Header assembly and heat exchanger

Abstract

The header assembly comprises a first pipe, a first connector, a second pipe and at least one first plate, the first pipe is provided with a first end in the length direction, the first pipe comprises a first sub-pipe section and a second sub-pipe section, and the first sub-pipe section and the second sub-pipe section are arranged in the length direction of the first pipe; the first end is positioned on the first sub-pipe section; the first interface is communicated with the first sub-pipe section; the first plate is at least partially located in a pipe cavity of the first sub-pipe section, the first plate comprises a first channel, and the first channel can communicate with pipe cavities of the first sub-pipe sections on the two sides of the first plate; the second pipe comprises a first opening and a second opening, the first opening is located between the first end and the first plate, the second opening is located in the second sub-pipe section, and the second pipe communicates with the first sub-pipe section and the second sub-pipe section. According to the header assembly, the distribution effect can be improved, and refrigerants can be distributed more evenly.

Description

Technical Field

[0001] The present application relates to the field of heat exchange technology, and in particular to a header assembly and a heat exchanger. Background Art

[0002] In the related art, when the heat exchanger is used as an evaporator, especially the heat exchanger with the manifold placed vertically (the flat tube placed horizontally), it mainly relies on setting up multiple circuits to try to meet the uniform distribution of the effective slow-heating surface of the entire heat exchanger. However, in each independent circuit, due to the inconsistent density of the refrigerant gas and liquid, the gas-liquid separation of the refrigerant will cause the flat tubes near the lower part of the manifold to have more liquid-phase refrigerant and less gas-phase refrigerant in the circuit along the gravity direction. The flat tubes near the upper part of the manifold have more gas-phase refrigerant and less liquid-phase refrigerant, that is, the gas-liquid two-phase refrigerant of the upper and lower multiple flat tubes in a single independent circuit cannot be evenly distributed. The amount of liquid-phase refrigerant flowing through the flat tubes is small, which will reduce the heat exchange performance of the heat exchanger in this part of the area. Summary of the invention

[0003] A first aspect of an embodiment of the present application provides a header assembly, which can improve the distribution effect and make the distribution of the refrigerant more uniform.

[0004] According to the first aspect of the embodiment of the present application, the header assembly specifically includes: A first tube, wherein the first tube has a first end in the length direction, the first tube comprises a first sub-tube segment and a second sub-tube segment, the first sub-tube segment and the second sub-tube segment are arranged along the length direction of the first tube, and the first end is located in the first sub-tube segment; a first interface, the first interface being in communication with the first sub-pipe segment; at least one first plate, wherein the first plate is at least partially located in the tube cavity of the first sub-tube segment, and the first plate comprises a first channel, and the first channel can communicate with the tube cavities of the first sub-tube segment on both sides of the first plate; The second tube comprises a first opening and a second opening, the first opening is located between the first end and the first plate, the second opening is located in the second sub-tube segment, and the second tube connects the first sub-tube segment and the second sub-tube segment.

[0005] The beneficial effects of the embodiments of the present application are: In the collecting pipe assembly of the embodiment of the present application, after the refrigerant enters the first sub-pipe segment from the first interface, the gaseous refrigerant will drive the liquid refrigerant to flow upward. When passing through the first channel of the first plate, since the flow cross-sectional area of ​​the first channel is smaller than the flow cross-sectional area of ​​the first sub-pipe segment, the refrigerant will be sprayed, thereby causing the gaseous refrigerant and the liquid refrigerant to mix. The first plate can also block the rise of part of the gaseous refrigerant and the sinking of the liquid refrigerant, reducing the gas-liquid separation of the refrigerant under the influence of gravity, thereby improving the uniformity of distribution; in addition, the refrigerant that is not distributed and gathered in the first sub-pipe segment in time will be introduced into the second sub-pipe segment through the second tube, thereby reducing the aggregation of the refrigerant and improving the uniformity of the refrigerant distribution in the first sub-pipe segment.

[0006] In addition, the manifold assembly provided in the first aspect of the present application may also have the following additional technical features: In an optional solution, the length of the first sub-segment is defined as L1, and the length of the second sub-segment is defined as L2, then L1 and L2 satisfy: 0.5 ≤ L1 / (L1+ L2) ≤ 0.9. When the ratio of the length of the first sub-segment to the length of the second sub-segment is within this range, the refrigerant gas-liquid separation phenomenon caused by the first sub-segment or the second sub-segment being too long can be avoided, and the refrigerant distribution effect is better.

[0007] In an optional solution, the first channel includes a first hole, the first hole is provided in the first plate, the number of the first holes is one or more, and / or the first channel includes a gap between the first plate and the tube wall of the first sub-tube segment. The refrigerant is sprayed by means of the first hole and / or the gap, thereby improving the overall distribution effect.

[0008] In an optional solution, the number of the first plates is N, N ≥ 3, and along the first direction, the first first plate is defined as a first sub-plate, and the flow cross-sectional area of ​​the first channel of the first sub-plate is S1, and the Nth first plate is defined as an Nth sub-plate, and the flow cross-sectional area of ​​the first channel of the Nth sub-plate is S N , there is an Mth sub-plate between the first sub-plate and the Nth sub-plate, and the flow cross-sectional area of ​​the first channel of the Mth sub-plate is S M , then: S1>S M >S N When there are multiple first plates, due to the gravity relationship between the gas-liquid two-phase refrigerant, the refrigerant flowing through each first plate will have resistance loss, and the flow rate of the refrigerant will become lower and lower along the flow direction of the refrigerant. Therefore, reducing the flow cross-sectional area of ​​the first channel along the flow direction of the refrigerant (i.e., the first direction) can ensure the flow rate of the refrigerant, thereby improving the distribution efficiency.

