Collecting pipe, heat exchanger and air conditioner

Abstract

The utility model discloses a collecting pipe, a heat exchanger and an air conditioner, the collecting pipe is provided with a pipe inlet, the side wall of the collecting pipe is provided with a plurality of branch outlets which are sequentially arranged at intervals in the direction far away from the pipe inlet, and the branch outlets which are farthest away from the pipe inlet are far-end outlets; a flow choking structure is arranged in the collecting pipe, a flow choking structure is arranged at at least one branch outlet except the far-end outlet, and the flow choking structures are used for reducing the overflowing area of the corresponding position of the collecting pipe so as to promote fluid in the collecting pipe to enter the branch outlets at the corresponding position. According to the collecting pipe disclosed by the utility model, the flow blocking structure is arranged at the at least one branch outlet, except the far-end outlet, of the collecting pipe, so that a large amount of fluid in the collecting pipe is prevented from flowing to the far-end outlet due to inertia, and the fluid in the collecting pipe is promoted to enter the branch outlets near the flow blocking structure; and the uniformity of fluid conveyed to each branch outlet by the collecting pipe is improved, so that the heat exchange capability of the heat exchanger using the collecting pipe is improved.

Description

Technical Field

[0001] This utility model relates to the field of air conditioning technology, and in particular to a manifold, heat exchanger and air conditioner. Background Technology

[0002] In related technologies, manifolds are often used as refrigerant distribution devices. However, in practical applications, due to the inertia of the refrigerant flowing in the pipes, excessive refrigerant is distributed to the far-end branches, while relatively less is distributed to the near-end branches. This uneven refrigerant distribution results in poor heat exchange capacity of the heat exchanger. Utility Model Content

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides a manifold that improves the uniformity of fluid distribution to each branch outlet and enhances the heat exchange capacity of the heat exchanger using the manifold.

[0004] This utility model also proposes a heat exchanger having the above-mentioned manifold.

[0005] This utility model also proposes an air conditioner having the above-mentioned heat exchanger.

[0006] According to a first aspect embodiment of the present invention, the manifold has an inlet and a plurality of branch outlets arranged sequentially at intervals along a direction away from the inlet on its sidewall, wherein the branch outlet furthest from the inlet is the distal outlet; the manifold is provided with a flow-blocking structure, and the flow-blocking structure is provided at at least one of the branch outlets other than the distal outlet, wherein the flow-blocking structure is used to reduce the flow area of ​​the manifold at the flow-blocking structure, so as to promote the fluid in the manifold to enter the branch outlet at the flow-blocking structure.

[0007] According to the present invention, the manifold has a flow-blocking structure at at least one branch outlet other than the far-end outlet. This structure prevents the fluid in the manifold from flowing to the far-end outlet in large quantities due to inertia, and promotes the fluid in the manifold to enter the branch outlet near the flow-blocking structure. Thus, based on the distribution characteristics of the refrigerant at each branch outlet, such as the influence of inertia, the flow-blocking structure can be set at the branch outlet with a smaller amount of refrigerant to improve the uniformity of fluid delivery from the manifold to each branch outlet, thereby improving the heat exchange capacity of the heat exchanger using the manifold.

[0008] In some embodiments, the flow obstruction structure includes an inner tube structure that connects the upstream and downstream sides of the inner tube structure. A buffer space is formed between the outer wall of the inner tube structure and the inner wall of the manifold. The buffer space is connected to the upstream side of the inner tube structure and isolated from the downstream side of the inner tube structure.

[0009] In some embodiments, the manifold includes a plurality of sub-pipes arranged sequentially along the axial direction of the manifold, at least two adjacent sub-pipes being an upstream pipe and a downstream pipe, the upstream end of the downstream pipe being tapered to form the inner pipe structure and extending into the downstream end of the upstream pipe, and the downstream end of the upstream pipe having the branch outlet formed thereon.

[0010] In some embodiments, the downstream pipe includes a downstream main pipe, a tapered pipe, and the inner pipe structure connected sequentially in a direction toward the upstream. The downstream main pipe and the inner pipe structure are both pipes of equal diameter, and the diameter of the inner pipe structure is smaller than that of the downstream main pipe. The diameter of the tapered pipe gradually decreases in the direction from the downstream main pipe to the inner pipe structure.

[0011] In some embodiments, the upstream pipe includes an upstream main pipe, a diverging pipe, and a sleeve structure connected sequentially in a downstream direction. The upstream main pipe and the sleeve structure are both pipes of equal diameter, and the diameter of the sleeve structure is larger than the diameter of the upstream main pipe. The diameter of the diverging pipe gradually increases from the upstream main pipe to the sleeve structure. The sleeve structure is fitted outside the downstream main pipe, and the inner pipe structure extends into the upstream main pipe. The inner diameter of the upstream main pipe constitutes the inner diameter of the upstream pipe, and the branch outlet is formed on the upstream main pipe.

[0012] In some embodiments, the ratio of the inner diameter of the inner tube structure to the inner diameter of the branch outlet is 0.7-1.2; and / or, the ratio of the distance between the inner tube structure and the upstream pipe to the inner diameter of the upstream pipe is 0.05-0.4.

[0013] In some embodiments, a locking structure is formed at the upstream end of the downstream pipe, and the locking structure is locked outside the port at the downstream end of the upstream pipe.

[0014] In some embodiments, at least one of the sub-pipes is a flow-blocking sleeve, wherein the branch outlet is provided on the side wall of the downstream end of the flow-blocking sleeve and the upstream end is formed as the inner pipe structure.

[0015] In some embodiments, the flow-blocking structure includes one inner tube structure, and the inner tube structure is centrally located relative to the axis of the manifold; or the flow-blocking structure includes a plurality of inner tube structures arranged in parallel and spaced apart.

[0016] In some embodiments, the branch outlet is located upstream of the inlet end of the inner tube structure; or, the branch outlet is radially opposite to the buffer space.

[0017] In some embodiments, the flow-blocking structure is located downstream of the corresponding branch outlet to facilitate the flow of fluid in the manifold into the branch outlet upstream of the flow-blocking structure.

[0018] In some embodiments, the flow-blocking structure includes at least one of an inner tube structure, an orifice plate structure, a baffle structure, and a screen structure.

[0019] In some embodiments, the axial distance between the flow-blocking structure and its upstream branch outlet is less than the inner diameter of the corresponding branch outlet, or the axial distance between the flow-blocking structure and its upstream branch outlet is 0-10 mm.

