WO2012034437A1 - 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
WO2012034437A1
WO2012034437A1 PCT/CN2011/076423 CN2011076423W WO2012034437A1 WO 2012034437 A1 WO2012034437 A1 WO 2012034437A1 CN 2011076423 W CN2011076423 W CN 2011076423W WO 2012034437 A1 WO2012034437 A1 WO 2012034437A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
refrigerant conduit
conduit
wall portion
axial direction
Prior art date
Application number
PCT/CN2011/076423
Other languages
English (en)
French (fr)
Inventor
刘华钊
穆慑尔·B·安德鲁
埃尔伯尔·斯蒂芬
维斯特加德·博矫恩
Original Assignee
三花丹佛斯（杭州）微通道换热器有限公司
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 三花丹佛斯（杭州）微通道换热器有限公司 filed Critical 三花丹佛斯（杭州）微通道换热器有限公司
Priority to US13/822,609 priority Critical patent/US20130213627A1/en
Priority to JP2013528501A priority patent/JP2013537298A/ja
Priority to EP11824507.5A priority patent/EP2618091A4/en
Publication of WO2012034437A1 publication Critical patent/WO2012034437A1/zh

Links

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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • 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
    • 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
    • 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
    • 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
    • F28D1/0535—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 the conduits having a non-circular cross-section
    • F28D1/05366—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
    • 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
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins

Definitions

  • the present invention relates to a refrigerant conduit, and a heat exchanger having the refrigerant conduit.
  • At least one of the inlet header and the outlet header of a typical heat exchanger is provided with a refrigerant conduit that acts as a distributor in the inlet header and as a collector in the outlet header .
  • the refrigerant conduit includes a plurality of generally circular openings disposed along its length, the centerline of each of the openings being substantially in the radial direction of the refrigerant conduit.
  • the axial direction of the refrigerant conduit is perpendicular to the center line of the opening, so that the refrigerant has a large resistance to discharge in the opening and a large pressure drop, which is disadvantageous for the distribution of the refrigerant.
  • 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 wall portion, At least a portion of the refrigerant guiding wall portion is disposed to be substantially inclined with respect to an axial direction of the duct for guiding the refrigerant passing through the opening.
  • the refrigerant guiding wall portion is a concave wall portion, and the concave wall portion is recessed toward the inner cavity.
  • At least a portion of the edge of the refrigerant guiding wall portion is separated from the tube wall, thereby forming the opening.
  • At least an angle between a middle portion of the refrigerant guiding wall portion in a direction perpendicular to the refrigerant conduit axial direction and an axial direction of the refrigerant conduit is greater than 0 degrees and less than 90 Degree, preferably from about 5 degrees to about 75 degrees, or at least the refrigerant
  • the angle between a portion of the guide wall portion and the axial direction of the refrigerant conduit is greater than 0 degrees and less than 90 degrees, preferably from about 5 degrees to about 75 degrees, or the refrigerant guiding wall portion and the refrigerant conduit
  • the axial angle range is greater than 0 degrees and less than 90 degrees, preferably from about 5 degrees to about 75 degrees.
  • At least a middle portion of the refrigerant guiding wall portion in a direction perpendicular to an axial direction of the refrigerant conduit is formed in a plurality of substantially linear portions in a section along an axial direction of the refrigerant conduit or It is substantially curved, or a cross section of the refrigerant guiding wall portion in the axial direction of the refrigerant conduit is constituted by a plurality of substantially straight portions or substantially curved.
  • At least the first end portion of the recessed wall portion in the axial direction of the refrigerant duct is separated from the tube wall, thereby forming the opening.
  • At least a middle portion of the recessed wall portion in a direction perpendicular to an axial direction of the refrigerant conduit is axially inclined with respect to the refrigerant conduit, or at least the refrigerant guide wall portion a portion is axially inclined with respect to the refrigerant conduit, or the recessed wall portion is axially inclined with respect to the refrigerant conduit, and a first end portion of the recessed wall portion is opposite to the first end portion The second end is closer to the axis of the refrigerant conduit.
  • At least a middle portion of the recessed wall portion in a direction perpendicular to an axial direction of the refrigerant conduit is substantially linear or straight in a cross section in the axial direction of the refrigerant conduit, or
  • the cross section of the recessed wall portion in the axial direction of the refrigerant conduit is substantially linear or straight.
  • At least an angle of a middle portion of the recessed wall portion in a direction perpendicular to an axial direction of the refrigerant conduit and an axial direction of the refrigerant conduit is greater than 0 degrees and less than 90
  • the angle, or the angle between the recessed wall portion and the axial direction of the refrigerant conduit, is greater than 0 degrees and less than 90 degrees.
  • At least a portion of the recessed wall portion in a direction perpendicular to an axial direction of the refrigerant conduit in the axial direction of the refrigerant conduit is constituted by a plurality of substantially straight portions or substantially It is curved, or the cross section of the recessed wall portion in the axial direction of the refrigerant conduit is composed of a plurality of substantially straight portions or substantially curved.
