Heat exchanger

Abstract

A heat exchanger, comprising a first header part (1), a second header part (3) and a plurality of heat exchange tubes (4), wherein the first header part (1) comprises a first header (11), a separator (13) and a first tube (12), the separator (13) is at least partially located in the first header (11), the first header (11) comprises a first tube section (111) and a second tube section (112), the first tube section (111) and the second tube section (112) are located on two sides of the separator (13), and the first tube (12) is in communication with the first tube section (111) and the second tube section (112); the second header part (3) comprises a second header (31), the second header (31) is spaced apart from the first header (11), and the heat exchange tubes (4) are in communication with the first header (11) and the second header (31); and the first header part (1) further comprises a communication portion (2), and the communication portion (2) is in communication with the first tube section (111) and the second tube section (112).

Description

Heat exchanger

[0001] Cross-reference to related applications

[0002] This application claims priority to Chinese Patent Application No. 2024112558493, filed on September 6, 2024, the entire contents of which are incorporated herein by reference. TECHNICAL FIELD

[0003] The present application relates to the technical field of heat exchange, in particular to a heat exchanger for heat pump. BACKGROUND

[0004] The heat exchanger needs to distribute refrigerant when working as an evaporator. The way of setting a partition and a pipe in the header can improve the uniformity of refrigerant distribution. However, when the heat exchanger works as a condenser, the flow direction of the refrigerant is opposite to that when the heat exchanger works as an evaporator. Due to the blocking of the partition, part of the reverse-flowing refrigerant needs to flow through the pipe before it can flow out of the header, which causes the flow resistance of this part of the refrigerant to be relatively large, the flow of the refrigerant to be slow, and the flow rate of the refrigerant in a unit of time to be relatively small, thereby reducing the heat exchange efficiency of the heat exchanger when working as a condenser. SUMMARY

[0005] The heat exchanger provided by the embodiments of the present application can reduce the heat exchange efficiency of the heat exchanger when working as a condenser.

[0006] The heat exchanger provided by the embodiments of the present application includes a first header part, a second header part, and a plurality of heat exchange pipes. The first header part includes a first header, a partition, and a first pipe. The partition is at least partially located in the first header. The first header includes a first pipe section and a second pipe section. The first pipe section and the second pipe section are respectively located on two sides of the partition. The first pipe communicates the first pipe section and the second pipe section. The second header part includes a second header. The second header is arranged at intervals with the first header. The heat exchange pipes communicate the first header and the second header. The first header part further includes a communication part. The communication part communicates the first pipe section and the second pipe section.

[0007] When the heat exchanger provided by the embodiments of the present application works as a condenser, the refrigerant can enter from the second header, flow into the first header after heat exchange by the heat exchange pipes, and part of the refrigerant blocked by the partition in the second pipe section of the first header can enter the first pipe section through the communication part and then flow out of the first pipe section directly, thereby reducing the flow resistance of the refrigerant in the first header when flowing under condensing conditions, facilitating the flow of the refrigerant, and improving the heat exchange efficiency of the heat exchanger when working as a condenser. BRIEF DESCRIPTION OF DRAWINGS

[0008] Fig. 1 is a structural schematic diagram of a heat exchanger in a specific embodiment according to the present application;

[0009] Fig. 2 is an enlarged structural schematic diagram of A in Fig. 1;

[0010] Fig. 3 is an enlarged structural schematic diagram of B in Fig. 1;

[0011] Fig. 4 is a schematic diagram of the flow direction of refrigerant when the heat exchanger works as a condenser according to the present application;

[0012] Fig. 5 is a schematic diagram of the flow direction of refrigerant when the heat exchanger works as an evaporator according to the present application;

[0013] Fig. 6 is a structural schematic diagram of a communication part in a specific embodiment according to the present application;

[0014] Fig. 7 is a structural schematic diagram of a communication part in a second specific embodiment according to the present application;

[0015] Fig. 8 is a structural schematic diagram of a communication part in a third specific embodiment according to the present application;

[0016] Fig. 9 is a three-dimensional structural schematic diagram of the communication part in Fig. 8;

[0017] Fig. 10 is a structural schematic diagram of a communication part in a fourth specific embodiment according to the present application;

[0018] Fig. 11 is a structural schematic diagram of a communication part in a fifth specific embodiment according to the present application;

[0019] Fig. 12 is a structural schematic diagram of a communication part in a sixth specific embodiment according to the present application.

