WO2012034436A1 - 制冷剂导管和具有该制冷剂导管的换热器 - Google Patents

制冷剂导管和具有该制冷剂导管的换热器 Download PDF

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Publication number
WO2012034436A1
WO2012034436A1 PCT/CN2011/076419 CN2011076419W WO2012034436A1 WO 2012034436 A1 WO2012034436 A1 WO 2012034436A1 CN 2011076419 W CN2011076419 W CN 2011076419W WO 2012034436 A1 WO2012034436 A1 WO 2012034436A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
refrigerant conduit
conduit
wall
header
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2011/076419
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English (en)
French (fr)
Inventor
刘华钊
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Danfoss Sanhua Hangzhou Micro Channel Heat Exchanger Co Ltd
Original Assignee
Danfoss Sanhua Hangzhou Micro Channel Heat Exchanger Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Danfoss Sanhua Hangzhou Micro Channel Heat Exchanger Co Ltd filed Critical Danfoss Sanhua Hangzhou Micro Channel Heat Exchanger Co Ltd
Priority to US13/822,612 priority Critical patent/US9528778B2/en
Publication of WO2012034436A1 publication Critical patent/WO2012034436A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • F28F9/0268—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box in the form of multiple deflectors for channeling the heat exchange medium
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • F25B39/028—Evaporators having distributing means

Definitions

  • the present invention relates to a refrigerant conduit for a heat exchanger, particularly a distributor or collector for use in a heat exchanger, and a heat exchanger having the refrigerant conduit.
  • At least one of the inlet header and the outlet header of a typical heat exchanger may be provided with a refrigerant conduit 100, as shown in Figure 7, which is used as a distributor in the inlet header, at the outlet Used as a collector in the header.
  • the refrigerant conduit 100 includes a plurality of generally circular openings 1 11 disposed along its length, the centerline 1 13 of each of the openings being substantially in the radial direction of the refrigerant conduit .
  • the axial direction of the refrigerant conduit and the center line 1 13 of the opening are perpendicular, so that the refrigerant has a large resistance to discharge in the opening 1 1 1 and a large pressure drop, which is disadvantageous for the distribution of the refrigerant.
  • An object of the present invention is to provide a refrigerant conduit and a heat exchanger having the same, which can improve the uniformity of refrigerant distribution.
  • a refrigerant conduit comprising: a pipe wall, an inner cavity formed in the pipe wall; an opening formed in the pipe wall; and a refrigerant guiding portion, At least a portion of the refrigerant guiding portion is disposed to be substantially inclined with respect to an axial direction of the duct for guiding the refrigerant passing through the opening.
  • a refrigerant conduit for a heat exchanger comprising: a pipe wall; and a passage formed in the pipe wall, the passage having an inner wall, wherein the passage At least a portion of the inner wall is generally inclined relative to the axial direction of the conduit.
  • a heat exchanger having the above refrigerant conduit.
  • the refrigerant flows obliquely through the opening with respect to the axial direction of the refrigerant conduit, whereby the resistance loss is small and the refrigerant distribution uniformity is improved.
  • FIG. 1 is a schematic view of a heat exchanger according to an embodiment of the present invention.
  • FIG. 2 is a schematic view of a refrigerant conduit according to a first embodiment of the present invention
  • FIG. 3 is a schematic view of a refrigerant conduit according to a second embodiment of the present invention
  • FIG. 4 is a heat exchanger according to an embodiment of the present invention.
  • Figure 5 is a partial schematic enlarged view of a heat exchanger according to an embodiment of the present invention
  • Figure 6 is a partially schematic enlarged view of a heat exchanger according to an embodiment of the present invention
  • Figure 7 is a conventional refrigeration Schematic diagram of the agent catheter. detailed description
  • a heat exchanger 100 includes: a first header 102; a second header 101, the second header 101 and the first header 102 A predetermined distance is spaced apart; a heat pipe 103 such as a flat tube, and two ends of the heat pipe 103 are respectively connected to the first header 102 and the second header 101 so that the refrigerant passages in the heat pipe 103 are respectively
  • the first header 102 and the second header 101 are in communication; the fins 104; and the refrigerant conduit 10, wherein the refrigerant conduit is disposed in at least one of the first and second headers 10.
