Collecting pipe, heat exchanger and air conditioner

Abstract

The utility model discloses a collecting pipe, heat exchanger and air conditioner, the collecting pipe is provided with a plurality of branch outlets at intervals along the axial direction of the collecting pipe, the collecting pipe comprises at least two sub-pipes which are sequentially arranged along the axial direction of the collecting pipe, at least two adjacent sub-pipes are respectively an upstream pipe and a downstream pipe, the downstream end of the upstream pipe is sleeved outside the upstream end of the downstream pipe, the end part, extending into the upstream pipe, of the downstream pipe is centrally shrunk to form an inner pipe structure, the upstream pipe comprises an upstream main pipe positioned at the upstream of the inner pipe structure, the inner diameter of the inner pipe structure is smaller than that of the upstream main pipe, and a branch outlet is formed at the downstream end of the upstream pipe; fluid in the upstream pipe is sent out through the branch outlets and the inner pipe structure. According to the collecting pipe, machining is convenient, and the uniformity of refrigerant distribution and output can be improved.

Description

TECHNICAL FIELD

[0001] The utility model relates to air conditioning technology field especially is related to a manifold, heat exchanger and air conditioner. BACKGROUND

[0002] In the related art, the manifold is often used as a refrigerant distribution device. However, in actual application, due to the inertia of the refrigerant flowing in the pipeline, the refrigerant distribution in the distal branch is excessive, while the refrigerant distribution in the proximal branch is relatively less. This uneven refrigerant distribution results in poor heat exchange capacity of the heat exchanger. SUMMARY

[0003] The utility model discloses at least one of the technical problems in the prior art. To this end, the utility model provides a manifold, which is easy to process and beneficial to improve the uniformity of refrigerant distribution output.

[0004] The utility model further provides a heat exchanger with the manifold.

[0005] The utility model further provides an air conditioner with the heat exchanger.

[0006] According to the manifold of the first aspect of the utility model, the manifold has a plurality of branch outlets arranged along the axial direction of the manifold, the manifold includes at least two sub-pipes arranged along the axial direction of the manifold, and the at least two adjacent sub-pipes are an upstream pipe and a downstream pipe, respectively. The downstream end of the upstream pipe is sleeved outside the upstream end of the downstream pipe, the end of the downstream pipe inserted into the upstream pipe is reduced in diameter to form an inner pipe structure, the upstream pipe includes an upstream main pipe located upstream of the inner pipe structure, the inner diameter of the inner pipe structure is smaller than the inner diameter of the upstream main pipe, the downstream end of the upstream pipe forms the branch outlet, and the fluid in the upstream pipe is sent out through the branch outlet and the inner pipe structure, respectively.

[0007] According to the manifold of the utility model, the manifold is easy to process and beneficial to improve the uniformity of refrigerant distribution output.

[0008] In some embodiments, the ratio of the inner diameter of the inner pipe structure to the inner diameter of the corresponding branch outlet is 0.7-1.2.

[0009] In some embodiments, the inner pipe structure is a constant-diameter pipe.

[0010] In some embodiments, the downstream pipe comprises, sequentially connected along a direction towards upstream, a downstream main pipe, a tapered pipe and the inner pipe structure, the downstream main pipe and the inner pipe structure are both equal-diameter pipes, and the inner pipe structure has a smaller pipe diameter than the downstream main pipe, and the tapered pipe has a gradually decreasing pipe diameter along a direction from the downstream main pipe to the inner pipe structure.

[0011] In some embodiments, the outer wall of the inner pipe structure is spaced apart from the inner wall of the upstream pipe to form a buffer space between the outer wall of the inner pipe structure and the inner wall of the upstream pipe, the buffer space being in communication with the upstream pipe and isolated from the downstream pipe.

[0012] In some embodiments, the inner pipe structure extends into the upstream main pipe, and the ratio of the spacing between the outer wall of the inner pipe structure and the inner wall of the upstream main pipe to the inner diameter of the upstream main pipe is 0.05-0.4.

[0013] In some embodiments, the upstream pipe comprises, sequentially connected along a direction towards downstream, the upstream main pipe, a tapered pipe and a sleeve structure, the upstream main pipe and the sleeve structure are both equal-diameter pipes, and the sleeve structure has a larger pipe diameter than the upstream main pipe, the tapered pipe has a gradually increasing pipe diameter along a direction from the upstream main pipe to the sleeve structure, and the sleeve structure is sleeved outside the downstream pipe.

[0014] In some embodiments, the upstream end of the downstream pipe is formed with a clamping structure clamped outside a port of the downstream end of the upstream pipe.

[0015] In some embodiments, the upstream pipe comprises the upstream main pipe and a shape-fitting pipe, the shape-fitting pipe being located downstream of the upstream main pipe, the shape-fitting pipe having a smaller pipe diameter than the upstream main pipe, the inner diameter of the shape-fitting pipe matching the outer diameter of the inner pipe structure, and the shape-fitting pipe being sleeved outside the inner pipe structure.

[0016] In some embodiments, the branch outlet provided at the downstream end of the upstream pipe is formed on the side wall of the upstream main pipe; and / or, the branch outlet is located upstream of the corresponding inner pipe structure, and the spacing between the upstream end of the inner pipe structure and the corresponding branch outlet in the axial direction of the manifold is 0-10 mm.

[0017] In some embodiments, at least one of the sub-pipes is a flow-blocking sleeve pipe, the flow-blocking sleeve pipe being provided with the branch outlet on the side wall of the downstream end and being formed as the inner pipe structure at the upstream end.

[0018] In some embodiments, the manifold is provided with a tube inlet, the most distal outlet of the plurality of branch outlets is a distal outlet, and the inner tube structure is provided at at least one of the branch outlets other than the distal outlet.

