribution chamber, passes through the first refrigerant outlet into the refrigerant loop, and then passes through the second refrigerant outlet into the refrigerant channel, thus exchanging heat with the heat exchange medium in the first heat exchange channel. When the refrigerant flow rate is low, because the first refrigerant outlet is located below the second refrigerant outlet, the refrigerant entering the distribution chamber includes liquid refrigerant. Therefore, some liquid refrigerant accumulates in the refrigerant loop and liquid seals the first refrigerant outlet. As the liquid refrigerant continues to accumulate in the refrigerant loop, the liquid level gradually approaches the second refrigerant outlet, and finally enters the refrigerant channel through the second refrigerant outlet. Because the first refrigerant outlet is sealed by liquid refrigerant, the flow resistance at the first refrigerant outlet increases, slowing down the refrigerant flow velocity and reducing gas-liquid separation. This increased resistance causes most of the refrigerant to flow along the first direction to the next refrigerant distribution structure, until the first refrigerant outlets of all distribution structures are sealed by liquid refrigerant. Therefore, by increasing the refrigerant flow resistance, the refrigerant can be more evenly distributed throughout the refrigerant channels, improving the evaporator's heat exchange efficiency. When the refrigerant flow rate is high, the refrigerant in the refrigerant loop is in a gas-liquid mixed mist state. There is no liquid seal at the first refrigerant outlet, resulting in low flow resistance and minimal impact on the refrigerant flow velocity. The refrigerant is less likely to evaporate prematurely due to excessive pressure drop, thus improving the evaporator's heat exchange efficiency.

[0008] According to some embodiments of the present invention, the minimum width of the first refrigerant outlet is D, which satisfies: 0.5mm≤D≤1.5mm; and / or the minimum flow area of ​​the second refrigerant outlet is greater than or equal to the minimum flow area of ​​the first refrigerant outlet.

[0009] According to some embodiments of the present invention, a polar coordinate system is established on a projection plane perpendicular to the central axis of the distribution cavity, with the center of the distribution cavity as the pole. A ray extending from the pole along the direction of gravity is defined as a 0° line, and the angle is defined as positive in the counterclockwise direction. At least a portion of the projected profile of the first refrigerant outlet is located in the region between 0° and 30° or between 330° and 360°.

[0010] According to some embodiments of the present invention, at least a portion of the projected profile of the second refrigerant outlet lies within a region between 45° and 315°.

[0011] According to some embodiments of the present invention, there are multiple second refrigerant outlets, and the multiple second refrigerant outlets are arranged at circumferential intervals along the refrigerant loop.

[0012] According to some embodiments of the present invention, the heat exchange plate assembly includes a first partition and a second partition connected to each other, and the refrigerant flow channel is formed between the first partition and the second partition.

[0013] According to some embodiments of the present invention, the second partition plate has a plurality of protrusions located in the refrigerant channel on the side facing the first partition plate, and the plurality of protrusions are spaced apart.

[0014] According to some embodiments of the present invention, the edge of the first partition is provided with a first folded edge that bends toward the second partition. The first folded edge is connected to the second partition. A baffle is provided in the refrigerant flow channel, which is connected to the first partition and the second partition. The baffle extends in the vertical direction, and the upper end of the baffle is connected to the first folded edge. The lower end of the baffle is spaced apart from the first folded edge. The baffle is configured to divide the refrigerant flow channel into a first flow segment and a second flow segment. The first flow segment and the second flow segment are connected through the gap between the lower end of the baffle and the first folded edge. The second refrigerant outlet is located in the first flow segment. The heat exchange plate assembly is provided with a third refrigerant outlet, which is located in the second flow segment.

[0015] According to some embodiments of the present invention, the body further includes two baffles, one of which is connected to one end of the body along the first direction, and the other baffle is connected to the other end of the body along the first direction, and a second heat exchange channel is formed between the baffles and the body, and the second heat exchange channel is connected to the first heat exchange channel.

[0016] A thermal management system according to a second aspect of the present invention includes a compressor, a condenser, a liquid receiver, an expansion valve, and an evaporator, wherein the evaporator is the evaporator described in the above embodiment. The outlet of the compressor is connected to the inlet of the condenser, the outlet of the condenser is connected to the inlet of the liquid receiver, the outlet of the liquid receiver is connected to the inlet of the expansion valve, the outlet of the expansion valve is connected to the distribution chamber of the evaporator, and the outlet of the evaporator is connected to the inlet of the compressor.