[0009] In an optional solution, the manifold assembly further includes a second plate, the second plate is at least partially located in the tube cavity of the first tube, and the first sub-tube segment and the second sub-tube segment are respectively located on both sides of the second plate; The number of the first boards is N, N≥3. Along the first direction, the first first board is defined as the first sub-board, the Nth first board is defined as the Nth sub-board, there is an Mth sub-board between the first sub-board and the Nth sub-board, the shortest distance from the first sub-board to the second board is L3, and the shortest distance between the Mth sub-board and the adjacent first board is L M , the shortest distance between the Nth sub-board and the first end is L N , then: L3≤L M ≤L N Similarly, along the flow direction of the refrigerant, increasing the distance between two adjacent first plates can ensure the flow rate of the refrigerant, thereby improving the distribution efficiency.

[0010] In an optional solution, the flow cross-sectional area of ​​the first sub-pipe segment is defined as S4, and S4 is equal to S N Between: 1 / 10≤ S N / S4<1 / 4. When the flow cross-sectional area of ​​the first channel of the Nth sub-plate is too small or too large, the refrigerant flow through the Nth sub-plate will decrease or increase, affecting the overall distribution effect. Therefore, setting a suitable proportion of the flow cross-sectional area can make the refrigerant flow more smoothly in the entire first sub-pipe section, thereby improving the distribution effect.

[0011] In an optional solution, a surface extending along the second direction and passing through the first sub-tube segment is defined as the first surface, the second direction is perpendicular to the first direction, and on the first surface, the projections of two adjacent first channels are staggered. The two adjacent first channels arranged in a staggered manner can alternately block the refrigerant, increase the time the refrigerant stays between the two adjacent first channels, thereby better achieving the effect of distributing while flowing and improving the uniformity of distribution.

[0012] In an optional solution, the second tube further includes a first connecting section, the first connecting section is located in the tube cavity of the first tube, or the first connecting section is at least partially located outside the first tube, and the first connecting section connects the first opening and the second opening. The first connecting section can be arranged in the tube cavity of the first tube or outside the first tube, so as to better adapt to different installation environments and different installation requirements.

[0013] In an optional solution, the first connecting section is located in the tube cavity of the first tube, the first plate is fixedly connected to the second tube, and / or the first plate is fixedly connected to the tube wall of the first sub-tube section.

[0014] In an optional solution, the first connecting section includes a second hole, the second hole is located in the tube wall of the first connecting section, and the distance from the second hole to the first interface is smaller than the distance from the first opening to the first interface. The second hole on the first connecting section allows a portion of the refrigerant to enter the first connecting section from the second hole, and then enter the second sub-tube section. Since the distance from the second hole to the first interface is smaller than the distance from the first opening to the first interface, the proportion of vapor refrigerant in the refrigerant entering the second sub-tube section from the first opening is higher than the proportion of liquid refrigerant, and the proportion of liquid refrigerant in the refrigerant entering from the second hole is higher than the proportion of vapor refrigerant, thereby balancing the gas-liquid ratio of the refrigerant entering the second sub-tube section and improving the uniformity of gas-liquid distribution in the second sub-tube section.

[0015] In an optional solution, the manifold assembly further includes a third tube, the third tube connects the first sub-tube segment and the second sub-tube segment, the third tube includes a third opening, the third opening is located in the first sub-tube segment, and the distance from the third opening to the first interface is smaller than the distance from the first opening to the first interface. The function of the third tube is similar to that of the second hole mentioned above, and can improve the uniformity of gas-liquid distribution in the second sub-tube segment.

[0016] In an optional solution, the first tube further includes a third sub-tube segment, which is arranged along the length direction of the first tube, connected to the first end, or an end of the second sub-tube segment away from the first sub-tube segment, and communicated with the first sub-tube segment. The refrigerant deposited in the first sub-tube segment can be introduced into the third sub-tube segment for distribution, thereby improving the distribution efficiency.

[0017] In an optional solution, the second tube further includes a fourth opening and a second connecting section, the fourth opening is located in the third sub-tube section, and the second connecting section connects the fourth opening and the connecting section of the second tube.

[0018] In an optional solution, the length of the third sub-segment is defined as L4, then L1 and L4 satisfy: 0.5 ≤ L1 / (L1 + L4) ≤ 0.9. Similarly, when the ratio of the length of the first sub-segment to the length of the third sub-segment is within this range, the refrigerant gas-liquid separation phenomenon caused by the first sub-segment or the third sub-segment being too long can be avoided, and the refrigerant distribution effect is better.

[0019] In an optional solution, the manifold assembly further includes a guide plate, the guide plate is at least partially located in the first sub-cavity, and the guide plate is configured to guide at least part of the fluid entering the first interface. The guide plate can shield the refrigerant entering the first interface to a certain extent, avoiding direct distribution of the refrigerant after entering from the first interface, thereby improving the uniformity of distribution.

