US20130312944A1 - Refrigerant distributing device and heat exchanger - Google Patents

Refrigerant distributing device and heat exchanger Download PDF

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Publication number
US20130312944A1
US20130312944A1 US13/992,002 US201113992002A US2013312944A1 US 20130312944 A1 US20130312944 A1 US 20130312944A1 US 201113992002 A US201113992002 A US 201113992002A US 2013312944 A1 US2013312944 A1 US 2013312944A1
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US
United States
Prior art keywords
hole
refrigerant
distributing
nozzle
distributing tube
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.)
Abandoned
Application number
US13/992,002
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English (en)
Inventor
Qiang Gao
Yanxing Li
Ningjie Huang
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.)
Sanhua Hangzhou Micro Channel Heat Exchanger Co Ltd
Danfoss AS
Original Assignee
Sanhua Holding Group Co Ltd
Danfoss AS
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 Sanhua Holding Group Co Ltd, Danfoss AS filed Critical Sanhua Holding Group Co Ltd
Assigned to SANHUA HOLDING GROUP CO., LTD., DANFOSS A/S reassignment SANHUA HOLDING GROUP CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LI, YANXING, HUANG, NINGJIE, GAO, QIANG
Publication of US20130312944A1 publication Critical patent/US20130312944A1/en
Assigned to DANFOSS A/S, SANHUA (HANGZHOU) MICRO CHANNEL HEAT EXCHANGE CO., LTD. reassignment DANFOSS A/S ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DANFOSS A/S, SANHUA HOLDING GROUP CO., LTD.
Abandoned 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
    • F28F9/027—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
    • 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
    • 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
    • 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
    • F28F9/0282—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry of conduit ends, e.g. by using inserts or attachments for modifying the pattern of flow at the conduit inlet or outlet
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/14—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means with multiple outlet openings; with strainers in or outside the outlet opening
    • B05B1/20—Arrangements of several outlets along elongated bodies, e.g. perforated pipes or troughs, e.g. spray booms; Outlet elements therefor
    • B05B1/202—Arrangements of several outlets along elongated bodies, e.g. perforated pipes or troughs, e.g. spray booms; Outlet elements therefor comprising inserted outlet elements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/34—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl
    • B05B1/3405—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl

Definitions

  • the invention relates to a refrigerant-distributing, device of a heat exchanger and a heat exchanger comprising the refrigerant-distributing device.
  • an object of a first aspect of the invention is to provide a refrigerant-distributing device capable of improving the refrigerant-distribution uniformity.
  • Embodiments of the first aspect of the invention provide a refrigerant-distributing device comprising: a distributing tube defining a first end and a second end in a length direction thereof and a plurality of nozzles disposed on the distributing tube along the length direction of the distributing tube, each nozzle having a predetermined length and being formed with as through-hole communicating an interior of the distributing tube and an exterior of the distributing tube.
  • the refrigerant-distributing device is capable of improving the flow-rate balance.
  • the flow resistance is increased because of the nozzles, the pressures at individual nozzles may be balanced, and the pressure imbalance between individual nozzles may be reduced greatly so that the refrigerant-flow rate along the length direction of the distributing tube is more balanced.
  • the refrigerant-distributing device can control and adjust the flow direction of the refrigerant.
  • the gaseous-liquid refrigerant may be ejected out of the nozzles along the radial direction, the axial direction, the circumferential direction, and other directions of the distributing tube so that the refrigerant-distribution uniformity in the exterior of the distributing tube is improved greatly.
  • the plurality of nozzles are arranged in a plurality of rows in a circumferential direction of the distributing tube, and the nozzles in each row are arranged spirally.
  • the through-hole is a circular hole and passes through inner and outer end surfaces of the nozzle, and a length of the through-hole is 0.125-250 times as large as a hydraulic diameter of the through-hole.
  • the through-hole passes through inner and outer end surfaces of the nozzle, and an axial direction of the through-hole is inclined relative to an axial direction of the nozzle.
  • the through-hole defines a first through-hole segment extending in a radial direction of the nozzle and a second through-hole segment extending in an axial direction of the nozzle, an inner end of the second through-hole segment is communicated with the interior of the distributing tube, an outer end of the second through-hole segment is closed, and the first through-hole segment communicates the second through-hole segment with the exterior of the distributing tube.
