Intermediate heat exchanger, heat management system and vehicle

Abstract

The utility model discloses an intermediate heat exchanger, a heat management system and a vehicle, the intermediate heat exchanger comprises a heat exchanger body, the heat exchanger body is provided with a cold side heat exchange layer used for introducing a cold side medium and a hot side heat exchange layer used for introducing a hot side medium; the first heat exchange fins are arranged in the heat side heat exchange layer; the first heat exchange fins are arranged in the cold side heat exchange layer, the second heat exchange fins are arranged in the cold side heat exchange layer, and the density of the first heat exchange fins is larger than that of the second heat exchange fins. According to the intermediate heat exchanger provided by the embodiment of the utility model, the density of the first heat exchange fins in the hot side heat exchange layer is greater than that of the second heat exchange fins in the cold side heat exchange layer, so that the pressure resistance of the first heat exchange fins is improved, the circulation resistance of the second heat exchange fins is reduced, and the overall flow resistance is further reduced; and the heat exchange amount is reduced within a reasonable range, so that the refrigerating and heating requirements of the heat management system are met.

Description

Technical Field

[0001] The utility model relates to the technical field of heat exchangers, and more specifically, to an intermediate heat exchanger, a thermal management system and a vehicle. Background Art

[0002] In the related art, in order to improve the high-pressure resistance capability, the intermediate heat exchanger needs to adopt a higher-density turbulence structure, which makes it difficult to simultaneously meet the heat exchange capacity, flow resistance and layout requirements of the thermal management system. Utility Model Content

[0003] The utility model aims to solve at least one of the technical problems existing in the prior art. To this end, one object of the utility model is to provide an intermediate heat exchanger, wherein the intermediate heat exchanger reduces heat exchange amount and flow resistance.

[0004] Another object of the present invention is to provide a thermal management system having the above intermediate heat exchanger.

[0005] Another object of the present invention is to provide a vehicle with the above thermal management system.

[0006] The intermediate heat exchanger according to an embodiment of the utility model includes: a heat exchanger body, the heat exchanger body having a cold side heat exchange layer for passing a cold side medium and a hot side heat exchange layer for passing a hot side medium; a first heat exchange fin, the first heat exchange fin is arranged in the hot side heat exchange layer; a second heat exchange fin, the second heat exchange fin is arranged in the cold side heat exchange layer, wherein the density of the first heat exchange fin is greater than the density of the second heat exchange fin.

[0007] According to the intermediate heat exchanger of the embodiment of the utility model, by making the density of the first heat exchange fins in the hot side heat exchange layer greater than the density of the second heat exchange fins in the cold side heat exchange layer, it is beneficial to improve the pressure resistance of the first heat exchange fins, reduce the flow resistance of the second heat exchange fins and thus reduce the overall flow resistance, and reduce the heat exchange rate within a reasonable range to meet the cooling and heating requirements of the thermal management system.

[0008] In addition, the intermediate heat exchanger according to the above embodiment of the utility model may also have the following additional technical features:

[0009] According to some embodiments of the present invention, the hot-side heat exchange layer and the cold-side heat exchange layer are arranged along a first direction, the first heat exchange fins include a plurality of first fins, and the two ends of the first fins along the first direction are respectively abutted against the two side walls opposite to the hot-side heat exchange layer, and the second heat exchange fins include a plurality of second fins, and the two ends of the second fins along the first direction are respectively abutted against the two side walls opposite to the cold-side heat exchange layer.

[0010] According to some embodiments of the utility model, a plurality of the first fins are arranged into a plurality of rows of first fin groups along a third direction, the first fin group includes a plurality of the first fins arranged at intervals along a second direction, a plurality of the second fins are arranged into a plurality of rows of second fin groups along the third direction, the second fin group includes a plurality of the second fins arranged at intervals along the second direction, and the first direction, the second direction and the third direction intersect each other.

[0011] According to some embodiments of the present invention, the thickness of the first fin along the second direction is greater than the thickness of the second fin along the second direction.

[0012] According to some embodiments of the present invention, among any three adjacent first fins of the same first fin group, the distance between two of the first fins located at both ends is L1; among any three adjacent second fins of the same second fin group, the distance between two of the second fins located at both ends is L2, wherein L1 is smaller than L2.

[0013] According to some embodiments of the present invention, the thickness of the first fin along the second direction is 0.2 mm to 0.4 mm; and / or the thickness of the second fin along the second direction is 0.2 mm to 0.4 mm.

[0014] According to some embodiments of the present invention, the width of the first fin along the third direction is 1 mm to 2.2 mm; and / or the width of the second fin along the third direction is 1 mm to 2.2 mm.

[0015] According to some embodiments of the present invention, the angle between the first fin and the first direction is 0° to 20°; and / or the angle between the second fin and the first direction is 0° to 20°.

[0016] According to some embodiments of the utility model, among any three adjacent first fins of the same first fin group, the spacing between two first fins located at both ends is 4.2 mm to 8.6 mm; and / or, among any three adjacent second fins of the same second fin group, the spacing between two second fins located at both ends is 4.2 mm to 8.6 mm.

[0017] According to some embodiments of the present invention, among any three adjacent first fins of the same first fin group, the two ends of the middle first fin along the first direction are respectively connected to the two adjacent first fins through first connecting pieces, and the first connecting piece extends along the second direction and abuts against the wall surface of the hot side heat exchange layer; among any three adjacent second fins of the same second fin group, the two ends of the middle second fin along the first direction are respectively connected to the two adjacent second fins through second connecting pieces, and the second connecting piece extends along the second direction and abuts against the wall surface of the hot side heat exchange layer.

[0018] According to some embodiments of the present invention, two adjacent first connecting pieces along the third direction are connected, and two adjacent second connecting pieces along the third direction are connected.

[0019] According to some embodiments of the utility model, two adjacent first connecting pieces along the third direction are partially staggered in the second direction and the staggered size is L3, and the spacing between two of the three first fins located at both ends along the second direction is L1, and L3 / L1 is 0.2-0.3; and / or, two adjacent second connecting pieces along the third direction are partially staggered in the second direction and the staggered size is L4, and the spacing between two of the three second fins located at both ends along the second direction is L2, and L4 / L2 is 0.2-0.3.

[0020] According to some embodiments of the present invention, the spacing between the two side walls of the hot side heat exchange layer along the first direction is 1.4mm~3mm; and / or the spacing between the two side walls of the cold side heat exchange layer along the first direction is 1.4mm~3mm.

