Heat exchanger

Abstract

The present application relates to a heat exchanger. The heat exchanger comprises a first header, a second header, and a plurality of heat exchange tubes, wherein the heat exchange tubes are communicated with the first header and the second header, the first header comprises a first tube section and a second tube section, the first tube section and the second tube section are arranged in the length direction of the first header, the first tube section has a first interface, and the first interface is communicated with a cavity of the first tube section. The heat exchanger further comprises a first distribution portion, wherein the first distribution portion is at least partially located in a cavity of the second header, the first distribution portion comprises a first partition member and a first tube, the second header comprises a third tube section and a fourth tube section, the third tube section and the fourth tube section are respectively located on two sides of the first partition member, the first tube at least partially extends in the length direction of the second header, and the first tube is communicated with the third tube section and the fourth tube section. The heat exchanger can improve the uniformity of refrigerant distribution in the heat exchanger.

Description

heat exchanger

[0001] Cross-reference of related applications

[0002] This application claims priority to Chinese patent application No. 202510238382.X, filed on February 28, 2025, the entire contents of which are incorporated herein by reference. Technical Field

[0003] This application relates to the field of heat exchange technology, specifically to a heat exchanger for a heat pump. Background Technology

[0004] When a heat exchanger is used as an evaporator or heat pump, vapor-liquid separation occurs in the two-phase refrigerant entering the heat exchanger. To ensure that the vapor and liquid refrigerants mix as evenly as possible, a distribution pipe can be installed at the inlet manifold, allowing for more uniform refrigerant distribution after entering the manifold. However, when the heat exchanger has two or more passes, the refrigerant, after passing through the first pass, will enter the next pass's heat exchange tube through another manifold. During the refrigerant's entry into this manifold, the increased flow space leads to pressure loss in the refrigerant flow, and the vapor-liquid separation becomes more severe, resulting in poorer uniformity of refrigerant distribution in subsequent passes and negatively impacting heat exchange performance. Summary of the Invention

[0005] This application provides a heat exchanger that can improve the uniformity of refrigerant distribution within the heat exchanger.

[0006] The heat exchanger provided in this application includes a first manifold, a second manifold, and a plurality of heat exchange tubes. The heat exchange tubes connect the first manifold and the second manifold. The first manifold includes a first tube segment and a second tube segment, which are arranged along the length of the first manifold. The first tube segment has a first interface, which communicates with the cavity of the first tube segment. The heat exchanger also includes a first distribution section, which is at least partially located within the cavity of the second manifold. The first distribution section includes a first partition and a first tube. The second manifold includes a third tube segment and a fourth tube segment, which are located on both sides of the first partition. The first tube extends at least partially along the length of the second manifold and communicates with the third tube segment and the fourth tube segment.

[0007] During operation, the refrigerant enters the first pipe section through the first inlet, exchanges heat through the heat exchange tube connected to the first pipe section, and then enters the second manifold. From the second manifold, it enters the heat exchange tube connected to the second pipe section for further heat exchange. During the refrigerant's journey from the second manifold to the corresponding heat exchange tube, since the second manifold includes a third and a fourth pipe section, and the first pipe extends at least partially along the length of the second manifold and connects to the third and fourth pipe sections, the flow space for the refrigerant is reduced. This decreases pressure loss and vapor-liquid separation. Simultaneously, the first pipe also guides and sprays the passing refrigerant, promoting mixing of the vapor and liquid refrigerant and improving the uniformity of refrigerant distribution within the heat exchanger. Attached Figure Description

[0008] Figure 1 is a schematic diagram of the structure of the heat exchanger provided in this application in a specific embodiment.

[0009] Figure 2 is a schematic diagram of the structure of the heat exchanger provided in this application in a second specific embodiment.

[0010] Figure 3 is a schematic diagram of the flow path of the refrigerant in the heat exchanger in Figure 2.

[0011] Figure 4 is a schematic diagram of the heat exchanger provided in this application in a third specific embodiment.

[0012] Figure 5 is a schematic diagram of the flow path of the refrigerant in the heat exchanger shown in Figure 4.

[0013] Figure 6 is a schematic diagram of the heat exchanger provided in this application in the fourth specific embodiment.

[0014] Figure 7 is a schematic diagram of the structure of the heat exchanger provided in the fifth specific embodiment of this application.

[0015] Figure 8 is a schematic diagram of the structure of the heat exchanger provided in this application in the sixth specific embodiment.

