Intermediate heat exchanger, heat management system and vehicle

Abstract

The invention discloses an intermediate heat exchanger, a heat management system and a vehicle, the intermediate heat exchanger is provided with a hot side opening, a cold side opening and a plurality of runners arranged in the first direction, the multiple runners comprise the cold side runner and the hot side runner, the cold side runner communicates with the cold side opening and is used for introducing a cold side medium, and the hot side runner communicates with the cold side opening and is used for introducing a hot side medium; the hot side flow channels are communicated with the hot side opening and used for introducing a hot side medium, the number of the cold side flow channels is larger than that of the hot side flow channels, the cold side flow channels comprise first cold side flow channels and second cold side flow channels, the first cold side flow channels are adjacent to the hot side flow channels, and the second cold side flow channels are spaced from the hot side flow channels. According to the intermediate heat exchanger, the number of the cold side flow channels is larger than that of the hot side flow channels, the flow resistance is reduced, the second cold side flow channels are separated from the hot side flow channels, the heat resistance can be increased to a certain extent, the heat exchange amount is controlled within a reasonable range while the flow resistance is reduced, and the temperature adjusting capacity of a heat management system is improved.

Description

Technical Field

[0001] The present invention 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

[0002] In the related art, the intermediate heat exchanger has high heat exchange capacity, but it is difficult to simultaneously meet the requirements of heat exchange amount, flow resistance, and space compactness required by the vehicle thermal management system. Summary of the Invention

[0003] The present invention aims to at least solve one of the technical problems existing in the prior art. To this end, an object of the present invention is to provide an intermediate heat exchanger that meets the requirements of space compactness, reduces flow resistance, and controls the heat exchange amount within a reasonable range.

[0004] The present invention also provides a thermal management system having the above intermediate heat exchanger.

[0005] The present invention further provides a vehicle having the above thermal management system.

[0006] According to an embodiment of the present invention, 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. 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 spaced apart from the hot side flow channel.

[0007] According to an embodiment of the present invention, by making the number of the cold side flow channels greater than the number of the hot side flow channels, the flow resistance is reduced, and the second cold side flow channel is spaced apart 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 regulation ability of the thermal management system.

[0008] In addition, the intermediate heat exchanger according to the above embodiment of the present invention may further have the following additional technical features:

[0009] According to some embodiments of the present invention, the intermediate heat exchanger includes a heat exchanger body having 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.

[0010] According to some embodiments of the present invention, the first cold-side flow channel is one; alternatively, the first cold-side flow channels are multiple, and the multiple first cold-side flow channels and the hot-side flow channel are arranged alternately along the first direction, wherein the second cold-side flow channel is located on a side of the first cold-side flow channel that is the outermost in the first direction and away from the hot-side flow channel.

[0011] According to some embodiments of the present invention, any of the hot-side flow channels is located between two of the first cold-side flow channels.

[0012] According to some embodiments of the present invention, the second cold-side flow channel is one; alternatively, the second cold-side flow channels are multiple, and at least two of the second cold-side flow channels are arranged continuously along the first direction.

[0013] According to some embodiments of the present invention, the intermediate heat exchanger includes: a heat exchanger body having the hot-side opening, the cold-side opening, multiple flow channels, and a communication port, the multiple flow channels including the hot-side flow channel and the first cold-side flow channel, the communication port communicating with the cold-side opening; a bypass pipe having the second cold-side flow channel, both ends of the bypass pipe being connected to the communication port, and a heat insulation layer being provided between the middle part of the bypass pipe and the heat exchanger body.

[0014] According to some embodiments of the present invention, the first cold-side flow channel and the hot-side flow channel are arranged alternately 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.

[0015] According to some embodiments of the present invention, 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.

[0016] According to some embodiments of the present invention, the heat exchanger body includes a mounting plate, a bottom plate, and multiple heat exchange plates provided between the mounting plate and the bottom plate, the mounting plate being provided with the hot-side opening and the cold-side opening, and the multiple heat exchange plates dividing the space between the mounting plate and the bottom plate into multiple flow channels.

[0017] According to some embodiments of the present invention, the heat exchanger body further includes heat exchange fins, the heat exchange fins being provided in the flow channels of the heat exchanger body, and the density of the heat exchange fins in the hot-side flow channel being greater than the density of the heat exchange fins in the cold-side flow channel.

[0018] According to some embodiments of the present invention, the plurality of heat exchange plates include a first heat exchange plate. The hot-side flow channel is located on the side of the first heat exchange plate close to the mounting plate, and the second cold-side flow channel is located on the 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.

[0019] According to some embodiments of the present invention, at least part of the structural strengthening portion 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.

[0020] The heat management system according to an embodiment of the present invention includes a manifold plate and an intermediate heat exchanger according to an embodiment of the present invention. The intermediate heat exchanger is mounted on the manifold plate.

[0021] According to some embodiments of the present invention, the heat 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. 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.

[0022] According to some embodiments of the present invention, 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 heat 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.

[0023] A vehicle according to an embodiment of the present invention includes a heat management system according to an embodiment of the present invention.