[0019] In some embodiments, the manifold is vertically arranged, the lower part of the manifold is provided with a tube inlet, and the plurality of branch outlets are arranged in sequence upward relative to the tube inlet; and / or, among at least two adjacent branch outlets, the inner diameter of the upstream branch outlet is greater than that of the downstream branch outlet.

[0020] According to the heat exchanger of the second aspect of the present application, the heat exchanger comprises a heat exchanger body, an input pipe and an output pipe, the heat exchanger body has a plurality of parallel branches; the input pipe is the manifold according to any one of the first aspect of the present application, the plurality of branch outlets are in one-to-one correspondence with the inlets of the plurality of parallel branches; and the output pipe is in one-to-one correspondence with the outlets of the plurality of parallel branches.

[0021] According to the heat exchanger of the second aspect of the present application, the heat exchanger comprises a heat exchanger body, an input pipe and an output pipe, the heat exchanger body has a plurality of parallel branches; the input pipe is the manifold according to any one of the first aspect of the present application, the plurality of branch outlets are in one-to-one correspondence with the inlets of the plurality of parallel branches; and the output pipe is in one-to-one correspondence with the outlets of the plurality of parallel branches.

[0022] According to the air conditioner of the third aspect of the present application, the heat exchanger according to the second aspect of the present application is used.

[0023] According to the air conditioner of the third aspect of the present application, the heat exchanger according to the second aspect of the present application is used.

[0024] Additional aspects and advantages of the present application will be partially given in the following description, some of which will become apparent from the following description, or will be understood by those skilled in the art through practice of the present application. BRIEF DESCRIPTION OF DRAWINGS

[0025] Figure 1 is a schematic view of a manifold according to an embodiment of the present application;

[0026] Figure 2 is Figure 1 is a partial schematic view of the inner tube structure shown in FIG.

[0027] Figure 3 is Figure 1 is an exploded schematic view of the inner tube structure shown in FIG.

[0028] Figure 4 is a partial schematic view of the inner tube structure according to another embodiment of the present application;

[0029] Figure 5is a partial schematic view of an inner tube structure according to another embodiment of the present application;

[0030] Figure 6 is a partial schematic view of an inner tube structure according to another embodiment of the present application;

[0031] Figure 7 is a schematic view of a manifold according to another embodiment of the present application;

[0032] Figure 8 is a schematic view of a heat exchanger according to one embodiment of the present application;

[0033] Figure 9 is a schematic view of an air conditioner according to one embodiment of the present application;

[0034] Figure 10 is an experimental comparison data graph of Example 1 and Comparative Example 1.

[0035] Reference signs:

[0036] Air conditioner 10000;

[0037] Heat exchanger 1000;

[0038] Heat exchanger body 1000c; parallel branch 1000c1; input pipe 1000a; output pipe 1000b;

[0039] Manifold 100; sub-pipe 4; flow blocking sleeve 4x;

[0040] Upstream pipe 41; upstream main pipe 411; gradually expanding pipe 412; sleeve structure 413; shape fitting pipe 414;

[0041] Downstream pipe 42; downstream main pipe 421; gradually reducing pipe 422; inner tube structure 3a; detent structure 424;

[0042] Pipe inlet 1; branch outlet 2; flow passage 31; buffer space 3a1. DETAILED DESCRIPTION

[0043] The embodiments of the present application are described in detail below, and examples of the embodiments are shown in the drawings, wherein the same or similar reference signs represent the same or similar elements or elements having the same or similar functions throughout. The embodiments described below by referring to the drawings are exemplary and are intended to explain the present application, and cannot be understood as a limitation of the present application.

[0044] Below, with reference to the drawings, the manifold 100 according to the first aspect embodiment of the present application is described.

[0045] Referring to Figures 1-3The manifold 100 has a plurality of branch outlets 2 arranged along the axial direction of the manifold 100, and the manifold 100 comprises at least two sub-pipes 4 arranged along the axial direction of the manifold 100 in sequence, the at least two adjacent sub-pipes 4 are respectively an upstream pipe 41 and a downstream pipe 42, the downstream end of the upstream pipe 41 is sleeved outside the upstream end of the downstream pipe 42, the end of the downstream pipe 42 extending into the upstream pipe 41 is centrally reduced in diameter to form an inner pipe structure 3a, the upstream pipe 41 comprises an upstream main pipe 411 located upstream of the inner pipe structure 3a, the inner diameter D1 of the inner pipe structure 3a is smaller than the inner diameter D4 of the upstream main pipe 411, and the downstream end of the upstream pipe 41 is formed with a branch outlet 2, and the fluid in the upstream pipe 41 is sent out through the branch outlet 2 and the inner pipe structure 3a respectively.

[0046] The axial direction of the manifold 100 is the flow direction of the manifold 100, that is, the flow direction of the fluid (such as refrigerant) in the manifold 100. The fluid in the manifold 100 flows towards the downstream distal end of the manifold 100 after entering the pipe inlet 1. It should be noted that the manifold 100 can be a straight pipe, but is not limited to a straight pipe, for example, can also be a bent pipe, a folded pipe, etc. Therefore, the axial direction of the manifold 100 is not limited to a straight line direction.

[0047] In the embodiment of the present application, the upstream pipe 41 refers to the pipe through which the refrigerant flows first in the flow direction, and the downstream pipe 42 refers to the pipe through which the refrigerant flows later in the flow direction. The upstream pipe 41 and the downstream pipe 42 are a relative concept, and are not specific to a certain sub-pipe 4. Therefore, for some sub-pipes 4, they can serve as both upstream pipes 41 and downstream pipes 42.