  • the heat exchanger can be any suitable heat exchanger, such as single row, multiple row, single loop and multiple loop heat exchangers.
  • the heat exchanger can be a microchannel heat exchanger.
  • the inner manifold portion of the inlet manifold in the multi-circuit of the microchannel heat exchanger and the manifold portion between the loops can also use this refrigerant conduit to direct and distribute refrigerant such as two-phase refrigerant.
  • a refrigerant conduit 10 according to a first embodiment of the present invention includes: a pipe wall 17, in which a cavity 19 is formed, an opening 11 formed in the pipe wall, and a refrigerant guiding portion are formed At least a portion of the refrigerant guiding portion is disposed to be substantially inclined with respect to the axial direction of the conduit for guiding the refrigerant passing through the opening 1 1 .
  • the refrigerant guiding portion is disposed such that the direction of the refrigerant flow flowing through the opening 11 is substantially inclined with respect to the axial direction of the refrigerant pipe 10.
  • the refrigerant guiding portion is disposed such that the refrigerant flow flowing through the opening 11 forms an angle with the axial direction of the conduit of about more than 0 degrees and less than 90 degrees, preferably about 5 degrees to about 75 degrees.
  • one end of the refrigerant conduit 10 is open and the other end can be closed or opened.
  • the spacing dl of the adjacent openings 11 can be gradually decreased along the flow direction of the refrigerant in the refrigerant conduit 10.
  • the pitch dl of the plurality of openings 1 1 may be equal.
  • the refrigerant conduit 10 thus designed can also be used as a collector in the outlet header 102.
  • the refrigerant conduit 10 can be designed to be in the direction from the end portion 31 of the refrigerant conduit 10 to be connected to the refrigerant line to the other end portion 33 of the opposite refrigerant conduit 10, that is, from the end portion From 31 to the other end portion 33, the pitch d1 of the opening 11 can be gradually reduced.
  • the end portion 33 of the refrigerant conduit 10 will be connected to the refrigerant line and the end portion 31 will not be connected to the refrigerant line.
  • a row of openings 1 1 may be provided along the axial direction of the refrigerant conduit 10, or a plurality of rows of openings 1 1, such as two or three rows, may be provided.
  • the openings 1 1 may be arranged substantially in a straight line, or in any other suitable manner, such as along a curved line, along a spiral, or the like.
  • the refrigerant conduit 10 is formed with a circular tube.
  • the refrigerant conduit 10 may also be formed of a tube having other cross-sectional shapes such as an elliptical shape, a rectangular shape, and the like, and the refrigerant conduit 10 may also be formed by a reduced diameter tube.
  • the refrigerant conduit 10 can also be any of those known in the art. Made of a suitable tube.
  • the cross-sectional area of the opening 11 may range from 0.2 square millimeters to 130 square millimeters.
  • the spacing of adjacent openings can range from 10 mm d 1 280 mm.
  • the refrigerant conduit 10 when the above-described refrigerant conduit 10 is used in the header 101 of the heat exchanger 100, the refrigerant flows along the interior of the refrigerant conduit, and the inclined opening 11 leads to the refrigerant. Therefore, the refrigerant is injected into the inner cavity of the collecting pipe along the inclined opening 11, the resistance loss is small, part of the refrigerant can be directly injected into the inner cavity of the flat pipe 103, and the remaining refrigerant is flushed to the end of the collecting pipe 101 and then reversely flowed. The refrigerant is evenly distributed into the remaining flat tubes 103. The refrigerant is mixed in the header 101 so that the gas-liquid mixture is uniform and no stratification occurs.