[0017] The thermal management system according to the embodiments of the present invention has at least the following beneficial effects:

[0018] The evaporator using the first aspect embodiment includes a body comprising multiple heat exchange plate assemblies. A first heat exchange channel is formed between adjacent heat exchange plate assemblies, and a refrigerant channel is formed within each heat exchange plate assembly. A refrigerant distribution structure is connected to the heat exchange plate assemblies. The first annular portion of the refrigerant distribution structure has a distribution chamber and a first refrigerant outlet. A refrigerant loop is formed between the first and second annular portions, and the second annular portion has a second refrigerant outlet. Therefore, the refrigerant enters from the distribution chamber, passes through the first refrigerant outlet into the refrigerant loop, and then passes through the second refrigerant outlet into the refrigerant channel, thereby exchanging heat with the heat exchange medium in the first heat exchange channel. When the refrigerant flow rate is low, because the first refrigerant outlet is located below the second refrigerant outlet, and the refrigerant entering the distribution chamber includes liquid refrigerant, some liquid refrigerant accumulates in the refrigerant loop and liquid seals the first refrigerant outlet. As the liquid refrigerant continues to accumulate in the refrigerant loop, the liquid level gradually approaches the second refrigerant outlet, and finally enters the refrigerant channel through the second refrigerant outlet. Because the first refrigerant outlet is sealed by liquid refrigerant, the flow resistance at the first refrigerant outlet increases, slowing down the refrigerant flow velocity and reducing gas-liquid separation. This increased resistance causes most of the refrigerant to flow along the first direction to the next refrigerant distribution structure, until the first refrigerant outlets of all distribution structures are sealed by liquid refrigerant. Therefore, by increasing the refrigerant flow resistance, the refrigerant can be more evenly distributed throughout the refrigerant channels, improving the evaporator's heat exchange efficiency. When the refrigerant flow rate is high, the refrigerant in the refrigerant loop is in a gas-liquid mixed mist state. There is no liquid seal at the first refrigerant outlet, resulting in low flow resistance and minimal impact on the refrigerant flow velocity. The refrigerant is less likely to evaporate prematurely due to excessive pressure drop, thus improving the evaporator's heat exchange efficiency.

[0019] The vehicle according to a third aspect of the present invention includes the thermal management system described in the above embodiments.

[0020] The vehicle according to the embodiments of this utility model has at least the following beneficial effects:

[0021] The thermal management system of the second aspect embodiment includes an evaporator comprising multiple heat exchange plate assemblies. A first heat exchange channel is formed between adjacent heat exchange plate assemblies, and a refrigerant channel is formed within each heat exchange plate assembly. A refrigerant distribution structure is connected to the heat exchange plate assemblies. The first annular portion of the refrigerant distribution structure has a distribution chamber and a first refrigerant outlet. A refrigerant loop is formed between the first and second annular portions, and the second annular portion has a second refrigerant outlet. Therefore, the refrigerant enters from the distribution chamber, passes through the first refrigerant outlet into the refrigerant loop, and then passes through the second refrigerant outlet into the refrigerant channel, thereby exchanging heat with the heat exchange medium in the first heat exchange channel. When the refrigerant flow rate is low, because the first refrigerant outlet is located below the second refrigerant outlet, and the refrigerant entering the distribution chamber includes liquid refrigerant, some liquid refrigerant accumulates in the refrigerant loop and liquid seals the first refrigerant outlet. As the liquid refrigerant continues to accumulate in the refrigerant loop, the liquid level gradually approaches the second refrigerant outlet, and finally enters the refrigerant channel through the second refrigerant outlet. Because the first refrigerant outlet is sealed by liquid refrigerant, the flow resistance at the first refrigerant outlet increases, slowing down the refrigerant flow velocity and reducing gas-liquid separation. This increased resistance causes most of the refrigerant to flow along the first direction to the next refrigerant distribution structure, until the first refrigerant outlets of all distribution structures are sealed by liquid refrigerant. Therefore, by increasing the refrigerant flow resistance, the refrigerant can be more evenly distributed throughout the refrigerant channels, improving the evaporator's heat exchange efficiency. When the refrigerant flow rate is high, the refrigerant in the refrigerant loop is in a gas-liquid mixed mist state. There is no liquid seal at the first refrigerant outlet, resulting in low flow resistance and minimal impact on the refrigerant flow velocity. The refrigerant is less likely to evaporate prematurely due to excessive pressure drop, thus improving the evaporator's heat exchange efficiency.

[0022] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0023] The present invention will be further described below with reference to the accompanying drawings and embodiments, wherein:

[0024] Figure 1 This is a schematic diagram of the structure of a thermal management system according to an embodiment of the present invention;

[0025] Figure 2 This is a schematic diagram of the structure of an evaporator according to an embodiment of the present invention;

[0026] Figure 3 This is an exploded view of an evaporator according to an embodiment of the present invention;

[0027] Figure 4 This is a cross-sectional view of an evaporator according to an embodiment of the present invention;

[0028] Figure 5 yes Figure 4 Enlarged view of point A in the middle;

[0029] Figure 6 This is a schematic diagram of the structure of the first partition plate according to an embodiment of the present invention;

[0030] Figure 7 This is a schematic diagram of the structure of the second partition plate according to an embodiment of the present invention;

[0031] Figure 8 This is a cross-sectional view of the heat exchanger plate assembly after connection according to one embodiment of the present invention;

[0032] Figure 9 yes Figure 8 Enlarged view of point B in the middle;

[0033] Figure 10 This is a schematic diagram of the end plate structure according to one embodiment of the present invention.