[0048] As shown in Figures 1-3 The inner cavity of the inner pipe structure 3a is a flow passage 31, and a part of the fluid (such as refrigerant) in the upstream pipe 41 can enter the downstream pipe 42 through the flow passage 31, and the remaining refrigerant in the upstream pipe 41 can flow out through the branch outlet 2 and enter the heat exchanger body 1000c.

[0049] In the related art, the manifold is often used as a refrigerant distribution device. However, in actual application, due to the inertia of the refrigerant flowing in the pipe, the refrigerant distribution in the distal branch is excessive, and the refrigerant distribution in the proximal branch is relatively less. This uneven refrigerant distribution results in poor heat exchange performance of the heat exchanger using the manifold, and poor energy efficiency of the air conditioner using the heat exchanger during the refrigeration and heating processes.

[0050] However, in the technical scheme of the utility model, since the inner diameter D1 of the inner tube structure 3a is smaller than the inner diameter D4 of the upstream main pipe 411, when the refrigerant flows from the upstream pipe 41 to the downstream pipe 42, the refrigerant will be hindered by the inner tube structure 3a, which is conducive to promoting the flow of the refrigerant in the upstream pipe 41 to the branch outlet 2, reducing the problem that most of the fluid enters the inner tube structure 3a due to inertial impact and misses the branch outlet 2. Thus, according to the distribution characteristics of the refrigerant affected by inertia of each branch outlet 2, the inner tube structure 3a can be arranged at the branch outlet 2 with a smaller refrigerant amount, so as to improve the refrigerant distribution uniformity of each branch outlet 2 and improve the refrigeration and heating energy efficiency of the air conditioner 10000.

[0051] In the technical scheme of the utility model, the end of the downstream pipe 42 is centrally reduced in diameter to form the inner tube structure 3a. That is, the diameter of the inner tube structure 3a is smaller than that of the main pipe section of the downstream pipe 42 (for example, the downstream main pipe 421 shown in the figure), and the axis of the inner tube structure 3a coincides with the axis of the main pipe section of the downstream pipe 42 (for example, the downstream main pipe 421 shown in the figure). Thus, the downstream pipe 42 and the inner tube structure 3a are convenient to process. However, the inner tube structure 3a is not limited to being processed by the pipe reducing process, and can be obtained by other ways of processing the downstream pipe 42. For example, the downstream pipe 42 can be an integral molded part or an integrated part formed by fixedly connecting a plurality of parts.

[0052] In addition, the upstream end of the downstream pipe 42 is arranged to form the inner tube structure 3a and extend into the downstream end of the upstream pipe 41. This nested connection makes the inner tube structure 3a convenient to process and fix to the required position, which is conducive to batch efficient production of the manifold 100. Furthermore, the manifold 100 comprises a plurality of sub-pipes 4 arranged in sequence along the fluid flow direction, so that the manifold 100 is easy to expand or reduce, and the number of sub-pipes 4 can be increased or reduced according to actual needs, so as to flexibly adapt to different types of heat exchangers 1000. From the production point of view, the sub-pipes 4 can be standardized, so that they can be produced in batches, improving production efficiency.

[0053] In the embodiment of the utility model, the specific positional relationship between the branch outlet 2 and the inner tube structure 3a is not limited. For example, referring to Figure 4 , the branch outlet 2 is arranged upstream of the inlet end of the inner tube structure 3a. Thus, the fluid hindered by the inner tube structure 3a can enter the branch outlet 2 upstream of the inner tube structure 3a, so that the flow rate, flow velocity and pressure of the fluid flowing out of the branch outlet 2 can be more effectively controlled. For example, referring to Figure 5 , the branch outlet 2 and the buffer space 3a1 are arranged in radial opposition. Thus, the fluid in the buffer space 3a1 can effectively enter the branch outlet 2, thereby improving the flow distribution ratio of the branch outlet 2.

[0054] In the embodiment of the utility model, the spatial direction and shape of the manifold 100 are not limited, and the specific parameters of the manifold 100 should be matched with the heat exchanger 1000.

[0055] In the embodiment of the utility model, the number of sub-pipes 4 of the manifold 100 is not limited, and the number and position of branch outlets 2 on each sub-pipe 4 are not limited. Exemplarily, one branch outlet 2 is arranged on each sub-pipe 4. Exemplarily, the number of sub-pipes 4 can be 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, etc. The spacing arrangement mode of the plurality of branch outlets 2 is not limited, and exemplarily, the plurality of branch outlets 2 can be arranged at equal intervals or at variable intervals, for example, the specific spacing can be matched with the spacing of the parallel branch 1000c1 of the heat exchanger 1000.

[0056] In the embodiment of the utility model, the fluid in the manifold 100 is refrigerant (refrigerant or cold carrier, etc.), and the phase state of the refrigerant in the manifold 100 is not limited, which can be liquid phase, gas phase or gas-liquid mixed phase.

[0057] In some embodiments, the branch outlet 2 arranged at the downstream end of the upstream pipe 41 is formed on the side wall of the upstream main pipe 411. Thus, since the inner diameter D1 of the inner pipe structure 3a is smaller than the inner diameter D4 of the upstream main pipe 411, and the branch outlet 2 is arranged on the side wall of the upstream main pipe 411, the amount of refrigerant flowing to the branch outlet 2 can be increased.

