Intermediate heat exchanger, thermal management system, and vehicle

Abstract

An intermediate heat exchanger (100), a thermal management system (200), and a vehicle (1000). The intermediate heat exchanger (100) is a plate heat exchanger, and is provided with a hot-side opening (45), a cold-side opening (40), and a plurality of flow channels arranged in a first direction (F1); the plurality of flow channels comprise cold-side flow channels and a hot-side flow channel (32); the cold-side flow channels are communicated with the cold-side opening (40) and are used for introducing a cold-side medium; the hot-side flow channel (32) is communicated with the hot-side opening (45) and is used for introducing a hot-side medium; the number of cold-side flow channels is greater than the number of hot-side flow channels (32); the cold-side flow channels include a first cold-side flow channel (311) and a second cold-side flow channel (312), the first cold-side flow channel (311) is adjacent to the hot-side flow channel (32), and the second cold-side flow channel (312) is spaced apart from the hot-side flow channel (32).

Description

Intermediate heat exchangers, thermal management systems and vehicles

[0001] CROSS-REFERENCE TO RELATED APPLICATIONS

[0002] This application claims priority to Chinese patent applications with application numbers 202311814903.9 and 202323574170.4 filed on December 25, 2023, entitled “Intermediate heat exchanger, thermal management system and vehicle,” the entire contents of which are incorporated by reference into this application. Technical Field

[0003] The present application relates to the technical field of heat exchangers, and more particularly, to an intermediate heat exchanger, a thermal management system, and a vehicle. Background Art

[0004] In the related art, the intermediate heat exchanger has high efficiency in heat exchange, but it is difficult to simultaneously meet the requirements of heat exchange capacity, flow resistance and space compactness required by the vehicle thermal management system. Summary of the Invention

[0005] The present application aims to solve at least one of the technical problems existing in the prior art. To this end, one object of the present application is to provide an intermediate heat exchanger that meets the requirements of space compactness, reduces flow resistance, and controls the heat exchange rate within a reasonable range.

[0006] The present application also proposes a thermal management system having the above intermediate heat exchanger.

[0007] The present application also provides a vehicle having the above thermal management system.

[0008] According to the intermediate heat exchanger of an embodiment of the present application, the intermediate heat exchanger is a plate heat exchanger and has a hot side opening, a cold side opening and a plurality of flow channels arranged along a first direction, the plurality of flow channels include cold side flow channels and hot side flow channels, the cold side flow channels are connected to the cold side opening and are used to pass the cold side medium, the hot side flow channels are connected to the hot side opening and are used to pass the hot side medium, wherein the number of the cold side flow channels is greater than the number of the hot side flow channels, the cold side flow channels include a first cold side flow channel and a second cold side flow channel, the first cold side flow channel is adjacent to the hot side flow channel, and the second cold side flow channel is separated from the hot side flow channel.

[0009] According to the intermediate heat exchanger of the embodiment of the present application, the number of cold-side flow channels is greater than the number of hot-side flow channels, thereby reducing the flow resistance, and the second cold-side flow channel is separated from the hot-side flow channel, which can increase the thermal resistance to a certain extent. While reducing the flow resistance, the heat exchange amount is controlled within a reasonable range, which is beneficial to improving the temperature control capability of the thermal management system.

[0010] In addition, the intermediate heat exchanger according to the above embodiment of the present application may also have the following additional technical features:

[0011] According to some embodiments of the present application, the intermediate heat exchanger includes a heat exchanger body having the multiple flow channels, and the second cold side flow channel is located on a side of the first cold side flow channel facing away from the hot side flow channel to be separated from the hot side flow channel.

[0012] According to some embodiments of the present application, there is one first cold side flow channel; or, there are multiple first cold side flow channels, and the multiple first cold side flow channels and the hot side flow channels are arranged alternately along the first direction, wherein the second cold side flow channel is located on the side of the outermost first cold side flow channel in the first direction away from the hot side flow channel.

[0013] According to some embodiments of the present application, any of the hot-side flow channels is located between two of the first cold-side flow channels.

[0014] According to some embodiments of the present application, there is one second cold-side flow channel; or, there are multiple second cold-side flow channels, and at least two of the second cold-side flow channels are arranged continuously along the first direction.

[0015] According to some embodiments of the present application, the intermediate heat exchanger includes: a heat exchanger body, the heat exchanger body having the hot side opening, the cold side opening, a plurality of the flow channels and a connecting port, the plurality of the flow channels including the hot side flow channel and the first cold side flow channel, the connecting port being connected to the cold side opening; a bypass pipe, the bypass pipe having the second cold side flow channel, both ends of the bypass pipe being connected to the connecting port, and an insulation layer being provided between the middle portion of the bypass pipe and the heat exchanger body.

[0016] According to some embodiments of the present application, the first cold side flow channel and the hot side flow channel are alternately arranged along the first direction, wherein the flow channel closest to the bypass pipe among the multiple flow channels of the heat exchanger body is the first cold side flow channel.

[0017] According to some embodiments of the present application, the thermal insulation layer includes an air insulation layer and / or a thermal insulation material layer located between at least a portion of the bypass pipe and the heat exchanger body.

[0018] According to some embodiments of the present application, the heat exchanger body includes a mounting plate, a base plate, and a plurality of heat exchange plates arranged between the mounting plate and the base plate, the mounting plate is provided with the hot side opening and the cold side opening, and the plurality of heat exchange plates divide the space between the mounting plate and the base plate into a plurality of the flow channels.

[0019] According to some embodiments of the present application, the heat exchanger body further includes heat exchange fins, which are arranged in the flow channel of the heat exchanger body, and the density of the heat exchange fins in the hot side flow channel is greater than the density of the heat exchange fins in the cold side flow channel.

[0020] According to some embodiments of the present application, the multiple heat exchange plates include a first heat exchange plate, the hot side flow channel is located on a side of the first heat exchange plate close to the mounting plate, the second cold side flow channel is located on a side of the first heat exchange plate away from the mounting plate, and the first heat exchange plate is provided with a through hole opposite to the cold side opening and a structural reinforcement portion opposite to the hot side opening.

[0021] According to some embodiments of the present application, at least a portion of the structural reinforcement portion extends away from the mounting plate relative to the first heat exchange plate and abuts against the adjacent heat exchange plate or the bottom plate.

[0022] A thermal management system according to an embodiment of the present application includes a current collecting plate and an intermediate heat exchanger according to an embodiment of the present application, wherein the intermediate heat exchanger is mounted on the current collecting plate.

[0023] According to some embodiments of the present application, the thermal management system includes: an external heat exchanger, a cabin heat exchanger, a compressor and a throttling device, the inlet of the compressor is connected to the cold side medium outlet of the intermediate heat exchanger, one of the external heat exchanger and the cabin heat exchanger is connected to the cold side medium inlet and the hot side medium outlet of the intermediate heat exchanger, and the other is connected to the hot side medium inlet of the intermediate heat exchanger and the outlet of the compressor, and the throttling device is connected between at least one of the external heat exchanger and the cabin heat exchanger and the hot side medium outlet.

[0024] According to some embodiments of the present application, the cabin heat exchanger includes a cabin evaporator and a cabin condenser, the throttling device includes a first throttle valve and a second throttle valve, the thermal management system has a heating mode and a cooling mode, the cabin condenser is connected to the outlet of the compressor and the hot-side medium inlet, the cabin evaporator is connected to the cold-side medium inlet and the hot-side medium outlet, the external heat exchanger is connected to the outlet of the compressor and the hot-side medium inlet, the first throttle valve is connected between the hot-side medium outlet and the cabin evaporator, and the second throttle valve is connected between the hot-side medium outlet and the external heat exchanger. In the cooling mode, the compressor, the external heat exchanger, the hot-side flow path of the intermediate heat exchanger, the first throttle valve, the cabin evaporator, and the cold-side flow path of the intermediate heat exchanger are connected to form a first refrigerant circulation flow path; in the heating mode, the compressor, the cabin condenser, the hot-side flow path of the intermediate heat exchanger, the second throttle valve, the external heat exchanger, and the cold-side flow path of the intermediate heat exchanger are connected to form a second refrigerant circulation flow path.