[0021] The thermal management system according to the embodiment of the present utility model includes the intermediate heat exchanger according to the embodiment of the present utility model.

[0022] A vehicle according to an embodiment of the present invention includes a thermal management system according to an embodiment of the present invention.

[0023] Additional aspects and advantages of the present invention will be given in part in the following description, and in part will become apparent from the following description, or will be learned through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] The above and / or additional aspects and advantages of the present invention will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0025] Figure 1 is a structural schematic diagram of an intermediate heat exchanger according to an embodiment of the utility model;

[0026] Figure 2 is a cross-sectional view of the hot side opening of the intermediate heat exchanger according to an embodiment of the utility model;

[0027] Figure 3 is a cross-sectional view of the cold side opening of the intermediate heat exchanger according to an embodiment of the utility model;

[0028] Figure 4 is a schematic structural diagram of a first heat exchange fin and a second heat exchange fin according to an embodiment of the utility model;

[0029] Figure 5 and Figure 6 It is a partial structural schematic diagram of the first heat exchange fins with different proportions according to the embodiment of the utility model;

[0030] Figure 7 and Figure 8 It is a partial structural schematic diagram of the second heat exchange fins with different proportions according to the embodiment of the utility model;

[0031] Fig. 9 is a partial structural schematic diagram of a thermal management system according to an embodiment of the utility model;

[0032] Fig.10 is a schematic diagram of a vehicle according to an embodiment of the utility model.

[0033] Reference numerals:

[0034] Vehicle 1000; thermal management system 200; collector plate 210;

[0035] Intermediate heat exchanger 100;

[0036] Heat exchanger body 10; heat exchange plate 11; connecting pipe 12; mounting plate 13; bottom plate 14;

[0037] First heat exchange fin 25; first fin group 211; first fin 221; first connecting piece 231;

[0038] The second heat exchange fin 26; the second fin group 212; the second fin 222; the second connecting piece 232;

[0039] Hot side heat exchange layer 301; cold side heat exchange layer 302;

[0040] Cold side medium inlet 41; cold side medium outlet 42; hot side medium inlet 43; hot side medium outlet 44;

[0041] The first direction F1; the second direction F2; the third direction F3. DETAILED DESCRIPTION

[0042] The embodiments of the present invention are described in detail below, and 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 invention, and cannot be understood as limiting the present invention.

[0043] In the description of the present invention, 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 invention and simplifying the description, and do not indicate or imply that the referred device or element 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 invention.

[0044] In the description of the present invention, "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 "above", "above" and "above" the second feature may include the first feature being directly above and diagonally above the second feature, or may simply mean that the first feature is at a higher level than the second feature.

[0045] With the rapid update and iteration of new energy vehicle technology, the thermal management system, as a key system that affects vehicle endurance and passenger experience, has become the focus of technological innovation. Compactness is the core competitiveness of electric vehicle thermal management integrated modules. The selection of compact, efficient heat exchange, and low flow resistance heat exchange structures is a difficult problem that needs to be overcome urgently.

[0046] In some related technologies, two fluid channels, high-pressure and low-pressure, are provided in the refrigerant flow channel plate, and heat exchange is performed through a partition plate. The heat exchange efficiency is low, the space occupied is large, and the structure is poorly compact.

[0047] In addition, harmful overheating will lead to low temperature control capability of the thermal management system. Therefore, the suction temperature of the compressor cannot be too high, and the heat exchange capacity of the intermediate heat exchanger cannot be too large. It must be within the range specified by the temperature control requirements of the thermal management 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 much flow resistance will also lead to low temperature control capability of the thermal management system. However, in order to ensure high pressure resistance, the intermediate heat exchanger in the related technology must have a high-density spoiler structure. Conventional spoiler structures are difficult to simultaneously meet the requirements of temperature control capability, heat exchange capacity, and flow resistance of the thermal management system.

[0048] 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 reduce flow resistance and heat exchange to a certain extent while ensuring high pressure resistance, so that the heat exchange is not too large and the flow resistance is reduced.

[0049] The intermediate heat exchanger 100 according to an embodiment of the present invention will be described below with reference to the accompanying drawings.

[0050] Reference Figure 1-Figure 9 As shown, the intermediate heat exchanger 100 according to the embodiment of the present invention may include: a heat exchanger body 10 , a first heat exchange fin 25 and a second heat exchange fin 26 .

[0051] Specifically, the heat exchanger body 10 has a cold side heat exchange layer 302 for passing the cold side medium and a hot side heat exchange layer 301 for passing the hot side medium. The cold side heat exchange layer 302 can provide a flow space for the cold side medium with a lower temperature, and the hot side heat exchange layer 301 can provide a flow space for the hot side medium with a higher temperature.

[0052] For example, in some embodiments, the heat exchanger body 10 may include a plurality of Figure 2 The heat exchange plates 11 are stacked (in the up and down direction as shown) to form a plate heat exchanger, and the space between two adjacent heat exchange plates 11 forms a cold side heat exchange layer 302 or a hot side heat exchange layer 301. The heat exchange medium in the adjacent cold side heat exchange layer 302 and the hot side heat exchange layer 301 can transfer energy through the middle heat exchange plate 11 to achieve heat exchange.

[0053] For example, in some embodiments, the heat exchanger body 10 may include a plurality of Figure 1 The heat exchange plates 11 are staggeredly arranged in the front-to-back direction (as shown) to form a cold-side heat exchange layer 302 or a hot-side heat exchange layer 301. The utility model does not limit this, and the heat exchanger body 10 can have a cold-side heat exchange layer 302 and a hot-side heat exchange layer 301.

[0054] In some embodiments, the heat exchanger body 10 is provided with a cold side opening and a hot side opening, at least one cold side heat exchange layer 302 is connected to the cold side opening, at least one hot side heat exchange layer 301 is connected to the hot side opening, and the cold side medium can be introduced into the cold side heat exchange layer 302 through the cold side opening, and the hot side medium can be introduced into the hot side heat exchange layer 301 through the hot side opening. In the intermediate heat exchanger 100, the cold side medium and the hot side medium are refrigerants at different positions in the same refrigerant circulation loop, specifically, the refrigerants at the suction port side of the compressor and the upstream side of the throttle valve.

