WO2020042425A1 - 换热管及空调器 - Google Patents

换热管及空调器 Download PDF

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Publication number
WO2020042425A1
WO2020042425A1 PCT/CN2018/120241 CN2018120241W WO2020042425A1 WO 2020042425 A1 WO2020042425 A1 WO 2020042425A1 CN 2018120241 W CN2018120241 W CN 2018120241W WO 2020042425 A1 WO2020042425 A1 WO 2020042425A1
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WO
WIPO (PCT)
Prior art keywords
heat exchange
exchange tube
fin
fins
tube according
Prior art date
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Ceased
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PCT/CN2018/120241
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English (en)
French (fr)
Inventor
刘华
张治平
岳清学
胡东兵
王春连
胡海利
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Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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Publication of WO2020042425A1 publication Critical patent/WO2020042425A1/zh
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins

Definitions

  • the present disclosure relates to the field of refrigeration technology, and in particular, to a heat exchange tube and an air conditioner.
  • Water-cooled condensers have developed rapidly due to their compact structure and wide applicability. High efficiency, energy saving and replacement of new refrigerants are still the main research directions at present.
  • Water-cooled heat exchangers are mostly horizontal shell-and-tube heat exchangers. Freon is taken in the shell side and water is taken in the tube side.
  • a factor that has a relatively large effect on its heat exchange is the performance of the heat exchange tubes in the shell. Inside the shell side, the refrigerant outside the condensing tube undergoes a phase change for heat exchange. The refrigerant condenses outside the tube to form a liquid film covering the surface of the heat exchange tube.
  • the current general strengthening technology is to use a combination cutter to extrude metal fins that spirally expand along the circumference of the tube through a combination cutter, and perform secondary rolling on the fins to form a boss and sharp corners.
  • the main strengthening mechanism is to increase the surface area outside the tube.
  • the thinned liquid film reduces the thermal resistance by using different bosses and sharp corners and radius of curvature.
  • the lower fins are spirally connected and form channels. Drain the liquid refrigerant. In this way, a convex plate and a sharp, sharp-angled thin liquid film are formed. At the same time, the formed convex plate also increases the resistance of the liquid film to drip and remove.
  • the embodiments of the present disclosure provide a heat exchange tube and an air conditioner to solve the technical problem that the liquid refrigerant existing on the surface of the heat exchange tube during use is obviously flooded on the surface.
  • An embodiment of the present disclosure provides a heat exchange tube including a tube body and fins disposed on an outer surface of the tube body. A channel is formed between adjacent fins, and a communication groove is formed on the fin. The communication grooves will be adjacent to each other. The communication channel is connected, and the communication groove is used for circulating the refrigerant.
  • the fins are coiled on the outer surface in a circumferential direction of the outer surface, and the communication groove is opened on the fins in the axial direction of the outer surface.
  • the fins are spirally arranged on the outer surface.
  • the fins are multiple, and the multiple fins are spaced apart on the outer surface.
  • the communication groove is opened deep on the fin to the bottom of the fin, or is opened to a predetermined length from the bottom of the fin.
  • the communication groove is disposed at an angle ⁇ with respect to the extending direction of the fin, and 0 ° ⁇ 90 °.
  • the cross-section of the communication groove is V-shaped, U-shaped, or Y-shaped.
  • a boss structure is pressed on the fin, and the boss structure is used to increase the surface area of the fin.
  • the boss structure includes a groove portion on the top of the fin and a sharp corner portion protruding relative to the side of the fin.
  • the boss structure is disposed at an angle ⁇ with respect to the extending direction of the fin, 15 ° ⁇ ⁇ ⁇ 65 °.
  • an inner rib structure is formed on the inner surface of the pipe body, and the inner rib structure is used to increase the surface area of the inner surface.
  • the inner rib structure is arranged on the inner surface in a spiral shape, and the inner rib structure is arranged at an angle ⁇ with respect to the center of the pipe body, 15 ° ⁇ ⁇ ⁇ 60 °.