[0020] In some embodiments, the flow-blocking structure helps to define a flow passage to connect the upstream and downstream sides of the flow-blocking structure, the flow passage and its upstream branch outlet being radially spaced along the manifold.

[0021] In some embodiments, the flow passage is centered relative to the axis of the manifold, or it is offset relative to the axis of the manifold toward the side of the pipe wall away from the branch outlet.

[0022] In some embodiments, in at least two adjacent branch outlets, the inner diameter of the upstream branch outlet is larger than the inner diameter of the downstream branch outlet.

[0023] In some embodiments, the manifold is vertically arranged, the inlet is located at the lower part of the manifold, and the plurality of branch outlets are arranged sequentially upward relative to the inlet.

[0024] A heat exchanger according to a second aspect of the present invention includes a heat exchanger body, an inlet pipe, and an outlet pipe. The heat exchanger body has multiple parallel branches. The inlet pipe is a manifold according to any embodiment of the first aspect of the present invention. The multiple branch outlets are connected to the inlets of the multiple parallel branches in a one-to-one correspondence. The outlet pipe is connected to the outlets of the multiple parallel branches in a one-to-one correspondence.

[0025] According to the embodiments of the present invention, the heat exchanger improves its heat exchange efficiency by providing the manifold described in the first aspect.

[0026] An air conditioner according to a third aspect of the present invention includes a heat exchanger according to a second aspect of the present invention.

[0027] According to the embodiments of the present invention, by setting the heat exchanger described in the second aspect, the cooling and heating efficiency of the air conditioner is improved, thereby enhancing the overall operating efficiency of the air conditioner and the user experience.

[0028] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0029] Figure 1 This is a schematic diagram of a manifold according to an embodiment of the present invention;

[0030] Figure 2 yes Figure 1 A partial schematic diagram of the manifold shown;

[0031] Figure 3 yes Figure 1 A partial schematic diagram of the manifold shown;

[0032] Figure 4 yes Figure 3 An exploded schematic diagram of the manifold shown;

[0033] Figure 5 This is a partial schematic diagram of a manifold according to an embodiment of the present invention;

[0034] Figure 6 This is a partial schematic diagram of a manifold according to another embodiment of the present invention;

[0035] Figure 7 This is a partial schematic diagram of a manifold according to another embodiment of the present invention;

[0036] Figure 8 This is a partial schematic diagram of a manifold according to another embodiment of the present invention;

[0037] Figure 9 This is a partial schematic diagram of a manifold according to another embodiment of the present invention;

[0038] Figure 10 This is a schematic diagram of a flow-blocking structure, which is a screen structure according to an embodiment of the present invention;

[0039] Figure 11 This is a partial schematic diagram of a manifold according to another embodiment of the present invention;

[0040] Figure 12 This is a schematic diagram of a manifold according to another embodiment of the present invention;

[0041] Figure 13 This is a schematic diagram of a heat exchanger according to an embodiment of the present invention;

[0042] Figure 14 This is a schematic diagram of an air conditioner according to an embodiment of the present invention;

[0043] Figure 15 This is a graph showing the experimental comparison data between Example 1 and Comparative Example 1.

[0044] Figure label:

[0045] Air conditioner 10000;

[0046] Heat exchanger 1000;

[0047] Heat exchanger body 1000c; parallel branch 1000c1; inlet pipe 1000a; outlet pipe 1000b;

[0048] 100mm manifold;

[0049] Sub-tube 4; choke sleeve 4x;

[0050] Upstream pipe 41; Upstream main pipe 411; Diverging pipe 412; Casing structure 413;

[0051] Downstream pipe 42; Downstream main pipe 421; Tapered pipe 422; Positioning structure 424;

[0052] Pipe inlet 1; Branch outlet 2; Remote outlet 2a;

[0053] Flow obstruction structure 3; Inner tube structure 3a; Orifice plate structure 3b; Baffle structure 3c; Screen structure 3d;

[0054] Overcurrent channel 31; cache space 3a1. Detailed Implementation

[0055] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain this utility model, and should not be construed as limiting this utility model.

[0056] The following disclosure provides numerous different embodiments or examples for implementing various structures of the present invention. To simplify the disclosure, specific examples of components and arrangements are described below. These are merely examples and are not intended to limit the scope of the invention. Furthermore, reference numerals and / or letters may be repeated in different examples. Such repetition is for simplification and clarity and does not in itself indicate a relationship between the various embodiments and / or arrangements discussed. In addition, examples of various specific processes and materials are provided in this invention; however, those skilled in the art will recognize the applicability of other processes and / or the use of other materials.

[0057] Hereinafter, with reference to the accompanying drawings, a manifold 100 according to a first aspect embodiment of the present invention will be described.

[0058] See Figure 1 The manifold 100 has a pipe inlet 1 and a plurality of branch outlets 2 arranged sequentially at intervals along a direction away from the pipe inlet 1 on its side wall. The branch outlet 2 that is farthest from the pipe inlet 1 is the distal outlet 2a. The manifold 100 is provided with a flow-blocking structure 3. At least one branch outlet 2 other than the distal outlet 2a is provided with a flow-blocking structure 3. The flow-blocking structure 3 is used to reduce the flow area of ​​the manifold 100 at the flow-blocking structure 3 so as to promote the fluid in the manifold 100 to enter the branch outlet 2 at the flow-blocking structure 3.

[0059] like Figure 1 As shown, multiple branch outlets 2 are arranged sequentially at intervals along the axial direction of the manifold 100. The "axial direction of the manifold 100" refers to the "flow direction of the manifold 100," meaning the direction of fluid (such as refrigerant) flow within the manifold 100. The fluid enters the manifold 100 from the pipe inlet 1 and flows towards the downstream end of the manifold 100. It is worth noting that the manifold 100 can be a straight pipe, but is not limited to a straight pipe; for example, it can also be a bent pipe, etc. Therefore, the axial direction of the manifold 100 is not limited to a straight line.

[0060] In related technologies, manifolds are often used as refrigerant distribution devices. However, in practical applications, due to the inertia of the refrigerant flowing in the pipes, excessive refrigerant is distributed to the far-end branches, while relatively less is distributed to the near-end branches. This uneven refrigerant distribution results in poor heat exchange performance of heat exchangers using such manifolds, leading to poor energy efficiency in air conditioners during both cooling and heating processes.