[0055] For example, in some specific embodiments, in the cooling mode, the compressor drives the refrigerant to flow through the outdoor heat exchanger, the liquid storage tank, the intermediate heat exchanger 100, the expansion valve, the cabin evaporator, the intermediate heat exchanger 100 in sequence, and finally returns to the compressor. At this time, the outdoor heat exchanger acts as a condenser to release heat to the air, and the cabin evaporator works to absorb the heat in the cabin to achieve cabin cooling; the high-temperature and high-pressure liquid refrigerant at the outlet of the liquid storage tank enters the intermediate heat exchanger 100 through the hot side opening, and the low-temperature and low-pressure gaseous refrigerant at the outlet of the evaporator enters the intermediate heat exchanger 100 through the cold side opening. The refrigerants in the two states exchange heat in the intermediate heat exchanger 100, thereby realizing the heat recovery heat exchange of the supercooled refrigerant and the superheated refrigerant in the cooling mode, increasing the supercooling degree before the expansion valve, thereby reducing throttling losses and improving refrigeration efficiency.

[0056] In the heat pump mode, the compressor drives the refrigerant to flow through the condenser, the liquid storage tank, the intermediate heat exchanger 100, the expansion valve, the outdoor heat exchanger, the intermediate heat exchanger 100, and finally returns to the compressor; at this time, the outdoor heat exchanger absorbs heat from the air as an evaporator, and the condenser works to release heat to the passenger compartment to achieve cabin heating. The high-temperature and high-pressure liquid refrigerant at the outlet of the liquid storage tank enters the intermediate heat exchanger 100 through the hot side opening, and the low-temperature and low-pressure gaseous refrigerant at the outlet of the outdoor heat exchanger enters the intermediate heat exchanger 100 through the cold side opening. The refrigerants in the two states exchange heat in the intermediate heat exchanger 100, thereby realizing the heat exchange of the supercooled refrigerant and the superheated refrigerant in the heat pump mode, increasing the supercooling before the expansion valve, thereby reducing throttling losses and improving refrigeration efficiency.

[0057] In addition, if Figure 2-Figure 3 As shown, the first heat exchange fin 25 is disposed in the hot side heat exchange layer 301, and the second heat exchange fin 26 is disposed in the cold side heat exchange layer 302. The first heat exchange fin 25 plays a certain supporting and turbulent role in the hot side heat exchange layer 301, and the second heat exchange fin 26 plays a certain supporting and turbulent role in the cold side heat exchange layer 302, so as to improve the pressure resistance of the heat exchanger body 10 and change the flow path of the heat exchange medium.

[0058] like Figure 4As shown, the density of the first heat exchange fin 25 is greater than the density of the second heat exchange fin 26. The density of the heat exchange fin refers to the size of the space occupied by the solid part of the heat exchange fin in a unit space, that is, the volume of the heat exchange fin in a unit space. The greater the density of the heat exchange fin, the stronger the high pressure resistance and the greater the flow resistance.

[0059] The pressure of the hot side medium is greater than that of the cold side medium. The hot side medium is insensitive to flow resistance, while the cold side medium is very sensitive to flow resistance. Therefore, a first heat exchange fin 25 with a higher density is provided in the hot side heat exchange layer 301 to obtain a higher pressure resistance, and a second heat exchange fin 26 with a lower density is provided in the cold side heat exchange layer 302 to obtain a lower flow resistance. The second heat exchange fin 26 with a lower density has a smaller contact area with the cold side medium, which is beneficial to reduce the heat exchange amount and prevent the heat exchange amount from being too high.

[0060] Thus, the hot side medium in the hot side heat exchange layer 301 exchanges heat with the cold side medium in the cold side heat exchange layer 302, and a first heat exchange fin 25 with a larger density is arranged in the hot side heat exchange layer 301, so that the pressure resistance of the first heat exchange fin 25 is enhanced, and a second heat exchange fin 26 with a smaller density is arranged in the cold side heat exchange layer 302, so that the flow resistance of the second heat exchange fin 26 is reduced, which is beneficial to reducing the overall flow resistance, thereby helping to improve the temperature control ability of the thermal management system 200, and helping to control the heat exchange amount not to be too high, within a reasonable range, so as to meet the cooling and heating requirements of the thermal management system 200.

[0061] According to the intermediate heat exchanger 100 of the embodiment of the utility model, by making the density of the first heat exchange fins 25 in the hot side heat exchange layer 301 greater than the density of the second heat exchange fins 26 in the cold side heat exchange layer 302, it is beneficial to improve the pressure resistance of the first heat exchange fins 25, reduce the flow resistance of the second heat exchange fins 26 and thus reduce the overall flow resistance, and reduce the heat exchange rate within a reasonable range to meet the cooling and heating requirements of the thermal management system 200.

[0062] The specific structures of the first heat exchange fin 25 and the second heat exchange fin 26 according to some embodiments of the present invention are described below with reference to the accompanying drawings.

[0063] The hot side heat exchange layer 301 and the cold side heat exchange layer 302 can be arranged in multiple directions. For example, in some embodiments of the present invention, Figure 2-Figure 3 As shown, the hot side heat exchange layer 301 and the cold side heat exchange layer 302 are arranged along the first direction F1, and the arrangement method can be a stacked arrangement, and the arrangement order can be an alternating arrangement, the hot side heat exchange layer 301 is located above the cold side heat exchange layer 302, the hot side heat exchange layer 301 is located below the cold side heat exchange layer 302, a disordered arrangement, etc., all of which are within the protection scope of the present utility model.

[0064] like Figure 2-Figure 3 and Figure 5-Figure 8As shown, the first heat exchange fin 25 includes a plurality of first fins 221, and the two ends of the first fins 221 along the first direction F1 are respectively in contact with the two side walls opposite to the hot side heat exchange layer 301; the second heat exchange fin 26 includes a plurality of second fins 222, and the two ends of the second fins 222 along the first direction F1 are respectively in contact with the two side walls opposite to the cold side heat exchange layer 302, which are beneficial to support the side wall surface of the heat exchange layer to improve the spatial stability of the hot side heat exchange layer 301 and the cold side heat exchange layer 302. For example, in some embodiments, the two ends of the first fin 221 are respectively in contact with two adjacent heat exchange plates 11 to support and limit the two heat exchange plates 11, so that the two heat exchange plates 11 are not easily deformed and collapsed.

