Heat exchange tube, heat exchanger and air conditioner

Abstract

The utility model discloses a heat exchange tube, heat exchanger and air conditioner, the heat exchange tube includes: tube body, the inner circumferential wall of tube body is provided with tooth structure along the length direction of tube body spiral extension, the tooth structure is provided with a plurality of at intervals along the circumferential direction of tube body, the ratio of tooth number of tooth structure to tooth height of tooth structure is 909-2100, the outer diameter of the pipe body ranges from 8.8 mm to 9.8 mm. According to the heat exchange tube, the tooth structures spirally extending in the length direction of the tube body are arranged on the inner circumferential wall of the tube body, the tooth structures are arranged at intervals in the circumferential direction of the tube body, and the ratio of the tooth number of the tooth structures to the tooth height of the tooth structures is 909-2100 for the heat exchange tube with the outer diameter of the tube body being 8.8 mm-9. 8 mm. The pressure drop of the heat exchange tube can be reduced, the flow path can be simplified under the condition that the heat exchange performance is not changed, and the complexity of the manufacturing process is reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of air treatment equipment, in particular to a heat exchange tube, a heat exchanger and an air conditioner. Background Art

[0002] In related technologies, conventional refrigerants R410A and R32 are high-pressure refrigerants, insensitive to pressure, and the heat transfer coefficient increases with the increase of pressure drop, and the overall heat transfer performance is improved. However, for potential future refrigerants such as R290, compared with conventional refrigerants, the refrigerating capacity per unit volume of R290 is 50% less, the allowable filling amount is 60% less, and the volume flow rate is more than twice as high. On the premise of using the same heat exchange tube, the flow rate of R290 in the system is high and the flow resistance loss is increased. To ensure the same heat transfer performance, the flow path will be relatively complex. Summary of the Utility Model

[0003] The utility model aims to solve at least one of the technical problems existing in the prior art. For this purpose, the utility model provides a heat exchange tube, which can reduce the pressure drop of the heat exchange tube, and can simplify the flow path and reduce the complexity of the manufacturing process while ensuring the same heat transfer performance.

[0004] The utility model also provides a heat exchanger, which includes the above-mentioned heat exchange tube.

[0005] The utility model also provides an air conditioner, which includes the above-mentioned heat exchanger.

[0006] The heat exchange tube according to an embodiment of the utility model includes: a tube body, on the inner peripheral wall of which there is a tooth structure spirally extending along the length direction of the tube body, the tooth structure being a plurality of teeth spaced along the circumferential direction of the tube body, the ratio of the number of teeth of the tooth structure to the tooth height of the tooth structure being 909-2100, wherein the outer diameter of the tube body is 8.8 mm - 9.8 mm.

[0007] The heat exchange tube according to an embodiment of the utility model, by providing a tooth structure spirally extending along the length direction of the tube body on the inner peripheral wall of the tube body, and the tooth structure being a plurality of teeth spaced along the circumferential direction of the tube body, for a heat exchange tube with an outer diameter of 8.8 mm - 9.8 mm of the tube body, making the ratio of the number of teeth of the tooth structure to the tooth height of the tooth structure be 909-2100, can reduce the pressure drop of the heat exchange tube, and can simplify the flow path and reduce the complexity of the manufacturing process while ensuring the same heat transfer performance.

[0008] According to some embodiments of the utility model, the ratio of the spiral angle of the tooth structure to the number of teeth of the tooth structure is 6.67-12.6.

[0009] According to some embodiments of the present utility model, the ratio of the number of teeth of the tooth structure to the tooth apex angle of the tooth structure is 6.67 - 12.6.

[0010] According to some embodiments of the present utility model, the helix angle of the tooth structure is 12° - 20°.

[0011] According to some embodiments of the present utility model, the tooth apex angle of the tooth structure is 10° - 18°.

[0012] According to some embodiments of the present utility model, the heat exchange tube is used for filling with R290 refrigerant.

[0013] The heat exchanger according to an embodiment of the present utility model includes the above-mentioned heat exchange tube.