[0020] Reference signs: first header part 1, first header 11, first pipe segment 111, second pipe segment 112, first pipe 12, first hole 121, first end 122, second end 123, first plate 13, communication part 2, first interface 21, first channel 22, second channel 23, first sub-channel 231, second sub-channel 232, seat body 24, first connecting pipe 25, second connecting pipe 26, third connecting pipe 27, second header part 3, second header 31, second interface 32, heat exchange pipe 4, fin 5.

[0021] The accompanying drawings, which are incorporated herein and form part of the specification, illustrate embodiments consistent with the present application and, together with the description, further serve to explain the principles of the application. DETAILED DESCRIPTION

[0022] For better understanding of the technical solutions of the present application, the embodiments of the present application are described in detail below with reference to the drawings.

[0023] It should be clear that the described embodiments are only part of the technical solutions of the present application, but not all the technical solutions. Based on the technical solutions in the present application, all other technical solutions obtained by those of ordinary skill in the art without creative labor are within the scope of protection of the present application.

[0024] The terms used in the embodiments of the present application are only for the purpose of describing specific embodiments, and are not intended to limit the present application. The singular forms "a", "said" and "the" used in the embodiments of the present application and the appended claims are also intended to include the plural forms, unless the context clearly indicates otherwise.

[0025] It should be understood that the term "and / or" used herein is only to describe the association relationship of the associated objects, which means that there can be three relationships, for example, A and / or B, which can represent the three cases of A alone, A and B together, and B alone. In addition, the character " / " in this paper generally represents that the front and rear associated objects are a "or" relationship.

[0026] It should be noted that the "up", "down", "left", "right" and other directional words described in the embodiments of the present application are described from the angle shown in the drawings, and should not be understood as a limitation on the embodiments of the present application. In addition, in the context, it should also be understood that when referring to an element connected to another element "on" or "under", it can be directly connected to another element "on" or "under", or indirectly connected to another element "on" or "under" through an intermediate element.

[0027] As shown in FIGS. 1-12, the present application provides a heat exchanger, which comprises a first header section 1, a second header section 3 and a plurality of heat exchange pipes 4, the first header section 1 comprises a first header 11, a partition 13 and a first pipe 12, the partition 13 is at least partially located in the first header 11, the first header 11 comprises a first pipe section 111 and a second pipe section 112, the first pipe section 111 and the second pipe section 112 are located on both sides of the partition 13 respectively, and the first pipe 12 communicates the first pipe section 111 and the second pipe section 112; the second header section 3 comprises a second header 31, the second header 31 is arranged in a spaced manner with the first header 11, and the heat exchange pipe 4 communicates the first header 11 and the second header 31; the first header section 1 further comprises a communication section 2, and the communication section 2 communicates the first pipe section 111 and the second pipe section 112.

