Heat exchange tube structure and condenser for outdoor unit

Abstract

The present application discloses a heat exchange tube structure and a condenser for an outdoor unit. Pipelines in an upper region of the heat exchange tube structure define a plurality of condensation flow paths, and pipelines in a lower region of the heat exchange tube structure define a plurality of subcooling flow paths. An axial distance between a straight tube at the topmost end and a straight tube at the bottommost end in the condensation flow paths is L1, and an axial distance between a straight tube at the topmost end and a straight tube at the bottommost end in the subcooling flow paths is L2.

Description

Heat exchange pipe structure and condenser for outdoor unit

[0001] Related Applications

[0002] This application claims priority to the following Chinese patent application:

[0003] Application No. 2024110470172, filed on July 31, 2024, entitled "Heat exchange pipe structure and condenser for outdoor unit";

[0004] The aforementioned patents are hereby incorporated by reference in their entirety. TECHNICAL FIELD

[0005] The present application relates to the field of heat exchange equipment, in particular to a heat exchange pipe structure and a condenser for an outdoor unit. BACKGROUND

[0006] In a multi-split air conditioner, the design of the outdoor unit condenser is often based on the rated operating condition and full load operation to ensure uniform distribution of heat exchange medium flow in each flow path at maximum load, thereby maximizing heat exchange efficiency. However, in actual operating scenarios, the multi-split air conditioner is often in a partial load operating state, among which, the small load operating state accounts for a considerable proportion. At this time, the circulation amount of heat exchange medium in the outdoor unit condenser pipeline is low, which causes the heat exchange medium in the lower flow path to liquefy and fail to be discharged, resulting in liquid accumulation problem. Further, the circulation amount of heat exchange medium in the condenser is reduced, which makes it difficult for the multi-split air conditioner to achieve optimal performance. SUMMARY

[0007] The present application provides a heat exchange pipe structure and a condenser for an outdoor unit to solve the problem of heat exchange medium accumulation in the outdoor unit condenser during partial load operation of the multi-split air conditioner, which further affects the heat exchange efficiency.

[0008] In a first aspect, the embodiments of the present application provide a heat exchange pipe structure for a condenser of an outdoor unit, which comprises a plurality of groups of transverse pipe units and a plurality of transition bends.

[0009] In some embodiments, each of the transverse pipe units comprises a plurality of straight pipes, the plurality of straight pipes are arranged side by side in the vertical direction, and each of the straight pipes extends in the horizontal direction, and the plurality of groups of transverse pipe units are arranged side by side in the horizontal direction.

[0010] In some embodiments, the plurality of groups of transverse pipe units in the upper region are connected alternately to a part of the transition bends to form a plurality of condensation flow paths, and the plurality of groups of transverse pipe units in the lower region are connected alternately to another part of the transition bends to form a plurality of supercooling flow paths.

[0011] In some embodiments, the transition bends are located on the same side of two adjacent straight pipes; the outlets of the condensation flow paths are connected to the inlets of the supercooling flow paths to deliver the heat exchange medium processed by the condensation flow paths to the supercooling flow paths for supercooling; in each group of the cross pipe units, the straight pipe a1 at the top end of the condensation flow path and the straight pipe a2 at the bottom end of the condensation flow path, and the straight pipe b1 at the top end of the supercooling flow path and the straight pipe b2 at the bottom end of the supercooling flow path, the straight pipe b1 is located below and adjacent to the straight pipe a2, the axial distance between the straight pipe a1 and the straight pipe a2 in the vertical direction is L1, and the axial distance between the straight pipe b1 and the straight pipe b2 in the vertical direction is L2, 12.5%≤(L2 / L1)×100%≤25.0%.

[0012] In some embodiments, the flow process of each condensation flow path is S1, the flow process of each supercooling flow path is S2, and 25%≤(S2 / S1)×100%≤50.0%.

[0013] In some embodiments, the flow channel lengths inside the straight pipes of the groups of cross pipe units are equal, the distances between two adjacent straight pipes of each cross pipe unit in the vertical direction are equal, the distances between two adjacent groups of cross pipe units in the horizontal direction are equal, and the flow channel lengths inside the transition bends are equal.

[0014] In some embodiments, the number of straight pipes of each condensation flow path is greater than the number of straight pipes of each supercooling flow path.

[0015] In some embodiments, the inlet of each condensation flow path is located at the end of one of the straight pipes of the leftmost cross pipe unit, and the outlet is located at the end of one of the straight pipes of the rightmost cross pipe unit; each condensation flow path is connected from the inlet to the outlet through x1 straight pipes of the same cross pipe unit, and then through a transition bend to the same position of the straight pipe of the adjacent cross pipe unit, until the outlet of the condensation flow path is reached; wherein x1 straight pipes are x1 straight pipes arranged in the vertical direction, and 3≤x1≤5.

[0016] In some embodiments, in the leftmost cross pipe unit, the inlets of two adjacent condensation flow paths are located at the ends of two adjacent straight pipes, respectively.

[0017] In the rightmost cross pipe unit, the outlets of two adjacent condensation flow paths are located at the ends of two adjacent straight pipes, respectively.

[0018] In some embodiments, the heat exchange tube structure further comprises: a condensing inlet tube comprising a first main tube and a plurality of first branch tubes connected to the first main tube, the first branch tubes being connected to inlets of two adjacent condensing flow paths, or the first branch tubes being connected to an inlet of a condensing flow path; and a condensing outlet tube comprising a second main tube and a plurality of second branch tubes connected to the second main tube, the second branch tubes being connected to outlets of two adjacent condensing flow paths, or the second branch tubes being connected to an outlet of a condensing flow path.

[0019] In some embodiments, the heat exchange tube structure further comprises: a condensing outlet tube comprising a second main tube connected to outlets of a plurality of condensing flow paths; a supercooling outlet tube comprising a third main tube; a plurality of supercooling flow paths forming a plurality of supercooling units, each supercooling unit comprising a plurality of supercooling flow paths, the inlets of the plurality of supercooling flow paths being connected to the second main tube; and the heat exchange tube structure comprising 2m+1 groups of the transverse tube units, two of the supercooling flow paths being in each group, and the two supercooling flow paths in the same group being connected to the third main tube at the 2m+1th group of the transverse tube units.