[0014] The heat exchanger according to an embodiment of the present utility model, by providing the above-mentioned heat exchange tube, with a tooth structure spirally extending along the length direction of the tube body provided on the inner peripheral wall of the tube body, and the tooth structure being a plurality of teeth arranged at intervals in the circumferential direction of the tube body, for a heat exchange tube with an outer diameter of the tube body of 8.8 mm - 9.8 mm, such that the ratio of the number of teeth of the tooth structure to the tooth height of the tooth structure is 909 - 2100, can reduce the pressure drop of the heat exchange tube, and can simplify the flow path and reduce the complexity of the manufacturing process while ensuring the heat exchange performance remains unchanged.

[0015] In some embodiments of the present utility model, the heat exchanger has a heat exchange flow path, and the heat exchange flow path flows from one end of the heat exchange tube in the length direction to the other end.

[0016] In some embodiments of the present utility model, the heat exchange flow path flows from one end of the heat exchanger in the height direction to the other end.

[0017] The air conditioner according to an embodiment of the present utility model includes the above-mentioned heat exchanger, wherein the heat exchanger is configured as an outdoor heat exchanger.

[0018] The air conditioner according to an embodiment of the present utility model, by providing the above-mentioned heat exchanger, the heat exchanger includes the above-mentioned heat exchange tube, with a tooth structure spirally extending along the length direction of the tube body provided on the inner peripheral wall of the tube body, and the tooth structure being a plurality of teeth arranged at intervals in the circumferential direction of the tube body, for a heat exchange tube with an outer diameter of the tube body of 8.8 mm - 9.8 mm, such that the ratio of the number of teeth of the tooth structure to the tooth height of the tooth structure is 909 - 2100, can reduce the pressure drop of the heat exchange tube, and can simplify the flow path and reduce the complexity of the manufacturing process while ensuring the heat exchange performance remains unchanged.

[0019] The additional aspects and advantages of the present utility model will be partially given in the following description, partially will become obvious from the following description, or will be understood through the practice of the present utility model. Description of the Drawings

[0020] The above and / or additional aspects and advantages of the present utility model will become apparent and be readily understood from the following description of the embodiments in conjunction with the accompanying drawings, where:

[0021] Figure 1 is a partial cross-sectional view of a heat exchange tube according to an embodiment of the present utility model;

[0022] Figure 2 is along Figure 1 a cross-sectional view taken along line C-C in

[0023] Figure 3 is a schematic flow path diagram of a heat exchanger according to an embodiment of the present utility model;

[0024] Figure 4 is a relationship curve between the comprehensive heat exchange performance of a heat exchanger and N / H according to an embodiment of the present utility model.

[0025] Reference numerals:

[0026] 100, heat exchanger;

[0027] 10, heat exchange tube;

[0028] 1, tube body; 2, tooth structure;

[0029] 20, fin;

[0030] 30, heat exchange flow path. Detailed implementation manners

[0031] The embodiments of the present utility model will be described in detail below. The examples of the embodiments are shown in the accompanying drawings, where the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below by referring to the accompanying drawings are exemplary and are only used to explain the present utility model and should not be construed as a limitation of the present utility model.

[0032] In the description of the present utility model, it should be understood that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation to the present utility model. In addition, the features defined as "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present utility model, unless otherwise specified, the meaning of "a plurality" is two or more.

[0033] In the description of the present utility model, it should be noted that, unless otherwise clearly specified and defined, the terms "installation", "connection", and "coupling" should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or an integral connection; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the communication inside two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present utility model can be understood according to specific circumstances.

[0034] The heat exchange tube 10 according to an embodiment of the present utility model will be described below with reference to the drawings.

[0035] As Figure 1 and Figure 2 shown, the heat exchange tube 10 according to an embodiment of the present utility model includes a tube body 1.

[0036] Specifically, the tube body 1 may be a circular tube structure, and the outer diameter of the tube body 1 is 8.8 mm - 9.8 mm. It can be understood that the present application is an improvement on the heat exchange tube 10 with an outer diameter of the tube body 1 of 8.8 mm - 9.8 mm.