  • 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
  • Figure 3 is a schematic cross-sectional view of a refrigerant conduit according to a first embodiment of the present invention
  • Figure 4 is a second embodiment of the present invention
  • Figure 5 is a schematic cross-sectional view of a refrigerant conduit according to a second embodiment of the present invention
  • Figure 6a is a schematic cross-sectional view of a refrigerant conduit according to a third embodiment of the present invention
  • FIG. 7a is a schematic cross-sectional view of a refrigerant conduit according to a fourth embodiment of the present invention
  • FIG. 7a is a schematic cross-sectional view of a refrigerant conduit according to a fourth embodiment of the present invention
  • FIG. 7b is a schematic view of a refrigerant conduit according to a fourth embodiment of the present invention
  • Figure 8a is a schematic cross-sectional view of a refrigerant conduit according to a fifth embodiment of the present invention
  • Figure 8b is a schematic view of a refrigerant conduit according to a fifth embodiment of the present invention
  • Figures 9a and 9b are heat exchangers according to the present invention A partially schematic enlarged view
  • Figure 10 is a partially schematic enlarged view of a heat exchanger in accordance with the present invention.
  • 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.
  • microchannel heat exchanger The refrigerant manifold can also be used to guide and distribute the two-phase refrigerant in the inner manifold portion of the inlet manifold and the manifold portion between the circuits.
  • the refrigerant conduit 10 according to the first embodiment of the present invention includes: a pipe wall 17 having an inner cavity 19 formed therein, an opening l lb formed in the pipe wall, and The refrigerant guiding wall portion, at least a portion of the refrigerant guiding wall portion is disposed to be substantially inclined with respect to an axial direction of the duct for guiding the refrigerant passing through the opening lib. At least a portion of the edge of the refrigerant guiding wall portion is separated from the tube wall 17, thereby forming the opening.
  • the refrigerant guiding wall portion is disposed such that the direction of the refrigerant flow flowing through the opening l ib is substantially inclined with respect to the axial direction of the refrigerant pipe 10.
  • at least a portion of the refrigerant guiding wall portion has an angle with the axial direction of the conduit of greater than 0 degrees and less than 90 degrees, preferably from about 5 degrees to about 75 degrees.
  • the refrigerant guiding wall portion is disposed such that the flow of the refrigerant flowing through the opening l ib and the axial direction of the conduit are greater than 0 degrees and less than 90 degrees, preferably from about 5 degrees to about 75 degrees.
  • the refrigerant conduit 10 is open at one end and can be closed or open at the other end.
  • the refrigerant conduit 10 further includes a recessed wall portion 23 that is recessed toward the inner cavity 19, preferably at least the first end portion 231 and the tube wall of the recessed wall portion 23 in the axial direction of the refrigerant conduit The 17 are separated from each other, thereby forming the opening l lb.
  • the recessed wall portion 23 constitutes an example of the refrigerant guiding wall portion.
  • At least the central portion 23a of the recessed wall portion 23 in the direction perpendicular to the axial direction of the refrigerant conduit or the recessed wall portion 23 is inclined with respect to the axial direction of the refrigerant conduit 10, or at least the recessed wall portion A portion of the portion 23 is inclined with respect to the axial direction of the refrigerant conduit 10, and the first end portion 231 of the recessed wall portion 23 is closer to the refrigerant conduit than the second end portion 232 opposite to the first end portion 231
  • the central portion 23a extends from the first end portion 231 to the second end portion 232 in the axial direction of the refrigerant conduit 10.
  • a slit having a certain depth is cut in a cutting direction perpendicular to the axial direction of the circular tube, and the slit is cut
  • the wall of one of the tubes in the axial direction is stamped to dent.
  • the orientation of the incision is determined by two directions: one is the incision depth direction (ie, the incision)
  • the depth of the slit is in the radial direction of the circular tube (up and down direction in Fig. 3), and the other is the cutting direction, which is perpendicular to the depth direction of the slit and perpendicular to the axial direction of the tube.
  • the depth direction of the slit may be less than 90 degrees from the radial direction of the tube, and the cutting direction may be less than 90 degrees from the axial direction of the tube.
  • the incision can be an incision in any suitable orientation.
  • the length of the slit in the circumferential direction that is, the length of the arc of the separating portion 12 in which the first end portion 231 and the tube wall are separated from each other is L, and the interval between adjacent openings is dl.
  • At least the middle portion 23a of the recessed wall portion 23 in the direction perpendicular to the axial direction of the refrigerant conduit 10 is substantially linear or straight in cross section along the axial direction of the refrigerant conduit, At least the inclination angle of the central portion 23a of the recessed wall portion 23 in the direction perpendicular to the axial direction of the refrigerant conduit with respect to the axial direction of the refrigerant conduit 10 is ⁇ .
  • a cross section of the recessed wall portion 23 in the axial direction of the refrigerant conduit is substantially linear or straight, and an inclination angle of the recessed wall portion 23 with respect to an axial direction of the refrigerant conduit 10 is ⁇ .
  • At least the angle ⁇ between the central portion 23a of the recessed wall portion 23 in the direction perpendicular to the axial direction of the refrigerant conduit and the axial direction of the refrigerant conduit 10 is greater than 0 degrees and less than 90 degrees, preferably An angle ⁇ of about 5 to 75 degrees, or the axial direction of the recessed wall portion 23 and the refrigerant conduit 10 is greater than 0 degrees and less than 90 degrees, preferably about 5 to 75 degrees.
  • the refrigerant conduit 10 thus designed can also be used as a collector in the outlet header 101.
  • the end portion 31 of the refrigerant conduit 10 can be connected to the refrigerant line, whether the refrigerant conduit 10 acts as a distributor in the inlet header 102 or as a collector in the outlet header 101.
  • the other end portion 33 may not be connected to the refrigerant line, or the end portion 33 of the refrigerant conduit 10 may be connected to the refrigerant line, and the end portion 31 may not be connected to the refrigerant line.
