Heat exchange tube, heat exchanger, heat management system and vehicle

Abstract

The invention discloses a heat exchange tube, a heat exchanger, a heat management system and a vehicle, the heat exchange tube comprises a body, at least one heat exchange flow channel is formed in the body, at least one flow guide assembly is arranged in the heat exchange flow channel, and the flow guide assembly comprises at least one first flow guide part; and the first flow guide part obliquely extends relative to the extension direction of the heat exchange runner. According to the heat exchange tube, the heat exchange tube is simple in structure. When the heat exchange tube is used for the heat exchanger, the heat exchanger can be used as a condenser or an evaporator, is a dual-purpose heat exchanger and is convenient to install and use.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of heat exchange, in particular to a heat exchange pipe, a heat exchanger, a thermal management system and a vehicle. BACKGROUND

[0002] The heat exchanger is a main component of the air conditioner. In the air conditioning equipment, the air introduced by the air blower is cooled at the heat exchanger due to heat exchange, and then the cooled air is supplied to the vehicle interior.

[0003] In the related art, the condenser and the evaporator of the vehicle are two independent heat exchangers, and the two heat exchangers work independently. The two independent heat exchangers also need to be equipped with their own mounting frames, and the occupied mounting space is relatively large. Moreover, the heat exchange capacity of the heat exchanger is limited. SUMMARY

[0004] The present application aims to solve at least one of the technical problems existing in the prior art. To this end, one object of the present application is to provide a heat exchange pipe, which has a simple structure. When the heat exchange pipe is used in a heat exchanger, the heat exchanger can be used as a condenser or an evaporator, that is, a dual-purpose heat exchanger, which is convenient to install and use.

[0005] A second object of the present application is to provide a heat exchanger using the above-mentioned heat exchange pipe.

[0006] A third object of the present application is to provide a thermal management system using the above-mentioned heat exchanger.

[0007] A fourth object of the present application is to provide a vehicle using the above-mentioned thermal management system.

[0008] According to the heat exchange pipe of the first aspect of the present application, the heat exchange pipe comprises a body, at least one heat exchange flow channel is formed on the body, at least one set of flow guide components is arranged in the heat exchange flow channel, the flow guide components comprise at least one first flow guide piece, and the first flow guide piece extends obliquely relative to the extension direction of the heat exchange flow channel.

[0009] According to the heat exchange pipe of the present application, the structure of the first flow guide piece is simple, the structure of the heat exchange pipe is simplified, and the production and processing are convenient. In addition, by arranging the first flow guide piece, the flow resistance of the heat exchange medium flowing from the above-mentioned one end to the above-mentioned other end in the heat exchange flow channel is increased, the flow time of the heat exchange medium in the heat exchange flow channel is prolonged, the heat exchange time is prolonged, and the heat exchange capacity of the heat exchange medium flowing from the above-mentioned one end to the above-mentioned other end in the heat exchange flow channel is improved. Moreover, the flow resistance of the heat exchange medium flowing from the above-mentioned one end to the above-mentioned other end in the heat exchange flow channel is greater than the flow resistance of the heat exchange medium flowing from the above-mentioned other end to the above-mentioned one end in the heat exchange flow channel, so as to realize different heat exchange capacities of the heat exchange medium in different flow directions. In addition, the heat exchanger is a dual-purpose heat exchanger, which can be used as an evaporator or a condenser, thereby reducing the space occupied by the heat exchanger in the thermal management system and being more conducive to the installation and use of the heat exchanger.

[0010] According to some embodiments of the present application, two ends of the extension direction of the heat exchange channel have a first flow passage and a second flow passage, and the first flow guide member extends in a direction from the first flow passage to the second flow passage and in a direction away from the central axis of the heat exchange channel.

[0011] According to some embodiments of the present application, the first flow guide member has an inclination angle α, and the α satisfies: 20°≤α≤40°.

[0012] According to some embodiments of the present application, the first flow guide member is a plurality of first flow guide members, and the plurality of first flow guide members form a first flow guide group and a second flow guide group, the first flow guide group and the second flow guide group are respectively located on two sides of the central axis of the heat exchange channel, the first flow guide group includes at least one first flow guide member, and the second flow guide group includes at least one first flow guide member.

[0013] According to some embodiments of the present application, the first flow guide group has a plurality of first flow guide members, and the plurality of first flow guide members of the first flow guide group are arranged in an axial direction of the heat exchange channel; and / or, the second flow guide group has a plurality of second flow guide members, and the plurality of second flow guide members of the second flow guide group are arranged in an axial direction of the heat exchange channel.

[0014] According to some embodiments of the present application, in a direction from the first flow passage to the second flow passage, lengths of the plurality of first flow guide members of the first flow guide group gradually increase in sequence; and / or, lengths of the plurality of second flow guide members of the second flow guide group gradually increase in sequence.

[0015] According to some embodiments of the present application, the flow guide assembly further includes a second flow guide member located on a side of the first flow guide member adjacent to the second flow passage.

[0016] According to some embodiments of the present application, in a direction from the first flow passage to the second flow passage, a width of the second flow guide member gradually increases and then gradually decreases.

[0017] According to some embodiments of the present application, the second flow guide member has a rhombus shape, and a central axis of the second flow guide member coincides with a central axis of the heat exchange channel.

[0018] According to some embodiments of the present application, an included angle between two sides of the second flow guide member close to the first flow guide member is β, and the β satisfies: 10°≤β≤30°.

[0019] According to some embodiments of the present application, a ratio of a length of the second flow guide to a minimum distance between a side of the second flow guide facing the first flow guide and the first flow guide is n, wherein the n satisfies: 3≤n≤10.