[0025] A vehicle according to an embodiment of the present application includes a thermal management system according to an embodiment of the present application.

[0026] Additional aspects and advantages of the present application will be given in part in the description below, and in part will become obvious from the description below, or will be learned through practice of the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] The above and / or additional aspects and advantages of the present application will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0028] FIG1 is a schematic structural diagram of an intermediate heat exchanger according to an embodiment of the present application;

[0029] 2 is a cross-sectional view of the intermediate heat exchanger at the hot side opening according to the first embodiment of the present application;

[0030] 3 is a cross-sectional view of the intermediate heat exchanger at the cold side opening according to the first embodiment of the present application;

[0031] FIG4 is a schematic structural diagram of an intermediate heat exchanger according to a second embodiment of the present application;

[0032] 5 is a cross-sectional view of an intermediate heat exchanger at a hot side opening according to a third embodiment of the present application;

[0033] 6 is a cross-sectional view of an intermediate heat exchanger at a cold-side opening according to a third embodiment of the present application;

[0034] 7 is a cross-sectional view of an intermediate heat exchanger at a hot side opening according to a fourth embodiment of the present application;

[0035] 8 is a cross-sectional view of an intermediate heat exchanger at a cold-side opening according to a fourth embodiment of the present application;

[0036] FIG9 is a schematic diagram of a partial structure of a thermal management system according to an embodiment of the present application;

[0037] FIG10 is a schematic diagram of a thermal management system according to an embodiment of the present application;

[0038] FIG11 is a flow diagram of a thermal management system in cooling mode according to an embodiment of the present application;

[0039] FIG12 is a flow diagram of a thermal management system in a heating mode according to an embodiment of the present application;

[0040] FIG13 is a schematic diagram of a vehicle according to an embodiment of the present application.

[0041] Reference numerals:

[0042] Vehicles 1000;

[0043] Thermal management system 200; manifold 210; external heat exchanger 220; cabin evaporator 230; cabin condenser 240; compressor 250; first throttle valve 261; second throttle valve 262; first on-off valve 271; second on-off valve 272; third on-off valve 273; fourth on-off valve 274; fifth on-off valve 275; sixth on-off valve 276; liquid storage tank 280;

[0044] Intermediate heat exchanger 100;

[0045] Heat exchanger body 10; communication port 101; heat exchange plate 11; first heat exchange plate 111; connecting pipe 12; mounting plate 13; bottom plate 14; structural reinforcement portion 15; end plate 151; side panel 152; through hole 161;

[0046] Heat exchange fins 20;

[0047] First cold side flow channel 311; second cold side flow channel 312; hot side flow channel 32;

[0048] Cold side opening 40; cold side medium inlet 41; cold side medium outlet 42; hot side opening 45; hot side medium inlet 43; hot side medium outlet 44;

[0049] Bypass pipe 50; thermal insulation layer 52;

[0050] First direction F1; second direction F2; third direction F3. Modes for Carrying Out the Invention

[0051] The following describes in detail embodiments of the present application. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present application and are not to be construed as limiting the present application.

[0052] In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present application.

[0053] In the description of this application, "first feature" and "second feature" may include one or more such features, "plurality" means two or more, the first feature "above" or "below" the second feature may include the first and second features being in direct contact, or may include the first and second features not being in direct contact but being in contact through another feature between them, the first feature being "above", "above" and "above" the second feature includes the first feature being directly above and diagonally above the second feature, or simply means that the first feature is horizontally higher than the second feature.

[0054] With the rapid advancement of new energy vehicle technology, thermal management systems, as a key system that impacts vehicle range and passenger experience, have become a focus of technological innovation. Compactness is the core competitiveness of integrated thermal management modules for electric vehicles. Selecting a compact, efficient, and low-flow-resistance heat exchange structure is an urgent challenge to overcome.

[0055] In some related technologies, high-pressure and low-pressure fluid channels are provided in the refrigerant flow channel plate, and heat exchange is performed through a partition plate. This results in low heat exchange efficiency, large occupied space, and poor structural compactness.

[0056] Furthermore, harmful overheating can lead to a reduced temperature control capability of the thermal management system. Therefore, the compressor suction temperature must be kept within the specified range, and the heat transfer capacity of the intermediate heat exchanger must be limited. To achieve their intended purpose, the flow resistance must be as low as possible, especially on the low-pressure side. Excessive flow resistance can also lead to a reduced temperature control capability of the thermal management system. However, the intermediate heat exchangers used in related technologies typically pursue the highest heat transfer capacity possible, making it difficult to simultaneously meet the heat transfer and flow resistance requirements of automotive thermal management systems.

[0057] Based on this, the present application proposes an intermediate heat exchanger 100 and a thermal management system 200 having the intermediate heat exchanger 100. The intermediate heat exchanger 100 can increase the thermal resistance to a certain extent, while reducing the flow resistance and controlling the heat exchange amount within a reasonable range.

[0058] The intermediate heat exchanger 100 according to an embodiment of the present application will be described below with reference to the accompanying drawings.

[0059] As shown in Figures 1-8 , the intermediate heat exchanger 100 according to an embodiment of the present application can be a plate heat exchanger, and has a hot-side opening 45, a cold-side opening 40, and multiple flow channels arranged along a first direction F1. The multiple flow channels include a cold-side flow channel and a hot-side flow channel 32. The cold-side flow channel communicates with the cold-side opening 40 and is used to pass a cold-side medium, while the hot-side flow channel 32 communicates with the hot-side opening 45 and is used to pass a hot-side medium.

[0060] In this application, a plate heat exchanger serves as an intermediate heat exchanger, guiding the refrigerant liquid condensed by the condenser and the refrigerant vapor vaporized by the evaporator after absorbing heat for heat exchange, thereby increasing the degree of subcooling before the throttle valve, thereby reducing throttling losses and improving cooling efficiency. Furthermore, the intermediate heat exchanger 100 can be independent of the manifold 210, for example, using an insert-type structure and being fixed to the manifold 210 by bolts. Compared to the heat exchange structure within the refrigerant flow channel plate in related technologies, the plate heat exchanger 100 as the intermediate heat exchanger has a more efficient heat exchange capacity, can greatly reduce the plate surface size of the manifold 210, and achieve a compact spatial structure.

[0061] For example, the intermediate heat exchanger 100 may include a heat exchanger body 10 having a hot-side opening 45, a cold-side opening 40, and multiple heat exchange layers, each of which forms a flow channel. In some embodiments, the intermediate heat exchanger 100 may further include a bypass pipe 50 connected to the heat exchanger body 10, with the space within the bypass pipe 50 forming a flow channel. The flow channel can provide flow space for the heat exchange medium on the cold side and the hot side. When the hot-side flow channel 32 and the cold-side flow channel are adjacent and there is a temperature difference, heat exchange can be achieved by transferring heat.

[0062] The arrangement and number of the multiple flow channels are not limited. For example, the multiple flow channels can be stacked along the first direction F1 (the vertical direction as shown in Figure 2) as shown in Figures 2 and 3 to make the structure compact and facilitate heat exchange; or the multiple flow channels can be arranged sequentially along the second direction F2 (the front-to-back direction as shown in Figure 1) or the third direction F3 (the left-to-right direction as shown in Figure 1), or the multiple flow channels can be arranged in an array. The first direction F1, the second direction F2, and the third direction F3 intersect each other, and the intersection here includes but is not limited to being perpendicular to each other. For example, as shown in Figures 1-3, the first direction F1 is the vertical direction, the second direction F2 is the front-to-back direction, and the third direction F3 is the left-to-right direction; for another example, the first direction F1 is the vertical direction, the second direction F2 and the third direction F3 are both perpendicular to the first direction F1, and the angle between the first direction F1 and the third direction F3 is an acute angle; etc.