[0058] In some embodiments, referring to Figure 2 , the ratio of the inner diameter D1 of the inner pipe structure 3a to the inner diameter D2 of the corresponding branch outlet 2 is 0.7-1.2. For example, 0.7, 0.8, 0.9, 1.0, 1.1, 1.2, etc. Thus, it is beneficial to adjust the flow distribution into the inner pipe structure 3a and the branch outlet 2, reduce the refrigerant flow into the inner pipe structure 3a, thereby improving the refrigeration and heating energy efficiency of the air conditioner 10000, improving the overall operation efficiency of the air conditioner and the user's use experience.

[0059] In the embodiment of the utility model, the cross-sectional shape of the inner pipe structure 3a is not limited, and exemplarily, the cross-sectional shape of the inner pipe structure 3a can be circular or polygonal, and in addition, the cross-sectional area of the inner pipe structure 3a can be fixed or variable. Exemplarily, the inner pipe structure 3a is an equal-diameter pipe, that is, the cross-sectional area of the inner pipe structure 3a is equal everywhere, thereby facilitating the processing of the inner pipe structure 3a and the stable flow of the refrigerant in the inner pipe structure 3a. Exemplarily, when the inner pipe structure 3a is not an equal-diameter pipe, the inner diameter of the inner pipe structure 3a at any position satisfies the ratio of 0.7-1.2 to the inner diameter D2 of the corresponding branch outlet 2.

[0060] In some embodiments, in combination with Figure 3The downstream pipe 42 includes, in sequence along the direction towards the upstream, a downstream main pipe 421, a tapered pipe 422 and an inner pipe structure 3a, the downstream main pipe 421 and the inner pipe structure 3a are both equal-diameter pipes, and the pipe diameter of the inner pipe structure 3a is smaller than that of the downstream main pipe 421, and the pipe diameter of the tapered pipe 422 gradually decreases along the direction from the downstream main pipe 421 to the inner pipe structure 3a.

[0061] In the above technical solution, the refrigerant entering the inner pipe structure 3a flows through the inner pipe structure 3a, the tapered pipe 422 and the downstream main pipe 421 in sequence, and the pipe diameter of the inner pipe structure 3a is smaller than that of the downstream main pipe 421, and the tapered pipe 422 is connected between the inner pipe structure 3a and the downstream main pipe 421, so that when the fluid flows from the inner pipe structure 3a into the downstream main pipe 421, it can gradually adapt to the change of the pipe diameter, reducing the formation of fluid impact and vortex, thereby optimizing the fluid dynamics performance and reducing energy loss. From the perspective of processing, for example, the inner pipe structure 3a and the tapered pipe 422 can be formed by reducing the pipe diameter of the downstream main pipe 421 through a pipe reducing process, and essentially the downstream pipe 42 is integrated, thereby enhancing the structural strength of the entire downstream pipe 42. In addition, the tapered pipe 422 reduces stress concentration points through smooth pipe diameter changes, improving the pressure resistance and service life of the pipe.

[0062] In some embodiments, in combination with Figure 4 and Figure 5 The outer wall of the inner pipe structure 3a is spaced apart from the inner wall of the upstream pipe 41 to form a buffer space 3a1 between the outer wall of the inner pipe structure 3a and the inner wall of the upstream pipe 41, the buffer space 3a1 is in communication with the upstream pipe 41 and is isolated from the downstream pipe 42. Wherein, "communication" and "isolation" are relative to fluid flow. Communication means that fluid can flow from one place to another; isolation means that there is no fluid passage between the two places.

[0063] Therefore, by providing the buffer space 3a1, when the refrigerant flows from the upstream pipe 41 to the downstream pipe 42, part of the refrigerant flows into the buffer space 3a1, and the buffer space 3a1 is isolated from the downstream pipe 42, the refrigerant forms a reflected backflow in the buffer space 3a1, which disturbs the flow of refrigerant to the inner pipe structure 3a, reducing the flow of refrigerant into the inner pipe structure 3a, thereby prompting the refrigerant to flow to the branch outlet 2 near the buffer space 3a1, and allowing the gaseous and liquid refrigerants to mix fully, reducing the influence of the inertial dynamic pressure of the refrigerant, and facilitating the refrigerant amount of the branch outlet 2 near the buffer space 3a1, so that the inner pipe structure 3a can be provided at the branch outlet 2 with less refrigerant amount according to the distribution characteristics of the refrigerant affected by inertia, to improve the uniformity of refrigerant distribution of each branch outlet 2, and improve the refrigeration and heating energy efficiency of the air conditioner 10000.

[0064] In addition, when the downstream pipe 42 comprises a downstream main pipe 421, a tapered pipe 422 and an inner pipe structure 3a connected in sequence along a direction towards the upstream, the downstream main pipe 421 and the inner pipe structure 3a are both equal-diameter pipes, the pipe diameter of the inner pipe structure 3a is smaller than that of the downstream main pipe 421, and the pipe diameter of the tapered pipe 422 gradually decreases along a direction from the downstream main pipe 421 to the inner pipe structure 3a, the outer wall of the tapered pipe 422 facilitates the formation of reflected backflow of the refrigerant in the buffer space 3a1, increases the disturbance to the refrigerant, thereby reducing the flow of the refrigerant into the inner pipe structure 3a, and forcing the refrigerant to flow more to the branch outlets 2 near the buffer space 3a1.

[0065] In some embodiments, in combination with Figure 2 The inner pipe structure 3a extends into the upstream main pipe 411, and the ratio of the spacing D3 between the outer wall of the inner pipe structure 3a and the inner wall of the upstream main pipe 411 to the inner diameter D4 of the upstream main pipe 411 is 0.05-0.4, for example, 0.05, 0.1, 0.2, 0.3, 0.4, etc. Thus, it is beneficial to adjust the intensity of the reflected backflow, which will hinder or disturb the flow of the refrigerant to the overflow passage 31, thereby indirectly adjusting the flow distribution into the inner pipe structure 3a and the branch outlets 2, and reducing the flow of the refrigerant into the inner pipe structure 3a.

