Heat exchanger and heat management assembly

Abstract

The utility model relates to a heat exchanger and a heat management component, the heat exchanger is provided with a flow channel, the flow channel comprises a first flow channel and a second flow channel, a medium in the first flow channel can exchange heat with a medium in the second flow channel, and the flow channel comprises at least one turning section. The included angle between the flow direction of a medium before flowing into the steering section and the flow direction of the medium flowing out of the steering section is defined as a steering angle, the steering angle of the steering section is 45-180 degrees, a first flow guide plate is arranged in at least one steering section and is an arc-shaped plate, a first surface is defined as a plane extending from the steering section, and a second surface is defined as a plane extending from the steering section. The extending direction of the first flow guide plate is perpendicular to the first face, and the section of the first flow guide plate can divide at least part of the circulation section of the steering section into two parts with the ratio of 1: 1 to 1: 2. The heat exchanger is favorable for improving the phenomena of non-uniform fluid distribution and turbulent flow, so that the fluid pressure loss is obviously reduced, and the overall performance of a system is improved.

Description

TECHNICAL FIELD

[0001] The utility model relates to fluid control technical field, concretely relates to a heat exchanger and heat management assembly for vehicle. BACKGROUND

[0002] The heat exchanger has various different types, taking the intermediate heat exchanger as an example, it can be used as the part of the automobile air conditioning system, is used for increasing the refrigerant supercooling degree before the air conditioning system throttling element, reduces the evaporator import enthalpy value, improves the system refrigerating capacity.Meanwhile, the compressor suction refrigerant dryness or superheat is promoted, and the compressor is ensured not to be liquid hit. However, when the low pressure side of the intermediate heat exchanger is overheated gaseous, if the pressure drop is too high, the compressor suction density will be reduced, the power consumption will be increased, and the system refrigeration coefficient will be reduced. SUMMARY

[0003] The heat exchanger is beneficial to reduce the flow resistance and improve the overall performance of the heat management assembly.

[0004] The heat exchanger is beneficial to reduce the flow resistance and improve the overall performance of the heat management assembly.

[0005] To achieve the above object, the heat exchanger provided by the technical scheme has a flow channel, the flow channel includes a first flow channel and a second flow channel, the medium in the first flow channel can exchange heat with the medium in the second flow channel, the flow channel includes at least one turning section, the included angle between the flow direction before the medium flows into the turning section and the flow direction after the medium flows out of the turning section is defined as a turning angle, the turning angle of the turning section is 45-180 degrees, a first flow guide plate is arranged in at least one turning section, the first flow guide plate is an arc-shaped plate, the first surface is defined as the plane extended by the turning section, the extension direction of the first flow guide plate is perpendicular to the first surface, and the cross section of the first flow guide plate can separate the flow passage cross section of at least part of the turning section into two parts in a ratio of 1:1 to 1:2.

[0006] In the technical scheme, the first flow guide plate is arranged in at least one turning section, the cross section of the first flow guide plate can separate the flow passage cross section of at least part of the turning section into two parts in a ratio of 1:1 to 1:2, the fluid concentrated in the wall surface close to one side at the turning section can be effectively distributed, the fluid is evenly distributed in the turning section, the uneven fluid distribution and turbulence phenomenon can be improved, the fluid pressure loss can be obviously reduced, and the overall performance of the system can be improved.

[0007] The heat management assembly provided by the technical scheme is provided with the heat exchanger, and the first flow guide plate is arranged in the at least one turning section, the cross section of the first flow guide plate can divide the flow passage cross section of the at least one turning section into two parts in a ratio of 1:1 to 1:2, the fluid concentrated on one side of the wall surface of the turning section can be effectively distributed, the fluid is evenly distributed in the turning section, the uneven distribution and turbulence of the fluid can be improved, the fluid pressure loss is obviously reduced, and the overall performance of the system is improved. BRIEF DESCRIPTION OF DRAWINGS

[0008] Figure 1 It is a schematic diagram of the overall structure of a heat exchanger;

[0009] Figure 2 It is a schematic diagram of the overall structure of a heat exchanger; Figure 1

[0010] Figure 3 It is a schematic diagram of the overall structure of a heat exchanger; Figure 1

[0011] Figure 4 It is a schematic diagram of the overall structure of a heat exchanger; Figure 1

[0012] Figure 5 It is a schematic diagram of the overall structure of a heat exchanger;

[0013] Figure 6 Figure 5 It is a schematic diagram of the overall structure of a heat exchanger;

[0014] Figure 7 It is a schematic diagram of the overall structure of a heat exchanger;

[0015] Figure 8 It is a schematic diagram of the overall structure of a heat exchanger; Figure 7

[0016] Figure 9 It is a schematic diagram of the overall structure of a heat exchanger;

[0017] Figure 10 It is a schematic diagram of the overall structure of a heat exchanger;

[0018] Figure 11 It is a schematic diagram of the overall structure of a heat exchanger; Figure 10

[0019] Figure 12 It is a schematic diagram of the overall structure of a heat exchanger;​​​​​​Figure 10 structure diagram of the heat exchanger shown in the third perspective view of the main shell;

[0020] Figure 13 for Figure 5 simulation fluid streamline diagram in the first flow channel of the heat exchanger without flow guide structure;

[0021] Figure 14 for Figure 5 simulation fluid streamline diagram in the first flow channel of the heat exchanger with the first flow guide plate;

[0022] Figure 15 structure diagram of the heat exchanger provided by the fifth embodiment of the present application;

[0023] Figure 16 for Figure 15 structure diagram of the heat exchanger shown in the second perspective view;

[0024] Figure 17 for Figure 15 exploded structure diagram of the heat exchanger shown;

[0025] Figure 18 for Figure 15 structure diagram of the first flow channel of the main shell of the heat exchanger in embodiment A;