  • a plurality of the first through-hole segments are formed and arranged in a circumferential direction of the second through-hole segment.
  • the through-hole defines a first through-hole segment and a second through-hole segment extending in an axial direction of the nozzle, an inner end of the second through-hole segment is communicated with the interior of the distributing tube, an outer end of the second through-hole segment is closed, the first through-hole segment communicates the second through-hole segment with the exterior of the distributing tube, and an axial direction of the first through-hole segment is deviated from a radial direction of the nozzle.
  • an inner end of each nozzle is extended into the interior of the distributing tube by a predetermined length.
  • an inner end of each nozzle is flush with an inner wall surface or an outer wall surface of the distributing tube.
  • the through-hole passes through inner and outer end surfaces of the nozzle, an axial direction of the through-hole is parallel with an axial direction of the nozzle, the distributing tube has a circular cross-section, a ratio H/D of a length H of the through-hole to a hydraulic diameter D of the distributing tube is in a range of 0.027-25, and a ratio H/L of the length H of the through-hole to a length L of the distributing tube is in a range of 3.3 ⁇ 10 ⁇ 4 ⁇ 0.125.
  • a sum of cross-sectional areas of the through-holes of the nozzles is 0.01%-40% of a circumferential surface area of the distributing tube.
  • Embodiments according to the second aspect of the invention provide a heat exchanger comprising: an inlet header; an outlet header; a plurality of heat-exchange tubes each having two ends connected with the inlet header and the outlet header, respectively, to communicate the inlet header and the outlet header; a plurality of fins disposed between adjacent heat-exchange tubes, respectively; and a refrigerant-distributing device according to embodiments of the first aspect of the invention disposed in the inlet header.
  • FIG. 1 is a schematic view of a refrigerant-distributing device according to a first embodiment of the invention
  • FIG. 2 is a top view of the refrigerant-distributing device shown in FIG. 1 ;
  • FIG. 3 is a schematic cross-sectional view of the refrigerant-distributing device shown in FIG. 1 ;
  • FIG. 4 is a partial sectional view of a refrigerant-distributing device according to a second embodiment of the invention.
  • FIG. 5 is a top view of the refrigerant-distributing device shown in FIG. 4 ;
  • FIG. 6 is a partial sectional view of a refrigerant-distributing device according to a third embodiment of the invention.
  • FIG. 7 is a top view of the refrigerant-distributing device shown in FIG. 6 ;
  • FIG. 8 is a schematic cross-sectional view of the refrigerant-distributing device shown in FIG. 6 ;
  • FIG. 9 is a partial sectional view of a refrigerant-distributing device according to a fourth embodiment of the invention.
  • FIG. 10 is a top view of the refrigerant-distributing device shown in FIG. 9 ;
  • FIG. 11 is a schematic cross-sectional view of the refrigerant-distributing device shown in FIG. 9 ;
  • FIG. 12 is a partial sectional view of a refrigerant-distributing device according to a fifth embodiment of the invention.
  • FIG. 13 is a top view of the refrigerant-distributing device shown in FIG. 12 ;
  • FIG. 14 is a schematic cross-sectional view of the refrigerant-distributing device shown in FIG. 12 ;
  • FIG. 15 is a schematic view of a refrigerant-distributing device according to a sixth embodiment of the invention.
  • FIG. 16 is a top view of the refrigerant-distributing device shown in FIG. 15 ;
  • FIG. 17 is a schematic cross-sectional view of the refrigerant-distributing device shown in FIG. 15 ;
  • FIG. 18 is a schematic view of a refrigerant-distributing device according to a seventh embodiment of the invention.
  • FIG. 19 is a top view of the refrigerant-distributing device shown in FIG. 18 ;
  • FIG. 20 is a schematic cross-sectional view of the refrigerant-distributing device shown in FIG. 18 ;
  • FIG. 21 is a schematic view of a refrigerant-distributing device according to an eighth embodiment of the invention.