  • the inner rib structure has a trapezoidal or triangular cross section.
  • the present disclosure also provides an air conditioner including a heat exchange tube, and the heat exchange tube is the above-mentioned heat exchange tube.
  • the communication grooves formed on the fins can make adjacent channels communicate, increase the area of the liquid refrigerant discharge channel after condensation, strengthen the refrigerant discharge capacity, and allow the refrigerant to be better on the surface of the heat exchange tube. Ground circulation. Furthermore, the excessive increase of the thickness of the liquid refrigerant on the surface of the heat exchange tube can be avoided, the flooding phenomenon on the surface of the heat exchange tube can be avoided, the effective heat exchange area can be ensured, and the heat exchange effect can be increased.
  • FIG. 1 is a schematic diagram of an overall structure of an embodiment of a heat exchange tube according to the present disclosure
  • FIG. 2 is a partial structural schematic diagram of the heat exchange tube of FIG. 1;
  • FIG. 3 is a partially enlarged structure diagram of FIG. 2; FIG.
  • FIG. 4 is a schematic plan view of the structure of FIG. 3;
  • FIG. 5 is a schematic view of the front view structure of FIG. 3; FIG.
  • FIG. 6 is a schematic structural view of the right side of FIG. 3;
  • FIG. 7 is a schematic sectional structural view of the heat exchange tube of FIG. 6.
  • FIG. 1 illustrates an embodiment of a heat exchange tube according to the present disclosure.
  • the heat exchange tube includes a tube body 10 and a fin 20 disposed on an outer surface 11 of the tube body 10.
  • a channel is formed between adjacent fins 20. 30.
  • the fin 20 is provided with a communication groove 21.
  • the communication groove 21 communicates with adjacent channels 30.
  • the communication groove 21 is used for circulating a refrigerant.
  • the adjacent channels 30 can be communicated, the area of the discharge channel of the liquid refrigerant after condensation is increased, the refrigerant discharge capacity is enhanced, and the refrigerant can be exchanged in The surface of the tube circulates better. Furthermore, the excessive increase of the thickness of the liquid refrigerant on the surface of the heat exchange tube can be avoided, the flooding phenomenon on the surface of the heat exchange tube can be avoided, the effective heat exchange area can be ensured, and the heat exchange effect can be increased.
  • the fins 20 are coiled on the outer surface 11 in the circumferential direction of the outer surface 11, and the communication groove 21 is opened on the fins 20 in the axial direction of the outer surface 11.
  • the above-mentioned winding arrangement along the circumferential direction of the outer surface 11 may be provided along the radial direction of the outer surface 11 or in a direction at an angle to the radial direction; Opening in the axial direction also refers to communicating adjacent channels 30 in the axial direction or in a direction at an angle to the axial direction.
  • the fins 20 are spirally arranged on the outer surface 11.
  • the fins 20 are multiple, and the multiple fins 20 are disposed at intervals on the outer surface 11, that is, a plurality of annular fins 20 are disposed on the outer surface 11.
  • the cross section of the communication groove 21 is Y-shaped, and the depth of the communication groove 21 on the fin 20 is opened to a predetermined length from the bottom of the fin 20.
  • the communication groove 21 is deeply opened on the fin 20 to the bottom of the fin 20. It should be noted that the depth of the communication groove 21 on the fin 20 should be as deep as possible on the basis of ensuring the stress intensity of the fin 20.
  • the cross-section of the communication groove 21 may also be V-shaped or U-shaped.
  • the plurality of communication grooves 21 are disposed at intervals on the fin 20.
  • the refrigerant discharge capacity can be further enhanced, so that the refrigerant can flow better on the surface of the heat exchange tube. It has been found through experiments that the number of communication grooves 21 uniformly distributed from 30 to 100 along the circumferential direction of the fins 20 can have a good refrigerant discharge capability.
