Heat exchanger and air conditioner

Abstract

The utility model relates to the technical field of air conditioners, and discloses a heat exchanger and an air conditioner. The heat exchanger comprises at least one heat exchange assembly, the heat exchange assembly comprises a first pipe set and a second pipe set, the second pipe set is located on one side of the first pipe set in the first direction, the first pipe set comprises a plurality of first heat exchange pipes which are sequentially communicated in the second direction, and the second pipe set comprises a plurality of second heat exchange pipes which are sequentially communicated in the second direction. The ends, in the second direction, of the first heat exchange pipes communicate with the ends, away from the second direction, of the second heat exchange pipes, and the cross sectional area of the first heat exchange pipes is larger than that of the second heat exchange pipes. According to the heat exchanger, the ends, in the second direction, of the multiple first heat exchange pipes communicate with the ends, deviating from the second direction, of the multiple second heat exchange pipes, so that heat exchange airflow can penetrate through the first pipe set and the second pipe set in the process of penetrating through the heat exchanger, and the heat exchange efficiency of the heat exchanger is improved advantageously.

Description

Technical Field

[0001] This application belongs to the field of air conditioner technology, and particularly relates to heat exchangers and air conditioners. Background Technology

[0002] Non-azeotropic refrigerant mixtures have become a research hotspot in the air conditioning industry due to their excellent environmental properties. Unlike single refrigerants, non-azeotropic refrigerant mixtures undergo temperature glide during isobaric phase change, resulting in low heat exchange efficiency in existing heat exchangers using non-azeotropic refrigerant mixtures as working fluids.

[0003] Therefore, improvements to existing technologies are necessary.

[0004] The above information is provided as background information only to aid in understanding this disclosure and does not constitute an assertion or admission that any of the above content can be used as prior art relative to this disclosure. Utility Model Content

[0005] This application provides a heat exchanger and an air conditioner to solve the problem of low heat exchange efficiency when using a non-azeotropic refrigerant mixture as the working fluid.

[0006] In a first aspect, embodiments of this application provide a heat exchanger, including at least one heat exchange component. The heat exchange component includes a first tube group and a second tube group. The second tube group is located on one side of the first tube group in a first direction. The first tube group includes a plurality of first heat exchange tubes connected sequentially along a second direction. The second tube group includes a plurality of second heat exchange tubes connected sequentially along a second direction. One end of the plurality of first heat exchange tubes in the second direction is connected to one end of the plurality of second heat exchange tubes opposite to the second direction. The cross-sectional area of ​​the first heat exchange tubes is larger than the cross-sectional area of ​​the second heat exchange tubes.

[0007] In one possible implementation, the first tube group is located on the leeward side of the heat exchanger, and the second tube group is located on the windward side of the heat exchanger.

[0008] In one possible implementation, the first heat exchange tube is any one of a round tube, a square tube, an elliptical tube, or an oblong tube, and the second heat exchange tube is any one of a round tube, a square tube, an elliptical tube, or an oblong tube.

[0009] In one possible implementation, both the first heat exchange tube and the second heat exchange tube are circular tubes, with the diameter of the first heat exchange tube being D1 and the diameter of the second heat exchange tube being D2, where 6mm ≤ D1 ≤ 8mm and 4mm ≤ D2 ≤ 6mm.

[0010] In one possible implementation, the heat exchange assembly further includes a connecting pipe, one end of which is connected to one end of the plurality of first heat exchange tubes in a second direction, and the other end of which is connected to one end of the plurality of second heat exchange tubes away from the second direction, wherein the cross-sectional area of ​​the connecting pipe gradually decreases along the direction from the first heat exchange tube to the second heat exchange tube.

[0011] In one possible implementation, the pipe spacing between the first pipe group and the second pipe group is L1, where 14mm ≤ L1 ≤ 18mm.

[0012] In one possible implementation, the distance between adjacent first heat exchange tubes is L2, where 18mm ≤ L2 ≤ 22mm.