[0028] In the embodiment, the first tube 12 and the partition 13 can play a good distribution role for the refrigerant in the heat exchanger, so that the heat exchanger is more uniform in distribution of the refrigerant when working as an evaporator. Specifically, when the heat exchanger works as an evaporator, the flow path of the refrigerant is as shown in FIG. 5. After the refrigerant enters the first tube segment 111 of the first header 11, part of the refrigerant will be directly distributed and enter the heat exchange tube 4 in communication with the first tube segment 111 for heat exchange under the guidance of the first tube 12, and the other part of the refrigerant will enter the second tube segment 112 for distribution through the first tube 12. In this process, the refrigerant spontaneously enters the low-pressure zone from the high-pressure zone. In addition, due to the vapor-liquid separation under the evaporation condition and the different weights of the gaseous refrigerant and the liquid refrigerant, the refrigerant entering the first tube 12 contains more gaseous refrigerant, thereby reducing the accumulation of the refrigerant in the first tube segment 111 and promoting the flow of the refrigerant. The continuous flow of the refrigerant can facilitate the mixing of the two-phase refrigerant during distribution, thereby improving the distribution effect of the two-phase refrigerant.

[0029] When the heat exchanger works as a condenser, if the communication part 2 is not provided, the refrigerant needs to pass through the first tube 12 after entering the second header 31 to enter the first tube segment 111, and then flows out from the first tube segment 111. In this flow process, the flow resistance of the refrigerant is large, which can cause the refrigerant to flow mainly from the upper segment region of the partition 13, and thus the refrigerant flowing through the heat exchange tube 4 in the lower segment region of the partition 13 is less, which does not fully utilize the area of the heat exchanger. This can also cause the liquid accumulation phenomenon to be more serious in the lower cavity of the heat exchanger due to the large resistance to the outlet during defrosting, and the liquid part of the defrosting is difficult to discharge.

[0030] As shown in FIG. 4, when the communication part 2 is provided, the refrigerant can enter the second header 31 when the heat exchanger works as a condenser, and flow into the first header 11 after heat exchange in the heat exchange tube 4. Part of the refrigerant blocked by the partition 13 in the first header 11 (i.e., the refrigerant in the second tube segment 112) can directly enter the first tube segment 111 through the communication part 2, and then directly flow out from the first tube segment 111, thereby reducing the flow resistance of the refrigerant in the first header 11 during flow under the condensation condition, and facilitating the flow of the refrigerant, thereby improving the heat exchange efficiency of the heat exchanger when working as a condenser.

[0031] As shown in FIGS. 1-11, in a specific embodiment, the communication part 2 is provided in the first header 11, and the communication part 2 includes a first interface 21, a first channel 22, and a second channel 23. The first channel 22 is close to the partition 13, the first channel 22 communicates the first interface 21 and the first tube segment 111, and the second channel 23 communicates the first channel 22 and the second tube segment 112.

[0032] The heat exchanger in the embodiment can improve the heat exchange efficiency when working as a condenser. When the heat exchanger works as a condenser, a part of the refrigerant in the first header 11 blocked by the partition 13 can enter the first channel 22 through the second channel 23 and then flow out directly from the first interface 21, thereby reducing the flow resistance of the refrigerant in the first header 11 when flowing, facilitating the flow of the refrigerant, and improving the heat exchange efficiency of the heat exchanger when working as a condenser.

[0033] In addition, when the heat exchanger provided with the communication part 2 works as an evaporator, the refrigerant enters from the first interface 21, most of which enters the first sub-pipe section 111 through the first channel 22 and then is distributed; a small part of the refrigerant in the first channel 22 can enter the second pipe section 112 directly through the second channel 23 and then be distributed. In this process, due to the flow inertia, the refrigerant will mostly flow into the first sub-pipe section 111, and the proportion of the refrigerant entering the second channel 23 is small, but as mentioned above, the refrigerant entering the first pipe 12 contains a large amount of gaseous refrigerant, and the gaseous-liquid separation of the refrigerant flowing from the first channel 22 into the second channel 23 is not obvious in the first sub-pipe section 111. Therefore, the refrigerant flowing from the first channel 22 into the second channel 23 can supplement the liquid refrigerant in the second pipe section 112 to some extent and improve the gas-liquid mixing ratio in the second pipe section 112. In addition, since the refrigerant flowing from the second channel 23 into the second pipe section 112 has a high flow rate, and the refrigerant flowing from the first pipe 12 into the second pipe section 112 has a low flow rate, the refrigerant flowing from the former can also disturb the refrigerant flowing from the latter, thereby making the gas-liquid mixture in the second pipe section 112 more uniform and being more conducive to the distribution of the refrigerant under the evaporator working condition.