  • the communication groove 21 is set at an angle ⁇ with respect to the extending direction of the fin 20, and 0 ° ⁇ ⁇ 90 °. Since the outer surface 11 of the fin 20 is spirally arranged, allowing the communication groove 21 to be arranged at an angle relative to the fin 20 is also beneficial to the circulation of the refrigerant in the axial direction. In addition, it is also possible to make the communication groove 21 perpendicular to the extending direction of the fin 20.
  • the fin 20 is pressed with a boss structure 22.
  • the boss structure 22 is used to increase the surface area of the fins 20 and can improve heat exchange efficiency during heat exchange.
  • the boss structure 22 includes a groove portion 221 on the top of the fin 20 and a sharp corner portion 222 protruding from the side of the fin 20. In this way, while increasing the heat exchange area, the sharp corners on the surface of the condenser tube are increased and strengthened. Using the characteristics of the large curvature of the corners 222 and the grooves 221, the refrigerant liquid film is thinned, thereby strengthening local condensation and condensation. The ability to play a role in strengthening the upper layer of the condenser tube to reduce the thickness of the liquid film adhered to the fins on the surface of the condenser tube when the refrigerant vapor condenses.
  • the boss structure 22 is disposed at an angle ⁇ with respect to the extending direction of the fin 20, and 15 ° ⁇ ⁇ ⁇ 65 °.
  • the outer surface 11 of the fin 20 is spirally arranged, so that the boss structure 22 is arranged at an angle with respect to the fin 20, which is also conducive to the circulation of the refrigerant in the axial direction. Heat exchange.
  • the groove portion 221 is formed by extruding the top of the original fin using a knurling die to form a groove portion structure having a depth of 0.1 to 0.45 mm and a width of 0.01 to 0.35 mm. . While forming the groove portion 221, due to the good plasticity of the metal material itself, two sharp corner portions 222 are naturally formed on both sides of the fin 20, and the structure of the sharp corner portions 222 extending to the side of the fin 20 is 0.05 ⁇ 0.2mm.
  • an inner rib structure 40 is formed on the inner surface of the pipe body 10.
  • the inner rib structure 40 is used to increase the surface area of the inner surface, which can improve the heat exchange efficiency during heat exchange, and also increases the degree of disturbance of the fluid in the tube, which can further enhance the heat exchange efficiency.
  • the inner rib structure 40 is spirally disposed on the inner surface, and the inner rib structure 40 is disposed at an angle ⁇ with respect to the center of the pipe body 10, 15 ° ⁇ ⁇ ⁇ 60 °.
  • the inner rib structures 40 are multiple, and the multiple inner rib structures 40 are evenly distributed on the inner surface. In some embodiments, there are 10 to 80 internal rib structures.
  • the inner surface of the pipe body 10 is rolled into a spiral convex rib structure 40 with a core of a pressure groove.
  • the inner rib structure 40 is disposed at an angle ⁇ with respect to the center of the pipe body 10, and the protrusion height of the inner rib structure 40 from the inner surface is 0.2 to 0.60 mm.
  • the cross section of the inner rib structure 40 is trapezoidal, and the cross section shaped inner rib structure 40 is more convenient for processing and has better heat exchange capability.
  • the bottom of the inner rib structure 40 is integrated with the inner surface and has a smooth transition with the inner surface, and the two corners have a smooth transition.
  • the cross section of the inner rib structure 40 may also be triangular.
  • the above-mentioned heat exchange tube is processed by a dedicated fin processing equipment, and an extrusion molding and chipless processing process is adopted.
  • a mother pipe with an outer diameter of 19.05mm and a wall thickness of 1.1mm is used for processing.
  • a grooved mold is used to roll the grooves on the mother tube outside the tube, and the formed grooves are pressed with a combination tool to form independent fins that spiral in the axial direction. Deformation caused by processing fins on the independent fins To form a communication groove.
  • the top of the fins is simultaneously extruded with a knurling die to form a boss structure.
  • the inner rib structure 40 is reinforced and synchronized. While the outer surface is squeezed by a combination cutter, the inner side is formed by a multi-head grooved core.
  • the present disclosure also provides an air conditioner including the above-mentioned heat exchange tube.