[0013] In one possible implementation, the distance between adjacent second heat exchange tubes is L3, where 16mm ≤ L3 ≤ 20mm.

[0014] In one possible implementation, the heat exchange assembly further includes fins, and both the first heat exchange tube and the second heat exchange tube are fixedly connected to the fins.

[0015] Secondly, embodiments of this application also provide an air conditioner, the air conditioner including the heat exchanger as described in any of the preceding claims.

[0016] Compared with the prior art, this application has the following beneficial effects:

[0017] The heat exchanger provided in this application embodiment connects one end of multiple first heat exchange tubes in a second direction to the opposite end of multiple second heat exchange tubes in the second direction, allowing the heat exchange airflow to pass through the first and second tube groups during its passage through the heat exchanger, which is beneficial to improving the heat exchange efficiency of the heat exchanger. When the non-azeotropic refrigerant absorbs heat in the heat exchanger, the non-azeotropic refrigerant with a higher dryness fraction first passes through the first tube group with a larger cross-sectional area to increase the heat exchange area, and then the non-azeotropic refrigerant with a lower dryness fraction passes through the second tube group with a smaller cross-sectional area to increase the flow velocity, which can improve the heat exchange efficiency of the heat exchanger. When the non-azeotropic refrigerant releases heat in the heat exchanger, the non-azeotropic refrigerant with a lower dryness fraction first passes through the second tube group with a smaller cross-sectional area to increase the flow velocity, and then the non-azeotropic refrigerant with a higher dryness fraction passes through the first tube group with a larger cross-sectional area to reduce pressure loss, which can improve the heat exchange efficiency of the heat exchanger and solve the problem of low heat exchange efficiency when using non-azeotropic refrigerant as the working fluid. Attached Figure Description

[0018] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0019] To gain a more complete understanding of this application and its beneficial effects, the following description will be provided in conjunction with the accompanying drawings. In the following description, the same reference numerals denote the same parts.

[0020] Figure 1 This is a schematic diagram of a first structure of a heat exchanger provided in an embodiment of this application.

[0021] Figure 2 This is a schematic diagram of a second structure of a heat exchanger provided in an embodiment of this application.

[0022] Explanation of reference numerals in the attached drawings: 1. Heat exchange assembly; 2. First tube group; 21. First heat exchange tube; 3. Second tube group; 31. Second heat exchange tube; 4. Fin. Detailed Implementation

[0023] To illustrate the possible application scenarios, technical principles, implementable specific solutions, and achievable objectives and effects of this application in detail, the following description, in conjunction with the listed specific embodiments and accompanying drawings, provides a detailed explanation. The embodiments described herein are merely illustrative of the technical solutions of this application and are therefore intended to limit the scope of protection of this application.

[0024] In the description of this application, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, features defined with "first" and "second" may explicitly or implicitly include one or more features.

[0025] The technical solutions in the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings.

[0026] This application provides a heat exchanger and an air conditioner to solve the problem of low heat exchange efficiency when using a non-azeotropic refrigerant mixture as the working fluid. The following description will be provided in conjunction with the accompanying drawings.

[0027] Please see Figure 1 and Figure 2This application provides a heat exchanger including at least one heat exchange component 1. The heat exchange component 1 includes a first tube group 2 and a second tube group 3. The second tube group 3 is located on one side of the first tube group 2 in a first direction. The first tube group 2 includes a plurality of first heat exchange tubes 21 connected sequentially along a second direction. The second tube group 3 includes a plurality of second heat exchange tubes 31 connected sequentially along a second direction. One end of the plurality of first heat exchange tubes 21 in the second direction is connected to one end of the plurality of second heat exchange tubes 31 opposite to the second direction. The cross-sectional area of ​​the first heat exchange tubes 21 is larger than the cross-sectional area of ​​the second heat exchange tubes 31.