[0020] According to some embodiments of the present application, the heat exchange passage defines a plurality of heat exchange regions in communication with each other, the plurality of heat exchange regions are arranged in sequence along an axial direction of the heat exchange passage, and each of the heat exchange regions is provided with the flow guide assembly, wherein a width of the heat exchange region along a direction perpendicular to the axial direction of the heat exchange passage gradually increases from the first flow-through opening to the second flow-through opening.

[0021] According to some embodiments of the present application, two adjacent heat exchange regions are in communication through an opening, the opening is located between the first flow-through opening and the second flow-through opening, and an end of the second flow guide away from the first flow guide is opposite to the opening.

[0022] According to some embodiments of the present application, a plurality of heat exchange passages are provided, and the plurality of heat exchange passages are arranged in intervals along a direction perpendicular to an extension direction of the heat exchange passage.

[0023] The heat exchanger according to the second aspect of the embodiments of the present application comprises the heat exchange tube according to the first aspect of the embodiments of the present application.

[0024] The heat management system according to the third aspect of the embodiments of the present application comprises the heat exchanger according to the second aspect of the embodiments of the present application.

[0025] According to some embodiments of the present application, the heat management system further comprises: an outside-vehicle heat exchanger; a compressor, the compressor having an inlet and an outlet, a first end of the outside-vehicle heat exchanger being connected to the second flow-through opening of the heat exchanger; and a switching member, the switching member having a first interface, a second interface, a third interface and a fourth interface, the first interface being connected to the outlet, the second interface being connected to a second end of the outside-vehicle heat exchanger, the third interface being connected to the inlet, the fourth interface being connected to the first flow-through opening, the first interface being in communication with one of the second interface and the fourth interface, and the third interface being in communication with the other one of the second interface and the fourth interface.

[0026] According to some embodiments of the present application, the switching member is a four-way valve.

[0027] The vehicle according to the fourth aspect of the embodiments of the present application comprises the heat exchanger according to the second aspect of the embodiments of the present application or the heat management system according to the third aspect of the embodiments of the present application.

[0028] Additional aspects and advantages of the present application will be in part apparent and in part pointed out below in the description of embodiments of the present application. BRIEF DESCRIPTION OF DRAWINGS

[0029] The above and / or additional aspects and advantages of the present application will become apparent and be readily appreciated from the following description of embodiments of the present application, taken in conjunction with the accompanying drawings.

[0030] Figure 1 is a schematic view of a heat exchange pipe according to an embodiment of the present application;

[0031] Figure 2 is Figure 1 is an enlarged view of the C part shown in the circle in

[0032] Figure 3 is a schematic view of a heat exchange flow channel of a heat exchange pipe according to an embodiment of the present application;

[0033] Figure 4 is a schematic view of a heat exchange pipe according to an embodiment of the present application from another angle;

[0034] Figure 5 is a schematic view of a heat exchange pipe according to an embodiment of the present application from still another angle;

[0035] Figure 6 is a schematic view of a thermal management system according to an embodiment of the present application, wherein the thermal management system is in a cooling state;

[0036] Figure 7 is a schematic view of a thermal management system according to an embodiment of the present application, wherein the thermal management system is in a heating state.

[0037] REFERENCE NUMERALS:

[0038] 100, heat exchange pipe; 200, thermal management system; 10, heat exchanger;

[0039] 1, body; 11, heat exchange flow channel; 111, first flow-through opening; 112, second flow-through opening;

[0040] 12, heat exchange region; 121, opening;

[0041] 2, flow guide assembly; 21, first flow guide; 22, first flow guide group;

[0042] 23, second flow guide group; 24, second flow guide;

[0043] 3, external heat exchanger; 31, first end; 32, second end;

[0044] 4, compressor; 41, inlet; 42, outlet;

[0045] 5, on-off member; 51, first interface; 52, second interface;

[0046] 53, third interface; 54, fourth interface;

[0047] 6, warm core; 7, PTC;

[0048] 8, electronic expansion valve. DETAILED DESCRIPTION

[0049] Embodiments of the present application are described in detail below with reference to the accompanying drawings. The embodiments described below are exemplary, and the following description refers to the accompanying drawings in which Figures 1-5 A heat exchange tube 100 according to an embodiment of the first aspect of the present application is described below.

[0050] As shown in Figure 1 and Figure 2 , the heat exchange tube 100 according to the embodiment of the first aspect of the present application includes a body 1.

[0051] Specifically, the body 1 is formed with at least one heat exchange channel 11, and at least one set of flow guide assemblies 2 is arranged in the heat exchange channel 11. The flow guide assemblies 2 include at least one first flow guide member 21, and the first flow guide member 21 extends obliquely relative to the extension direction of the heat exchange channel 11.

[0052] For example, in the examples of Figure 1 and Figure 2 , the body 1 is formed with the heat exchange channel 11, and the heat exchange channel 11 extends along a first direction (e.g., the left-right direction in Figure 3 ) of the body 1. The oblique extension of the first flow guide member 21 relative to the extension direction of the heat exchange channel 11 can be understood as that the extension direction of the first flow guide member 21 is not parallel to the extension direction of the heat exchange channel 11. When the heat exchange tube 100 is used in the heat exchanger 10, the heat exchange medium can flow along the extension direction of the heat exchange channel 11, and the heat exchange medium can flow from one end of the extension direction of the heat exchange channel 11 to the other end, or from the other end to the one end.