[0065] In some embodiments, Figure 5-Figure 8 As shown, a plurality of first fins 221 are arranged along a third direction F3 to form a plurality of rows of first fin groups 211, the first fin group 211 includes a plurality of first fins 221 arranged at intervals along a second direction F2, a plurality of second fins 222 are arranged along a third direction F3 to form a plurality of rows of second fin groups 212, and the second fin group 212 includes a plurality of second fins 222 arranged at intervals along the second direction F2.

[0066] A heat exchange channel extending generally along the second direction F2 is defined between two adjacent first fins 221 along the third direction F3 for the circulation of the medium on the heating side, and a heat exchange channel extending generally along the third direction F3 is defined between two adjacent first fins 221 arranged along the second direction F2 for the circulation of the medium on the heating side. A heat exchange channel extending generally along the second direction F2 is defined between two adjacent second fins 222 along the third direction F3 for the circulation of the medium on the cooling side, and a heat exchange channel extending generally along the third direction F3 is defined between two adjacent second fins 222 arranged along the second direction F2 for the circulation of the medium on the cooling side.

[0067] As a result, the first heat exchange fin 25 and the second heat exchange fin 26 cause turbulence to allow the heat exchange medium to flow in multiple directions, so as to facilitate heat exchange between the hot side medium and the cold side medium, and the direction of the heat exchange channel is changeable. For example, the hot side medium flowing along the second direction F2 in the hot side heat exchange layer 301 can be reversed and flow along the third direction F3 after passing through a first fin 221, which is beneficial to change the flow path of the heat exchange medium and play a turbulent role.

[0068] The direction of the heat exchange channel is variable. The heat exchange channel can extend along a certain direction, can extend obliquely relative to a certain direction, or can extend in a zigzag manner. For example, in some embodiments, Figure 5 and Figure 7 As shown, the heat exchange channel extending along the third direction F3 is generally formed as a straight channel, which is beneficial to reducing the resistance of the flow along the third direction F3.

[0069] The density difference between the first heat exchange fin 25 and the second heat exchange fin 26 can be adjusted by fin thickness, fin spacing, etc. In some embodiments, the first heat exchange fin 25 includes a plurality of first fins 221, and the second heat exchange fin 26 includes a plurality of second fins 222, and the thickness of the first fin 221 is greater than the thickness of the second fin 222 so that the density of the first heat exchange fin 25 is greater than the density of the second heat exchange fin 26; or the spacing between two adjacent first fins 221 is smaller than the spacing between two adjacent second fins 222, so that the density of the first heat exchange fin 25 is greater than the density of the second heat exchange fin 26; or, the thickness of the first fin 221 is greater than the thickness of the second fin 222, and the spacing between two adjacent first fins 221 is smaller than the spacing between two adjacent second fins 222.

[0070] Specifically, in some embodiments of the present invention, Figure 6 and Figure 8 As shown, the thickness of the first fin 221 along the second direction F2 is greater than the thickness of the second fin 222 along the second direction F2. The greater the thickness of the fin, the greater the volume of the fin in the unit space, that is, the greater the density of the fin, and thus the greater the density of the heat exchange fin. Therefore, the thickness of the first fin 221 along the second direction F2 is greater than the thickness of the second fin 222 along the second direction F2, so that the density of the first heat exchange fin 25 is greater than the density of the second heat exchange fin 26, which is conducive to improving the pressure resistance, reducing the heat exchange amount and the overall flow resistance, and the thickness processing operation is simple and easy to achieve.

[0071] In some specific embodiments, Figure 6 As shown, the thickness t1 of the first fin 221 along the second direction F2 is 0.2 mm to 0.4 mm; in some specific embodiments, such as Figure 8 As shown, the thickness t2 of the second fin 222 along the second direction F2 is 0.2 mm to 0.4 mm. Here, the thickness refers to the distance between the two side surfaces of the fin along the second direction F2. If the thickness of the fin is too small, the pressure resistance will be too low; if the thickness is too large, it will have a greater adverse effect on the flow resistance. Within the above size range, it is beneficial to take into account the dual requirements of pressure resistance and low flow resistance. For example, in some embodiments, t1 is 0.2 mm, 0.3 mm, 0.4 mm, etc. For example, in some embodiments, t2 is 0.2 mm, 0.3 mm, 0.4 mm, etc.

[0072] In some embodiments of the present invention, Figure 6 and Figure 8As shown, among any three adjacent first fins 221 of the same first fin group 211, the spacing between the two first fins 221 at the two ends is L1; among any three adjacent second fins 222 of the same second fin group 212, the spacing between the two second fins 222 at the two ends is L2, wherein L1 is smaller than L2. The larger the fin spacing, the smaller the volume of the fins in the unit space, that is, the smaller the density of the fins, and thus the smaller the density of the heat exchange fins. Therefore, L1 is smaller than L2, which is conducive to making the density of the first heat exchange fin 25 greater than the density of the second heat exchange fin 26, thereby achieving the effect of improving the pressure resistance, reducing the heat exchange amount and the overall flow resistance.

[0073] In some specific embodiments, Figure 6 As shown, among any three adjacent first fins 221 of the same first fin group 211, the distance L1 between the two first fins 221 at the two ends is 4.2 mm to 8.6 mm; in some specific embodiments, such as Figure 8 As shown, among any three adjacent second fins 222 of the same second fin group 212, the distance L2 between the two second fins 222 at the two ends is 4.2 mm to 8.6 mm. Here, the distance between the two fins refers to the distance between the two fins on the same side surface along the second direction F2 (such as Figure 6 The distance between two center points opposite to each other along the second direction F2 on the front side surfaces of the two fins shown.

[0074] If the fin spacing is too small, it will have a significant adverse effect on the flow resistance; if the spacing is too large, the pressure resistance will be too low. Within the above size range, it is beneficial to take into account the dual requirements of pressure resistance and low flow resistance. For example, in some embodiments, L1 is 4.2mm, 6mm, 8.6mm, etc. For example, in some embodiments, L2 is 4.2mm, 6mm, 8.6mm, etc.

[0075] The density of the heat exchange fins can be adjusted by fin thickness, fin spacing, etc. For example, in some embodiments, L1 is equal to L2, and t1 is greater than t2; in some embodiments, t1 is equal to t2, and L1 is less than L2; in some embodiments, t1 is greater than t2, and L1 is less than L2. This can make the density of the first heat exchange fin 25 greater than the density of the second heat exchange fin 26, thereby meeting the multiple requirements of pressure resistance, low heat exchange and low flow resistance. For example, in some embodiments, L1 is 7mm, L2 is 7mm, t1 is 0.4mm, and t2 is 0.3mm; in some embodiments, t1 is 0.2mm, t2 is 0.2mm, L1 is 4.2mm, and L2 is 6mm; in some embodiments, t1 is 0.3mm, t2 is 0.2mm, L1 is 6mm, and L2 is 8.6mm.