  • the air conditioner using the above heat exchange tube has better heat exchange performance and higher refrigeration efficiency.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

一种换热管及空调器，换热管包括管体（10）和设置在管体（10）外表面上的翅片（20），相邻的翅片（20）之间形成有通道（30）。翅片（20）上开设有连通槽（21），连通槽（21）将相邻的通道（30）连通，连通槽（21）用于流通冷媒。增加了凝结后液体冷媒的排出通道面积，强化了冷媒排出能力，让冷媒可以在换热管的表面更好地流通；进而可以避免液态冷媒在换热管的表面厚度增加过多，增加热阻降低换热效率。

Description

换热管及空调器
相关申请
本申请是以申请号为201811003111.2，申请日为2018年8月30日，发明名称为“换热管及空调器”的中国专利申请为基础，并主张其优先权，该中国专利申请的公开内容在此作为整体引入本申请中。
技术领域
本公开涉及制冷技术领域，具体而言，涉及一种换热管及空调器。
背景技术
在空调与制冷行业中，水冷式冷凝器因结构紧凑，适用性宽广，得到了快速发展。高效、节能以及新冷媒的替代仍是目前主要的研究方向。水冷式换热器大多为卧式壳管式换热器，壳程内走氟利昂，管程内走水。而在冷凝器中，对其换热影响比较大的一个因素就是壳体中换热管的性能的优劣。在壳程内部，冷凝管外侧的冷媒发生相变进行换热，冷媒在管外凝结形成液膜覆盖在换热管表面，该液膜的存在增大了冷媒侧的热阻，管内通过增加扰动进行换热。所以热阻分布主要存在管外。根据弱侧强化原则，对管外进行强化显得尤为重要，应最大限度的降低管外热阻提高换热性能。
对于冷凝管管外强化，现行的一般强化技术为通过组合刀具在管外挤压出沿管子圆周螺旋扩张的金属翅片，并在翅片上进行二次滚压，形成凸台和尖锐的尖角。其主要强化机理，是在于增加了管外的表面积，在利用形成的凸台和尖锐的尖角和曲率半径不同，摊薄液膜降低热阻。而下层翅片螺旋相连，并形成通道。将液态冷媒排走。利用这种方式形成了凸台和尖锐的尖角摊薄液膜，同时形成的凸台也增加了液膜的滴落和排除的阻力。
高效管单管传热实验研究发现，冷凝管在冷凝过程中，汽态冷媒在冷凝管表面进行凝结，之后凝结形成的液态冷媒沿管子翅片之间的通道流动到冷凝管下面，并沿翅片与翅片之间形成的通道排走。而传统的冷凝管在强化冷凝过程中，翅片与翅片之间形成的通道，沿轴向呈螺旋分布联通，横向通道在下部未能联通。所以在凝结形成的液态冷媒随着冷凝强度的加强，液态冷媒厚度在增加，热阻也会随着进一步增大。严重的时候，液态冷媒会在换热管表面形成液泛，减少有效换热面积，造成冷凝效果衰 减。
发明内容
本公开实施例提供了一种换热管及空调器，以解决现有技术中换热管在使用时存在的液态冷媒在表面液泛现象明显的技术问题。
本公开实施方式提供一种换热管，包括管体和设置在管体的外表面上的翅片，相邻的翅片之间形成有通道，翅片上开设有连通槽，连通槽将相邻的通道连通，连通槽用于流通冷媒。
在一些实施例中，翅片在外表面上沿外表面的圆周方向盘绕设置，连通槽在翅片上沿外表面的轴向方向开设。
在一些实施例中，翅片在外表面上呈螺旋状盘绕设置。
在一些实施例中，翅片为多条，多条翅片在外表面上间隔设置。
在一些实施例中，连通槽在翅片上深度开设到翅片的底部，或者开设到距离翅片的底部预定长度的位置。
在一些实施例中，连通槽为多个，多个连通槽在翅片上间隔设置。
在一些实施例中，连通槽相对于翅片的延伸方向呈角度β设置，0°＜β≤90°。
在一些实施例中，连通槽的截面呈V形、U形或者Y形。