[0024] Additional aspects and advantages of the present invention will be given in part in the following description, become apparent in part from the following description, or be learned by practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] The above and / or additional aspects and advantages of the present invention will become apparent and be readily understood from the description of embodiments in conjunction with the following drawings, in which:

[0026] Figure 1 is a schematic structural diagram of an intermediate heat exchanger according to an embodiment of the present invention;

[0027] Figure 2 is a cross-sectional view of the intermediate heat exchanger at the hot-side opening according to the first embodiment of the present invention;

[0028] Figure 3 is a cross-sectional view of the intermediate heat exchanger at the cold-side opening according to the first embodiment of the present invention;

[0029] Figure 4 is a schematic structural diagram of an intermediate heat exchanger according to the second embodiment of the present invention;

[0030] Figure 5 is a cross-sectional view of the intermediate heat exchanger at the hot-side opening according to the third embodiment of the present invention;

[0031] Figure 6 is a cross-sectional view of the intermediate heat exchanger at the cold-side opening according to the third embodiment of the present invention;

[0032] Figure 7 is a cross-sectional view of the intermediate heat exchanger at the hot-side opening according to the fourth embodiment of the present invention;

[0033] Figure 8 is a cross-sectional view of the intermediate heat exchanger at the cold-side opening according to the fourth embodiment of the present invention;

[0034] Figure 9 is a partial schematic structural diagram of a thermal management system according to an embodiment of the present invention;

[0035] Figure 10 is a schematic diagram of a thermal management system according to an embodiment of the present invention;

[0036] Figure 11 is a flow path diagram of the thermal management system in the refrigeration mode according to an embodiment of the present invention;

[0037] Figure 12 is a flow path diagram of the thermal management system in the heating mode according to an embodiment of the present invention;

[0038] Figure 13 is a schematic diagram of a vehicle according to an embodiment of the present invention.

[0039] Reference Numerals:

[0040] Vehicle 1000;

[0041] 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;

[0042] Intermediate heat exchanger 100;

[0043] 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 15; end plate 151; side wall plate 152; through hole 161;

[0044] Heat exchange fins 20;

[0045] First cold-side flow channel 311; second cold-side flow channel 312; hot-side flow channel 32;

[0046] 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;

[0047] Bypass pipe 50; heat insulation layer 52;

[0048] First direction F1; second direction F2; third direction F3. Detailed Embodiment

[0049] The embodiments of the present invention will be described in detail below. Examples of the embodiments are shown in the drawings, where 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 drawings are exemplary only for explaining the present invention and should not be construed as limiting the present invention.

[0050] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present invention.

[0051] In the description of the present invention, the "first feature" and the "second feature" may include one or more of such features. The meaning of "a plurality" is two or more. The first feature being "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 additional features therebetween. The first feature being "above", "over" and "on top of" the second feature includes the first feature being directly above and obliquely above the second feature, or merely indicating that the first feature has a higher horizontal height than the second feature.

[0052] With the rapid update and iteration of new energy vehicle technologies, the thermal management system, as a key system affecting vehicle range and passenger experience, has become the focus of technological innovation. Compactness is the core competitiveness of the thermal management integration module for electric vehicles. Selecting a compact, highly efficient heat exchange, and low-flow resistance heat exchange structure is a problem that urgently needs to be solved at present.

[0053] In some related technologies, two fluid channels, namely a high-pressure channel and a low-pressure channel, are provided in the refrigerant flow channel plate, and heat exchange is carried out through a partition. The heat exchange efficiency is low, the occupied space is large, and the structural compactness is poor.

[0054] In addition, harmful overheating will cause the temperature regulation ability of the thermal management system to be low. Therefore, the suction temperature of the compressor cannot be too high, and the heat exchange amount of the intermediate heat exchanger cannot be too large. It must be within the range specified by the system to play a beneficial role. At the same time, the lower the flow resistance, the better, especially the refrigerant flow resistance on the low-pressure side. Too large a flow resistance will also cause the temperature regulation ability of the thermal management system to be low. However, the intermediate heat exchangers in related technologies usually pursue the higher the heat exchange amount, the better, and it is difficult to simultaneously meet the requirements of the heat exchange amount and flow resistance required by the vehicle thermal management system.

[0055] 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.

[0056] The intermediate heat exchanger 100 according to an embodiment of the present invention will be described below with reference to the drawings.

[0057] Refer to Figures 1 - 8 As shown, the intermediate heat exchanger 100 according to an embodiment of the present invention may be a plate heat exchanger, and the intermediate heat exchanger 100 has a hot-side opening 45, a cold-side opening 40, and a plurality of flow channels arranged along a first direction F1. The plurality of flow channels include cold-side flow channels and hot-side flow channels 32. The cold-side flow channels are communicated with the cold-side opening 40 and are used for introducing a cold-side medium, and the hot-side flow channels 32 are communicated with the hot-side opening 45 and are used for introducing a hot-side medium.

[0058] In this application, the plate heat exchanger serves as an intermediate heat exchanger. The plate heat exchanger is used to guide the refrigerant liquid condensed by the condenser and the refrigerant vapor vaporized by absorbing heat in the evaporator to exchange heat, improve the subcooling degree before the throttle valve, thereby reducing the throttling loss and improving the refrigeration efficiency. And the intermediate heat exchanger 100 can be independent of the manifold 210. For example, it can adopt an inserted structure and be fixed on the manifold 210 by bolts. Compared with the built-in heat exchange structure in the refrigerant flow channel plate in the related art, the plate heat exchanger as the intermediate heat exchanger 100 has a more efficient heat exchange capacity, can greatly reduce the plate surface size of the manifold 210, and realize the compactness of the space structure.

[0059] For example, the intermediate heat exchanger 100 may include a heat exchanger body 10. The heat exchanger body 10 has a hot side opening 45, a cold side opening 40, and a plurality of heat exchange layers. Each heat exchange layer is formed as 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. The space inside the bypass pipe 50 is formed as a flow channel. The flow channel can provide a flow space for the heat exchange media 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.