[0020] A second aspect of an embodiment of the present application provides a heat exchanger, comprising: a first header and a second header, the first header and the second header are arranged at intervals, the first header comprises at least one header assembly provided in an embodiment of the first aspect, and the header assembly is arranged along a length direction of the first header; A plurality of heat exchange tubes are provided, wherein the plurality of heat exchange tubes are connected to the first header and the second header.

[0021] The beneficial effects of the embodiments of the present application are: According to a heat exchanger provided in the second aspect of the present application, the heat exchanger applies the header assembly of the first aspect embodiment to the heat exchanger. Since the header assembly of the first aspect embodiment has a better distribution effect, the refrigerant entering each heat exchange tube from the first header is distributed more evenly, so the heat exchange effect of each heat exchange tube is better, thereby improving the heat exchange performance of the entire heat exchanger.

[0022] In an optional solution, the heat exchanger further comprises fins, wherein the fins are arranged at intervals on at least a portion of the heat exchange tubes along the length direction of the first header; When the heat exchanger is working, the length direction of the first header is parallel to the gravity direction.

[0023] It should be understood that the foregoing general description and the following detailed description are exemplary only and are not restrictive of the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 A schematic structural diagram of a specific embodiment of a manifold assembly provided in the present application; Figure 2 A schematic structural diagram of a second specific embodiment of the manifold assembly provided in the present application; Figure 3 A schematic structural diagram of a third specific embodiment of the manifold assembly provided by the present application; Figure 4 A schematic structural diagram of a fourth specific embodiment of the manifold assembly provided by the present application; Figure 5 A schematic structural diagram of a fifth specific embodiment of the manifold assembly provided in the present application; Figure 6A schematic structural diagram of a sixth specific embodiment of the manifold assembly provided by the present application; Figure 7 A schematic structural diagram of a seventh specific embodiment of the manifold assembly provided by the present application; Figure 8 A schematic structural diagram of an eighth specific embodiment of the manifold assembly provided by the present application; Fig. 9 A schematic structural diagram of a ninth specific embodiment of the header assembly provided by the present application; Fig.10 A schematic diagram of the structure of a specific embodiment of the heat exchanger provided in this application.

[0025] Figure numerals: first tube 1, first end 11, first sub-tube segment 12, second sub-tube segment 13, third sub-tube segment 14, first interface 2, first plate 3, first channel 31, first hole 311, gap 312, first sub-plate 32, Mth sub-plate 33, Nth sub-plate 34, second tube 4, first opening 41, second opening 42, first connecting segment 43, second hole 431, third opening 44, second connecting segment 45, second plate 5, first surface 6, third tube 7, fourth opening 71, guide plate 8, first header 91, second header 92, heat exchange tube 93, fin 94.

[0026] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the present application and, together with the description, serve to explain the principles of the present application. Implementation

[0027] In order to better understand the technical solution of the present application, the embodiments of the present application are described in detail below with reference to the accompanying drawings.

[0028] It should be clear that the described embodiments are only part of the embodiments of the present application, rather than all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in the field without creative work are within the scope of protection of the present application.

[0029] 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 plural forms, unless the context clearly indicates other meanings.

[0030] It should be understood that the term "and / or" used in this article is only a description of the association relationship of associated objects, indicating that there can be three relationships. For example, A and / or B can represent: A exists alone, A and B exist at the same time, and B exists alone. In addition, the character " / " in this article generally indicates that the associated objects before and after are in an "or" relationship.

[0031] It should be noted that the directional words such as "upper", "lower", "left", and "right" described in the embodiments of the present application are described at the angles shown in the accompanying drawings and should not be understood as limiting the embodiments of the present application. In addition, in the context, it is also necessary to understand that when it is mentioned that an element is connected to another element "upper" or "lower", it can not only be directly connected to another element "upper" or "lower", but also indirectly connected to another element "upper" or "lower" through an intermediate element.

[0032] A first aspect of an embodiment of the present application provides a manifold assembly. This article describes its technical solution and technical effects by taking the application of the manifold assembly in a heat exchanger as an example. The heat exchanger in the embodiment of the present application can be a parallel flow heat exchanger or a parallel flow microchannel heat exchanger, but the specific type of heat exchanger is not limited to the description in this article, and can also be other types of heat exchangers that require distribution of heat exchange medium, which are not listed one by one here.

[0033] Refrigerant vapor compression system is a well-known technology in the art. For the evaporator in the air-conditioning system that adopts the refrigerant vapor compression cycle, the refrigerant in the system will become a gas-liquid two-phase state after passing through the throttling device and then reach the evaporator inlet. Whether the refrigerant two-phase fluid, especially the liquid therein, can be evenly distributed to each channel for heat exchange is the key to the design and structure of the evaporator.

[0034] In actual operation, when the liquid distribution in each channel is uneven due to changes in working conditions or unreasonable design of the liquid distributor, the refrigerant flow in the tube will be unevenly distributed. Some tubes have less flow, which evaporates prematurely and causes excessive superheat at the outlet of the tube; while some tubes have too much flow, resulting in too small superheat at the outlet, or even containing some liquid. Both will make the heat exchange area of ​​the evaporator not fully utilized, thus seriously affecting the system performance. Therefore, how to quickly and effectively achieve uniform distribution of refrigerant inside the heat exchanger is a major problem in the current industry.

