WO2021114738A1 - 换热管、换热器及空调器 - Google Patents

换热管、换热器及空调器 Download PDF

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Publication number
WO2021114738A1
WO2021114738A1 PCT/CN2020/112202 CN2020112202W WO2021114738A1 WO 2021114738 A1 WO2021114738 A1 WO 2021114738A1 CN 2020112202 W CN2020112202 W CN 2020112202W WO 2021114738 A1 WO2021114738 A1 WO 2021114738A1
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WIPO (PCT)
Prior art keywords
heat exchange
fin
tube body
exchange tube
tube according
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PCT/CN2020/112202
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English (en)
French (fr)
Inventor
刘华
张治平
胡东兵
胡海利
岳清学
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珠海格力电器股份有限公司
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Publication of WO2021114738A1 publication Critical patent/WO2021114738A1/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
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/04—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by preventing the formation of continuous films of condensate on heat-exchange surfaces, e.g. by promoting droplet formation
    • 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
    • F25B2339/02—Details of evaporators
    • 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 belongs to the field of heat exchange technology, and specifically relates to a heat exchange tube, a heat exchanger and an air conditioner.
  • the freon refrigerant drips row by row in the evaporating tube.
  • the freon refrigerant on the evaporating tube must ensure that there is enough amount to quickly enter the cavity on the outer surface, so as to prevent part of the surface from being caused by the refrigerant.
  • the surface of the flooded evaporator tube is smooth, which can only provide the vaporization core used for evaporation, and cannot drain, extend, or stagnate the Freon refrigerant.
  • the present disclosure provides a heat exchange tube, a heat exchanger, and an air conditioner.
  • the present disclosure provides a heat exchange tube, including:
  • Fin components the fin components are spirally distributed on the outer wall of the tube along the axis of the tube;
  • Fin components include:
  • the root of the wing which is connected to the tube;
  • the fin base is formed by bending from the end of the fin root to one side.
  • the fin base and the fin base form a ⁇ -shaped fin.
  • a cavity structure is formed between the ⁇ -shaped fins adjacent in the axial direction of the tube body, which are adjacent to each other in the circumferential direction of the tube body. There are gaps between the ⁇ -shaped fins;
  • the convex part is arranged on the fin base part, and the convex part forms a cross flow channel on the outer surface of the fin assembly.
  • the protrusion is a cone-like boss.
  • the number of fin assemblies distributed along the circumference of the tube body is 50-170.
  • the circumferential spacing of the cavity structure in the cross section of the tube body is 0.03 mm-0.6 mm.
  • the helix angle of the fin assembly helically distributed on the outer wall of the tube is 0.2°-5°.
  • the number of protrusions provided on the fin base is 1-5.
  • the span of the protrusion along the axial or circumferential direction of the tube body is 0.03 mm-0.3 mm.
  • the height of the protrusion is 0.05 mm-0.2 mm.
  • the inner wall of the tube is provided with a threaded internal tooth structure
  • the number of screw heads of the internal tooth structure is 6 to 90
  • the tooth tip angle of the internal tooth structure is 10°-120°
  • the helix angle is 10° -75°
  • the tooth height of the internal tooth structure is 0.1mm-0.6mm.
  • the present disclosure also provides a heat exchanger, including any one of the above heat exchange tubes.
  • the present disclosure also provides an air conditioner, which includes any of the above heat exchange tubes.
  • Fig. 1 is a schematic structural diagram of a heat exchange tube according to an embodiment of the disclosure
  • Fig. 2 is a schematic diagram of a partial structure of a heat exchange tube according to an embodiment of the disclosure.
  • an embodiment of the present disclosure provides a heat exchange tube.
  • the heat exchange tube includes: a tube body 1; a fin assembly 2.
  • the fin assembly 2 is distributed in a spiral shape along the axis of the tube body 1 in the tube.
  • Body 1 outer wall.
  • the fin assembly 2 includes a fin base 3, a fin base 4 and a protrusion 7.
  • the fin base 3 is connected to the tube body 1.
  • the wing base part 4 is formed by bending from the end of the fin base part 3 to one side.