[0016] Reference numerals: First manifold 1, First pipe section 11, First interface 111, Fifth sub-pipe section 112, Sixth sub-pipe section 113, Second pipe section 12, Second manifold 2, Third pipe section 21, First end 211, First sub-pipe section 212, Second sub-pipe section 213, Third sub-pipe section 214, Fourth sub-pipe section 215, Fourth pipe section 22, Second end 221, Heat exchange tube 3, First distribution section 4, First partition 41, First pipe 42, First through hole 421, First sub-pipe 422, Second sub-pipe 423, Second through hole 424, Second partition 43, Second pipe 44, Third partition 45, Second distribution section 5, Fourth partition 51, Third pipe 52, Pipe connector 6, First connecting pipe 61, Capillary tube 62, Fin 7.

[0017] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application. Detailed Implementation

[0018] To better understand the technical solution of this application, the embodiments of this application will be described in detail below with reference to the accompanying drawings.

[0019] The terminology used in the embodiments of this application is for the purpose of describing particular embodiments only and is not intended to be limiting of this application. The singular forms “a,” “the,” and “the” used in the embodiments of this application and the appended claims are also intended to include the plural forms unless the context clearly indicates otherwise.

[0020] It should be understood that the term "and / or" used in this article is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, and B existing alone. Additionally, the character " / " in this article generally indicates that the preceding and following related objects have an "or" relationship.

[0021] It should be noted that the directional terms such as "upper," "lower," "left," and "right" described in the embodiments of this application are used to describe the angles shown in the accompanying drawings and should not be construed as limiting the embodiments of this application. Furthermore, in the context, it should be understood that when referring to an element being connected "upper" or "lower" to another element, it can be directly connected to the other element "upper" or "lower," or indirectly connected through an intermediate element.

[0022] As shown in Figures 1-8, this application embodiment provides a heat exchanger that can improve the uniformity of refrigerant distribution within the heat exchanger. Specifically, the heat exchanger includes a first manifold 1, a second manifold 2, and a plurality of heat exchange tubes 3. The heat exchange tubes 3 connect the first manifold 1 and the second manifold 2. The first manifold 1 includes a first pipe section 11 and a second pipe section 12, which are arranged along the length of the first manifold 1. The first pipe section 11 has a first interface 111, which communicates with the cavity of the first pipe section 11. During evaporation, the refrigerant can enter the first pipe section 11 from the first interface 111. The heat exchanger is divided into two independent processes. The refrigerant can enter the first pipe section 11 from the first interface 111, and then enter multiple heat exchange tubes 3 connected to the first pipe section 11 for heat exchange (the first process of the heat exchanger). After that, it enters the second manifold 2, and then enters multiple heat exchange tubes connected to the second pipe section 12 and the second manifold 2 for heat exchange (the second process of the heat exchanger). In the first and second processes, the specific number of heat exchange tubes 3 can be preset according to the actual situation, and this article does not make a specific limitation on this.

[0023] In addition, the heat exchanger also includes a first distribution section 4, which is at least partially located in the cavity of the second manifold 2. The first distribution section 4 includes a first partition 41 and a first pipe 42. The first partition 41 may be a baffle or other barrier. The second manifold 2 includes a third pipe section 21 and a fourth pipe section 22. The third pipe section 21 and the fourth pipe section 22 are arranged along the length direction of the second manifold 2 and are located on both sides of the first partition 41, respectively. The first pipe 42 extends at least partially along the length direction of the second manifold 2 and connects the third pipe section 21 and the fourth pipe section 22.

[0024] In this embodiment, when the heat exchanger is in operation, the refrigerant can enter the first pipe section 11 from the first interface 111, exchange heat through the heat exchange tube 3 connected to the first pipe section 11, enter the second manifold 2, and then enter the heat exchange tube 3 connected to the second pipe section 12 from the second manifold 2 for heat exchange. During the process of refrigerant entering the corresponding heat exchange tube 3 from the second manifold 2, since the second manifold 2 includes a third tube section 21 and a fourth tube section 22, and the first tube 42 extends at least partially along the length of the second manifold 2 and connects the third tube section 21 and the fourth tube section 22, the flow space of the refrigerant can be reduced, thereby reducing the pressure loss and vapor-liquid separation of the refrigerant. At the same time, at least a portion of the refrigerant in the third tube section 21 can only enter the fourth tube section 22 through the first tube 42. The cavity of the first tube 42 is smaller, which reduces the flow space of the refrigerant, thereby increasing the kinetic energy of the passing refrigerant and making it easier to reach the top of the fourth tube section 22. That is, the first tube 42 can also guide and spray the passing refrigerant, which is conducive to promoting the mixing of vapor and liquid refrigerant, so that the refrigerant flows along the extension direction of the first tube 42 and enters each heat exchange tube 3 of the second process, thereby improving the uniformity of refrigerant distribution in the heat exchanger.