  • FIG. 22 is a top view of the refrigerant-distributing device shown in FIG. 21 ;
  • FIG. 23 is a schematic cross-sectional view of the refrigerant-distributing device shown in FIG. 21 ;
  • FIG. 24 is a schematic view of a heat exchanger according to an embodiment of the invention.
  • FIG. 25 is a schematic partial cross-sectional view of an inlet header of the heat exchanger shown in FIG. 24 ;
  • FIG. 26 is a graph illustrating a comparison between a “refrigerant distribution” effect of a refrigerant-distributing device according to an embodiment of the-invention and a “refrigerant distribution” effect of a conventional distributing tube.
  • relative terms such as “length direction,” “lateral,” “axial direction,” “upper,” “lower,” “front,” “rear,” “left,” “right,” “vertical,” “horizontal” “top,” “bottom,” “inner,” and “outer” as well as derivatives thereof (e.g., “horizontally,” “downwardly,” “upwardly,” etc.) should be construed to refer to the orientation as then described or as shown in the figure(s) under discussion. These relative terms are for convenience of description and do not require that the invention be constructed or operated in a particular orientation.
  • the refrigerant-distributing device comprises a distributing tube 1 having a first end (i.e., the left end in FIG. 1 ) and a second end (i.e., the right end in FIG. 1 ) in a length direction (i.e., the left and right direction in FIG. 1 ) thereof.
  • a plurality of nozzles 2 are disposed on the distributing tube 1 along the length direction of the distributing tube 1 , and each nozzle 2 has a predetermined length and is formed with a through-hole 21 communicating an interior of the distributing tube 1 and an exterior of the distributing tube 1 .
  • the exterior of the distributing tube 1 means an interior of a header when the refrigerant-distributing device is mounted into the header of a heat exchanger.
  • the first end of the distributing tube 1 is open, and the second end of the distributing tube 1 is closed.
  • the second end of the distributing tube 1 may be open and then closed by an end wall of the header when the refrigerant-distributing device is mounted into the header of the heat exchanger.
  • the left end of the distributing tube 1 is referred as an “inlet end” of the distributing tube 1 (that is, the left-end opening of the distributing tube 1 is used as the refrigerant inlet of the distributing tube 1 ).
  • the plurality of nozzles 2 are mounted on the distributing tube 1 along the length direction of the distributing tube 1 , and the “pumping” effect may be generated in the nozzles 2 under the same pressure as that in the related art such that the flow rate in the nozzles 2 is larger than that in openings of a conventional distributing tube when the hydraulic diameter of the nozzle 2 is identical with that of the opening of the conventional distributing tube.
  • the gaseous refrigerant and the liquid refrigerant may be mixed again when flowing in the through-holes 21 of the nozzles 2 , thus further reducing the gas-liquid separation.
  • the through-holes 21 of the nozzles 2 may increase the length of the refrigerant-ejection passage-so-as to increase the refrigerant-distribution-pressure difference such that the refrigerant flow-rate distribution is more uniform along the entire length direction of the distributing tube 1 , thus improving the heat-exchange performance of the heat exchanger.
  • the nozzles 2 each having a predetermined length are disposed on the distributing tube 1 .
  • the refrigerant-flow rate Q follows a formula:
  • A is a cross-sectional area of the through-hole 21 of the nozzle 2
  • H is a pressure head
  • g is the gravity acceleration
  • ⁇ 0 is a flow-rate coefficient. Because the flow-rate coefficient ⁇ 0 of the nozzle 2 is 0.82 and the flow-rate coefficient ⁇ 0 of the opening in the conventional distributing tube is 0.62, the flow rate in the nozzle 2 is larger than that in the opening in the conventional distributing tube when the hydraulic diameter of the nozzle 2 is identical with that of the opening in the conventional distributing tube.
  • the refrigerant flows out of the distributing tube through individual openings formed in the wall of the distributing tube, the pressure drops in the individual openings are unequal, and a pressure difference between the refrigerant inlet and the opening farthest from the refrigerant inlet (i.e., the last opening) differs greatly from that between the refrigerant inlet and the opening nearest to the refrigerant inlet (i.e., the first opening) such that the refrigerant flow-rate distribution along a length direction of the distributing tube is non-uniform (that is, the flow rate in the first opening is much larger than that in the last opening).