[0063] Among them, in the intermediate heat exchanger 100, the hot side medium with higher temperature and the cold side medium with lower temperature are refrigerants at different positions in the same refrigerant circulation loop, specifically the refrigerants at the compressor suction port side and the upstream side of the throttle valve.

[0064] In some embodiments, as shown in FIG1 , the cold-side opening 40 includes a cold-side medium inlet 41 and a cold-side medium outlet 42, and the hot-side opening 45 includes a hot-side medium inlet 43 and a hot-side medium outlet 44. Cold-side medium can enter the cold-side flow channel through the cold-side medium inlet 41 and flow out of the cold-side flow channel through the cold-side medium outlet 42; hot-side medium can enter the hot-side flow channel 32 through the hot-side medium inlet 43 and flow out of the hot-side flow channel 32 through the hot-side medium outlet 44. For example, as shown in FIG1-3 , the cold-side opening 40 and the hot-side opening 45 are arranged along a second direction F2 (the front-to-back direction as shown in FIG1 ). The cold-side opening 40 includes the cold-side medium inlet 41 and the cold-side medium outlet 42 arranged along a third direction F3 (the left-to-right direction as shown in FIG1 ), and the hot-side opening 45 includes the hot-side medium inlet 43 and the hot-side medium outlet 44 arranged along the third direction F3.

[0065] It should be noted that the arrangement order of the cold-side medium inlet 41 and the cold-side medium outlet 42, and the arrangement order of the hot-side medium inlet 43 and the hot-side medium outlet 44, can be the same or opposite. For example, as shown in Figures 1-3, the cold-side medium inlet 41 is located to the left of the cold-side medium outlet 42, and the hot-side medium inlet 43 is located to the right of the hot-side medium outlet 44. This allows the cold-side medium and the hot-side medium to flow in opposite directions in the third direction F3. This can reduce the temperature difference between the cold-side medium and the hot-side medium at corresponding locations to a certain extent, thereby facilitating the control of heat exchange within a reasonable range.

[0066] It should also be noted that the locations of the cold-side medium inlet 41, cold-side medium outlet 42, hot-side medium inlet 43, and hot-side medium outlet 44 in the first direction F1 are not limited. For example, the four openings can be located on the same side in the first direction F1, as shown in Figures 1-3, to facilitate connection between the intermediate heat exchanger 100 and structures such as the manifold 210. Alternatively, some of the four openings can be located on one side in the first direction F1, while others can be located on the other side in the first direction F1. This is also within the scope of protection of this application.

[0067] In addition, in the present application, the number of cold side flow channels is greater than the number of hot side flow channels 32. The cold side flow channels include first cold side flow channels 311 and second cold side flow channels 312, the first cold side flow channels 311 are adjacent to the hot side flow channels 32, and the second cold side flow channels 312 are spaced apart from the hot side flow channels 32.

[0068] Among them, the hot side flow channel 32 can be one or more, and the cold side flow channels are multiple and the number is greater than the hot side flow channels 32, that is, the number of cold side flow channels is increased, thereby providing more circulation space for the cold side medium, reducing the resistance to the flow of the cold side medium, and helping to improve the temperature control ability of the thermal management system 200.

[0069] The first cold side flow channel 311 is adjacent to the hot side flow channel 32, which means that the first cold side flow channel 311 and the hot side flow channel 32 are separated only by a wall surface without any other air layer, heat insulation material, etc. For example, the first cold side flow channel 311 and the hot side flow channel 32 are separated by the heat exchange plate 11, so that the cold side medium in the first cold side flow channel 311 and the hot side medium in the hot side flow channel 32 can directly exchange heat through the heat exchange plate 11.

[0070] The second cold side flow channel 312 is separated from the hot side flow channel 32, that is, the second cold side flow channel 312 and the hot side flow channel 32 are not only separated by a wall, but also provided with at least one of the structures such as the first cold side flow channel 311, an air layer, and a heat insulation material. For example, the second cold side flow channel 312 and the hot side flow channel 32 are separated by multiple heat exchange plates 11 and the first cold side flow channel 311, so that the cold side medium in the second cold side flow channel 312 and the hot side medium in the hot side flow channel 32 cannot directly exchange heat through the heat exchange plate 11.

[0071] Among them, the heat exchange amount of the cold side medium in the second cold side flow channel 312 can be different according to the setting position of the second cold side flow channel 312. For example, a first cold side flow channel 311 is provided between the second cold side flow channel 312 and the hot side flow channel 32, so that when the temperature of the cold side medium in the first cold side flow channel 311 rises, heat exchange can occur with the cold side medium in the second cold side flow channel 312 to a certain extent, but the heat exchange amount of the cold side medium in the second cold side flow channel 312 is low; for another example, an air layer and a heat insulation material are provided between the second cold side flow channel 312 and the hot side flow channel 32. In the embodiment with equal structures separated, the cold side medium in the second cold side flow channel 312 basically does not undergo heat exchange; therefore, compared with the cold side medium in the first cold side flow channel 311, the thermal resistance of the cold side medium in the second cold side flow channel 312 is increased, so that the overall heat exchange of the intermediate heat exchanger 100 is controlled within a reasonable range, and the heat exchange required by the thermal management system 200 is guaranteed by the heat exchange of the cold side medium in the first cold side flow channel 311, thereby controlling the overall heat exchange within an appropriate range, which is beneficial to improving the temperature regulation capability of the thermal management system 200.

[0072] According to the intermediate heat exchanger 100 of the embodiment of the present application, the number of cold-side flow channels is greater than the number of hot-side flow channels 32, thereby reducing the flow resistance, and the second cold-side flow channel 312 is separated from the hot-side flow channel 32, which can increase the thermal resistance to a certain extent. While reducing the flow resistance, the heat exchange amount is controlled within a reasonable range, which is beneficial to improving the temperature regulation capability of the thermal management system 200.

[0073] There are many specific ways in which the second cold-side flow channel 312 is spaced apart from the hot-side flow channel 32 , which are described in detail below with reference to the accompanying drawings.

[0074] According to some embodiments of the present application, as shown in Figures 2-6 , an intermediate heat exchanger 100 includes a heat exchanger body 10 having multiple flow channels. Specifically, all hot-side flow channels 32 and all cold-side flow channels are integrated into the heat exchanger body 10 , resulting in a highly integrated and compact structure.

[0075] Furthermore, the second cold-side flow channel 312 is located on a side of the first cold-side flow channel 311 facing away from the hot-side flow channel 32, so as to be separated from the hot-side flow channel 32. In other words, the second cold-side flow channel 312 and the hot-side flow channel 32 are separated by the first cold-side flow channel 311, eliminating the need for additional spacing structures, thereby improving structural compactness and simplifying the structure.

[0076] In the embodiment of the present application, there can be one or more first cold-side flow channels 311. For example, in an embodiment where there is only one first cold-side flow channel 311, all hot-side flow channels 32 are located on one side of the first cold-side flow channel 311, and all second cold-side flow channels 312 are located on the other side of the first cold-side flow channel 311, thereby controlling the heat exchange rate within an appropriate range and preventing excessive heat exchange.

[0077] For example, in some embodiments, as shown in Figures 2-6 , there are multiple first cold-side flow channels 311, and the multiple first cold-side flow channels 311 are arranged alternately with the hot-side flow channels 32 along the first direction F1. In other words, along the first direction F1, the flow channels are arranged in the order of one first cold-side flow channel 311 and one hot-side flow channel 32. In addition, in this alternating arrangement, the two flow channels at both ends of the first direction F1 can both be first cold-side flow channels 311, or one can be the first cold-side flow channel 311 and the other can be the hot-side flow channel 32.

[0078] The second cold-side flow channel 312 is located on a side of the outermost first cold-side flow channel 311 in the first direction F1 away from the hot-side flow channel 32 .