[0026] Figure 19 for Figure 15 structure diagram of the first flow channel of the main shell of the heat exchanger in embodiment B;

[0027] Figure 20 for Figure 15 structure diagram of the first flow channel of the main shell of the heat exchanger in embodiment C;

[0028] Figure 21 for Figure 15 structure diagram of the first flow channel of the main shell of the heat exchanger in embodiment D;

[0029] Figure 22 for Figure 15 structure diagram of the first flow channel of the main shell of the heat exchanger in embodiment E;

[0030] Figure 23 for Figure 15 structure diagram of the first flow channel of the main shell of the heat exchanger in embodiment F;

[0031] Figure 24 for Figure 15 structure diagram of the first flow channel of the main shell of the heat exchanger in embodiment G;

[0032] Figure 25 for Figure 15Structure diagram of embodiment H of the first flow channel of the main housing of the heat exchanger shown;

[0033] Figure 26 For Figure 15 Structure diagram of embodiment I of the first flow channel of the main housing of the heat exchanger shown;

[0034] Figure 27 For Figure 15 Structure diagram of embodiment J of the first flow channel of the main housing of the heat exchanger shown;

[0035] Figure 28 For Figure 15 Structure diagram of embodiment L of the first flow channel of the main housing of the heat exchanger shown;

[0036] Figure 29 For Figure 28 C-C view of the heat exchanger shown;

[0037] Figure 30 Structure diagram of the first embodiment of the heat management assembly;

[0038] Figure 31 Structure diagram of the second embodiment of the heat management assembly.

[0039] In the figure:

[0040] 1-flow channel plate; 4-accumulator; 10-main housing; 11-first groove; 12-second groove; 21-first sealing plate; 22-second sealing plate; 23-condenser; 24-evaporator; 31-first flow channel; 311-first inlet; 312-first outlet; 313-straight section; 314-turning section; 3144-arc-shaped outer wall; 3145-arc-shaped inner wall; 32-second flow channel; 321-second inlet; 322-second outlet; 323-straight section; 315-first flow guide plate; 316-second flow guide plate; 3161-channel; 317-inlet chamfer structure; 318-outlet chamfer structure; 319-inlet straight section; 3110-introduction straight section; 3111-extended turning section; 3112-lateral introduction section; 3113-introduction turning section; 3114-oblique introduction section; 3131-first straight section 3132-second straight section; 3133-third straight section; 3134-fourth straight section; 3141-first turning section; 3142-second turning section; 3143-third turning section; 320-circular arc section; 33-separation plate; 330-flow guide surface; 301-first valve device; 302-second valve device; 303-third valve device; 304-fourth valve device; 305-fifth valve device; 306-sixth valve device; 307-seventh valve device; 41-low pressure connector; 42-high pressure connector. DETAILED DESCRIPTION

[0041] In order to make the person skilled in the art better understand the utility model scheme, the utility model is further explained in detail below in combination with the drawings and specific embodiments.

[0042] In this paper, the terms such as 'up, down, inner, outer' are established based on the positional relationship shown in the drawings, and according to the different drawings, the corresponding positional relationship may also change accordingly, therefore, it cannot be understood as an absolute limitation on the scope of protection; moreover, the relationship terms such as 'first' and'second' are only used to distinguish one component from another component with the same name, and do not necessarily require or imply any such actual relationship or order between the components.

[0043] Please refer to Figure 1 , Figure 1 It is a schematic diagram of the overall structure of a heat exchanger; Figure 2 It is Figure 1 The exploded structure schematic diagram of the heat exchanger shown in the figure; Figure 3 It is Figure 1 The structure schematic diagram of the low-pressure side of the heat exchanger shown in the figure; Figure 4 It is Figure 1 The structure schematic diagram of the high-pressure side of the heat exchanger shown in the figure.

[0044] As shown in the figure, in a specific embodiment, the heat exchanger provided by the utility model is a H-shaped intermediate heat exchanger, mainly composed of a main shell 10 located in the middle and a first sealing plate 21 and a second sealing plate 22 located on both sides of the main shell 10, the main shell 10 can be formed by cold extrusion process, and then subsequent machining is carried out to meet the technical requirements, the main shell 10 has a first surface a and a second surface b in the thickness direction, the first surface a is formed with a first groove 11, and the second surface b is formed with a second groove 12, that is, the main shell 10 is provided with a flow channel groove, the flow channel groove includes the first groove 11 and the second groove 12, the bottom of the first groove 11 and the second groove 12 is in a planar shape, and the cross section of both is in the shape of 'H', the first sealing plate 21 covers the first surface a to seal the first groove 11 and form a first flow channel 31, and the second sealing plate 22 covers the second surface b to seal the second groove 12 and form a second flow channel 32, the depth of the first groove 11 is greater than that of the second groove 12, the first flow channel 31 flows through low-pressure refrigerant, and the second flow channel 32 flows through high-pressure refrigerant.

[0045] The first flow channel 31 is provided with a first inlet 311 and a first outlet 312 at two ends thereof for medium inflow and outflow, and the second flow channel 32 is provided with a second inlet 321 and a second outlet 322 at two ends thereof for medium inflow and outflow, the first flow channel 31 has three parallel straight line sections 313 from the first inlet 311 to the first outlet 312, and two adjacent straight line sections 313 are connected in a head-to-tail mode through a semicircular turning section 314, the turning angle of the turning section 314 is defined as the included angle between the flow direction before the medium inflows into the turning section 314 and the flow direction after the medium outflows from the turning section 314, and the turning angle of the turning section 314 is 180° (the same below), the medium can be turned by 180° through the turning section 314, and the first flow channel 31 has an overall "S" shape, one end of which is curved, and the second flow channel 32 has a shape similar to the first flow channel 31.