[0053] Therefore, by arranging the obliquely extending first flow guide member 21, when the heat exchange medium flows from the one end to the other end (e.g., the left end to the right end in Figure 1During the process of flowing from A to B, the first flow guide 21 has a certain degree of obstruction to the flow of the heat exchange medium, thereby increasing the flow resistance of the heat exchange medium flowing from the one end to the other end of the heat exchange flow channel 11, prolonging the flow time of the heat exchange medium in the heat exchange flow channel 11, prolonging the heat exchange time, and improving the heat exchange capacity of the heat exchange medium flowing from the one end to the other end of the heat exchange flow channel 11. In addition, during the process of flowing from B to A, the inclined first flow guide 21 has a good flow guiding effect on the heat exchange medium, thereby reducing the flow resistance of the heat exchange medium flowing from the other end to the one end of the heat exchange flow channel 11, and the heat exchange medium flows more smoothly. That is, the flow resistance is different when the heat exchange medium flows in different directions in the heat exchange flow channel 11, and the flow resistance of the heat exchange medium flowing from the one end to the other end of the heat exchange flow channel 11 is greater than that flowing from the other end to the one end of the heat exchange flow channel 11, so as to realize different heat exchange capacities of the heat exchange medium in different flow directions.

[0054] According to the heat exchange pipe 100 of the embodiment of the present application, the first flow guide 21 has a simple structure, which simplifies the structure of the heat exchange pipe 100 and facilitates production and processing. In addition, by arranging the first flow guide 21, the flow resistance of the heat exchange medium flowing from the one end to the other end of the heat exchange flow channel 11 is increased, the flow time of the heat exchange medium in the heat exchange flow channel 11 is prolonged, the heat exchange time is prolonged, and the heat exchange capacity of the heat exchange medium flowing from the one end to the other end of the heat exchange flow channel 11 is improved. Moreover, the flow resistance of the heat exchange medium flowing from the one end to the other end of the heat exchange flow channel 11 is greater than that flowing from the other end to the one end of the heat exchange flow channel 11, so as to realize different heat exchange capacities of the heat exchange medium in different flow directions. In addition, the heat exchanger 10 is a dual-purpose heat exchanger, which can be used as an evaporator and a condenser, thereby reducing the space occupied by the heat exchanger 10 in the thermal management system 200 and being more conducive to the installation and use of the heat exchanger 10.

[0055] According to some embodiments of the present application, in combination with Figure 1 and Figure 3 , the two ends of the extension direction of the heat exchange flow channel 11 have a first flow passage 111 and a second flow passage 112, and the first flow guide 21 extends in the direction from the first flow passage 111 to the second flow passage 112 and in the direction away from the central axis of the heat exchange flow channel 11.

[0056] For example, in Figure 3In the example shown in FIG. 1, the heat exchange flow channel 11 has a first flow-through opening 111 and a second flow-through opening 112 formed at two ends of the length direction of the heat exchange flow channel 11, respectively. The first flow guide 21 extends in a straight line in a direction away from the central axis of the heat exchange flow channel 11 from left to right. The heat exchange medium can flow from the first flow-through opening 111 to the second flow-through opening 112 along the extension direction of the heat exchange flow channel 11, or flow from the second flow-through opening 112 to the first flow-through opening 111 along the extension direction of the heat exchange flow channel 11.

[0057] The present application proposes that, by designing the flow guide assembly 2, the flow resistance is small when evaporating, and the heat exchange medium such as refrigerant flows quickly. When condensing, the flow resistance is large, and the refrigerant flows out of the heat exchange pipe 100 after being fully heat exchanged in the heat exchange flow channel 11, so that the heat exchange performance when condensing can be effectively improved. That is, when the air conditioner is refrigerating, the heat exchanger 10 is used as an evaporator, the heat exchange medium can flow from the second flow-through opening 112 to the first flow-through opening 111, and the flow resistance is small during the flow. When the air conditioner is heating, the heat exchanger 10 is used as a condenser, so that the heat exchange medium flows from the first flow-through opening 111 to the second flow-through opening 112, and the flow resistance is large during the flow. Therefore, by controlling the flow direction of the heat exchange medium, the different functions of the heat exchanger 10 can be realized, that is, the heat exchanger 10 is a dual-purpose heat exchanger, which can be used as an evaporator and a condenser. The space occupied by the heat exchanger 10 in the thermal management system 200 is reduced, which is more conducive to the installation and use of the heat exchanger 10. In addition, the structure of the first flow guide 21 is simple, which simplifies the structure of the heat exchange pipe 100 and facilitates production and processing.

[0058] According to some embodiments of the present application, in combination Figure 3 The inclination angle of the first flow guide 21 is α, and α satisfies: 20°≤α≤40°. For example, when the inclination angle of the first flow guide 21 is less than 20°, the inclination angle of the first flow guide 21 is small, and when the heat exchange medium flows from the first flow-through opening 111 to the second flow-through opening 112, the flow resistance effect of the first flow guide 21 is poor, the heat exchange time of the heat exchange medium is shortened, and the heat exchange effect of the heat exchange pipe 100 is reduced. When the inclination angle of the first flow guide 21 is greater than 40°, when the heat exchange medium flows from the first flow-through opening 111 to the second flow-through opening 112, the flow resistance effect of the first flow guide 21 on the heat exchange medium is increased, and the flow resistance during the process of the heat exchange medium flowing from the second flow-through opening 112 to the first flow-through opening 111 is also increased, which reduces the difference between the flow resistances of the heat exchange medium in different flow directions, and reduces the heat exchange effect when the heat exchanger 10 is used as a condenser.