  • a row of openings l ib may be provided along the axial direction of the refrigerant conduit 10, or a plurality of rows of openings l lb may be provided, for example, two or three rows.
  • the above-mentioned opening l ib and recessed wall portion 23 can be formed by press forming.
  • the refrigerant conduit 10 is formed of a circular tube.
  • the refrigerant conduit 10 may also be formed of a tube having other cross-sectional shapes such as an elliptical shape or a rectangular shape, and the refrigerant conduit 10 may also be
  • the refrigerant conduit 10 can also be made of any suitable tube known in the art.
  • the refrigerant flows along the interior of the refrigerant conduit, and the recessed wall portion 23 mainly serves as a refrigerant.
  • the refrigerant is sprayed along the surface of the recessed wall portion 23 into the inner cavity of the collecting pipe, and 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 collecting pipe 102-end and then reversed.
  • the flow causes the refrigerant to be hooked into the remaining flat tubes 103.
  • the refrigerant is mixed in the header 102 so that the gas-liquid mixture is uniformly hooked, and no delamination occurs.
  • FIGS. 4 and 5 show schematic views of 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 middle portion 23a of the recessed wall portion 23 in the direction perpendicular to the axial direction of the refrigerant conduit 10 is composed of a plurality of substantially linear portions or a plurality of substantially straight portions, or a section of the recessed wall portion 23 along the axial direction of the refrigerant conduit 10 is a plurality of substantially straight lines. A portion or a plurality of substantially straight portions.
  • the middle portion 23a extends from the first end portion 231 to the second end portion 232 in the axial direction of the refrigerant conduit 10.
  • At least the cross section of the recessed wall portion 23 in the axial direction perpendicular to the axial direction of the refrigerant conduit 10 in the axial direction of the refrigerant conduit 10 is constituted by an arc-like portion, or A section of the recessed wall portion 23 along the axial direction of the refrigerant conduit 10 is constituted by an arc-like portion.
  • At least the middle portion 23a of the recessed wall portion 23 in the axial direction perpendicular to the refrigerant conduit 10 is substantially curved, curved or curved in cross section along the axial direction of the refrigerant conduit 10.
  • a section of the recessed wall portion 23 along the axial direction of the refrigerant conduit 10 is substantially curved, curved or curved.
  • the central portion 23a extends from the first end portion 231 to the second end portion 232 in the axial direction of the refrigerant conduit 10.
  • the arcuate or arc-like shape is provided by the recessed wall portion 23, which is advantageous in reducing the resistance of the refrigerant flowing through the opening.
  • FIGS. 6a and 6b show a refrigerant conduit 10 in accordance with a third embodiment of the present invention.
  • the structure of the refrigerant conduit 10 of this embodiment may be substantially the same as that of any one of the refrigerant conduits 10 of the first embodiment to the second embodiment, except for the portions described below.
  • the recessed wall portion 23 has a substantially triangular shape, and the bottom edge of the triangular recessed wall portion 23 is connected to the tube wall 17, and the remaining edges are separated from the tube wall 17.
  • the entire recessed wall portion 23 may be in a substantially flat plane, i.e., the entire recessed wall portion 23 may be substantially flat.
  • Figures 7a and 7b show a refrigerant conduit 10 in accordance with a fourth embodiment of the present invention.
  • the structure of the refrigerant conduit 10 of this embodiment may be substantially the same as that of any of the refrigerant conduits 10 of the first to third embodiments except for the portions described below.
  • the recessed wall portion 23 is generally arcuate, and the straight sides of the arcuate recessed wall portion 23 are connected to the tube wall 17, and the remaining edges are separated from the tube wall 17.
  • the entire recessed wall portion 23 may be substantially flat, that is, the entire recessed wall portion 23 may be substantially flat.
  • Example 5
  • FIGS. 8a and 8b show a refrigerant conduit 10 in accordance with a fifth embodiment of the present invention.
  • the structure of the refrigerant conduit 10 of this embodiment may be substantially the same as that of any of the refrigerant conduits 10 of the first to third embodiments except for the portions described below.
  • the recessed wall portion 23 is substantially arched, and the remaining edges of the recessed wall portion 23 are connected to the tube wall 17, except that the first end portion 231 is separated from the tube wall 17. It can be seen from the embodiment of the above recessed wall portion 23:
  • At least a portion of the central portion 23a of the refrigerant guiding wall portion such as the recessed wall portion 23 in the direction perpendicular to the axial direction of the refrigerant conduit 10 is substantially linear or straight in the axial direction of the refrigerant conduit, and the middle portion
  • the inclination angle of 23a with respect to the axial direction of the refrigerant conduit 10 is ⁇ .
  • a cross section of the refrigerant guiding wall portion such as the recessed wall portion 23 in the axial direction of the refrigerant conduit is substantially linear or straight, and a refrigerant guiding wall portion such as the recessed wall portion 23 is opposed to the cooling
  • the axial inclination angle of the agent catheter 10 is ⁇ .
  • the included angle ⁇ ranges from about greater than 0 degrees and less than 90 degrees, preferably from about 5 degrees to 75 degrees.
  • At least the middle portion 23a of the refrigerant guiding wall portion in the direction perpendicular to the axial direction of the refrigerant conduit 10 in the axial direction of the refrigerant conduit 10 is substantially straight or a plurality of straight portions a portion of the composition, or substantially curved, curved or curved; or a section of the refrigerant guiding wall portion along the axial direction of the refrigerant conduit 10 is composed of a plurality of substantially straight portions or a plurality of substantially straight portions Composed, or substantially curved, curved or curved.