在一些实施例中，翅片上压制有凸台结构，凸台结构用于增大翅片的表面积。
在一些实施例中，凸台结构包括位于翅片的顶部的凹槽部以及相对于翅片的侧面凸出的尖角部。
在一些实施例中，凸台结构相对于翅片的延伸方向呈角度α设置，15°≤α≤65°。
在一些实施例中，管体的内表面上形成有内肋结构，内肋结构用于增大内表面的表面积。
在一些实施例中，内肋结构呈螺旋状设置在内表面上，内肋结构相对于管体的中心呈角度λ设置，15°≤λ≤60°。
在一些实施例中，内肋结构的截面呈梯形或三角形。
本公开还提供了一种空调器，包括换热管，换热管为上述的换热管。
在上述实施例中，通过翅片上开设的连通槽，可以使得相邻的通道连通，增加了凝结后液态冷媒的排出通道面积，强化了冷媒排出能力，让冷媒可以在换热管的表面 更好地流通。进而，可以避免液态冷媒在换热管的表面厚度增加过多，避免换热管的表面出现液泛现象，保证有效换热面积，增加换热效果。
附图说明
构成本公开的一部分的附图用来提供对本公开的进一步理解，本公开的示意性实施例及其说明用于解释本公开，并不构成对本公开的不当限定。在附图中：
图1是根据本公开的换热管的实施例的整体结构示意图；
图2是图1的换热管的局部结构示意图；
图3是图2的局部放大结构示意图；
图4是图3的俯视结构示意图；
图5是图3的主视结构示意图；
图6是图3的右视结构示意图；
图7是图6的换热管的剖视结构示意图。
具体实施方式
为使本公开的目的、技术方案和优点更加清楚明白，下面结合实施方式和附图，对本公开做进一步详细说明。在此，本公开的示意性实施方式及其说明用于解释本公开，但并不作为对本公开的限定。
图1示出了本公开的换热管的实施例，该换热管包括管体10和设置在管体10的外表面11上的翅片20，相邻的翅片20之间形成有通道30。翅片20上开设有连通槽21，连通槽21将相邻的通道30连通，连通槽21用于流通冷媒。
应用本公开的技术方案，通过翅片20上开设的连通槽21，可以使得相邻的通道30连通，增加了凝结后液态冷媒的排出通道面积，强化了冷媒排出能力，让冷媒可以在换热管的表面更好地流通。进而，可以避免液态冷媒在换热管的表面厚度增加过多，避免换热管的表面出现液泛现象，保证有效换热面积，增加换热效果。
在一些实施例的技术方案中，如图2所示，翅片20在外表面11上沿外表面11的圆周方向盘绕设置，连通槽21在翅片20上沿外表面11的轴向方向开设。需要说明的是，上述沿外表面11的圆周方向盘绕设置，可以是沿外表面11的径向方向设置，也可以是沿与径向方向呈一定角度的方向设置；上述的沿外表面11的轴向方向开设，也指的是在轴向方向上或者与轴向方向呈一定角度的方向上连通相邻的通道30。
在一些实施例的技术方案中，如图1和图2所示，翅片20在外表面11上呈螺旋状盘绕设置。作为其他的可选的实施方式，翅片20为多条，多条翅片20在外表面11上间隔设置，即多条环形的翅片20设置在外表面11上。
如图3和图6所示，在一些实施例的技术方案中，连通槽21的截面为Y形，连通槽21在翅片20上的深度开设到距离翅片20的底部预定长度的位置。作为其他的可选的实施方式，连通槽21在翅片20上深度开设到翅片20的底部也是可行的。需要说明的是，连通槽21在翅片20上开设的深度，在保证翅片20的应力强度的基础上，应当是越深越好。
此外，作为其他的可选的实施方式，连通槽21的截面还可以呈V形或者U形。
在一些实施例的技术方案中，连通槽21为多个，多个连通槽21在翅片20上间隔设置。通过设置多个连通槽21，可以进一步地强化冷媒排出能力，让冷媒可以在换热管的表面更好地流通。通过实验发现，沿翅片20的圆周方向进行均布数量30～100个的连通槽21可以起到良好的冷媒排出能力。