[0034] As can be seen, the communication part 2 in the embodiment can improve the heat exchange efficiency of the heat exchanger under the condensing condition and improve the distribution performance of the heat exchanger under the evaporating condition. Therefore, the heat exchanger provided with the communication part 2 can be used as an evaporator and a condenser at the same time, and has good heat exchange performance under the evaporating condition and the condensing condition. Therefore, the heat exchanger in the present application can have an evaporating condition and a condensing condition when working, under the evaporating condition, the refrigerant enters the heat exchanger from the inlet of the first pipe section 111 for heat exchange, and under the condensing condition, the refrigerant enters the heat exchanger from the inlet of the second header 31 for heat exchange.

[0035] It should be noted that the role of the partition 13 is to form a physical isolation for the first header 11, so that the first pipe section 111 and the second pipe section 112 are isolated and not connected when not communicated through the first pipe 12. The partition 13 is at least partially located in the first header 11. Here, the at least partially means that the partition 13 can be completely located in the first header 11, or only a part of the partition 13 is located in the first header 11 and the other part of the partition 13 extends out of the wall of the first header 11. For example, when the area of the partition 13 is slightly larger than the cross-sectional area of the first header 11, the partition 13 is partially located in the first header 11.

[0036] In a specific embodiment, the flow passage cross-sectional area of the first channel 22 is greater than the flow passage cross-sectional area of the second channel 23. For example, the maximum flow passage cross-sectional area of the first channel 22 is defined as S1, and the maximum flow passage cross-sectional area of the second channel 23 is defined as S2. Then, S1 / S2≥5. In the evaporation working condition, most of the refrigerant needs to enter the first pipe section 111 from the first channel 22 to achieve the expected distribution effect. Although the flow passage inertia makes the refrigerant flow in the direction of the first channel 22, if the flow passage cross-sectional area of the second channel 23 is too large, the amount of refrigerant entering the second channel 23 will increase, which will reduce the amount of refrigerant in the first pipe section 111 and affect the uniformity of the distribution. Therefore, the flow passage cross-sectional area of the first channel 22 needs to be greater than the flow passage cross-sectional area of the second channel 23, and specifically, the flow passage cross-sectional area of the first channel 22 is greater than 5 times the flow passage cross-sectional area of the second channel 23, which can better balance the refrigerant distribution of the heat exchanger in the evaporation and condensation working conditions.

[0037] In the condensation working condition, since the first channel 22 is directly communicated with the first interface 21, the pressure in the first channel 22 is less than the pressure in the first pipe section 111, and the refrigerant will preferentially flow from high pressure to low pressure. Therefore, although the flow passage cross-sectional area of the second channel 23 is small, more refrigerant will still flow from the second channel 23 into the first channel 22, which is also the reason why the flow passage cross-sectional area of the second channel 23 is small, but it can still meet the requirement that the refrigerant flows from the second channel 23 into the first channel 22 to reduce the part of the flow resistance of the refrigerant in the condensation working condition.

[0038] As shown in FIGS. 2 and 6-10, in a specific embodiment, the communication part 2 further comprises a seat body 24, which is directly or indirectly connected with the first header 11. In a specific embodiment, the seat body 24 can be directly or indirectly connected with the outer wall of the first header 11. The first interface 21, the first channel 22 and the second channel 23 are arranged in the seat body 24. The first channel 22 extends at least partially along the thickness direction of the seat body 24, and the second channel 23 extends at least partially along the length direction of the seat body 24.