[0035] In order to improve the distribution effect and make the refrigerant distribution more uniform, the first aspect of the embodiment of the present application provides a header assembly. Figure 1As shown, the manifold assembly includes a first tube 1, a first interface 2, at least one first plate 3, and a second tube 4. The first tube 1 has a first end 11 in the length direction, and the first tube 1 includes a first sub-tube segment 12 and a second sub-tube segment 13. The first sub-tube segment 12 and the second sub-tube segment 13 are arranged along the length direction of the first tube 1, and the first end 11 is located in the first sub-tube segment 12; the first interface 2 is connected to the first sub-tube segment 12; the first plate 3 is at least partially located in the tube cavity of the first sub-tube segment 12, and the first plate 3 includes a first channel 31, and the first channel 31 can connect the tube cavities of the first sub-tube segment 12 on both sides of the first plate 3; the second tube 4 includes a first opening 41 and a second opening 42, the first opening 41 is located between the first end 11 and the first plate 3, the second opening 42 is located in the second sub-tube segment 13, and the second tube 4 connects the first sub-tube segment 12 and the second sub-tube segment 13.

[0036] Specifically, the first tube 1 is a tubular structure with sealed ends and hollow inside, such as a rectangular tube or a cylindrical tube. In this embodiment, the first tube 1 is a cylindrical tube body, and the first end 11 of the first tube 1 can be an end cap of the first tube 1 along the length direction, and the end cap is sealed to the first tube 1. In addition, the first sub-tube segment 12 and the second sub-tube segment 13 can be formed by separating the first tube 1 by the second plate 5, and the second plate 5 is at least partially located in the tube cavity of the first tube 1, and the first sub-tube segment 12 and the second sub-tube segment 13 are respectively located on both sides of the second plate 5. It should be noted that, the at least part mentioned here means that the second plate 5 can be completely located in the tube cavity of the first tube 1, for example, the outer wall of the entire second plate 5 is fixedly connected to the inner wall of the first tube 1 by welding or the like, so that the entire second plate 5 is completely located in the tube cavity of the first tube 1; in addition, the second plate 5 can also be only partially located in the tube cavity of the first tube 1, and the other part extends out of the tube cavity of the first tube 1. For example, when the second plate 5 is arranged on the first tube 1 by plugging or the like, the area of ​​the second plate 5 needs to be slightly larger than the cross-section of the first tube 1 to ensure the stable cooperation between the second plate 5 and the first tube 1, that is, the second plate 5 is partially located in the tube cavity of the first tube 1.

[0037] like Figure 1 As shown, in this embodiment, the function of the second plate 5 is to physically isolate the first tube 1, so that the first tube 1 forms a first sub-tube segment 12 and a second sub-tube segment 13. When the first sub-tube segment 12 and the second sub-tube segment 13 are not connected through the second tube 4, the first sub-tube segment 12 and the second sub-tube segment 13 are isolated from each other and not connected.

[0038] When the header assembly of this embodiment is assembled into the heat exchanger and operates as an evaporator, the refrigerant enters the first sub-tube segment 12 from the first interface 2, and the gas-liquid separation of the refrigerant causes the gaseous refrigerant to drive the liquid refrigerant to flow upward. When passing through the first channel 31 of the first plate 3, since the flow cross-sectional area of ​​the first channel 31 is smaller than the flow cross-sectional area of ​​the first sub-tube segment 12, the first plate 3 and the first channel 31 can play two roles. One is the throttling expansion effect of the first channel 31, that is, when the refrigerant passes through the first channel 31, the two-phase refrigerant will be sprayed, so that the two-phase refrigerant will be mixed during the spraying process, and part of the mixed two-phase refrigerant will be distributed, and the other part will continue to flow along the tube cavity of the first sub-tube segment 12, and will be sprayed and merged again when flowing through the next first channel 31. This multiple spraying and fusion can make the gas-liquid mixing of the two-phase refrigerant more uniform, thereby improving the uniformity of distribution. The second is the barrier effect. Because the refrigerant in the gas-liquid two-phase state will be affected by gravity and will have a certain degree of gas-liquid stratification, the gaseous refrigerant tends to gather in the upper space of the tube cavity, and the liquid refrigerant tends to accumulate in the lower part of the tube cavity. Therefore, the first plate 3 can block the rise of gas and the sinking of liquid to a large extent, thereby making the refrigerant mixing between the several tube cavities of the first sub-tube segment 12 separated by the first plate 3 more even.

[0039] In the process of two-phase refrigerant flowing and distributing, due to the influence of gravity, the vapor refrigerant in the uppermost refrigerant generally has more liquid refrigerant, and the accumulated refrigerant will slow down the flow rate of the refrigerant, affecting the uniformity of distribution. Therefore, the refrigerant that has not been distributed in time at the uppermost part of the first sub-segment 12 can be introduced into the second sub-segment 13 through the first opening 41 and the second opening 42 of the second tube 4, thereby increasing the distribution efficiency and improving the uniformity of distribution. It should be noted that because the first interface 2 is connected to the first sub-segment 12, the refrigerant that continuously enters from the first interface 2 will make the pressure in the first sub-segment 12 always higher than that in the second sub-segment 13, and the refrigerant flows from high pressure to low pressure without reverse flow.