[0061] However, in the technical solution of this utility model, the refrigerant distribution in the manifold 100 is adjusted by providing a flow-blocking structure 3 inside the manifold 100. Specifically, a flow-blocking structure 3 is provided at at least one branch outlet 2 of the manifold 100 other than the far-end outlet 2a, so as to prevent the fluid in the manifold 100 from flowing too much to the far-end outlet 2a of the branch outlet 2 due to inertia. This can promote the fluid in the manifold 100 to enter the branch outlet 2 near the flow-blocking structure 3. In this way, according to the distribution characteristics of the refrigerant in each branch outlet 2, such as the influence of inertia, a flow-blocking structure is set at the branch outlet 2 with a smaller amount of refrigerant, so as to improve the uniformity of refrigerant distribution in each branch outlet 2.

[0062] This improves the uniformity of fluid distribution within the manifold 100. When each branch outlet 2, except for the far-end outlet 2a, is equipped with a flow-blocking structure 3, the refrigerant in each branch outlet 2 of the heat exchanger 1000 becomes relatively uniform. This improves the problem of uneven heat exchange in the heat exchanger 1000 caused by excessive refrigerant in the branch corresponding to the far-end outlet 2a and insufficient refrigerant in the branch corresponding to the near-end outlet. Consequently, it enhances the heat exchange capacity of the heat exchanger 1000 using the manifold 100 and improves the cooling and heating efficiency of the air conditioner 10000 using the heat exchanger 1000, thereby improving the overall operating efficiency of the air conditioner and the user experience.

[0063] It is worth noting that "at least one branch outlet 2 other than the far outlet 2a is provided with a flow-blocking structure 3" should be understood as: at least one branch outlet 2 other than the far outlet 2a must be provided with a flow-blocking structure 3, but for the far outlet 2a, the flow-blocking structure 3 can be set at the far outlet 2a as needed, or the flow-blocking structure 3 can be not set, that is, it is optional whether the flow-blocking structure 3 is set at the far outlet 2a.

[0064] In embodiments of this utility model, the spatial orientation and shape of the manifold 100 are not limited, and the specific parameters of the manifold 100 should match those of the heat exchanger 1000. The position of the pipe inlet 1 is not limited. For example, one end of the manifold 100 is the pipe inlet 1, and the other end is sealed with a plug or sealing plate. The two ends should be set according to the flow direction of the refrigerant.

[0065] In embodiments of this utility model, the number of branch outlets 2 of the manifold 100 is not limited. For example, there can be 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, etc. The spacing of the multiple branch outlets 2 is not limited. For example, the multiple branch outlets 2 can be set at equal intervals or at varying intervals. For example, the specific spacing can be matched with the spacing of the parallel branches 1000c1 of the heat exchanger 1000.

[0066] In the embodiments of this utility model, a flow-blocking structure 3 is provided at each branch outlet 2. The form of the flow-blocking structure 3 is not limited. The form of the flow-blocking structure 3 should be able to reduce the flow area of ​​the corresponding position of the manifold 100 (that is, the position where the flow-blocking structure 3 is provided in the manifold 100). For example, when the flow-blocking structure 3 includes flow-blocking units with small axial dimensions (such as the orifice plate structure 3b, baffle structure 3c, screen structure 3d, etc. mentioned later), it can include multiple flow-blocking units arranged in series. For another example, when the flow-blocking structure 3 includes flow-blocking units with large axial dimensions (such as the inner tube structure 3a mentioned later), it can include only one flow-blocking unit. Here, axial direction refers to the flow direction of the manifold 100, and series means arranged sequentially along the axial direction. It is worth noting that the flow obstruction structure 3 is set at the branch outlet 2, but the specific positional relationship between the flow obstruction structure 3 and the branch outlet 2 is not limited. For example, the flow obstruction structure 3 can be located downstream of the branch outlet 2. If the flow obstruction structure 3 has a certain length in the axial direction of the manifold 100, the branch outlet 2 can also be set to correspond to the flow obstruction structure 3. That is, at this time, a part of the flow obstruction structure 3 can be located upstream of the branch outlet 2.

[0067] In the embodiments of this utility model, "upstream" refers to the position through which the refrigerant first flows in the direction of flow, and "downstream" refers to the position through which the refrigerant flows in the direction of flow. Upstream and downstream are relative concepts, rather than specific locations.

[0068] In the embodiments of this utility model, the fluid in the manifold 100 is a refrigerant (such as a refrigerant or a coolant). The phase of the refrigerant in the manifold 100 is not limited; it may be a liquid phase, a gas phase, or a gas-liquid mixture.

[0069] For example, such as Figure 1 As shown, the manifold 100 is a generally straight cylindrical pipe arranged vertically. The manifold 100 has an inlet 1 at its lower part in the direction of gravity, with the upper end sealed. There are three branch outlets 2, spaced apart vertically. The refrigerant flows through the manifold 100 from bottom to top, with the uppermost branch outlet 2 being the last outlet 2 the refrigerant reaches (the far end outlet 2a). The flow-blocking structure 3 is located downstream of the two branch outlets 2 other than the far end outlet 2a. Therefore, the flow area of ​​the manifold 100 at the flow-blocking structure 3 is reduced, and the refrigerant flow is obstructed near the flow-blocking structure 3. This promotes the entry of the obstructed refrigerant into the branch outlets 2 upstream of the flow-blocking structure 3, reducing the amount of refrigerant entering the far end outlet 2a. At this point, the refrigerant flow rate at each branch outlet 2 is relatively uniform, thereby improving the cooling and heating efficiency of the air conditioner 10000, enhancing the overall operating efficiency of the air conditioner, and improving the user experience.

[0070] In some embodiments, see Figure 2The flow obstruction structure 3 includes an inner tube structure 3a, which connects the upstream and downstream sides of the inner tube structure 3a. A buffer space 3a1 is formed between the outer wall of the inner tube structure 3a and the inner wall of the collector pipe 100. The buffer space 3a1 is connected to the upstream side of the inner tube structure 3a and isolated from the downstream side of the inner tube structure 3a.

[0071] The inner tube structure 3a extends along the flow direction of the manifold 100. The phrase "the inner tube structure 3a extends along the flow direction of the manifold 100" can be interpreted broadly, meaning that the axis of the inner tube structure 3a and the manifold 100 can be parallel or not. The inner cavity of the inner tube structure 3a is the flow channel 31. As long as a portion of the refrigerant upstream of the inner tube structure 3a can enter the flow channel 31 and then enter the downstream of the inner tube structure 3a, it is acceptable.