[0020] In some embodiments, the supercooling flow paths of each supercooling unit comprise a first supercooling flow path and a second supercooling flow path; in the 1st group of the transverse tube units, the inlets of the first supercooling flow path and the second supercooling flow path are located at the ends of the straight tubes farthest from each other, and the inlet of the first supercooling flow path is located above the inlet of the second supercooling flow path; the first supercooling flow path and the second supercooling flow path each pass through x2 segments of the straight tubes in the same transverse tube unit from the inlet, and the last straight tube in the x2 segments of the straight tubes is connected to the straight tube in the adjacent transverse tube unit at the same position by a transition elbow; and in the mth group of the transverse tube units, the last straight tube in the x2 segments of the straight tubes of the first supercooling flow path and the second supercooling flow path is connected to a first adapter pipe, the first adapter pipe being connected to one of the straight tubes in the 2m+1th group of the transverse tube units, and in the 2m+1th group of the transverse tube units, the outlet of the first supercooling flow path and the outlet of the second supercooling flow path are gathered at the end of the last straight tube after passing through the x2 segments of the straight tubes, and form a first total outlet; wherein 2≤x2≤4.

[0021] In some embodiments, the supercooling flow paths of each of the supercooling units comprise a third supercooling flow path and a fourth supercooling flow path; in the m+1th group of the horizontal tube units, the inlet of the third supercooling flow path and the inlet of the fourth supercooling flow path are located at the ends of the straight tubes farthest from each other, and the inlet of the third supercooling flow path is located above the inlet of the fourth supercooling flow path; each of the third supercooling flow path and the fourth supercooling flow path is connected to the straight tube of the same horizontal tube unit after passing through x2 straight tubes from the inlet of the third supercooling flow path and the inlet of the fourth supercooling flow path, respectively, by a transition elbow pipe; and in the 2mth group of the horizontal tube units, the last straight tube of the x2 straight tubes of each of the third supercooling flow path and the fourth supercooling flow path is connected to a second transition pipe, and the second transition pipe is connected to another straight tube of the 2m+1th group of the horizontal tube units; and in the 2m+1th group of the horizontal tube units, the outlet of the third supercooling flow path and the outlet of the fourth supercooling flow path converge at the end of the last straight tube after passing through the x2 straight tubes, and form a second total outlet; wherein in the 2m+1th group of the horizontal tube units, the first total outlet and the second total outlet are located at the ends of the straight tubes farthest from each other, and the first total outlet is located above the second total outlet.

[0022] In some embodiments, the condensation outlet pipe comprises a plurality of third branch pipes connected to the second main pipe, and the supercooling outlet pipe comprises a plurality of fourth branch pipes connected to the third main pipe; the inlet of the first supercooling flow path and the inlet of the third supercooling flow path are connected to one of the third branch pipes, and the inlet of the second supercooling flow path and the inlet of the fourth supercooling flow path are connected to another of the third branch pipes; the outlet of the first supercooling flow path and the outlet of the second supercooling flow path are connected to one of the fourth branch pipes, and the outlet of the third supercooling flow path and the outlet of the fourth supercooling flow path are connected to another of the fourth branch pipes.

[0023] In some embodiments, two adjacent groups of the horizontal tube units are arranged in a vertical staggered manner; and / or, the horizontal tube units have a windward side and a leeward side, the heat exchange tube structure comprises a condensation inlet pipe, the condensation inlet pipe comprises a first main pipe connected to the inlets of a plurality of the condensation flow paths, the first main pipe is arranged on the leeward side of a plurality of the horizontal tube units, and the second main pipe and the third main pipe are arranged on the windward side of a plurality of the horizontal tube units.

[0024] In some embodiments, the number of the condensation flow paths is n1, the number of the supercooling flow paths is n2, and the heat exchange tube structure satisfies at least one of the following conditions: (1) n1>n2; (2) 7≤n1≤11; (3) 7≤n2≤11.

[0025] In a second aspect, the embodiments of the present application further provide a condenser for an outdoor unit, comprising the heat exchange pipe structure, and a plurality of fins arranged along the extension direction of the straight pipes, the fins having a plurality of fin holes, and the straight pipes of the plurality of horizontal pipe units are arranged in the fin holes one by one.

[0026] Based on the heat exchange pipe structure and the condenser for an outdoor unit, the pipe in the upper region is configured as a condensing flow path, and the pipe in the lower region is configured as a supercooling flow path. By controlling 12.5%≤(L2 / L1)×100%≤25.0%, the proportion of the condensing flow path in the upper region and the supercooling flow path in the lower region is appropriate. Under the premise that the circulation amount of the heat exchange medium is unchanged in each load state, the heat exchange medium distributed in each condensing flow path is increased in the part-load operating state in the heat exchange pipe structure of the present application. The heat exchange medium in each condensing flow path converges and then enters the supercooling flow path, so that there is enough heat exchange medium in the supercooling flow path in the lower region. Therefore, the liquid accumulation problem of the heat exchange pipe structure is improved, and the utilization efficiency of the condenser is improved. In the present application, the supercooling flow path is provided to further reduce the temperature of the liquid heat exchange medium at the outlet of the heat exchange pipe structure, avoid the insufficient supercooling degree of the heat exchange medium, and slow down the vaporization of the heat exchange medium flowing out of the outdoor unit condenser in the long pipe under the installation characteristics of the multi-split air conditioner long pipe and high drop. BRIEF DESCRIPTION OF DRAWINGS

[0027] In order to more clearly illustrate the technical solutions of the embodiments of the present application or the prior art, the drawings needed in the embodiments or the prior art description will be briefly introduced below. Obviously, the drawings in the following description are only some embodiments of the present application, and other drawings can be obtained by those skilled in the art without creative labor.