[0060] Among them, the arrangement mode and quantity of the plurality of flow channels are not limited. For example, the plurality of flow channels can be arranged in a stacked manner along the first direction F1 (such as the up and down direction shown in Figure 2 and Figure 3 ) to make the structure compact and facilitate heat exchange; or the plurality of flow channels can be arranged in sequence along the second direction F2 (such as the front and back direction shown in Figure 2 ) or the third direction F3 (such as the left and right direction shown in Figure 1 ), or the plurality of flow channels can be arranged in an array. The first direction F1, the second direction F2, and the third direction F3 intersect pairwise. Here, the intersection includes but is not limited to being perpendicular to each other. For example, as shown in Figure 1 Figures 1 - 3 , the first direction F1 is the up and down direction, the second direction F2 is the front and back direction, and the third direction F3 is the left and right direction; for another example, the first direction F1 is the up and down direction, both the second direction F2 and the third direction F3 are perpendicular to the first direction F1, and the included angle between the first direction F1 and the third direction F3 is an acute angle; etc.

[0061] Among them, in the intermediate heat exchanger 100, the hot side medium with a higher temperature and the cold side medium with a lower temperature are refrigerants at different positions in the same refrigerant circulation loop, specifically the refrigerants on the compressor suction port side and the upstream side of the throttle valve.

[0062] Figure 1 ​​As shown, 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. The 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; the 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 Figures 1 - 3 As shown, the cold-side opening 40 and the hot-side opening 45 are arranged along the second direction F2 (such as Figure 1 the front-back direction shown), the cold-side opening 40 includes a cold-side medium inlet 41 and a cold-side medium outlet 42 arranged along the third direction F3 (such as Figure 1 the left-right direction shown), and the hot-side opening 45 includes a hot-side medium inlet 43 and a hot-side medium outlet 44 arranged along the third direction F3.

[0063] 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 Figures 1 - 3 As shown, the cold-side medium inlet 41 is located on the left side of the cold-side medium outlet 42, and the hot-side medium inlet 43 is located on the right side of the hot-side medium outlet 44, so that the cold-side medium and the hot-side medium flow in opposite directions in the third direction F3, which can reduce the temperature difference between the cold-side medium and the hot-side medium at the corresponding upper and lower positions to a certain extent, thus facilitating the control of the heat exchange amount within a reasonable range.

[0064] In addition, it should be noted that the setting positions of the cold-side medium inlet 41, the cold-side medium outlet 42, the hot-side medium inlet 43, and the hot-side medium outlet 44 in the first direction F1 are not limited. For example, the four openings can be arranged on the same side in the first direction F1 as Figures 1 - 3 shown, so as to facilitate the connection of structures such as the intermediate heat exchanger 100 and the manifold 210; a part of the four openings can also be arranged on one side in the first direction F1 and the other part can be arranged on the other side in the first direction F1, which is also within the protection scope of this application.

[0065] In addition, in this 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 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.

[0066] 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 that of the hot-side flow channel 32, that is, the number of cold-side flow channels is increased, so as to provide more flow space for the cold-side medium, reduce the flow resistance of the cold-side medium, and is beneficial to improving the temperature regulation ability of the thermal management system 200.

[0067] 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 other air layers, heat insulation materials, etc. For example, the first cold-side flow channel 311 and the hot-side flow channel 32 are separated by a 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.

[0068] The second cold-side flow channel 312 is spaced apart 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 surface, but also provided with at least one of the structures such as the first cold-side flow channel 311, an air layer, a heat insulation material, etc. For example, the second cold-side flow channel 312 and the hot-side flow channel 32 are separated by a plurality of 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.

[0069] Among them, the heat exchange amount of the cold-side medium in the second cold-side flow channel 312 can vary according to the installation position of the second cold-side flow channel 312. For example, when the first cold-side flow channel 311 is provided between the second cold-side flow channel 312 and the hot-side flow channel 32, heat exchange can occur to a certain extent between the cold-side medium in the first cold-side flow channel 311 and the cold-side medium in the second cold-side flow channel 312 when the temperature of the cold-side medium in the first cold-side flow channel 311 rises, but the heat exchange amount of the cold-side medium in the second cold-side flow channel 312 is relatively low; for another example, in an embodiment where the second cold-side flow channel 312 and the hot-side flow channel 32 are separated by an air layer, a heat insulation material, etc., the cold-side medium in the second cold-side flow channel 312 basically does not undergo heat exchange; thus, 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 increases, so that the overall heat exchange amount of the intermediate heat exchanger 100 is controlled within a reasonable range, and the heat exchange amount required by the thermal management system 200 is ensured through the heat exchange of the cold-side medium in the first cold-side flow channel 311, thereby controlling the overall heat exchange amount within an appropriate range, which is beneficial to improving the temperature regulation ability of the thermal management system 200.

[0070] According to the intermediate heat exchanger 100 of the embodiment of the present invention, by having the number of cold-side flow channels greater than the number of hot-side flow channels 32, the flow resistance is reduced, and the second cold-side flow channel 312 is spaced apart 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.

[0071] There can be various specific forms in which the second cold-side flow channel 312 is spaced apart from the hot-side flow channel 32, which will be described in detail below with reference to the accompanying drawings.

[0072] According to some embodiments of the present invention, such as Figures 2 - 6As shown, the intermediate heat exchanger 100 includes a heat exchanger body 10, and the heat exchanger body 10 has a plurality of flow channels. That is, all the hot-side flow channels 32 and all the cold-side flow channels are integrated in the heat exchanger body 10. The intermediate heat exchanger 100 has a high degree of integration and good structural compactness.

[0073] In addition, 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, so as to be spaced apart 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 spaced apart by the first cold-side flow channel 311, without the need to additionally provide other spacing structures, which is beneficial to improving the structural compactness and simplifying the structure.

[0074] In the embodiments of the present application, the first cold-side flow channel 311 can be one or more. For example, in an embodiment where the first cold-side flow channel 311 is one, all the hot-side flow channels 32 are located on one side of the first cold-side flow channel 311, and all the second cold-side flow channels 312 are located on the other side of the first cold-side flow channel 311, so as to control the heat exchange amount within a suitable range and avoid excessive heat exchange amount.