[0072] In the above technical solution, the flow obstruction structure 3 is an inner pipe structure 3a. The area of ​​the flow passage 31 of the inner pipe structure 3a is smaller than the flow area of ​​the manifold 100. Therefore, when the refrigerant flows through the inner pipe structure 3a, a portion of the refrigerant flows into the buffer space 3a1. The buffer space 3a1 is isolated from the downstream side of the inner pipe structure 3a. The refrigerant forms a reflected backflow in the buffer space 3a1. The reflected backflow disturbs the refrigerant flowing into the flow passage 31, reducing the refrigerant flow into the inner pipe structure 3a. This forces more refrigerant to flow to the branch outlet 2 near the buffer space 3a1, and allows the gaseous and liquid refrigerants to mix fully, reducing the influence of refrigerant inertial dynamic pressure. This is beneficial to improving the uniformity of refrigerant distribution in each branch pipe and improving the cooling and heating efficiency of the air conditioner 10000.

[0073] In the embodiments of this utility model, the cross-sectional shape of the inner tube structure 3a is not limited. For example, the cross-sectional shape of the inner tube structure 3a can be circular or polygonal. In addition, the cross-sectional area of ​​the inner tube structure 3a can be fixed or variable.

[0074] In embodiments of this invention, "connection" and "isolation" are relative to fluid flow. Connection means that fluid can flow from one place to another; isolation means that there is no fluid channel between the two places.

[0075] In some embodiments, see Figure 3 The manifold 100 includes a plurality of sub-pipes 4 arranged sequentially along the axial direction of the manifold 100 (i.e. the flow direction of the manifold 100). At least two adjacent sub-pipes 4 are an upstream pipe 41 and a downstream pipe 42, respectively. The upstream end of the downstream pipe 42 is narrowed to form an inner pipe structure 3a and extends into the downstream end of the upstream pipe 41. The downstream end of the upstream pipe 41 has a branch outlet 2.

[0076] The phrase "the end of the downstream pipe 42 is reduced in diameter to form the inner pipe structure 3a" means that the diameter of the inner pipe structure 3a is smaller than the diameter of the main body section of the downstream pipe 42 (e.g., the downstream main pipe 421 shown in the figure), thereby facilitating the processing of both the downstream pipe 42 and the inner pipe structure 3a. The axis of the inner pipe structure 3a may coincide with (i.e., be centered) or may not coincide with (i.e., be eccentric) the axis of the main body section of the downstream pipe 42 (e.g., the downstream main pipe 421 shown in the figure). However, the inner pipe structure 3a is not limited to being processed by a pipe reduction process; it can be obtained by processing the downstream pipe 42 in other ways. For example, the downstream pipe 42 can be a single-piece molded part or a single-piece part consisting of multiple parts fixedly connected together.

[0077] In the above technical solution, the manifold 100 is composed of multiple sub-pipes 4, making the manifold 100 easy to expand or shrink. The number of sub-pipes 4 can be increased or decreased according to actual needs, flexibly adapting to different models of heat exchangers 1000. Furthermore, the sub-pipes 4 can be standardized, enabling mass production and improving production efficiency. The upstream end of the downstream pipe 42 is formed as an inner pipe structure 3a and extends into the downstream end of the upstream pipe 41. This nested connection method makes the flow-blocking structure 3 easy to process and fix in the required position, facilitating efficient mass production.

[0078] In the embodiments of this utility model, upstream pipe 41 refers to the pipe through which the refrigerant flows first in the flow direction, and downstream pipe 42 refers to the pipe through which the refrigerant flows later in the flow direction. Upstream pipe 41 and downstream pipe 42 are relative concepts and do not refer to a specific sub-pipe 4. Therefore, for some sub-pipes 4, they can serve as both upstream pipe 41 and downstream pipe 42.

[0079] In some embodiments, see Figure 4 The downstream pipe 42 includes a downstream main pipe 421, a tapered pipe 422, and an inner pipe structure 3a connected sequentially in the upstream direction. Both the downstream main pipe 421 and the inner pipe structure 3a are pipes of equal diameter, with the diameter of the inner pipe structure 3a being smaller than that of the downstream main pipe 421. The tapered pipe 422 connects the downstream main pipe 421 and the inner pipe structure 3a, and the diameter of the tapered pipe 422 gradually decreases from the downstream main pipe 421 to the inner pipe structure 3a. It is worth noting that the downstream pipe 42 is mainly composed of the downstream main pipe 421, and the length of the downstream main pipe 421 accounts for the majority of the length of the downstream pipe 42. Therefore, the inner diameter of the downstream main pipe 421 constitutes the inner diameter of the downstream pipe 42.

[0080] In the above technical solution, the refrigerant entering the inner pipe structure 3a flows sequentially through the inner pipe structure 3a, the converging pipe 422, and the downstream main pipe 421. The diameter of the inner pipe structure 3a is smaller than the diameter of the downstream main pipe 421. The converging pipe 422 connects the inner pipe structure 3a and the downstream main pipe 421, allowing the fluid to gradually adapt to the change in pipe diameter as it flows from the inner pipe structure 3a into the downstream main pipe 421, reducing fluid impact and eddy formation, thereby optimizing fluid dynamics performance and reducing energy loss. Furthermore, the outer wall of the converging pipe 422 makes it easier for the refrigerant to form a reflective backflow within the buffer space 3a1, increasing the disturbance effect on the refrigerant and thus reducing the refrigerant flow rate entering the inner pipe structure 3a, forcing more refrigerant to flow towards the branch outlet 2 near the buffer space 3a1.

[0081] From a manufacturing perspective, exemplarily, the inner pipe structure 3a and the tapered pipe 422 can be formed by reducing the diameter of the downstream main pipe 421 through a pipe-shrinking process, essentially becoming an integrated downstream pipe 42, thereby enhancing the overall structural strength of the downstream pipe 42. Furthermore, the tapered pipe 422, through its smooth diameter change, reduces stress concentration points, improving the pipe's pressure resistance and service life.

[0082] In some embodiments, see Figure 4 The upstream pipe 41 includes an upstream main pipe 411, a diverging pipe 412, and a sleeve structure 413 connected sequentially in the downstream direction. Both the upstream main pipe 411 and the sleeve structure 413 are pipes of equal diameter, with the sleeve structure 413 having a larger diameter than the upstream main pipe 411. The diverging pipe 412 connects the upstream main pipe 411 and the sleeve structure 413, and its diameter gradually increases from the upstream main pipe 411 to the sleeve structure 413. The sleeve structure 413 is fitted over the downstream main pipe 421, and the inner pipe structure 3a extends into the upstream main pipe 411. A branch outlet 2 is formed on the upstream main pipe 411. It is worth noting that the upstream pipe 41 is mainly composed of the upstream main pipe 411, whose length accounts for the majority of the length of the upstream pipe 411; therefore, the inner diameter of the upstream main pipe 411 constitutes the inner diameter of the upstream pipe 41.