[0028] FIG. 1 is a structural schematic diagram of a heat exchange pipe structure according to an embodiment of the present application;

[0029] FIG. 2 is a structural schematic diagram of another heat exchange pipe structure according to an embodiment of the present application;

[0030] FIG. 3 is a structural schematic diagram of the connection between a transition bend pipe and a straight pipe in a condensing pipe according to an embodiment of the present application;

[0031] FIG. 4 is a structural schematic diagram of a condensing flow path according to an embodiment of the present application;

[0032] FIG. 5 is a structural schematic diagram of another condensing flow path according to an embodiment of the present application;

[0033] FIG. 6 is a structural schematic diagram of a first supercooling flow path according to an embodiment of the present application;

[0034] Fig. 7 is a structural schematic diagram of a second subcooling flow path according to an embodiment of the present application;

[0035] Fig. 8 is a structural schematic diagram of a third subcooling flow path according to an embodiment of the present application;

[0036] Fig. 9 is a structural schematic diagram of a fourth subcooling flow path according to an embodiment of the present application;

[0037] Reference signs:

[0038] 1, heat exchange tube structure; 10, condensation flow path; 20, subcooling flow path; 30, condensation inlet tube; 40, condensation outlet tube; 50, subcooling outlet tube; 21, first subcooling flow path; 22, second subcooling flow path; 23, third subcooling flow path; 24, fourth subcooling flow path; 31, first main tube; 32, first branch tube; 41, second branch tube; 42, second main tube; 43, third branch tube; 51, third main tube; 52, fourth branch tube; 100, transition elbow; 200, straight tube; 201, first adapter tube; 202, second adapter tube; X, air flow direction.

[0039] The implementation, functional features and advantages of the present application will be further described with reference to the embodiments and the accompanying drawings. Embodiments of the present application

[0040] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present application. Obviously, the described embodiments are only some of the embodiments of the present application, but not all the embodiments of the present application. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative work fall within the scope of protection of the present application.

[0041] It should be noted that all directional indications (such as up, down, left, right, front, back, etc.) in the embodiments of the present application are only used to explain the relative positional relationship, movement condition, etc. between components in a certain posture (as shown in the drawings), and if the certain posture changes, the directional indications also change accordingly.

[0042] In addition, the description such as “first”, “second” and the like in the present application is only for the purpose of description, and cannot be understood as indicating or implying the relative importance of the indicated technical features or implicitly indicating the number of the indicated technical features. Therefore, the features limited by “first”, “second” can explicitly or implicitly include at least one of the features. In the description of the present application, the meaning of “multiple” is at least two, for example, two, three, etc., unless otherwise specifically limited.

[0043] In the present application, unless otherwise expressly specified and limited, the terms "connection", "fixation" and the like shall be understood in a broad sense, for example, "fixation" can be fixed connection, or detachable connection, or integral; can be mechanical connection, or electrical connection; can be direct connection, or indirect connection through intermediate medium, can be internal communication of two elements or interaction relationship of two elements, unless otherwise expressly limited. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0044] In addition, the technical solutions of various embodiments of the present application can be combined with each other, but it must be based on the fact that a person skilled in the art can realize it, when the combination of technical solutions appears contradictory or unachievable, it should be considered that the combination of technical solutions does not exist, nor is it within the scope of protection claimed in the present application.

[0045] In a multi-connected air conditioner, the flow path design of the outdoor unit condenser is often based on the rated operating condition and full load operation condition to ensure that the heat exchange medium flow is evenly distributed in each flow path at maximum load, thereby maximizing the heat exchange efficiency. This flow path design has good condensing effect under full load or high load operating conditions, but under small load refrigeration conditions, such as 25%, 20% and lower load conditions, due to the low circulation amount of heat exchange medium, the gravitational pressure drop has a great influence on the distribution of heat exchange medium in each condensing flow path, and the amount of heat exchange medium in each condensing flow path from top to bottom gradually decreases. Among them, the amount of heat exchange medium in the lower condensing flow path is extremely small, and the condensed and liquefied heat exchange medium cannot flow out of the condensing flow path and accumulate in the pipeline, affecting the heat exchange effect of the condenser.

[0046] Based on the above problems of the related art, the present application provides a heat exchange pipe structure and a condenser for an outdoor unit. The pipeline in the lower region of the heat exchange pipe structure is configured as a plurality of subcooling flow paths, and the outlets of the plurality of condensing flow paths above the heat exchange pipe structure are in communication with the inlets of the plurality of subcooling flow paths, so as to transport the heat exchange medium subjected to condensing treatment in the plurality of condensing flow paths to the plurality of subcooling flow paths for subcooling treatment. In this way, the heat exchange medium in the plurality of condensing flow paths flows into the plurality of subcooling flow paths, so that there is enough heat exchange medium in the pipeline at the bottom of the heat exchange pipe structure to improve the liquid accumulation problem caused by too little heat exchange medium. By controlling the ratio of the subcooling flow path in the lower region to the condensing flow path in the upper region in the vertical direction, the appropriate amount of heat exchange medium can be distributed in each condensing flow path under small load operation, avoiding liquid accumulation, and at the same time avoiding excessive length of the subcooling flow path, which causes large pressure loss, so that the outdoor unit condenser has good performance.