[0059] Therefore, by setting the inclination angle a of the first flow guide 21 to satisfy 20°≤a≤40°, the inclination angle of the first flow guide 21 is reasonable, which can greatly improve the heat exchange performance of the heat exchange medium and improve the heat exchange effect of the heat exchange pipe 100. In addition, the flow resistance difference of the heat exchange medium with different flow directions is moderate, so that the heat exchange pipe 100 can be used as an evaporator or a condenser, thereby improving the use performance of the heat exchange pipe 100. The heat exchange medium flowing between the first flow guide 21 and the inner wall of the heat exchange flow channel 11 is collected again near the inner wall of the heat exchange flow channel 11 after flowing out at different intervals, forming a local counterflow effect, thereby achieving a larger fluid flow resistance effect from A to B. Due to the larger flow resistance, the local counterflow effect of the first flow guide 21 and the inner wall of the heat exchange flow channel 11 can slow down the flow of the fluid in the channel, prolong the heat exchange time, and thus improve the heat exchange capacity from A to B.

[0060] According to some embodiments of the present application, in combination with Figure 1 and Figure 3 , the first flow guide 21 is a plurality of first flow guides 21, and the plurality of first flow guides 21 form a first flow guide group 22 and a second flow guide group 23. The first flow guide group 22 and the second flow guide group 23 are respectively located on both sides of the central axis of the heat exchange flow channel 11. The first flow guide group 22 includes at least one first flow guide 21, and the second flow guide group 23 includes at least one first flow guide 21. In the description of the present application, "a plurality of" means two or more.

[0061] For example, in the examples of Figure 1 and Figure 3 , the first flow guide group 22 and the second flow guide group 23 are symmetrically arranged about the central axis of the heat exchange flow channel 11. Taking the case where the first flow guide group 22 is arranged on the upper side of the central axis of the heat exchange flow channel 11 and the second flow guide group 23 is arranged on the lower side of the central axis of the heat exchange flow channel 11 as an example. Therefore, by setting the first flow guide group 22 and the second flow guide group 23, a part of the heat exchange medium flowing from the first flow passage 111 can flow to the second flow passage 112 through the first flow guide group 22, and another part can flow to the second flow passage 112 through the second flow guide group 23, thereby increasing the flow resistance effect of the flow guide assembly 2, prolonging the heat exchange time of the heat exchange medium in the heat exchange flow channel 11, and further improving the heat exchange effect of the heat exchange pipe 100.

[0062] According to some embodiments of the present application, in combination with Figure 1 and Figure 3 , the first flow guide 21 of the first flow guide group 22 is a plurality of first flow guides 21, and the plurality of first flow guides 21 of the first flow guide group 22 are arranged at intervals along the axial direction of the heat exchange flow channel 11. And / or, the first flow guide 21 of the second flow guide group 23 is a plurality of first flow guides 21, and the plurality of first flow guides 21 of the second flow guide group 23 are arranged at intervals along the axial direction of the heat exchange flow channel 11.

[0063] For example, in the example shown in the figure, the first flow guide group 22 and the second flow guide group 23 are each provided with four first flow guide elements 21. The multiple first flow guide elements 21 of the first flow guide group 22 and the multiple first flow guide elements 21 of the second flow guide group 23 are arranged symmetrically about the central axis of the heat exchange channel 11. Figure 3 In the vertical direction, the first flow port 111 is located between the first guide group 22 and the second guide group 23. The first guide member 21 is mainly used to guide the heat exchange medium flowing from A to B into the channels between each first guide member 21. In addition, due to the setting of the tilt angle, the heat exchange medium flowing from B to A flows through the channel with a lower pressure drop.

[0064] This configuration, through multiple first flow guides 21, further increases the flow resistance of the heat exchange medium as it flows from the first flow port 111 to the second flow port 112, increases the flow time of the heat exchange medium within the heat exchange channel 11, and also increases the contact area between the heat exchange medium and the flow guide assembly 2, enhancing boiling and condensation heat exchange performance. Simultaneously, it achieves a difference in flow resistance between the forward and reverse directions, further improving the heat exchange effect of the heat exchange tube 100. Furthermore, the first flow guide group 22 and the second flow guide group 23 are rationally arranged and aesthetically pleasing, which is beneficial for the production and processing of the heat exchange tube 100 and improves processing efficiency. It should be noted that the number of first flow guides 21 in the first flow guide group 22 and the second flow guide group 23, as well as the spacing between adjacent first flow guides 21, can be set according to specific applications to better meet actual needs.

[0065] According to some embodiments of the present invention, with reference to Figure 3 From the first flow port 111 toward the second flow port 112, the lengths of the plurality of first flow guides 21 in the first flow guide group 22 increase sequentially. And / or, the lengths of the plurality of first flow guides 21 in the second flow guide group 23 increase sequentially.

[0066] For example, in Figure 3 In the example, from left to right, the lengths of the multiple first guide elements 21 in the first guide group 22 increase sequentially, and the lengths of the multiple first guide elements 21 in the second guide group 23 also increase sequentially. When the heat exchange medium flows towards the first guide element 21 near the first flow port 111, it first flows in the direction of extension of the first guide element 21, and then flows towards another adjacent first guide element 21 in the left-right direction. Thus, by setting the lengths of the multiple first guide elements 21 to increase sequentially, it is beneficial for the heat exchange medium to flow sequentially to the adjacent first guide elements 21, and the contact area with the guide assembly 2 also gradually increases, resulting in better heat exchange performance of the heat exchange tube 100, thereby improving the performance of the heat exchange tube 100.

[0067] According to some embodiments of the present invention, in combination Figure 1 and Figure 3The guide assembly 2 further comprises a second guide member 24 located at one side of the first guide member 21 adjacent to the second flow-through port 112.