[0083] In the above technical solution, the sleeve structure 413 is fitted over the downstream main pipe 421, enhancing the connection strength between the upstream pipe 41 and the downstream pipe 42. Especially in high-pressure or high-temperature applications of the heat exchanger 1000, it can more effectively resist the impact of external pressure and internal fluid. Setting both the sleeve structure 413 and the downstream main pipe 421 as pipes of equal diameter increases the contact area between them, providing reliable support, enhancing the overall strength of the manifold 100, and improving the durability of the manifold 100 under high pressure or harsh environments.

[0084] From a manufacturing perspective, exemplarily, the sleeve structure 413 and the expanding pipe 412 can be formed by expanding the diameter of the upstream main pipe 411 through a pipe expansion process, essentially creating a single integrated upstream pipe 41, thereby enhancing the overall structural strength of the upstream pipe 41. Furthermore, the expanding pipe 412, through its smooth diameter change, reduces stress concentration points, improving the pipe's pressure resistance and service life. However, the sleeve structure 413 and the expanding pipe 412 are not limited to being manufactured through a pipe expansion process; they can be obtained by manufacturing the upstream pipe 41 in other ways. Exemplarily, the upstream pipe 41 can be a single-piece molded component or a single-piece component consisting of multiple parts fixedly connected together.

[0085] In some embodiments, see Figure 5 The ratio of the inner diameter D1 of the inner pipe structure 3a to the inner diameter D2 of the adjacent branch outlet 2 is 0.7-1.2, etc. Therefore, by adjusting and controlling the ratio of the inner diameter D1 of the inner pipe structure 3a to the inner diameter D2 of the branch outlet 2, the flow distribution into the inner pipe structure 3a and the branch outlet 2 is adjusted, reducing the refrigerant flow into the inner pipe structure 3a, thereby improving the cooling and heating efficiency of the air conditioner 10000, enhancing the overall operating efficiency of the air conditioner, and improving the user experience.

[0086] In embodiments of this utility model, the cross-sectional shape of the inner tube structure 3a is not limited. For example, the cross-sectional shape of the inner tube structure 3a can be circular or polygonal. Furthermore, the cross-sectional area of ​​the inner tube structure 3a can be fixed or variable. For example, the inner tube structure 3a is a tube of constant diameter, meaning its cross-sectional area is equal everywhere, which facilitates the processing of the inner tube structure 3a and the stable flow of the refrigerant within it. For example, when the inner tube structure 3a is not a tube of constant diameter, the inner diameter at any position of the inner tube structure 3a satisfies the ratio of its inner diameter to the inner diameter D2 of the corresponding branch outlet 2 being 0.7-1.2.

[0087] In some embodiments, see Figure 5 The ratio of the distance D3 between the inner pipe structure 3a and the manifold 100 to the inner diameter D4 of the manifold 100 is 0.05-0.4, for example, 0.05, 0.1, 0.2, 0.3, 0.4, etc. That is, adjusting the ratio of the area where the refrigerant flow is obstructed to the flow area of ​​the refrigerant in the manifold 100 to adjust the intensity of the backflow reflection. The backflow reflection will obstruct or disturb the refrigerant flowing to the flow channel 31, thereby indirectly adjusting the flow distribution into the inner pipe structure 3a and the branch outlet 2, and reducing the refrigerant flow into the inner pipe structure 3a.

[0088] In some embodiments, see Figure 5The ratio of the inner diameter D1 of the inner tube structure 3a to the inner diameter D2 of the branch outlet 2 is 0.7-1.2, and the ratio of the distance D3 between the inner tube structure 3a and the manifold 100 to the inner diameter D4 of the manifold 100 is 0.05-0.4.

[0089] Therefore, by adjusting the flow distribution into the inner pipe structure 3a and the branch outlet 2 through direct and indirect adjustment methods, the refrigerant in each parallel branch 1000c1 of the heat exchanger 1000 is relatively uniform, which improves the problem of uneven heat exchange caused by too much refrigerant in the branch corresponding to the far outlet 2a and too little refrigerant in the branch corresponding to the near outlet. This improves the cooling and heating efficiency of the air conditioner 10000, enhances the overall operating efficiency of the air conditioner and the user experience.

[0090] In some embodiments, see Figure 4 A locking structure 424 is formed at the upstream end of the downstream pipe 42, and the locking structure 424 is locked outside the port at the downstream end of the upstream pipe 41.

[0091] In the above technical solution, the locking structure 424 effectively prevents relative movement of the upstream and downstream pipes 42 in the axial direction (i.e., the direction of fluid flow). The length of the sleeve connection between the downstream pipe 42 and the upstream pipe 41 can be limited by the setting position of the locking structure 424, so that the relative position of the flow-blocking structure 3 and the nearby branch outlet 2 is accurate, improving the effectiveness of the flow-blocking structure 3 in promoting fluid to enter the branch outlet 2. In addition, in some embodiments, the above-mentioned locking can also be used to form a pre-position, and the two sub-pipes 4 can be reliably connected together by welding or other methods.

[0092] In the embodiments of this utility model, the form of the card slot structure 424 is not limited. For example, the card slot structure 424 can be a buckle, a protrusion, or other forms, and the specific form needs to be determined according to the actual application scenario.

[0093] In some embodiments, see Figure 1 At least one sub-pipe 4 is a flow-blocking sleeve 4x, with a branch outlet 2 on the side wall of the downstream end of the flow-blocking sleeve 4x and an inner pipe structure 3a formed at the upstream end. Thus, the flow-blocking sleeve 4x can serve as both an upstream pipe 41 and a downstream pipe 42, and can be mass-produced as a connecting fitting to reduce production costs.

[0094] For example, at least two sub-pipes 4 are flow-blocking sleeves 4x, serving as the upstream pipe 41 and the downstream pipe 42, respectively. Therefore, during installation and maintenance, the upstream pipe 41 and the downstream pipe 42 differ only in the order of refrigerant flow, allowing for interchangeable use. This increases the ease of installation and maintenance of the manifold 100, reducing the operational difficulty and time cost of installation. By reducing the number of different types of parts, inventory management is simplified, inventory costs are reduced, and confusion and errors caused by a large variety of parts are minimized.

