EP2392886B1 - Orientation insensitive refrigerant distributor tube - Google Patents

Orientation insensitive refrigerant distributor tube Download PDF

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Publication number
EP2392886B1
EP2392886B1 EP11167680.5A EP11167680A EP2392886B1 EP 2392886 B1 EP2392886 B1 EP 2392886B1 EP 11167680 A EP11167680 A EP 11167680A EP 2392886 B1 EP2392886 B1 EP 2392886B1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
orifices
distributor tube
tube
evaporator
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.)
Not-in-force
Application number
EP11167680.5A
Other languages
German (de)
French (fr)
Other versions
EP2392886A3 (en
EP2392886A2 (en
Inventor
Shrikant Mukund Joshi
Douglas Charles Wintersteen
Russel Scott Johnson
Yanping Xia
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.)
Mahle International GmbH
Original Assignee
Mahle International GmbH
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 Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP2392886A2 publication Critical patent/EP2392886A2/en
Publication of EP2392886A3 publication Critical patent/EP2392886A3/en
Application granted granted Critical
Publication of EP2392886B1 publication Critical patent/EP2392886B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • 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
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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
    • F28D2001/0253—Particular components
    • F28D2001/026—Cores
    • F28D2001/0273—Cores having special shape, e.g. curved, annular
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators

Definitions

  • the present disclosure relates to an inlet distributor for an evaporator; more particularly to an inlet distributor having a plurality of orifices arranged along the length of the distributor tube.
  • Automotive heat exchangers typically include an inlet header, an outlet header, and a plurality of refrigerant tubes hydraulically connecting the headers for refrigerant flow therebetween. Corrugated fins interconnect adjacent refrigerant tubes to increase the available heat transfer area, as well as to increase the structural integrity of the heat exchanger.
  • the coil of the heat exchanger is defined by the refrigerant tubes and interconnecting corrugated fins. To meet the demands of residential and commercial applications, the size of the coil of the heat exchanger has to be increased accordingly, which in turn dramatically increased the lengths of the inlet and outlet headers.
  • a typical distributor tube extends the length of the inlet header and includes a plurality of uniformly spaced orifices for distributing the two-phase refrigerant throughout the length of the header.
  • the orifices are oriented at a designed angle relative to the center of the cross-section of the refrigerant tube to provide the maximum performance for the coil in a specific application.
  • the angle of the orifices is selected based on testing a vertical slab coil design with the refrigerant tube aligned in the opposite direction of gravity.
  • Indoor evaporators also have the additional challenge of packaging constraints; the evaporators have to fit within the limited volume offered by the plenums of residential HVAC systems.
  • the refrigerant tubes lie in a plane much like that of an automotive heat exchanger, and for maximum efficiency it is preferable that the refrigerant tubes are aligned in the direction of gravity with the inlet header lower than the outlet header.
  • two smaller slab coils are assembled into an A-Frame design or a single larger slab coil is bent into an ARC design.
  • the A-Frame design or ARC design may need to be installed in various orientations with respect to gravity, in which the refrigerant tubes may not be aligned in the direction of gravity and the inlet header may not be lower than the outlet header.
  • the desired distribution of refrigerant flowing through the coil may be adversely affected due to the orientation of the evaporator. There is a long felt need for an evaporator that provides good refrigerant distribution regardless of its orientation.
  • the invention relates to a heat exchanger assembly according to claim 1.
  • a residential indoor evaporator may be constructed by using two slab coils in an A-Frame design or a single slab coil bent into an ARC design. Shown in Figs.
  • FIGS. 1A-1C are representations of an end view of an A-Frame design or ARC design residential indoor evaporator 10 having an inlet header 12a, an outlet header 12b spaced apart from the inlet header 12a, and a plurality of refrigerant tubes 14 hydraulically connecting the headers 12a, 12b for refrigerant flow.
  • An evaporator coil 16, partially shown in Figs. 2 and 3 is defined by the plurality of refrigerant tubes 14 together with external fins 15 interconnecting the adjacent refrigerant tubes 14.
  • the evaporator 10 includes a distributor tube 20 in the inlet header 12a, shown in Figs. 2-7 , for improved refrigerant distribution.
  • the above mentioned components of the evaporator 10 are typically constructed of a heat conductive material such as aluminum.
  • Each of the A-Frame design and ARC design provides an evaporator 10 having at least one apex 18.
  • the A-Frame or ARC design can be installed within a HVAC plenum in various orientations with respect to the direction of gravity, in which the apex 18 may be up, down, horizontal, and any other orientation therebetween.
  • the inlet header 12a may be located above the outlet header 12b, below the outlet header 12b, or horizontal with the outlet header12b.
  • the headers 12a, 12b are typically perpendicular to that of the direction of gravity, but the bottom header may be slightly angled toward the direction of gravity to facilitate condensate drainage.
  • a standard angle designed for the orifices 22 of the distribution tube 20 relative to the refrigerant tube 14 may not necessarily work efficiently when used in all the various potential orientations of the evaporator 10. It was found that only certain range of angles of the orifices 22 of the distribution tube 20 relative to the refrigerant tube 14 are acceptable for each of the various evaporator coil 16 orientations. In other words, orifice angles are application specific; therefore, the desired orifice range of angles has to be calculated for each specific orientation of the evaporator 10.
  • the liquid phase 24 of a two-phase refrigerant flowing through the distributor tube 20 tends to migrate to the bottom of the interior surface 28 of the distributor tube 20 due to gravity. It is suspected that the liquid phase 24 does not necessary puddle on the bottom or low spot of the distribution tube 20, but instead it is pressed against and rides up a portion of the interior surface 28 of the distributor tube 20 by the flow of refrigerant through the distributor tube 20, thereby forming a liquid refrigerant cross-sectional profile 30 much like a crescent moon with its apex on the bottom.
  • the limit would be annular flow where the liquid distributes around the entire peripheral internal surface 28 of the distribution tube 20, but more typically a thicker layer would exist on the bottom.
  • the liquid refrigerant cross-sectional profile 30 occupies the interior surface 28 of the distributor tube 20 from 45 to 315 degrees with respect to the opposite direction of gravity being 0 degree. During normal operating conditions, the liquid refrigerant cross-sectional profile 30 occupies the interior surface 28 of the distributor tube 20 from 90 to 270 degrees.
  • An aspect of the invention provides a means to transport the liquid phase refrigerant from the distributor tube 20 to the refrigerant tubes 14 for efficient boiling and thus improved heat transfer performance regardless of the orientation of the A-Frame or ARC evaporator coil evaporator.
  • Fig. 5 shows a cylindrical refrigerant distributor tube 20 extending along a substantially central axis (A-axis).
  • Pairs of orifices 22 are substantially uniformly spaced along the length of the distributor tube 20, in which each pair of orifices 22 is located about its respective point on the A-axis.
  • one of the orifices 22 may be oriented 90 to 180 degrees apart from the other with respect to the pair's respective point on the A-axis.
  • each pair of orifices 22 may be rotated 90 to 180 degrees from the adjacent pair of orifices 22.
  • Fig. 6 shows a cylindrical refrigerant distributor tube 20 extending along the A-axis.
  • Groups of four (4) orifices 22 are substantially uniformly spaced along the length of the distributor tube 20, in which each group of orifices 22 is located about its respective point on the A-axis.
  • each of the orifices 22 may be oriented 90 degrees apart from the adjacent orifice 22 with respect to the group's respective point on the A-axis.
  • each group of (4) orifices 22 may be rotated 45 degrees from the adjacent group of (4) orifices 22.
  • Fig. 7 shows a cylindrical refrigerant distributor tube 20 according to the invention and having a plurality of orifices 22 spiraled along the tube. With respect to an end view of the A-axis, each succeeding orifice 22 may be offset 45 to 180 degrees from the preceding orifice 22.