[0040] like Figure 2As shown, in a specific embodiment, the length of the first sub-segment 12 is defined as L1, and the length of the second sub-segment 13 is defined as L2, then L1 and L2 satisfy: 0.5 ≤ L1 / (L1+ L2) ≤ 0.9. When the heat exchanger to which the manifold is applied is used as an evaporator, because the dryness of the refrigerant at the inlet of the evaporator is generally below 0.5, when the above ratio is less than 0.5, it means that the length of the first sub-segment 12 may be small, and its tube cavity is not enough to provide a large enough space for the flow and distribution of the refrigerant. At this time, a large amount of two-phase refrigerant will be brought into the tube cavity of the second sub-segment 13, and the refrigerant in the second sub-segment 13 will have gas-liquid stratification along the gravity direction. When the ratio is greater than 0.9, the tube cavity space of the second sub-segment 13 is too small, and it is easy to be filled with the refrigerant introduced by the distribution pipe, but a large amount of gas cannot be introduced, resulting in the first sub-segment 12 also being filled with refrigerant, causing uneven liquid distribution. Therefore, when the length ratio of the first sub-segment 12 to the second sub-segment 13 satisfies the above range, the refrigerant distribution effect is better.

[0041] like Figure 2-3 As shown, in a specific embodiment, the first channel 31 includes a first hole 311, the first hole 311 is provided in the first plate 3, the number of the first holes 311 is one or more, and / or the first channel 31 includes a gap 312 located between the first plate 3 and the tube wall of the first sub-tube segment 12. It should be supplemented that the shape of the first hole 311 and the gap 312 can be circular or rectangular, or can be an irregular shape, such as a combination of multiple shapes, etc., which is not specifically limited herein, as long as the first hole 311 and the gap 312 can communicate with the tube cavity of the first sub-tube segment 12 on both sides of the first plate 3. In addition, the first hole 311 and the gap 312 can exist separately, or can exist simultaneously in the same first sub-tube segment 12. The refrigerant is sprayed by means of the first hole 311 and / or the gap 312, thereby improving the overall distribution effect.

[0042] In addition, due to the gravity relationship between the gas-liquid two-phase refrigerant and the barrier effect of the first plate 3, the refrigerant flowing through each first plate 3 will have a pressure loss, and its flow rate will become lower and lower along the flow direction of the refrigerant. Therefore, the number, position, etc. of the first holes 311 and the gaps 312 can be adjusted according to actual distribution requirements. In this regard, the embodiments of the present application will be described in detail below.

[0043] like Figure 2 As shown, in a specific embodiment, the number of first plates 3 is N, N ≥ 3, along the first direction, the first first plate 3 is defined as the first sub-plate 32, the flow cross-sectional area of ​​the first channel 31 of the first sub-plate 32 is S1, the Nth first plate 3 is the Nth sub-plate 34, the flow cross-sectional area of ​​the first channel 31 of the Nth sub-plate 34 is S NThere is an Mth sub-plate 33 between the first sub-plate 32 and the Nth sub-plate 34, and the flow cross-sectional area of ​​the first channel 31 of the Mth sub-plate 33 is S M , then: S1>S M >S N When there are multiple first plates 3, reducing the flow cross-sectional area of ​​the first channel 31 along the flow direction (ie, the first direction) of the refrigerant can ensure the flow rate of the refrigerant, thereby improving the distribution efficiency.

[0044] For example, when the number of first plates 3 is 3, along the first direction, the first first plate 3 is the first sub-plate 32, the second first plate 3 is the Mth sub-plate 33, and the third first plate 3 is the Nth sub-plate 34. At this time, the flow cross-sectional area of ​​the first channel 31 of each first plate 3 satisfies S1>S M >S N ; When the number of first plates 3 is greater than three, any Nth sub-plate 34 between the first sub-plate 32 and the Nth sub-plate 34 also satisfies the above relationship. On this basis, the flow cross-sectional area of ​​the N first plates 3 along the first direction can be gradually reduced. In addition, it should be noted that when the number of first plates 3 is two, the flow cross-sectional area of ​​the second first plate 3 can also be designed to be smaller than the flow cross-sectional area of ​​the first first plate 3. However, because the number of first plates 3 is small, the first plates 3 have little effect on the pressure of the refrigerant. Therefore, this article does not make specific limitations and descriptions on this situation.

[0045] In a specific embodiment, if the number of first boards 3 is N, N ≥ 3, along the first direction, the first first board 3 is defined as the first sub-board 32, the Nth first board 3 is defined as the Nth sub-board 34, there is an Mth sub-board 33 between the first sub-board 32 and the Nth sub-board 34, the shortest distance from the first sub-board 32 to the second board 5 is L3, and the shortest distance between the Mth sub-board 33 and the adjacent first board 3 is L M , the shortest distance between the Nth sub-plate 34 and the first end 11 is L N , then: L3≤L M ≤L N Similarly, along the flow direction of the refrigerant, increasing the distance between two adjacent first plates 3 can ensure the flow rate of the refrigerant, thereby improving the distribution efficiency.