[0068] For example, in the examples of Figure 1 and Figure 3 , the second guide member 24 is located between the first guide assembly 22 and the second guide assembly 23 in the up-down direction, and is located between the first guide member 21 and the second flow-through port 112 in the left-right direction. When the heat exchange medium flows in the heat exchange flow channel 11, the heat exchange medium flows through the plurality of first guide members 21 and then flows to the second guide member 24, and then flows between the second guide member 24 and the inner wall of the heat exchange flow channel 11 to the second flow-through port 112.

[0069] Therefore, by arranging the second guide member 24, the contact area between the heat exchange medium and the heat exchange assembly is further increased, the flow time of the heat exchange medium in the heat exchange flow channel 11 is further prolonged, the flow resistance of the heat exchange medium from the first flow-through port 111 to the second flow-through port 112 is further increased, and the heat exchange performance of the heat exchange medium from the second flow-through port 112 to the first flow-through port 111 can be ensured. The present application realizes different flow resistances of the heat exchanger 10 in different flow directions through the heat exchange flow channel 11 with a special shape, the combination design of the first guide member 21 in the heat exchange flow channel 11 and the shuttle-shaped second guide member 24, increases the flow resistance of the condensation process in the forward direction (A to B) while keeping the flow resistance of the evaporation process in the reverse direction (B to A) unchanged, and improves the heat exchange performance of the condensation process in the forward direction. The heat exchange area can also be increased, thereby significantly improving the condensation heat exchange capacity of the heat exchanger 10 in the heating condition while keeping the evaporation heat exchange capacity unchanged in the refrigeration condition.

[0070] According to some embodiments of the present application, referring to Figure 1 and Figure 3 , the width of the second guide member 24 gradually increases and then gradually decreases from the first flow-through port 111 to the second flow-through port 112.

[0071] For example, in the examples of Figure 1 and Figure 3In the example shown in FIG. 6, the second flow guide 24 extends along the left-right direction, and the width of the second flow guide 24 gradually increases and then gradually decreases from left to right. In this way, when the heat exchange medium flows from the first flow-through port 111 toward the second flow-through port 112, the heat exchange medium flowing to the second flow guide 24 is divided under the action of the second flow guide 24 and flows to the upper and lower sides of the second flow guide 24, respectively, and forms a local counterflow effect at the inner wall surface of the heat exchange flow channel 11. The local counterflow effect can slow down the flow of the heat exchange medium in the heat exchange flow channel 11, and the heat exchange time is prolonged, thereby improving the heat exchange capacity from A to B. In addition, by gradually reducing the width of the second flow guide 24, the heat exchange medium is concentrated on the side close to the second flow-through port 112, thereby smoothly flowing to the second flow-through port 112, improving the heat exchange effect, and also facilitating the flow of the heat exchange medium. In addition, the width of the second flow guide 24 close to the second flow-through port 112 gradually decreases from left to right. When the heat exchange medium flows into the second flow-through port 112, it is beneficial to divide the heat exchange medium, so as to facilitate the flow of the heat exchange medium to the first flow guide group 22 and the second flow guide group 23 through the second flow guide 24, thereby also facilitating the flow of the heat exchange medium from B to A.

[0072] According to some embodiments of the present application, in combination Figures 1-5 , the second flow guide 24 is in the shape of a rhombus, and the central axis of the second flow guide 24 coincides with the central axis of the heat exchange flow channel 11. For example, in the example shown in FIG. 6, Figures 1-5 , the first flow-through port 111, the second flow-through port 112, and the second flow guide 24 are all arranged on the central axis of the heat exchange flow channel 11.

[0073] In this way, the second flow guide 24 is symmetrical about the central axis of the heat exchange flow channel 11, and the heat exchange medium flowing to the second flow guide 24 from the first flow-through port 111 or the second flow-through port 112 can be uniformly divided under the action of the second flow guide 24, thereby making the distribution of the heat exchange medium in the heat exchange flow channel 11 more uniform in the up-down direction, making the heat exchange effect at each position in the heat exchange flow channel 11 substantially the same, and better improving the heat exchange performance of the heat exchange tube 100. In addition, the structure of the second flow guide 24 is simple, easy to produce and process, and has good flow guiding effect, thereby simplifying the structure of the heat exchange tube 100 and improving the production efficiency. The second flow guide 24 in the shape of a shuttle guides the heat exchange medium flowing from the middle of the first flow guide 21 from A to B to flow to B, and also guides the heat exchange medium flowing from B to A to flow into the rear first flow guide 21 with a lower pressure drop.

[0074] According to some embodiments of the present application, in combination Figure 3 , the included angle between the two sides of the second flow guide 24 close to the first flow guide 21 is β, and β satisfies: 10°≤β≤30°. For example, in the example shown in FIG. 6, Figure 3In the example, the angle between the side of the second guide member 24 near the first guide group 22 and the side of the second guide group 23 is β, and the angle between the two sides near the second flow port 112 is also β. This configuration ensures that the angle between the two sides of the second guide member 24 near the first guide member 21 is reasonable, and the inclination angle of the two sides of the second guide member 24 near the first guide member 21 is also reasonable. This results in better flow guidance from the second guide member 24, and also ensures a reasonable spacing between the side of the second guide member 24 facing the first guide group 22 and the first guide member 21 of the first guide group 22, and a reasonable spacing between the side of the second guide member 24 facing the second guide group 23 and the first guide member 21 of the second guide group 23. This arrangement is beneficial for both heat exchange in the heat exchange tube 100 and the flow of the heat exchange medium.