[0095] In the embodiments of this utility model, when there are multiple flow-blocking sleeves 4x, the structures of the multiple flow-blocking sleeves 4x can be the same, but the lengths can be different. In this way, flow-blocking sleeves 4x of different lengths can be selected according to the parameters of the heat exchanger 1000 to form a flow-collecting pipe 100.

[0096] In some embodiments, see Figure 5 The flow-blocking structure 3 includes an inner tube structure 3a, which is centrally located relative to the axis of the manifold 100. This centrally located inner tube structure 3a helps reduce eddy currents within the manifold 100, lowering energy loss and improving fluid transport efficiency. The single, centrally located inner tube structure 3a is easy to manufacture and install, enhancing the convenience of manufacturing and installation.

[0097] In some embodiments, see Figure 6 The flow-blocking structure 3 includes multiple inner tube structures 3a arranged in parallel and spaced apart. Therefore, by adjusting the number and spacing of the inner tube structures 3a, the distribution and direction of the fluid can be controlled more precisely, meeting the needs of complex fluid systems and improving the system's adaptability and flexibility.

[0098] In some embodiments, see Figure 5 The ratio of the inner diameter D1 of the inner pipe structure 3a to the inner diameter D2 of the adjacent branch outlet 2 is 0.7-1.2, etc. Therefore, by adjusting and controlling the ratio of the inner diameter D1 of the inner pipe structure 3a to the inner diameter D2 of the branch outlet 2, the flow distribution into the inner pipe structure 3a and the branch outlet 2 is adjusted, reducing the refrigerant flow into the inner pipe structure 3a, thereby improving the cooling and heating efficiency of the air conditioner 10000, enhancing the overall operating efficiency of the air conditioner, and improving the user experience.

[0099] In embodiments of this utility model, the cross-sectional shape of the inner tube structure 3a is not limited. For example, the cross-sectional shape of the inner tube structure 3a can be circular or polygonal. Furthermore, the cross-sectional area of ​​the inner tube structure 3a can be fixed or variable. For example, the inner tube structure 3a is a tube of constant diameter, meaning its cross-sectional area is equal everywhere, which facilitates the processing of the inner tube structure 3a and the stable flow of the refrigerant within it. For example, when the inner tube structure 3a is not a tube of constant diameter, the inner diameter at any position of the inner tube structure 3a satisfies the ratio of its inner diameter to the inner diameter D2 of the corresponding branch outlet 2 being 0.7-1.2.

[0100] In some embodiments, see Figure 5 The ratio of the distance D3 between the inner pipe structure 3a and the upstream pipe 41 to the inner diameter D4 of the upstream pipe 41 is 0.05-0.4, for example, 0.05, 0.1, 0.2, 0.3, 0.4, etc., which adjusts the ratio of the area where the refrigerant flow is obstructed to the flow area of ​​the refrigerant in the manifold 100, thereby adjusting the intensity of the backflow reflection. The backflow reflection will obstruct or disturb the refrigerant flowing to the flow channel 31, thereby indirectly adjusting the flow distribution into the inner pipe structure 3a and the branch outlet 2, and reducing the refrigerant flow into the inner pipe structure 3a.

[0101] In some embodiments, see Figure 5 The ratio of the inner diameter D1 of the inner tube structure 3a to the inner diameter D2 of the adjacent branch outlet 2 is 0.7-1.2, and the ratio of the distance D3 between the inner tube structure 3a and the upstream pipe 41 to the inner diameter D4 of the upstream pipe 41 is 0.05-0.4.

[0102] Therefore, by adjusting the flow distribution into the inner pipe structure 3a and the branch outlet 2 through direct and indirect adjustment methods, the refrigerant in each parallel branch 1000c1 of the heat exchanger 1000 is relatively uniform, which improves the problem of uneven heat exchange caused by too much refrigerant in the branch corresponding to the far outlet 2a and too little refrigerant in the branch corresponding to the near outlet. This improves the cooling and heating efficiency of the air conditioner 10000, enhances the overall operating efficiency of the air conditioner and the user experience.

[0103] In some embodiments, see Figure 6 Branch outlet 2 is located upstream of the inlet end of the inner tube structure 3a. This facilitates the flow of reflected backflowing fluid into the branch outlet 2 upstream of the inner tube structure 3a, thereby increasing the flow distribution ratio of branch outlet 2.

[0104] In some embodiments, see Figure 7 Branch outlet 2 and buffer space 3a1 are arranged radially opposite each other. As a result, the fluid in buffer space 3a1 can effectively enter branch outlet 2, thereby improving the flow distribution ratio of branch outlet 2.

[0105] In some embodiments, see Figures 8-10 The flow-blocking structure 3 is located downstream of the corresponding branch outlet 2 to facilitate the flow of fluid in the manifold 100 into the branch outlet 2 upstream of the flow-blocking structure 3. Thus, by placing the flow-blocking structure 3 downstream of the branch outlet 2, the fluid obstructed by the flow-blocking structure 3 can enter the branch outlet 2 upstream of the flow-blocking structure 3, which can more effectively control the flow rate, velocity, and pressure of the fluid flowing out of the branch outlet 2.

[0106] When the flow obstruction structure 3 is located downstream of the corresponding branch outlet 2, the form of the flow obstruction structure 3 is not limited. For example, in some embodiments, the flow obstruction structure 3 may include at least one of the following: inner tube structure 3a, orifice plate structure 3b, baffle structure 3c, and screen structure 3d. Therefore, appropriate forms and parameters of the flow obstruction structure 3 can be flexibly selected according to different fluid characteristics, pipeline layouts, and process requirements. This ensures uniform fluid distribution while optimizing the resistance characteristics of the fluid passing through the flow obstruction structure 3, reducing energy consumption, and improving the adaptability and flexibility of the system.

[0107] In some embodiments of this utility model, different flow-blocking structures 3 can be selected at different branch outlets 2, or the same flow-blocking structure 3 can be selected at different branch outlets 2, thereby flexibly adapting to different fluid characteristics, pipeline layouts and process requirements.

[0108] In some embodiments, see Figure 5 or Figure 8 The axial distance A between the flow-blocking structure 3 and its upstream branch outlet 2 is less than the inner diameter D2 of the corresponding branch outlet 2; or, the axial distance A between the flow-blocking structure 3 and its upstream branch outlet 2 is 0-10 mm, such as 0 mm, 2 mm, 4 mm, 6 mm, 8 mm, 10 mm, etc. Therefore, the flow-blocking structure 3 is closer to its upstream branch outlet 2, and the flow rate entering the branch outlet 2 of the manifold 100 will be more effectively affected by the flow-blocking structure 3. That is, the fluid can respond to the regulating effect of the flow-blocking structure 3 more quickly, thereby improving the response speed and dynamic performance of the entire fluid system, which is beneficial to maintaining the uniformity of fluid distribution.