[0028] By connecting one end of multiple first heat exchange tubes 21 in the second direction to the opposite end of multiple second heat exchange tubes 31 in the second direction, the heat exchange airflow can pass through the first tube group 2 and the second tube group 3 during its passage through the heat exchanger, which is beneficial to improving the heat exchange efficiency of the heat exchanger. When the non-azeotropic refrigerant absorbs heat in the heat exchanger, the non-azeotropic refrigerant with a higher dryness fraction first passes through the first tube group 2 with a larger cross-sectional area to increase the heat exchange area, and then the non-azeotropic refrigerant with a lower dryness fraction passes through the second tube group 3 with a smaller cross-sectional area to increase the flow velocity, which can improve the heat exchange efficiency of the heat exchanger. When the non-azeotropic refrigerant releases heat in the heat exchanger, the non-azeotropic refrigerant with a lower dryness fraction first passes through the second tube group 3 with a smaller cross-sectional area to increase the flow velocity, and then the non-azeotropic refrigerant with a higher dryness fraction passes through the first tube group 2 with a larger cross-sectional area to reduce pressure loss, which can improve the heat exchange efficiency of the heat exchanger and solve the problem of low heat exchange efficiency when using non-azeotropic refrigerant as the working fluid.

[0029] Please see Figure 1 and Figure 2 The heat exchange assembly 1 also includes a connecting pipe and fins 4. The connecting pipe is connected to the first tube group 2 and the second tube group 3. One end of the connecting pipe is connected to one end of a plurality of first heat exchange tubes 21 in a second direction, and the other end is connected to one end of a plurality of second heat exchange tubes 31 away from the second direction. The cross-sectional area of ​​the connecting pipe gradually decreases along the direction from the first heat exchange tube 21 to the second heat exchange tube 31, so that the non-azeotropic refrigerant mixture flows from the first tube group 2 to the second tube group 3. The number of fins 4 is set to multiple, and the multiple fins 4 are spaced apart along the length direction of the first connecting pipe. Both the first connecting pipe and the second connecting pipe are connected to the fins 4. The arrangement of the fins 4 increases the heat dissipation area of ​​the first connecting pipe and the second connecting pipe, thereby improving the heat exchange efficiency of the heat exchanger.

[0030] Please see Figure 1In this embodiment, the first direction is horizontal and the second direction is vertical. The first tube group 2 includes multiple first heat exchange tubes 21 arranged and connected in the vertical direction, and the second tube group 3 includes multiple second heat exchange tubes 31 arranged and connected in the vertical direction. As the non-azeotropic refrigerant absorbs heat in the heat exchanger, its dryness continuously increases with the heat absorption process, and it gradually changes from a gaseous state to a liquid state. This allows the non-azeotropic refrigerant to pass sequentially through the first tube group 2 and the second tube group 3. The liquid non-azeotropic refrigerant can accelerate its flow in the first tube group 2 and the second tube group 3 under the influence of gravity, thereby improving the heat exchange efficiency. When a non-azeotropic refrigerant releases heat within the heat exchanger, its dryness continuously decreases as the heat release process proceeds. The non-azeotropic refrigerant gradually changes from a liquid to a gaseous state, allowing it to pass sequentially through the second tube group 3 and the first tube group 2. The gaseous non-azeotropic refrigerant experiences greater buoyancy, which helps to balance the effects of gravity and pressure loss on its heat exchange efficiency, thereby increasing the overall heat exchange efficiency.

[0031] Please see Figure 2 In some embodiments of this application, the first direction is a downward-sloping direction, and the second direction is a vertical direction, such that the second tube group 3 is located in the downward-sloping direction of the first tube group 2. When the non-azeotropic refrigerant absorbs heat in the heat exchanger, the liquid non-azeotropic refrigerant can flow accelerated from the first tube group 2 to the second tube group 3 under the action of gravity, further improving the heat exchange efficiency. When the non-azeotropic refrigerant releases heat in the heat exchanger, the non-azeotropic refrigerant in the second tube group 3 can flow upward-slopingly to the first tube group 2, further reducing the pressure loss of the non-azeotropic refrigerant.