[0039] In the embodiment, the seat body 24 is directly connected to the first header 11, and in some other embodiments, the seat body 24 can also be connected to the first header 11 through an intermediate piece or the like (i.e., indirectly connected), which will not be described herein. When the seat body 24 is directly connected to the first header 11, the side of the seat body 24 facing the first header 11 has a circular arc surface, so as to be fitted to the outer pipe wall of the first header 11. The first channel 22 and the second channel 23 are groove channels provided in the seat body 24. By integrally arranging the first interface 21, the first channel 22 and the second channel 23 in the seat body 24, and then connecting the seat body 24 to the first header 11, the structure of the heat exchanger can be more compact. In addition, the first channel 22 extends at least partially along the thickness direction of the seat body 24, and the second channel 23 extends at least partially along the length direction of the seat body 24, so that more of the refrigerant entering from the first interface 21 enters the first pipe section 11 under the action of flow inertia, and a small part of the refrigerant enters the second pipe section 112 through the second channel 23.

[0040] It should be noted that the "second channel 23 extends at least partially along the length direction of the seat body 24" mentioned in the embodiment means that the length direction of the second channel 23 can extend entirely along the length direction of the seat body 24, or can extend only partially along the length direction of the seat body 24. For example, in order to reduce the refrigerant flow entering the second channel 23 in the evaporating condition, the second channel 23 can be arranged as a zigzag flow path or the like, so as to reduce the bypass flow. Or it can be arranged to adjust the gas-liquid ratio of the refrigerant entering the second channel 23 in the evaporating condition, which will be described in subsequent embodiments.

[0041] As shown in FIGS. 7-10, in a specific embodiment, the second channel 23 includes a first sub-channel 231 and a second sub-channel 232, the number of the first sub-channels 231 is at least two, the first sub-channels 231 are communicated with the first channel 22 and the second sub-channel 232, and the second sub-channel 232 is communicated with the first sub-channels 231 and the second pipe section 112. In the embodiment, by arranging the flow area of the second channel 23 to be smaller than the flow area of the first channel 22, the bypass flow of the refrigerant entering the second channel 23 in the evaporator condition of the heat exchanger can be reduced, and by dividing the second channel 23 into at least two first sub-channels 231 communicated with the first channel 22, different distribution effects can be achieved, so as to adapt to different distribution requirements.

[0042] As shown in FIGS. 7-9, in a specific embodiment, the at least two first sub-channels 231 are respectively communicated with the upper part of the first channel 22, or the at least two first sub-channels 231 are respectively communicated with the lower part of the first channel 22.

[0043] It can be understood that, in the evaporation working condition, the refrigerant entering the first channel 22 from the first interface 21 is in a gas-liquid mixed state, although the space of the first channel 22 is small and the proportion of gas-liquid separation of the refrigerant flowing in the first channel 22 is small, but because the gaseous refrigerant is lighter and the liquid refrigerant is heavier, therefore, the lighter gaseous refrigerant in the gas-liquid mixed refrigerant will be concentrated in the upper part of the first channel 22, and the heavier liquid refrigerant will be concentrated in the lower part of the first channel 22. Therefore, when the at least two first sub-channels 231 are respectively communicated with the upper part of the first channel 22, the proportion of the gaseous refrigerant in the refrigerant flowing into the first sub-channels 231 will be higher than that of the liquid refrigerant; when the at least two first sub-channels 231 are respectively communicated with the lower part of the first channel 22, the proportion of the liquid refrigerant in the refrigerant flowing into the first sub-channels 231 will be higher than that of the gaseous refrigerant. Therefore, different connection modes can achieve different distribution effects, and thus can be designed according to different types of heat exchangers.