[0109] The axial distance between the flow-blocking structure 3 and its upstream branch outlet 2 refers to the minimum distance between the flow-blocking structure 3 and its upstream branch outlet 2 along the fluid flow direction of the manifold 100 (i.e., the axial direction of the manifold 100). For example, when the flow-blocking structure 3 is located above the branch outlet 2, the distance between the lower edge of the flow-blocking structure 3 and the upper edge of the branch outlet 2.

[0110] In some embodiments, see Figure 11The flow obstruction structure 3 participates in defining the flow passage 31 to connect the upstream and downstream of the flow obstruction structure 3. The flow passage 31 and its upstream branch outlet 2 are arranged radially at intervals along the manifold 100.

[0111] In the above technical solution, by setting the flow passage 31 and its upstream branch outlet 2 at a radial distance along the manifold 100, the possibility of fluid passing directly through the flow passage 31 without entering the branch outlet 2 is reduced. This allows the flow obstruction structure 3 to more effectively promote the entry of the obstructed fluid into the branch outlet 2, making the flow distribution between the flow passage 31 and the branch outlet 2 easier to control by adjusting the parameters of the flow obstruction structure 3, thereby improving the accuracy and uniformity of the flow distribution.

[0112] The arrangement of the flow passage 31 and its upstream branch outlet 2 at radial intervals along the manifold 100 is not limited; for example, in some embodiments, see [reference needed]. Figure 5 The flow channel 31 is centered relative to the axis of the manifold 100, or, for example, see Figure 11 The flow passage 31 is offset relative to the axis of the manifold 100, with the side of the pipe wall away from the branch outlet 2. Therefore, when the flow passage 31 is centered relative to the axis of the manifold 100, it helps reduce the flow deviation and eddy current phenomena within the manifold 100, improving the uniformity and stability of fluid distribution. When the flow passage 31 is offset relative to the axis of the manifold 100, with the side of the pipe wall away from the branch outlet 2, the regulating effect of the flow-blocking structure 3 can be further enhanced, allowing more fluid in the manifold 100 to flow towards the branch outlet 2.

[0113] In some embodiments, see Figure 12 In at least two adjacent branch outlets 2, the inner diameter of the upstream branch outlet 2 (e.g., inner diameter D5 as shown in the figure) is larger than the inner diameter of the downstream branch outlet 2 (e.g., inner diameter D6 as shown in the figure). Therefore, by adjusting the inner diameters of the upstream and downstream branch outlets 2, the flow path and distribution ratio of the fluid in the manifold 100 can be flexibly controlled. Specifically, the larger inner diameter of the upstream branch outlet 2 reduces the resistance when the fluid passes through, allowing the fluid to flow more smoothly into the upstream branch outlet 2. This, to a certain extent, balances the flow distribution between the upstream and downstream branch outlets 2, improving the uniformity of fluid distribution at each branch outlet 2 of the manifold 100.

[0114] For example, the inner diameters of the multiple branch outlets 2 decrease sequentially along the fluid flow direction.

[0115] In some embodiments, see Figure 12The manifold 100 is vertically arranged, with the inlet 1 located at the bottom. Multiple branch outlets 2 are arranged upwards relative to the inlet 1. Thus, through gravity, excessive fluid flow within the manifold 100 to the distal outlet 2a of the branch outlets 2 is prevented from flowing excessively due to inertia. This promotes the flow of fluid from the manifold 100 into other branch outlets 2, improving the uniformity of fluid distribution across the branch outlets 2 of the manifold 100.

[0116] It is worth noting that the pipe inlet 1 is located at the lower part of the manifold 100. The specific meaning of "lower part" is not limited; for example, it could refer to the lower end of the pipe. When the lower part of the manifold 100 is a straight pipe, the pipe inlet 1 can be located at the very bottom of the manifold 100. However, when the lower part of the manifold 100 is a bent pipe (e.g., ...), ... Figure 12 As shown), pipe inlet 1 can be located at the end of the bend.

[0117] Hereinafter, with reference to the accompanying drawings, a heat exchanger 1000 according to a second aspect embodiment of the present invention will be described.

[0118] See Figure 13 The heat exchanger 1000 includes a heat exchanger body 1000c, an inlet pipe 1000a, and an outlet pipe 1000b. The heat exchanger body 1000c has multiple parallel branches 1000c1. The inlet pipe 1000a is a manifold 100 according to any embodiment of the first aspect of the present invention. Multiple branch outlets 2 are connected to the inlets of multiple parallel branches 1000c1 in a one-to-one correspondence. The outlet pipe 1000b is connected to the outlets of multiple parallel branches 1000c1 in a one-to-one correspondence.

[0119] According to the embodiment of the present utility model, the heat exchanger 1000 improves the uniformity of refrigerant flow in the multiple parallel branches 1000c1 of the heat exchanger 1000 by setting the manifold 100 of the first aspect, thereby reducing the waste of heat exchange area of ​​the heat exchanger 1000 and improving the cooling and heating efficiency of the heat exchanger 1000.

[0120] The specific composition of the heat exchanger body 1000c is not limited. For example, in some embodiments of this utility model, the form of the heat exchanger body 1000c is not limited. The heat exchanger body 1000c may include stacked multi-layer fins and heat exchange tubes through which the multi-layer fins are disposed. Each parallel branch 1000c1 includes multiple heat exchange tubes connected in series and / or in parallel. Alternatively, in other embodiments of this utility model, the heat exchanger body 1000c may also include multiple flat tubes, each flat tube having multiple flow channels. Each flat tube constitutes a parallel branch 1000c1.

[0121] Hereinafter, with reference to the accompanying drawings, an air conditioner 10000 according to a third aspect embodiment of the present invention will be described.

[0122] See Figure 14 The air conditioner 10000 includes a heat exchanger 1000 according to a second aspect embodiment of the present invention.

[0123] According to the embodiment of the present utility model, the air conditioner 10000 improves the overall operating efficiency of the air conditioner and the user experience by setting the heat exchanger 1000 of the second aspect described above.

[0124] The type of air conditioner 10000 is not limited. For example, it can be an integrated air conditioner (such as a kitchen air conditioner, a portable air conditioner, a window air conditioner, etc.) or a split air conditioner (such as a split wall-mounted unit, a split floor-standing unit, etc.).