[0075] For example, in some embodiments, as Figures 2 - 6 shown, the first cold-side flow channel 311 is multiple, and the multiple first cold-side flow channels 311 and the hot-side flow channels 32 are alternately arranged along the first direction F1. In other words, along the first direction F1, they are arranged in the order of one first cold-side flow channel 311 and one hot-side flow channel 32. And in the above alternating arrangement structure, the two flow channels at both ends of the first direction F1 can both be the first cold-side flow channels 311, or one of them can be the first cold-side flow channel 311 and the other can be the hot-side flow channel 32.

[0076] Among them, the second cold-side flow channel 312 is located on the side of the outermost first cold-side flow channel 311 in the first direction F1 away from the hot-side flow channel 32.

[0077] In an embodiment where the two flow channels at both ends of the first direction F1 are both the first cold-side flow channels 311, all the second cold-side flow channels 312 can be all located on the same side of the alternating arrangement structure along the first direction F1, or part of them can be located on one side of the alternating arrangement structure along the first direction F1 and the other part can be located on the other side of the alternating arrangement structure along the first direction F1. In an embodiment where the flow channel at one end of the first direction F1 is the first cold-side flow channel 311, all the second cold-side flow channels 312 are located on the side of this first cold-side flow channel 311 away from the hot-side flow channel 32. This can all achieve the separation of the second cold-side flow channel 312 from the hot-side flow channel 32, increasing the thermal resistance, and all the multiple first cold-side flow channels 311 can efficiently exchange heat with the hot-side flow channels 32, so as to meet the requirements of heat exchange efficiency and heat exchange amount, and further keep the overall heat exchange amount of the intermediate heat exchanger 100 within a suitable range.

[0078] For example, in such as Figure 2and Figure 3 In the specific example shown, the first cold-side flow channel 311 and the hot-side flow channel 32 are alternately arranged in the up-and-down direction, where the lowermost flow channel is the first cold-side flow channel 311, and multiple second cold-side flow channels 312 are all located below the first cold-side flow channel 311. For example Figure 5 and Figure 6 In the specific example shown, the first cold-side flow channel 311 and the hot-side flow channel 32 are alternately arranged in the up-and-down direction, where the uppermost flow channel is the first cold-side flow channel 311, and the second cold-side flow channel 312 is located above the first cold-side flow channel 311. Of course, in other embodiments, when the structural arrangement permits, the second cold-side flow channels 312 can also be respectively arranged above and below the alternately arranged structure, or alternately arranged structures are respectively provided above and below the second cold-side flow channels 312.

[0079] In some specific embodiments, as Figures 2 - 6 shown, 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 the heat exchange efficiency. Moreover, in the alternately arranged structure, the two flow channels at both ends are both the first cold-side flow channels 311. Then, among all the flow channels of the heat exchanger body 10, the two flow channels at both ends are both cold-side flow channels, thereby reducing the heat loss caused by heat transfer through the heat exchange plate 11, the mounting plate 13, the bottom plate 14, etc. to the outside of the intermediate heat exchanger 100. For example Figure 2 and Figure 3 shown, the uppermost one is the first cold-side flow channel 311 and the lowermost one is the second cold-side flow channel 312, as Figure 5 and Figure 6 shown, the uppermost one is the second cold-side flow channel 312 and the lowermost one is the first cold-side flow channel 311.

[0080] 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, and can achieve the purpose of increasing the thermal resistance to control the heat transfer amount.

[0081] In other embodiments, as Figure 2 and Figure 3 shown, there are multiple second cold-side flow channels 312, and the second cold-side flow channels 312 are continuously arranged along the first direction F1. The continuous arrangement makes at least one side of the second cold-side flow channel 312 adjacent to another second cold-side flow channel 312, reducing the heat exchange area between the second cold-side flow channel 312 and the first cold-side flow channel 311, and is more conducive to increasing the thermal resistance to control the heat transfer amount within a reasonable range.

[0082] For example Figure 2 and Figure 3As shown, there are two second cold-side channels 312. The upper side of the upper second cold-side channel 312 is adjacent to the first cold-side channel 311 and exchanges a small amount of heat. The lower side of the upper second cold-side channel 312 is adjacent to the lower second cold-side channel 312, and the heat exchange amount can be ignored, and the effect of controlling the heat exchange amount is better.

[0083] According to some other embodiments of the present invention, as Figure 7 and Figure 8 shown, 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 channels. The plurality of channels include a hot-side channel 32 and a first cold-side channel 311. Among them, the number of channels included in the heat exchanger body 10 is less than the total number of channels of the intermediate heat exchanger 100. The channels of the heat exchanger body 10 may only include the hot-side channel 32 and the first cold-side channel 311, or may also include the hot-side channel 32, the first cold-side channel 311, and the second cold-side channel 312 at the same time, which are all within the protection scope of the present invention.

[0084] In addition, the heat exchanger body 10 has a communication port 101, and the communication port 101 is communicated with the cold-side opening 40. The bypass pipe 50 has a second cold-side channel 312, and both ends of the bypass pipe 50 are connected to the communication port 101, so that the cold-side medium flowing into the cold-side opening 40 can flow into the second cold-side channel 312 of the bypass pipe 50 through the communication port 101. And a heat insulation layer 52 is provided between the middle part of the bypass pipe 50 and the heat exchanger body 10. The heat insulation layer 52 can reduce or prevent heat transfer, so that the second cold-side channel 312 is separated from the heat exchanger body 10, that is, the second cold-side channel 312 is separated from the hot-side channel 32.