[0076] In some specific embodiments, Figure 6As shown, the width b1 of the first fin 221 along the third direction F3 is 1 mm to 2.2 mm; in some specific embodiments, such as Figure 8 As shown, the width b2 of the second fin 222 along the third direction F3 is 1 mm to 2.2 mm. b1 and b2 may be equal or different.

[0077] If the fin width is too small, the fin strength will be reduced, resulting in too low pressure resistance; if the width is too large, the contact area between the heat exchange medium flowing along the second direction F2 and the fin will be increased, thereby having a greater adverse effect on the flow resistance in the second direction F2. Within the above size range, it is beneficial to take into account the dual requirements of pressure resistance and low flow resistance. For example, in some embodiments, b1 is 1mm, 2mm, 2.2mm, etc. For example, in some embodiments, b2 is 1mm, 2mm, 2.2mm, etc.

[0078] In some embodiments, the width b1 of the first fin 221 along the third direction F3 (i.e., the distance between the two side surfaces of the first fin 221 along the third direction F3) is greater than the thickness t1 of the first fin 221 along the second direction F2, so that the first fin 221 is formed into a sheet-like structure. The width b2 of the second fin 222 along the third direction F3 (i.e., the distance between the two side surfaces of the second fin 222 along the third direction F3) is greater than the thickness t2 of the second fin 222 along the second direction F2, so that the second fin 222 is formed into a sheet-like structure, which is conducive to reducing the flow resistance in the third direction F3.

[0079] In some specific embodiments, Figure 6 As shown, the angle α1 between the first fin 221 and the first direction F1 is 0° to 20°. In the embodiment where the first direction F1 is perpendicular to the second direction F2, the angle between the first fin 221 and the second direction F2 is 70° to 90°. Figure 8 As shown, the angle α2 between the second fin 222 and the first direction F1 is 0° to 20°. In the embodiment where the first direction F1 is perpendicular to the second direction F2, the angle between the second fin 222 and the second direction F2 is 70° to 90°. α1 and α2 may be equal or different.

[0080] If the angle between the fin and the first direction F1 is too large, the distance between two adjacent fins will increase, which will have a greater adverse effect on the pressure resistance. Within the above size range, it is conducive to meeting the pressure resistance requirements. For example, in some embodiments, α1 is 0°, 10°, 20°, etc. For example, in some embodiments, α2 is 0°, 10°, 20°, etc.

[0081] In the embodiment where the fins are at a certain angle to the first direction F1, the inclination directions of the fins of multiple rows of fin groups can be the same or different, and the inclination directions of multiple fins in the same fin group can be the same or different. Figure 6and Figure 8 As shown, any two adjacent first fins 221 of the same first fin group 211 have opposite inclination directions, so that the two first fins 221 are arranged in a trapezoidal shape; any two adjacent second fins 222 of the same second fin group 212 have opposite inclination directions, so that the two second fins 222 are arranged in a trapezoidal shape, which is easier to shape and has higher structural stability.

[0082] In some specific embodiments, Figure 6 As shown, the distance h1 between the two opposite side walls of the hot side heat exchange layer 301 along the first direction F1 is 1.4 mm to 3 mm, the corresponding size of the first heat exchange fin 25 along the first direction F1 is 1.4 mm to 3 mm, and the height of the first fin 221 along the first direction F1 is 1.4 mm to 3 mm. In some specific embodiments, such as Figure 8 As shown, the distance h2 between the two opposite side walls of the cold side heat exchange layer 302 along the first direction F1 is 1.4mm-3mm, the corresponding size of the second heat exchange fin 26 along the first direction F1 is 1.4mm-3mm, and the height of the second fin 222 along the first direction F1 is 1.4mm-3mm.

[0083] h1 and h2 can be equal or different. If the distance between the two side walls of the heat exchange layer along the first direction F1 is too small, the flow space of the heat exchange medium will be reduced, which will have a greater adverse effect on the flow resistance; if it is too large, the intermediate heat exchanger 100 will occupy a larger space in the first direction F1, making the structure less compact. Within the above size range, it is beneficial to take into account the dual requirements of low flow resistance and compact structure. For example, in some embodiments, h1 is 1.4mm, 2mm, 3mm, etc. For example, in some embodiments, h2 is 1.4mm, 2mm, 3mm, etc.

[0084] In some embodiments of the present invention, Figure 5-Figure 8 As shown, among any three adjacent first fins 221 of the same first fin group 211, the two ends of the middle first fin 221 along the first direction F1 are respectively connected to the two adjacent first fins 221 through the first connecting piece 231, and the first connecting piece 231 extends along the second direction F2 and abuts against the wall surface of the hot side heat exchange layer 301. The multiple first fins 221 of the first fin group 211 are connected by the first connecting piece 231 to form a toothed structure arranged along the second direction F2 and extending continuously.

[0085] Among any three adjacent second fins 222 of the same second fin group 212, the two ends of the middle second fin 222 along the first direction F1 are respectively connected to two adjacent second fins 222 through second connecting pieces 232, and the second connecting pieces 232 extend along the second direction F2 and abut against the wall surface of the hot side heat exchange layer 301. The multiple second fins 222 of the second fin group 212 are connected by the second connecting piece 232 to form a toothed structure arranged along the second direction F2 and extending continuously.

[0086] By connecting the connecting pieces at both ends along the first direction F1, and the connecting pieces extending along the second direction F2, the relative positions of the multiple fins of the same fin group in the second direction F2 are stabilized, and in some embodiments, they are firmly abutted against the heat exchange plate 11, which is conducive to improving the stability of the heat exchange amount and flow resistance, and can improve the structural stability of the fins, and the fins are not easily deformed, which is conducive to improving the service life. The connecting piece abuts against the wall surface of the heat exchange layer, so that the heat exchange medium can exchange heat with the wall surface through the connecting piece, and then achieve heat exchange with the heat exchange medium in the adjacent heat exchange layer, which is conducive to increasing the heat exchange area and improving the heat exchange efficiency.