  • the opening 1 1 is a passage formed in the pipe wall 17, and the axis 13 of the passage is inclined with respect to the axial direction of the refrigerant pipe 10, and the inner wall of the passage forms an example of the refrigerant guiding portion.
  • the angle ? formed by the axis 13 of the passage and the axial direction of the refrigerant conduit 10 is greater than 0 degrees and less than 90 degrees, preferably from about 5 degrees to about 75 degrees.
  • At least a portion of the inner wall of the channel has an angle to the axial direction of the catheter that is greater than 0 degrees and less than 90 degrees, preferably from about 5 degrees to about 75 degrees.
  • the refrigerant conduit 10 can be designed to: in the direction from the end 31 of the refrigerant conduit 10 to be connected to the refrigerant line to the other end 33 of the opposite refrigerant conduit 10,
  • the above-mentioned angle ⁇ can be gradually increased, that is, from the end portion 31 to the other end portion 33, the angle ⁇ formed by the axis 13 of the passage and the axial direction of the refrigerant pipe 10 can be gradually increased.
  • the cross section of the channel may be substantially circular.
  • the inner walls of all channels can be inclined.
  • the cross section of the passage may be other shapes, for example, at least a portion of the inner wall of the passage is inclined and serves as a refrigerant guiding portion, for example, only the inner wall of the passage at the end 31 side is inclined.
  • FIG. 3 shows a refrigerant conduit 10 in accordance with a second embodiment of the present invention.
  • the refrigerant conduit 10 of the second embodiment may be the same as the refrigerant conduit 10 of the first embodiment except for the contents described below.
  • the opening 11 is formed in the tube wall 17.
  • the passage, the axis 13 of the passage is inclined with respect to the axial direction of the duct 10, and the inner wall of the passage forms an example of the refrigerant guiding portion.
  • the angle a of the axis 13 of the channel with the axial direction of the catheter 10 is greater than about 0 degrees and less than 90 degrees, preferably between 5 and 75 degrees.
  • the refrigerant conduit 10 includes an inclined wall portion 21 which is inclined as a portion of the tube wall 17 with respect to the axial direction of the refrigerant conduit 10, and the opening 11 is formed in the inclined wall portion 21.
  • the refrigerant conduit 10 may further include an inclined wall portion 22 by which a portion of the passage inner wall of the opening 1 1 is brought close to the inclined wall portion 22, whereby the inclined wall portion 22 may form a refrigerant guiding portion.
  • FIG. 6 is a partially enlarged schematic view of a heat exchanger 100 in accordance with an embodiment of the present invention.
  • the refrigerant pipe 10 may be provided with an opening 11.
  • the refrigerant pipe 10 when used as a distributor in the inlet header 101, in the direction from the end portion 31 to the other end portion 33 of the refrigerant pipe 10, at the slave end
  • the portion of the heat exchanger tube 103 such as a flat tube having no opening 1 in the range of the opening portion 1 in the range of no opening from the end portion 31 to the end portion 31 - the distance corresponding to the entire portion
  • the ratio of the number of heat exchange tubes 103 in the heat exchange tubes 103 is greater than 20% and less than 99%, so that a good distribution effect can be obtained. Experiments have shown that a very significant uniform distribution of the refrigerant can be obtained when the ratio is greater than 95% and less than 99%.
  • the refrigerant conduit 10 thus designed can also be used as a collector in the outlet header 102 to achieve uniform distribution of refrigerant.
  • the refrigerant conduit 10 may be provided with an opening 1 1 corresponding to the entire heat exchange tube 103.
  • the refrigerant conduit 10 can be designed to: a flat tube-free exchange at a position from the end portion 31 of the refrigerant conduit 10 to be connected to the refrigerant line to a predetermined distance from the end portion 3 1
  • the number of heat pipes 103 is changed from the range of the entire heat exchange tubes 103 corresponding to the refrigerant conduit 10.