[0044] As shown in FIG. 10, in a specific embodiment, part of the at least two first sub-channels 231 are communicated with the upper part of the first channel 22, and the other part are communicated with the lower part of the first channel 22. As mentioned above, the lighter gaseous refrigerant in the gas-liquid mixed refrigerant will be concentrated in the upper part of the first channel 22, and the heavier liquid refrigerant will be concentrated in the lower part of the first channel 22, therefore, the mode that part of the first sub-channels 231 are communicated with the upper part of the first channel 22 and the other part are communicated with the lower part of the first channel 22 can introduce higher proportion of gaseous refrigerant into the first sub-channels 231, and also can introduce higher proportion of liquid refrigerant into the first sub-channels 231, so that the gas-liquid ratio of the refrigerant entering the second sub-channels 232 is more balanced, and ultimately the gas-liquid ratio of the refrigerant entering the second pipe section 112 is more balanced, which is beneficial to the uniform distribution of the refrigerant.

[0045] It should be noted that, in the above-mentioned embodiments, “the upper part of the first channel 22” and “the lower part of the first channel 22” are mentioned, wherein the “upper part of the first channel 22” can refer to the upper middle position of the first channel 22, or can refer to the top position of the first channel 22. Similarly, the “lower part of the first channel 22” can refer to the lower middle position of the first channel 22, or can refer to the bottom position of the first channel 22, which will not be described one by one herein.

[0046] As shown in FIG. 11, in one embodiment, the communication part 2 comprises a first connector 25 and a second connector 26, the first channel 22 comprises a lumen of the first connector 25, and the second channel 23 comprises a lumen of the second connector 26. In this embodiment, the first connector 25 is connected to the first pipe section 111, and the second connector 26 is connected to the first connector 25 and the second pipe section 112, which can achieve the same effect as the above embodiment of the seat 24. In addition, the second connector 26 can be connected to different positions of the first connector 25 to achieve different distribution effects, for example, connecting the second connector 26 to the upper part of the first connector 25 can introduce more gaseous refrigerant, and connecting the second connector 26 to the lower part of the first connector 25 can introduce more liquid refrigerant, which has the same principle as the above embodiment, and thus will not be described in detail.

[0047] As shown in FIG. 12, in one embodiment, the communication part 2 comprises a third connector 27 and a one-way valve (not shown), the one-way valve is arranged on the third connector 27, one end of the third connector 27 is connected to the second pipe section 112, and the other end is close to the partition 13 and connected to the first pipe section 111, and in the direction from the second pipe section 112 to the first pipe section 111, the one-way valve communicates the lumen of the third connector 27.

[0048] In this embodiment, the third connector 27 connects the first pipe section 111 and the second pipe section 112, which can directly introduce the refrigerant in the second pipe section 112 into the first pipe section 111, thereby improving the heat exchange effect of the heat exchanger in the condensation working condition. However, such a connection method can also cause a part of the refrigerant in the first pipe section 111 to directly enter the second pipe section 112 from the third connector 27 in the evaporation working condition, resulting in poor distribution of the heat exchange tubes 4 on the upper part of the first pipe section 111 (a part of the refrigerant in the first pipe section 111 enters the second pipe section 112 from the third connector 27, which affects the pressure and flow rate of the refrigerant in the first pipe section 111, and the refrigerant cannot reach the upper part of the first pipe section 111), which will affect the distribution performance of the heat exchanger in the evaporation working condition to some extent. The one-way valve can effectively solve this problem.

[0049] In other embodiments, the first channel 22 communicates the first interface 21 and the first pipe section 111, and the second channel 23 communicates the first channel 22 and the second pipe section 112. In the evaporation working condition, the refrigerant enters from the first interface 21, then enters the first pipe section 111 through the first channel 22, and the flow rate of the refrigerant is very fast in this process. According to the principle of flow inertia and high pressure to low pressure, the refrigerant will directly rush into the first pipe section 111, so that less refrigerant enters the second channel 23, and such a connection method will not affect the pressure and flow rate of the refrigerant in the first pipe section 111, so that such a connection method has better heat exchange effect in the evaporation working condition and the condensation working condition.