[0034] Figure label:

[0035] Thermal Management System 1000;

[0036] Condenser 100; Liquid receiver 200; Expansion valve 300; Evaporator 400; Body 410; Second heat exchange channel 412; Heat exchange inlet 413; Heat exchange outlet 414; Heat exchange plate assembly 420; First partition 421; First folded edge 4211; Second partition 422; Protrusion 4221; Second folded edge 4222; Refrigerant channel 423; First flow section 4231; Second flow section 4232; First heat exchange channel 430; Refrigerant distribution structure 440; First annular portion 441; Second annular portion 442; Distribution chamber 443; First refrigerant outlet 444; Refrigerant annular channel 445; Second refrigerant outlet 446; Baffle 450; Third refrigerant outlet 460; Baffle 470; End plate 480; First refrigerant connector 481; Second refrigerant connector 482; Surrounding edge 490; Compressor 500. Detailed Implementation

[0037] 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.

[0038] In the description of this utility model, it should be understood that the directional descriptions, such as up, down, front, back, left, right, etc., indicate the directional or positional relationship based on the directional or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0039] In the description of this utility model, "several" means one or more, "multiple" means two or more, "greater than," "less than," and "exceeding" are understood to exclude the stated number, while "above," "below," and "within" are understood to include the stated number. If "first" or "second" is used in the description, it is only for the purpose of distinguishing technical features and should not be construed as indicating or implying relative importance, or implicitly indicating the number of indicated technical features, or implicitly indicating the order of the indicated technical features.

[0040] In the description of this utility model, unless otherwise explicitly defined, terms such as "setting," "installation," and "connection" should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this utility model in conjunction with the specific content of the technical solution.

[0041] Thermal management systems are used in vehicles, including cars and trams. They regulate the temperature of the passenger compartment, such as by providing cooling or heating. In trams, the thermal management system can also regulate the temperature of the battery pack, ensuring it operates within a suitable range.

[0042] Reference Figure 1 As shown in the embodiment of this utility model, the thermal management system 1000 includes a compressor 500, a liquid receiver 200, an expansion valve 300, a condenser 100, and an evaporator 400. The compressor 500, condenser 100, liquid receiver 200, and evaporator 400 are arranged sequentially from left to right and connected to each other. The expansion valve 300 is connected to the liquid receiver 200. Due to the limited space inside the vehicle, to reduce the space occupied by the thermal management system 1000, the compressor 500, condenser 100, liquid receiver 200, and evaporator 400 are directly connected, eliminating some piping and making the overall structure of the thermal management system 1000 more compact.

[0043] Reference Figure 2 , Figure 3 , Figure 4 and Figure 5 As shown, an evaporator according to one embodiment of the present invention can be used in a thermal management system 1000. The evaporator 400 of this embodiment includes a body 410 and multiple refrigerant distribution structures 440. The body 410 includes multiple perimeters 490 and multiple heat exchange plate assemblies 420. The multiple heat exchange plate assemblies 420 are arranged along a first direction, which may be... Figure 4 In the left-right direction, multiple perimeters 490 are correspondingly connected between two adjacent heat exchanger plate groups 420. At least a portion of the structure of the two adjacent heat exchanger plate groups 420 is spaced apart along the first direction, and a first heat exchange channel 430 is formed within the perimeters 490. The first heat exchange channel 430 is used for the flow of heat exchange medium, which can be water, glycerin, etc. For ease of explanation, the following embodiments will use water as an example for the heat exchange medium. A refrigerant channel 423 is provided within the heat exchanger plate group 420. For example, the heat exchanger plate group 420 includes a first partition 421 and a second partition 422 connected to each other. The refrigerant channel 423 is formed between the first partition 421 and the second partition 422, and the refrigerant channel 423 is isolated from the first heat exchange channel 430. Multiple refrigerant distribution structures 440 are respectively connected to the corresponding heat exchanger plate groups 420. For example, the refrigerant distribution structure 440 is connected between the first partition 421 and the second partition 422.