[0037] The heat transfer coefficient K and pressure drop P inside the heat exchanger 100 are both composed of two parts. One is the heat transfer coefficient K1 and pressure drop P1 corresponding to the inlet flow velocity of the heat exchange tube 10. Under the same mass flow rate, the more the flow paths are divided, the lower the flow velocity, the smaller K1, and the smaller P1. Conversely, the fewer the flow paths are divided, the higher the flow velocity, the higher K1, and the higher P1. The other is the heat transfer coefficient K2 and pressure drop P2 corresponding to the tooth profile parameters inside the heat exchange tube 10. The higher K2 is inside the heat exchange tube 10, the higher P2 is, and the lower K2 is, the smaller P2 is. It is defined that the heat transfer coefficient K of the heat exchanger 100 inside the tube is K = K1 * K2, and P = P1 * P2. Since the pressure drop of R290 is relatively large and the existing flow paths are relatively complex, which increases the welding difficulty and manufacturing consistency, therefore, to ensure the same heat transfer coefficient and pressure drop, it is necessary to comprehensively consider the influence of the flow path and tooth profile parameters on heat transfer and pressure drop. On the basis of simplifying the flow path, ensuring the performance remains unchanged, the tooth profile parameters inside the heat exchange tube 10 can be reasonably set to reduce the pressure drop.

[0038] In the present application, a tooth structure 2 is provided on the inner peripheral wall of the tube body 1. The tooth structure 2 is a protruding structure on the inner peripheral wall of the tube body 1. The tooth structure 2 spirally extends along the length direction of the tube body 1. The tooth structure 2 is a plurality of ribs arranged at intervals along the circumferential direction of the tube body 1. The ratio of the number of teeth N of the tooth structure 2 to the tooth height H of the tooth structure 2 is 909 - 2100. Among them, when calculating the ratio of the number of teeth N to the tooth height H, the tooth height is calculated in millimeters.

[0039] The more the number of teeth N is, the greater the processing difficulty, the greater the flow resistance inside the tube, the greater the pressure drop, and the better the heat transfer performance. Conversely, the fewer the number of teeth N is, the smaller the processing difficulty, the smaller the flow resistance inside the tube, the smaller the pressure drop, and the worse the heat transfer performance. The greater the tooth height H is, the greater the processing difficulty, the greater the flow resistance inside the tube, the greater the pressure drop, and the better the heat transfer performance. Conversely, the smaller the tooth height H is, the smaller the processing difficulty, the smaller the flow resistance inside the tube, the smaller the pressure drop, and the worse the heat transfer performance.

[0040] As Figure 4 shown, when the tooth tip angle α, helix angle β, and the wall thickness of the tube body 1 remain unchanged, by changing the tooth height H and the number of teeth N, the comprehensive heat transfer performance is the ratio of the heat transfer coefficient to the cube root of the pressure drop. Taking the range with a deviation within ±3% from the maximum value as the preferred range, it can achieve substantially the same heat transfer performance as the heat exchange tube of the same size in the prior art. At this time, the ratio of the number of teeth N to the tooth height H is 909 - 2100, where the tooth tip angle α is 12° and the helix angle β is 15°.

[0041] Meanwhile, when the ratio of the number of teeth N to the tooth height H is within 909 - 2100, it is also convenient for the processing of the heat exchange tube 10 and reduces costs, including processing costs and material costs, etc.

[0042] For example, the ratio of the number of teeth N to the tooth height H can be 1000, 1100, 1200, 1300, 1400, 1500, 1600, 1700, 1800, 1900, 2000, 2100, or the like.

[0043] Optionally, the heat exchange tube 10 is a copper tube, which has high structural strength and good heat exchange performance.

[0044] It should be noted that the number of teeth can be the number of tooth structures 2 in the cross-section perpendicular to the axis of the heat exchange tube 10, the tooth height can be the height by which the tooth structure 2 protrudes from the inner peripheral wall of the tube body 1, the tooth apex angle can be the angle between the two side walls opposite to each other in the height direction of the tooth structure 2, and the helix angle is the angle between the extending direction of the tooth structure 2 and the axis of the heat exchange tube 10.