  • the middle portion 23a extends from the first end portion 231 to the second end portion 232 in the axial direction of the refrigerant conduit 10.
  • At least a section of the middle portion 23a of the refrigerant guiding wall portion in a direction perpendicular to the axial direction of the refrigerant conduit 10 along the axial direction of the refrigerant conduit 10 includes at least one substantially straight line At least one of the at least one portion and the at least one substantially curved portion, or the cross section of the refrigerant guiding wall portion in the axial direction of the refrigerant conduit, includes at least one substantially straight portion and at least one portion of a substantially curved shape At least one of the parts.
  • FIG. 9a and 9b and Figure 10 are partial enlarged schematic views of a heat exchanger 100 in accordance with the present invention.
  • the refrigerant pipe 10 may be provided with an opening l lb.
  • the refrigerant conduit 10 when used as a distributor in the inlet header 102, from the end portion 31 of the refrigerant conduit 10 to the other end portion 33 In the non-opening range from the end portion 31 to the position at a distance from the end portion 31, the refrigerant conduit 10 is not provided with the opening 10b, and the number N of the heat exchange tubes 103 such as the flat tubes in the range of no opening is corresponding to The ratio of the number T of heat exchange tubes 103 in the entire heat exchange tube 103 is more than 20% and less than 99%, so that a good distribution effect can be obtained.
  • the refrigerant conduit 10 thus designed can also be used as a collector in the outlet header 101 to achieve uniform distribution of the refrigerant.
  • the refrigerant conduit 10 acts as a distributor in the inlet header 102 or as a collector in the outlet header 101, the end 31 of the refrigerant conduit 10 will be connected to the refrigerant line, and the other end 33 Will not be connected to the refrigerant line.
  • the refrigerant conduit 10 can be designed to: heat exchange such as a flat tube having no opening range from the end portion 31 of the refrigerant conduit 10 to be connected to the refrigerant line to a position at a predetermined distance from the end portion 31
  • the ratio of the number N of tubes 103 to the number T of heat exchange tubes 103 over the entire heat exchange tubes 103 corresponding to the refrigerant conduit 10 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 element 35 may not be provided, and the other end portion 33 of the refrigerant conduit 10 is open.
  • the refrigerant conduit 10 thus designed can also be used as a collector in the outlet header 101, thereby achieving the effect of uniformly distributing the refrigerant.
  • the two-phase refrigerant in the refrigerant conduit 10 is ejected from the opening l ib, and a part of the two-phase refrigerant directly enters the inner cavity of the heat exchange tube 103 such as a flat tube, thereby preventing excessive liquid-phase refrigerant from entering such as a flat tube.
  • Heat exchange tube 103 The remaining refrigerant is flushed to the header 102 and then 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 13 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 ⁇ of the center line 14 of the opening l ib substantially perpendicular to the axial direction of the refrigerant conduit 10 (for example, the axis 13 of the passage) and the longitudinal direction of the heat exchange tube 103 (or the axis 105 of the heat exchange tube 103) is 0. Within a range of 90 degrees, a good distribution effect can be obtained.
  • the centerline 14 can pass through the axis of the refrigerant conduit 10 (i.e., the axial centerline) 15 and perpendicular to the axis 15 of the refrigerant conduit 10, while passing through the midpoint of the transverse direction of the opening lib, the transverse direction and refrigeration
  • the axis 15 of the agent catheter 10 is perpendicular and perpendicular to the centerline 14 of the opening.
  • the lateral direction is the direction in which the axis 105 extends.
  • the refrigerant flows along the inner cavity of the refrigerant conduit, and the refrigerant guiding wall portion mainly serves to guide the refrigerant, and the refrigerant is sprayed to the collecting portion along the refrigerant guiding wall portion.
  • 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 collecting pipe 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 opening in the above embodiment, and the refrigerant guiding wall portion have a symmetrical structure
  • the opening, and the refrigerant guiding wall portion may have an asymmetrical structure
  • the opening, and the refrigerant guiding wall portion may be symmetrical or asymmetrical with respect to a plane passing through the central axis of the refrigerant pipe.
  • the embodiment of the refrigerant guiding wall portion is the recessed wall portion, however, the refrigerant guiding wall portion is not limited thereto, and the refrigerant passing through the opening may be guided by other suitable means.
  • a refrigerant guide wall portion such as a separately formed guide pipe or guide may be welded near the opening of the refrigerant pipe or welded inside or outside the refrigerant pipe to guide the refrigerant passing through the opening.
  • the opening may take various suitable shapes, and the refrigerant guiding wall portion may also adopt any suitable shape and structure.
  • the present invention is not limited to this. Alternatively, it may be separated from the tube wall only on both sides or one side of the circumferential direction of the refrigerant guiding wall portion, thereby forming the opening; or any suitable one in the refrigerant guiding wall portion. The other edges are separated from the tube wall, thereby forming the opening.
  • the refrigerant guiding wall portion may be a flat plate shape, a curved surface, or a flat portion and a curved portion.
  • a cross section of the refrigerant guiding wall portion along the axial direction of the refrigerant conduit is substantially linear or straight, and is formed by a plurality of substantially straight lines, or is substantially curved.
  • the refrigerant guiding wall portion is along the Refrigerants
  • the axial section of the conduit may comprise at least one substantially linear portion or at least a substantially curved portion, or at least a substantially straight portion and at least a substantially curved portion.