[0066] In some embodiments, in combination with Figure 2 The upstream pipe 41 comprises an upstream main pipe 411, a tapered pipe 412 and a sleeve structure 413 connected in sequence along a direction towards the downstream, the upstream main pipe 411 and the sleeve structure 413 are both equal-diameter pipes, the pipe diameter of the sleeve structure 413 is greater than that of the upstream main pipe 411, the pipe diameter of the tapered pipe 412 gradually increases along a direction from the upstream main pipe 411 to the sleeve structure 413, and the sleeve structure 413 is sleeved outside the downstream pipe 42.

[0067] In the above technical solution, by setting the pipe diameter of the sleeve structure 413 to be greater than that of the upstream main pipe 411, it is beneficial for the sleeve structure 413 to be smoothly sleeved outside the downstream pipe 42, reducing the connection difficulty of the two, and this way is easy to construct a larger buffer space 3a1, and from the perspective of processing, the sleeve structure 413 and the tapered pipe 412 can be formed by expanding the pipe diameter of the upstream main pipe 411 through a pipe expanding process, which is essentially an integrated upstream pipe 41, thereby enhancing the structural strength of the upstream pipe 41 as a whole. In addition, the tapered pipe 412 reduces stress concentration points through smooth pipe diameter changes, improving the pressure resistance and service life of the pipe. However, the sleeve structure 413 and the tapered pipe 412 are not limited to being processed by the pipe expanding process, and the sleeve structure 413 and the tapered pipe 412 can be obtained by processing the upstream pipe 41 in other ways. For example, the upstream pipe 41 can be an integrally formed piece, or an integrated piece fixedly connected by multiple parts.

[0068] In some embodiments, the length of the downstream main pipe 421 is greater than half of the length of the downstream pipe 42, where the length refers to the dimension along the axial direction of the manifold 100. Thus, the downstream pipe 42 is mainly composed of the downstream main pipe 421, and the length of the downstream main pipe 421 occupies a substantial portion of the length of the downstream pipe 42, and thus the inner diameter of the downstream main pipe 421 constitutes the inner diameter of the downstream pipe 42. In some embodiments, the substantial portion of the downstream pipe 42 is of a constant diameter structure, which facilitates the processing of the downstream pipe 42 and stabilizes the flow of the refrigerant in the downstream pipe 42.

[0069] In some embodiments, the length of the upstream main pipe 411 is greater than half of the length of the upstream pipe 41, where the length refers to the dimension along the axial direction of the manifold 100. Thus, the upstream pipe 41 is mainly composed of the upstream main pipe 411, and the length of the upstream main pipe 411 occupies a substantial portion of the length of the upstream pipe 41, and thus the inner diameter of the upstream main pipe 411 constitutes the inner diameter of the upstream pipe 41. In some embodiments, the substantial portion of the upstream pipe 41 is of a constant diameter structure, which facilitates the processing of the upstream pipe 41 and stabilizes the flow of the refrigerant in the upstream pipe 41.

[0070] In some embodiments, referring to Figure 2 , the inner diameter of the downstream main pipe 421 is equal to the inner diameter of the upstream main pipe 411, for example, both are D4 as shown in Figure 2 . Thus, the flow state of the refrigerant is not substantially changed when the refrigerant flows through the upstream pipe 41 and the downstream pipe 42 in sequence, i.e., the state parameters of the refrigerant (such as flow rate, pressure, etc.) are not substantially affected by the change in pipe diameter, and the relatively stable state of the refrigerant reduces the variables that need to be considered for flow distribution adjustment, making flow distribution adjustment more convenient.

[0071] In addition, the inner diameter of the downstream main pipe 421 is equal to the inner diameter of the upstream main pipe 411, which increases the possibility of standardization of the manifold, so that in some embodiments, the upstream pipe 41 and the downstream pipe 42 can be of the same specification, and can be selected in no order during assembly, which increases the convenience of installation and maintenance of the manifold 100 and reduces the operation difficulty and time cost of installation.

[0072] In some embodiments, referring to Figure 2 , the upstream end of the downstream pipe 42 is formed with a clamping structure 424, which is clamped outside the port of the downstream end of the upstream pipe 41.

[0073] In the above technical solution, the relative movement of the upstream pipe 41 and the downstream pipe 42 in the axial direction (i.e., the fluid flow direction) is effectively prevented by the blocking effect of the blocking structure 424. The length of the sleeved connection between the downstream pipe 42 and the upstream pipe 41 can be limited by the setting position of the blocking structure 424, so that the relative position of the inner pipe structure 3a and the nearby branch outlet 2 is accurate, and the effectiveness of the inner pipe structure 3a in promoting the fluid into the branch outlet 2 is improved. In addition, in some embodiments, the above-mentioned clamping can also be used to form a pre-positioning, and the two sub-pipes 4 can be reliably connected together by welding or the like subsequently.

[0074] In the embodiments of the present application, the form of the blocking structure 424 is not limited, and exemplary forms of the blocking structure 424 include buckles, clamping protrusions, etc., and the specific form needs to be determined according to the actual application scenario.