[0085] Under the heat insulation effect of the heat insulation layer 52, the cold-side medium flowing through the second cold-side channel 312 does not exchange heat with the hot-side medium, or the heat exchange amount between the cold-side medium flowing through the second cold-side channel 312 and the hot-side medium is very low, and even can be ignored.

[0086] Thus, the heat exchange amount can be controlled not to be too high, within a reasonable range, to meet the refrigeration and heating requirements of the thermal management system 200. And, compared with all channels being integrated in the heat exchanger body 10, by setting the bypass pipe 50, the structure change of the heat exchanger body 10 during the production process is less. Only a communication port 101 needs to be provided on the heat exchanger body 10, such as the bottom plate 14, and connected to the bypass pipe 50, without changing the structure of other parts of the heat exchanger body 10. For intermediate heat exchangers 100 with different heat exchange amounts, only the size of the communication port 101 and the size of the bypass pipe 50 need to be changed, and it has no impact on the structure of other parts of the heat exchanger body 10, which is beneficial to reducing the production cost and difficulty.

[0087] The bypass pipe 50 refers to a structure with a closed circumferential surface and open ends, enabling the bypass pipe 50 to independently define the second cold-side flow channel 312. The size and position of the second cold-side flow channel 312 can be adjusted more flexibly and it is easier to achieve pipe sealing. The cross-section of the bypass pipe 50 perpendicular to the flow direction includes, but is not limited to, circular, square, elliptical, etc. Bypass pipes 50 of different sizes can have different cross-sectional areas or lengths along the flow direction to control the heat exchange amount and flow resistance.

[0088] In some embodiments, as Figure 8 shown, the bypass pipe 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, such as Figure 8 the left-right direction shown), and 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, and the two second extension sections are respectively connected to both ends of the first extension section and the two communication ports 101. The connection method between the bypass pipe 50 and the heat exchange body can be, but is not limited to, welding, threaded connection, snap connection, etc.

[0089] The cooperation of the first extension section and the two second extension sections causes the bypass pipe 50 to generally form a U-shaped structure. The second extension section enables the first extension section to be spaced apart from the heat exchange body by a predetermined gap more uniformly, making the structure more compact and the heat insulation effect more uniform.

[0090] In some embodiments, as Figure 7 and Figure 8 shown, the first cold-side flow channel 311 and the hot-side flow channel 32 are arranged alternately along the first direction F1, making the heat exchange efficiency between the cold-side medium in the first cold-side flow channel 311 and the hot-side medium in the hot-side flow channel 32 higher. Among the multiple flow channels of the heat exchanger body 10, the flow channel closest to the bypass pipe 50 is the first cold-side flow channel 311. For example, Figure 7 and Figure 8 in the heat exchanger body 10 shown, the lowermost flow channel is the first cold-side flow channel 311. In other words, between the hot-side flow channel 32 and the second cold-side flow channel 312 of the bypass pipe 50, there is not only the insulation layer 52, but also the first cold-side flow channel 311 acting as a spacer, which has a better effect of reducing the heat transfer to the second cold-side flow channel 312, thus being beneficial to improving the accuracy of heat exchange amount control.

[0091] In some embodiments, the heat insulation layer 52 may include an air heat insulation layer located between at least a part of the bypass pipe 50 and the heat exchanger body 10. Since air has a low thermal conductivity, the air heat insulation layer can reduce the transfer of heat from the heat exchanger body 10 to the bypass pipe 50, thereby reducing the heat exchange of the cold-side medium in the bypass pipe 50 and achieving a good effect of increasing the thermal resistance. Moreover, by controlling the size of the air heat insulation layer along the first direction F1, the effect of heat transfer from the heat exchanger body 10 to the bypass pipe 50 can also be controlled, thereby controlling the heat transfer amount and improving the flexibility of heat transfer amount control.

[0092] In some embodiments, the heat insulation layer 52 may include a heat insulation material layer located between at least a part of the bypass pipe 50 and the heat exchanger body 10. The heat insulation material layer can achieve a good heat insulation effect and occupies a small space, which is beneficial to making the overall structure of the intermediate heat exchanger 100 more compact. For example, the heat insulation material layer can be made of materials such as glass fiber, asbestos, or metal with a thermal conductivity lower than that of the bottom plate 14 of the heat exchanger body 10.

[0093] It should be noted that the heat insulation material layer and the air heat insulation layer can also be provided simultaneously, which can further improve the heat insulation effect and the accuracy of heat transfer amount control.

[0094] The heat exchanger body 10 according to some embodiments of the present invention will be described below with reference to the accompanying drawings.

[0095] In some embodiments of the present invention, as Figures 2 - 8 shown, the heat exchanger body 10 includes a mounting plate 13, a bottom plate 14, and a plurality of heat exchange plates 11 disposed between the mounting plate 13 and the bottom plate 14. The mounting plate 13 is provided with a hot-side opening 45 and a cold-side opening 40, and the plurality of heat exchange plates 11 divide the space between the mounting plate 13 and the bottom plate 14 into a plurality of flow channels. The heat exchanger body 10 is formed as a plate heat exchanger, and the flow channels of the heat exchanger body 10 are formed as heat exchange layers. The heat exchange area between adjacent heat exchange layers is large, the heat exchange efficiency is higher, and the structure is more compact.

[0096] In some embodiments, as Figures 2 - 8 shown, the heat exchanger body 10 further includes heat exchange fins 20, and the heat exchange fins 20 are disposed in the flow channels 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, improve the heat exchange efficiency, and prevent the heat transfer amount from being too low to affect the temperature control ability of the thermal management system 200.