[0087] In some embodiments, Figure 5-Figure 8 As shown, two adjacent first connecting pieces 231 along the third direction F3 are connected, and two adjacent second connecting pieces 232 along the third direction F3 are connected. The relative positions of the multiple fin groups in the third direction F3 are stabilized, which is beneficial to improving the flow stability of the heat exchange medium and the structural stability of the fin group. The fins are not easily deformed, which is beneficial to improving the service life.

[0088] The connecting pieces at both ends of the first direction F1 are connected by fins, and the two adjacent connecting pieces along the third direction F3 are connected, which is also conducive to staggering the structure and is more convenient for molding. Figure 6 and Figure 8 As shown, two connecting pieces adjacent to each other along the third direction F3 are partially staggered and connected along the second direction F2.

[0089] In some specific embodiments, Figure 6 As shown, two adjacent first connecting pieces 231 along the third direction F3 are partially staggered in the second direction F2, and the staggered dimension is L3. The distance between two first fins 221 located at both ends of any three adjacent first fins 221 along the second direction F2 is L1, and L3 / L1 is 0.2-0.3. In some specific embodiments, as Figure 8 As shown, two adjacent second connecting pieces 232 along the third direction F3 are partially staggered in the second direction F2 and the staggered dimension is L4, and the spacing between two second fins 222 at both ends of any three adjacent second fins 222 along the second direction F2 is L2, and L4 / L2 is 0.2-0.3.

[0090] Here, partial staggering means that the surfaces of the two connecting sheets facing each other along the third direction F3 are partially connected, and the unconnected parts of the two connecting sheets are respectively located on both sides of the connected part along the second direction F2. The staggering size means the size of the unconnected part of each connecting sheet along the second direction F2.

[0091] L3 and L4 can be equal or unequal, and L3 / L1 and L4 / L2 can be equal or unequal. If L3 / L1 is too small, the spacing between the first fin 221 and the first fin 221 on one side of the adjacent first fin group 211 along the second direction F2 will be too small; if L3 / L1 is too large, the spacing between the first fin 221 and the first fin 221 on the other side of the adjacent first fin group 211 along the second direction F2 will be too small, both of which will have a significant adverse effect on the flow resistance of the hot side heat exchange layer 301 along the second direction F2. Similarly, if L4 / L2 is too large or too small, it will also have a significant adverse effect on the flow resistance of the cold side heat exchange layer 302 along the second direction F2. Within the above size range, it is conducive to meeting the low flow resistance requirement.

[0092] For example, in some embodiments, L3 / L1 is 0.2 mm, 0.25 mm, 0.3 mm, etc. For example, in some embodiments, L4 / L2 is 0.2 mm, 0.25 mm, 0.3 mm, etc.

[0093] In some specific embodiments, Figure 1-Figure 3 As shown, the cold side openings and the hot side openings are arranged along the second direction F2, and the cold side openings include openings arranged along the third direction F3 (such as Figure 2 The hot side opening includes a cold side medium inlet 41 and a cold side medium outlet 42 arranged along the third direction F3, and the hot side opening includes a hot side medium inlet 43 and a hot side medium outlet 44 arranged along the third direction F3. The cold side medium can enter the cold side heat exchange layer 302 through the cold side medium inlet 41 and flow out of the cold side heat exchange layer 302 through the cold side medium outlet 42; the hot side medium can enter the hot side heat exchange layer 301 through the hot side medium inlet 43 and flow out of the hot side heat exchange layer 301 through the hot side medium outlet 44.

[0094] 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. Figure 1-Figure 4 As shown, the first direction F1 is the up-down direction, the second direction F2 is the front-back direction, and the third direction F3 is the left-right direction; for another example, the first direction F1 is the up-down 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.

[0095] 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. Figure 1-Figure 3As 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, thereby reducing the heat exchange amount.

[0096] It should be noted that 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 are not limited to the arrangement positions in the first direction F1. Figure 1-Figure 3 As shown, they are arranged on the same side in the first direction F1 to facilitate the connection between the intermediate heat exchanger 100 and structures such as the collecting plate 210; the four openings can also be partially arranged on one side in the first direction F1 and the other partially arranged on the other side in the first direction F1, which is also within the protection scope of the present application.

[0097] like Fig. 9 As shown, the thermal management system 200 disclosed in the embodiment of the present application includes the intermediate heat exchanger 100 disclosed in the embodiment of the present application. Since the intermediate heat exchanger 100 according to the embodiment of the present utility model has the above-mentioned beneficial technical effects, the thermal management system 200 according to the embodiment of the present utility model, by making the density of the first heat exchange fins 25 in the hot side heat exchange layer 301 greater than the density of the second heat exchange fins 26 in the cold side heat exchange layer 302, is conducive to improving the pressure resistance of the first heat exchange fins 25, reducing the flow resistance of the second heat exchange fins 26 and thus reducing the overall flow resistance, and reducing the heat exchange within a reasonable range, so as to meet the cooling and heating requirements of the thermal management system 200.

[0098] In the present application, the plate heat exchanger is used as an intermediate heat exchanger, and the plate heat exchanger is used to guide the refrigerant liquid condensed by the condenser and the refrigerant steam after absorbing heat and vaporizing by the evaporator for heat exchange, thereby increasing the supercooling degree before the throttle valve, thereby reducing throttling losses and improving refrigeration efficiency. In addition, the intermediate heat exchanger 100 can be independent of the flow channel of the collector plate 210, for example, using an inserted structure and fixed to the collector plate 210 by bolts. Compared with the heat exchange structure in the refrigerant flow channel plate in the related art, the intermediate heat exchanger 100 has a more efficient heat exchange capacity, which can greatly reduce the plate size of the collector plate 210 and achieve a compact spatial structure.

[0099] like Fig.10As 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 utility model has the above-mentioned beneficial technical effects, the vehicle 1000 according to the embodiment of the present utility model, by making the density of the first heat exchange fin 25 in the hot side heat exchange layer 301 greater than the density of the second heat exchange fin 26 in the cold side heat exchange layer 302, is conducive to improving the pressure resistance of the first heat exchange fin 25, reducing the flow resistance of the second heat exchange fin 26 and thus reducing the overall flow resistance, and reducing the heat exchange within a reasonable range, so as to meet the cooling and heating requirements of the thermal management system 200.