  • the ratio of the number T of heat pipes 103 is greater than about 20% and less than about 99%, preferably greater than about 95% and less than about 99%.
  • the other end portion 33 of the refrigerant conduit 10 is closed by an element 35.
  • the member 35 may be omitted, and the other end portion 33 of the refrigerant conduit 10 is open, whereby a very remarkable effect of uniformly distributing the refrigerant can be obtained.
  • the refrigerant conduit 10 thus designed can also be used as a collector in the outlet header 102, thereby achieving the effect of evenly distributing the refrigerant.
  • the two-phase refrigerant in the refrigerant conduit 10 is ejected from the opening 11 and a portion of the two-phase refrigerant directly enters the inner cavity of the heat exchange tube 103 such as a flat tube, and the remaining refrigerant is flushed to the header.
  • the 101-end is reversely flowed, thereby being evenly distributed into the heat exchange tubes 103 such as flat tubes.
  • the refrigerant conduit 10 is opposed to the heat exchange tube 103, or the center line 15 of the refrigerant conduit 10 is on an extension line of the axis 105 of the heat exchange tube 103 such as a flat tube. It will be apparent that the refrigerant conduit 10 and the heat exchange tubes 103 can be positioned in any suitable relative position.
  • the angle ⁇ between the axis 13 of the passage and the longitudinal direction of the heat transfer tube 101 (or the axis 105 of the heat transfer tube 103) is in the range of 0 to 90 degrees, whereby a good distribution effect can be obtained.
  • the refrigerant flows along the inner cavity of the refrigerant conduit, and the refrigerant guiding portion mainly serves to guide the refrigerant, and the refrigerant is injected into the inner cavity of the collecting pipe along the refrigerant guiding portion, and the resistance loss is small.