[0046] Due to the limitation of installation space and other reasons, in order to meet the requirement of heat exchange performance, the first flow channel 31 and the second flow channel 32 are as long as possible and have an "S" shape, and the semicircular turning section 314 of the flow channel form can cause uneven fluid distribution and turbulence due to the sudden change of the fluid flow direction, so that the pressure loss is large.

[0047] Please refer to Figure 5 、 Figure 6 , Figure 5 a decomposition structure schematic view of a heat exchanger provided by the first embodiment of the utility model; Figure 6 as shown in Figure 5 the structure schematic view of the high-pressure side of the heat exchanger.

[0048] In order to solve the above technical problems, the first flow channel 31 of the heat exchanger is provided with a first flow guide plate 315 inside two semicircular turning sections 314, and a second flow guide plate 316 is arranged inside three smooth sections of the first flow channel 31.

[0049] The transition angle of the smooth section is defined as the included angle between the flow direction before the medium inflows into the smooth section and the flow direction after the medium outflows from the smooth section, and the transition angle of the smooth section is greater than or equal to 0 degrees and less than 45 degrees, in the embodiment, the transition angle of the smooth section is 0 degrees, the inlet medium flow direction is consistent with the outlet medium flow direction, which is shown as a straight line section 313 in the figure, the inlet of the heat exchanger is directly connected to the inlet of the straight line section 313, and the outlet of the straight line section 313 is connected to the inlet of the turning section 314.

[0050] Specifically, the first flow guide plate 315 is arc-shaped, and the arc of the first flow guide plate 315 is consistent with the flow direction of the corresponding semicircular turning section 314, that is, the first flow guide plate 315 is also semicircular in shape, the first surface S1 is defined as the plane on which the turning section 314 extends, the first flow guide plate 315 protrudes along the L direction and is perpendicular to the first surface S1, the first flow guide plate 315 is located at the middle position of the semicircular turning section 314 of the first flow passage 31, and the cross section thereof can separate the flow passage cross section of at least part of the turning section 314 into two parts in a ratio of 1:1 to 1:2. In this embodiment, the separation ratio is 1:1.

[0051] Since the second flow guide plate 316 in this embodiment is low in height, it can also be regarded as a flow guide rib. Two second flow guide plates 316 are respectively arranged in each straight section 313, and the two second flow guide plates 316 are arranged at equal intervals, that is, the cross-sectional areas of the three sub-flow passages separated by the two second flow guide plates 316 are substantially the same. The first flow guide plate 315 and the second flow guide plate 316 have a spacing distance along the flow direction, the end of the first flow guide plate 315 corresponds to the passage between the two second flow guide plates 316, and the two ends of the second flow guide plate 316 are in the shape of a streamlined sharp head to reduce fluid resistance as much as possible.

[0052] Similarly, the heat exchanger also has a flow guide plate structure on the high-pressure side, that is, the interior of the two semicircular turning sections 314 of the second flow passage 32 also respectively has a first flow guide plate 315. Unlike the first flow passage 31, since the second flow passage 32 is a high-pressure flow passage, in this embodiment, the interiors of the three straight sections 323 are not designed with second flow guide plates 316.

[0053] By increasing the first flow guide plate 315, the flow passage cross section is separated into two parts in a ratio of 1:1, which can effectively distribute the fluid concentrated near one side of the wall at the turning section, and the fluid is evenly distributed at the turning section, which can improve the uneven distribution and turbulence of the fluid, thereby significantly reducing the fluid pressure loss and improving the overall performance of the system.

[0054] Of course, two first flow guide plates 315 can also be arranged in the semicircular turning section 314, and the two first flow guide plates 315 are arranged at equal intervals, that is, the cross-sectional areas of the three sub-flow passages separated by the two first flow guide plates 315 are substantially the same.

[0055] The wall forming the turning section 314 comprises an arc-shaped outer wall 3144 and an arc-shaped inner wall 3145, the curvature radius of the arc-shaped outer wall 3144 is greater than that of the arc-shaped inner wall 3145, and the first flow guide plate 315 extends from the inlet end M of the turning section 314 to the outlet end N of the turning section 314.

[0056] The first flow guide plate 315 can be arranged to be inclined to the arc-shaped outer wall 3144 or the arc-shaped inner wall 3145, and after being arranged to be inclined, the flow passage section is divided into a range of 1:1 to 1:2.

[0057] Please refer to Figure 7 、 Figure 8 , Figure 7 The structure diagram of the low-pressure side of the heat exchanger provided by the second embodiment of the utility model is shown. Figure 8 For Figure 7 The axial side view of the heat exchanger shown.

[0058] As shown in the figure, compared with the first embodiment, the difference of the present embodiment is that:

[0059] Three straight sections 313 of the first flow channel 31 are respectively provided with a second flow guide plate 316, and the second flow guide plate 316 is not in the form of a flow guide rib, but has the same height as the first flow guide plate 315, the adjacent first flow guide plate 315 and the second flow guide plate 316 are not disconnected in the flow direction, but are arranged continuously, and the length of the head and tail second flow guide plates 316 does not penetrate the straight section 313, but is shortened by a certain distance relative to the straight section 313. This structure can also achieve the purpose of increasing the heat exchange capacity and reducing the flow resistance

[0060] Moreover, the second flow guide plate 316 is added before entering the turning section 314, which can divert the fluid in the flow channel in advance, so that the fluid flowing through the turning section 314 will not cause a large amount of fluid to deviate to one side, thereby improving the uniformity of fluid distribution.

[0061] In the present embodiment, the same parts as in the first embodiment are given the same reference numerals, and the same textual description is omitted.

[0062] Please refer to Figure 9 , Figure 9 The structure diagram of the low-pressure side of the heat exchanger provided by the third embodiment of the utility model is shown.