[0025] It should be further explained that, without the first partition 41 and the first pipe 42, the amount of refrigerant (especially liquid refrigerant) reaching the top of the second manifold 2 after flowing out of the heat exchange tube 3 in the first process is relatively small due to pressure loss and gas-liquid separation. In this embodiment, the method of reducing the refrigerant flow space by using the first partition 41 and the first pipe 42 can effectively reduce the pressure loss of the refrigerant. At the same time, the first pipe 42 can also guide the refrigerant. This distribution method not only effectively improves the uniformity of distribution in the heat exchanger from the first process to the second process, but also does not increase the space occupied by the heat exchanger compared to the method of leading out the refrigerant through the external pipe and then introducing it for distribution.

[0026] In this embodiment, the first manifold 1 and the second manifold 2 can be an integral manifold, or a separate plate-type or combined manifold. Furthermore, the heat exchange tube 3 can be a conventional single-channel heat exchange tube or a multi-channel microchannel flat tube; no specific limitation is made herein. Generally, microchannel flat tubes have better heat exchange performance; therefore, the heat exchange tube 3 in this embodiment is preferably a microchannel flat tube.

[0027] Furthermore, the first manifold 1 includes a first pipe segment 11 and a second pipe segment 12, which are arranged along the length of the first manifold 1. The first pipe segment 11 and the second pipe segment 12 can be two independent pipe segments, or they can be formed by the first manifold 1 being separated by a barrier (such as a partition). Generally, in the absence of other connecting elements, the first pipe segment 11 and the second pipe segment 12 are not connected to each other.

[0028] Similarly, the first partition 41 also serves to block the second manifold 2, dividing it into two mutually isolated third pipe sections 21 and 22. This results in the third pipe section 21 having a smaller space than the original second manifold 2 after the refrigerant enters it. Furthermore, the first pipe 42 also reduces the space of the second manifold 2, thereby reducing gas-liquid separation and pressure loss of the refrigerant within it. With this arrangement, some refrigerant can enter the connected heat exchange tube 3 through the space between the outer wall of the first pipe 42 and the third pipe section 21, while the other part enters the first pipe 42, then the fourth pipe section 22, and finally the connected heat exchange tube 3. This distribution method increases the uniformity of refrigerant distribution from the first to the second flow, which is beneficial for improving the heat exchanger's performance.

[0029] As shown in Figure 1, in one specific embodiment, the third pipe segment 21 has a first end 211 along its length, which is away from the fourth pipe segment 22. The length of the cavity wall of the third pipe segment 21 between the first spacer 41 and the first end 211 is defined as L, the length of the cavity wall of the first pipe segment 11 is L1, and the length of the cavity wall of the second pipe segment 12 is L2. Then: 1 / 2 ≤ (L-L1) / L2 ≤ 2 / 3. The first pipe 42 is at least partially located in the third pipe segment 21, and its end communicates with the fourth pipe segment 22. Generally, the shorter the length of the fourth pipe segment 22, the closer the end of the first pipe 42 is to the first spacer 41. This effectively prevents refrigerant accumulation at the top of the first spacer 41, thus preventing liquid buildup. In some embodiments, the end of the first pipe 42 may be approximately flush with the top of the first spacer 41. It should be noted that in the embodiments described herein, the length of the cavity wall refers to the wall length corresponding to the inner cavity of the pipe segment.

[0030] Specifically, in this embodiment, the first end 211 is one end of the third pipe section 21. When the heat exchanger is placed vertically as shown in Figure 1, the first end 211 is the bottom end of the third pipe section 21. The position of the first spacer 41 determines the length of the cavities of the third pipe section 21 and the fourth pipe section 22. The longer the third pipe section 21 is, the shorter the fourth pipe section 22 will be. When the position of the first spacer 41 satisfies 1 / 2≤(L-L1) / L2≤2 / 3, it means that the first spacer 41 is located at 1 / 2 to 2 / 3 of the height of the second pipe section 12. At this time, a portion of the refrigerant in the third pipe section 21 can enter the connected heat exchange tube 3 through the space between the outer wall of the first pipe 42 and the third pipe section 21 for heat exchange, while another portion of the refrigerant will enter the first pipe 42, and then enter the fourth pipe section 22 through the first pipe 42, and finally enter the connected heat exchange tube 3 through the fourth pipe section 22 for heat exchange.