[0046] In a specific embodiment, the flow cross-sectional area of ​​the first sub-pipe segment 12 is defined as S4, S4 and S N Between: 1 / 10≤ S N / S4<1 / 4. When the flow cross-sectional area of ​​the first channel 31 of the Nth sub-plate 34 is too small or too large, the refrigerant flow through the Nth sub-plate 34 will decrease or increase, affecting the overall distribution effect. Therefore, setting a suitable proportion of the flow cross-sectional area can make the refrigerant flow more smoothly in the entire first sub-pipe section 12, ensuring the uniformity of distribution. In this way, the flow of the refrigerant between two adjacent first channels 31 will not be hindered due to the small flow area of ​​the first channel 31, and the distribution of the refrigerant will not be affected due to the large flow area of ​​the first channel 31.

[0047] In addition, considering the actual effect, the recommended optimal range of the hydraulic diameter of the first channel is: 1mm~10mm. When the hydraulic diameter is less than 1mm, the channel flow resistance is too large. When it is greater than 10mm, it is difficult to produce an effective injection effect. Therefore, within this range, the two-phase refrigerant can be more effectively distributed evenly.

[0048] like Figure 2 As shown, in a specific embodiment, a surface extending along the second direction and passing through the first sub-tube segment 12 is defined as the first surface 6, the second direction is perpendicular to the first direction, and on the first surface 6, the projections of two adjacent first channels 31 are misaligned, that is, the projections of two adjacent first channels 31 do not overlap. It should be noted that "misalignment" and "non-overlapping" should be understood in a broad sense, that is, the projections of the two first channels 31 are not completely opposite. The two adjacent first channels 31 arranged in a staggered manner can alternately block the refrigerant and increase the time the refrigerant stays between the two adjacent first channels 31, thereby better achieving the effect of distribution while flowing and improving the uniformity of distribution.

[0049] like Figure 1-7 As shown, in a specific embodiment, the second tube 4 also includes a first connecting section 43, the first connecting section 43 is located in the tube cavity of the first tube 1, or the first connecting section 43 is at least partially located outside the first tube 1, and the first connecting section 43 connects the first opening 41 and the second opening 42. In this embodiment, the first connecting section 43 can be arranged in the tube cavity of the first tube 1 or outside the first tube 1, so as to better adapt to different installation environments and different installation requirements. Generally speaking, when the diameter of the first tube 1 can accommodate the second tube 4 and does not affect the flow of the refrigerant, the first connecting section 43 of the second tube 4 can be arranged in the tube cavity of the first tube 1, so that the pipe fittings around the first tube 1 can be reduced, and the whole structure is more concise after being installed in the heat exchanger for use. At the same time, the built-in first connecting section 43 can also effectively avoid damage caused by bumps and the like. When the first connecting section 43 is located in the tube cavity of the first tube 1, the first plate 3 is fixedly connected to the second tube 4, and / or the first plate 3 is fixedly connected to the tube wall of the first sub-tube section 12. This connection method can make the first plate 3 more stably and firmly installed in the first tube 1.

[0050] When the diameter of the first tube 1 is small, placing the first connecting section 43 of the second tube 4 inside the first tube 1 will result in a smaller remaining tube cavity space of the first tube 1, which may affect the flow and distribution of the refrigerant. The first connecting section 43 can be placed outside the tube. It should be noted that the first connecting section 43 can also be placed close to the outer tube wall of the first tube 1 to reduce the installation space.

[0051] like Figure 6 As shown, in a specific embodiment, the first connecting section 43 includes a second hole 431, and the second hole 431 is located on the tube wall of the first connecting section 43. The distance from the second hole 431 to the first interface 2 is smaller than the distance from the first opening 41 to the first interface 2. The second hole 431 on the first connecting section 43 allows a portion of the refrigerant to enter the first connecting section 43 from the second hole 431, and then enter the second sub-tube section 13. Since the distance from the second hole 431 to the first interface 2 is smaller than the distance from the first opening 41 to the first interface 2, when the gas and liquid of the two-phase refrigerant are separated, the liquid refrigerant sinks and the vapor refrigerant rises, so that the proportion of the vapor refrigerant in the refrigerant entering the second sub-tube section 13 from the first opening 41 is higher than the proportion of the liquid refrigerant, and the proportion of the liquid refrigerant in the refrigerant entering from the second hole 431 is higher than the proportion of the vapor refrigerant, so that the gas-liquid ratio of the refrigerant entering the second sub-tube section 13 can be balanced through the second hole 431, and the uniformity of gas-liquid distribution in the second sub-tube section 13 is improved. It should be noted that the number of the second holes 431 can be one or more, and the positions of the second holes 431 can be between the first opening 41 and the first interface 2 .

[0052] like Figure 7 As shown, in a specific embodiment, the manifold assembly further includes a third tube 7, the third tube 7 connects the first sub-tube segment 12 and the second sub-tube segment 13, the third tube 7 includes a third opening 44, the third opening 44 is located in the first sub-tube segment 12, and the distance from the third opening 44 to the first interface 2 is less than the distance from the first opening 41 to the first interface 2. The function of the third tube 7 is similar to that of the second hole 431 described above, and can improve the uniformity of gas-liquid distribution in the second sub-tube segment 13.