[0045] According to the heat exchange tube 10 of the embodiment of the present invention, by providing a tooth structure 2 spirally extending along the length direction on the inner peripheral wall of the tube body 1, and the tooth structure 2 is a plurality of teeth arranged at intervals in the circumferential direction of the tube body 1, for the heat exchange tube 10 with an outer diameter of 8.8 mm - 9.8 mm of the tube body 1, the ratio of the number of teeth of the tooth structure 2 to the tooth height of the tooth structure 2 is 909 - 2100, which can reduce the pressure drop of the heat exchange tube 10. Without changing the heat exchange performance, it is possible to simplify the flow path and reduce the complexity of the manufacturing process.

[0046] In some embodiments of the present invention, the ratio of the helix angle β of the tooth structure 2 to the number of teeth N of the tooth structure 2 is 6.67 - 12.6. Among them, the larger the number of teeth N and the helix angle β, the more difficult it is to process. The ratio of the helix angle β to the number of teeth N is 6.67 - 12.6, which is not only convenient for the processing of the tooth structure 2, ensures the feasibility of forming teeth, reduces the processing cost, but also can ensure the heat exchange performance of the heat exchange tube 10. For example, the ratio of the helix angle β of the tooth structure 2 to the number of teeth N of the tooth structure 2 can be 7, 7.5, 8, 8.5, 9, 9.5, 10, 11, 11.5, 12, 12.5, or the like.

[0047] In some embodiments of the present invention, the ratio of the number of teeth N of the tooth structure 2 to the tooth apex angle α of the tooth structure 2 is 6.67 - 12.6. Among them, the smaller the tooth apex angle, the smaller the tooth width when the tooth height is constant, the smaller the area of the inner peripheral wall of the tube body 1 covered by the tooth structure 2, the larger the heat exchange surface in the heat exchange tube 10, and the better the heat exchange effect. However, if the tooth apex angle is too small, the teeth are prone to being inverted. Making the ratio of the number of teeth N of the tooth structure 2 to the tooth apex angle α of the tooth structure 2 be 6.67 - 12.6 can not only ensure the heat exchange performance, but also avoid the occurrence of inverted teeth, facilitate the processing of the tooth structure 2, and reduce the cost. For example, the ratio of the number of teeth N of the tooth structure 2 to the tooth apex angle α of the tooth structure 2 can be 7, 7.5, 8, 8.5, 9, 9.5, 10, 11, 11.5, 12, 12.5, or the like.

[0048] In some embodiments of the present utility model, the helix angle β of the tooth structure 2 is 12°-20°. For example, the helix angle β of the tooth structure 2 can be 12°, 13°, 14°, 15°, 16°, 17°, 18°, 19° or 20°, etc. In the related art, for heat exchange tubes with the same pipe diameter, in order to adapt to conventional refrigerants, the helix angle is 40°. Compared with the existing heat exchange tubes, the present application can not only reduce the flow resistance inside the heat exchange tube 10, thereby reducing the pressure drop, which is beneficial to simplifying the flow path on the premise of the same heat exchange performance and reducing the complexity of the manufacturing process, but also facilitate the processing of the heat exchange tube 10 and reduce the processing cost and material cost, etc.

[0049] In some embodiments of the present utility model, the tooth apex angle α of the tooth structure 2 is 10°-18°. For example, the tooth apex angle α of the tooth structure 2 can be 11°, 12°, 13°, 14°, 15°, 16° or 17°. The smaller the tooth apex angle, the better the heat exchange, but if the tooth apex angle is too small, the teeth are prone to being inverted. In the present application, setting the tooth apex angle α of the tooth structure 2 to be 10°-18° can not only ensure the heat exchange performance, facilitate the processing of the tooth structure 2, but also avoid the teeth of the tooth structure 2 from being inverted.

[0050] In some embodiments of the present utility model, the heat exchange tube 10 is used for charging R290 refrigerant. It can be understood that the heat exchange tube 10 of the present application can be used for R290 refrigerant, which can not only reduce the flow resistance loss of the R290 refrigerant, but also simplify the flow path and reduce the complexity of the manufacturing process under the condition of the same heat exchange performance.