[0063] As shown in the figure, compared with the first embodiment, the difference of the present embodiment is that:

[0064] The second flow guide plate 316 is internally provided with one or more channels 3161, which are communicated with both ends of the second flow guide plate 316 along the flow direction of the second flow guide plate 316, and the cross-sectional area of the channel 3161 can be of any shape, such as a circle, a rectangle, or a polygon, etc.

[0065] By designing the channel 3161 in the interior of the second flow guide plate 316, the fluid can not only flow through the exterior of the second flow guide plate 316 under the flow guiding effect of the second flow guide plate 316, but also a part of the fluid can flow through the interior of the second flow guide plate 316, thereby further increasing the flow and heat exchange area relative to the first embodiment, and also reducing the fluid deceleration, achieving the purpose of reducing the flow resistance.

[0066] In the embodiment, the same parts as those in the first embodiment are given the same reference numerals, and the same textual description is omitted.

[0067] It should be noted that in other embodiments, the interior of the first flow guide plate 315 can also be provided with one or more channels 3161, and the channel 3161 penetrates along the flow direction of the first flow guide plate 315.

[0068] Please refer to Figures 10 to 12 , Figure 10 the structure diagram of the low-pressure side of the heat exchanger provided by the fourth embodiment of the present application; Figure 11 is Figure 10 the structure diagram of the high-pressure side of the heat exchanger shown in the figure;

[0069] Figure 12 is Figure 10 the front view of the low-pressure side of the heat exchanger. As shown in the figure, relative to the first embodiment, the difference of the present embodiment is that:

[0070] In order to reduce the flow resistance, the first flow passage 31 and the second flow passage 32 of the heat exchanger are in a smooth arc shape, and do not have a turning section with a turning angle greater than 90°. Therefore, relative to the first embodiment, the interior of the first flow passage 31 and the second flow passage 32 is not designed with the first flow guide plate 315, but only with the second flow guide plate 316, and the extension direction of the second flow guide plate 316 is consistent with the flow direction of the first flow passage 31 and the second flow passage 32.

[0071] In the embodiment, the same parts as those in the first embodiment are given the same reference numerals, and the same textual description is omitted.

[0072] Please refer to Figure 13 , Figure 14 , Figure 13 the simulation fluid streamline diagram of the heat exchanger before the flow guide structure is added; Figure 14 the simulation fluid streamline diagram of the heat exchanger after the flow guide structure is added.

[0073] As shown in the figure, according to the simulation fluid streamline diagram before adding the guide structure and after adding the guide structure, it can be seen that before adding the guide structure, the first flow channel 31 and the second flow channel 32 in the shape of "S" will cause uneven fluid distribution and turbulence due to the sudden change of the flow direction of the fluid at the semicircular turning section, thereby causing the pressure loss to become large.

[0074] By adding the first guide plate 315, the flow passage cross section is divided into two parts in the ratio of 1:1 to 1:2, the fluid concentrated near one side of the wall at the turning section can be effectively distributed, the fluid is evenly distributed at the turning section, the uneven fluid distribution and turbulence phenomenon can be improved, thereby obviously reducing the fluid pressure loss and improving the overall performance of the system.

[0075] Please refer to Figure 15 , Figure 16 , Figure 17 , Figure 15 the structural schematic view of the heat exchanger provided by the fifth embodiment of the utility model; Figure 16 is Figure 15 the structural schematic view of the heat exchanger in another view; Figure 17 is Figure 15 the exploded structural schematic view of the heat exchanger.

[0076] As shown in the figure, in the fifth embodiment, the utility model provides another structure form intermediate heat exchanger, this intermediate heat exchanger also comprises main shell 10, first sealing plate 21 and second sealing plate 22 etc., different from the above-mentioned heat exchanger in the shape of long strip, the heat exchanger of this embodiment is in the shape of rectangle with certain thickness as a whole.

[0077] Specifically, first sealing plate 21 and main shell 10 are welded to form low-pressure side refrigerant flow channel, second sealing plate 22 and main shell 10 are welded to form high-pressure side refrigerant flow channel, and refrigerant heat exchange is carried out, wherein low-pressure joint 41 is welded together with main shell 10, and two high-pressure joints 42 are welded together with second sealing plate 22.

[0078] The thickness of first sealing plate 21 and second sealing plate 22 is 2-3mm, the depth of first flow channel 31 (i.e. low-pressure side flow channel) of main shell 10 is 10-16mm, the depth of second flow channel 32 (i.e. high-pressure flow channel) is 4-8mm, and the thickness of high-low pressure partition plate 33 of main shell 10 is 2-3mm, so the thickness of the intermediate heat exchanger is 20-33mm.

[0079] When used, interface P1 is connected with the outlet of Chiller, interface P2 is connected with the outlet of indoor evaporator, interface P5 is connected with the inlet of compressor, interface P4 is connected with the outlet of liquid accumulator, and interface P3 is connected with the expansion valve of indoor evaporator and the electromagnetic valve of battery pack inlet.

[0080] Compared with the coaxial tube, the scheme has smaller volume and is more suitable for integration, and does not require complex pipelines. Compared with the scheme in which the intermediate heat exchanger is integrated on the flow channel plate, the intermediate heat exchanger is separately arranged, and has higher freedom, and the main flow channel plate can be machined from an aluminum block or a forged flow channel plate.

[0081] In order to solve the problem of excessive flow resistance of the low-pressure side refrigerant, the scheme increases the guide plate feature in the first flow channel 31 (i.e., the low-pressure side flow channel), prevents the refrigerant from generating airflow separation at the turning, and further increases the flow resistance, i.e., the problem of excessive flow resistance at the right-angle turning.