[0053] Since the distance from the third opening 44 to the first interface 2 is smaller than the distance from the first opening 41 to the first interface 2, the proportion of liquid refrigerant in the refrigerant entering from the third opening 44 is higher than the proportion of vapor refrigerant, so that the gas-liquid ratio in the refrigerant of the second sub-pipe section 13 can be balanced, and the uniformity of distribution can be improved. In addition, the third tube 7 can also be placed inside or outside the tube. The installation position of the second tube 4 has been described in detail above, so the installation of the third tube 7 will not be described in detail herein.

[0054] like Figure 8-9As shown, in a specific embodiment, the first tube 1 also includes a third sub-tube segment 14, the third sub-tube segment 14 is arranged along the length direction of the first tube 1, the third sub-tube segment 14 is connected to the first end 11, or the end of the second sub-tube segment 13 away from the first sub-tube segment 12, and the third sub-tube segment 14 is connected to the first sub-tube segment 12. The third sub-tube segment 14 can also be formed by dividing the first tube 1 by another second plate 5, and the flow of the refrigerant can be accelerated by the third sub-tube segment 14, thereby improving the distribution efficiency. In addition, in the case where the first tube 1 also includes the third sub-tube segment 14, a fourth opening 44 and a second connecting segment 45 can be provided on the second tube 4, the fourth opening 44 is located in the third sub-tube segment 14, and the second connecting segment 45 connects the fourth opening 44 and the connecting segment of the second tube 4.

[0055] like Figure 8 As shown, in a specific embodiment, if the length of the third sub-segment 14 is defined as L4, then L1 and L4 satisfy: 0.5 ≤ L1 / (L1 + L4) ≤ 0.9. Similarly, when the ratio of the length of the first sub-segment 12 to the length of the third sub-segment 14 is within this range, the refrigerant gas-liquid separation phenomenon caused by the first sub-segment 12 or the third sub-segment 14 being too long can be reduced, and the refrigerant distribution effect is better.

[0056] like Figure 4 As shown, in a specific embodiment, the manifold assembly further includes a guide plate 8, which is at least partially located in the first sub-cavity, and is configured to guide at least part of the fluid entering the first interface 2. The guide plate 8 can shield the refrigerant entering the first interface 2 to a certain extent, thereby preventing the refrigerant from being directly distributed after entering from the first interface 2, thereby improving the uniformity of distribution.

[0057] like Fig.10 As shown, the second aspect of the embodiment of the present application provides a heat exchanger, including: a first header 91 and a second header 92, the first header 91 and the second header 92 are arranged at intervals, the first header 91 includes at least one header assembly provided in the first aspect embodiment, the header assembly is arranged along the length direction of the first header 91; a plurality of heat exchange tubes 93, the plurality of heat exchange tubes 93 connect the first header 91 and the second header 92. The heat exchanger applies the header assembly of the first aspect embodiment to the heat exchanger. Since the header assembly of the first aspect embodiment has a better distribution effect, the refrigerant entering each heat exchange tube 93 from the first header 91 is more evenly distributed, so the heat exchange effect of each heat exchange tube 93 is better, thereby improving the heat exchange performance of the entire heat exchanger.

[0058] The heat exchange tube 93 in the embodiment of the present application may be a microchannel flat tube, or a heat exchange tube in other forms such as a round tube. In addition, the heat exchanger further includes fins 94, which are arranged at intervals on at least part of the heat exchange tubes 93 along the length direction of the first header 91; the fins 94 may be horizontally inserted fins 94 that are roughly parallel to the first header 91 or the second header 92, or may be corrugated fins 94 that are roughly parallel to the heat exchange tube 93 and located between at least part of two adjacent heat exchange tubes 93. In addition, when the heat exchanger in the embodiment of the present application works as an evaporator, in order to achieve a distribution effect, the first header 91 and the second header 92 are arranged roughly perpendicular to the ground, that is, the length direction of the first header 91 is parallel to the gravity direction. In order to achieve a better drainage effect, the fins 94 are horizontally inserted fins.

[0059] The above are only preferred embodiments of the present application and are not intended to limit the present application. For those skilled in the art, the present application may have various modifications and variations. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present application shall be included in the protection scope of the present application.

Claims

1. A header assembly, characterized in that: include: A first tube (1), the first tube (1) having a first end (11) in a length direction, the first tube (1) comprising a first sub-tube segment (12) and a second sub-tube segment (13), the first sub-tube segment (12) and the second sub-tube segment (13) being arranged along the length direction of the first tube (1), and the first end (11) being located at the first sub-tube segment (12); A first interface (2), the first interface (2) being in communication with the first sub-pipe section (12); at least one first plate (3), the first plate (3) being at least partially located in the tube cavity of the first sub-tube segment (12), the first plate (3) comprising a first channel (31), the first channel (31) being capable of communicating with the tube cavities of the first sub-tube segment (12) on both sides of the first plate (3); a second tube (4), the second tube (4) comprising a first opening (41) and a second opening (42), the first opening (41) being located between the first end (11) and the first plate (3), the second opening (42) being located in the second sub-tube segment (13), the second tube (4) being in communication with the first sub-tube segment (12) and the second sub-tube segment (13).

2. The header assembly according to claim 1, characterized in that The length of the first sub-segment (12) is defined as L1, and the length of the second sub-segment (13) is defined as L2. Then L1 and L2 satisfy: 0.5≤L1 / (L1+L2)≤0.

9.