[0044] Reference Figure 6 , Figure 7 , Figure 8 and Figure 9 As shown, the refrigerant distribution structure 440 includes a first annular portion 441 and a second annular portion 442. The first annular portion 441 is located within the second annular portion 442, and the first annular portion 441 and the second annular portion 442 are spaced apart. The first annular portion 441 encloses a distribution cavity 443, and the distribution cavities 443 of the plurality of first annular portions 441 are sequentially connected along a first direction. The sidewall of the first annular portion 441 is provided with a first refrigerant outlet 444 communicating with the distribution cavity 443. A refrigerant loop 445 is formed between the first annular portion 441 and the second annular portion 442, and the refrigerant loop 445 is arranged around the first annular portion 441, and the refrigerant loop 445 is connected to the first refrigerant outlet 444. The second annular portion 442 is provided with a second refrigerant outlet 446, and the refrigerant loop 445 is connected to the refrigerant flow channel 423 through the second refrigerant outlet 446. In the vertical direction, the first refrigerant outlet 444 is located below the second refrigerant outlet 446.

[0045] Using the above scheme, the refrigerant enters from the distribution chamber 443. Part of the refrigerant enters the refrigerant loop 445 through the first refrigerant outlet 444, and then enters the refrigerant flow channel 423 through the second refrigerant outlet 446, thereby exchanging heat with the heat exchange medium in the first heat exchange flow channel 430; the other part of the refrigerant flows to the next distribution chamber 443. Since the first refrigerant outlet 444 is located below the second refrigerant outlet 446, when the refrigerant flow rate is low, the refrigerant entering the distribution chamber 443 includes liquid refrigerant. Therefore, some liquid refrigerant will accumulate in the refrigerant loop 445 and liquid seal the first refrigerant outlet 444. As the liquid refrigerant continues to accumulate in the refrigerant loop 445, the liquid level will gradually approach the second refrigerant outlet 446, and finally enter the refrigerant flow channel 423 through the second refrigerant outlet 446. Because the first refrigerant outlet 444 is sealed by liquid refrigerant, the flow resistance at the first refrigerant outlet 444 increases, which slows down the refrigerant flow rate and reduces gas-liquid separation. Due to this increased flow resistance, most of the refrigerant flows along the first direction to the next refrigerant distribution structure 440 until all the first refrigerant outlets 444 of all refrigerant distribution structures 440 are sealed by liquid refrigerant. Therefore, by increasing the refrigerant flow resistance, the refrigerant can be more evenly distributed to all refrigerant channels 423, improving the heat exchange efficiency of the evaporator 400. When the refrigerant flow rate is high, the refrigerant in the refrigerant loop 445 appears as a gas-liquid mixture in a mist-like state with no obvious liquid level. Therefore, there is essentially no liquid seal at the first refrigerant outlet 444, which has little impact on the overall refrigerant flow rate. The low resistance also prevents premature evaporation due to excessive pressure drop, thus further improving the heat exchange efficiency of the evaporator 400.

[0046] Reference Figure 9 As shown, in this embodiment of the present invention, the minimum width of the first refrigerant outlet 444 is D, satisfying: 0.5mm ≤ D ≤ 1.5mm. For example, the value of D can be 0.5mm, 0.6mm, 0.8mm, 1mm, 1.2mm, 1.5mm, etc. It is understandable that when the minimum width D of the first refrigerant outlet 444 is less than 0.5mm, the flow cross-section of the first refrigerant outlet 444 is too small, and the resistance to refrigerant passage is too great. Regardless of the refrigerant flow velocity, it is difficult to effectively discharge the refrigerant, resulting in a significant reduction in refrigerant flow efficiency. When the minimum width D of the first refrigerant outlet 444 is greater than 1.5mm, the flow cross-section of the first refrigerant outlet 444 is too large, and the refrigerant can easily pass through the first refrigerant outlet 444. This easily leads to the refrigerant being mainly distributed in the first few refrigerant channels 423, while the subsequent refrigerant channels 423 receive less refrigerant, resulting in uneven refrigerant distribution. Therefore, by reasonably designing the minimum width D of the first refrigerant outlet 444 to be within the range of 0.5mm to 1.5mm, it is possible to increase the resistance to refrigerant flow to a certain extent while also improving the uniformity of refrigerant distribution, thereby improving the heat exchange efficiency of the evaporator 400.

[0047] Continue to refer to Figure 9 As shown, in this embodiment of the present invention, the minimum flow area of ​​the second refrigerant outlet 446 is greater than or equal to the minimum flow area of ​​the first refrigerant outlet 444. If the minimum flow area of ​​the second refrigerant outlet 446 is less than that of the first refrigerant outlet 444, secondary throttling of the refrigerant is likely to occur, resulting in excessive system pressure drop. This would cause the refrigerant to evaporate prematurely at the refrigerant distribution structure 440, reducing the heat absorption capacity of the evaporator 400 and lowering the cooling effect. Therefore, by designing the minimum flow area of ​​the second refrigerant outlet 446 to be greater than or equal to that of the first refrigerant outlet 444, the secondary throttling situation can be reduced, the system pressure drop can be decreased, and it can be ensured that the refrigerant enters the refrigerant flow channel 423 before evaporation, thereby improving the heat absorption capacity of the evaporator 400 and enhancing the cooling effect.