[0047] Please refer to Fig. 1-2, Fig. 1 is a structure diagram of a heat exchange pipe structure 1 according to an embodiment of the present application, Fig. 2 is a structure diagram of another heat exchange pipe structure 1 according to an embodiment of the present application, the heat exchange pipe structure 1 comprises multiple groups of horizontal pipe units and multiple transition bend pipes 100, the multiple groups of horizontal pipe units are arranged side by side along the horizontal direction, each horizontal pipe unit comprises multiple straight pipes 200 extending along the horizontal direction, the multiple straight pipes 200 are arranged side by side along the vertical direction, and the transition bend pipe 100 is connected to the same side of two straight pipes 200. Among them, the multiple straight pipes 200 in the upper region of the multiple groups of horizontal pipe units are alternately connected with a part of the transition bend pipes 100 to form multiple condensation flow paths 10, and the multiple straight pipes 200 in the lower region of the multiple groups of horizontal pipe units are alternately connected with another part of the transition bend pipes 100 to form multiple supercooling flow paths 20. In the embodiment of the present application, the outlets of the multiple condensation flow paths 10 and the inlets of the multiple supercooling flow paths 20 are communicated to transport the heat exchange medium processed by the multiple condensation flow paths 10 to the multiple supercooling flow paths 20 for supercooling processing. In the present application, the region below the heat exchange pipe structure 1 is configured as the supercooling flow path 20, on the one hand, under the premise that the circulation amount of the heat exchange medium in each load state is unchanged, the amount of the heat exchange medium distributed in each condensation flow path 10 is increased in the partial load operation state, and on the other hand, the liquid heat exchange medium in the multiple condensation flow paths 10 converges and then enters the supercooling flow path 20, which can ensure that there is sufficient heat exchange medium in the pipeline at the bottom of the heat exchange pipe structure 1. In this way, in the partial load operation state, especially in the small load operation state, liquid accumulation in the heat exchange pipe structure 1 of the air conditioning system caused by too little heat exchange medium is avoided, and the heat exchange performance of the air conditioning system in the partial load operation state is improved.

[0048] It should be noted that in the structure diagrams of the whole and part of the heat exchange pipe structure 1 in the embodiments of the present application, in order to facilitate the description of the arrangement mode of each flow path pipeline, each straight pipe 200 is schematically shown in a plane perpendicular to the extension direction of the straight pipe 200, and in the actual visual angle, the pipe diameter of the straight pipe 200 is the same as that of the transition bend pipe 100, and the straight pipe 200 cannot be directly seen in the above-mentioned visual angle diagram.

[0049] In an embodiment of the present application, two adjacent groups of horizontal pipe units are arranged in the vertical direction. A part of the transition bend pipes 100 are connected to the same side of two adjacent straight pipes 200 in the same group of horizontal pipe units to communicate the straight pipes 200 in the same group of horizontal pipe units, and another part of the transition bend pipes 100 are connected to the same side of two adjacent straight pipes 200 in two adjacent groups of horizontal pipe units to communicate the straight pipes 200 in the two adjacent groups of horizontal pipe units.

[0050] As shown in FIGS. 3-5, FIG. 3 is a schematic view of the connection structure of the transition bend 100 and the straight pipe 200 in the condensing flow path 10 according to an embodiment of the present application, FIG. 4 is a schematic view of the structure of a condensing flow path 10 according to an embodiment of the present application, and FIG. 5 is a schematic view of the structure of another condensing flow path 10 according to an embodiment of the present application. In the present embodiment, in each group of horizontal pipe units, the straight pipe 200 at the top end of the condensing flow path 10 is a straight pipe a1, the straight pipe 200 at the bottom end is a straight pipe a2, the straight pipe 200 at the top end of the subcooling flow path 20 is a straight pipe b1, and the straight pipe 200 at the bottom end is a straight pipe b2. The straight pipe b1 is arranged below and adjacent to the straight pipe a2. In the vertical direction, the axial spacing between the straight pipe a1 and the straight pipe a2 is L1, the axial spacing between the straight pipe b1 and the straight pipe b2 is L2, and 12.5%≤(L2 / L1)×100%≤25.0%. It can be understood that the heat exchange pipe structure of the present embodiment configures the upper region of the pipe as the condensing flow path and the lower region of the pipe as the subcooling flow path. By controlling 12.5%≤(L2 / L1)×100%≤25.0%, the proportion of the condensing flow path 10 in the upper region and the subcooling flow path 20 in the lower region is appropriate, so as to ensure that the heat exchanger has good use performance. If (L2 / L1)×100%<12.5%, the proportion of the lower region in the heat exchange pipe structure 1 is too small, and the heat exchange medium in the condensing flow path 10 at the relatively bottom end of the plurality of condensing flow paths 10 in the upper region is still small. The improvement effect on the liquid accumulation problem under the part load operation state is not good. If (L2 / L1)×100%>25.0%, the proportion of the subcooling flow path 20 in the heat exchange pipe structure 1 is too large, the process length of the subcooling flow path 20 is too long, which leads to large pressure loss, the proportion of the condensing flow path 10 is small, the amount of heat exchange medium that can be accommodated by the plurality of condensing flow paths 10 is reduced, and then the refrigeration capacity of the outdoor unit condenser is reduced.

[0051] In the related art, in order to adapt to diversified installation scenes, the pipe between the outdoor unit and the indoor unit of the multi-split air conditioner has the characteristics of long pipe and high drop. Therefore, the liquid heat exchange medium obtained after refrigeration of the outdoor unit condenser must maintain a considerable subcooling degree, otherwise it is likely to vaporize by absorbing environmental heat when passing through the long pipe, which affects the refrigeration effect of the multi-split air conditioner. In the present embodiment, the subcooling flow path 20 is arranged in the lower region of the heat exchange pipe structure 1, which can further reduce the temperature of the liquid heat exchange medium after condensation, so as to ensure that the heat exchange medium flowing out of the outdoor unit condenser maintains sufficient subcooling degree. In an embodiment of the present application, the process of each condensing flow path 10 is S1, the process of each subcooling flow path 20 is S2, and 25%≤(S2 / S1)×100%≤50.0%. By controlling S2 / S1 to satisfy the above range, it is ensured that the subcooling flow path 20 has sufficient process length to achieve the required subcooling degree, while avoiding unnecessary pressure loss and cost increase caused by too long subcooling flow path 20.

[0052] Further, the flow channel lengths inside the straight pipes 200 of the multiple groups of the cross pipe units are equal, the intervals of the adjacent two straight pipes 200 of each cross pipe unit in the vertical direction are equal, the intervals of the adjacent two groups of the cross pipe units in the horizontal direction are equal, and the flow channel lengths inside the multiple transition bend pipes 100 are equal. In a specific implementation, the number of the straight pipes 200 of each condensation flow path 10 is greater than the number of the straight pipes 200 of each supercooling flow path 20, and the flow lengths of the condensation flow path 10 and the supercooling flow path 20 and the relative length relationship between the two flow lengths are controlled by controlling the number of the straight pipes 200.