[0075] Of course, the present application is not limited thereto, and the outer wall of the inner pipe structure 3a and the inner wall of the upstream pipe 41 can also not define a buffer space 3a1, for example, as shown in Figure 6 In some embodiments, the upstream pipe 41 includes an upstream main pipe 411 and a shape-fitting pipe 414, the shape-fitting pipe 414 is located downstream of the upstream main pipe 411, the pipe diameter of the shape-fitting pipe 414 is smaller than the pipe diameter of the upstream main pipe 411, the inner diameter of the shape-fitting pipe 414 matches the outer diameter of the inner pipe structure 3a, and the shape-fitting pipe 414 is sleeved outside the inner pipe structure 3a. In this way, since the pipe diameter of the shape-fitting pipe 414 is smaller than the pipe diameter of the upstream main pipe 411, the shape-fitting pipe 414 also forms resistance to the refrigerant of the upstream main pipe 411, thereby promoting more refrigerant to enter the branch outlet 2.

[0076] The "inner diameter of the shape-fitting pipe 414 matches the outer diameter of the inner pipe structure 3a" means that the inner diameter of the shape-fitting pipe 414 is close to or equal to the outer diameter of the inner pipe structure 3a, so that the two can be relatively tightly sleeved and matched, thereby improving the stability and sealing performance of the connection position. The connection mode of the upstream main pipe 411 and the shape-fitting pipe 414 is not limited, for example, the two can be connected through a stepped surface, or can also be connected through a gradual transition section (for example Figure 6 as shown in the scheme).

[0077] In some embodiments, referring to Figure 2 , the branch outlet 2 is located upstream of the corresponding inner pipe structure 3a, and the spacing A between the upstream end of the inner pipe structure 3a and the corresponding branch outlet 2 in the axial direction of the manifold 100 is 0-10 mm. For example, 0 mm, 2 mm, 4 mm, 6 mm, 8 mm, 10 mm, etc. In this way, the inner pipe structure 3a is relatively close to the branch outlet 2 upstream thereof, and the flow of the manifold 100 into the branch outlet 2 will be more effectively affected by the inner pipe structure 3a, that is, the fluid can respond more quickly to the regulating action of the inner pipe structure 3a, thereby improving the response speed and dynamic performance of the entire fluid system, thereby facilitating the uniformity of fluid distribution.

[0078] The spacing A between the upstream end of the inner tube structure 3a and the corresponding branch outlet 2 in the axial direction of the manifold 100 refers to the minimum spacing between the inner tube structure 3a and the branch outlet 2 upstream thereof in the fluid flow direction of the manifold 100, for example, the spacing between the lower edge of the inner tube structure 3a and the upper edge of the branch outlet 2 when the inner tube structure 3a is located above the branch outlet 2.

[0079] In some embodiments, referring to Figure 1 The at least one sub-tube 4 is a choke sleeve 4x, the downstream end of the choke sleeve 4x is provided with a branch outlet 2 on the side wall thereof, and the upstream end is formed into an inner tube structure 3a. In this way, the choke sleeve 4x can serve as both the upstream tube 41 and the downstream tube 42, and can be mass-produced as a universal part, thereby reducing production costs.

[0080] For example, the at least two sub-tubes 4 are both choke sleeves 4x, and serve as the upstream tube 41 and the downstream tube 42, respectively. In this way, the upstream tube 41 and the downstream tube 42 can be used interchangeably during installation and maintenance, thereby increasing the convenience of installation and maintenance of the manifold 100 and reducing the operation difficulty and time cost of installation. Since the number of different types of parts is reduced, inventory management can be simplified, inventory costs can be reduced, and confusion and errors caused by a large number of different types of parts can be reduced.

[0081] In the embodiments of the present application, when there are a plurality of choke sleeves 4x, the structures of the plurality of choke sleeves 4x can be the same, but the lengths can be different. In this way, choke sleeves 4x of different lengths can be selected according to the parameters of the heat exchanger 1000 to form the manifold 100.

[0082] In some embodiments, referring to Figure 7 Among the at least two adjacent branch outlets 2, the inner diameter of the branch outlet 2 upstream (for example, the inner diameter D5 shown in the figure) is greater than the inner diameter of the branch outlet 2 downstream (for example, the inner diameter D6 shown in the figure). In this way, 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 upstream branch outlet 2 with a large inner diameter can reduce the resistance when the fluid passes through, so that the fluid can flow more smoothly into the upstream branch outlet 2, thereby balancing the flow distribution between the upstream and downstream branch outlets 2 to some extent and improving the uniformity of fluid distribution of each branch outlet 2 of the manifold 100.

[0083] For example, the inner diameters of the plurality of branch outlets 2 decrease in turn along the fluid flow direction.

[0084] In some embodiments, referring to Figure 7The manifold 100 is vertically arranged, and the lower part of the manifold 100 is provided with a pipe inlet 1, and a plurality of branch outlets 2 are arranged in sequence upward relative to the pipe inlet 1.

[0085] Therefore, under the action of gravity, the fluid in the manifold 100 is hindered from flowing excessively to the distal outlet 2a in the branch outlet 2 under the action of inertia, and the fluid in the manifold 100 is promoted to enter other branch outlets 2, thereby improving the uniformity of fluid distribution of each branch outlet 2 of the manifold 100.

[0086] It should be noted that the pipe inlet 1 is arranged at the lower part of the manifold 100, and the specific meaning of the lower part is not limited, for example, it can be the pipe end of the lower part. When the lower part of the manifold 100 is a straight pipe, the pipe inlet 1 can be located at the lowermost end of the manifold 100, and when the lower part of the manifold 100 is a bent pipe (for example, as shown in the drawings), the pipe inlet 1 can be located at the pipe end of the bent pipe. Figure 7

[0087] In some embodiments, referring to Figure 1 , the distal outlet 2a farthest from the pipe inlet 1 is provided with an inner pipe structure 3a at each branch outlet 2 except the distal outlet 2a. That is, the inner pipe structure 3a is necessarily arranged at each branch outlet 2 except the distal outlet 2a, but for the distal outlet 2a, the inner pipe structure 3a can be arranged or not arranged according to actual needs, that is, whether the inner pipe structure 3a is arranged at the distal outlet 2a is optional.