[0082] Please refer to Figures 18 to 22 , Figure 18 for Figure 15 the structural schematic view of the first flow channel of the main shell of the heat exchanger according to Embodiment A; Figure 19 for Figure 15 the structural schematic view of the first flow channel of the main shell of the heat exchanger according to Embodiment B; Figure 20 for Figure 15 the structural schematic view of the first flow channel of the main shell of the heat exchanger according to Embodiment C; Figure 21 for Figure 15 the structural schematic view of the first flow channel of the main shell of the heat exchanger according to Embodiment D; Figure 22 for Figure 15 the structural schematic view of the first flow channel of the main shell of the heat exchanger according to Embodiment E.

[0083] As shown in the figure, in this embodiment, when the first flow channel 31 of the heat exchanger adopts the flow channel shown in Embodiment A, the first flow channel 31 has seven parallel transverse straight segments 313, adjacent straight segments 313 have opposite flow directions and are connected in communication through a 180° turning segment 314, and the flow channel as a whole forms a continuous S shape in the vertical direction.

[0084] The inlet straight segment 319 of the first flow channel 31 is connected in communication with the first inlet 311, and the inlet straight segment 319 is perpendicular to the straight segment 313 and connected in communication with one end of the first straight segment 313 through a 90° turning segment 314.

[0085] The other end of the first straight segment 313 is provided with an introduction straight segment 3110 connected in communication with the interface P1, and the introduction straight segment 3110 is perpendicular to the straight segment 313.

[0086] Compared with the flow channel shown in Embodiment A, the straight segments 313 of the flow channel shown in Embodiment B are widened, so that the number of straight segments 313 is reduced, and the first flow channel 31 has four parallel straight segments 313, adjacent straight segments 313 have opposite flow directions and are connected in communication through a 180° turning segment 314.

[0087] Compared with the flow channel shown in embodiment B, the flow channel shown in embodiment A increases the flow path, which can improve the heat exchange efficiency. The heat exchange capacity of the flow channel shown in embodiment B is significantly increased, but the flow resistance is also increased.

[0088] To this end, the flow channel shown in embodiment C, the flow channel shown in embodiment D and the flow channel shown in embodiment E can be formed by increasing the flow guide structure on the basis of the flow channel shown in embodiment B.

[0089] Specifically, the flow channel shown in embodiment C is provided with an arc-shaped first flow guide plate 315 inside one 90° turning section 314 and three 180° turning sections 314, respectively, each first flow guide plate 315 separates the flow cross section into two parts in a ratio of 1:1; on the basis of the flow channel shown in embodiment C, the flow channel shown in embodiment D is further provided with a second flow guide plate 316 inside the first straight section 313, the two ends of the second flow guide plate 316 are continuously provided with the adjacent first flow guide plate 315, the continuous arrangement of the three flow guide plates enables the first flow guide plate 315 to continue to distribute the liquid in the flow channel to the next first flow guide plate 315, reducing the phenomenon that the liquid is concentrated on one side in the second turning section; and in the first 90° turning section 314 downstream of the inlet, the first flow guide plate 315 is arranged close to the arc-shaped outer wall 3144 to divide the fluid, and in the three 180° turning sections 314, the first flow guide plate 315 is arranged close to the arc-shaped inner wall 3145, after the offset arrangement, the flow cross section is divided into two parts in a ratio of 1:2.

[0090] It should be noted here that in other embodiments, if the incoming material is uniform, the first turning section 314 is 45-150°, the first flow guide plate 315 is arranged close to the arc-shaped outer wall 3144, and the first flow guide plate 315 has a bias, which can be in a ratio of 1:2, and in other embodiments, it can be in a range of 1:1 to 1:2.

[0091] On the basis of the flow channel shown in embodiment C, the flow channel shown in embodiment E is further provided with a second flow guide plate 316 inside the inlet straight section 319 and the second to fourth straight sections 313, and the second flow guide plate 316 of the inlet straight section 319 is continuously provided with the first flow guide plate 315 of the first 90° turning section 314, the remaining first flow guide plates 315 are continuously provided with the second flow guide plates 316, and only at the position corresponding to the introduction straight section 3110 are they disconnected. Moreover, since the inlet section has been evenly distributed, the cross-sectional area separated by the first flow guide plate 315 and the second flow guide plate 316 behind is arranged in a ratio of 1:1.

[0092] Compared with the flow channel shown in embodiment B, the flow channel shown in embodiment C increases the first flow guide plate 315, so that the originally unevenly distributed turbulent flow area at the turning section becomes an area with relatively uniform fluid distribution, and the flow resistance is significantly reduced.

[0093] Compared with the flow channel shown in Embodiment B, the flow channel shown in Embodiment D increases the continuous guide structure at the inlet end, and the heat exchange amount is basically unchanged, and the flow resistance is obviously reduced. Compared with the flow channel shown in Embodiment C, the first segment and the second segment are continuously arranged, which reduces the airflow separation that may occur in the gap between the first segment and the second segment, thereby reducing the flow resistance.

[0094] Compared with the flow channel shown in Embodiment C, the first guide plate 315 at the inlet of the flow channel shown in Embodiment E extends in the inlet direction, and the subsequent first guide plate 315 and the second guide plate 316 are continuously arranged, which can complete the uniform distribution of the fluid before entering the turbulent flow area of the turn. The fluid on both sides of the guide plate is evenly distributed, so that the overall fluid is reduced.

[0095] Please refer to Figures 23 to 28 , Figure 23 for Figure 15 the structural schematic diagram of Embodiment F of the first flow channel of the main shell of the heat exchanger; Figure 24 for Figure 15 the structural schematic diagram of Embodiment G of the first flow channel of the main shell of the heat exchanger; Figure 25 for Figure 15 the structural schematic diagram of Embodiment H of the first flow channel of the main shell of the heat exchanger; Figure 26 for Figure 15 the structural schematic diagram of Embodiment I of the first flow channel of the main shell of the heat exchanger; Figure 27 for Figure 15 the structural schematic diagram of Embodiment J of the first flow channel of the main shell of the heat exchanger; Figure 28 for Figure 15 the structural schematic diagram of Embodiment L of the first flow channel of the main shell of the heat exchanger.