  • the refrigerant-distributing device because the nozzles 2 each having a predetermined length are disposed on the distributing tube 1 , the refrigerant-flow passage in each nozzle 2 is lengthened, and the refrigerant-distribution-pressure drop in the nozzles 2 is larger than that in the openings in the conventional distributing tube such that a pressure difference between the refrigerant inlet and the first nozzle 2 (for example, the left-most nozzle in FIG. 1 ) is substantially identical with a pressure difference between the refrigerant inlet and the last nozzle 2 (for example, the right-most nozzle in FIG. 1 ).
  • the refrigerant distribution along the length direction of the distributing tube 1 is more uniform, as shown in FIG. 26 .
  • the abscissas s represent a distance from each opening in the conventional distributing tube to the refrigerant inlet and a distance from each nozzle 2 in the refrigerant-distributing device according to embodiments of the invention to the refrigerant inlet, and the ordinates in represent a refrigerant-flow rate in each opening and a refrigerant-flow rate in each nozzle 2 .
  • the refrigerant-distributing device will be described below with reference to FIGS. 1-3 .
  • the plurality of nozzles 2 are disposed on the distributing tube 1 along the length direction (i.e., the left and right direction in FIG. 1 ) of the distributing tube 1 and arranged on the distributing tube 1 in a straight line.
  • the distributing tube 1 is formed with a plurality of mounting holes 11 , and each nozzle 2 is fitted and mounted in one mounting hole 11 .
  • each nozzle 2 is cylindrical, and the through-hole 21 is a circular hole and passes through an inner end surface (e.g., the lower end surface in FIG. 1 ) and an outer end surface (e.g., the upper end surface in FIG. 1 ) of the nozzle 2 .
  • a length of the through-hole 21 is 0.125-250 times as large as a hydraulic diameter of the through-hole 21 . It should be noted that if the length of the through-hole 21 of the nozzle 2 is too large, the flow resistance of the refrigerant in the nozzle 2 will be increased; and, if the length of the through-hole 21 of the nozzle 2 is too small, the “pumping” effect will be weakened. Therefore, it has been found that the balance between reducing the resistance and maintaining the “pumping” effect may be achieved by controlling the length of the through-hole 21 to be 0.125-250 times as large as the hydraulic diameter of the through-hole 21 .
  • an outer end (i.e., the upper end in FIG. 1 ) of the through-hole 21 has an enlarged segment 22 , thus facilitating the machining of the through-hole 21 .
  • the plurality of nozzles 2 are spaced apart from each other at equal intervals in the length direction of the distributing tube 1 .
  • the invention is not limited to this.
  • the plurality of nozzles 2 may be spaced apart from each other at unequal intervals.
  • an axial direction of the through-hole 21 is consistent with an axial direction of the nozzle 2 .
  • an inner end (i.e., the end of each nozzle 2 close to the distributing tube 1 ) of each nozzle 2 is extended into the interior of the distributing tube 1 by a predetermined length. Because the nozzle 2 is inserted into the interior of the distributing tube 1 , the refrigerant is agitated when flowing in the distributing tube 1 along the axial direction of the distributing tube 1 , and the gaseous refrigerant and the liquid refrigerant are separated from and then remixed with each other continuously such that the gaseous refrigerant and the liquid refrigerant may be still mixed uniformly when flowing to a region in the distributing tube 1 away from the refrigerant inlet of the distributing tube 1 .
  • the inner end of each nozzle 2 is flush with the inner wall surface or the outer wall surface of the distributing tube 1 .
  • the through-hole 21 passes through the inner end surface and the outer end surface of the nozzle 2 , and the axial direction of the through-hole 21 is parallel with the axial direction of the nozzle 2 .
  • the distributing tube 1 is a circular tube, a ratio H/D of a length H of the through-hole 21 to a hydraulic diameter D of the distributing tube 1 is in a range of 0.027-25, and a ratio of the length of the through-hole 21 to a length L of the distributing tube 1 is in a range of 3.3 ⁇ 10 ⁇ 4 ⁇ 0.125.
  • ⁇ P ⁇ (1/ d ) ⁇ 2 /2
  • ⁇ P tube ⁇ 2 ( L/D ) ⁇ 2 /2
  • the flow-rate distribution between individual nozzles 2 of the distributing tube 1 may be optimized.