[0053] It should be noted that in the embodiments of the present application, the pipe arrangement modes inside the multiple groups of the cross pipe units are the same, the pipe arrangement modes between the multiple groups of the cross pipe units are the same, and the fins in the outdoor unit condenser are uniformly arranged. Therefore, the flow lengths of the flow paths also reflect the heat exchange areas of the corresponding flow paths. In the embodiments of the present application, the heat exchange area M1 of the condensation area (including the multiple condensation flow paths and the fins connected thereto) and the heat exchange area M2 of the supercooling area (including the multiple supercooling flow paths and the fins connected thereto), and the ratio of M2 / M1 is closely related to the ratio of L1 / L2, and 12.5%≤(M2 / M1)×100%≤25.0%.

[0054] In an embodiment of the present application, the multiple condensation flow paths 10 are arranged from top to bottom, the inlet of each condensation flow path 10 is located at the end of one of the straight pipes 200 of the leftmost cross pipe unit, and the outlet is located at the end of one of the straight pipes 200 of the rightmost cross pipe unit. Each condensation flow path 10 is connected from the inlet to the straight pipe 200 at the same position in the adjacent cross pipe unit through one of the transition bend pipes 100 after passing through x1 straight pipes in the same cross pipe unit, until the outlet of the condensation flow path 10 is reached. Wherein, the x1 straight pipes are x1 straight pipes arranged in sequence in the vertical direction, and 3≤x1≤5. It should be noted that the smaller the pipe diameter of the straight pipe 200, the higher the flow speed of the heat exchange medium inside the straight pipe 200, and the greater the flow resistance. Therefore, a shorter flow length needs to be matched to maintain the fluid pressure and flow of the heat exchange medium. Under the premise that the number of the straight pipes 200 in each cross pipe unit is constant, the greater the value of x1, the fewer the number of the condensation flow paths 10 in the heat exchange pipe structure 1, and the longer the flow length of each condensation flow path 10. Therefore, the value of x1 in the embodiments of the present application is related to the pipe diameter of the straight pipe 200, and when the pipe diameter of the straight pipe 200 is larger, the value of x1 is also allowed to be larger.

[0055] Optionally, in the heat exchange pipe structure 1 as shown in FIG. 1, three groups of cross pipe units are provided, the pipe diameter of the straight pipe 200 is φ5, and the value of x1 can be 4.

[0056] In an embodiment of the present application, in the leftmost cross-pipe unit, the inlets of the two adjacent condensation flow paths 10 are located at the ends of the two adjacent straight pipes 200; in the rightmost cross-pipe unit, the outlets of the two adjacent condensation flow paths 10 are located at the ends of the two adjacent straight pipes 200. The inlet temperatures of the condensation flow paths 10 are similar, and as the condensation process proceeds, the temperatures of the straight pipes 200 adjacent to each other in the two adjacent condensation flow paths 10 also remain similar in the vertical direction. This design helps to reduce the area where the temperature gradient inside the heat exchange pipe structure 1 is too large, and improves the uniformity of the overall temperature distribution.

[0057] The heat exchange pipe structure 1 further includes a condensation inlet pipe 30 and a condensation outlet pipe 40. The condensation inlet pipe 30 includes a first main pipe 31 and a plurality of first branch pipes 32 connected to the first main pipe 31, and the heat exchange medium in the first main pipe 31 enters each condensation flow path 10 through the plurality of first branch pipes 32. In the present application, if the inlets of the two adjacent condensation flow paths 10 are located at the ports of the two adjacent straight pipes 200, the two condensation flow paths 10 can be connected to the same first branch pipe 32 to reduce the number of first branch pipes 32 and lower the cost. At this time, the side of the first branch pipe 32 away from the first main pipe 31 is provided with two connection ports, and the two connection ports are respectively connected to the inlets of the two adjacent condensation flow paths 10. In particular, in the upper region of the heat exchange pipe structure 1, the inlet of the first condensation flow path 10 from top to bottom and / or the inlet of the last condensation flow path 10 are not adjacent to the inlets of the other condensation flow paths 10. At this time, the first branch pipe 32 connected thereto is provided with only one connection port on the side away from the first main pipe 31, and is connected to the inlet of only one condensation flow path 10.

[0058] The condensation outlet pipe 40 includes a plurality of second branch pipes 41 and a second main pipe 42 connected to the plurality of second branch pipes 41, and the condensed heat exchange medium in the plurality of second branch pipes 41 flows into the second main pipe 42 and then flows into the supercooling flow path 20 through the second branch pipes 41. Similarly, if the outlets of the two adjacent condensation flow paths 10 are located at the ports of the two adjacent straight pipes 200, the two condensation flow paths 10 can be connected to the same second branch pipe 41 to reduce the number of second branch pipes 41 and lower the cost. Among the plurality of second branch pipes 41, at least part of the second branch pipes 41 are connected to the outlets of the two adjacent condensation flow paths 10. In particular, the inlet of the first condensation flow path 10 from top to bottom and / or the inlet of the last condensation flow path 10 can not be adjacent to the inlets of the other condensation flow paths 10. Correspondingly, the second branch pipe 41 connected thereto is connected to the outlet of only one condensation flow path 10.

[0059] It should be noted that when the multi-connected air conditioner is in full load or large load operation state, the flow of the heat exchange medium of the plurality of second branch pipes 41 converging to the second main pipe 42 is large, at this time, if only one subcooling flow path 20 is arranged in the lower area, the flow length of the subcooling flow path 20 will be longer, and the pressure loss of the heat exchange medium in one subcooling flow path 20 is large. In the embodiment of the application, a plurality of subcooling flow paths 20 are arranged to reduce the flow length of a single subcooling flow path 20, reduce the flow of the heat exchange medium in each subcooling flow path 20, and improve the flow efficiency of the heat exchange medium in the lower area.