[0031] In this embodiment, the refrigerant in the original second manifold 2 is divided into two parts for distribution. The flow space of these two parts of refrigerant is reduced compared to the original flow space of the second manifold 2, thereby reducing the pressure loss of the refrigerant and the phenomenon of gas-liquid separation. In addition, the first pipe 42 can also play a certain role in turbulence of the refrigerant in the cavity of the second manifold 2, which is conducive to promoting the mixing of gaseous refrigerant and liquid refrigerant, so that the refrigerant can be distributed more evenly in the heat exchanger. To increase the turbulence effect, the outer wall of the first pipe 42 can be roughened or some protrusions or teeth can be added, etc., which are not specifically limited in this article.

[0032] As shown in Figure 1, in one specific embodiment, the sidewall of the first tube 42 is provided with a plurality of first through holes 421. At least some of the first through holes 421 are arranged at intervals along the length direction of the first tube 42. The maximum distance between the first through hole 421 and the first end 211 is defined as L3, then L3 < L - L1.

[0033] As described in the previous embodiment, a portion of the refrigerant in the third pipe section 21 can enter the first pipe 42 and then enter the fourth pipe section 22 for distribution. The proportion of refrigerant entering the first pipe 42 can be increased by the multiple spaced first through holes 421. In addition to the first through holes 421, at least one third through hole 425 can be provided on the side of the first pipe 42 near the first spacer 41. Since the first through hole 421 is positioned lower, more liquid refrigerant enters, while the third through hole 425 is positioned higher, resulting in more gaseous refrigerant entering. This arrangement balances the refrigerant vapor-liquid ratio entering the first pipe 42, making the refrigerant mixture in the first pipe 42 more uniform.

[0034] As shown in Figure 2, in one specific embodiment, the first distribution section 4 further includes a second partition 43 and a second pipe 44. The third pipe section 21 includes a first sub-pipe section 212 and a second sub-pipe section 213. The first sub-pipe section 212 and the second sub-pipe section 213 are arranged along the length direction of the third pipe section 21. The first sub-pipe section 212 and the second sub-pipe section 213 are respectively located on both sides of the second partition 43, and the first sub-pipe section 212 is adjacent to the fourth pipe section 22. The second pipe 44 extends at least partially along the length direction of the second manifold 2, and the second pipe 44 connects the fourth pipe section 22 and the first sub-pipe section 212.

[0035] In this embodiment, the distribution section is augmented with a second partition 43 and a second pipe 44. The second partition 43 divides the third pipe segment 21 into a first sub-pipe segment 212 and a second sub-pipe segment 213. Generally, the lumen length of the fourth pipe segment 22 is greater than the lumen length of the first sub-pipe segment 212. Furthermore, the structure of the second partition 43 can be the same as that of the first partition 41, which will not be elaborated upon here.

[0036] As shown in Figure 3, this separation method allows the refrigerant to enter only the second sub-pipe section 213 after the first heat exchange process when the heat exchanger is working as an evaporator. The second sub-pipe section 213 has a smaller cavity than the original third pipe section 21, which can further reduce the pressure loss and vapor-liquid separation of the refrigerant. After entering the second sub-pipe section 213, the refrigerant enters the fourth pipe section 22 through the first pipe 42. Part of the refrigerant entering the fourth pipe section 22 can enter the connected heat exchange pipe 3 for heat exchange, while the other part of the refrigerant can enter the first sub-pipe section 212 through the second pipe 44, and then enter the connected heat exchange pipe 3 from the first sub-pipe section 212 for heat exchange.

[0037] In this heat exchange process, because the first pipe 42 is positioned lower within the fourth pipe section 22, the refrigerant flowing out of the first pipe 42 causes the rising vaporous refrigerant to carry the liquid refrigerant upwards, distributing it within the fourth pipe section 22. During this process, some refrigerant enters the second pipe 44 and then the second sub-pipe section 213. Due to vapor-liquid separation under evaporation conditions and the difference in weight between the vaporous and liquid refrigerants, the refrigerant entering the second pipe 44 contains a higher proportion of vaporous refrigerant. This reduces refrigerant accumulation in the fourth pipe section 22, promoting refrigerant flow. The continuous flow of refrigerant facilitates more thorough mixing of the two-phase refrigerant during distribution, thereby improving the distribution effect of the two-phase refrigerant.