[0050] As shown in FIGS. 1-3, in one embodiment, the first pipe 12 is at least partially located in the first header 11, and the length direction of the first pipe 12 extends along the length direction of the first header 11, and the side wall of the first pipe 12 is provided with at least one first hole 121, and the first hole 121 is located on the side of the first pipe 12 away from the second pipe section 112.

[0051] In some embodiments, the first pipe 12 can be completely located in the first header 11 and extend along the length direction of the first header 11, which can not only introduce refrigerant into the second pipe section 112, but also guide the refrigerant flowing and distributing in the first pipe section 111 and the second pipe section 112 to flow and distribute along the length direction. In addition, the first hole 121 is located on the side of the first pipe 12 away from the second pipe section 112, more specifically, on the position of the first pipe 12 close to the end portion on the side away from the second pipe section 112. This is because the refrigerant generally accumulates more on the side of the first pipe section 111 away from the second pipe section 112 during the process of flowing and distributing in the first pipe section 111, resulting in a slow flow rate of the refrigerant in the first pipe section 111. Therefore, arranging the first hole 121 on the side of the first pipe 12 away from the second pipe section 112 can guide the accumulated refrigerant to flow to the second pipe section 112, thereby promoting the flow of the refrigerant and achieving better mixing and distribution effect. In addition, when the first hole 121 is a through hole penetrating through the opposite side walls of the first pipe 12, the number of the first holes 121 can be two or so to meet the expected refrigerant distribution requirements.

[0052] As shown in FIGS. 1-3, in one embodiment, the first pipe 12 has a first end 122 and a second end 123 in the length direction, the first end 122 is located in the first pipe section 111 and fixedly connected with the first pipe section 111, and the second end 123 is located in the second pipe section 112, and the second end 123 has a predetermined gap with the end portion of the second pipe section 112.

[0053] As shown in FIG. 3, the first end 122 of the first pipe 12 is plugged by a plug and fixedly connected with the first pipe section 111. Generally, the first pipe 12 and the first pipe section 111 of the first header 11 are fixed by brazing. In addition, the second end 123 and the opening on the side of the second passage 23 away from the first passage 22 are substantially flush, which can make the refrigerant flowing out of the second end 123 fully mixed with the refrigerant flowing out of the second passage 23 under the evaporation working condition, so that the gas-liquid mixture of the refrigerant entering the corresponding heat exchange tube 4 from the second pipe section 112 is more uniform, and the heat exchange effect of the heat exchanger is improved.

[0054] As shown in FIGS. 1-3 and 10, in one specific embodiment, the heat exchanger further comprises a plurality of fins 5, the length direction of the fins 5 extends along the length direction of the first header 11 or the second header 31, and the plurality of fins 5 are arranged at intervals along the length direction of the heat exchange pipe 4; the fins 5 mentioned herein can be corrugated fins, or through-hole fins, or transversely inserted fins with insertion slots, etc., which are not specifically limited herein. The second header portion 3 further comprises a second interface 32, which is in communication with the second header 31, and the refrigerant can enter or flow out of the second header 31 through the second interface 32.

[0055] The above only describes the preferred embodiments of the present application and is not intended to limit the present application. Various modifications and changes can be made by those skilled in the art based on the principles and spirit of the present application. Any modification, equivalent replacement, improvement, etc. made within the spirit and principles of the present application shall be included in the protection scope of the present application.

[0056] All embodiments of the present disclosure can be executed independently or in combination with other embodiments, and are considered to be within the protection scope required by the present disclosure.

Claims

1. A heat exchanger, characterized by, The application relates to a heat exchange device, which comprises a first header section (1), a second header section (3) and a plurality of heat exchange pipes (4), the first header section (1) comprises a first header (11), a partition (13) and a first pipe (12), the partition (13) is at least partially located in the first header (11), the first header (11) comprises a first pipe section (111) and a second pipe section (112), the first pipe section (111) and the second pipe section (112) are respectively located on two sides of the partition (13), the first pipe (12) is connected with the first pipe section (111) and the second pipe section (112), the second header section (3) comprises a second header (31), the second header (31) is arranged in a spaced manner with the first header (11), the heat exchange pipe (4) is connected with the first header (11) and the second header (31), and the first header section (1) further comprises a connecting section (2), the connecting section (2) is connected with the first pipe section (111) and the second pipe section (112).