  • the fin base part 3 and the fin base part 4 form a ⁇ -shaped fin (L-shaped fin), a cavity structure 5 is formed between the ⁇ -shaped fins adjacent in the axial direction of the tube body 1, and the ⁇ -shaped fins adjacent in the circumferential direction of the tube body 1 A gap 6 is left between the fins; the protrusion 7 is arranged on the fin base 4, and the protrusion 7 forms a cross flow channel on the outer surface of the fin assembly 2.
  • the protrusion 7 is a cone-like boss.
  • the number of fin assemblies 2 distributed along the outer circumference of the tube body 1 is 50-170, that is, the number of spiral heads of the spiral fins is 50-170, preferably 130.
  • the circumferential spacing of the cavity structure 5 in the cross section of the tube body 1 is 0.03 mm-0.6 mm, preferably 0.32 mm.
  • the spiral angle of the fin assembly 2 spirally distributed on the outer wall of the tube body 1 is 0.2°-5°, preferably 29', which is approximately equal to 0.4833°.
  • the number of protrusions 7 provided on the fin base portion 4 is 1-5, preferably two.
  • the span of the protrusion 7 along the axial or circumferential direction of the tube body 1 is 0.03 mm-0.3 mm.
  • the height of the protrusion 7 is 0.05 mm-0.2 mm, preferably 0.05 mm.
  • the many cavity structures 5 formed by the gaps between the ⁇ -shaped fins provide the vaporization core when the refrigerant evaporates, thereby enhancing the evaporation heat exchange;
  • the cavity structures 5 are connected along the spirally formed annular channel, The annular flow of the refrigerant is enhanced, and the disturbance of the vapor and liquid phases when the refrigerant evaporates, thereby enhancing the heat exchange effect;
  • the refrigerant evaporates, the refrigerant can be continuously filled in, and the refrigerant vapor is discharged, so that the evaporation can continue to form a continuous evaporation process.
  • the outer surface of the fin assembly 2 of this embodiment is provided with one or more protrusions 7, which can increase the roughness of the outer surface of the heat exchange tube, increase the contact area between the refrigerant and the heat exchange tube, and ensure that the refrigerant can be exchanged with each other.
  • the outer surface of the heat pipe is fully contacted to enhance the heat exchange effect; it can delay the falling speed of part of the refrigerant, ensure that enough refrigerant can enter the cavity structure 5, and ensure a continuous evaporation process.
  • a plurality of protrusions 7 form a cross flow channel on the outer surface, which can guide the excess refrigerant on the outer surface of the heat exchange tube to avoid the accumulation of refrigerant on the outer surface of the heat exchange tube. On the one hand, it can prevent the outer surface of the tube from forming too thick.
  • the liquid film is not conducive to heat transfer, and causes the lower tube to lack refrigerant and dry evaporation; on the other hand, it can prevent the upper row of refrigerant from dripping on the excessively thick liquid film, causing the refrigerant to splash, and cannot participate in heat exchange , Resulting in reduced heat transfer efficiency; the cross flow channel can also ensure the directionality of the refrigerant falling, prevent the deviation when the refrigerant drips, and cannot drip to the tube directly below, so that the lower row tube lacks refrigerant and causes dryness. At the same time, the refrigerant cannot contact with the heat exchange tube and the efficiency of the evaporator is reduced.
  • the inner wall of the tube body 1 is provided with a threaded internal tooth structure 8, which increases the heat transfer area of the heat transfer tube and can enhance the turbulent flow of the fluid in the heat transfer tube to increase the heat exchange efficiency in the tube.
  • the number of screw heads of 8 is 6-90
  • the tip angle of the internal tooth structure 8 is 10°-120°
  • the tooth height of the internal tooth structure 8 is 0.1mm-0.6mm.
  • the cross section of the internal tooth structure 8 is triangular-like, and the included angle between the internal tooth structure 8 and the axis of the tube body 1, that is, the spiral angle ranges from 10° to 75°.
  • the number of spiral heads of the internal tooth structure 8 is 56, the tooth tip angle of the internal tooth structure 8 is 40°, the tooth height of the internal tooth structure 8 is 0.42mm, and the axis of the internal tooth structure 8 and the tube body 1 The included angle is 48°.
  • the internal tooth structure 8 of the heat exchange tube, the fin assembly 2 and the tube body 1 are integrally formed.