  • Part of the refrigerant can be directly injected into the inner cavity of the heat pipe, and the remaining refrigerant is flushed to one end of the header and then distributed in the opposite direction and evenly distributed to the remaining heat pipe.
  • the refrigerant is mixed in the header so that the gas-liquid mixture is uniform and no delamination occurs.
  • the refrigerant guiding portion may be any suitable member for guiding the refrigerant or changing the direction of the refrigerant, and the member may be separately formed and connected. It is formed inside or outside the refrigerant conduit or integrally with the refrigerant conduit.

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

Description

制冷剂导管和具有该制冷剂导管的换热器 技术领域
本发明涉及一种用于换热器的制冷剂导管，尤其是用于换热器中 的分配器或收集器， 和具有该制冷剂导管的换热器。
背景技术
典型的换热器的入口集流管和出口集流管中的至少一个可以设 有制冷剂导管 100， 如图 7所示， 该制冷剂导管在入口集流管中用作 分配器， 在出口集流管中用作收集器。
现有技术中， 如图 7所示， 制冷剂导管 100包括沿其长度布置的 多个大体圆形的开口 1 11， 该开口中的每一个的中心线 1 13大致在制 冷剂导管的径向上。 此种制冷剂导管的轴向和开口中心线 1 13垂直， 因此制冷剂在开口 1 1 1中喷出的阻力大， 压降大， 不利于制冷剂的分 配。
发明内容
本发明的目的是提供一种制冷剂导管和具有该制冷剂导管的换 热器， 该冷剂导管能够提高制冷剂分配的均匀性。
根据本发明的一个方面， 本发明提供了一种制冷剂导管， 该制冷 剂导管， 包括： 管壁， 该管壁内形成内腔； 形成在管壁中的开口； 以 及制冷剂导向部分，该制冷剂导向部分的至少一部分设置为相对于导 管的轴向大致倾斜， 用于引导通过所述开口的制冷剂。
根据本发明的另一方面，本发明提供了一种用于换热器的制冷剂 导管， 该导管包括： 管壁； 以及形成在管壁中的通道， 所述通道具有 内壁， 其中所述通道的内壁的至少一部分相对于导管的轴向大致倾 斜。 根据本发明的一个方面，本发明提供一种具有上述制冷剂导管的 换热器。
通过采用本发明的制冷剂导管的一些实施方式，制冷剂通过开口 相对于制冷剂导管的轴向倾斜流动， 由此阻力损失较小且提高了制冷 剂分配均匀性。
附图说明
图 1为根据本发明的实施例的换热器的示意图；
图 2为根据本发明的第一实施例的制冷剂导管的示意图； 图 3为根据本发明的第二实施例的制冷剂导管的示意图； 图 4为根据本发明的实施例的换热器的局部示意放大图； 图 5为根据本发明的实施例的换热器的局部示意放大图； 图 6为根据本发明的实施例的换热器的局部示意放大图； 以及 图 7为传统的制冷剂导管的示意图。 具体实施方式
下面结合附图及具体实施方式对本发明做进一步说明。