[0079] In an embodiment where both flow channels located at both ends of the first direction F1 are first cold-side flow channels 311, the second cold-side flow channels 312 may all be located on the same side of the alternating arrangement structure along the first direction F1, or may be partially located on one side of the alternating arrangement structure along the first direction F1 and partially located on the other side of the alternating arrangement structure along the first direction F1. In an embodiment where the flow channel located at one end of the first direction F1 is the first cold-side flow channel 311, all of the second cold-side flow channels 312 are located on one side of the first cold-side flow channel 311 that is opposite the hot-side flow channel 32. This allows the second cold-side flow channels 312 to be separated from the hot-side flow channel 32, increasing thermal resistance. The plurality of first cold-side flow channels 311 can all efficiently exchange heat with the hot-side flow channel 32, thereby meeting heat exchange efficiency and heat exchange capacity requirements, and thereby maintaining the overall heat exchange capacity of the intermediate heat exchanger 100 within an appropriate range.

[0080] For example, in the specific examples shown in Figures 2 and 3, the first cold-side flow channel 311 and the hot-side flow channel 32 are arranged alternately in the vertical direction, wherein the bottom flow channel is the first cold-side flow channel 311, and the plurality of second cold-side flow channels 312 are all located below the first cold-side flow channel 311. For example, in the specific examples shown in Figures 5 and 6, the first cold-side flow channel 311 and the hot-side flow channel 32 are arranged alternately in the vertical direction, wherein the top flow channel is the first cold-side flow channel 311, and the second cold-side flow channels 312 are located above the first cold-side flow channel 311. Of course, in other embodiments, if the structural arrangement allows, the second cold-side flow channels 312 can also be respectively arranged above and below the alternating arrangement structure, or an alternating arrangement structure can be respectively provided above and below the second cold-side flow channel 312.

[0081] In some specific embodiments, as shown in Figures 2 to 6, any hot-side flow channel 32 is located between two first cold-side flow channels 311. Both sides of each hot-side flow channel 32 can exchange heat with the first cold-side flow channel 311 to improve heat exchange efficiency. Moreover, in the alternating arrangement structure, the two flow channels at both ends are the first cold-side flow channels 311, and then among all the flow channels of the heat exchanger body 10, the two flow channels at both ends are the cold-side flow channels, thereby reducing heat loss caused by heat transfer to the outside of the intermediate heat exchanger 100 through the heat exchange plate 11, the mounting plate 13, and the bottom plate 14. For example, as shown in Figures 2 and 3, the top is the first cold-side flow channel 311 and the bottom is the second cold-side flow channel 312, and as shown in Figures 5 and 6, the top is the second cold-side flow channel 312 and the bottom is the first cold-side flow channel 311.

[0082] In some embodiments, there is one second cold side flow channel 312, which can reduce the flow resistance to a certain extent, and the second cold side flow channel 312 is located on the side of the first cold side flow channel 311 facing away from the hot side flow channel 32, which can achieve the purpose of increasing thermal resistance to control the heat exchange amount.

[0083] In other embodiments, as shown in Figures 2 and 3, there are multiple second cold-side flow channels 312, and the second cold-side flow channels 312 are arranged continuously along the first direction F1. The continuous arrangement allows at least one side of a second cold-side flow channel 312 to be adjacent to another second cold-side flow channel 312, reducing the heat exchange area between the second cold-side flow channels 312 and the first cold-side flow channels 311, which is more conducive to increasing thermal resistance and controlling the heat exchange rate within a reasonable range.

[0084] For example, as shown in Figures 2 and 3, there are two second cold side flow channels 312, of which the upper side of the second cold side flow channel 312 located above is adjacent to the first cold side flow channel 311 and performs a small amount of heat exchange, and the lower side of the second cold side flow channel 312 located above is adjacent to the second cold side flow channel 312 located below, and the heat exchange amount can be ignored, so the effect of controlling the heat exchange amount is better.

[0085] According to other embodiments of the present application, as shown in Figures 7 and 8, the intermediate heat exchanger 100 includes a heat exchanger body 10 and a bypass pipe 50. The heat exchanger body 10 has a hot-side opening 45, a cold-side opening 40, and a plurality of flow channels, wherein the plurality of flow channels include a hot-side flow channel 32 and a first cold-side flow channel 311. The number of flow channels included in the heat exchanger body 10 is less than the total number of flow channels of the intermediate heat exchanger 100. The flow channels of the heat exchanger body 10 may include only the hot-side flow channel 32 and the first cold-side flow channel 311, or may include the hot-side flow channel 32, the first cold-side flow channel 311, and the second cold-side flow channel 312 at the same time, all of which are within the scope of protection of the present application.

[0086] In addition, the heat exchanger body 10 has a communication port 101, which communicates with the cold-side opening 40. The bypass pipe 50 has a second cold-side flow channel 312, with both ends of the bypass pipe 50 connected to the communication port 101. This allows the cold-side medium flowing into the cold-side opening 40 to flow into the second cold-side flow channel 312 of the bypass pipe 50 through the communication port 101. A thermal insulation layer 52 is provided between the middle portion of the bypass pipe 50 and the heat exchanger body 10. The thermal insulation layer 52 can reduce or prevent heat transfer, thereby isolating the second cold-side flow channel 312 from the heat exchanger body 10, that is, isolating the second cold-side flow channel 312 from the hot-side flow channel 32.

[0087] Under the heat insulation effect of the heat insulation layer 52, the cold side medium flowing through the second cold side flow channel 312 does not exchange heat with the hot side medium, or the heat exchange between the cold side medium and the hot side medium flowing through the second cold side flow channel 312 is very low or even negligible.

[0088] This allows the heat exchange rate to be controlled from being excessively high, remaining within a reasonable range to meet the cooling and heating requirements of the thermal management system 200. Furthermore, compared to a heat exchanger body 10 where all flow channels are integrated, the provision of the bypass pipe 50 reduces the need for structural changes to the heat exchanger body 10 during production. Simply providing a communication port 101 on the heat exchanger body 10, such as the base plate 14, and connecting it to the bypass pipe 50 is sufficient, without requiring structural changes to other parts of the heat exchanger body 10. For intermediate heat exchangers 100 with varying heat exchange rates, only the dimensions of the communication port 101 and the bypass pipe 50 need to be modified, without affecting the structure of other parts of the heat exchanger body 10, thus reducing production costs and complexity.

[0089] The bypass pipe 50 is a closed-surface, open-ended structure that independently defines the second cold-side flow channel 312. This allows for flexible adjustment of the size and position of the second cold-side flow channel 312 and facilitates pipe sealing. The bypass pipe 50 can have a cross-sectional shape perpendicular to the flow direction, including, but not limited to, circular, square, and elliptical. Bypass pipes 50 of varying sizes can have varying cross-sectional areas or lengths along the flow direction to control heat exchange and flow resistance.

[0090] In some embodiments, as shown in Figure 8 , the bypass duct 50 includes a first extension section and two second extension sections. The first extension section extends along the arrangement direction of the two communication ports 101 (i.e., the third direction F3, or the left-right direction as shown in Figure 8 ), while the second extension section extends along the first direction F1. The first extension section is spaced apart from the heat exchange body to form an air insulation layer. The two second extension sections respectively connect the ends of the first extension section and the two communication ports 101. The connection between the bypass duct 50 and the heat exchange body may be, but is not limited to, welding, threading, or clamping.

[0091] The first extension section and the two second extension sections cooperate to form the bypass pipe 50 into a generally U-shaped structure. The second extension section enables the first extension section to be more evenly spaced apart from the heat exchange body by a predetermined gap, making the structure more compact and the heat insulation effect more uniform.