[0060] In the embodiment of the application, the heat exchange pipe structure 1 further comprises a subcooling outlet pipe 50, the subcooling outlet pipe 50 comprises a third main pipe 51, a plurality of subcooling flow paths 20 form a plurality of subcooling units, each subcooling unit comprises a plurality of subcooling flow paths 20, and the inlets of the plurality of subcooling flow paths 20 are in communication with the second main pipe 42. The heat exchange pipe structure 1 comprises 2m+1 groups of transverse pipe units, the plurality of subcooling flow paths 20 are two by two as a group, and the two subcooling flow paths 20 in the same group converge at the 2m+1th group of transverse pipe units and are in communication with the third main pipe 51.

[0061] The condensing outlet pipe 40 further comprises a plurality of third branch pipes 43 in communication with the second main pipe 42, and the subcooling outlet pipe 50 comprises a plurality of fourth branch pipes 52 in communication with the third main pipe 51. Please refer to FIGS. 6-9, FIG. 6 is a structural schematic diagram of a first subcooling flow path 21 according to an embodiment of the application, FIG. 7 is a structural schematic diagram of a second subcooling flow path 22 according to an embodiment of the application, FIG. 8 is a structural schematic diagram of a third subcooling flow path 23 according to an embodiment of the application, and FIG. 9 is a structural schematic diagram of a fourth subcooling flow path 24 according to an embodiment of the application. The subcooling unit comprises the first subcooling flow path 21, the second subcooling flow path 22, the third subcooling flow path 23, and the fourth subcooling flow path 24, wherein the inlet of the first subcooling flow path 21 and the inlet of the third subcooling flow path 23 are commonly in communication with one of the third branch pipes 43, and the inlet of the second subcooling flow path 22 and the inlet of the fourth subcooling flow path 24 are commonly in communication with another third branch pipe 43; the outlet of the first subcooling flow path 21 and the outlet of the second subcooling flow path 22 are commonly in communication with one of the fourth branch pipes 52, and the outlet of the third subcooling flow path 23 and the outlet of the fourth subcooling flow path 24 are commonly in communication with another third branch pipe 43. The heat exchange medium after condensation of the second main pipe 42 is once divided into a plurality of third branch pipes 43, and after passing through the third branch pipe 43, it is twice divided into two subcooling flow paths 20, and the flow of the heat exchange medium in each subcooling flow path 20 is reduced after multiple divisions. The number of pipelines in the lower area is limited, and in the embodiment of the application, the second half of the flow of every two subcooling flow paths 20 is converged to ensure the flow length of each subcooling flow path 20 and ensure that the heat exchange medium passing through the subcooling flow path 20 has sufficient subcooling degree.

[0062] As shown in FIGS. 6-7, each supercooling unit's supercooling flow path 20 includes a first supercooling flow path 21 and a second supercooling flow path 22; in the first group of cross-pipe units, the inlet of the first supercooling flow path 21 and the inlet of the second supercooling flow path 22 are located at the ends of the straight pipes 200 farthest from each other, and the inlet of the first supercooling flow path 21 is located above the inlet of the second supercooling flow path 22; each of the first supercooling flow path 21 and the second supercooling flow path 22, from its inlet, is connected to the straight pipe 200 in the same position in the adjacent cross-pipe unit by a transition elbow 100 after passing through x2 straight pipes in the same cross-pipe unit; and in the mth group of cross-pipe units, the last straight pipe 200 in the x2 straight pipes of each of the first supercooling flow path 21 and the second supercooling flow path 22 is connected to a first adapter pipe 201, and the first adapter pipe 201 is connected to one of the straight pipes 200 in the 2m+1th group of cross-pipe units, and in the 2m+1th group of cross-pipe units, the outlet of the first supercooling flow path 21 and the outlet of the second supercooling flow path 22 are located at the ends of the last straight pipe 200 after passing through x2 straight pipes; wherein 2≤x2≤4.

[0063] As shown in FIGS. 8-9, each supercooling unit's supercooling flow path 20 includes a third supercooling flow path 23 and a fourth supercooling flow path 24; in the m+1th group of cross-pipe units, the inlet of the third supercooling flow path 23 and the inlet of the fourth supercooling flow path 24 are located at the ends of the straight pipes 200 farthest from each other, and the inlet of the third supercooling flow path 23 is located above the inlet of the fourth supercooling flow path 24; each of the third supercooling flow path 23 and the fourth supercooling flow path 24, from its inlet, is connected to the straight pipe 200 in the same position in the adjacent cross-pipe unit by a transition elbow 100 after passing through x2 straight pipes in the same cross-pipe unit; and in the 2mth group of cross-pipe units, the last straight pipe 200 in the x2 straight pipes of each of the third supercooling flow path 23 and the fourth supercooling flow path 24 is connected to a second adapter pipe 202, and the second adapter pipe 202 is connected to another straight pipe 200 in the 2m+1th group of cross-pipe units, and in the 2m+1th group of cross-pipe units, the outlet of the third supercooling flow path 23 and the outlet of the fourth supercooling flow path 24 are located at the ends of the last straight pipe 200 after passing through x2 straight pipes.

[0064] The outlets of the first supercooling flow path 21 and the second supercooling flow path 22 are defined as the first total outlet, and the outlets of the third supercooling flow path 23 and the fourth supercooling flow path 24 are defined as the second total outlet, and in the 2m+1th group of cross-pipe units, the first total outlet and the second total outlet are located at the ends of the straight pipes farthest from each other, and the first total outlet is located above the second total outlet.

[0065] In the heat exchange pipe structure 1 as shown in FIG. 1, three groups of transverse pipe groups are provided, i.e. m = 1, and the value of x2 is 1. The inlets of the first subcooling flow path 21 and the second subcooling flow path 22 are located in the first group of transverse pipe group units, the inlets of the third subcooling flow path 23 and the fourth subcooling flow path 24 are located in the second group of transverse pipe units, and the first total outlet and the second total outlet are both located in the third group of transverse pipe units.