2. The heat exchanger of claim 1, wherein The connecting section (2) is arranged on the first header (11), the connecting section (2) comprises a first interface (21), a first channel (22) and a second channel (23), the first channel (22) is close to the partition (13), the first channel (22) is connected with the first interface (21) and the first pipe section (111), and the second channel (23) is connected with the first channel (22) and the second pipe section (112).

3. The heat exchanger of claim 2, wherein The flow area of the first channel (22) is greater than that of the second channel (23), the maximum flow area of the first channel (22) is defined as S1, and the maximum flow area of the second channel (23) is defined as S2, so that S1 / S2 is greater than or equal to 5.

4. The heat exchanger according to claim 2 or 3, characterized in that The connecting section (2) further comprises a seat body (24), the seat body (24) is directly or indirectly connected to the outer wall of the first header (11), the first interface (21), the first channel (22) and the second channel (23) are arranged on the seat body (24), the first channel (22) at least partially extends along the thickness direction of the seat body (24), and the second channel (23) at least partially extends along the length direction of the seat body (24).

5. The heat exchanger of claim 4, wherein The second channel (23) comprises a first sub-channel (231) and a second sub-channel (232), the number of the first sub-channels (231) is at least two, the first sub-channels (231) are connected with the first channel (22) and the second sub-channels (232), and the second sub-channels (232) are connected with the first sub-channels (231) and the second pipe section (112).

6. The heat exchanger of claim 5, wherein At least two first sub-channels (231) are respectively connected with the upper part of the first channel (22), or at least two first sub-channels (231) are respectively connected with the lower part of the first channel (22).

7. The heat exchanger of claim 5, wherein At least part of the first sub-channels (231) are connected with the upper part of the first channel (22), and at least part of the first sub-channels (231) are connected with the lower part of the first channel (22).

8. The heat exchanger of claim 1, wherein The communication part (2) comprises a third connecting pipe (27) and a one-way valve, the one-way valve is arranged on the third connecting pipe (27), one end of the third connecting pipe (27) communicates with the second pipe section (112), the other end is close to the partition (13) and communicates with the first pipe section (111), and the one-way valve communicates the lumen of the third connecting pipe (27) in the direction from the second pipe section (112) to the first pipe section (111).

9. The heat exchanger according to claim 2 or 3, characterized in that The communication part (2) comprises a first connecting pipe (25) and a second connecting pipe (26), the first channel (22) comprises the lumen of the first connecting pipe (25), and the second channel (23) comprises the lumen of the second connecting pipe (26).

10. The heat exchanger according to any one of claims 1 to 3 or 5 to 8, characterized in that The first pipe (12) is at least partially located in the first header (11), and the length direction of the first pipe (12) extends along the length direction of the first header (11), and the side wall of the first pipe (12) is provided with at least one first hole (121), and the first hole (121) is located on the side of the first pipe (12) away from the second pipe section (112).

11. The heat exchanger of claim 10, wherein The first pipe (12) has a first end (122) and a second end (123) in the length direction, the first end (122) is located in the first pipe section (111) and is fixedly connected with the first pipe section (111), the second end (123) is located in the second pipe section (112), and the second end (123) has a preset gap with the end of the second pipe section (112).

12. The heat exchanger according to any one of claims 1 to 3 or 5 to 8 or 11, characterized in that The heat exchanger has an evaporation working condition and a condensation working condition in working, in the evaporation working condition, the refrigerant enters the heat exchanger for heat exchange from the first pipe section (111), and in the condensation working condition, the refrigerant enters the heat exchanger for heat exchange from the second header (31).

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