如图 1所示， 根据本发明的实施例的换热器 100包括： 第一集流 管 102;第二集流管 101，所述第二集流管 101与所述第一集流管 102 间隔开预定距离； 诸如扁管的散热管 103， 所述散热管 103的两端分 别与所述第一集流管 102和第二集流管 101相连以便散热管 103内的 制冷剂通道分别与所述第一集流管 102和第二集流管 101相连通；翅 片 104; 以及制冷剂导管 10， 所述第一和第二集流管中的至少一个内 设有所述制冷剂导管 10。 该换热器可以是任何合适的换热器， 例如 单排、 多排、 单回路和多回路换热器等。 此外， 该换热器可以是微通 道换热器。例如， 微通道换热器多回路中的进口集流管内腔部分以及 回路之间的集流管内腔部分也可釆用此制冷剂导管对诸如两相制冷 剂的制冷剂进行导向和分配。 实施例 1
图 2 示出了根据本发明的第一实施例的制冷剂导管 10。 如图 1 所示， 根据本发明的第一实施例的制冷剂导管 10包括： 管壁 17， 该 管壁 Π内形成内腔 19， 形成在管壁中的开口 1 1， 以及制冷剂导向部 分，该制冷剂导向部分的至少一部分设置为相对于导管的轴向大致倾 斜-， 用于引导通过所述开口 1 1 的制冷剂。 该制冷剂导向部分设置为 使得通过开口 1 1流动的制冷剂流的方向相对于制冷剂导管 10的轴向 大致倾斜。 例如， 该制冷剂导向部分设置为使得通过开口 1 1流动的 制冷剂流与导管的轴向所成的角度为大约大于 0度并且小于 90度， 优选大约 5度至大约 75度。 参照图 4和 5， 制冷剂导管 10的一端开 口， 另一端可封闭也可开口。
对于制冷剂导管 10用作分配器时，沿着制冷剂导管 10中的制冷 剂流动方向， 相邻开口 1 1的间距 dl可以逐渐减小。 作为选择， 多个 开口 1 1的间距 dl可以相等。
如此设计的制冷剂导管 10同样可以在出口集流管 102中用作收 集器。
参照图 4和 5， 无论制冷剂导管 10在入口集流管 101 中用作分 配器还是在出口集流管 102中用作收集器， 制冷剂导管 10的端部 31 都将与制冷剂管路连接， 另一端部 33将不与制冷剂管路连接。 因此， 可以将冷剂导管 10设计为： 在从将与制冷剂管路连接的制冷剂导管 10的端部 31到相对的制冷剂导管 10的另一个端部 33的方向上， 即 从端部 31到另一端部 33， 开口 1 1的间距 dl可以逐渐减小。 作为选 择， 制冷剂导管 10的端部 33将与制冷剂管路连接， 端部 31将不与 制冷剂管路连接。
可以沿制冷剂导管 10的轴向方向， 设置一排开口 1 1， 或设置多 排开口 1 1， 例如两排或三排。 开口 1 1可以大致沿直线排列， 或以任 何其它合适的方式排列， 例如沿曲线排列， 沿螺旋线排列等。
在上面的示例中， 制冷剂导管 10用圆管形成。制冷剂导管 10也 可以用诸如椭圆形、矩形等其它截面形状的管形成， 此外制冷剂导管 10也可以用变径管形成。 制冷剂导管 10也可以用本领域公知的任何 合适的管制成。
开口 11 的横截面积范围可以为 0.2平方毫米至 130平方毫米。 相邻开口间距的范围可以为 10mm d 1 280mm。
参见图 1、 4和 5， 当把上述制冷剂导管 10用于换热器 100的集 流管 101 中时， 制冷剂沿着制冷剂导管内腔流动， 倾斜的开口 1 1起 导向制冷剂的作用， 制冷剂沿着倾斜的开口 11喷射到集流管内腔， 阻力损失较小， 部分制冷剂可以直接射入扁管 103内腔， 剩余制冷剂 冲到集流管 101 —端再反向流动， 使制冷剂均匀分配到余下的扁管 103中。 制冷剂在集流管 101中混合， 使得气液混合均匀， 不产生分 层现象。
如图 2所示， 开口 1 1是形成在管壁 17中的通道， 所述通道的轴 线 13相对于制冷剂导管 10的轴向倾斜，所述通道的内壁形成制冷剂 导向部分的一个示例。所述通道的轴线 13与制冷剂导管 10的轴向所 成的角度 α为大于 0度并且小于 90度，优选为大约 5度至大约 75度。
在一些实施例中，所述通道的内壁的至少一部分与导管的轴向的 夹角为大于 0度并且小于 90度， 优选为大约 5度至大约 75度。
参照图 4和 5， 可以将冷剂导管 10设计为： 在从将与制冷剂管 路连接的制冷剂导管 10的端部 31到相对的制冷剂导管 10的另一个 端部 33的方向上， 上述夹角 α可以逐渐增加， 即从端部 31到另一端 部 33， 所述通道的轴线 13与制冷剂导管 10的轴向所成的角度 α可以 逐渐增加。
所述通道的横截面可以大致是圆形的。全部通道的内壁可以都是 倾斜的。 作为选择， 通道的横截面可以是其它形状的， 例如， 通道的 至少一部分内壁是倾斜的并用作制冷剂导向部分，例如仅仅通道的在 端部 31—侧的内壁是倾斜的。 实施例 2