[0066] In an embodiment of the present application, the transverse pipe unit has a windward side and a leeward side. In the heat exchange pipe structure 1, the first main pipe 31 in the condensation inlet pipe 30 is arranged on the leeward side of the plurality of transverse pipe units, and the second main pipe 42 of the condensation outlet pipe 40 is arranged on the windward side of the plurality of transverse pipe units. In this way, in the horizontal direction, the overall flow direction of the heat exchange medium in each condensation flow path 10 is opposite to the air flow direction X. This counter-flow arrangement is conducive to improving the heat exchange efficiency. Further, the third main pipe 51 in the subcooling outlet pipe 50 is arranged on the windward side of the plurality of transverse pipe units. Although the second main pipe 42 is arranged on the windward side of the plurality of transverse pipe units, in the embodiment of the present application, the inlets of each subcooling flow path 20 are arranged on the leeward side of the plurality of transverse pipe units and are communicated with the second main pipe 42 through a plurality of third branch pipes 43. In this way, each subcooling flow path 20 is also arranged in counter-flow.

[0067] In an embodiment of the present application, the number of condensation flow paths 10 is n1, and the number of subcooling flow paths 20 is n2. The heat exchange pipe structure 1 satisfies at least one of the following conditions: (1) n1 > n2; (2) 7 ≤ n1 ≤ 11; (3) 7 ≤ n2 ≤ 11. It can be understood that the number of pipes in the upper region of the heat exchange pipe structure 1 is more than the number of pipes in the lower region. Under this premise, if the number of subcooling flow paths 20 in the lower region is too large, the flow process of each subcooling flow path 20 will be short, and it is difficult to ensure that the temperature of the heat exchange medium at the outlet of the heat exchange pipe structure 1 is low enough. Taking the heat exchange pipe structure 1 as shown in FIG. 1 as an example, the number of condensation flow paths 10 is 9, and the number of subcooling flow paths 20 is 8.

[0068] The present application also provides a condenser for an outdoor unit, which comprises the above-mentioned heat exchange pipe structure 1 and a plurality of fins. The plurality of fins are arranged in a spaced manner along the extension direction of the straight pipes. The fins have a plurality of fin holes, and the straight pipes of the plurality of transverse pipe units are arranged in the fin holes one by one.

[0069] In the condenser of the outdoor unit, the inlet of the heat exchange pipe structure 1 is communicated with the compressor, and the outlet of the heat exchange pipe structure 1 is connected with the heat exchanger of the indoor unit through a throttling device. In the refrigeration process, the gaseous heat exchange medium discharged by the compressor enters each condensation flow path 10 through the condensation inlet pipe 30 of the inlet of the heat exchange pipe structure 1 to be condensed, forming liquid heat exchange medium. Then, the liquid heat exchange medium is further subcooled in each subcooling flow path 20 and then enters the heat exchanger of the indoor unit through the throttling device at the outlet of the heat exchange pipe structure 1.

[0070] The above description is merely a preferred embodiment of this application and does not limit the patent scope of this application. Any equivalent structural transformations made based on the concept of this application and the contents of the specification and drawings of this application, or direct / indirect applications in other related technical fields, are included within the patent protection scope of this application.

Claims

1. A heat exchange tube structure for use in the condenser of an outdoor unit, wherein, include: Multiple sets of horizontal tube units, each of the horizontal tube units includes multiple straight tubes, the multiple straight tubes are arranged side by side in the vertical direction, and each of the straight tubes extends in the horizontal direction, the multiple sets of horizontal tube units are arranged side by side in the horizontal direction; Multiple transition bends, multiple sets of the horizontal pipe units located in the upper region, multiple segments of the straight pipes and a portion of the transition bends are alternately connected to form multiple condensation flow paths, and multiple sets of the horizontal pipe units located in the lower region, multiple segments of the straight pipes and another portion of the transition bends are alternately connected to form multiple subcooling flow paths; wherein, each of the transition bends is located on the same side of two adjacent segments of the straight pipes; The outlets of the multiple condensation flow paths are connected to the inlets of the multiple subcooling flow paths, so as to transport the heat exchange medium after condensation treatment by the multiple condensation flow paths to the multiple subcooling flow paths for subcooling treatment. In each group of horizontal tube units, the straight tube at the top of the condensation flow path is straight tube a1, and the straight tube at the bottom is straight tube a2. Similarly, the straight tube at the top of the subcooling flow path is straight tube b1, and the straight tube at the bottom is straight tube b2. Straight tube b1 is located below and adjacent to straight tube a2. In the vertical direction, the axial distance between straight tube a1 and straight tube a2 is L1, and the axial distance between straight tube b1 and straight tube b2 is L2. 12.5%≤(L2 / L1)×100%≤25.0%.

2. The heat exchange tube structure according to claim 1, wherein, The flow path of each condensation flow path is S1, and the flow path of each subcooling flow path is S2, with 25% ≤ (S2 / S1) × 100% ≤ 50.0%.

3. The heat exchange tube structure according to claim 2, wherein, The flow channel lengths inside the straight pipes of the multiple sets of horizontal pipe units are equal, and the vertical spacing between two adjacent straight pipe segments of each horizontal pipe unit is equal, the horizontal spacing between two adjacent sets of horizontal pipe units is equal, and the flow channel lengths inside the multiple transition bends are equal. The number of straight pipes in each of the condensation flow paths is greater than the number of straight pipes in each of the subcooling flow paths.

4. The heat exchange tube structure according to claim 1, wherein, The inlet of each of the condensation flow paths is located at the end of one of the straight pipes of the leftmost horizontal pipe unit, and the outlet is located at the end of one of the straight pipes of the rightmost horizontal pipe unit. Each of the condensation flow paths, starting from its inlet, passes through the x1 segment of the straight pipe of the same horizontal pipe unit, and is then connected by the last straight pipe in the x1 segment to the straight pipe of the same position in the adjacent horizontal pipe unit via a transition bend, until it reaches the outlet of the condensation flow path. Wherein, the straight pipes in segment x1 are the straight pipes arranged sequentially along the vertical direction, and 3≤x1≤5.