[0096] As shown in the figure, in this embodiment, the first flow channel 31 of the low-pressure side of the heat exchanger can also adopt the flow channel shown in Embodiments F to L, which will be described below.

[0097] For the flow channel shown in Embodiment F, it is generally in the shape of a "y" letter, with the inlet at the top and the outlet at the bottom. The flow resistance of this "y" type flow channel is small, and the heat exchange amount can meet the general use requirements.

[0098] For the flow channel shown in embodiment G, it has two vertical first linear segments 3131 and third linear segments 3133; the first linear segment 3131 is parallel to the third linear segment 3133 and the flow direction of the first linear segment 3131 is the same as that of the third linear segment 3133, and the first linear segment 3131 and the third linear segment 3133 are connected by the second linear segment 3132 which is oblique, the first linear segment 3131 and one end of the second linear segment 3132 are connected by the first turning segment 3141, and the other end of the second linear segment 3132 is connected with the third linear segment 3133 by the second turning segment 3142, that is, the main part of the flow channel is S-shaped in the transverse direction, and the turning angles of the first turning segment 3141 and the second turning segment 3142 are both greater than 90° and less than 180°, and specifically, the turning angles of the first turning segment 3141 and the second turning segment 3142 are both 135°.

[0099] The first flow channel 31 also has a fourth linear segment 3134, and the flow direction of the fourth linear segment 3134 is perpendicular to the third linear segment 3133 and extends from the third linear segment 3133 to the side of the first linear segment 3131, and one end of the third linear segment 313 is connected with the fourth linear segment 3134 by the third turning segment 3143.

[0100] The inlet linear segment 319 of the first flow channel 31 is connected with the first inlet 311, and the inlet linear segment 319 is connected with the first linear segment 3131 by the extension turning segment 3111 with a turning angle less than 90°, and the extension line of the inlet linear segment 319 is parallel to the first linear segment 3131 and the third linear segment 3133, and the extension line of the inlet linear segment 319 is located between the first linear segment 3131 and the third linear segment 3133 and deviates to the first linear segment 3131.

[0101] The extension turning segment 3111 is provided with a lateral introduction segment 3112, and the lateral introduction segment 3112 is connected with the interface P1 by the introduction turning segment 3113, and the turning angle of the introduction turning segment 3113 is less than or equal to 90°.

[0102] Compared with the flow channel shown in embodiment G, the flow channel shown in embodiment H has three changes, the first change is that the first turning segment 3141 is tangent to and connected with the second turning segment 3142 to cancel the oblique second linear segment 3132, the second change is that the first linear segment 3131 is replaced by the circular arc segment 320, and the third change is that the second turning segment 3142 is provided with the introduction linear segment 3110 connected with the interface P1, and the introduction linear segment 3110 and the third linear segment 3133 are located in the same linear direction and the flow directions of the two are opposite. Since the second linear segment 3132 is cancelled and the first linear segment 3131 is changed to the arc segment 320, the flow channel is smoother, and the flow resistance is further reduced.

[0103] Compared with the flow channel shown in the embodiment G, the flow channel shown in the embodiment I is additionally provided with an arc-shaped first flow guide plate 315 in the first turning section 3141 and the second turning section 3142 respectively, so that the turbulent flow area with uneven fluid distribution at the turning section becomes an area with relatively uniform fluid distribution, and the flow resistance is obviously reduced; moreover, the inlet is provided with a 45° extension turning section 3111, after the 45° bending, the fluid enters the 135° first turning section 3141, in the 45° extension turning section 3111, the fluid is close to the arc-shaped outer wall 3144 of the extension turning section 3111, the arc-shaped inner wall 3145 of the 135° first turning section 3141 is located on the same side of the arc-shaped outer wall 3144 of the 45° extension turning section 3111, so that the fluid in the 135° first turning section 3141 still tends to be concentrated and distributed close to the wall on the same side, in the embodiment, the extension turning section 3111 is not provided with a corresponding first flow guide plate 315, the first straight section 3131 and the second straight section 3132 are provided with respective corresponding second flow guide plates 316, the first turning section 3141 is provided with the first flow guide plate 315, the flow guide plates in the three continuous flow channel sections are continuously arranged, in view of the fluid flow trend in the flow channel 31, the first flow guide plate 315 is close to the arc-shaped inner wall 3145, specifically, the first flow guide plate 315 divides the flow passage section of the first turning section 3141 into two parts in a ratio of 1:2, and the first flow guide plate 315 can uniformly distribute the fluid concentrated close to the arc-shaped inner wall 3145.

[0104] Compared with the flow channel shown in the embodiment H, the flow channel shown in the embodiment J is provided with the first flow guide plate 315 in the extension turning section 3111, the first turning section 3141 and the second turning section 3142, and the three first flow guide plates 315 are integrated, the heat exchange amount is basically unchanged, and the flow resistance is obviously reduced; similarly to the embodiment I, the first flow guide plate 315 is arranged close to the arc-shaped inner wall 3145, and moreover, in order not to affect the confluence of the fluid introduced from the introduction straight section 3110, the first flow guide plate 315 does not extend to the outlet of the second turning section 3142.

[0105] Compared with the flow channel shown in the embodiment I, the flow channel shown in the embodiment L is different in the position of the interface P1, and the inlet straight section 319 is provided with a diagonal introduction section 3114 which is communicated with the interface P1.

[0106] Of course, the specific position of the interface of the intermediate heat exchanger is not limited in the utility model, and can be designed flexibly according to actual needs.