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Description

制冷剂导管和具有该制冷剂导管的换热器
技术领域
本发明涉及一种制冷剂导管， 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设有制冷剂 导管， 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， 制冷剂导管包括沿其长度布置的多个大体圆形的开口， 该开口中的每一个的中心线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垂直， 因此制冷剂在开口中喷出的阻力大， 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 导向壁部分，该制冷剂导向壁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。所述制冷剂导向壁部分是凹 陷壁部分， 所述凹陷壁部分朝向内腔凹陷。
根据本发明的一个方面，所述制冷剂导向壁部分的至少一部分边缘与 管壁相互分离开， 由此形成所述开口。
根据本发明的一个方面，至少所述制冷剂导向壁部分的在与所述制冷 剂导管轴向垂直的方向上的中部与所述制冷剂导管轴向的夹角范围是大 于 0度并且小于 90度， 优选为大约 5度至大约 75度， 或至少所述制冷剂 导向壁部分的一部分与所述制冷剂导管轴向的夹角范围是大于 0度并且 小于 90度， 优选为大约 5度至大约 75度， 或所述制冷剂导向壁部分与所 述制冷剂导管轴向的夹角范围是大于 0度并且小于 90度， 优选为大约 5 度至大约 75度。
根据本发明的一个方面，至少所述制冷剂导向壁部分的在与所述制冷 剂导管轴向垂直的方向上的中部沿所述制冷剂导管轴向的截面由多段大 致直线状的部分构成或大致是曲线状的，或所述制冷剂导向壁部分的沿所 述制冷剂导管轴向的截面由多段大致直线状的部分构成或大致是曲线状 的。
优选方式是，至少所述凹陷壁部分的制冷剂导管轴向上的第一端部与 管壁相互分离开， 由此形成所述开口。
根据本发明的另一方面，至少所述凹陷壁部分的在与所述制冷剂导管 轴向垂直的方向上的中部相对于所述制冷剂导管轴向倾斜，或至少所述制 冷剂导向壁部分的一部分相对于所述制冷剂导管轴向倾斜，或所述凹陷壁 部分相对于所述制冷剂导管轴向倾斜，并且所述凹陷壁部分的第一端部比 与所述第一端部相对的第二端部更靠近制冷剂导管轴线。
根据本发明的另一方面，至少所述凹陷壁部分的在与所述制冷剂导管 轴向垂直的方向上的中部沿所述制冷剂导管轴向的截面大致是直线状的 或直的，或所述凹陷壁部分的沿所述制冷剂导管轴向的截面大致是直线状 的或直的。
根据本发明的另一方面，至少所述凹陷壁部分的在与所述制冷剂导管 轴向垂直的方向上的中部与所述制冷剂导管轴向的夹角的范围为大于 0 度并且小于 90度， 或所述凹陷壁部分与所述制冷剂导管轴向的夹角的范 围为大于 0度并且小于 90度。
根据本发明的另一方面，至少所述凹陷壁部分的在与所述制冷剂导管 轴向垂直的方向上的中部沿所述制冷剂导管轴向的截面由多段大致直线 状的部分构成或大致是曲线状的，或所述凹陷壁部分的沿所述制冷剂导管 轴向的截面由多段大致直线状的部分构成或大致是曲线状的。
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为根据本发明的第一实施例的制冷剂导管的示意剖视图； 图 4为根据本发明的第二实施例的制冷剂导管的示意剖视图； 图 5为根据本发明的第二实施例的制冷剂导管的放大示意剖视图； 图 6a为根据本发明的第三实施例的制冷剂导管的示意剖视图； 图 6b为根据本发明的第三实施例的制冷剂导管的示意图； 图 7a为根据本发明的第四实施例的制冷剂导管的示意剖视图； 图 7b为根据本发明的第四实施例的制冷剂导管的示意图； 图 8a为根据本发明的第五实施例的制冷剂导管的示意剖视图； 图 8b为根据本发明的第五实施例的制冷剂导管的示意图； 图 9a和 9b为根据本发明的换热器的局部示意放大图； 以及 图 10为根据本发明的换热器的局部示意放大图。 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采 用此制冷剂导管对两相制冷剂进行导向和分配。 实施例 1
图 2和 3示出了根据本发明的第一实施例的制冷剂导管 10。 如图 2 和 3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 17内形^ t内腔 19， 形成在管壁中的开口 l lb， 以及制冷剂导向壁部 分， 该制冷剂导向壁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 l ib的制冷剂。制冷剂导向壁部分的至少一部 分边缘与管壁 17相互分离开， 由此形成所述开口。 该制冷剂导向壁部分 设置为使得通过开口 l ib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， 制冷剂导向壁部分的至少一部分与导管的轴向的夹 角大于 0度并且小于 90度， 优选为大约 5度至大约 75度。例如， 该制冷 剂导向壁部分设置为使得通过开口 l ib流动的制冷剂流与导管的轴向所 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。参照 图 9a和％， 制冷剂导管 10的一端开口， 另一端可封闭也可开口。
制冷剂导管 10还包括凹陷壁部分 23， 所述凹陷壁部分 23朝向内腔 19凹陷， 优选方式是， 至少所述凹陷壁部分 23的制冷剂导管轴向上的第 一端部 231与管壁 17相互分离开， 由此形成所述开口 l lb。 该凹陷壁部 分 23构成制冷剂导向壁部分的一个示例。