  • H 1-25 millimeters
  • d 0.1-8 millimeters
  • D 1-36 millimeters
  • L 0.2-3 meters.
  • the flow-rate distribution between individual nozzles 2 of the distributing tube 1 may be optimized.
  • the distributing tube 1 has a circular cross-section
  • the through-hole 21 in the nozzle 2 is a circular hole (i.e., the through-hole has a circular cross-section).
  • the invention is not limited to this.
  • the distributing tube 1 may have a rectangular cross-section, and the cross-section of the through-hole 21 may have a square shape or any other suitable shape.
  • the length of the through-hole 21 may be increased without changing the length of the nozzle 2 . Therefore, the length of the refrigerant-flow passage may be increased to enhance the “mixing” effect of the gaseous refrigerant and the liquid refrigerant, and the direction of the refrigerant-flow passage may be changed so that the refrigerant is ejected out of the distributing tube 1 at a particular angle to improve the “distribution” effect.
  • the nozzle 2 is cylindrical
  • the through-hole 21 passes through an inner end surface and an outer end surface of the nozzle 2
  • the through-hole 21 has a cross-shaped cross-section.
  • the invention is not limited to this.
  • the through-hole 21 may have a rectangular cross-section. Since the through-hole 21 has a non-circular cross-section, the “pumping” effect and the “ejection” effect may be further enhanced, and the gas-liquid separation may be eliminated.
  • each nozzle 2 is extended into the interior of the distributing tube 1 by a predetermined length, and the inner end of the each nozzle 2 is formed with a bent portion.
  • the nozzle 2 may be of a bent cylinder.
  • An angle ⁇ between the bent portion and the main body of the nozzle 2 may be in a range of about 45 degrees-180 degrees.
  • first through-hole segment 212 is communicated with the second through-hole segment 211
  • outer end of the first through-hole segment 212 is communicated with the exterior of the distributing tube 1 .
  • a plurality of the first through-bole segments 212 are formed and arranged in the circumferential direction of the second through-hole segment 211 .
  • the refrigerant Since the first through-hole segment 212 is extended in the radial direction of the nozzle 2 , the refrigerant is easy to control to be ejected out of the nozzle 2 along various radial directions of the nozzle 2 , but may not be ejected along the radial direction of the distributing tube 1 , thus improving the distribution uniformity of the refrigerant in the exterior of the distributing tube 1 . Therefore, the refrigerant may be distributed in the exterior of the distributing tube 1 more uniformly.
  • the through-hole 21 defines a plurality of first through-hole segments 212 and a second through-hole segment 211 extending in an axial direction of the nozzle 2 .
  • the inner end of the second through-hole segment 211 is communicated with the interior of the distributing tube 1 , and the outer end of the second through-hole segment 211 is closed.
  • the first through-hole segments 212 communicate the second through-hole segment 211 with the exterior of the distributing tube 1 .
  • the first through-hole segments 212 and the second through-hole segment 211 have circular cross-sections, and the axial direction of the first through-hole segment 212 is deviated from the radial direction of the nozzle 2 (for example, the axial direction of the first through-hole segment 212 is consistent with a tangential direction of the second through-hole segment 211 ). Therefore, the refrigerant passing through the first through-hole segment 212 is ejected along a direction deviated from the radial direction of the nozzle 2 , and, consequently, the rotation of the refrigerant after being ejected into the second through-hole segment 212 is enhanced, thus improving the distribution uniformity of the refrigerant in the exterior of the distributing tube 1 . Therefore, the gaseous refrigerant and the liquid refrigerant may be distributed in the exterior of the distributing tube 1 more uniformly.
  • the through-bole 21 defines a first through-hole segment 212 and a second through-hole segment 211 extending in an axial direction of the nozzle 2 .
  • the first through-hole segment 212 and the second through-hole segment 211 have rectangular cross-sections.
  • a plurality of first through-hole segments 212 may be formed and extended in the radial direction of the nozzle 2 or a direction deviated from the radial direction of the nozzle 2 .
  • the refrigerant-distributing device will be described below with reference to FIGS. 21-23 .