[0107] The above Figures 16 to 29 The technical solutions shown in the above Figure 30The flow guide surface 330 is arranged opposite to the inlet of the flow channel, for example, the local flow guide surface can be processed by using a ball end mill to further reduce the flow resistance. In other embodiments, the flow guide surface 330 can also be arranged at the outlet end of the flow channel.

[0108] Compared with the flow channel shown in embodiment F, the flow channel shown in embodiment B increases the S-shaped path, and the heat exchange amount of the flow channel shown in embodiment B is significantly increased, and the flow resistance is also increased, and the heat exchange amount and the flow resistance of the flow channel shown in embodiment G are increased; compared with the flow channel shown in embodiment B, the flow channel shown in embodiment G reduces the turning angle and is smoother, and can significantly reduce the flow resistance.

[0109] In addition, the arrangement of the first flow guide plate 315 and the second flow guide plate 316 indirectly increases the fluid heat exchange area, and can improve the heat exchange amount to a certain extent.

[0110] In order to verify the above technical effects, the simulation input data are as follows:

[0111]

[0112]

[0113] The following are the test data of the flow resistance and the heat exchange amount of each scheme on the low-pressure side, which further prove the effects brought by the structure changes.

[0114] Flow path embodiment Flow rate (kg / h) Flow resistance (Kpa) Heat exchange (W) A 100 12.6 292 A 150 44.4 572 B 150 24 440 B 200 47.5 537 C 150 13.1 429 C 200 23.4 519 D 200 20.3 508.5 E 200 22.8 543.1 F 200 10.9 330.7 G 200 16 425.1 H 200 12.5 390.3 I 200 12.6 417 L 200 14.7 406

[0115] The above embodiments are only preferred schemes of the present application, and the specific embodiments are not limited thereto, and targeted adjustments can be made according to actual needs to obtain different embodiments. For example, similar flow guide structures are arranged in the form of welding, gluing or other forms; one or more first flow guide plates 315 and / or second flow guide plates 316 are arranged; the first flow guide plate 315 and / or the second flow guide plate 316 have different shapes, heights and thicknesses; or the first flow guide plate 315 and the adjacent another first flow guide plate 315 or the second flow guide plate 316 are arranged in a spaced manner or integrally arranged along the flow direction, or the first flow guide plate 315 is composed of a plurality of separately arranged plate members, or the second flow guide plate 316 is composed of a plurality of separately arranged plate members, and the like. Since there are many possible ways, they will not be illustrated one by one here.

[0116] Please refer to Figure 30 , Figure 31 , Figure 30 is a schematic diagram of a three-dimensional structure of a first embodiment of a thermal management assembly; Figure 31 is a schematic diagram of a three-dimensional structure of a second embodiment of a thermal management assembly.

[0117] In addition to the heat exchanger, the utility model also provides a kind of thermal management assembly, as Figure 30 The thermal management assembly shown in the figure has two heat exchange devices, flow channel plate 1, liquid reservoir 4 and several valve devices, and specifically includes first valve device 301, second valve device 302, third valve device 303, fourth valve device 304 and fifth valve device 305, and the valve device is for example expansion valve or stop valve, and the number is not limited to three, which can be set according to the actual needs of the system.

[0118] Two heat exchange devices are shown in the figure, which are condenser 23 and evaporator 24, and more heat exchange devices can also be included, and flow channel plate 1 is used to realize the integrated design of components, and flow channels for refrigerant flow are provided in flow channel plate 1, and at least part of the components of the thermal management assembly can be embedded on flow channel plate 1, and can be fixedly connected or limitingly connected with flow channel plate 1, and can be connected in communication with the corresponding position of the flow channel through the interface, of course, part of the components of the refrigeration system can also be connected in communication with the flow channel through external pipeline, so that the integrated design of the refrigeration system can be realized, the external pipeline is reduced, and the structure of the refrigeration system is relatively compact.

[0119] As shown in Figure 30 The thermal management assembly is integrated with the heat exchanger shown in Figures 1 to 13 The overall structure of the heat exchanger extends in the horizontal direction.

[0120] As shown in Figure 31 Another thermal management assembly shown in the figure is provided with liquid reservoir 4, and several valve devices are integrated on the head of liquid reservoir 4, specifically including sixth valve device 306 and seventh valve device 307, wherein the sixth valve device 306 is a multi-way valve, and the seventh valve device 307 is an expansion valve, and the valve device is used to switch the operating mode of the thermal management assembly. As shown in the figure, the thermal management assembly is integrated with the heat exchanger shown in Figures 16 to 30 The overall structure of the heat exchanger extends in the vertical direction.

[0121] The heat exchanger and the thermal management assembly provided by the utility model are described in detail above. In this paper, specific examples are applied to describe the principles and implementation modes of the utility model, and the above examples are only used to help understand the core idea of the utility model. It should be pointed out that for ordinary skilled persons in the technical field, some improvements and modifications can be made to the utility model without departing from the principles of the utility model, and these improvements and modifications also fall within the protection scope of the claims of the present application.

Claims

1. A heat exchanger, characterized by The heat exchanger has a flow channel, the flow channel includes a first flow channel (31) and a second flow channel (32), the medium flowing in the first flow channel (31) can exchange heat with the medium flowing in the second flow channel (32), the flow channel includes at least one turning section (314), the angle defined by the flow direction before the medium flows into the turning section (314) and the flow direction after the medium flows out of the turning section (314) is a turning angle, the turning angle of the turning section (314) is 45-180 degrees, at least one first guide plate (315) is arranged in the turning section (314), the first guide plate (315) is an arc-shaped plate, a first surface (S1) is defined as the plane in which the turning section (314) extends, the extension direction of the first guide plate (315) is perpendicular to the first surface (S1), and the cross section of the first guide plate (315) can divide the flow passage cross section of at least part of the turning section (314) into two parts in a ratio of 1:1 to 1:

2.