[0051] The heat exchanger 100 according to an embodiment of the present utility model will be described below.

[0052] The heat exchanger 100 according to an embodiment of the present utility model includes the above-mentioned heat exchange tube 10. The heat exchanger 100 further includes a plurality of fins 20, and the heat exchange tube 10 is passed through the fins 20. Among them, the heat exchanger 100 can be an outdoor heat exchanger or an indoor heat exchanger; in a preferred embodiment, the heat exchanger 100 is an outdoor heat exchanger.

[0053] The heat exchanger 100 according to an embodiment of the present utility model, by providing the above-mentioned heat exchange tube 10, with a tooth structure 2 spirally extending along the inner peripheral wall of the tube body 1 and the tooth structure 2 being a plurality of spaced-apart strips along the circumferential direction of the tube body 1, for a heat exchange tube 10 with an outer diameter of the tube body 1 being 8.8 mm - 9.8 mm, making the ratio of the number of teeth of the tooth structure 2 to the tooth height of the tooth structure 2 be 909 - 2100, can reduce the pressure drop of the heat exchange tube 10, and can achieve simplifying the flow path and reducing the complexity of the manufacturing process while ensuring the same heat exchange performance.

[0054] In some embodiments of the present utility model, such as Figure 3As shown, the heat exchanger 100 has a heat exchange flow path 30 that flows from one end to the other end in the length direction of the heat exchange tube 10. It can be understood that there is one heat exchange flow path 30 without branches, and the heat exchange flow path 30 has one inlet and one outlet. The refrigerant flowing into the heat exchanger 100 directly flows into the heat exchange flow path 30 and then flows out of the heat exchanger 100 from the heat exchange flow path 30. Specifically, the heat exchange tube 10 includes a plurality of U-shaped tubes arranged at intervals, and the heat exchange flow path 30 can flow through all the U-shaped tubes. This can reduce the number of heat exchange flow paths 30, simplify the flow path, and reduce the complexity of the manufacturing process.

[0055] In the related art, based on the heat exchange tubes in the prior art, due to the large pressure drop of the heat exchange tubes, the flow path is relatively complex. For example, the heat exchange flow path in the prior art includes two heat exchange sub-flow paths arranged in parallel and a flow path connected in series with both heat exchange sub-flow paths, which is more complex in structure compared to the present application. For R290, the pipe diameter D satisfies 8.8 mm ≤ D ≤ 9.8 mm; Condensation: Dry bulb temperature of the working condition is 35 °C, wet bulb temperature is 24 °C, inlet temperature is 75 °C, pressure is 3100 KPa, outlet subcooling degree is 10 °C, air volume is 2500; Evaporation: Dry bulb temperature of the working condition is 7 °C, wet bulb temperature is 6 °C, temperature before the valve is 30 °C, saturation temperature is 48 °C, inlet temperature is 0.5 °C. The comparison between the present application and the prior art is shown in Table 1 below.

[0056] Table 1

[0057] Original scheme Existing scheme Pipe diameter (mm) 9.52 9.52 Tooth height (mm) 0.18 0.075 Helix angle (°) 40 15 Tooth tip angle (°) 25 12 Number of teeth (°) 70 112 Flow path 2 inlets and 1 outlet 1 inlet and 1 outlet Condensation capacity (W) 4782 4846 Condensation heat transfer coefficient ((W / m2·K)) 3364 3496 Condensation pressure drop (KPa) 3.9 4.78 Evaporation capacity (W) 4078 4035 Evaporation heat transfer coefficient ((W / m2·K)) 7920 7868 Evaporation pressure drop (KPa) 14.9 15.8

[0058] As can be seen from Table 1 above, for R290, the pipe diameter D satisfies 8.8 mm ≤ D ≤ 9.8 mm. Under the condition that the heat exchange performance is generally the same, the structure of the heat exchange tube 10 in the present application is simpler, the processing is more convenient, the pressure drop inside the tube is lower, the flow path is simpler, and the manufacturing process will be simpler.