[0088] Therefore, when the inner pipe structure 3a is arranged at each branch outlet 2 except the distal outlet 2a, the refrigerant in each branch outlet 2 of the heat exchanger 1000 can be relatively uniform, thereby improving the problem of uneven heat exchange of the heat exchanger 1000 caused by excessive refrigerant in the branch corresponding to the distal outlet 2a and insufficient refrigerant in the branch corresponding to the proximal outlet, thereby improving the uniformity of fluid distribution in the manifold 100, thereby improving the heat exchange capacity of the heat exchanger 1000 using the manifold 100, improving the refrigeration and heating energy efficiency of the air conditioner 10000 using the heat exchanger 1000, and improving the overall operation efficiency of the air conditioner and the user's experience.

[0089] Of course, the present application is not limited thereto, for example, in other embodiments of the present application, according to actual needs, the inner pipe structure 3a can also not be arranged at some branch outlets 2.

[0090] Next, the heat exchanger 1000 according to the second aspect of the present application is described with reference to the drawings.

[0091] Referring to Figure 8 ​The heat exchanger 1000 comprises a heat exchanger body 1000c, an input pipe 1000a and an output pipe 1000b, the heat exchanger body 1000c has a plurality of parallel branches 1000c1 inside; the input pipe 1000a is the collecting pipe 100 according to any one of the embodiments of the first aspect of the present application, a plurality of branch outlets 2 are in one-to-one correspondence with the inlets of the plurality of parallel branches 1000c1 in communication; and the output pipe 1000b is in one-to-one correspondence with the outlets of the plurality of parallel branches 1000c1 in communication.

[0092] The heat exchanger 1000 according to the embodiments of the present application improves the uniformity of the refrigerant flow of the plurality of parallel branches 1000c1 of the heat exchanger 1000 by arranging the collecting pipe 100 of the first aspect, reduces the waste of the heat exchange area of the heat exchanger 1000, and improves the refrigeration and heating energy efficiency of the heat exchanger 1000.

[0093] The specific structure of the heat exchanger body 1000c is not limited, for example, in some embodiments of the present application, the form of the heat exchanger body 1000c is not limited, the heat exchanger body 1000c can include a plurality of stacked layers of fins, and a plurality of heat exchange pipes penetrating the plurality of layers of fins, each parallel branch 1000c1 includes a plurality of heat exchange pipes in series and / or parallel; or in some other embodiments of the present application, the heat exchanger body 1000c can also include a plurality of flat tubes, the flat tubes have a plurality of flow channels inside, and one flat tube constitutes one parallel branch 1000c1.

[0094] Next, referring to the drawings, the air conditioner 10000 according to the third aspect of the present application is described.

[0095] Referring to Figure 9 The air conditioner 10000 comprises the heat exchanger 1000 according to the second aspect of the present application.

[0096] The air conditioner 10000 according to the embodiments of the present application improves the overall operation efficiency of the air conditioner and the user's experience by arranging the heat exchanger 1000 of the second aspect.

[0097] The type of the air conditioner 10000 is not limited, for example, it can be an all-in-one air conditioner (such as a kitchen air conditioner, a mobile air conditioner, a window type air conditioner, etc.) or a split air conditioner (such as a split hanging machine, a split cabinet machine, etc.).

[0098] Other structures of the air conditioner 10000 according to the embodiments of the present application, such as air duct components and panel components, etc., and operations are known to those skilled in the art, and will not be described in detail here.

[0099] Referring to Figure 10, comparative example 1 is compared with example 1, each inner pipe structure 3a is cancelled, and the rest of the experimental parameters are the same. Figure 10 It can be seen from the experimental data that, compared with comparative example 1, the refrigeration performance coefficient EER (Energy Efficiency Ratio) of the air conditioner in example 1 is improved from 2.64 to 2.81; and the heating performance coefficient COP (coefficient of performance) of the air conditioner is improved from 3.27 to 3.30, so that the technical scheme of the air conditioner 10000 can improve the refrigeration and heating performance coefficients of the air conditioner 10000, and improve the energy efficiency of the air conditioner 10000.

[0100] The following disclosure provides many different embodiments or examples for implementing different structures of the present application. In order to simplify the disclosure of the present application, the components and settings of specific examples are described below. Of course, they are only examples, and the purpose is not to limit the present application. In addition, the present application can repeatedly refer to numbers and / or letters in different examples. Such repetition is for the purpose of simplification and clarity, and in itself does not indicate the relationship between the various embodiments and / or settings discussed. In addition, the present application provides examples of various specific processes and materials, but those skilled in the art can realize the applicability of other processes and / or the use of other materials.

[0101] In the description of the present application, 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" and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and therefore cannot be understood as indicating or implying that the devices or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the present application.

[0102] In addition, the terms "first", "second" are only for the purpose of description, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first", "second" can explicitly or implicitly include one or more of the features. In the description of the present application, the meaning of "multiple" is two or more, unless otherwise specifically limited.

[0103] In the present application, unless otherwise explicitly specified and limited, the terms "mounting", "connecting", "connecting", "fixing" and the like should be understood broadly, for example, it can be fixedly connected, or it can be detachably connected, or it can be integrated; it can be directly connected, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two elements or the interaction relationship between two elements. For ordinary skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0104] In the present application, unless otherwise explicitly specified and limited, the first feature is "on" or "under" the second feature. The first and second features can be in direct contact, or the first and second features can be in indirect contact through an intermediate medium. Moreover, the first feature "above", "above" and "above" the second feature can be directly above or obliquely above the first feature, or only indicate that the horizontal height of the first feature is higher than that of the second feature. The first feature "below", "below" and "below" the second feature can be directly below or obliquely below the first feature, or only indicate that the horizontal height of the first feature is less than that of the second feature.