[0100] 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, a vehicle, a ship, a spacecraft, etc. Among them, the spacecraft can include an airplane, a rocket, a space shuttle, and a spacecraft.

[0101] Among them, vehicle 1000 can be a new energy vehicle. In some embodiments, the new energy vehicle can be a pure electric vehicle with a 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 a motor as the main driving force. Regarding the internal combustion engine and 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 motor can use power batteries, hydrogen fuel cells, etc., which are not specifically limited here. It should be noted that this is only an exemplary description of the structure of new energy vehicles, etc., and it does not limit the scope of protection of the utility model.

[0102] 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, wherein the thermal management system 200 mainly includes: valves, heat exchangers, compressors and pumps, such as electronic water pumps or other water pumps, wherein the thermal management system 200 has a circulating refrigerant, which may be Freon, propane, etc.

[0103] A thermal management system 200 according to a specific embodiment of the present invention is described in detail below 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 to the present invention.

[0104] like Figure 1-Figure 9As shown, 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 direction, so that the intermediate heat exchanger 100 can be independent of the collecting plate 210. The connecting pipes 12 adopt an inserted structure to realize pipeline connection, and the intermediate heat exchanger 100 is fixed to the collecting plate 210 by fasteners to realize structural integration, which can greatly reduce the plate size of the collecting plate 210 and realize a compact structure.

[0105] The intermediate heat exchanger 100 includes a heat exchanger body 10, a first heat exchange fin 25, and a second heat exchange fin 26. 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, wherein 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.

[0106] A plurality of heat exchange plates 11 are stacked in the up-down direction, and the space between the mounting plate 13 and the bottom plate 14 is divided into a hot side heat exchange layer 301 and a cold side heat exchange layer 302. The hot side heat exchange layer 301 and the cold side heat exchange layer 302 are alternately arranged in the up-down direction. The hot side medium inlet 43 and the hot side medium outlet 44 are respectively connected to the hot side heat exchange layer 301, and the cold side medium inlet 41 and the cold side medium outlet 42 are respectively connected to the cold side heat exchange layer 302.

[0107] The first heat exchange fin 25 is arranged in the hot side heat exchange layer 301, and the second heat exchange fin 26 is arranged in the cold side heat exchange layer 302. The density of the first heat exchange fin 25 is greater than the density of the second heat exchange fin 26. The hot side medium is not sensitive to flow resistance, and the use of the first heat exchange fin 25 with a higher density can obtain a greater pressure resistance; the cold side medium is sensitive to flow resistance, and the use of the second heat exchange fin 26 with a lower density can obtain a lower flow resistance, and is conducive to reducing the heat exchange amount, so that the heat exchange amount will not be too large.

[0108] The high-temperature and high-pressure liquid refrigerant flows into the hot side heat exchange layer 301 through the hot side medium inlet 43, and then flows out through the hot side medium outlet 44. The low-temperature and low-pressure gaseous refrigerant flows into the cold side heat exchange layer 302 through the cold side medium inlet 41, and then flows out through the cold side medium outlet 42. The high-temperature and high-pressure liquid refrigerant and the low-temperature and low-pressure gaseous refrigerant exchange heat through the heat exchange plate 11, the first heat exchange fin 25 and the second heat exchange fin 26.

[0109] The first heat exchange fin 25 is formed by stamping a metal plate to form a plurality of first connecting plates 231 and a plurality of first fins 221 located between the upper and lower layers of first connecting plates 231; the second heat exchange fin 26 is formed by stamping a metal plate to form a plurality of second connecting plates 232 and a plurality of second fins 222 located between the upper and lower layers of second connecting plates 232.

[0110] Among them, Figure 6 As shown, the first fin 221 and the first connecting piece 231 are both sheets extending in the left-right direction, and a first connecting piece 231 at the upper end connects two adjacent first fins 221 in front and behind to form an inverted U-shaped tooth structure, and a first connecting piece 231 at the lower end connects two adjacent first fins 221 in front and behind to form a positive U-shaped tooth structure. The tooth structures corresponding to the two adjacent first connecting pieces 231 in the left and right are arranged in staggered teeth in the front-to-back direction, and the non-staggered parts of the two first connecting pieces 231 are connected as a whole.

[0111] like Figure 8 As shown, the second fins 222 and the second connecting pieces 232 are both sheets extending in the left-right direction, and a second connecting piece 232 at the upper end connects two adjacent second fins 222 in front and back to form an inverted U-shaped tooth structure, and a second connecting piece 232 at the lower end connects two adjacent second fins 222 in front and back to form a positive U-shaped tooth structure. The tooth structures corresponding to the two adjacent second connecting pieces 232 in the left and right are arranged in staggered teeth in the front-to-back direction, and the non-staggered parts of the two second connecting pieces 232 are connected as a whole.

[0112] Among any three adjacent first fins 221 of the same first fin group 211, the spacing between the two first fins 221 located at the two ends is L1, and among any three adjacent second fins 222 of the same second fin group 212, the spacing between the two second fins 222 located at the two ends is L2, 4.2mm≤L1<L2≤8.6mm. Within the above size range, it is beneficial to take into account the dual requirements of pressure resistance and low flow resistance.

[0113] The thickness t1 of the first fin 221 along the front-to-back direction is greater than the thickness t2 of the second fin 222 along the front-to-back direction, and 0.2mm≤t2<t1≤0.4mm. Within the above size range, it is beneficial to take into account the dual requirements of pressure resistance and low flow resistance.

[0114] L1<L2 and t2<t1, which is conducive to making the density of the first heat exchange fins 25 greater than the density of the second heat exchange fins 26, thereby achieving the effect of reducing the heat exchange amount and the overall flow resistance.

[0115] Two adjacent first connecting pieces 231 along the left-right direction are partially staggered in the front-to-back direction with a staggered dimension of L3, 0.2≤L3 / L1≤0.3; two adjacent second connecting pieces 232 along the left-right direction are partially staggered in the front-to-back direction with a staggered dimension of L4, 0.2≤L4 / L2≤0.3. Within the above-mentioned dimension range, it is beneficial to meet the low flow resistance requirements.

[0116] The width of the first fin 221 along the left-right direction is b1, 1mm≤b1≤2.2mm, and the width of the second fin 222 along the left-right direction is b2, 1mm≤b2≤2.2mm. Within the above size range, it is beneficial to take into account the dual requirements of pressure resistance and low flow resistance.