[0038] As shown in Figure 4, in one specific embodiment, the first distribution section 4 further includes a third partition 45, the structure of which may be the same as that of the first partition 41. In some embodiments, the third partition 45 is a plate or other partition with a partitioning function. The third pipe section 21 includes a third sub-pipe section 214 and a fourth sub-pipe section 215 formed by the third partition 45. The third sub-pipe section 214 and the fourth sub-pipe section 215 are arranged along the length direction of the third pipe section 21, and are located on both sides of the third partition 45. The first through hole 421 is located in the cavity of the fourth sub-pipe section 215.

[0039] Based on the embodiment shown in Figure 1, this embodiment adds a third partition 45 to the first distribution section 4. The third partition 45 divides the third pipe section 21 into a third sub-pipe section 214 and a fourth sub-pipe section 215. As shown in Figure 5, under the blocking effect of the third partition 45 and the first partition 41, the refrigerant can enter the third sub-pipe section 214 and the fourth sub-pipe section 215 respectively after passing through the first heat exchange process. The lumens of the third sub-pipe section 214 and the fourth sub-pipe section 215 are smaller than the original third pipe section 21, thus further reducing the pressure loss and vapor-liquid separation of the refrigerant to a certain extent.

[0040] In this embodiment, when the heat exchanger operates as an evaporator, the refrigerant in the first pipe section 11, after heat exchange through the heat exchange tube 3 connected to it, has a portion that can only enter the third sub-pipe section 214, and then enter the next-pass heat exchange tube 3 connected to the third sub-pipe section 214 for heat exchange. The other portion of the refrigerant can only enter the fourth sub-pipe section 215, then enter the fourth pipe section 22 through the first pipe 42, and subsequently enter the heat exchange tube 3 connected to the fourth pipe section 22 for heat exchange. This distribution arrangement structure can further reduce the cavity of the third pipe section 21, allowing the refrigerant to flow and distribute according to a preset ratio, thereby improving the uniformity of refrigerant distribution. During use, the positions of the first partition 41 and the third partition 45 can be adjusted according to distribution requirements, thereby adjusting the cavity ratio of the third sub-pipe section 214 and the fourth sub-pipe section 215. The specific positions and ratios of these two components are not specifically limited herein.

[0041] As shown in Figure 6, in one specific embodiment, the third pipe segment 21 has a first end 211 in the length direction. Similarly, when the heat exchanger is placed vertically as shown in Figure 6, the first end 211 is the bottom end of the third pipe segment 21, and the first end 211 is far away from the fourth pipe segment 22. The length of the pipe wall of the third pipe segment 21 between the first partition 41 and the first end 211 is defined as L, and the length of the pipe wall of the first pipe segment 11 is defined as L1. Then: 1 / 3≤L / L1≤1 / 2; the first pipe 42 is located between the third pipe segment 21 and the fourth pipe segment 22, and the length direction of the first pipe 42 extends along the length direction of the second manifold 2.

[0042] In this embodiment, the length of the third pipe section 21 is shorter than the length of the first pipe section 11. That is, in the portion of the heat exchange tube 3 connected to the first pipe section 11, one part is connected to the third pipe section 21, and the other part is connected to the fourth pipe section 22. This allows a portion of the refrigerant that has completed heat exchange in the first process to directly enter the fourth pipe section 22, while the other part can only enter the third pipe section 21 and then enter the fourth pipe section 22 through the first pipe 42. Since the flow velocities of these two portions of refrigerant are different when entering the fourth pipe section 22 (the cavity of the third pipe section 21 is smaller, the pressure loss of the refrigerant entering the third pipe section 21 is smaller, and the kinetic energy increases after passing through the first pipe 42 with a smaller cavity, so this portion of refrigerant has a faster flow velocity), the refrigerants with different flow velocities can disturb each other after entering the fourth pipe section 22, allowing the refrigerant in the fourth pipe section 22 to undergo further mixing and flow, thereby promoting the mixing of gaseous refrigerant and liquid refrigerant, so that the refrigerant can be more evenly distributed to each of the connected heat exchange tubes 3 in the second process.

[0043] As shown in Figure 7, in one specific embodiment, the third pipe segment 21 has a first end 211 in the length direction, which is far away from the fourth pipe segment 22. The length of the cavity wall of the third pipe segment 21 between the first spacer 41 and the first end 211 is defined as L, and the length of the cavity wall of the first pipe segment 11 is defined as L1. Then, L = L1. It should be noted that in this embodiment, the length of the first pipe segment 11 is equal to the length of the third pipe segment 21. This is to indicate that when the lengths are equal, the number of heat exchange tubes 3 connecting the first pipe segment 11 is approximately equal to the number of heat exchange tubes 3 connecting the third pipe segment 21. That is, the refrigerant flowing out of the first pipe segment 11 flows into the third pipe segment 21 after heat exchange through the corresponding heat exchange tubes 3. Therefore, L = L1 can have a certain error. Such an error is acceptable as long as the number of heat exchange tubes 3 connecting the first pipe segment 11 is approximately equal to the number of heat exchange tubes 3 connecting the third pipe segment 21. This will not be elaborated further in this article.