[0097] The greater the density of the heat exchange fins 20, the stronger the high-pressure resistance ability, and the greater the flow resistance; and the pressure of the hot-side medium is greater than that of the cold-side medium. The hot-side medium is not sensitive to the flow resistance, while the cold-side medium is very sensitive to the flow resistance. Therefore, heat exchange fins 20 with a relatively large density are arranged in the hot-side flow channel 32 corresponding to the hot-side medium to obtain a relatively large pressure resistance ability. At the same time, heat exchange fins 20 with a relatively small density are arranged in the cold-side flow channel corresponding to the cold-side medium to obtain a relatively low flow resistance. Thus, the overall flow resistance of the intermediate heat exchanger 100 is reduced and the pressure resistance ability is improved.

[0098] The density of the heat exchange fins 20 refers to the size of the space occupied by the solid part of the heat exchange fins 20 in a unit space, that is, the volume of the heat exchange fins 20 in a unit space. The heat exchange fins 20 include a plurality of fins extending along the first direction F1 and arranged along the second direction F2 and the third direction F3. The density of the heat exchange fins 20 can be adjusted in terms of fin thickness, fin width, fin quantity, fin pitch, etc. Among them, 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 more the fin quantity, the greater the density of the heat exchange fins 20; the smaller the fin pitch, the greater the density of the heat exchange fins 20.

[0099] For example, in some embodiments, the thickness of the fins 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 pitch between two adjacent fins of the heat exchange fins 20 in the hot-side flow channel 32 is smaller than the pitch between two adjacent fins of the heat exchange fins 20 in the cold-side flow channel.

[0100] 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, so as to meet the dual requirements of pressure resistance ability and low flow resistance.

[0101] According to some embodiments of the present invention, as Figures 2 - 4 shown, a plurality of 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 or can be arranged on the side of the first heat exchange plate 111 close to the bottom plate 14.

[0102] 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, therefore, 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.

[0103] Since the hot-side runners 32 are all located on the side of the first heat exchange plate 111 close to the mounting plate 13, there is no need to provide holes for the hot-side medium to pass through in the area of the first heat exchange plate 111 opposite to the hot-side opening 45. In addition, the pressure of the hot-side medium is greater than that of the cold-side medium. Therefore, as Figure 4 shown, the first heat exchange plate 111 is provided with a structural strengthening portion 15 opposite to the hot-side opening 45. The structural strengthening portion 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 strengthening portion 15 with greater structural strength, thereby reducing the impact force on the structures of other areas and improving the overall pressure resistance. While the structures of other areas can adopt structures with a strength lower than that of the structural strengthening portion 15 to meet the pressure resistance requirements, for example, a lower-density structure such as a flat plate structure, which is beneficial to reducing the flow resistance and improving the temperature regulation ability of the thermal management system 200.

[0104] In some embodiments, as Figure 4 shown, the structural strengthening portion 15 at least partially extends away from the mounting plate 13 relative to the first heat exchange plate 111, and in the embodiment where there is another heat exchange plate 11 (denoted as the second heat exchange plate) between the first heat exchange plate 111 and the bottom plate 14, the structural strengthening portion 15 can abut against the adjacent second heat exchange plate; in the embodiment where the first heat exchange plate 111 is adjacent to the bottom plate 14, the structural strengthening portion 15 abuts against the adjacent bottom plate 14. The adjacent second heat exchange plate or bottom plate 14 that abuts against each other can support the structural strengthening portion 15, increase the overall thickness of the plate in the area opposite to the hot-side opening 45, and thus play a role in structural strengthening.

[0105] It should be noted that in the embodiments where the structural strengthening portion 15 abuts against the adjacent second heat exchange plate or bottom plate 14, the structural strengthening portion 15 and the adjacent second heat exchange plate or bottom plate 14 can be in contact fit or welded together, etc. Among them, the welded connection has a better effect of improving the structural strength and can play a limiting role in the direction perpendicular to the first direction F1, thereby improving the overall durability.

[0106] In some specific embodiments, the plate thickness of the bottom plate 14 is greater than that of the heat exchange plate 11, and the structural strengthening effect of the structural strengthening portion 15 abutting against the bottom plate 14 is better.

[0107] In some specific embodiments, as Figure 4As shown, 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 structural strengthening effect of the second heat exchange plate on the structural strengthening part 15 will be weak, and the pressure resistance of the second heat exchange plate itself will be too weak; if the thickness of the second heat exchange plate is too large, it will occupy too much space and increase the cost. Within the above thickness range, the pressure resistance strength of the second heat exchange plate and the structural strengthening effect on the structural strengthening part 15 are good, and it is beneficial to make the structure compact and reduce the cost.

[0108] In the embodiments of the present application, the specific structure of the structural strengthening part 15 can be flexibly set. For example, it can be a boss, a rib, a bending structure, etc.

[0109] For example, in some embodiments, as Figure 4 shown, the structural strengthening part 15 includes an end plate 151 and a side wall plate 152. One end of the side wall plate 152 along the first direction F1 (such as Figure 4 the upper end shown) is connected to the periphery of the end plate 151, and the other end of the side wall plate 152 along the first direction F1 (such as Figure 4 the lower end shown) is connected to other parts of the first heat exchange plate 111. The structural strengthening part 15 is generally formed into a boss structure, which is simple and easy to process. For example, other parts of the first heat exchange plate 111 and the structural strengthening part 15 can be formed by sheet metal deformation processing from a flat plate, and the manufacturing efficiency is high.

[0110] In addition, in the embodiment where the structural strengthening part 15 abuts against the bottom plate 14, the end plate 151 abuts against the adjacent bottom plate 14; in the embodiment where the structural strengthening part 15 abuts against the adjacent second heat exchange plate, the end plate 151 abuts against the adjacent second heat exchange plate. Thus, the end plate 151 is opposite to the hot side opening 45, and a relatively large area of surface-to-surface abutting fit can be formed between the end plate 151 and the adjacent bottom plate 14 or the second heat exchange plate, so as to greatly increase the thickness of the plate in the area opposite to the hot side opening 45, and the area of the thickening area can be large enough, so that the structural strengthening part 15 itself is not easily deformed, the pressure resistance uniformity is improved, and the compactness is improved.