[0048] Continue to refer to Figure 9 As shown in the embodiment of this utility model, a polar coordinate system is established on the projection plane perpendicular to the central axis of the distribution cavity 443, with the center point of the distribution cavity 443 as the pole. The ray extending from the pole along the direction of gravity is defined as the 0° line, and the angle is defined as positive in the counterclockwise direction. At least a portion of the projected outline of the first refrigerant outlet 444 lies within the region between 0° and 30° and between 330° and 360°. It should be noted that 360° is equivalent to 0°, and the region between 0° and 30° and between 330° and 360° refers to the region between the 330° ray and the 30° ray in the counterclockwise direction. The first refrigerant outlet 444 may be entirely located within the region between 330° and 30°, or a portion of the structure may be located within the region between 330° and 30°, while another portion may be located outside the region between 330° and 30°. Understandably, when the projected profile of the first refrigerant outlet 444 lies entirely outside the region between 330° and 30°, the height of the first refrigerant outlet 444 is relatively high, making it difficult to be liquid-sealed by liquid refrigerant in a short time. This results in uneven distribution of refrigerant within different refrigerant channels 423. Therefore, by rationally designing the first refrigerant outlet 444 to be located within the region between 330° and 30°, it can be ensured that the first refrigerant outlet 444 is liquid-sealed by liquid refrigerant in a short time. This increases the resistance to refrigerant flow, allowing more refrigerant to be distributed into other refrigerant channels 423, thus improving the uniformity of refrigerant distribution.

[0049] Continue to refer to Figure 9As shown, in this embodiment of the present invention, at least a portion of the projected outline of the second refrigerant outlet 446 lies within the region between 45° and 315°. It should be noted that the region between 45° and 315° refers to the area between the 45° ray and the 315° ray in a counter-clockwise direction. The second refrigerant outlet 446 may be entirely located within the region between 45° and 315°, or it may be partially located within the region between 45° and 315°, with the other part located outside the region between 45° and 315°. It is understood that when the second refrigerant outlet 446 is entirely located outside the region between 45° and 315°, the height of the second refrigerant outlet 446 is relatively low, and the distance to the first refrigerant outlet 444 is relatively close. This can easily cause the liquid refrigerant in the refrigerant loop 445 to be directly discharged through the second refrigerant outlet 446 into the refrigerant flow channel 423, preventing the liquid refrigerant from sealing the first refrigerant outlet 444 and resulting in uneven refrigerant distribution. Therefore, by rationally designing at least part of the projected profile of the second refrigerant outlet 446 to be located in the region between 45° and 315°, it is possible to ensure that the liquid refrigerant in the refrigerant loop 445 effectively seals the first refrigerant outlet 444, increases the refrigerant's resistance to flow, and allows more refrigerant to be distributed into other refrigerant channels 423, thereby improving the uniformity of refrigerant distribution.

[0050] In this embodiment of the invention, there are multiple second refrigerant outlets 446, which are spaced apart circumferentially along the refrigerant loop 445. By providing multiple second refrigerant outlets 446, the discharge efficiency of the refrigerant in the refrigerant loop 445 can be improved. Furthermore, the multiple outlets allow refrigerant to be discharged in multiple directions, ensuring sufficient heat exchange between the refrigerant and the water in the first heat exchange channel 430, resulting in higher heat exchange efficiency.

[0051] Reference Figure 3 and Figure 8 As shown in the embodiment of this utility model, the second partition 422 has a plurality of protrusions 4221 on the side facing the first partition 421. These protrusions 4221 are located within the refrigerant flow channel 423 and are spaced apart. The protrusions 4221 can be a structure where one side of the second partition 422 is recessed, causing the other side to protrude. By providing the protrusions 4221, the contact area between the refrigerant and the second partition 422 can be effectively increased. Simultaneously, the side of the second partition 422 facing away from the refrigerant flow channel 423 can also increase its contact area with water, thereby improving the heat exchange efficiency between the refrigerant and water.