[0075] According to some embodiments of the present invention, the ratio of the length of the second guide member 24 to the minimum distance between the side of the second guide member 24 facing the first guide member 21 and the first guide member 21 is n, where n satisfies: 3≤n≤10.

[0076] For example, in Figure 3 In the example, the minimum distance between the second guide member 24 and the first guide member 21 of the first guide group 22 is d, that is, the minimum distance between the upper left side of the second guide member 24 and the rightmost first guide member 21 of the first guide group 22 is d. The length of the second guide member 24 along the axial direction of the heat exchange channel 11 is l, and l and d satisfy: l / d = n. Of course, the relationship between the minimum distance of the second guide member 24 to the first guide member 21 of the second guide group 23 and the length of the second guide member 24 is the same as above. With this setting, the length of the second guide member 24 is reasonably set, so that there is a certain gap between the first guide member 21 near the second connection port and the second connection port, thereby increasing the flow space of the heat exchange medium between the first guide member 21, the second guide member 24 and the inner wall of the heat exchange channel 11. At the same time, it also avoids the second guide element 24 occupying too much space in the heat exchange channel 11, so that the heat exchange performance of the heat exchange tube 100 is better under the combined action of the first guide element 21 and the second guide element 24. Moreover, it also makes the counterflow effect of the heat exchange medium at the second guide element 24 and the inner wall of the heat exchange channel 11 better.

[0077] According to some embodiments of the present invention, in combination Figures 1-5 Multiple interconnected heat exchange regions 12 are defined within the heat exchange channel 11. The multiple heat exchange regions 12 are arranged sequentially along the axial direction of the heat exchange channel 11. Each heat exchange region 12 is provided with a flow guiding component 2. The width of the heat exchange region 12 gradually increases from the first flow port 111 toward the second flow port 112 in the direction perpendicular to the axial direction of the heat exchange channel 11 (e.g., the up and down direction in Figure 3).

[0078] For example, in the example of Figure 1 six heat exchange regions 12 are formed in each heat exchange channel 11, the structures of the heat exchange regions 12 are the same, the heat exchange regions 12 are sequentially communicated in the left-right direction, and each heat exchange region 12 is substantially in the shape of a water droplet. The leftmost heat exchange region 12 of the heat exchange regions 12 has a first flow passage 111, the rightmost heat exchange region 12 of the heat exchange regions 12 has a second flow passage 112, and the structures of the heat exchange components in each heat exchange region 12 are the same. Thus, the batch production of the heat exchange tube 100 is facilitated, and the production efficiency is improved. In addition, by gradually increasing the width of the heat exchange region 12 in the direction perpendicular to the axial direction of the heat exchange channel 11, the flow resistance of the heat exchange medium from A to B is significantly increased under the combined action of the shape of the heat exchange region 12, the first flow guide 21 and the second flow guide 24, and the heat exchange performance of the heat exchange tube 100 is further improved. In addition, the structure of the heat exchange region 12 is aesthetically pleasing. It should be noted that the number of heat exchange regions 12 can be set according to specific use to better meet actual application.

[0079] According to some embodiments of the present application, referring to Figure 3 two adjacent heat exchange regions 12 are communicated through an opening 121, the opening 121 is located between the first flow passage 111 and the second flow passage 112, and the end of the second flow guide 24 away from the first flow guide 21 is opposite to the opening 121.

[0080] For example, in the example of Figure 1 six heat exchange regions 12 are formed in each heat exchange channel 11, five openings 121 are formed between the six heat exchange regions 12, the five openings 121 are arranged at intervals along the central axis of the heat exchange channel 11, and the opening 121, the first flow passage 111 and the second flow passage 112 are on the same axis. In this way, two adjacent heat exchange regions 12 can be communicated through the opening 121, and the second flow guide 24 in each heat exchange region 12 is adjacent to the opening 121, and each heat exchange channel 11 is symmetrical about its central axis, and the distribution of the heat exchange medium on the upper and lower sides in the heat exchange channel 11 is relatively uniform, so that the heat exchange effect in the heat exchange channel 11 is also relatively consistent.

[0081] According to some embodiments of the present application, in combination with Figure 1 the heat exchange channel 11 is a plurality of heat exchange channels 11, and the plurality of heat exchange channels 11 are arranged at intervals in the direction perpendicular to the extension direction of the heat exchange channel 11. For example, in Figure 1In the example, the plurality of heat exchange channels 11 are arranged in parallel with each other, and the plurality of heat exchange channels 11 are arranged in the up-down direction. In this way, on the one hand, the contact area between the heat exchange medium and the body 1 is increased, thereby improving the heat exchange effect of the heat exchange pipe 100, so that the heat exchange pipe 100 has good heat exchange effect everywhere along the axial direction perpendicular to the heat exchange channel 11. On the other hand, the heat exchange media in the plurality of heat exchange channels 11 do not interfere with each other, so that the state of the heat exchange medium flowing into each heat exchange channel 11 is approximately the same, reducing the temperature difference of the heat exchange medium in each heat exchange channel 11, and improving the heat exchange uniformity of the heat exchange pipe 100. Moreover, it is also conducive to the orderly flow of the heat exchange medium in each heat exchange channel 11.

[0082] According to the heat exchanger 10 of the second aspect of the present application, the heat exchanger 10 comprises the heat exchange pipe 100 according to the first aspect of the present application.

[0083] According to the heat exchanger 10 of the present application, the heat exchanger 10 is a dual-purpose heat exchanger, which can be used as an evaporator and a condenser, thereby improving the heat exchange effect and applicability of the heat exchanger 10, and being more conducive to the popularization and use of the heat exchanger 10.