[0111] In some specific embodiments, as Figure 5 shown, 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 strengthening effect of the end plate 151 will be weak and the pressure resistance ability will be weak; if the thickness of the end plate 151 is too large, the cost will increase. Within the above thickness range, the pressure resistance strength and the structural strengthening effect of the end plate 151 are good, and it is beneficial to reduce the cost.

[0112] As shown Figures 9 - 12 In the heat management system 200 disclosed in the embodiments of the present application, as shown, it includes a manifold 210 and an intermediate heat exchanger 100 disclosed in the embodiments of the present application. The intermediate heat exchanger 100 is installed on the manifold 210. The plate heat exchanger serves as the intermediate heat exchanger 100 and is integrated on the manifold 210, independent of the flow channels of the manifold 210. It can adopt a plug-in structure and be fixed on the manifold 210 by bolts. Compared with the refrigerant flow channel plate built-in heat exchange structure in the related art, the intermediate heat exchanger 100 has a more efficient heat exchange capacity, can greatly reduce the plate surface size of the manifold 210, and achieve a compact spatial structure.

[0113] In addition, due to the above-mentioned beneficial technical effects of the intermediate heat exchanger 100 according to the embodiments of the present invention, the heat management system 200 according to the embodiments of the present invention has good spatial compactness. And by making the number of cold-side flow channels greater than the number of hot-side flow channels 32, the flow resistance is reduced. Moreover, the second cold-side flow channel 312 is spaced apart 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 heat management system 200.

[0114] In some embodiments, as shown Figure 10 In the heat management system 200, it includes: an external heat exchanger 220, a cabin heat exchanger, a compressor 250, and a throttling device. Among them, 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, and 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 throttling 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.

[0115] The external heat exchanger 220 can exchange heat with the external environment outside the cabin, the cabin heat exchanger can exchange heat with the environment inside the cabin, and the compressor 250 is used to drive the heat exchange medium in the loop to flow, so as to achieve the heat exchange between the cabin and the external environment through the circulating flow of the heat exchange medium.

[0116] 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 arranging the intermediate heat exchanger 100 between the condenser and the evaporator in the circulation loop, the intermediate heat exchanger 100 is used to guide the heat exchange between the refrigerant liquid condensed by the condenser and the refrigerant vapor vaporized by absorbing heat in the evaporator, so as to increase the subcooling degree before the throttling device, thereby reducing the throttling loss and improving the refrigeration efficiency.

[0117] In some embodiments, continue to refer to Figure 10As shown in the figure, 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.

[0118] 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 setting two throttle valves, the flow paths of the refrigerant in the cabin heat exchanger and the external heat exchanger 220 can be switched, thereby realizing function switching.

[0119] Specifically, the thermal management system 200 has a heating mode and a cooling mode. As Figure 11 shown, in the cooling mode, the compressor 250, the external heat exchanger 220, the hot-side flow channel 32 of the intermediate heat exchanger 100, the first throttle valve 261, the cabin evaporator 230, and the cold-side flow channel of the intermediate heat exchanger 100 are connected and form a first refrigerant circulation flow path.

[0120] The compressor 250 does work to drive the refrigerant to flow through the external heat exchanger 220, the intermediate heat exchanger 100, the first throttle valve 261, the cabin evaporator 230, and 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 into the air, the cabin evaporator 230 works to absorb the heat in the cabin, realizing cabin cooling; 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 two-state refrigerants exchange heat in the intermediate heat exchanger 100, thereby realizing the heat recovery heat exchange between the subcooled refrigerant and the superheated refrigerant in the cooling mode, increasing the subcooling degree before the first throttle valve 261, thereby reducing the throttling loss and improving the cooling efficiency.

[0121] As Figure 12 shown, in the heating mode, the compressor 250, the cabin condenser 240, the hot-side flow channel 32 of the intermediate heat exchanger 100, the second throttle valve 262, the external heat exchanger 220, and the cold-side flow channel of the intermediate heat exchanger 100 are connected and form a second refrigerant circulation flow path.

[0122] The compressor 250 does work to drive the refrigerant to flow through the cabin condenser 240, the intermediate heat exchanger 100, the second throttle valve 262, the external heat exchanger 220, the intermediate heat exchanger 100 in sequence, and finally return to the compressor 250. At this time, the external heat exchanger 220 acts as an evaporator to absorb heat from the air, and the cabin condenser 240 works to release heat to the cabin, realizing the heating of the cabin. The high-temperature and high-pressure liquid refrigerant flowing out of the cabin condenser 240 enters the intermediate heat exchanger 100 through the hot-side medium inlet 43, and the low-temperature and low-pressure gaseous refrigerant at the outlet of the external heat exchanger 220 enters the intermediate heat exchanger 100 through the cold-side medium inlet 41. The refrigerants in two states exchange heat in the intermediate heat exchanger 100, thereby realizing the regenerative heat exchange between the subcooled refrigerant and the superheated refrigerant in the heating mode, increasing the subcooling degree before the second throttle valve 262, thereby reducing the throttling loss and improving the refrigeration efficiency.

[0123] In some embodiments, as Figures 10 - 12 shown, 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 outlets of the cabin condenser 240 and 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.

[0124] 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.

[0125] In the refrigeration mode, as Figure 11 shown, 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 conducted; in the heating mode, as Figure 12 shown, 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 conducted, 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 with simple control.