[0125] Other components of the air conditioner 10000 according to the present invention, such as air duct components and panel components, as well as its operation, are known to those skilled in the art and will not be described in detail here.

[0126] See Figure 15 Experimental comparison and verification were conducted. Example 1 used the manifold 100 of this utility model embodiment, with flow-blocking structures 3 installed upstream of each branch outlet 2 except for the distal outlet 2a. Comparative Example 1, compared to Example 1, eliminated all flow-blocking structures 3; all other experimental parameters remained the same. Figure 15 As can be seen from the data, compared with Comparative Example 1, the cooling performance coefficient (EER) of the air conditioner in Example 1 increased from 2.64 to 2.81; the heating performance coefficient (COP) of the air conditioner increased from 3.27 to 3.30. From these experimental data, it can be seen that the technical solution of this utility model can improve the cooling and heating performance coefficients of the air conditioner 10000 and improve the energy efficiency of the air conditioner 10000 by setting the flow obstruction structure 3 upstream of each branch outlet 2 except for the far-end outlet 2a in the manifold 100.

[0127] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model.

[0128] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this utility model, "a plurality of" means two or more, unless otherwise explicitly specified.

[0129] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. For those skilled in the art, the specific meaning of the above terms in this utility model can be understood according to the specific circumstances.

[0130] In this utility model, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0131] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0132] Although embodiments of the present invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A manifold, characterized in that, The manifold has a pipe inlet, and the side wall of the manifold has a plurality of branch outlets arranged at intervals along a direction away from the pipe inlet, the branch outlet being the one furthest from the pipe inlet; The manifold is provided with a flow-blocking structure, and the flow-blocking structure is provided at at least one of the branch outlets except for the distal outlet. The flow-blocking structure is used to reduce the flow area of ​​the manifold at the flow-blocking structure, so as to promote the fluid in the manifold to enter the branch outlet at the flow-blocking structure.

2. The manifold according to claim 1, characterized in that, The flow obstruction structure includes an inner tube structure, which connects the upstream and downstream sides of the inner tube structure. A buffer space is formed between the outer wall of the inner tube structure and the inner wall of the collector tube. The buffer space is connected to the upstream side of the inner tube structure and isolated from the downstream side of the inner tube structure.

3. The manifold according to claim 2, characterized in that, The manifold includes a plurality of sub-pipes arranged sequentially along the axial direction of the manifold. At least two adjacent sub-pipes are an upstream pipe and a downstream pipe, respectively. The upstream end of the downstream pipe is narrowed to form the inner pipe structure and extends into the downstream end of the upstream pipe. The downstream end of the upstream pipe forms the branch outlet.

4. The manifold according to claim 3, characterized in that, The downstream pipe includes a downstream main pipe, a tapered pipe, and the inner pipe structure connected sequentially in the direction towards the upstream. The downstream main pipe and the inner pipe structure are both pipes of equal diameter, and the diameter of the inner pipe structure is smaller than that of the downstream main pipe. The diameter of the tapered pipe gradually decreases in the direction from the downstream main pipe to the inner pipe structure.

5. The manifold according to claim 4, characterized in that, The upstream pipe includes an upstream main pipe, a diverging pipe, and a sleeve structure connected sequentially in a downstream direction. The upstream main pipe and the sleeve structure are both pipes of equal diameter, and the diameter of the sleeve structure is larger than that of the upstream main pipe. The diameter of the diverging pipe gradually increases from the upstream main pipe to the sleeve structure. The sleeve structure is fitted outside the downstream main pipe, and the inner pipe structure extends into the upstream main pipe. The inner diameter of the upstream main pipe constitutes the inner diameter of the upstream pipe, and the branch outlet is formed on the upstream main pipe.

6. The manifold according to claim 3, characterized in that, The upstream end of the downstream pipe has a locking structure that locks into the port of the downstream end of the upstream pipe.

7. The manifold according to claim 3, characterized in that, At least one of the sub-pipes is a flow-blocking sleeve, and the downstream end of the flow-blocking sleeve is provided with the branch outlet on its side wall and the upstream end is formed as the inner pipe structure.

8. The manifold according to claim 2, characterized in that, The flow-blocking structure includes one inner tube structure, and the inner tube structure is centrally located relative to the axis of the manifold; or the flow-blocking structure includes multiple inner tube structures arranged in parallel and spaced apart.

9. The manifold according to claim 2, characterized in that, The ratio of the inner diameter of the inner tube structure to the inner diameter of the branch outlet is 0.7-1.2; and / or the ratio of the distance between the inner tube structure and the manifold to the inner diameter of the manifold is 0.05-0.

4.

10. The manifold according to any one of claims 2-9, characterized in that, The branch outlet is located upstream of the inlet end of the inner tube structure; or, the branch outlet is radially opposite to the buffer space.

11. The manifold according to claim 1, characterized in that, The flow-blocking structure is located downstream of the corresponding branch outlet to facilitate the flow of fluid in the manifold into the branch outlet upstream of the flow-blocking structure.

12. The manifold according to claim 11, characterized in that, The flow-blocking structure includes at least one of the following: inner tube structure, perforated plate structure, baffle structure, and screen structure.

13. The manifold according to claim 11, characterized in that, The axial distance between the flow-blocking structure and its upstream branch outlet is less than the inner diameter of the corresponding branch outlet, or the axial distance between the flow-blocking structure and its upstream branch outlet is 0-10 mm.

14. The manifold according to claim 11, characterized in that, The flow-blocking structure helps to define a flow channel to connect the upstream and downstream of the flow-blocking structure. The flow channel and its upstream branch outlet are arranged radially apart from each other in the manifold.

15. The manifold according to claim 14, characterized in that, The flow passage is centered relative to the axis of the manifold, or it is offset relative to the axis of the manifold toward the side of the pipe wall away from the branch outlet.

16. The manifold according to claim 1, characterized in that, In at least two adjacent branch outlets, the inner diameter of the upstream branch outlet is larger than the inner diameter of the downstream branch outlet.

17. The manifold according to claim 1, characterized in that, The manifold is vertically arranged, with the inlet located at the bottom of the manifold, and the multiple branch outlets arranged sequentially upwards relative to the inlet.

18. A heat exchanger, characterized in that, include: The heat exchanger body has multiple parallel branches within it; The input pipe is a collector pipe according to any one of claims 1-17, and the plurality of branch outlets are connected to the inlets of the plurality of parallel branches in a one-to-one correspondence; The output tube is connected to the outlet of each of the parallel branches.

19. An air conditioner, characterized in that, Includes the heat exchanger according to claim 18.

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