[0117] The angle between the first fin 221 and the up-down direction is α1, 0°<α1≤20°, and the angle between the second fin 222 and the up-down direction is α2, 0°<α2≤20°. Within the above size range, the first fin 221 and the second fin 222 are easy to form and have higher structural stability.

[0118] The distance between the two side walls of the hot side heat exchange layer 301 in the up and down direction, that is, the height of the first fin 221, is h1, 1.4mm≤h1≤3mm, and the distance between the two side walls of the cold side heat exchange layer 302 in the up and down direction, that is, the height of the second fin 222, is h2, 1.4mm≤h2≤3mm. Within the above-mentioned size range, it is beneficial to take into account the dual requirements of low flow resistance and compact structure.

[0119] The density of the heat exchange fins can be adjusted by the above-mentioned fin spacing L1 and L2, fin thickness t1 and t2, and the above-mentioned ratios L3 / L1 and L4 / L2, fin width b1 and b2, fin angle α1 and α2, fin height h1 and h2, which are conducive to meeting the multiple requirements of pressure resistance, low flow resistance, fin molding, structural stability and structural compactness. By using the high-density first heat exchange fin 25 in the hot side heat exchange layer 301, it is conducive to improving the heat exchange and pressure resistance; by using the low-density second heat exchange fin 26 in the cold side heat exchange layer 302, it is conducive to reducing the flow resistance and adjusting the heat exchange amount so that the heat exchange amount is not too high and is within a reasonable range.

[0120] Other structures and operations of the thermal management system 200 and the vehicle 1000 according to the embodiment of the present invention are well known to those skilled in the art and will not be described in detail herein.

[0121] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installation", "connection" and "connection" 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 a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0122] In the description of this specification, the description with reference to the terms "embodiment", "specific embodiment", "example", etc. means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the utility model. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0123] Although the embodiments of the present invention 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 spirit of the present invention, and that the scope of the present invention is defined by the claims and their equivalents.

Claims

1. An intermediate heat exchanger, characterized in that: include: A heat exchanger body, wherein the heat exchanger body has a cold side heat exchange layer for passing a cold side medium and a hot side heat exchange layer for passing a hot side medium; A first heat exchange fin, wherein the first heat exchange fin is disposed in the hot side heat exchange layer; The second heat exchange fin is arranged in the cold side heat exchange layer, wherein: The density of the first heat exchange fins is greater than the density of the second heat exchange fins.

2. The intermediate heat exchanger according to claim 1, characterized in that: The hot-side heat exchange layer and the cold-side heat exchange layer are arranged along a first direction, the first heat exchange fin includes a plurality of first fins, and the two ends of the first fin along the first direction are respectively abutted against the two side walls opposite to the hot-side heat exchange layer, and the second heat exchange fin includes a plurality of second fins, and the two ends of the second fin along the first direction are respectively abutted against the two side walls opposite to the cold-side heat exchange layer.

3. The intermediate heat exchanger according to claim 2, characterized in that: A plurality of the first fins are arranged into a plurality of rows of first fin groups along a third direction, the first fin group includes a plurality of the first fins arranged at intervals along a second direction, a plurality of the second fins are arranged into a plurality of rows of second fin groups along the third direction, the second fin group includes a plurality of the second fins arranged at intervals along the second direction, and the first direction, the second direction and the third direction intersect each other.

4. The intermediate heat exchanger according to claim 3, characterized in that: A thickness of the first fin along the second direction is greater than a thickness of the second fin along the second direction.

5. The intermediate heat exchanger according to claim 3 or 4, characterized in that: Among any three adjacent first fins in the same first fin group, the distance between the two first fins located at both ends is L1; among any three adjacent second fins in the same second fin group, the distance between the two second fins located at both ends is L2, wherein L1 is smaller than L2.

6. The intermediate heat exchanger according to claim 3, characterized in that: The thickness of the first fin along the second direction is 0.2 mm to 0.4 mm; and / or the thickness of the second fin along the second direction is 0.2 mm to 0.4 mm.

7. The intermediate heat exchanger according to claim 3, characterized in that: The width of the first fin along the third direction is 1 mm to 2.2 mm; and / or the width of the second fin along the third direction is 1 mm to 2.2 mm.

8. The intermediate heat exchanger according to claim 3, characterized in that: The included angle between the first fin and the first direction is 0° to 20°; and / or the included angle between the second fin and the first direction is 0° to 20°.

9. The intermediate heat exchanger according to claim 3, characterized in that: Among any three adjacent first fins of the same first fin group, the distance between the two first fins located at both ends is 4.2mm~8.6mm; and / or, among any three adjacent second fins of the same second fin group, the distance between the two second fins located at both ends is 4.2mm~8.6mm.

10. The intermediate heat exchanger according to claim 3, characterized in that: Among any three adjacent first fins of the same first fin group, two ends of the middle first fin along the first direction are respectively connected to two adjacent first fins through first connecting pieces, and the first connecting piece extends along the second direction and abuts against the wall surface of the hot-side heat exchange layer; Among any three adjacent second fins of the same second fin group, the two ends of the middle second fin along the first direction are respectively connected to two adjacent second fins through second connecting pieces, and the second connecting pieces extend along the second direction and abut against the wall surface of the hot side heat exchange layer.

11. The intermediate heat exchanger according to claim 10, characterized in that: Two adjacent first connecting pieces along the third direction are connected, and two adjacent second connecting pieces along the third direction are connected.

12. The intermediate heat exchanger according to claim 10, characterized in that: Two adjacent first connecting pieces along the third direction are partially staggered in the second direction and the staggered dimension is L3, and the distance between two first fins at both ends of any three adjacent first fins along the second direction is L1, and L3 / L1 is 0.2-0.3; and / or, Two adjacent second connecting pieces along the third direction are partially staggered in the second direction and the staggered dimension is L4. The distance between two second fins at both ends of any three adjacent second fins along the second direction is L2, and L4 / L2 is 0.2-0.

3.

13. The intermediate heat exchanger according to claim 2, characterized in that: The distance between the two side walls of the hot side heat exchange layer opposite to each other along the first direction is 1.4 mm to 3 mm; and / or the distance between the two side walls of the cold side heat exchange layer opposite to each other along the first direction is 1.4 mm to 3 mm.

14. A thermal management system, characterized in that: Comprising an intermediate heat exchanger according to any one of claims 1-13.

15. A vehicle, characterized in that: Comprising a thermal management system according to claim 14.

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