[0052] Reference Figure 6 , Figure 7 and Figure 8As shown in the embodiment of this utility model, the edge of the first partition 421 is provided with a first folded edge 4211, which is bent toward the second partition 422. The edge of the second partition 422 is provided with a second folded edge 4222, which is bent toward the direction away from the first partition 421. The first folded edge 4211 is connected to the second folded edge 4222. The first folded edge 4211 and the second folded edge 4222 belonging to the same heat exchange plate group 420 constitute a surrounding edge 490. The refrigerant flow channel 423 is provided with a baffle 450 connected to the first partition 421 and the second partition 422. For example, the baffle 450 is a structure formed by protruding from the side of the first partition 421 toward the second partition 422, and the baffle 450 abuts against the second partition 422. The baffle 450 extends vertically, with its upper end connected to the first folded edge 4211 and its lower end spaced apart from the first folded edge 4211. The baffle 450 is configured to divide the refrigerant channel 423 into a first flow segment 4231 and a second flow segment 4232. The first flow segment 4231 and the second flow segment 4232 are arranged along a second direction, perpendicular to the first direction, for example, a front-to-back direction. The first flow segment 4231 and the second flow segment 4232 are connected through the gap between the lower end of the baffle 450 and the first folded edge 4211. The second refrigerant outlet 446 is located in the upper half of the first flow segment 4231. The heat exchange plate assembly 420 is provided with a third refrigerant outlet 460, which is located in the upper half of the second flow segment 4232.

[0053] Using the above scheme, the flow direction of the refrigerant in the refrigerant channel 423 can be referred to Figure 8 As shown by the dashed arrow, the refrigerant enters the first flow section 4231 through the second refrigerant outlet 446. Due to the presence of the baffle 450, the refrigerant flows downward and enters the second flow section 4232 through the gap between the baffle 450 and the first folded edge 4211. Then, the refrigerant flows upward to the third refrigerant outlet 460 and finally exits the evaporator 400. Therefore, the path traveled by the refrigerant can be effectively extended, allowing the refrigerant to have sufficient heat exchange with the water and improving heat exchange efficiency.

[0054] Reference Figure 3 , Figure 6 and Figure 8As shown, in this embodiment of the present invention, the heat exchange plate assembly 420 is further provided with a heat exchange inlet 413 and a heat exchange outlet 414. The heat exchange inlet 413 and the heat exchange outlet 414 are spaced apart in the front-to-back direction. The heat exchange inlet 413 and the heat exchange outlet 414 are connected to the first heat exchange channel 430. Therefore, water can enter the first heat exchange channel 430 through the heat exchange inlet 413 and then exit the first heat exchange channel 430 through the heat exchange outlet 414. In order to further improve the heat exchange efficiency of the refrigerant in the first heat exchange channel 430 and the refrigerant channel 423, the flow direction of the water in the first heat exchange channel 430 is opposite to the flow direction of the refrigerant in the refrigerant channel 423. This makes the temperature difference distribution between the refrigerant and the water more uniform and ensures that the water and the refrigerant always maintain a large temperature difference, resulting in higher heat exchange efficiency of the refrigerant.

[0055] Understandably, since the first heat exchange channel 430 is only formed between the heat exchange plate assemblies 420, the refrigerant channels 423 located at the left and right ends of the body 410 have a smaller area available for heat exchange. Therefore, refer to... Figure 4 , Figure 5 and Figure 10 As shown in the embodiment of this utility model, the body 410 further includes two baffles 470, one baffle 470 being connected to one end of the body 410 along the first direction, and the other baffle 470 being connected to the other end of the body 410 along the first direction. For example, the two baffles 470 are respectively connected to the left and right ends of the body 410. A second heat exchange channel 412 is formed between the baffles 470 and the body 410, and the second heat exchange channel 412 is connected to the first heat exchange channel 430. Therefore, the second heat exchange channel 412 can increase the heat exchange area of ​​the refrigerant channels 423 located at the left and right ends of the body 410, thereby improving the heat exchange efficiency.

[0056] Reference Figure 2 As shown in the embodiment of this utility model, the evaporator 400 further includes an end plate 480, which is connected to one end of the body 410, for example, to the left end of the body 410. A first refrigerant connector 481 and a second refrigerant connector 482 are spaced apart on the end plate 480. The inner cavity of the first refrigerant connector 481 communicates with the refrigerant inlet, and the inner cavity of the second refrigerant connector 482 communicates with the third refrigerant outlet 460. The first refrigerant connector 481 is used to communicate with the vent of the liquid storage tank 200, and the second refrigerant connector 482 is used to communicate with the refrigerant circuit on the liquid storage tank 200. To ensure the sealing of the connection, sealing rings can be provided on the first refrigerant connector 481 and the second refrigerant connector 482 to improve the sealing of the connection and prevent refrigerant leakage.

[0057] A thermal management system 1000 according to one embodiment of this utility model includes an evaporator 400, a compressor 500, a condenser 100, a liquid receiver 200, and an expansion valve 300 as described above. The outlet of the compressor 500 is connected to the inlet of the condenser 100, the outlet of the condenser 100 is connected to the inlet of the liquid receiver 200, the outlet of the liquid receiver 200 is connected to the inlet of the expansion valve 300, the outlet of the expansion valve 300 is connected to the distribution chamber 443 of the evaporator 400, and the third refrigerant outlet 460 of the evaporator 400 is connected to the inlet of the compressor 500.