图 3示出了根据本发明的第二实施例的制冷剂导管 10。 除了下 面描述的内容之外， 第二实施例的制冷剂导管 10与第一实施例的制 冷剂导管 10可以相同。 如图 3所示， 开口 1 1是形成在管壁 17中的 通道， 所述通道的轴线 13相对于导管 10的轴向倾斜， 所述通道的内 壁形成制冷剂导向部分的一个示例。所述通道的轴线 13与导管 10的 轴向所成的角度 α为大约大于 0度并且小于 90度， 优选为 5度至 75 度。 此外， 制冷剂导管 10包括倾斜壁部分 21， 所述倾斜壁部分 21 作为管壁 17的一部分相对于所述制冷剂导管 10的轴向倾斜，所述开 口 1 1形成在倾斜壁部分 21中。
制冷剂导管 10还可以包括倾斜壁部分 22， 通过使开口 1 1 的一 部分通道内壁与倾斜壁部分 22接近， 由此倾斜壁部分 22可以形成制 冷剂导向部分。
下面更具体地描述根据本发明的实施例的换热器 100。 图 4、 5、
6为根据本发明的实施例的换热器 100的局部放大示意图。
参照图 5，在沿集流管 101的轴向上的设有诸如扁管的散热管 103 的区域内， 制冷剂导管 10可以设有开口 1 1。
如图 5所示， 例如， 制冷剂导管 10在入口集流管 101中用作分 配器时， 从制冷剂导管 10的入口侧的端部 3 1到另一端部 33的方向 上， 在从端部 3 1到距离端部 31—定距离的位置的无开口范围内， 制 冷剂导管 10不设开口 1 1， 在无开口范围内的诸如扁管的换热管 103 的数量 Ν与对应于整个换热管 103范围的换热管 103的数量 Τ的比 值为大于 20%且小于 99%，如此可以获得良好的分配效果。实验表明， 在该比值为大于 95%且小于 99%时可以获得非常显著的均匀分配制 冷剂的效果。 如此设计的制冷剂导管 10 同样可以在出口集流管 102 中用作收集器， 实现均匀分配制冷剂的效果。
如图 4所示， 制冷剂导管 10可以在对应于整个换热管 103范围 都设有开口 1 1。
无论制冷剂导管 10在入口集流管 101 中用作分配器还是在出口 集流管 102中用作收集器，制冷剂导管 10的端部 31都将与制冷剂管 路连接， 另一端部 33将不与制冷剂管路连接。 因此， 可以将制冷剂 导管 10 设计为： 在从将与制冷剂管路连接的制冷剂导管 10 的端部 31到距离该端部 3 1预定距离的位置的无开口范围的诸如扁管的换热 管 103的数量 Ν与制冷剂导管 10所对应的整个换热管 103范围的换 热管 103的数量 T的比值为大于大约 20%且小于大约 99%， 优选为 大于大约 95%且小于大约 99%。
如图 5所示， 制冷剂导管 10的另一端部 33用元件 35封闭。 作 为选择， 如图 4所示， 可以不设置元件 35， 制冷剂导管 10的另一端 部 33是开口的， 由此可以获得非常显著的均匀分配制冷剂的效果。 如此设计的制冷剂导管 10同样可以在出口集流管 102中用作收集器， 由此实现均匀分配制冷剂的效果。
当用作分配器时，制冷剂导管 10中的两相制冷剂从开口 1 1喷射 出来， 一部分两相制冷剂直接进入诸如扁管的换热管 103内腔， 剩余 制冷剂冲到集流管 101—端再反向流动， 由此均匀分配到诸如扁管的 换热管 103中。
如图 6所示， 制冷剂导管 10与换热管 103相对， 或者制冷剂导 管 10的中心线 15在诸如扁管的换热管 103的轴线 105的延长线上。 显然， 制冷剂导管 10与换热管 103可以以任何合适的相对位置进行 定位。 通道的轴线 13与换热管 101的长度方向 （或换热管 103的轴 线 105 ) 的夹角 φ在 0度到 90度的范围内， 由此可以获得良好的分配 效果。
在上述实施例中， 制冷剂沿着制冷剂导管内腔流动， 制冷剂导向 部分主要起对制冷剂导向的作用，制冷剂沿着制冷剂导向部分喷射到 集流管内腔， 阻力损失较小， 部分制冷剂可以直接射入散热管内腔， 剩余制冷剂冲到集流管一端再反向流动均匀分配到余下的散热管中。 制冷剂在集流管中混合， 使得气液混合均匀， 不产生分层现象。
上面描述了作为制冷剂导向部分的通道， 但是本发明不限于此， 例如制冷剂导向部分可以是任何合适的用于引导制冷剂的或改制冷 剂的方向的部件，该部件可以单独形成并连接在制冷剂导管的内侧或 外侧， 或与制冷剂导管一体形成。