[0032] Please see Figure 1 In this embodiment, the number of heat exchange components 1 is set to four, and the four heat exchange components 1 are arranged sequentially at intervals along the vertical direction. The first tube group 2 includes four first heat exchange tubes 21, and the second tube group 3 includes four second heat exchange tubes 31. It should be understood that in some embodiments of this application, the number of heat exchange components 1 can be increased or decreased according to the thermal design requirements, the number of first heat exchange tubes 21 in the first tube group 2 can be increased or decreased according to the thermal design requirements, and the number of second heat exchange tubes 31 in the second tube group 3 can be increased or decreased according to the thermal design requirements.

[0033] Please see Figure 1 and Figure 2The first tube group 2 is located on the leeward side of the heat exchanger, and the second tube group 3 is located on the windward side of the heat exchanger. When the non-azeotropic refrigerant absorbs heat in the heat exchanger, its temperature decreases after flowing to the second tube group 3. By placing the second tube group 3 on the windward side of the heat exchanger, the temperature difference between the second tube group 3 and the heat exchange airflow can be increased, thereby increasing the heat exchange efficiency of the heat exchanger.

[0034] Please see Figure 1 and Figure 2 The first heat exchange tube 21 can be any one of a round tube, square tube, elliptical tube, or oblong tube, and the second heat exchange tube 31 can be any one of a round tube, square tube, elliptical tube, or oblong tube. In this embodiment, both the first heat exchange tube 21 and the second heat exchange tube 31 are round tubes, the diameter of the first heat exchange tube 21 is D1, the diameter of the second heat exchange tube 31 is D2, 6mm≤D1≤8mm, and 4mm≤D2≤6mm. In this embodiment, the diameter D1 of the first heat exchange tube 21 is 7 mm, and the diameter D2 of the second heat exchange tube 31 is 5 mm. In some embodiments of this application, the diameter D1 of the first heat exchange tube 21 is any one of 6 mm, 6.2 mm, 6.4 mm, 6.6 mm, 6.8 mm, 7.2 mm, 7.4 mm, 7.6 mm, 7.8 mm, and 8 mm, and the diameter D2 of the second heat exchange tube 31 is any one of 4 mm, 4.2 mm, 4.4 mm, 4.6 mm, 4.8 mm, 5.2 mm, 5.4 mm, 5.6 mm, 5.8 mm, and 6 mm. By ensuring that 6 mm ≤ D1 ≤ 8 mm and 4 mm ≤ D2 ≤ 6 mm, the pressure loss of the non-azeotropic refrigerant mixture within the heat exchanger can be reduced, thereby improving heat exchange efficiency, while lowering the production cost of the heat exchanger.

[0035] Please see Figure 1 and Figure 2 The tube spacing between the first tube group 2 and the second tube group 3 is L1, where 14mm ≤ L1 ≤ 18mm. In this embodiment, the value of L1 between the first tube group 2 and the second tube group 3 is 15mm. In some embodiments of this application, the value of L1 between the first tube group 2 and the second tube group 3 is any one of 14mm, 14.5mm, 15.5mm, 16mm, 16.5mm, 17mm, 17.5mm, and 18mm. By ensuring that 14mm ≤ L1 ≤ 18mm, not only can the production cost of the heat exchanger be controlled, but the heat exchange efficiency of the heat exchanger can also be guaranteed.

[0036] Please see Figure 1 and Figure 2The distance between adjacent first heat exchange tubes 21 is L2, and the distance between adjacent second heat exchange tubes 31 is L3, where 18mm ≤ L2 ≤ 22mm and 16mm ≤ L3 ≤ 20mm. In this embodiment, the value of distance L2 between adjacent first heat exchange tubes 21 is 21mm, and the value of distance L3 between adjacent second heat exchange tubes 31 is 19mm. In some embodiments of this application, the value of distance L2 between adjacent first heat exchange tubes 21 is any one of 18mm, 18.5mm, 19mm, 19.5mm, 20mm, 20.5mm, 21.5mm, and 22mm, and the value of distance L3 between adjacent first heat exchange tubes 21 is any one of 16mm, 16.5mm, 17mm, 17.5mm, 18mm, 18.5mm, 19.5mm, and 20mm. By ensuring that 18mm≤L2≤22mm and 16mm≤L3≤20mm, not only can the production cost of the heat exchanger be controlled, but the heat exchange efficiency of the heat exchanger can also be guaranteed.