[0058] The thermal management system 1000 of this utility model embodiment adopts the evaporator 400 of the above embodiment. The main body 410 includes multiple heat exchange plate assemblies 420, with a first heat exchange channel 430 formed between adjacent heat exchange plate assemblies 420, and a refrigerant channel 423 formed within each heat exchange plate assembly 420. A refrigerant distribution structure 440 is connected to the heat exchange plate assemblies 420. The first annular portion 441 of the refrigerant distribution structure 440 has a distribution chamber 443 and a first refrigerant outlet 444. A refrigerant loop 445 is formed between the first annular portion 441 and the second annular portion 442, and the second annular portion 442 has a second refrigerant outlet 446. Therefore, the refrigerant enters from the distribution chamber 443, enters the refrigerant loop 445 through the first refrigerant outlet 444, and then enters the refrigerant channel 423 through the second refrigerant outlet 446, thereby exchanging heat with the heat exchange medium within the first heat exchange channel 430. Since the first refrigerant outlet 444 is located below the second refrigerant outlet 446, and the refrigerant entering the distribution chamber 443 includes liquid refrigerant, some liquid refrigerant will accumulate in the refrigerant loop 445 and liquid seal the first refrigerant outlet 444. As the liquid refrigerant continues to accumulate in the refrigerant loop 445, the liquid level will gradually approach the second refrigerant outlet 446, and finally enter the refrigerant flow channel 423 through the second refrigerant outlet 446. Because the first refrigerant outlet 444 is liquid-sealed by the liquid refrigerant, the flow resistance of the first refrigerant outlet 444 increases, which slows down the flow rate of the refrigerant and reduces gas-liquid separation. Due to the increased flow resistance of the first refrigerant outlet 444, most of the refrigerant will flow along the first direction to the next refrigerant distribution structure 440, until the first refrigerant outlets 444 of all refrigerant distribution structures 440 are liquid-sealed by the liquid refrigerant. Therefore, by increasing the resistance to refrigerant flow, the refrigerant can be more evenly distributed to all refrigerant channels 423, thereby improving the heat exchange efficiency of the evaporator 400.

[0059] Since the thermal management system 1000 adopts all the technical solutions of the evaporator 400 in the above embodiments, it has at least all the beneficial effects brought about by the technical solutions in the above embodiments, which will not be repeated here.

[0060] The vehicle of one embodiment of this utility model can be an automobile or a tram, and the vehicle includes the thermal management system 1000 of the above embodiment. The vehicle of this utility model adopts the thermal management system 1000 of the above embodiment. The evaporator 400 of the thermal management system 1000 includes multiple heat exchange plate groups 420 by setting body 410. A first heat exchange flow channel 430 is formed between adjacent heat exchange plate groups 420, and a refrigerant flow channel 423 is formed within the heat exchange plate group 420. The refrigerant distribution structure 440 is connected to the heat exchange plate assembly 420. The first annular portion 441 of the refrigerant distribution structure 440 is provided with a distribution chamber 443 and a first refrigerant outlet 444. A refrigerant loop 445 is formed between the first annular portion 441 and the second annular portion 442. The second annular portion 442 is provided with a second refrigerant outlet 446. Therefore, the refrigerant enters from the distribution chamber 443, enters the refrigerant loop 445 through the first refrigerant outlet 444, and then enters the refrigerant flow channel 423 through the second refrigerant outlet 446, thereby exchanging heat with the heat exchange medium in the first heat exchange flow channel 430. Since the first refrigerant outlet 444 is located below the second refrigerant outlet 446, and the refrigerant entering the distribution chamber 443 includes liquid refrigerant, some liquid refrigerant will accumulate in the refrigerant loop 445 and liquid seal the first refrigerant outlet 444. As the liquid refrigerant continues to accumulate in the refrigerant loop 445, the liquid level will gradually approach the second refrigerant outlet 446, and finally enter the refrigerant flow channel 423 through the second refrigerant outlet 446. Because the first refrigerant outlet 444 is liquid-sealed by the liquid refrigerant, the flow resistance of the first refrigerant outlet 444 increases, which slows down the flow rate of the refrigerant and reduces gas-liquid separation. Due to the increased flow resistance of the first refrigerant outlet 444, most of the refrigerant will flow along the first direction to the next refrigerant distribution structure 440, until the first refrigerant outlets 444 of all refrigerant distribution structures 440 are liquid-sealed by the liquid refrigerant. Therefore, by increasing the resistance to refrigerant flow, the refrigerant can be more evenly distributed to all refrigerant channels 423, thereby improving the heat exchange efficiency of the evaporator 400.