3. The header assembly according to claim 1 or 2, characterized in that: The first channel (31) comprises a first hole (311), the first hole (311) is arranged on the first plate (3), the number of the first holes (311) is one or more, and / or the first channel (31) comprises a gap (312) located between the first plate (3) and the tube wall of the first sub-tube segment (12).

4. The header assembly according to claim 3, characterized in that The number of the first plates (3) is N, where N≥3. Along the first direction, the first first plate (3) is defined as a first sub-plate (32), the flow cross-sectional area of ​​the first channel (31) of the first sub-plate (32) is S1, the Nth first plate (3) is defined as an Nth sub-plate (34), and the flow cross-sectional area of ​​the first channel (31) of the Nth sub-plate (34) is S N , an Mth sub-plate (33) is provided between the first sub-plate (32) and the Nth sub-plate (34), and the flow cross-sectional area of ​​the first channel (31) of the Mth sub-plate (33) is S M , then: S1>S M >S N .

5. The header assembly according to claim 3, characterized in that The header assembly further comprises a second plate (5), wherein the second plate (5) is at least partially located in the tube cavity of the first tube (1), and the first sub-tube segment (12) and the second sub-tube segment (13) are respectively located on both sides of the second plate (5); The number of the first boards (3) is N, where N≥3. Along the first direction, the first first board (3) is defined as a first sub-board (32), the Nth first board (3) is defined as an Nth sub-board (34), an Mth sub-board (33) is located between the first sub-board (32) and the Nth sub-board (34), the shortest distance from the first sub-board (32) to the second board (5) is L3, and the shortest distance between the Mth sub-board (33) and an adjacent first board (3) is L M , the shortest distance between the Nth sub-plate (34) and the first end (11) is L N , then: L3≤L M ≤L N .

6. The header assembly according to claim 4, characterized in that The flow cross-sectional area of ​​the first sub-pipe section (12) is defined as S4, and the S4 is equal to the S N Between: 1 / 10≤ S N / S4<1 / 4.

7. The header assembly according to claim 4, characterized in that A surface extending along a second direction and passing through the first sub-tube segment (12) is defined as a first surface (6), the second direction is perpendicular to the first direction, and on the first surface (6), projections of two adjacent first channels (31) are misaligned.

8. The header assembly according to any one of claims 1-2 or 4-7, characterized in that: The second tube (4) further comprises a first connecting section (43), the first connecting section (43) being located in the tube cavity of the first tube (1), or the first connecting section (43) being at least partially located outside the first tube (1), the first connecting section (43) connecting the first opening (41) and the second opening (42).

9. The header assembly according to claim 8, characterized in that The first connecting section (43) is located in the tube cavity of the first tube (1), the first plate (3) is fixedly connected to the second tube (4), and / or the first plate (3) is fixedly connected to the tube wall of the first sub-tube section (12).

10. The header assembly according to claim 9, characterized in that The first connecting section (43) comprises a second hole (431), the second hole (431) being located on the tube wall of the first connecting section (43), and the distance between the second hole (431) and the first interface (2) being smaller than the distance between the first opening (41) and the first interface (2).

11. The header assembly according to claim 8, characterized in that The manifold assembly further comprises a third pipe (7), the third pipe (7) being connected to the first sub-pipe segment (12) and the second sub-pipe segment (13), the third pipe (7) comprising a third opening (71), the third opening (71) being located in the first sub-pipe segment (12), the distance between the third opening (71) and the first interface (2) being shorter than the distance between the first opening (41) and the first interface (2).

12. The header assembly according to any one of claims 4-7 or 9-11, characterized in that: The first tube (1) further comprises a third sub-tube segment (14), the third sub-tube segment (14) being arranged along the length direction of the first tube (1), the third sub-tube segment (14) being connected to the first end (11), or an end of the second sub-tube segment (13) away from the first sub-tube segment (12), and the third sub-tube segment (14) being in communication with the first sub-tube segment (12).

13. The header assembly according to claim 12, characterized in that The second tube (4) further comprises a fourth opening (44) and a second connecting section (45), the fourth opening (44) being located at the third sub-tube section (14), and the second connecting section (45) connecting the fourth opening (44) and the connecting section of the second tube (4).

14. The header assembly according to claim 12, characterized in that The length of the third sub-pipe segment (14) is defined as L4, then L1 and L4 satisfy: 0.5 ≤ L1 / (L1 + L4) ≤ 0.

9.

15. The header assembly according to any one of claims 1-2 or 4-7 or 13-14, characterized in that: The manifold assembly further comprises a guide plate (8), wherein the guide plate (8) is at least partially located in the first sub-cavity, and the guide plate (8) is configured to guide at least part of the fluid entering the first interface (2).

16. A heat exchanger, characterized in that: include: A first header (91) and a second header (92), wherein the first header (91) and the second header (92) are arranged at intervals, wherein the first header (91) comprises at least one header assembly according to any one of claims 1 to 15, and wherein the header assembly is arranged along the length direction of the first header (91); A plurality of heat exchange tubes (93), wherein the plurality of heat exchange tubes (93) are connected to the first header (91) and the second header (92).

17. The heat exchanger according to claim 16, characterized in that It also includes fins (94), wherein the fins (94) are arranged at intervals on at least a portion of the heat exchange tubes (91) along the length direction of the first header (91); When the heat exchanger is in operation, the length direction of the first header (91) is parallel to the direction of gravity.

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