[0105] In the description of the present application, the description of the terms "one embodiment", "some embodiments", "example", "specific example" or "some examples" means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present application. In the present application, the illustrative description of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art can combine and combine the different embodiments or examples described in the present application and the features of the different embodiments or examples without contradiction.

[0106] Although the embodiments of the present application have been shown and described, those skilled in the art can understand that various changes, modifications, replacements and variations can be made to these embodiments without departing from the principles and purposes of the present application, and the scope of the present application is defined by the claims and their equivalents.

Claims

1. A header characterized by, The manifold has a plurality of branch outlets arranged along an axial direction of the manifold, the manifold comprises at least two sub-pipes arranged along an axial direction of the manifold in sequence, at least two adjacent sub-pipes are an upstream pipe and a downstream pipe respectively, a downstream end of the upstream pipe is sleeved outside an upstream end of the downstream pipe, an end of the downstream pipe inserted into the upstream pipe is reduced in diameter in the middle to form an inner pipe structure, the upstream pipe comprises an upstream main pipe located upstream of the inner pipe structure, an inner diameter of the inner pipe structure is smaller than an inner diameter of the upstream main pipe, the downstream end of the upstream pipe is formed with the branch outlet, and fluid in the upstream pipe is sent out through the branch outlet and the inner pipe structure respectively.

2. The collector according to claim 1, characterized in that A ratio of the inner diameter of the inner pipe structure to an inner diameter of the corresponding branch outlet is 0.7-1.

2.

3. The collector according to claim 1, wherein The inner pipe structure is a constant-diameter pipe.

4. The collector according to claim 3, characterized in that The downstream pipe comprises a downstream main pipe, a tapered pipe and the inner pipe structure connected in sequence along a direction towards the upstream, the downstream main pipe and the inner pipe structure are constant-diameter pipes, a pipe diameter of the inner pipe structure is smaller than a pipe diameter of the downstream main pipe, and the pipe diameter of the tapered pipe gradually decreases along a direction from the downstream main pipe to the inner pipe structure.

5. The collector according to any one of claims 1-4, characterized in that An outer wall of the inner pipe structure is spaced apart from an inner wall of the upstream pipe to form a buffer space between the outer wall of the inner pipe structure and the inner wall of the upstream pipe, the buffer space is in communication with the upstream pipe and is isolated from the downstream pipe.

6. The collector according to claim 5, characterized in that The inner pipe structure is inserted into the upstream main pipe, and a ratio of a spacing between the outer wall of the inner pipe structure and the inner wall of the upstream main pipe to an inner diameter of the upstream main pipe is 0.05-0.

4.

7. The collector according to claim 5, wherein The upstream pipe comprises the upstream main pipe, a tapered pipe and a sleeve structure connected in sequence along a direction towards the downstream, the upstream main pipe and the sleeve structure are constant-diameter pipes, a pipe diameter of the sleeve structure is greater than a pipe diameter of the upstream main pipe, the pipe diameter of the tapered pipe gradually increases along a direction from the upstream main pipe to the sleeve structure, and the sleeve structure is sleeved outside the downstream pipe.

8. The collector according to claim 7, characterized in that An upstream end of the downstream pipe is formed with a clamping structure clamped outside a port of a downstream end of the upstream pipe.

9. The collector according to any one of claims 1-4, wherein, The upstream pipe comprises the upstream main pipe and a shape-fitting pipe, the shape-fitting pipe is located downstream of the upstream main pipe, a pipe diameter of the shape-fitting pipe is smaller than a pipe diameter of the upstream main pipe, an inner diameter of the shape-fitting pipe matches an outer diameter of the inner pipe structure, and the shape-fitting pipe is sleeved outside the inner pipe structure.

10. The collector according to claim 1, wherein The branch outlet provided at the downstream end of the upstream pipe is formed on a side wall of the upstream main pipe; and / or the branch outlet is located upstream of the corresponding inner pipe structure, and a spacing between an upstream end of the inner pipe structure and the corresponding branch outlet in an axial direction of the manifold is 0-10 mm.

11. The collector according to claim 1, wherein At least one of the sub-pipes is a flow-blocking sleeve pipe, the branch outlet is provided on a side wall of a downstream end of the flow-blocking sleeve pipe and an upstream end of the flow-blocking sleeve pipe is formed as the inner pipe structure.

12. The collector according to claim 1, wherein The manifold is provided with a pipe inlet, a farthest branch outlet of the plurality of branch outlets is a far-end outlet, and the inner pipe structure is provided at at least one branch outlet except the far-end outlet.

13. The collector according to claim 1, wherein The manifold is vertically arranged, a pipe inlet is arranged at the lower part of the manifold, and a plurality of branch outlets are arranged in sequence upward relative to the pipe inlet; and / or, in at least two adjacent branch outlets, the inner diameter of the upstream branch outlet is greater than the inner diameter of the downstream branch outlet.

14. A heat exchanger, characterized by The application relates to a heat exchanger. The heat exchanger body has a plurality of parallel branches; The input pipe is a manifold according to any one of claims 1-13, and a plurality of branch outlets are in one-to-one correspondence with the inlets of the plurality of parallel branches; The output pipe is in one-to-one correspondence with the outlets of the plurality of parallel branches.

15. An air conditioner characterized by comprising: The application relates to a heat exchanger. The heat exchanger body has a plurality of parallel branches;

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