至少所述凹陷壁部分 23在与所述制冷剂导管轴向垂直的方向上的中 部 23a或所述凹陷壁部分 23相对于所述制冷剂导管 10的轴向倾斜，或至 少所述凹陷壁部分 23的一部分相对于所述制冷剂导管 10的轴向倾斜，并 且所述凹陷壁部分 23的第一端部 231比与所述第一端部 231相对的第二 端部 232更靠近制冷剂导管 10的轴线 15。 所述中部 23a在所述制冷剂导 管 10轴向上从第一端部 231延伸到第二端部 232。
如图 2和 3所示，作为形成开口 l ib的一种方法， 在形成制冷剂导管 的圆管的管壁中， 在垂直于圆管轴向的切割方向切一定深度的切口， 并将 切口轴向方向的一侧的圆管管壁冲压使之凹陷。由此形成开口 l ib和凹陷 壁部分 23。 切口的方位由两个方向确定： 一个是切口深度方向 （即切口
4 在深度上的方向）， 切口深度方向在圆管的径向上 （图 3中的上下方向）， 另一个是切割方向， 切割方向与切口深度方向垂直并且与圆管轴向垂直。 作为选择， 切口深度方向可以与圆管的径向成小于 90度的角度， 并且切 割方向可以与圆管轴向成小于 90度的角度。 切口可以是任何合适方位的 切口。
如图 2和 3所示，切口在圆周方向上的长度， 即第一端部 231与管壁 相互分离开的分离部分 12的圆弧长度为 L， 并且相邻开口间距为 dl。
作为一种实施方式， 至少所述凹陷壁部分 23在与所述制冷剂导管 10 的轴向垂直的方向上的中部 23a沿所述制冷剂导管轴向的截面大致是直 线状的或直的， 至少所述凹陷壁部分 23在与所述制冷剂导管轴向垂直的 方向上的中部 23a相对于所述制冷剂导管 10的轴向的倾斜角度为 γ。作为 选择， 所述凹陷壁部分 23的沿所述制冷剂导管轴向的截面大致是直线状 的或直的，所述凹陷壁部分 23相对于所述制冷剂导管 10的轴向的倾斜角 度为 γ。至少所述凹陷壁部分 23在与所述制冷剂导管轴向垂直的方向上的 中部 23a与所述制冷剂导管 10的轴向的夹角 γ的范围为大于 0度并且小于 90度， 优选为大约 5度至 75度， 或所述凹陷壁部分 23与所述制冷剂导 管 10的轴向的夹角 γ的范围为大于 0度并且小于 90度， 优选为大约 5度 至 75度。
如此设计的制冷剂导管 10同样可以在出口集流管 101中用作收集器。 参照图 9a和 9b， 无论制冷剂导管 10在入口集流管 102中用作分配 器还是在出口集流管 101中用作收集器，制冷剂导管 10的端部 31可以与 制冷剂管路连接， 另一端部 33可以不与制冷剂管路连接， 或者制冷剂导 管 10的端部 33可以与制冷剂管路连接， 端部 31可以不与制冷剂管路连 接。
可以沿制冷剂导管 10的轴向方向， 设置一排开口 l ib, 或设置多排 开口 l lb， 例如两排或三排。
作为另一种形成开口 l ib的方法， 上述开口 l ib和凹陷壁部分 23可 以通过冲压成型。
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
5 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。
参见图 1、 9a和 ， 当把上述制冷剂导管 10用于换热器 100的集流 管 102中时， 制冷剂沿着制冷剂导管内腔流动， 凹陷壁部分 23主要起导 向制冷剂的作用， 制冷剂沿着凹陷壁部分 23的表面喷射到集流管内腔， 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 102—端再反向流动， 使制冷剂均勾分配到余下的扁管 103中。制 冷剂在集流管 102中混合， 使得气液混合均勾， 不产生分层现象。 实施例 2
图 4和 5示出了根据本发明的第二实施例的制冷剂导管 10的示意图。 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 4和 5所示并参照图 2 , 在第三实施例的制冷剂导管 10中， 至 少所述凹陷壁部分 23的在与所述制冷剂导管 10轴向垂直的方向上的中部 23a沿所述制冷剂导管 10的轴向的截面由多段大致直线状的部分或多段 大致直的部分构成，或所述凹陷壁部分 23的沿所述制冷剂导管 10的轴向 的截面由多段大致直线状的部分或多段大致直的部分构成。 所述中部 23a 在所述制冷剂导管 10的轴向上从第一端部 231延伸到第二端部 232。 作 为选择，至少所述凹陷壁部分 23的在与所述制冷剂导管 10的轴向垂直的 方向上的中部 23a沿所述制冷剂导管 10的轴向的截面由类弧形的部分构 成，或所述凹陷壁部分 23的沿所述制冷剂导管 10的轴向的截面由类弧形 的部分构成。
作为选择，至少所述凹陷壁部分 23在与所述制冷剂导管 10轴向垂直 的方向上的中部 23a沿所述制冷剂导管 10轴向的截面大致是曲线状的、 弯曲的或弧形的；或者所述凹陷壁部分 23的沿所述制冷剂导管 10轴向的 截面大致是曲线状的、弯曲的或弧形的。所述中部 23a在所述制冷剂导管 10轴向上从第一端部 231延伸到第二端部 232。
通过凹陷壁部分 23设置成弧形或类弧形的， 有利于减少制冷剂流经 开口处的阻力。
6 实施例 3
图 6a和 6b示出了根据本发明的第三实施例的制冷剂导管 10。 除了 下面描述的部分之外， 该实施例的制冷剂导管 10的结构可以与第一实施 例至第二实施例中的制冷剂导管 10中的任意一个的结构大致相同。 如图 6a和 6b所示， 凹陷壁部分 23大致为三角形的形状， 并且三角形的凹陷 壁部分 23的底边与管壁 17相连， 且其余边缘与管壁 17分开。 该实施例 中， 整个凹陷壁部分 23可以在大致一个平面上， 即整个凹陷壁部分 23可 以是大致平板状。 实施例 4
图 7a和 7b示出了根据本发明的第四实施例的制冷剂导管 10。 除了 下面描述的部分之外， 该实施例的制冷剂导管 10的结构可以与第一实施 例至第三实施例中的制冷剂导管 10中的任意一个的结构大致相同。 如图 7a和 7b所示， 凹陷壁部分 23大致为弓形， 并且弓形的凹陷壁部分 23的 直边与管壁 17相连， 且其余边缘与管壁 17分开。 该实施例中， 整个凹陷 壁部分 23可以在大致一个平面上，即整个凹陷壁部分 23可以是大致平板 状。 实施例 5