[0126] As Figure 13 shown, 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. Since the thermal management system 200 according to the embodiment of the present invention has the above beneficial technical effects, the vehicle 1000 according to the embodiment of the present invention has good space compactness, and by having the number of cold-side channels greater than the number of hot-side channels 32, the flow resistance is reduced, and the second cold-side channel 312 is spaced apart from the hot-side 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.

[0127] The thermal management system 200 disclosed in the embodiment of the present application can be used in a device that needs to use the thermal management system 200 or a control system of the thermal management system 200. The device can be, but is not limited to, vehicles, ships, spacecraft, etc. Among them, the spacecraft can include airplanes, rockets, space shuttles, and spaceships, etc.

[0128] Among them, the 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 vehicle or an extended-range vehicle with an internal combustion engine and an electric motor as the main driving forces at the same time. 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 for the electric motor can use power batteries, hydrogen fuel cells, etc., which are not specifically limited here. It should be noted that only an exemplary description of the structure of the new energy vehicle and the like is made here, and it does not limit the protection scope of the present invention.

[0129] In some embodiments, the thermal management system 200 is an important component for regulating the automotive cockpit environment (temperature, humidity, etc.) and the working environments of other components. Among them, the thermal management system 200 mainly includes: valves, heat exchangers, compressors, and pumps. The pumps can be, for example, electric water pumps or other water pumps. Among them, there is a refrigerant circulating in the thermal management system 200, and the refrigerant can be freon, propane, etc.

[0130] Next, the thermal management system 200 according to a specific embodiment of the present invention will be described in detail with reference to the accompanying drawings. It should be understood that the following description is only an exemplary illustration and cannot be construed as a limitation of the invention.

[0131] As Figures 1 - 3 and Figure 9As shown, the thermal management system 200 includes a manifold 210 and an intermediate heat exchanger 100. Four connecting pipes 12 of the intermediate heat exchanger 100 are provided on the same side of the heat exchanger body 10 in the up-and-down direction, enabling the intermediate heat exchanger 100 to be independent of the manifold 210. The pipeline connection is achieved through an insertion structure using the connecting pipes 12, and sealing is achieved by using a sealing ring. The intermediate heat exchanger 100 is fixed on the manifold 210 through fasteners to achieve structural integration, which can greatly reduce the plate size of the manifold 210 and achieve a compact structure.

[0132] 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.

[0133] The plurality of heat exchange plates 11 are stacked in the up-and-down direction, and the space between the mounting plate 13 and the bottom plate 14 is divided into seven heat exchange layers. Each heat exchange layer forms a flow channel, and heat exchange fins 20 are provided in the flow channel. 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 alternately arranged in the up-and-down direction. Each hot-side flow channel 32 is located between two first cold-side flow channels 311. The two second cold-side flow channels 312 are arranged continuously up and down and are located below the lowermost first cold-side flow channel 311. The cold-side medium inlet 41 and the cold-side medium outlet 42 are respectively communicated with the cold-side flow channels, and the hot-side medium inlet 43 and the hot-side medium outlet 44 are respectively communicated with the hot-side flow channels 32.

[0134] 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, and there is a first cold-side flow channel 311 in between, so that the cold-side medium in the second cold-side flow channel 312 does not participate 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 a large thermal resistance, playing a role in controlling the heat exchange amount within a reasonable range. Thus, the second cold-side flow channel 312 plays a role in adjusting the heat exchange amount and reducing the flow resistance, and can meet the heat exchange amount range and low flow resistance requirements required by the thermal management system 200 while meeting the high-pressure resistance.

[0135] The other components and operations of the thermal management system 200 and the vehicle 1000 according to the embodiments of the present invention are known to those of ordinary skill in the art and will not be described in detail here.

[0136] In the description of the present invention, it should be noted that, unless otherwise clearly specified and defined, the terms "installed", "connected", and "coupled" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the communication inside two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific situations.

[0137] In the description of this specification, the descriptions referring to the terms "embodiment", "specific embodiment", "example", etc. mean that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

[0138] Although the embodiments of the present invention have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, substitutions and variations can be made to these embodiments without departing from the principles and spirit of the present invention. The scope of the present invention is defined by the claims and their equivalents.

Claims

1. An intermediate heat exchanger, characterized in that, 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 communicated with the cold side opening and are used for introducing cold side media, and the hot side flow channels are communicated with the hot side opening and are used for introducing hot side media. 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, characterized in that, 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, characterized in that, Any of the hot side flow channels is located between two of the first cold side flow channels.

5. The intermediate heat exchanger according to claim 2, 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 claim 1, characterized in that, 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 communicated with the cold side opening; a bypass pipe, the bypass pipe having the second cold side flow channel. Two ends of the bypass pipe are connected to the communication port, and a heat insulation layer is provided between a middle part of the bypass pipe and the heat exchanger body.

7. The intermediate heat exchanger according to claim 6, characterized in that, 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, 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, characterized in that 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 a space between the mounting plate and the bottom plate into the plurality of flow channels.

10. The intermediate heat exchanger according to claim 9, characterized in that, 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, wherein, A plurality of the heat exchange plates includes 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 structure strengthening portion opposite to the hot side opening.

12. The intermediate heat exchanger according to claim 11, wherein, The structure 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, characterized in that, 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. An inlet of the compressor is connected to a cold side medium outlet of the intermediate heat exchanger. One of the external heat exchanger and the cabin heat exchanger is connected to a cold side medium inlet and a hot side medium outlet of the intermediate heat exchanger, and the other is connected to a hot side medium inlet of the intermediate heat exchanger and an 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, characterized in that, 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 heat 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 communicated to 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 communicated to form a second refrigerant circulation flow path.

16. A vehicle, characterized in that, It includes a heat management system according to any one of claims 13-15.

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