在一些实施例的技术方案中，如图3和图4所示，连通槽21相对于翅片20的延伸方向呈角度β设置，0°＜β≤90°。由于翅片20外表面11上呈螺旋状盘绕设置，让连通槽21相对于翅片20呈角度设置，也有利于冷媒在轴向方向上流通。此外，让连通槽21相对于翅片20的延伸方向垂直也是可行的。
如图3和图5所示，作为一种优选的实施方式，翅片20上压制有凸台结构22。凸台结构22用于增大翅片20的表面积，在换热时可以提高换热效率。如图5和图6所示，在一些实施例的技术方案中，凸台结构22包括位于翅片20的顶部的凹槽部221以及相对于翅片20的侧面凸出的尖角部222，这样在增大了换热面积的同时，增加和强化了冷凝管表面尖锐的尖角，利用尖角部222和凹槽部221转角曲率大的特点，摊薄冷媒液膜，从而强化了局部冷凝凝结能力，起到了在冷凝管上层强化减薄制冷剂蒸汽凝结时粘附在冷凝管表面翅片上的液膜厚度的能力。
如图4所示，在一些实施例的技术方案中，凸台结构22相对于翅片20的延伸方向呈角度α设置，15°≤α≤65°。同理，由于在一些实施例的技术方案中，翅片20外表面11上呈螺旋状盘绕设置，让凸台结构22相对于翅片20呈角度设置，也有利于冷媒在轴向方向上流通换热。
在一些实施例的技术方案中，凹槽部221的形成是利用滚花模具在原有翅片顶部进行挤压而成，形成深度为0.1～0.45mm，宽度为0.01～0.35mm的凹槽部结构。在形 成凹槽部221的同时，由于金属材料本身良好的塑性，在翅片20两侧自然形成两个尖角部222，该尖角部222结构向翅片20侧面延伸凸出的长度为0.05～0.2mm。
如图1和图7所示，在一些实施例的技术方案中，管体10的内表面上形成有内肋结构40。在使用时，内肋结构40用于增大内表面的表面积，在换热时可以提高换热效率，同时还增加了管内流体的扰动程度，从而可以进一步增强换热效率。
在一些实施例的技术方案中，内肋结构40呈螺旋状设置在内表面上，内肋结构40相对于管体10的中心呈角度λ设置，15°≤λ≤60°。在一些实施例中，内肋结构40为多条，多条内肋结构40在内表面上均匀分布。在一些实施例中，内肋结构40为10～80个。
在一些实施例的技术方案中，在管体10的内表面用压槽的衬芯滚压成螺旋状的凸起内肋结构40。内肋结构40相对于管体10的中心呈角度λ设置，同时内肋结构40相对内表面的凸起高度为0.2～0.60mm。
如图2所示，在一些实施例的技术方案中，内肋结构40的截面呈梯形，该截面形状的内肋结构40更便于加工，换热能力也较好。在一些实施例中，内肋结构40的底部与内表面成一体，并与内表面呈圆滑过渡，两顶角呈圆滑过渡。作为其他的可选实施方式，内肋结构40的截面还可以呈三角形。
在本公开的技术方案中，上述的换热管是在专用的翅片加工设备进行加工而成，采用挤压成型无屑加工工艺。本案例采用外径19.05mm，光管壁厚为1.1mm母管进行加工。管外使用带沟槽模具在母管上滚压成沟槽，利用组合刀具对形成的沟槽进行挤压，形成沿轴向螺旋的独立翅片，在独立翅片上因加工翅片产生的形变，而形成连通槽。翅片顶部同时采用滚花模具对独立翅片顶部进行二次挤压形成凸台结构。内肋结构40强化同步进行，在利用组合刀具挤压外表面的同时，内侧使用多头带沟槽结构的衬芯同步挤压形成。
需要说明的是，上述换热管的技术方案尤其适用于冷凝管。
本公开还提供了一种空调器，该空调器包括上述的换热管。采用上述换热管的空调器，换热性能更好，制冷效率更高。
以上所述仅为本公开的优选实施例而已，并不用于限制本公开，对于本领域的技术人员来说，本公开实施例可以有各种更改和变化。凡在本公开的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本公开的保护范围之内。

Claims (15)