图 8a和 8b示出了根据本发明的第五实施例的制冷剂导管 10。 除了 下面描述的部分之外， 该实施例的制冷剂导管 10的结构可以与第一实施 例至第三实施例中的制冷剂导管 10中的任意一个的结构大致相同。 如图 8a和 8b所示， 凹陷壁部分 23大致为拱形， 并且出了第一端部 231与管 壁 17相互分离开之外， 凹陷壁部分 23的其余的边与管壁 17相连。 从上述凹陷壁部分 23的实施例可以看出：
至少诸如凹陷壁部分 23的制冷剂导向壁部分在与所述制冷剂导管 10 的轴向垂直的方向上的中部 23a沿所述制冷剂导管轴向的截面大致是直 线状的或直的，中部 23a相对于所述制冷剂导管 10的轴向的倾斜角度为 γ。 作为选择， 诸如凹陷壁部分 23的制冷剂导向壁部分的沿所述制冷剂导管 轴向的截面大致是直线状的或直的， 诸如凹陷壁部分 23的制冷剂导向壁 部分相对于所述制冷剂导管 10的轴向的倾斜角度为 γ。 夹角 γ的范围为大 约大于 0度并且小于 90度， 优选为大约 5度至 75度。
作为选择， 至少制冷剂导向壁部分的在与所述制冷剂导管 10轴向垂 直的方向上的中部 23a沿所述制冷剂导管 10的轴向的截面由多段大致直 线状的部分或多段大致直的部分构成， 或者大致是曲线状的、弯曲的或弧 形的； 或者制冷剂导向壁部分的沿所述制冷剂导管 10的轴向的截面由多 段大致直线状的部分或多段大致直的部分构成， 或者大致是曲线状的、弯 曲的或弧形的。 所述中部 23a在所述制冷剂导管 10的轴向上从第一端部 231延伸到第二端部 232。
作为一种实施方式，至少所述制冷剂导向壁部分的在与所述制冷剂导 管 10的轴向垂直的方向上的中部 23a沿所述制冷剂导管 10的轴向的截面 包括至少一段大致直线状的部分和至少一段大致曲线状的部分中的至少 一种，或所述制冷剂导向壁部分的沿所述制冷剂导管轴向的截面包括至少 一段大致直线状的部分和至少一段大致曲线状的部分中的至少一种。
在上述实施例中， 至少第一端部 231与管壁 17分离开， 作为选择， 也可以是凹陷壁部分 23的至少一部分边缘与管壁 11分离开。 下面更具体地描述根据本发明的实施例的换热器 100。 图 9a和 9b和 图 10为根据本发明的换热器 100的局部放大示意图。
参照图 9a和 9b， 在沿集流管 102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 l lb。
如图 9a和 9b所示， 作为选择， 例如， 制冷剂导管 10在入口集流管 102中用作分配器时，从制冷剂导管 10的入口侧的端部 31到另一端部 33 的方向上， 在从端部 31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 10b， 在无开口范围内的诸如扁管的换热管 103 的数量 N与对应于整个换热管 103范围的换热管 103的数量 T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 101中用作收集器， 实现均匀分配制冷剂的效果。
无论制冷剂导管 10在入口集流管 102中用作分配器还是在出口集流 管 101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 31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 N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 9a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 9b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 101中用作收集器， 由此实现均匀分 配制冷剂的效果。
制冷剂导管 10中的两相制冷剂从开口 l ib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，从而避免过多的液相制冷剂进 入这些诸如扁管的换热管 103。 剩余制冷剂冲到集流管 102—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 10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 13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。 开口 l ib的与制冷剂导管 10的轴向大致垂直的中心线 14 (例如， 通道的轴线 13 ) 与换热管 103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。该中心线 14可以通 过制冷剂导管 10的轴线（即轴向中心线） 15， 并垂直于制冷剂导管 10的 轴线 15， 同时通过所述开口 l ib的横向方向的中点， 横向方向与制冷剂 导管 10的轴线 15垂直，并垂直于所述开口的中心线 14。如图 10中所示， 横向方向为轴线 105延伸的方向。
在上述实施例中，制冷剂沿着制冷剂导管内腔流动， 制冷剂导向壁部 分主要起对制冷剂导向的作用，制冷剂沿着制冷剂导向壁部分喷射到集流 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。
虽然结合附图对本发明进行了说明，但是附图中公开的实施例旨在对 本发明优选实施方式进行示例性说明， 而不能理解为对本发明的一种限 制。
例如， 上述实施例中的开口， 以及制冷剂导向壁部分（例如， 凹陷壁 部分） 具有对称结构， 作为选择， 开口， 以及制冷剂导向壁部分 （例如， 凹陷壁部分）可以具有不对称的结构，例如，釆用圆管加工制冷剂导管时， 相对于通过制冷剂导管中心轴线的平面，开口，以及制冷剂导向壁部分（例 如， 凹陷壁部分） 可以对称， 也可以不对称。