[0044] When the number of heat exchange tubes 3 connecting the first pipe section 11 is equal to the number of heat exchange tubes 3 connecting the third pipe section 21, the refrigerant will all enter the third pipe section 21 after the heat exchange in the first process, and then enter the fourth pipe section 22 through the first pipe 42 with a smaller cavity. In this process, the first pipe 42 can guide and accelerate the refrigerant, thereby improving the uniformity of distribution.

[0045] As shown in Figure 7, in one specific embodiment, the first pipe 42 includes a first sub-pipe 422 and a second sub-pipe 423. The distance from the first sub-pipe 422 to the first end 211 is less than the distance from the second sub-pipe 423 to the first end 211. The fourth pipe segment 22 has a second end 221 in the length direction. When the heat exchanger is placed vertically as shown in Figure 7, the second end 221 is the top end of the fourth pipe segment 22, and the second end 221 is far away from the third pipe segment 21. The distance from the first sub-pipe 422 to the second end 221 is less than the distance from the second sub-pipe 423 to the second end 221.

[0046] It is understandable that after the refrigerant enters the third pipe section 21, although the cavity of the third pipe section 21 is smaller than that of the second manifold 2, it is still larger than that of the heat exchange pipe 3. In addition, the dryness of the refrigerant increases after the heat exchange of the first process, and the gas-liquid separation will be more serious. Therefore, the refrigerant will still experience gas-liquid separation in the third pipe section 21. The gaseous refrigerant will flow upward, while the liquid refrigerant will sink due to gravity.

[0047] In this embodiment, the distance from the first sub-pipe 422 to the first end 211 is less than the distance from the second sub-pipe 423 to the first end 211, and the distance from the first sub-pipe 422 to the second end 221 is less than the distance from the second sub-pipe 423 to the second end 221. This allows more liquid refrigerant in the third pipe section 21 to enter the first sub-pipe 422, which has a lower end position, while more gaseous refrigerant enters the second sub-pipe 423, which has a higher end position. Since the outlet position of the first sub-pipe 422 is higher than the outlet position of the second sub-pipe 423, the liquid refrigerant flowing out of the first sub-pipe 422 will sink, while the gaseous refrigerant flowing out of the second sub-pipe 423 will flow upward. This flow pattern can further promote the mixing of gaseous and liquid refrigerant in the fourth pipe section 22, thereby improving the uniformity of refrigerant distribution.

[0048] As shown in Figure 8, in one specific embodiment, the first pipe 42 is at least partially located in the fourth pipe segment 22, the end of the first pipe 42 is connected to the third pipe segment 21, and the side wall of the first pipe 42 is provided with a plurality of second through holes 424, at least some of the second through holes 424 are arranged at intervals along the length direction of the first pipe 42.

[0049] In this embodiment, the first pipe 42 is at least partially located within the fourth pipe section 22. After the refrigerant enters the third pipe section 21, it can only enter the fourth pipe section 22 through the multiple second through holes 424 spaced apart on the first pipe 42, and then be distributed into the heat exchange tubes 3 at various locations. With the first partition 41 separating the second manifold 2 and reducing refrigerant gas-liquid separation, the end of the first pipe 42 is connected to the third pipe section 21. This allows the refrigerant in the third pipe section 21 to enter only the first pipe 42, be distributed into the fourth pipe section 22 along the spaced second through holes 424 on the first pipe 42, and then enter the heat exchange tubes 3 at various locations for heat exchange. This distribution method effectively improves the uniformity of refrigerant distribution during the second process of the heat exchanger, thereby improving the uniformity of heat exchange in the heat exchanger.

[0050] As shown in Figures 1-8, in one specific embodiment, the heat exchanger further includes a second distribution section 5, which is at least partially located within the cavity of the first pipe section 11. The second distribution section 5 includes a fourth partition 51 and a third pipe 52. The fourth partition 51 divides the first pipe section 11 into a fifth sub-pipe section 112 and a sixth sub-pipe section 113. The fifth sub-pipe section 112 and the sixth sub-pipe section 113 are arranged along the length direction of the first pipe section 11, and are located on both sides of the fourth partition 51, respectively. The third pipe 52 extends at least partially along the length direction of the first pipe section 11, and connects the fifth sub-pipe section 112 and the sixth sub-pipe section 113. The first interface 111 is located in the fifth sub-pipe section 112.