  • the plurality of nozzles 2 are spirally arranged in the length direction of the distributing tube 1 . Therefore, the gaseous refrigerant and the liquid refrigerant may be spirally ejected along the length direction of the distributing tube 1 so that the gaseous refrigerant and the liquid refrigerant may be uniformly distributed in the exterior of the distributing tube 1 .
  • the plurality of nozzles 2 are arranged in one row.
  • the plurality of nozzles 2 may be arranged in a plurality of rows in a circumferential direction of the distributing tube 1 and the nozzle 2 in each row may be arranged spirally or linearly.
  • the nozzles 2 are cylindrical.
  • the-invention is not limited to this.
  • the nozzles 2 may be of a prism having a rectangular cross-section or a cross-section of other shapes.
  • the nozzles 2 may be manufactured separately and mounted onto the distributing tube 1 .
  • the nozzles 2 and the distributing tube 1 may be integrally manufactured (for example, the nozzles 2 and the distributing tube 1 are integrally cast).
  • the “distribution” effect may be improved, and the separation of the gaseous refrigerant and the liquid refrigerant may be reduced, thus improving the “heat exchange” effect.
  • the heat exchanger according to an embodiment of the invention will be described below with reference to FIGS. 24-25 .
  • the heat exchanger according to an embodiment of the invention comprises an inlet header 100 , an outlet header 200 , a plurality of heat-exchange tubes 300 , a plurality of fins 400 , and a refrigerant-distributing device described with reference to embodiments of the invention.
  • each heat-exchange tube 300 Two ends of each heat-exchange tube 300 are connected with the inlet header 100 and the outlet header 200 , respectively, to communicate the inlet header 100 and the outlet header 200 .
  • the plurality of fins 400 are disposed between adjacent heat-exchange tubes 300 , respectively.
  • the refrigerant-distributing device is disposed in the inlet header 100 .
  • one end (i.e., a right end in FIG. 24 ) of the distributing tube 1 of the refrigerant-distributing device is inserted into the inlet header 100 along a length direction of the inlet header 100 .
  • the one end of the distributing tube 1 may be closed by a separate end cap or the right-end wall of the inlet header 100 .
  • the other end (i.e., a left end in FIG. 24 ) of the distributing tube 1 may be exposed out of the inlet header 100 and used as a refrigerant inlet of the heat exchanger.
  • the “refrigerant distribution” effect and the heat-exchange performance are good.
  • the refrigerant-distributing device may also be disposed in the outlet header 200 .
  • the refrigerant-distributing device is used as a refrigerant-collecting device.
  • the refrigerant-distributing device according to an embodiment of the invention may be disposed in the inlet header 100 and the outlet header 200 simultaneously.
  • the refrigerant-distributing device and the heat exchanger are capable of improving the flow-rate balance. Since the flow resistance is increased by the through-holes of the nozzles, the pressure difference between individual nozzles may be balanced, and the pressure imbalance between individual nozzles may be reduced largely so that the refrigerant-flow rate along the length direction of the distributing tube may be more balanced.
  • the refrigerant-distributing device and the heat exchanger are capable of controlling and adjusting the direction of the refrigerant.
  • the gaseous refrigerant and the liquid refrigerant may be ejected out of the nozzles not only along the radial direction of the distributing tube, but also along the axial direction, the circumferential direction, or other directions of the distributing tube so that the refrigerant-distribution uniformity in the exterior of the distributing tube may be improved largely.

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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)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
US13/992,002 2010-12-08 2011-05-09 Refrigerant distributing device and heat exchanger Abandoned US20130312944A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CN201010590176.9 2010-12-08
CN201010590176.9A CN102564204B (zh) 2010-12-08 2010-12-08 制冷剂分配装置和具有它的换热器
PCT/CN2011/073846 WO2012075772A1 (zh) 2010-12-08 2011-05-09 制冷剂分配装置和具有它的换热器

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US (1) US20130312944A1 (ja)
EP (1) EP2650635B1 (ja)
JP (1) JP6114995B2 (ja)
CN (1) CN102564204B (ja)
WO (1) WO2012075772A1 (ja)

Cited By (5)

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