上述实施例中的各种结构可以通过适当的相互组合而形成新的 实施方式。 一个实施例中的特征， 也可以用于其它实施例， 或替换其 它实施例中的特征。

Claims

权 利 要 求 书
1、 一种用于换热器的制冷剂导管， 包括：
管壁， 该管壁内形成内腔；
形成在管壁中的开口； 以及
制冷剂导向部分，该制冷剂导向部分的至少一部分设置为相对于 导管的轴向大致倾斜， 用于引导通过所述开口的制冷剂。
2、 一种用于换热器的制冷剂导管， 包括：
管壁； 以及
形成在管壁中的通道， 所述通道具有内壁，
其中所述通道的内壁的至少一部分相对于导管的轴向大致倾斜。
3、 根据权利要求 1所述的制冷剂导管， 其中所述开口是形成在 管壁中的通道， 所述通道的内壁形成制冷剂导向部分。
4、 根据权利要求 2或 3所述的制冷剂导管， 其中所述通道的轴 线相对于导管的轴向倾斜。
5、根据权利要求 2至 4中的任意一项所述的制冷剂导管， 包括: 倾斜壁部分， 所述倾斜壁部分作为管壁的一部分相对于所述轴向倾 斜， 所述通道形成在倾斜壁部分中。
6、 根据权利要求 2至 5中的任意一项所述的制冷剂导管， 其中 所述通道的轴线与制冷剂导管的轴向所成的角度为大于 0 度并且小 于 90度， 优选为大约 5度至大约 75度。
7、 根据权利要求 2至 6中的任意一项所述的制冷剂导管， 还包 将与制冷剂管路连接的制冷剂导管的第一端部，以及与第一端部 相对的制冷剂导管的第二端部， 其中，
在从制冷剂导管的第一端部到制冷剂导管的第二端部的方向上， 所述通道的轴线相对于导管的轴向的夹角逐渐增加。
8、 根据权利要求 1、 3至 6中的任意一项所述的制冷剂导管， 还 包括：
将与制冷剂管路连接的制冷剂导管的第一端部，以及与第一端部 相对的制冷剂导管的第二端部， 其中，
在从制冷剂导管的第一端部到制冷剂导管的第二端部的方向上， 所述开口的间距逐渐减小。
9、 根据权利要求 1所述的制冷剂导管， 包括： 倾斜壁部分， 所 述倾斜壁部分作为管壁的一部分相对于所述轴向倾斜，所述开口形成 在倾斜壁部分中。
10、根据权利要求 1所述的制冷剂导管， 其中所述制冷剂导管还 包括：
将与制冷剂管路连接的制冷剂导管的第一端部，以及与第一端部 相对的制冷剂导管的第二端部， 其中
使用中制冷剂导管的第二端部是开口的。
1 1、 一种换热器， 包括：
第一集流管；
第二集流管， 所述第二集流管与所述第一集流管间隔开预定距 离；
散热管，所述散热管的两端分别与所述第一集流管和第二集流管 相连； 和
制冷剂导管，所述第一和第二集流管中的至少一个内设有所述制 冷剂导管， 其中， 所述制冷剂导管为权利要求 1至 10中的任意一项所述的 制冷剂导管。
12、 根据权利要求 1 1所述的换热器， 其中所述制冷剂导管还包 括：
将与制冷剂管路连接的制冷剂导管的第一端部，以及与第一端部 相对的制冷剂导管的第二端部， 以及
从制冷剂导管的第一端部到距离该制冷剂导管的第一端部预定 距离的位置的无开口范围， 其中
在该无开口范围的换热管的数量与所述制冷剂导管所对应的全 部换热管的数量的比值为大于大约 20%且小于大约 99%。
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* Cited by examiner, † Cited by third party
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US9417014B2 (en) 2010-09-13 2016-08-16 Danfoss A/S Refrigerant guiding pipe and heat exchanger having refrigerant guiding pipe
JPWO2013191056A1 (ja) * 2012-06-18 2016-05-26 三菱電機株式会社 熱交換器
DE102015105379B3 (de) * 2015-04-09 2016-06-02 Denso Automotive Deutschland Gmbh Heizwärmetauscher mit Einlassdüse

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