[0051] In the aforementioned embodiments, the first distribution unit 4 distributes the refrigerant from the first process to the second process in the heat exchanger, while the second distribution unit 5 in this embodiment distributes the refrigerant when it enters the heat exchanger during the first process. During evaporation, gas-liquid separation still occurs when the refrigerant enters the fifth sub-pipe section 112 from the first interface 111. After entering the fifth sub-pipe section 112, a portion of the refrigerant, guided by the third pipe 52, is directly distributed and enters each heat exchange tube 3 connected to the fifth sub-pipe section 112 for heat exchange, while the other portion enters the sixth sub-pipe section 113 through the third pipe 52 for distribution. During this process, the refrigerant spontaneously moves from the high-pressure zone to the low-pressure zone. In addition, due to the vapor-liquid separation under evaporation conditions and the difference in weight between the vapor and liquid refrigerants, the refrigerant entering the third tube 52 contains a higher proportion of vapor refrigerant. This reduces the accumulation of refrigerant in the fifth sub-tube section 112 and promotes refrigerant flow. The continuous flow of refrigerant facilitates the thorough mixing of the two-phase refrigerant during distribution, thereby improving the distribution effect of the two-phase refrigerant.

[0052] As shown in Figures 6-8, in one specific embodiment, the heat exchanger further includes a pipe fitting 6, which includes a first connecting pipe 61 and a capillary tube 62. The first connecting pipe 61 is connected to the first interface 111, and the capillary tube 62 is connected to the first connecting pipe 61 and the sixth sub-pipe segment 113.

[0053] In the previous embodiment, although the added second distribution section 5 can improve the uniformity of refrigerant distribution when entering the heat exchanger, when the heat exchanger is operating as a condenser, the refrigerant flowing in the opposite direction is blocked by the fourth partition 51 after entering the sixth sub-tube section 113, resulting in a large flow resistance. Therefore, the refrigerant flow rate in this part is slow, which adversely affects the heat exchange performance of the heat exchanger under condensation conditions. However, after the capillary tube 62 connects the first connecting pipe 61 and the sixth sub-tube section 113, the refrigerant blocked in the sixth sub-tube section 113 can directly enter the first connecting pipe 61 through the capillary tube 62 and then flow directly out from the first connecting pipe 61. This reduces the flow resistance encountered by the refrigerant in the sixth sub-tube section 113 under condensation conditions, making the refrigerant flow more convenient and thus improving the heat exchange efficiency of the heat exchanger when operating as a condenser.

[0054] It should be noted that the heat exchangers in the various embodiments of this article also include an outlet for refrigerant outflow and other components such as fins. In some embodiments, the outlet for refrigerant outflow can be located on the side wall of the second pipe section 12 and communicate with the lumen of the second pipe section 12. Fins can be disposed between at least a portion of the heat exchange tubes 3. The fins can be corrugated fins, or insert fins or through-tube fins, etc. Since these components do not affect the distribution performance of the heat exchanger, they will not be described in detail here.

[0055] The above examples illustrate the principles and implementation methods of this application. The descriptions of the embodiments are merely for the purpose of helping to understand the methods and core ideas of this application. It should be noted that those skilled in the art can make various improvements and modifications to this application without departing from its principles, and these improvements and modifications should also fall within the protection scope of this application.

Claims

1. A heat exchanger, characterized in that, The heat exchanger includes a first manifold (1), a second manifold (2), and a plurality of heat exchange tubes (3). The heat exchange tubes (3) connect the first manifold (1) and the second manifold (2). The first manifold (1) includes a first pipe section (11) and a second pipe section (12). The first pipe section (11) and the second pipe section (12) are arranged along the length of the first manifold (1). The first pipe section (11) has a first interface (111) that communicates with the cavity of the first pipe section (11). The heat exchanger also includes a first distribution section (4). The first distribution section (4) is at least partially located within the cavity of the second manifold (2). The first distribution section (4) includes a first partition (41) and a first pipe (42). The second manifold (2) includes a third pipe segment (21) and a fourth pipe segment (22). The third pipe segment (21) and the fourth pipe segment (22) are located on both sides of the first partition (41). The first pipe (42) extends at least partially along the length direction of the second manifold (2), and the first pipe (42) connects the third pipe segment (21) and the fourth pipe segment (22).