2. The heat exchanger of claim 1, wherein The wall forming the turning section (314) includes an arc-shaped outer wall (3144) and an arc-shaped inner wall (3145), the curvature radius of the arc-shaped outer wall (3144) is greater than that of the arc-shaped inner wall (3145), and the first guide plate (315) extends from an inlet end (M) of the turning section (314) to an outlet end (N) of the turning section (314); The cross section of the first guide plate (315) can divide the flow passage cross section of at least part of the turning section (314) into two parts in a ratio of 1:1; Or, the turning angle of the turning section (314) is 45-150 degrees, and the first guide plate (315) is arranged close to the arc-shaped outer wall (3144); Or, the turning angle of the turning section (314) is 150-180 degrees, and the first guide plate (315) is arranged close to the arc-shaped inner wall (3145).

3. The heat exchanger of claim 1, wherein The wall forming the turning section (314) includes an arc-shaped outer wall (3144) and an arc-shaped inner wall (3145), the curvature radius of the arc-shaped outer wall (3144) is greater than that of the arc-shaped inner wall (3145), the first guide plate (315) extends from an inlet end (M) of the turning section (314) to an outlet end (N) of the turning section (314), the turning section (314) includes an extension turning section (3111) and a first turning section (3141), the turning angle of the extension turning section (3111) is 45 degrees, the turning angle of the first turning section (3141) is 135 degrees, along the radial direction of the flow channel, the arc-shaped outer wall (3144) of the extension turning section (3111) and the arc-shaped inner wall (3145) of the first turning section (3141) are located on the same side of the flow channel, and the first guide plate (315) of the first turning section (3141) is arranged close to the arc-shaped inner wall (3145).

4. The heat exchanger of claim 2, wherein The flow channel comprises a smooth section, an included angle between a flow direction before the medium flows into the smooth section and a flow direction after the medium flows out of the smooth section is defined as a transition angle, the transition angle of the smooth section is greater than or equal to 0 degrees and less than 45 degrees, an inlet of the heat exchanger is directly communicated with an inlet of the smooth section, an outlet of the smooth section is communicated with an inlet of the turning section (314), a second flow guide plate (316) is arranged in the smooth section, and the second flow guide plate (316) divides at least part of a flow passage section of the smooth section into two parts in a ratio of 1:1 to 1:

2.

5. The heat exchanger of claim 4, wherein A cross section of the first flow guide plate (315) can divide a flow passage section of the turning section (314) into two parts in a ratio of 1:1, the second flow guide plate (316) divides a flow passage section of the smooth section into two parts in a ratio of 1:1, and the first flow guide plate (315) and the second flow guide plate (316) are integrally arranged.

6. The heat exchanger of claim 4, wherein The first flow guide plate (315) and the second flow guide plate (316) are arranged in a spaced manner, or the second flow guide plate (316) comprises a plurality of plate members arranged in a split manner.

7. A heat exchanger according to any one of claims 4-6, characterised in that An inside of the first flow guide plate (315) is provided with one or more channels (3161) penetrating in a flow guide direction of the first flow guide plate (315), and / or an inside of the second flow guide plate (316) is provided with one or more channels (3161) penetrating in a flow guide direction of the second flow guide plate (316).

8. The heat exchanger according to any one of claims 1 to 6, characterized in that The flow channel comprises at least two straight sections (313), adjacent straight sections (313) are arranged in parallel, flow directions of the medium in adjacent two straight sections (313) are opposite, and adjacent two straight sections (313) are communicated through the turning section (314), and at least two straight sections (313) are arranged along a gravity direction or along a horizontal direction.

9. The heat exchanger according to any one of claims 1-6, characterized in that The flow channel comprises a first straight section (3131) and a third straight section (3133), the first straight section (3131) is parallel to the third straight section (3133), and flow directions of the medium in the first straight section (3131) and the third straight section (3133) are the same, a turning angle of the turning section (314) is 135 degrees, the turning section (314) comprises a first turning section (3141) and a second turning section (3142), the first turning section (3141) is arranged at an outlet end of the first straight section (3131), and the second turning section (3142) is arranged at an inlet end of the third straight section (3133). The flow channel comprises a second straight section (3132), one end of the second straight section (3132) is communicated with the first turning section (3141), and the other end of the second straight section (3132) is communicated with the second turning section (3142). Or, the turning section (314) is in a circular arc structure, the first turning section (3141) and the second turning section (3142) are directly communicated, and an outlet end of the first turning section (3141) is tangent to an inlet end of the second turning section (3142).

10. The heat exchanger according to any one of claims 1-6, characterized in that The heat exchanger comprises a main shell (10), a first sealing plate (21) and a second sealing plate (22), the first sealing plate (21) is located on one side of the main shell (10), the second sealing plate (22) is located on the other side of the main shell (10), the main shell (10) is fixedly connected or positionally connected with the first sealing plate (21) and the second sealing plate (22) respectively, the main shell (10) comprises a flow channel groove, the flow channel groove comprises a first groove (11) and a second groove (12), the wall forming the first flow channel (31) comprises the wall of the first groove (11) and the wall of the first sealing plate (21), the wall forming the second flow channel (32) comprises the wall of the second groove (12) and the wall of the second sealing plate (22), the first flow guide plate (315) is located in the first flow channel (31) and / or the second flow channel (32).

11. The heat exchanger of claim 10, wherein The first flow guide plate (315) is welded with at least one of the main shell (10), the first sealing plate (21) and the second sealing plate (22) or is in an integral structure.

12. A thermal management assembly comprising two or more of a reservoir (4), a heat exchange device (23, 24) and a valve device, characterised in that, The thermal management assembly further comprises the heat exchanger according to any one of claims 1 to 11.

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