  • the specific process is as follows: first process the spiral fins on the outer surface of the heat exchange tube body 1, then use a knurling knife to cut the spiral fins into multiple independent fins, and then roll the fins with a rolling cutter Form into a ⁇ shape, and finally use a special knife to press the convex part on the fin.
  • the use of rolling and spinning technology does not increase the manufacturing materials of the heat exchange tube, which not only saves the production cost, but also increases the strength and heat transfer area of the heat exchange tube.
  • the embodiment of the present disclosure also provides a heat exchanger, which includes any of the above heat exchange tubes.
  • the embodiment of the present disclosure also provides an air conditioner, which includes any of the heat exchange tubes described above.
  • the heat exchange tube, heat exchanger and air conditioner provided by the present disclosure have at least the following beneficial effects:
  • the heat exchange tube of the present disclosure includes many cavities, which can enhance the evaporative heat exchange and the annular axial flow of the refrigerant; the outer surface of the fin assembly is provided with protrusions, which increase the surface roughness of the heat exchange tube and increase the heat exchange area at the same time , Forming a cross flow channel on the outer surface of the heat exchange tube to drain the excess refrigerant.

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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，换热管包括：管体（1）和翅片组件（2），翅片组件（2）沿管体（1）的轴线呈螺旋状分布在管体（1）外壁，包括翅根部（3）、翅台部（4）和凸起部（7），翅根部（3）连接在管体（1）上，翅台部（4）从翅根部（3）末端向一侧弯曲形成，翅根部（3）与翅台部（4）形成Г形翅片，沿管体（1）轴向相邻的Г形翅片之间形成空穴结构（5），沿管体（1）轴向相邻的Г形翅片之间留有缝隙（6）；还包括凸起部（7），设置于翅台部（4）上，凸起部（7）在翅片组件（2）外表面形成交叉流道。

Description

换热管、换热器及空调器
相关申请的交叉引用
本公开是以申请号为201911258683.X，申请日为2019年12月10日，公开名称为“换热管、换热器及空调器”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公开中。
技术领域
本公开属于换热技术领域，具体涉及一种换热管、换热器及空调器。
背景技术