[0061] Since the vehicle adopts all the technical solutions of the thermal management system 1000 of the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be repeated here.

[0062] The embodiments of the present utility model have been described in detail above with reference to the accompanying drawings. However, the present utility model is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of the present utility model.

Claims

1. An evaporator, characterized in that, include: The body includes multiple perimeters and multiple heat exchange plate assemblies arranged along a first direction. The multiple perimeters are correspondingly connected between two adjacent heat exchange plate assemblies. At least a portion of the structures of the two adjacent heat exchange plate assemblies are spaced apart within the perimeters and form a first heat exchange channel for the flow of heat exchange medium within the perimeters. The heat exchange plate assemblies are provided with a cold medium channel for the flow of cold medium, and the cold medium channel is isolated from the first heat exchange channel. Multiple refrigerant distribution structures are respectively connected to the corresponding heat exchange plate groups. Each refrigerant distribution structure includes a first annular portion and a second annular portion. The first annular portion is located inside the second annular portion and is spaced apart from the second annular portion. The first annular portion encloses a distribution cavity. The first annular portion has a first refrigerant outlet communicating with the distribution cavity. A refrigerant loop is formed between the first annular portion and the second annular portion, communicating with the first refrigerant outlet. The second annular portion has a second refrigerant outlet. The refrigerant loop communicates with the refrigerant flow channel through the second refrigerant outlet, so that the refrigerant enters the refrigerant loop in the distribution cavity through the first refrigerant outlet and is discharged to the refrigerant flow channel through the second refrigerant outlet. In the vertical direction, the first refrigerant outlet is located below the second refrigerant outlet.

2. The evaporator according to claim 1, characterized in that: The minimum width of the first refrigerant outlet is D, which satisfies: 0.5mm ≤ D ≤ 1.5mm; and / or The minimum flow area of ​​the second refrigerant outlet is greater than or equal to the minimum flow area of ​​the first refrigerant outlet.

3. The evaporator according to claim 1, characterized in that: On a projection plane perpendicular to the central axis of the distribution cavity, a polar coordinate system is established with the center of the distribution cavity as the pole. A ray extending from the pole along the direction of gravity is defined as the 0° line, and the angle is defined as positive in the counterclockwise direction. At least a portion of the projected profile of the first refrigerant outlet lies within the region between 0° and 30° or between 330° and 360°.

4. The evaporator according to claim 3, characterized in that: At least a portion of the projected profile of the second refrigerant outlet lies within the region between 45° and 315°.

5. The evaporator according to claim 1 or 4, characterized in that: There are multiple second refrigerant outlets, which are spaced apart circumferentially along the refrigerant loop.

6. The evaporator according to claim 1, characterized in that: The heat exchange plate assembly includes a first partition and a second partition connected to each other, and the refrigerant flow channel is formed between the first partition and the second partition.

7. The evaporator according to claim 6, characterized in that: The second partition has a plurality of protrusions located within the refrigerant flow channel on the side facing the first partition, and the plurality of protrusions are spaced apart.

8. The evaporator according to claim 6, characterized in that: The first partition has a first folded edge that bends toward the second partition. The first folded edge is connected to the second partition. A baffle is provided in the refrigerant channel, connecting the first partition and the second partition. The baffle extends in the vertical direction, and its upper end is connected to the first folded edge. The lower end of the baffle is spaced apart from the first folded edge. The baffle is configured to divide the refrigerant channel into a first flow segment and a second flow segment. The first flow segment and the second flow segment are connected through the gap between the lower end of the baffle and the first folded edge. The second refrigerant outlet is located in the first flow segment. The heat exchange plate assembly has a third refrigerant outlet, which is located in the second flow segment.

9. The evaporator according to claim 1, characterized in that: The body also includes two baffles, one of which is connected to one end of the body along the first direction, and the other baffle is connected to the other end of the body along the first direction. A second heat exchange channel is formed between the baffles and the body, and the second heat exchange channel is connected to the first heat exchange channel.

10. A thermal management system, characterized in that: The device includes a compressor, a condenser, a liquid receiver, an expansion valve, and an evaporator according to any one of claims 1 to 9, wherein the outlet of the compressor is connected to the inlet of the condenser, the outlet of the condenser is connected to the inlet of the liquid receiver, the outlet of the liquid receiver is connected to the inlet of the expansion valve, the outlet of the expansion valve is connected to the distribution chamber of the evaporator, and the outlet of the evaporator is connected to the inlet of the compressor.

11. The thermal management system according to claim 10, characterized in that, The compressor, the condenser, the liquid storage tank, and the evaporator are arranged and connected in sequence along the first direction, and the expansion valve is connected above the liquid storage tank.

12. A vehicle, characterized in that: Includes the thermal management system described in claim 10 or 11.

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