[0084] According to the heat management system 200 of the third aspect of the present application, in combination with Figure 6 and Figure 7 , the heat management system 200 comprises the heat exchanger 10 according to the second aspect of the present application.

[0085] According to the heat management system 200 of the present application, by using the heat exchanger 10 described above, only one in-vehicle heat exchanger 10 is needed in the heat management system 200 to realize both refrigeration and heating functions, thereby reducing the number of heat exchangers 10, reducing the space occupied by the installation of the heat exchanger 10, and reducing the cost of the heat management system 200.

[0086] According to some embodiments of the present application, in combination with Figure 6 and Figure 7 , the heat management system 200 further comprises an out-of-vehicle heat exchanger 3, a compressor 4, and a switching component 5.

[0087] In combination with Figure 6 and Figure 7 , the compressor 4 has an inlet 41 and an outlet 42, the first end 31 of the out-of-vehicle heat exchanger 3 is connected to the second flow-through port 112 of the heat exchanger 10, the switching component 5 has a first interface 51, a second interface 52, a third interface 53, and a fourth interface 54, the first interface 51 is connected to the outlet 42, the second interface 52 is connected to the second end 32 of the out-of-vehicle heat exchanger 3, the third interface 53 is connected to the inlet 41, and the fourth interface 54 is connected to the first flow-through port 111. The first interface 51 is in communication with one of the second interface 52 and the fourth interface 54, and the third interface 53 is in communication with the other one of the second interface 52 and the fourth interface 54.

[0088] For example, when the thermal management system 200 is in cooling mode, the refrigerant flow path is: compressor 4 - outlet 42 - first interface 51 of on / off component 5 - second interface 52 - second end 32 - external heat exchanger 3 - first end 31 - electronic expansion valve 8 - second flow port 112 - heat exchanger 10 - first flow port 111 - fourth interface 54 - third interface 53 - inlet 41, thus forming the refrigerant flow path. The cooling process is as follows: the heat exchange medium is refrigerant (phase change heat) which is compressed by the compressor 4 and discharged. At this time, the first interface 51 and the second interface 52 are connected, and the refrigerant enters the external heat exchanger 3 through the flow channels of the first interface 51 and the second interface 52 to interact with the air (the air flow direction at the external heat exchanger 3 is as follows). Figure 6 (Indicated by arrow D) Heat exchange achieves cooling and condensation. Afterwards, it passes through electronic expansion valve 8 for throttling and depressurization before entering heat exchanger 10 (flowing from B to A) for heat absorption and evaporation. At this point, the air inside the vehicle (airflow direction at heat exchanger 10 is as follows) can be cooled and condensed. Figure 6 (As indicated by the middle arrow E) refrigeration is achieved. At this time, the third interface 53 and the fourth interface 54 are connected, and finally the flow returns to the inlet 41 of the compressor 4 through the flow channels of the fourth interface 54 and the third interface 53.

[0089] For example, when the thermal management system 200 is in heating mode, the refrigerant flow path is: compressor 4 - outlet 42 - first interface 51 - fourth interface 54 - first flow port 111 - heat exchanger 10 - second flow port 112 - electronic expansion valve 8 - first end 31 - external heat exchanger 3 - second end 32 - second interface 52 - third interface 53 - inlet 41. The heating process is as follows: the heat exchange medium, refrigerant, is compressed by compressor 4, flows through the first interface 51 and fourth interface 54 into heat exchanger 10 to exchange heat with the air inside the vehicle to achieve cooling and condensation (flowing from A to B), at which time the air inside the vehicle can be heated. Afterwards, it passes through electronic expansion valve 8 for throttling and depressurization and cooling, then enters external heat exchanger 3 to absorb heat and evaporate, and finally returns to inlet 41 of compressor 4 through the second interface 52 and third interface 53. For example, the refrigerant flowing through the above-mentioned refrigeration cycle loop is a refrigerant, including R134a, R410a, CO2, R290, etc.

[0090] Thus, it can be seen from the structure of the dual-purpose heat exchanger, the working process description in the refrigeration and heating modes that the heat exchanger 10 can be used to complete the evaporation and condensation functions, the condensation heat exchange capacity in the refrigeration mode is significantly improved, the low-cost heat pump air conditioning scheme is realized, and the performance in the refrigeration, heating and other modes can be ensured. In the working process of the thermal management system 200, the refrigeration, heating and other modes can be flexibly switched according to the user demand, the existing thermal management system 200 such as the air conditioning system and related equipment of the traditional vehicle can be greatly utilized, the modification and additional cost is low. In addition, by arranging the on-off piece 5, the flow direction of the refrigerant can be changed by controlling the communication relationship between the first interface 51, the second interface 52, the third interface 53 and the fourth interface 54, the control logic of the thermal management system 200 is simple, the use is convenient, and the use performance of the thermal management system 200 is improved.

[0091] Optionally, in combination with Figure 6 and Figure 7 , the thermal management system 200 further comprises a heating piece, the heating piece can include a warm core 6 and a PTC 7, and the heating piece is adjacent to the air outlet of the heat exchanger 10. Thus, in the heating state, the indoor air can be heated by the warm core 6 and the PTC 7 after the heat exchange of the heat exchanger 10, so as to improve the air outlet temperature and improve the heating effect. Of course, when the thermal management system 200 is in the heating state, at least one of the heating piece and the heat exchanger 10 is used for heating to ensure the heating effect.