在降膜蒸发器中，氟利昂制冷剂逐排蒸发管滴落，在蒸发管上的氟利昂制冷剂一方面要保证有足够的量能迅速进入外表面的空穴中，这样可防止部分表面因冷媒不够导致干斑的产生；另一方面，要能迅速在管外表面沿轴向和周向延展，防止管表面冷媒积累太多，同时防止上排冷媒继续滴落时发生飞溅现象，使部分冷媒不能参与换热；同时，冷媒从上向下滴淋时，还需有一定的方向性，能保证上排管的冷媒正好滴落在下排管上方，使所有的冷媒都能够进行换热。
而满液式蒸发管表面光滑，仅能提供蒸发所用的汽化核心，不能引流、延展、停滞氟利昂制冷剂。这就意味着降膜蒸发的独特换热形式不能得到充分强化，因此迫切需要一种专用于降膜蒸发器的降膜蒸发管，既能提供核态沸腾所需的汽化核心，又能强化对流换热。
公开内容
因此，本公开提供一种换热管、换热器及空调器。
本公开提供一种换热管，包括：
管体；
翅片组件，翅片组件沿管体的轴线呈螺旋状分布在管体外壁；
翅片组件包括：
翅根部，翅根部连接在管体上；
翅台部，从翅根部末端向一侧弯曲形成，翅根部与翅台部形成Г形翅片，沿管体 轴向相邻的Г形翅片之间形成空穴结构，沿管体周向相邻的Г形翅片之间留有缝隙；和
凸起部，设置于翅台部上，凸起部在翅片组件外表面形成交叉流道。
在一些实施例中，凸起部为类锥型凸台。
在一些实施例中，翅片组件沿管体轴向每英寸设有11-60个。
在一些实施例中，翅片组件沿管体的圆周分布数量为50-170个。
在一些实施例中，空穴结构在管体横截面内的周向间距为0.03mm-0.6mm。
在一些实施例中，翅片组件在管体外壁螺旋状分布的螺旋角为0.2°-5°。
在一些实施例中，翅台部上设置的凸起部的数量为1-5个。
在一些实施例中，凸起部的沿管体轴向或周向的跨度为0.03mm-0.3mm。
在一些实施例中，凸起部的高度为0.05mm-0.2mm。
在一些实施例中，管体内壁设有螺纹状的内齿结构，内齿结构的螺旋头数为6-90个，内齿结构的齿顶角为10°-120°，螺旋角为10°-75°，内齿结构的齿高为0.1mm-0.6mm。
本公开还提供一种换热器，包括上述任一的换热管。
本公开还提供一种空调器，包括上述任一的换热管。
附图说明
图1为本公开实施例的换热管的结构示意图；
图2为本公开实施例的换热管的局部结构示意图。
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，下面将结合本公开具体实施例及相应的附图对本公开技术方案进行清楚、完整地描述。显然，所描述的实施例仅是本公开一部分实施例，而不是全部的实施例。基于本公开中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都属于本公开保护的范围。
结合图1至图2所示，本公开实施例提供一种换热管，换热管包括：管体1；翅片组件2，翅片组件2沿管体1的轴线呈螺旋状分布在管体1外壁。翅片组件2包括翅根部3、翅台部4和凸起部7。翅根部3连接在管体1上。翅台部4从翅根部3末 端向一侧弯曲形成。翅根部3与翅台部4形成Г形翅片(L形翅片)，沿管体1轴向相邻的Г形翅片之间形成空穴结构5，沿管体1周向相邻的Г形翅片之间留有缝隙6；凸起部7设置在翅台部4上，凸起部7在翅片组件2外表面形成交叉流道。
在一些实施例中，凸起部7为类锥型凸台。
在一些实施例中，翅片组件2沿管体1轴向每英寸设有11-60个，优选为56个。
在一些实施例中，翅片组件2沿管体1的外圆周分布数量为50-170个，即螺旋状翅片的螺旋头数为50-170个，优选地为130个。
在一些实施例中，空穴结构5在管体1横截面内的周向间距为0.03mm-0.6mm，优选地为0.32mm。
在一些实施例中，翅片组件2在管体1外壁螺旋状分布的螺旋角为0.2°-5°，优选的为29’，约等于0.4833°。
在一些实施例中，翅台部4上设置的凸起部7的数量为1-5个，优选为2个。
在一些实施例中，凸起部7的沿管体1轴向或周向的跨度为0.03mm-0.3mm。
在一些实施例中，凸起部7的高度为0.05mm-0.2mm，优选地为0.05mm。
本公开实施例中Г形翅片间的间隙所形成的许多空穴结构5，提供了制冷剂蒸发时的汽化核心，从而强化了蒸发换热；空穴结构5沿螺旋相连形成的环形通道，增强了制冷剂环向流动，增强制冷剂蒸发时汽液相的扰动，从而增强换热效果；每个空穴结构5之间都存在轴向和周向间隙，利于制冷剂进入空穴，保证制冷剂蒸发时制冷剂能够源源不断的补入，和制冷剂蒸汽的排出，使蒸发能持续进行，形成连续不断的蒸发过程。
本实施例的翅片组件2外表面设置有一个或多个的凸起部7，可增加换热管外表面的粗糙度，增加制冷剂与换热管的接触面积，保证制冷剂能和换热管外表面充分接触，增强换热效果；并可延缓部分制冷剂的下落速度，保证足够多的制冷剂能够进入空穴结构5，保证形成连续不断的蒸发过程。