[0059] In some embodiments of the present utility model, as Figure 3 shown, the heat exchange flow path 30 flows from one end to the other end in the height direction of the heat exchanger 100. This can simplify the arrangement of the flow path and facilitate the connection between multiple U-shaped tubes. For example, in Figure 3 the example shown, the heat exchange tube 10 includes a plurality of U-shaped tubes. The plurality of U-shaped tubes are arranged in a row in the thickness direction of the heat exchanger 100 and are spaced apart in the height direction of the heat exchanger 100. The heat exchange flow path 30 sequentially flows through the plurality of U-shaped tubes along the height direction of the heat exchanger 100.

[0060] The air conditioner according to the embodiments of the present utility model will be described below.

[0061] The air conditioner according to the embodiments of the present utility model includes the above-mentioned heat exchanger 100, wherein the heat exchanger 100 is configured as an outdoor heat exchanger.

[0062] According to the air conditioner of the embodiment of the present utility model, by providing the heat exchanger 100 as described above, the heat exchanger 100 includes the heat exchange tube 10 as described above. A tooth structure 2 is provided on the inner peripheral wall of the tube body 1 and spirally extends along the length direction of the tube body 1. The tooth structure 2 is a plurality of teeth spaced apart in the circumferential direction of the tube body 1. For the heat exchange tube 10 with an outer diameter of the tube body 1 being 8.8 mm - 9.8 mm, the ratio of the number of teeth of the tooth structure 2 to the tooth height of the tooth structure 2 is 909 - 2100, which can reduce the pressure drop of the heat exchange tube 10. Without changing the heat exchange performance, it is possible to simplify the flow path and reduce the complexity of the manufacturing process.

[0063] Other components and operations of the air conditioner according to the embodiment of the present utility model are known to those of ordinary skill in the art and will not be described in detail here.

[0064] In the description of this specification, the description with reference to terms such as "one embodiment", "some embodiments", "illustrative embodiments", "examples", "specific examples", or "some examples" etc. means that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present utility model. In this specification, the schematic representations of the above terms do 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.

[0065] Although the embodiments of the present utility model have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, substitutions, and variations can be made to these embodiments without departing from the principles and spirit of the present utility model. The scope of the present utility model is defined by the claims and their equivalents.

Claims

1. A heat exchange tube, characterized in that: include: A pipe body, wherein the inner circumferential wall of the pipe body is provided with a tooth structure extending spirally along the length direction of the pipe body, the tooth structure is a plurality of teeth arranged at intervals along the circumferential direction of the pipe body, and the ratio of the number of teeth of the tooth structure to the tooth height of the tooth structure is 909-2100, Wherein, the outer diameter of the tube body is 8.8mm-9.8mm.

2. The heat exchange tube according to claim 1, characterized in that: The ratio of the helix angle of the tooth structure to the number of teeth of the tooth structure is 6.67-12.

6.

3. The heat exchange tube according to claim 1, characterized in that: The ratio of the number of teeth of the tooth structure to the tooth top angle of the tooth structure is 6.67-12.

6.

4. The heat exchange tube according to claim 1, characterized in that: The helix angle of the tooth structure is 12°-20°.

5. The heat exchange tube according to claim 1, characterized in that: The tooth top angle of the tooth structure is 10°-18°.

6. The heat exchange tube according to claim 1, characterized in that: The heat exchange tube is used for filling R290 refrigerant.

7. A heat exchanger, characterized in that: The heat exchange tube comprises the heat exchange tube according to any one of claims 1 to 6.

8. The heat exchanger according to claim 7, characterized in that The heat exchanger has a heat exchange flow path, and the heat exchange flow path flows from one end to the other end in the length direction of the heat exchange tube.

9. The heat exchanger according to claim 8, characterized in that The heat exchange flow path flows from one end to the other end of the heat exchanger in the height direction.

10. An air conditioner, characterized in that: The method comprises a heat exchanger according to any one of claims 7 to 9, wherein the heat exchanger is configured as an outdoor heat exchanger.

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