此外， 上述实施例中， 制冷剂导向壁部分的实施例为凹陷壁部分， 然 而， 制冷剂导向壁部分并不限于此， 而可以釆用其它合适的方式对通过开 口的制冷剂进行导向。例如， 可以将单独制作的导向管、 导向件等制冷剂 导向壁部分焊接在制冷剂导管的开口附近，或焊接在制冷剂导管内部或外 部，对通过开口的制冷剂进行导向。此外，开口可以采用各种合适的形状， 并且制冷剂导向壁部分也可以采用任何合适的形状和结构。
此外， 上述实施例中， 至少所述制冷剂导向壁部分的制冷剂导管轴向 上的一侧的第一端部与管壁相互分离开， 由此形成所述开口。 然而， 本发 明不限于此。作为选择， 也可以仅仅在所述制冷剂导向壁部分的圆周方向 的两侧或一侧与管壁相互分离开， 由此形成所述开口； 或者在所述制冷剂 导向壁部分的任何合适的其它边缘与管壁相互分离开， 由此形成所述开 □。
此外， 在上述实施例中， 所述制冷剂导向壁部分也可以是平板状的， 曲面状的， 或同时包括平板状的部分和曲面状的部分。制冷剂导向壁部分 的沿所述制冷剂导管轴向的截面大致是直线状的或直的，由多段大致直线 构成， 或是大致曲线状的， 作为选择， 制冷剂导向壁部分的沿所述制冷剂 导管轴向的截面可以包括至少一段大致直线状的部分或至少一段大致曲 线状的部分， 或至少一段大致直线状的部分和至少一段大致曲线状的部 分。

Claims

权 利 要 求
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
制冷剂导向壁部分，该制冷剂导向壁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，
其中所述制冷剂导向壁部分是凹陷壁部分，所述凹陷壁部分朝向内腔 凹陷。
2、 根据权利要求 1所述的制冷剂导管， 其中：
所述制冷剂导向壁部分的至少一部分边缘与管壁相互分离开，由此形 成所述开口。
3、 根据权利要求 1或 2所述的制冷剂导管， 其中：
至少所述制冷剂导向壁部分的在与所述制冷剂导管轴向垂直的方向 上的中部相对于所述制冷剂导管轴向倾斜，或至少所述制冷剂导向壁部分 的一部分相对于所述制冷剂导管轴向倾斜，或所述制冷剂导向壁部分相对 于所述制冷剂导管轴向倾斜。
4、 根据权利要求 1至 3中的任意一项所述的制冷剂导管， 其中， 至 少所述制冷剂导向壁部分的在与所述制冷剂导管轴向垂直的方向上的中 部沿所述制冷剂导管轴向的截面大致是直线状的或直的，或所述制冷剂导 向壁部分的沿所述制冷剂导管轴向的截面大致是直线状的或直的。
5、 根据权利要求 1至 4中的任意一项所述的制冷剂导管， 其中， 至 少制冷剂导向壁部分的在与所述制冷剂导管轴向垂直的方向上的中部与 所述制冷剂导管轴向的夹角的范围为大于 0度并且小于 90度， 或
所述制冷剂导向壁部分与所述制冷剂导管轴向的夹角的范围为大于 0 度并且小于 90度。
6、 根据权利要求 1至 3中的任意一项所述的制冷剂导管， 其中， 至 少所述制冷剂导向壁部分的在与所述制冷剂导管轴向垂直的方向上的中 部沿所述制冷剂导管轴向的截面包括至少一段大致直线状的部分和至少 一段大致曲线状的部分中的至少一种， 或
所述制冷剂导向壁部分的沿所述制冷剂导管轴向的截面包括至少一 段大致直线状的部分和至少一段大致曲线状的部分中的至少一种。
7、 根据权利要求 1至 6中的任意一项所述的制冷剂导管， 其中至少 所述制冷剂导向壁部分的制冷剂导管轴向上的端部与管壁相互分离开，由 此形成所述开口。
8、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。
9、 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 8中的任意一项所述的制冷剂 导管。
10、 根据权利要求 9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 在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%。
14
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Publication number Priority date Publication date Assignee Title
US9417014B2 (en) 2010-09-13 2016-08-16 Danfoss A/S Refrigerant guiding pipe and heat exchanger having refrigerant guiding pipe
US9528778B2 (en) 2010-09-13 2016-12-27 Sanhua (Hangzhou) Micro Channel Heat Exchanger Co., Ltd. Refrigerant guiding pipe and heat exchanger having refrigerant guiding pipe
DE102014011150A1 (de) * 2014-07-25 2016-01-28 Mtu Friedrichshafen Gmbh Wärmetauscher mit mindestens einem Sammeltank
DE102014011150B4 (de) 2014-07-25 2022-12-29 Rolls-Royce Solutions GmbH Wärmetauscher mit mindestens einem Sammeltank

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CN101922882A (zh) 2010-12-22
US20130213627A1 (en) 2013-08-22
CN101922882B (zh) 2011-12-28
JP2013537298A (ja) 2013-09-30
EP2618091A1 (en) 2013-07-24

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