同时，多个凸起部7在外表面形成交叉流道，可对换热管外表面多余的制冷剂进行引流，避免制冷剂堆积在换热管外表面，一方面可防止管外表面形成过厚的液膜不利于传热，以及造成下排管缺少制冷剂而发生干蒸；另一方面，可防止上排制冷剂滴落在过厚的液膜上造成制冷剂飞溅，而不能参与换热，导致传热效率降低；交叉流道还可保证制冷剂下落的方向性，防止制冷剂滴落时发生偏移，不能滴落到正下方的管子上，从而使下排管缺少制冷剂造成干蒸，同时使制冷剂无法与换热管接触造成蒸发 器效率降低。
在一些实施例中，管体1内壁设有螺纹状的内齿结构8，增大换热管的传热面积，并且能够增强传热管内流体紊流，使管内换热效率增加，内齿结构8的螺旋头数为6-90个，内齿结构8的齿顶角为10°-120°，内齿结构8的齿高为0.1mm-0.6mm。内齿结构8的截面为类三角形，内齿结构8与管体1的轴线夹角，即螺旋角范围为10°～75°。最优的设计中内齿结构8的螺旋头数为56个，内齿结构8的齿顶角为40°，内齿结构8的齿高为0.42mm，内齿结构8与管体1的轴线夹角为48°。
本实施例的换热管内齿结构8与翅片组件2与管体1一体成型加工。具体加工过程为：先在换热管管体1外表面加工出螺旋翅片，接着利用滚花刀将螺旋翅片切割成多个独立翅片，随后用滚压刀具将翅片滚压弯折成Г形，最后用专用刀具在翅片上压制出凸起部。采用滚压和旋压技术加工不增加换热管的制造材料，既节约了生产成本，又能增加换热管的强度和传热面积。
本公开实施例还提供一种换热器，包括上述任一的换热管。
本公开实施例还提供一种空调器，包括上述任一的换热管。
本公开提供的换热管、换热器及空调器至少具有下列有益效果：
本公开的换热管包括许多空穴结构，能够强化蒸发换热，增强制冷剂环向轴向流动；翅片组件外表面设置凸起部，增加换热管表面粗糙度，增加换热面积同时，在换热管外表面形成交叉流道，将多余制冷剂引流。
本领域的技术人员容易理解的是，在不冲突的前提下，上述各有利方式可以自由地组合、叠加。
以上仅为本公开的较佳实施例而已，并不用以限制本公开，凡在本公开的原则之内所作的任何修改、等同替换和改进等，均应包含在本公开的保护范围之内。以上仅是本公开的优选实施方式，应当指出，对于本技术领域的普通技术人员来说，在不脱离本公开技术原理的前提下，还可以做出若干改进和变型，这些改进和变型也应视为本公开的保护范围。

Claims (12)

  1. 一种换热管，包括：
    管体(1)；和
    翅片组件(2)，所述翅片组件(2)沿所述管体(1)的轴线呈螺旋状分布在所述管体(1)外壁；
    其中，所述翅片组件(2)包括：
    翅根部(3)，所述翅根部(3)连接在所述管体(1)上；
    翅台部(4)，从所述翅根部(3)末端向一侧弯曲形成，所述翅根部(3)与所述翅台部(4)形成Г形翅片，沿所述管体(1)轴向相邻的所述Г形翅片之间形成空穴结构(5)，沿所述管体(1)周向相邻的Г形翅片之间留有缝隙(6)；和
    凸起部(7)，设置于所述翅台部(4)上，所述凸起部(7)在所述翅片组件(2)外表面形成交叉流道。
  2. 根据权利要求1所述的换热管，其中，所述凸起部(7)为类锥型凸台。
  3. 根据权利要求1所述的换热管，其中，所述翅片组件(2)沿所述管体(1)轴向每英寸设有11-60个。
  4. 根据权利要求1所述的换热管，其中，所述翅片组件(2)沿所述管体(1)的圆周分布数量为50-170个。
  5. 根据权利要求1所述的换热管，其中，所述空穴结构(5)在所述管体(1)横截面内的周向间距为0.03mm-0.6mm。
  6. 根据权利要求1所述的换热管，其中，所述翅片组件(2)在所述管体(1)外壁螺旋状分布的螺旋角为0.2°-2.5°。
  7. 根据权利要求1-6任一所述的换热管，其中，所述翅台部(4)上设置的所述凸起部(7)的数量为1-5个。
  8. 根据权利要求7所述的换热管，其中，所述凸起部(7)的沿所述管体(1)轴向或周向的跨度为0.03mm-0.3mm。
  9. 根据权利要求7所述的换热管，其中，所述凸起部(7)的高度为0.05mm-0.2mm。
  10. 根据权利要求1-6、8、9任一所述的换热管，其中，所述管体(1)内壁设有螺纹状的内齿结构(8)，所述内齿结构(8)的螺旋头数为6-90个，所述内齿结构(8)的齿顶角为10°-120°，螺旋角为10°-75°，所述内齿结构(8)的齿高为0.1mm-0.6mm。
  11. 一种换热器，包括权利要求1-10任一所述的换热管。
  12. 一种空调器，包括权利要求1-10任一所述的换热管。
PCT/CN2020/112202 2019-12-10 2020-08-28 换热管、换热器及空调器 WO2021114738A1 (zh)

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