5. The heat exchange tube structure according to claim 4, wherein, In the leftmost horizontal tube unit, the inlets of the two adjacent condensation flow paths are located at the ends of the two adjacent straight tubes, respectively; In the rightmost horizontal tube unit, the outlets of the two adjacent condensation flow paths are located at the ends of the two adjacent straight tubes.

6. The heat exchange tube structure according to claim 4 or 5, wherein, The heat exchanger tube structure also includes: The condenser inlet pipe includes a first main pipe and a plurality of first branch pipes connected to the first main pipe. The first branch pipes are connected to the inlets of two adjacent condenser flow paths, or the first branch pipes are connected to the inlet of one of the condenser flow paths. The condensate outlet pipe includes a plurality of second branch pipes and a second main pipe connected to the plurality of second branch pipes. The second branch pipes are connected to the outlets of two adjacent condensate flow paths, or the second branch pipes are connected to the outlet of one of the condensate flow paths.

7. The heat exchange tube structure according to claim 1, wherein, The heat exchanger tube structure also includes: The condensate outlet pipe includes a second main pipe connected to the outlets of the plurality of said condensate flow paths; Subcooled outlet pipe, including the third main pipe; Multiple subcooling flow paths form multiple subcooling units, and each subcooling unit includes multiple subcooling flow paths, the inlets of which are all connected to the second main pipe; The heat exchange tube structure includes 2m+1 sets of horizontal tube units, and multiple subcooling flow paths are grouped in pairs. The two subcooling flow paths in the same group intersect at the 2m+1 set of horizontal tube units and are connected to the third main tube.

8. The heat exchange tube structure according to claim 7, wherein, The subcooling flow path of each of the subcooling units includes a first subcooling flow path and a second subcooling flow path; In the first group of horizontal tube units, the inlet of the first subcooling flow path and the inlet of the second subcooling flow path are respectively located at the ends of the straight tubes furthest from each other, and the inlet of the first subcooling flow path is located above the inlet of the second subcooling flow path. After each of the first subcooling flow paths and the second subcooling flow paths passes through the x2 segments of the straight pipe of the same horizontal pipe unit from their inlet, the last straight pipe in the x2 segments of the straight pipe is connected to the straight pipe of the same position in the adjacent horizontal pipe unit through a transition bend. Furthermore, in the horizontal tube unit of the m group, the last straight pipe in the x2 segments of the straight pipe of the first subcooling flow path and the second subcooling flow path is connected to a first adapter pipe. The first adapter pipe is connected to one of the straight pipes of the horizontal tube unit of the 2m+1 group. In the horizontal tube unit of the 2m+1 group, after passing through the x2 segments of the straight pipe, the outlet of the first subcooling flow path and the outlet of the second subcooling flow path converge at the end of the last straight pipe and form a first total outlet. Where 2≤x2≤4.

9. The heat exchange tube structure according to claim 8, wherein, The subcooling flow path of each of the subcooling units includes a third subcooling flow path and a fourth subcooling flow path; In the (m+1)th group of the horizontal tube unit, the inlet of the third subcooling flow path and the inlet of the fourth subcooling flow path are respectively located at the ends of the straight tubes furthest from each other, and the inlet of the third subcooling flow path is located above the inlet of the fourth subcooling flow path. The third subcooling flow path and the fourth subcooling flow path each pass through the x2 segment of the straight pipe of the same horizontal pipe unit from their inlet, and are then connected by the last straight pipe in the x2 segment of the straight pipe to the straight pipe of the same position in the adjacent horizontal pipe unit through a transition bend. Furthermore, in the horizontal tube unit of the 2m group, the last straight pipe in the x2 segments of the straight pipe of the third subcooling flow path and the fourth subcooling flow path is connected to a second adapter pipe. The second adapter pipe is connected to another straight pipe of the horizontal tube unit of the 2m+1 group. In the horizontal tube unit of the 2m+1 group, after passing through the x2 segments of the straight pipe, the outlets of the third subcooling flow path and the fourth subcooling flow path converge at the end of the last straight pipe and form a second total outlet. In the horizontal tube unit of the 2m+1 group, the first total outlet and the second total outlet are located at the ends of the straight tubes furthest from each other, and the first total outlet is located above the second total outlet.

10. The heat exchange tube structure according to claim 9, wherein, The condensate outlet pipe includes multiple third branch pipes connected to the second main pipe, and the subcooling outlet pipe includes multiple fourth branch pipes connected to the third main pipe; The inlet of the first subcooling flow path and the inlet of the third subcooling flow path are connected to one of the third branch pipes, and the inlet of the second subcooling flow path and the inlet of the fourth subcooling flow path are connected to the other third branch pipe. The outlets of the first subcooling flow path and the second subcooling flow path are connected to one of the fourth branch pipes, and the outlets of the third subcooling flow path and the fourth subcooling flow path are connected to the other fourth branch pipe.

11. The heat exchange tube structure according to claim 7, wherein, The two adjacent sets of the horizontal tube units are staggered in the vertical direction; and / or, The horizontal tube unit has a windward side and a leeward side. The heat exchange tube structure includes a condenser inlet pipe. The condenser inlet pipe includes a first main pipe. The first main pipe is connected to the inlet of multiple condenser flow paths. The first main pipe is located on the leeward side of multiple sets of horizontal tube units. The second main pipe and the third main pipe are located on the windward side of multiple sets of horizontal tube units.

12. The heat exchange tube structure according to any one of claims 1-11, wherein, The number of condensation flow paths is n1, the number of subcooling flow paths (20) is n2, and the heat exchange tube structure (1) satisfies at least one of the following conditions: (1) n1 > n2; （2）7≤n1≤11； （3）7≤n2≤11。 13. A condenser for an outdoor unit, wherein, include: The heat exchange tube structure as described in any one of claims 1-12; as well as Multiple fins are arranged at intervals along the extension direction of the straight tube. The fins have multiple rows of fin holes, and the straight tubes of the multiple rows of the horizontal tube units are correspondingly inserted through the fin holes.

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