  1. 一种换热管，包括管体(10)和设置在所述管体(10)的外表面(11)上的翅片(20)，相邻的所述翅片(20)之间形成有通道(30)，其中，所述翅片(20)上开设有连通槽(21)，所述连通槽(21)将相邻的所述通道(30)连通，所述连通槽(21)用于流通冷媒。
  2. 根据权利要求1所述的换热管，其中，所述翅片(20)在所述外表面(11)上沿所述外表面(11)的圆周方向盘绕设置，所述连通槽(21)在所述翅片(20)上沿所述外表面(11)的轴向方向开设。
  3. 根据权利要求2所述的换热管，其中，所述翅片(20)在所述外表面(11)上呈螺旋状盘绕设置。
  4. 根据权利要求2所述的换热管，其中，所述翅片(20)为多条，多条所述翅片(20)在所述外表面(11)上间隔设置。
  5. 根据权利要求1所述的换热管，其中，所述连通槽(21)在所述翅片(20)上深度开设到所述翅片(20)的底部，或者开设到距离所述翅片(20)的底部预定长度的位置。
  6. 根据权利要求1所述的换热管，其中，所述连通槽(21)为多个，多个所述连通槽(21)在所述翅片(20)上间隔设置。
  7. 根据权利要求1所述的换热管，其中，所述连通槽(21)相对于所述翅片(20)的延伸方向呈角度β设置，0°＜β≤90°。
  8. 根据权利要求1所述的换热管，其中，所述连通槽(21)的截面呈V形、U形或者Y形。
  9. 根据权利要求1所述的换热管，其中，所述翅片(20)上压制有凸台结构(22)，所述凸台结构(22)用于增大所述翅片(20)的表面积。
  10. 根据权利要求9所述的换热管，其中，所述凸台结构(22)包括位于所述翅片(20)的顶部的凹槽部(221)以及相对于所述翅片(20)的侧面凸出的尖角部(222)。
  11. 根据权利要求9所述的换热管，其中，所述凸台结构(22)相对于所述翅片(20)的延伸方向呈角度α设置，15°≤α≤65°。
  12. 根据权利要求1所述的换热管，其中，所述管体(10)的内表面上形成有内肋结构(40)，所述内肋结构(40)用于增大所述内表面的表面积。
  13. 根据权利要求12所述的换热管，其中，所述内肋结构(40)呈螺旋状设置在所述内表面上，所述内肋结构(40)相对于所述管体(10)的中心呈角度λ设置，15°≤λ≤60°。
  14. 根据权利要求12所述的换热管，其中，所述内肋结构(40)的截面呈梯形或三角形。
  15. 一种空调器，包括换热管，其中，所述换热管为权利要求1至14中任一项所述的换热管。
PCT/CN2018/120241 2018-08-30 2018-12-11 换热管及空调器 Ceased WO2020042425A1 (zh)

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CN110108148A (zh) * 2019-05-29 2019-08-09 珠海格力电器股份有限公司 换热管及设有其的空调器
CN113124702A (zh) * 2019-12-31 2021-07-16 深圳山源电器股份有限公司 一种传热管散热结构及其制作方法
CN111854502A (zh) * 2020-07-08 2020-10-30 珠海格力电器股份有限公司 换热管及空调机组
CN111947497A (zh) * 2020-08-25 2020-11-17 珠海格力电器股份有限公司 换热管及空调机组
CN120444741B (zh) * 2025-07-07 2025-09-12 珠海格力电器股份有限公司 换热结构、换热控制方法及新风系统

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