[0092] In some embodiments, as shown in Figures 7 and 8 , the first cold-side flow channels 311 and the hot-side flow channels 32 are alternately arranged along the first direction F1, thereby increasing the heat exchange efficiency between the cold-side medium in the first cold-side flow channels 311 and the hot-side medium in the hot-side flow channels 32. Among the multiple flow channels in the heat exchanger body 10, the flow channel closest to the bypass pipe 50 is the first cold-side flow channel 311. For example, the flow channel at the bottom of the heat exchanger body 10 shown in Figures 7 and 8 is the first cold-side flow channel 311. In other words, the hot-side flow channel 32 and the second cold-side flow channel 312 of the bypass pipe 50 are separated not only by the thermal insulation layer 52 but also by the first cold-side flow channel 311, which effectively reduces the heat transfer to the second cold-side flow channel 312, thereby facilitating improved accuracy in heat exchange control.

[0093] In some embodiments, the insulation layer 52 may include an air insulation layer positioned between at least a portion of the bypass tube 50 and the heat exchanger body 10. Air has a low thermal conductivity, and the air insulation layer can reduce heat transfer from the heat exchanger body 10 to the bypass tube 50, thereby reducing heat exchange with the cold-side medium within the bypass tube 50 and effectively increasing thermal resistance. Furthermore, by controlling the dimension of the air insulation layer along the first direction F1, the heat transfer from the heat exchanger body 10 to the bypass tube 50 can be controlled, thereby controlling the heat exchange rate and improving heat exchange control flexibility.

[0094] In some embodiments, the thermal insulation layer 52 may include a layer of thermal insulation material positioned between at least a portion of the bypass pipe 50 and the heat exchanger body 10. The thermal insulation material layer provides excellent thermal insulation and occupies little space, thereby making the overall structure of the intermediate heat exchanger 100 more compact. For example, the thermal insulation material layer may be made of fiberglass, asbestos, or a metal having a lower thermal conductivity than the bottom plate 14 of the heat exchanger body 10.

[0095] It should be noted that a heat insulation material layer and an air heat insulation layer can be provided at the same time, which can further improve the heat insulation effect and the accuracy of heat exchange control.

[0096] The heat exchanger body 10 according to some embodiments of the present application will be described below with reference to the accompanying drawings.

[0097] In some embodiments of the present application, as shown in Figures 2-8 , a heat exchanger body 10 includes a mounting plate 13, a base plate 14, and multiple heat exchange plates 11 disposed between the mounting plate 13 and the base plate 14. The mounting plate 13 is provided with a hot-side opening 45 and a cold-side opening 40. The multiple heat exchange plates 11 divide the space between the mounting plate 13 and the base plate 14 into multiple flow channels. The heat exchanger body 10 is formed as a plate heat exchanger, with the flow channels of the heat exchanger body 10 forming heat exchange layers. This provides a large heat exchange area between adjacent heat exchange layers, resulting in higher heat exchange efficiency and a more compact structure.

[0098] In some embodiments, as shown in Figures 2-8 , the heat exchanger body 10 further includes heat exchange fins 20, which are disposed within the flow channel of the heat exchanger body 10. The heat exchange fins 20 can increase the heat exchange area between the heat exchange plates 11 and the heat exchange medium, thereby improving heat exchange efficiency and preventing the heat exchange amount from being too low and affecting the temperature control capability of the thermal management system 200.

[0099] The greater the density of the heat exchange fins 20, the stronger the high pressure resistance and the greater the flow resistance; and the pressure of the hot side medium is greater than the pressure of the cold side medium, the hot side medium is not sensitive to flow resistance, and the cold side medium is very sensitive to flow resistance. Therefore, the hot side medium is provided with heat exchange fins 20 with a higher density in the hot side flow channel 32 to obtain a greater pressure resistance, and at the same time, the cold side medium is provided with heat exchange fins 20 with a lower density in the cold side flow channel to obtain a lower flow resistance, thereby reducing the overall flow resistance of the intermediate heat exchanger 100 and improving the pressure resistance.

[0100] The density of the heat exchange fins 20 refers to the size of the space occupied by the substantial portion of the heat exchange fins 20 per unit space, that is, the volume of the heat exchange fins 20 per unit space. The heat exchange fins 20 include a plurality of fins extending along a first direction F1 and arranged along a second direction F2 and a third direction F3. The density of the heat exchange fins 20 can be adjusted by adjusting the fin thickness, fin width, number of fins, and fin spacing. The greater the fin thickness, the greater the density of the heat exchange fins 20; the greater the fin width, the greater the density of the heat exchange fins 20; the greater the number of fins, the greater the density of the heat exchange fins 20; and the smaller the fin spacing, the greater the density of the heat exchange fins 20.

[0101] For example, in some embodiments, the thickness of the heat exchange fins 20 in the hot side flow channel 32 along the second direction F2 is greater than the thickness of the fins of the heat exchange fins 20 in the cold side flow channel along the second direction F2; in some embodiments, the distance between two adjacent fins of the heat exchange fins 20 in the hot side flow channel 32 is less than the distance between two adjacent fins of the heat exchange fins 20 in the cold side flow channel.

[0102] This can make the density of the heat exchange fins 20 in the hot side flow channel 32 greater than the density of the heat exchange fins 20 in the cold side flow channel, thereby meeting the dual requirements of pressure resistance and low flow resistance.

[0103] According to some embodiments of the present application, as shown in Figures 2 to 4, the multiple heat exchange plates 11 include a first heat exchange plate 111, the hot side flow channel 32 is located on the side of the first heat exchange plate 111 close to the mounting plate 13, and the second cold side flow channel 312 is located on the side of the first heat exchange plate 111 away from the mounting plate 13. The first cold side flow channel 311 can be located on the side of the first heat exchange plate 111 close to the mounting plate 13, and can also be arranged on the side of the first heat exchange plate 111 close to the bottom plate 14.

[0104] Since the second cold side flow channel 312 is located on the side of the first heat exchange plate 111 away from the mounting plate 13 , a through hole 161 opposite to the cold side opening 40 is provided on the first heat exchange plate 111 so that the cold side medium can flow into the second cold side flow channel 312 through the through hole 161 .

[0105] Since the hot side flow channels 32 are all located on the side of the first heat exchange plate 111 close to the mounting plate 13, the area on the first heat exchange plate 111 opposite to the hot side opening 45 does not need to be provided with a hole for the hot side medium to pass through. In addition, the pressure of the hot side medium is greater than that of the cold side medium. Therefore, as shown in Figure 4, the first heat exchange plate 111 is provided with a structural reinforcement 15 opposite to the hot side opening 45. The structural reinforcement 15 can enhance the structural strength of the first heat exchange plate 111 and the pressure resistance of the area where it is located, so that the hot side medium flowing into the hot side opening 45 directly impacts the structural reinforcement 15 with greater structural strength, thereby reducing the impact force on the structures in other areas and improving the overall pressure resistance. While meeting the pressure resistance requirements, the structures in other areas can adopt a structure with a strength lower than the structural reinforcement 15, for example, a lower density structure such as a flat plate structure, so as to reduce the flow resistance and improve the temperature control capability of the thermal management system 200.

[0106] In some embodiments, as shown in FIG4 , the structural reinforcement portion 15 at least partially extends away from the mounting plate 13 relative to the first heat exchange plate 111. In embodiments where another heat exchange plate 11 (referred to as a second heat exchange plate) is disposed between the first heat exchange plate 111 and the bottom plate 14, the structural reinforcement portion 15 may abut against the adjacent second heat exchange plate. In embodiments where the first heat exchange plate 111 is adjacent to the bottom plate 14, the structural reinforcement portion 15 abuts against the adjacent bottom plate 14. The adjacent and mutually abutting second heat exchange plate or bottom plate 14 can support the structural reinforcement portion 15, increasing the overall thickness of the plate in the area opposite the hot-side opening 45, thereby providing structural reinforcement.

[0107] It should be noted that in the embodiment where the structural reinforcement portion 15 abuts against the adjacent second heat exchange plate or bottom plate 14, the structural reinforcement portion 15 and the adjacent second heat exchange plate or bottom plate 14 may be in contact with each other or may be welded together, etc. Among them, the welded connection is more effective in improving the structural strength and can play a limiting role in the direction perpendicular to the first direction F1, thereby improving the overall durability.