[0092] According to some optional embodiments of the present application, the on-off piece 5 is a four-way valve. Thus, the structure of the on-off piece 5 is simple, the use is convenient, the control precision is high, and the use cost is low. As the evaporation and condensation dual-purpose heat exchanger of the indoor air conditioning system, the four-way valve is used to reduce the cost of the thermal management system 200 and ensure the refrigeration and heating performance.

[0093] The vehicle according to the fourth aspect embodiment of the present application comprises the heat exchanger 10 according to the second aspect embodiment or the thermal management system 200 according to the third aspect embodiment.

[0094] According to the vehicle of the present application, the heat exchange effect of the air conditioner of the vehicle is good, the use experience of the user is improved, and the use cost of the air conditioner can be reduced.

[0095] The other configurations and operations of the heat exchange pipe 100, the heat exchanger 10, the thermal management system 200 and the vehicle according to the embodiments of the present application are known to those skilled in the art, and will not be described in detail here.

[0096] In the description of the application, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like are used to indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation on the present application.

[0097] In the description of the present application, the description of the terms "one embodiment", "some embodiments", "illustrative embodiment", "example", "specific example", or "some examples" and the like means that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present application. In the present specification, the illustrative description of the above terms does not necessarily refer to the same embodiment or example.

[0098] Although embodiments of the present application have been shown and described, those skilled in the art can understand that various changes, modifications, replacements and variations can be made to these embodiments without departing from the principles and spirit of the present application, and the scope of the present application is defined by the claims and their equivalents.

Claims

1. A heat exchange tube, characterized in that, Includes a body, on which at least one heat exchange channel is formed, and at least one set of flow guiding components are provided in the heat exchange channel. The flow guiding components include at least one first flow guiding member, which extends obliquely relative to the extension direction of the heat exchange channel.

2. The heat exchange tube according to claim 1, characterized in that, The heat exchange channel has a first flow port and a second flow port at both ends of its extension direction, and extends obliquely from the first flow port toward the second flow port and from the first flow guide in a direction away from the central axis of the heat exchange channel.

3. The heat exchange tube according to claim 2, characterized in that, The tilt angle of the first guide member is α, wherein α satisfies: 20°≤α≤40°.

4. The heat exchange tube according to claim 1, characterized in that, There are multiple first flow guides, and the multiple first flow guides constitute a first flow guide group and a second flow guide group. The first flow guide group and the second flow guide group are respectively located on both sides of the central axis of the heat exchange channel. The first flow guide group includes at least one first flow guide, and the second flow guide group includes at least one first flow guide.

5. The heat exchange tube according to claim 4, characterized in that, The first flow guide element of the first flow guide group is a plurality of such elements, and the plurality of first flow guide elements of the first flow guide group are arranged at intervals along the axial direction of the heat exchange channel; and / or The second guide element of the second guide group is multiple, and the multiple second guide elements of the second guide group are arranged at intervals along the axial direction of the heat exchange channel.

6. The heat exchange tube according to claim 5, characterized in that, From the direction of the first flow port toward the second flow port, The lengths of the plurality of first guide elements in the first guide group increase sequentially; and / or The lengths of the multiple second guide elements in the second guide group increase sequentially.

7. The heat exchange tube according to claim 1, characterized in that, The flow guiding component further includes: The second flow guide is located on the side of the first flow guide adjacent to the second flow port.

8. The heat exchange tube according to claim 7, characterized in that, From the first flow port toward the second flow port, the width of the second flow guide gradually increases and then gradually decreases.

9. The heat exchange tube according to claim 8, characterized in that, The second flow guide is rhomboid in shape, and its central axis coincides with the central axis of the heat exchange channel.

10. The heat exchange tube according to claim 8, characterized in that, The included angle between the two sides of the second guide member closest to the first guide member is β, wherein β satisfies: 10°≤β≤30°.

11. The heat exchange tube according to claim 8, characterized in that, The ratio of the length of the second guide to the minimum distance between the side of the second guide facing the first guide and the first guide is n, where n satisfies: 3≤n≤10.

12. The heat exchange tube according to claim 2, characterized in that, The heat exchange channel defines multiple interconnected heat exchange areas, which are arranged sequentially along the axial direction of the heat exchange channel. Each heat exchange area is provided with the flow guiding component. The width of the heat exchange area gradually increases from the first flow port toward the second flow port along the axial direction perpendicular to the heat exchange channel.

13. The heat exchange tube according to claim 12, characterized in that, The two adjacent heat exchange zones are connected by an opening located between the first flow port and the second flow port, and the end of the second flow guide that is away from the first flow guide is opposite to the opening.

14. The heat exchange tube according to any one of claims 1-13, characterized in that, The heat exchange channels are multiple, and the multiple heat exchange channels are arranged at intervals along the extension direction perpendicular to the heat exchange channels.

15. A heat exchanger, characterized in that, Includes the heat exchange tube according to any one of claims 1-14.

16. A thermal management system, characterized in that, Includes the heat exchanger according to claim 15.

17. The thermal management system according to claim 16, characterized in that, Further includes: External heat exchanger; The compressor has an inlet and an outlet, and the first end of the external heat exchanger is connected to the second flow port of the heat exchanger. The switching component has a first interface, a second interface, a third interface, and a fourth interface. The first interface is connected to the outlet, the second interface is connected to the second end of the external heat exchanger, the third interface is connected to the inlet, and the fourth interface is connected to the first flow port. The first interface is connected to one of the second interface and the fourth interface, and the third interface is connected to the other of the second interface and the fourth interface.

18. The thermal management system according to claim 17, characterized in that, The switching element is a four-way valve.

19. A vehicle, characterized in that, Includes the heat exchanger according to claim 15, or the thermal management system according to any one of claims 16-18.

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