[0037] This application also provides an air conditioner that includes the heat exchanger described above. Since this air conditioner has the aforementioned heat exchanger, it possesses at least some or all of the beneficial effects of the aforementioned heat exchanger, which will not be elaborated upon here.

[0038] In the above embodiments, the descriptions of each embodiment have different focuses. For parts not described in detail in a certain embodiment, please refer to the relevant descriptions in other embodiments.

[0039] Finally, it should be noted that although the above embodiments have been described in the text and drawings of this application, this should not limit the scope of patent protection of this application. Any technical solutions that are based on the essential concept of this application and utilize the content described in the text and drawings of this application, resulting in equivalent structural or procedural substitutions or modifications, as well as the direct or indirect application of the technical solutions of the above embodiments to other related technical fields, are all included within the scope of patent protection of this application.

Claims

1. A heat exchanger, characterized by, The heat exchanger comprises at least one heat exchange assembly (1), the heat exchange assembly (1) comprises a first tube group (2) and a second tube group (3), the second tube group (3) is located on one side of the first tube group (2) in a first direction, the first tube group (2) comprises a plurality of first heat exchange tubes (21) sequentially communicated in a second direction, the second tube group (3) comprises a plurality of second heat exchange tubes (31) sequentially communicated in the second direction, one end of the plurality of first heat exchange tubes (21) in the second direction is communicated with one end of the plurality of second heat exchange tubes (31) away from the second direction, and a cross-sectional area of the first heat exchange tube (21) is greater than a cross-sectional area of the second heat exchange tube (31).

2. The heat exchanger of claim 1, wherein The first tube group (2) is arranged on a leeward side of the heat exchanger, and the second tube group (3) is arranged on a windward side of the heat exchanger.

3. The heat exchanger of claim 1, wherein The first heat exchange tube (21) is any one of a round tube, a square tube, an oval tube or an oblong tube, and the second heat exchange tube (31) is any one of a round tube, a square tube, an oval tube or an oblong tube.

4. The heat exchanger of claim 3, wherein The first heat exchange tube (21) and the second heat exchange tube (31) are both round tubes, a tube diameter of the first heat exchange tube (21) is D1, a tube diameter of the second heat exchange tube (31) is D2, 6mm≤D1≤8mm, and 4mm≤D2≤6mm.

5. The heat exchanger of claim 3, wherein The heat exchange assembly (1) further comprises a connecting tube, one end of the connecting tube is connected with one end of the plurality of first heat exchange tubes (21) in the second direction, the other end of the connecting tube is connected with one end of the plurality of second heat exchange tubes (31) away from the second direction, and a cross-sectional area of the connecting tube gradually decreases in a direction from the first heat exchange tube (21) to the second heat exchange tube (31).

6. The heat exchanger of claim 1, wherein A tube spacing between the first tube group (2) and the second tube group (3) is L1, and 14mm≤L1≤18mm.

7. The heat exchanger of claim 1, wherein A distance between adjacent first heat exchange tubes (21) is L2, and 18mm≤L2≤22mm.

8. The heat exchanger of claim 1, wherein A distance between adjacent second heat exchange tubes (31) is L3, and 16mm≤L3≤20mm.

9. The heat exchanger of claim 1, wherein The heat exchange assembly (1) further comprises a fin (4), and the first heat exchange tube (21) and the second heat exchange tube (31) are fixedly connected with the fin (4).

10. An air conditioner characterized by comprising: The air conditioner comprises the heat exchanger according to any one of claims 1-9.

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