[0108] In some specific embodiments, the thickness of the bottom plate 14 is greater than the thickness of the heat exchange plate 11 , and the structural reinforcement effect of the abutment between the structural reinforcement portion 15 and the bottom plate 14 is better.

[0109] In some specific embodiments, as shown in Figure 4 , the thickness of the second heat exchange plate along the first direction F1 is 0.3 mm to 0.6 mm. For example, the thickness of the second heat exchange plate along the first direction F1 can be 0.3 mm, 0.4 mm, 0.5 mm, 0.6 mm, etc. If the thickness of the second heat exchange plate is too small, the second heat exchange plate will have a weaker structural reinforcement effect on the structural reinforcement portion 15 and its own pressure resistance will be too weak. If the thickness of the second heat exchange plate is too large, it will occupy too much space and increase costs. Within the above thickness range, the second heat exchange plate has good pressure resistance and structural reinforcement effect on the structural reinforcement portion 15, which is conducive to a compact structure and reduced costs.

[0110] In the embodiment of the present application, the specific structure of the structural reinforcement portion 15 can be flexibly set, for example, it can be a boss, a rib, a bent structure, etc.

[0111] For example, in some embodiments, as shown in FIG4 , the structural reinforcement portion 15 includes an end plate 151 and a side panel 152. One end of the side panel 152 along the first direction F1 (the upper end as shown in FIG4 ) is connected to the periphery of the end plate 151, and the other end of the side panel 152 along the first direction F1 (the lower end as shown in FIG4 ) is connected to the rest of the first heat exchange plate 111. The structural reinforcement portion 15 is generally formed as a boss structure, which is simple and easy to manufacture. For example, the rest of the first heat exchange plate 111 and the structural reinforcement portion 15 can be formed from a single flat plate through sheet metal deformation processing, resulting in high manufacturing efficiency.

[0112] Furthermore, in the embodiment where the structural reinforcement 15 abuts the base plate 14, the end plate 151 abuts the adjacent base plate 14; and in the embodiment where the structural reinforcement 15 abuts the adjacent second heat exchange plate, the end plate 151 abuts the adjacent second heat exchange plate. As a result, the end plate 151 faces the hot-side opening 45, and the end plate 151 and the adjacent base plate 14 or second heat exchange plate can abut over a large area. This significantly increases the thickness of the plate in the area facing the hot-side opening 45, and the area of ​​the thickened area can be sufficiently large, making the structural reinforcement 15 itself less susceptible to deformation, improving pressure resistance uniformity, and enhancing compactness.

[0113] In some specific embodiments, as shown in FIG5 , the thickness of the end plate 151 along the first direction F1 is 0.3 mm to 0.6 mm. For example, the thickness of the end plate 151 along the first direction F1 can be 0.3 mm, 0.4 mm, 0.5 mm, 0.6 mm, etc. If the thickness of the end plate 151 is too small, the structural reinforcement effect and pressure resistance of the end plate 151 will be weak; if the thickness of the end plate 151 is too large, the cost will increase. Within the above thickness range, the end plate 151 has good pressure resistance and structural reinforcement effect, and is conducive to reducing costs.

[0114] As shown in Figures 9-12, the thermal management system 200 disclosed in the embodiment of the present application includes a manifold 210 and an intermediate heat exchanger 100 disclosed in the embodiment of the present application, with the intermediate heat exchanger 100 mounted on the manifold 210. A plate heat exchanger serves as the intermediate heat exchanger 100 and is integrated into the manifold 210, independent of the flow path of the manifold 210. It can adopt an insertable structure and be fixed to the manifold 210 by bolts. Compared to the heat exchange structure within the refrigerant flow channel plate in related technologies, the intermediate heat exchanger 100 has more efficient heat exchange capacity, can significantly reduce the plate surface size of the manifold 210, and achieve a compact spatial structure.

[0115] In addition, since the intermediate heat exchanger 100 according to the embodiment of the present application has the above-mentioned beneficial technical effects, the thermal management system 200 according to the embodiment of the present application has good spatial compactness, and the number of cold side flow channels is greater than the number of hot side flow channels 32, which reduces the flow resistance, and the second cold side flow channel 312 is separated from the hot side flow channel 32, which can increase the thermal resistance to a certain extent. While reducing the flow resistance, the heat exchange amount is controlled within a reasonable range, which is beneficial to improving the temperature regulation ability of the thermal management system 200.

[0116] In some embodiments, as shown in FIG10 , a thermal management system 200 includes an external heat exchanger 220, a cabin heat exchanger, a compressor 250, and a throttle device. The inlet of the compressor 250 is connected to the cold-side medium outlet 42 of the intermediate heat exchanger 100. One of the external heat exchanger 220 and the cabin heat exchanger is connected to the cold-side medium inlet 41 and the hot-side medium outlet 44 of the intermediate heat exchanger 100. The other of the external heat exchanger 220 and the cabin heat exchanger is connected to the hot-side medium inlet 43 of the intermediate heat exchanger 100 and the outlet of the compressor 250. The throttle device is connected between at least one of the external heat exchanger 220 and the cabin heat exchanger and the hot-side medium outlet 44.

[0117] The external heat exchanger 220 can exchange heat with the external environment outside the cabin, and the cabin heat exchanger can exchange heat with the environment inside the cabin. The compressor 250 is used to drive the flow of the heat exchange medium in the circuit to achieve heat exchange between the cabin and the external environment through the circulation of the heat exchange medium.

[0118] One of the external heat exchanger 220 and the cabin heat exchanger is formed as a condenser, and the other is formed as an evaporator. By installing an intermediate heat exchanger 100 between the condenser and the evaporator in the circulation loop, the intermediate heat exchanger 100 guides the refrigerant liquid condensed by the condenser and the refrigerant vapor evaporated by the evaporator after absorbing heat to exchange heat, thereby increasing the subcooling degree before the throttling device, thereby reducing throttling losses and improving cooling efficiency.

[0119] 10 , in some embodiments, the cabin heat exchanger includes a cabin evaporator 230 and a cabin condenser 240, and the throttling device includes a first throttle valve 261 and a second throttle valve 262. The cabin condenser 240 is connected to the outlet of the compressor 250 and the hot-side medium inlet 43, the cabin evaporator 230 is connected to the cold-side medium inlet 41 and the hot-side medium outlet 44, the external heat exchanger 220 is connected to the outlet of the compressor 250 and the hot-side medium inlet 43, the first throttle valve 261 is connected between the hot-side medium outlet 44 and the external heat exchanger 220, and the second throttle valve 262 is connected between the hot-side medium outlet 44 and the cabin evaporator 230.

[0120] Thus, the cabin evaporator 230 and the cabin condenser 240 are connected to different openings of the intermediate heat exchanger 100 through different branches, and by providing two throttle valves, the flow paths of the refrigerant in the cabin heat exchanger and the external heat exchanger 220 can be switched, thereby achieving functional switching.

[0121] Specifically, thermal management system 200 has a heating mode and a cooling mode. As shown in FIG11 , in cooling mode, compressor 250, external heat exchanger 220, hot-side flow path 32 of intermediate heat exchanger 100, first throttle valve 261, cabin evaporator 230, and the cold-side flow path of intermediate heat exchanger 100 are connected to form a first refrigerant circulation path.