2. The heat exchanger according to claim 1, characterized in that, The third pipe segment (21) has a first end (211) in the length direction. The first end (211) is away from the fourth pipe segment (22). The length of the wall of the third pipe segment (21) between the first spacer (41) and the first end (211) is defined as L. The length of the wall of the first pipe segment (11) is defined as L1. The length of the wall of the second pipe segment (12) is defined as L2. Then: 1 / 2≤(L-L1) / L2≤2 / 3; The first pipe (42) is at least partially located in the third pipe segment (21), and the end of the first pipe (42) is in communication with the fourth pipe segment (22).

3. The heat exchanger according to claim 2, characterized in that, The sidewall of the first tube (42) is provided with a plurality of first through holes (421), and at least some of the first through holes (421) are arranged at intervals along the length direction of the first tube (42). The maximum distance between the first through hole (421) and the first end (211) is defined as L3, then L3 < L-L1.

4. The heat exchanger according to claim 2 or 3, characterized in that, The first distribution section (4) further includes a second partition (43) and a second pipe (44). The third pipe section (21) includes a first sub-pipe section (212) and a second sub-pipe section (213). The first sub-pipe section (212) and the second sub-pipe section (213) are located on both sides of the second partition (43), and the first sub-pipe section (212) is adjacent to the fourth pipe section (22). The second pipe (44) extends at least partially along the length direction of the second manifold (2), and the second pipe (44) connects the fourth pipe section (22) and the first sub-pipe section (212).

5. The heat exchanger according to claim 3, characterized in that, The first distribution section (4) further includes a third partition (45), the third pipe section (21) includes a third sub-pipe section (214) and a fourth sub-pipe section (215), the third sub-pipe section (214) and the fourth sub-pipe section (215) are respectively located on both sides of the third partition (45), and the first through hole (421) is located in the cavity of the fourth sub-pipe section (215).

6. The heat exchanger according to any one of claims 1 to 5, characterized in that, The third pipe segment (21) has a first end (211) in the length direction. The first end (211) is away from the fourth pipe segment (22). The length of the cavity wall of the third pipe segment (21) between the first spacer (41) and the first end (211) is defined as L. The length of the cavity wall of the first pipe segment (11) is defined as L1. Then: 1 / 3≤L / L1≤1 / 2; the first pipe (42) is located between the third pipe segment (21) and the fourth pipe segment (22).

7. The heat exchanger according to any one of claims 1 to 5, characterized in that, The third pipe segment (21) has a first end (211) in the length direction. The first end (211) is far away from the fourth pipe segment (22). The length of the wall of the third pipe segment (21) between the first spacer (41) and the first end (211) is defined as L. The length of the wall of the first pipe segment (11) is defined as L1. Then: L = L1.

8. The heat exchanger according to claim 7, characterized in that, The first pipe (42) includes a first sub-pipe (422) and a second sub-pipe (423), the distance from the first sub-pipe (422) to the first end (211) is less than the distance from the second sub-pipe (423) to the first end (211); the fourth pipe segment (22) has a second end (221) in the length direction, the second end (221) is away from the third pipe segment (21), and the distance from the first sub-pipe (422) to the second end (221) is less than the distance from the second sub-pipe (423) to the second end (221).

9. The heat exchanger according to claim 7, characterized in that, The first pipe (42) is at least partially located in the fourth pipe segment (22), and the end of the first pipe (42) is connected to the third pipe segment (21). The sidewall of the first pipe (42) is provided with a plurality of second through holes (424), and at least some of the second through holes (424) are arranged at intervals along the length direction of the first pipe (42).

10. The heat exchanger according to any one of claims 1 to 9, characterized in that, The heat exchanger further includes a second distribution section (5), which is at least partially located within the cavity of the first pipe section (11). The second distribution section (5) includes a fourth partition (51) and a third pipe (52). The first pipe section (11) includes a fifth sub-pipe section (112) and a sixth sub-pipe section (113). The fifth sub-pipe section (112) and the sixth sub-pipe section (113) are respectively located on both sides of the fourth partition (51). The third pipe (52) extends at least partially along the length direction of the first pipe section (11) and connects the fifth sub-pipe section (112) and the sixth sub-pipe section (113). The first interface (111) is located in the fifth sub-pipe section (112).

11. The heat exchanger according to claim 10, characterized in that, The heat exchanger also includes a pipe fitting (6), which includes a first connecting pipe (61) and a capillary tube (62). The first connecting pipe (61) is connected to the first interface (111), and the capillary tube (62) is connected to the first connecting pipe (61) and the sixth sub-pipe section (113).

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