[0122] The compressor 250 performs work, driving the refrigerant to flow through the external heat exchanger 220, the intermediate heat exchanger 100, the first throttle valve 261, the cabin evaporator 230, the intermediate heat exchanger 100 in sequence, and finally returns to the compressor 250; at this time, the external heat exchanger 220 acts as a condenser to release heat to the air, and the cabin evaporator 230 works to absorb heat in the cabin, thereby cooling the cabin; the high-temperature and high-pressure liquid refrigerant flowing out of the external heat exchanger 220 enters the intermediate heat exchanger 100 through the hot-side medium inlet 43, and the low-temperature and low-pressure gaseous refrigerant at the evaporator outlet enters the intermediate heat exchanger 100 through the cold-side medium inlet 41. The refrigerants in the two states exchange heat in the intermediate heat exchanger 100, thereby realizing heat recovery heat exchange between the supercooled refrigerant and the superheated refrigerant in the cooling mode, improving the subcooling degree before the first throttle valve 261, thereby reducing throttling losses and improving cooling efficiency.

[0123] As shown in FIG12 , in the heating mode, the compressor 250 , the cabin condenser 240 , the hot-side flow path 32 of the intermediate heat exchanger 100 , the second throttle valve 262 , the external heat exchanger 220 , and the cold-side flow path of the intermediate heat exchanger 100 are connected to form a second refrigerant circulation path.

[0124] Compressor 250 operates, driving the refrigerant through cabin condenser 240, intermediate heat exchanger 100, second throttle valve 262, external heat exchanger 220, intermediate heat exchanger 100, and finally back to compressor 250. At this point, external heat exchanger 220 acts as an evaporator, absorbing heat from the air, while cabin condenser 240 operates to release heat to the cabin, thereby warming the cabin. The high-temperature, high-pressure liquid refrigerant flowing out of cabin condenser 240 enters intermediate heat exchanger 100 through hot-side medium inlet 43, while the low-temperature, low-pressure gaseous refrigerant exiting external heat exchanger 220 enters intermediate heat exchanger 100 through cold-side medium inlet 41. The two refrigerants exchange heat within intermediate heat exchanger 100, achieving heat recovery between the supercooled and superheated refrigerants in heating mode. This increases the degree of subcooling before second throttle valve 262, thereby reducing throttling losses and improving cooling efficiency.

[0125] In some embodiments, as shown in Figures 10-12 , the thermal management system 200 may further include a liquid storage tank 280, a first on-off valve 271, a second on-off valve 272, a third on-off valve 273, a fourth on-off valve 274, a fifth on-off valve 275, and a sixth on-off valve 276. The outlet of the liquid storage tank 280 is connected to the hot-side medium inlet 43 of the intermediate heat exchanger 100, and the outlet of the cabin condenser 240 and the outlet of the external heat exchanger 220 are both connected to the inlet of the liquid storage tank 280. The external heat exchanger 220 has a first connection end and a second connection end.

[0126] The first on-off valve 271 is connected between the outlet of the compressor 250 and the inlet of the cabin condenser 240, the second on-off valve 272 is connected between the outlet of the compressor 250 and the first connection end of the external heat exchanger 220, the third on-off valve 273 is connected between the outlet of the cabin condenser 240 and the inlet of the liquid storage tank 280, the fourth on-off valve 274 is connected between the second connection end of the external heat exchanger 220 and the inlet of the liquid storage tank 280, the fifth on-off valve 275 is connected between the first connection end of the external heat exchanger 220 and the cold side medium inlet 41 of the intermediate heat exchanger 100, and the sixth on-off valve 276 is connected between the outlet of the cabin evaporator 230 and the cold side medium inlet 41 of the intermediate heat exchanger 100.

[0127] In the cooling mode, as shown in Figure 11, the first on-off valve 271, the third on-off valve 273, the fifth on-off valve 275 and the second throttle valve 262 are disconnected, and the second on-off valve 272, the fourth on-off valve 274, the sixth on-off valve 276 and the first throttle valve 261 are connected; in the heating mode, as shown in Figure 12, the first on-off valve 271, the third on-off valve 273, the fifth on-off valve 275 and the second throttle valve 262 are connected, and the second on-off valve 272, the fourth on-off valve 274, the sixth on-off valve 276 and the first throttle valve 261 are disconnected, thereby realizing mode switching and simple control.

[0128] As shown in Figure 13, the vehicle 1000 disclosed in the embodiment of the present application includes the thermal management system 200 disclosed in the embodiment of the present application. Due to the aforementioned beneficial technical effects of the thermal management system 200 according to the embodiment of the present application, the vehicle 1000 according to the embodiment of the present application has good spatial compactness. The number of cold-side flow channels is greater than the number of hot-side flow channels 32, which reduces flow resistance. The second cold-side flow channel 312 is separated from the hot-side flow channel 32, which can increase thermal resistance to a certain extent. While reducing flow resistance, the heat exchange amount is controlled within a reasonable range, which is conducive to improving the temperature control capability of the thermal management system 200.

[0129] The thermal management system 200 disclosed in the embodiments of the present application can be used in a device requiring the thermal management system 200 or a control system of the thermal management system 200. The device can be, but is not limited to, a vehicle, a ship, a spacecraft, etc. The spacecraft can include, for example, an airplane, a rocket, a space shuttle, and a spacecraft.

[0130] Among them, vehicle 1000 can be a new energy vehicle. In some embodiments, the new energy vehicle can be a pure electric vehicle with an electric motor as the main driving force. In other embodiments, the new energy vehicle can also be a hybrid electric vehicle or an extended-range vehicle with an internal combustion engine and an electric motor as the main driving force. Regarding the internal combustion engine and the electric motor mentioned in the above embodiments that provide driving power for the new energy vehicle, the internal combustion engine can use gasoline, diesel, hydrogen, etc. as fuel, and the way to provide electrical energy to the electric motor can use power batteries, hydrogen fuel cells, etc., and no special limitation is made here. It should be noted that this is only an exemplary description of the structure of new energy vehicles, etc., and is not intended to limit the scope of protection of this application.

[0131] In some embodiments, the thermal management system 200 is an important component for regulating the vehicle cabin environment (temperature, humidity, etc.) and the working environment of other components. The thermal management system 200 mainly includes: valves, heat exchangers, compressors and pumps, such as electronic water pumps or other water pumps. The thermal management system 200 has a circulating refrigerant, which can be Freon, propane, etc.

[0132] The following describes in detail a thermal management system 200 according to a specific embodiment of the present application with reference to the accompanying drawings. It should be understood that the following description is merely illustrative and should not be construed as limiting the application.

[0133] As shown in Figures 1 to 3 and 9, the thermal management system 200 includes a collecting plate 210 and an intermediate heat exchanger 100. The four connecting pipes 12 of the intermediate heat exchanger 100 are arranged on the same side of the heat exchanger body 10 in the up and down directions, so that the intermediate heat exchanger 100 can be independent of the collecting plate 210. The connecting pipes 12 adopt an insert-type structure to achieve pipeline connection, and a sealing ring is used to test the sealing. The intermediate heat exchanger 100 is fixed to the collecting plate 210 by fasteners to achieve structural integration, which can greatly reduce the plate surface size of the collecting plate 210 and achieve a compact structure.

[0134] The intermediate heat exchanger 100 includes a heat exchanger body 10 and a plurality of heat exchange fins 20. The heat exchanger body 10 includes a mounting plate 13, a bottom plate 14 located below the mounting plate 13, a plurality of heat exchange plates 11 located between the mounting plate 13 and the bottom plate 14, and four connecting pipes 12 provided on the mounting plate 13. The four connecting pipes 12 respectively define a cold side medium inlet 41, a cold side medium outlet 42, a hot side medium inlet 43, and a hot side medium outlet 44.

[0135] Multiple heat exchange plates 11 are stacked vertically, dividing the space between the mounting plate 13 and the base plate 14 into seven heat exchange layers. Each heat exchange layer forms a flow channel, within which heat exchange fins 20 are located. The seven flow channels include two hot-side flow channels 32, three first cold-side flow channels 311, and two second cold-side flow channels 312. The three first cold-side flow channels 311 and the two hot-side flow channels 32 are arranged alternately vertically, with each hot-side flow channel 32 located between two first cold-side flow channels 311. The two second cold-side flow channels 312 are arranged vertically and continuously below the lowest first cold-side flow channel 311. The cold-side medium inlet 41 and the cold-side medium outlet 42 are respectively connected to the cold-side flow channels, while the hot-side medium inlet 43 and the hot-side medium outlet 44 are respectively connected to the hot-side flow channels 32.

[0136] In the above embodiment, the number of cold-side flow channels is greater than the number of hot-side flow channels 32, and the second cold-side flow channel 312 is not directly adjacent to the hot-side flow channel 32, but is separated by the first cold-side flow channel 311. This prevents the cold-side medium in the second cold-side flow channel 312 from participating in heat exchange, or, although the cold-side medium in the second cold-side flow channel 312 participates in heat exchange, the heat exchange effect is reduced due to the large thermal resistance, thereby controlling the heat exchange rate within a reasonable range. Thus, the second cold-side flow channel 312 regulates the heat exchange rate and reduces the flow resistance, meeting the heat exchange range and low flow resistance requirements of the thermal management system 200 while ensuring high pressure resistance.

[0137] Other structures and operations of the thermal management system 200 and the vehicle 1000 according to the embodiment of the present application are well known to those skilled in the art and will not be described in detail here.

[0138] In the description of this application, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood in a broad sense. For example, they can refer to fixed connections, detachable connections, or integral connections; mechanical connections or electrical connections; direct connections or indirect connections through an intermediate medium; and internal connections between two components. Those skilled in the art will understand the specific meanings of the above terms in this application based on the specific circumstances.

[0139] Throughout this specification, reference to terms such as "embodiment," "specific embodiment," and "example" means that the specific features, structures, materials, or characteristics described in conjunction with that embodiment or example are included in at least one embodiment or example of the present application. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

[0140] Although the embodiments of the present application have been shown and described, those skilled in the art will appreciate that various changes, modifications, substitutions, and variations may be made to the embodiments without departing from the principles and intent of the present application, and that the scope of the present application is defined by the claims and their equivalents.

Claims

1. An intermediate heat exchanger, wherein, The intermediate heat exchanger is a plate heat exchanger and has a hot-side opening, a cold-side opening, and a plurality of flow channels arranged in a first direction. The plurality of flow channels include cold-side flow channels and hot-side flow channels. The cold-side flow channels are in communication with the cold-side opening and are used for introducing a cold-side medium, and the hot-side flow channels are in communication with the hot-side opening and are used for introducing a hot-side medium. Among them, the number of the cold-side flow channels is greater than the number of the hot-side flow channels. The cold-side flow channels include a first cold-side flow channel and a second cold-side flow channel. The first cold-side flow channel is adjacent to the hot-side flow channel, and the second cold-side flow channel is spaced apart from the hot-side flow channel.

2. The intermediate heat exchanger according to claim 1, wherein, The intermediate heat exchanger includes a heat exchanger body. The heat exchanger body has the plurality of flow channels. The second cold-side flow channel is located on a side of the first cold-side flow channel facing away from the hot-side flow channel to be spaced apart from the hot-side flow channel.

3. The intermediate heat exchanger according to claim 2, wherein, the first cold-side flow channel is one; or, the first cold-side flow channels are multiple, and the multiple first cold-side flow channels and the hot-side flow channels are alternately arranged in the first direction. Among them, the second cold-side flow channel is located on a side of the outermost first cold-side flow channel in the first direction facing away from the hot-side flow channel.

4. The intermediate heat exchanger according to claim 3, wherein, Any one of the hot-side flow channels is located between two of the first cold-side flow channels.

5. The intermediate heat exchanger according to any one of claims 2-4, wherein, the second cold-side flow channel is one; or, the second cold-side flow channels are multiple, and the second cold-side flow channels are continuously arranged in the first direction.

6. The intermediate heat exchanger according to any one of claims 1-5, wherein, The intermediate heat exchanger includes: a heat exchanger body, the heat exchanger body having the hot-side opening, the cold-side opening, the plurality of flow channels, and a communication port. The plurality of flow channels include the hot-side flow channels and the first cold-side flow channels. The communication port is in communication with the cold-side opening; a bypass pipe, the bypass pipe having the second cold-side flow channel. Both ends of the bypass pipe are connected to the communication port, and a heat insulation layer is provided between the middle part of the bypass pipe and the heat exchanger body.

7. The intermediate heat exchanger according to claim 6, wherein, The first cold-side flow channels and the hot-side flow channels are alternately arranged in the first direction. Among the plurality of flow channels of the heat exchanger body, the flow channel closest to the bypass pipe is the first cold-side flow channel.

8. The intermediate heat exchanger according to claim 6 or 7, wherein, The heat insulation layer includes an air heat insulation layer and / or a heat insulation material layer located between at least a part of the bypass pipe and the heat exchanger body.

9. The intermediate heat exchanger according to any one of claims 2-8, wherein, The heat exchanger body includes a mounting plate, a bottom plate, and a plurality of heat exchange plates provided between the mounting plate and the bottom plate. The mounting plate is provided with the hot-side opening and the cold-side opening. The plurality of heat exchange plates divide the space between the mounting plate and the bottom plate into the plurality of flow channels.

10. The intermediate heat exchanger according to claim 9, wherein, The heat exchanger body further includes heat exchange fins. The heat exchange fins are provided in the flow channels of the heat exchanger body. The density of the heat exchange fins in the hot-side flow channels is greater than the density of the heat exchange fins in the cold-side flow channels.

11. The intermediate heat exchanger according to claim 9 or 10, wherein, A plurality of the heat exchange plates include a first heat exchange plate. The hot-side flow channel is located on a side of the first heat exchange plate close to the mounting plate, and the second cold-side flow channel is located on a side of the first heat exchange plate away from the mounting plate. The first heat exchange plate is provided with a through hole opposite to the cold-side opening and a structural strengthening portion opposite to the hot-side opening.

12. The intermediate heat exchanger according to claim 11, wherein, The structural strengthening portion at least partially extends away from the mounting plate relative to the first heat exchange plate and abuts against an adjacent heat exchange plate or the bottom plate.

13. A thermal management system, wherein, It includes a manifold plate and an intermediate heat exchanger according to any one of claims 1-12, and the intermediate heat exchanger is mounted on the manifold plate.

14. The thermal management system according to claim 13, wherein, It includes: An external heat exchanger, a cabin heat exchanger, a compressor, and a throttling device. The inlet of the compressor is connected to the cold-side medium outlet of the intermediate heat exchanger. One of the external heat exchanger and the cabin heat exchanger is connected to the cold-side medium inlet and the hot-side medium outlet of the intermediate heat exchanger, and the other is connected to the hot-side medium inlet of the intermediate heat exchanger and the outlet of the compressor. The throttling device is connected between at least one of the external heat exchanger and the cabin heat exchanger and the hot-side medium outlet.

15. The thermal management system according to claim 14, wherein, The cabin heat exchanger includes a cabin evaporator and a cabin condenser. The throttling device includes a first throttle valve and a second throttle valve. The thermal management system has a heating mode and a cooling mode. The cabin condenser is connected to the outlet of the compressor and the hot-side medium inlet. The cabin evaporator is connected to the cold-side medium inlet and the hot-side medium outlet. The external heat exchanger is connected to the outlet of the compressor and the hot-side medium inlet. The first throttle valve is connected between the hot-side medium outlet and the cabin evaporator. The second throttle valve is connected between the hot-side medium outlet and the external heat exchanger. In the cooling mode, the compressor, the external heat exchanger, the hot-side flow channel of the intermediate heat exchanger, the first throttle valve, the cabin evaporator, and the cold-side flow channel of the intermediate heat exchanger are connected and form a first refrigerant circulation flow path; in the heating mode, the compressor, the cabin condenser, the hot-side flow channel of the intermediate heat exchanger, the second throttle valve, the external heat exchanger, and the cold-side flow channel of the intermediate heat exchanger are connected and form a second refrigerant circulation flow path.

16. A vehicle, wherein, It includes a thermal management system according to any one of claims 13-15.

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