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

Description

    TECHNICAL FIELD OF INVENTION
  • The present disclosure relates to an inlet distributor for an evaporator; more particularly to an inlet distributor having a plurality of orifices arranged along the length of the distributor tube.
    • BACKGROUND OF INVENTION
  • Residential and commercial air conditioning and heat pump systems are known to employ modified automotive heat exchangers, which are desirable for its proven high heat transfer efficiency, durability, and relatively ease of manufacturability. Automotive heat exchangers typically include an inlet header, an outlet header, and a plurality of refrigerant tubes hydraulically connecting the headers for refrigerant flow therebetween. Corrugated fins interconnect adjacent refrigerant tubes to increase the available heat transfer area, as well as to increase the structural integrity of the heat exchanger. The coil of the heat exchanger is defined by the refrigerant tubes and interconnecting corrugated fins. To meet the demands of residential and commercial applications, the size of the coil of the heat exchanger has to be increased accordingly, which in turn dramatically increased the lengths of the inlet and outlet headers. For a heat exchanger operating in evaporator mode, the increased length of the headers tends to result in refrigerant mal-distribution through the refrigerant tubes. Momentum and gravity effects, due to the large mass differences between the liquid and gas phases, can result in separation of the phases in the inlet header and cause poor refrigerant distribution through the refrigerant tubes. Poor refrigerant distribution degrades evaporator performance and can result in uneven temperature distribution over the coil. To assist in providing uniform refrigerant distribution though the refrigerant tubes, it is known to provide a distributor tube in the inlet header. JP2004278935 , US2006102331 , WO2008060270 and WO2010005676 disclose heat exchangers provided with distributor tubes. US-A-2006102331 discloses a heat exchanger assembly according to the preamble of claim 1.
  • A typical distributor tube extends the length of the inlet header and includes a plurality of uniformly spaced orifices for distributing the two-phase refrigerant throughout the length of the header. The orifices are oriented at a designed angle relative to the center of the cross-section of the refrigerant tube to provide the maximum performance for the coil in a specific application. Typically, the angle of the orifices is selected based on testing a vertical slab coil design with the refrigerant tube aligned in the opposite direction of gravity. Indoor evaporators also have the additional challenge of packaging constraints; the evaporators have to fit within the limited volume offered by the plenums of residential HVAC systems. In a slab coil design, the refrigerant tubes lie in a plane much like that of an automotive heat exchanger, and for maximum efficiency it is preferable that the refrigerant tubes are aligned in the direction of gravity with the inlet header lower than the outlet header. To provide the cooling capacity required within a limited space, two smaller slab coils are assembled into an A-Frame design or a single larger slab coil is bent into an ARC design. The A-Frame design or ARC design may need to be installed in various orientations with respect to gravity, in which the refrigerant tubes may not be aligned in the direction of gravity and the inlet header may not be lower than the outlet header. The desired distribution of refrigerant flowing through the coil may be adversely affected due to the orientation of the evaporator. There is a long felt need for an evaporator that provides good refrigerant distribution regardless of its orientation.
    • SUMMARY OF THE INVENTION
  • The invention relates to a heat exchanger assembly according to claim 1.
    • BRIEF DESCRIPTION OF DRAWINGS
  • This invention will be further described with reference to the accompanying drawings in which:
    • Figs. 1A-C show representative end views of an A-type coil or bent coil design evaporator.
    • Fig. 2 shows a distributor tube in an inlet header of an evaporator, in which the orifices of the distributor tube are oriented in a direction opposite that of the direction of gravity.
    • Fig. 3 shows a distributor tube in an inlet header of an evaporator, in which the orifices of the distributor tube are oriented in the direction of gravity.
    • Fig. 4 shows a cross-section of the inlet header having a distributor tube with the liquid phase of refrigerant pressed-up against the interior surface of the distributor tube.
    • Fig. 5 shows a refrigerant distributor tube having groups of two (2) orifices along the length of the distributor tube, wherein the orifices in each group are oriented 180 degrees apart from each other and the groups of two (2) orifices are rotated 90 degrees apart from each other.
    • Fig. 6 shows a refrigerant distributor tube having groups of four (4) orifices along the length of the distributor tube, wherein the orifices in each group are oriented 90 degrees apart from each other.
    • Fig. 7 shows a refrigerant distributor tube according to the invention and having a plurality of orifices spiraled along the tube at an exemplary 90 degrees between adjacent orifices.
  • Only the distributor tube disclosed and described with respect to Fig. 7 is in accordance with the invention. The distributor tubes disclosed in Figs. 5 and 6 do not form part of the invention and only present examples which are useful for understanding the invention.
    • DETAILED DESCRIPTION OF INVENTION
  • For a typical slab coil design evaporator, the desired angle of the orifices of a distributor tube is selected based on testing of a vertical slab coil in which the refrigerant tubes are aligned in the direction of gravity with the inlet header lower than the outlet header. To accommodate the packaging constraints required for residential applications, a residential indoor evaporator may be constructed by using two slab coils in an A-Frame design or a single slab coil bent into an ARC design. Shown in Figs. 1A-1C are representations of an end view of an A-Frame design or ARC design residential indoor evaporator 10 having an inlet header 12a, an outlet header 12b spaced apart from the inlet header 12a, and a plurality of refrigerant tubes 14 hydraulically connecting the headers 12a, 12b for refrigerant flow. An evaporator coil 16, partially shown in Figs. 2 and 3, is defined by the plurality of refrigerant tubes 14 together with external fins 15 interconnecting the adjacent refrigerant tubes 14. The evaporator 10 includes a distributor tube 20 in the inlet header 12a, shown in Figs. 2-7, for improved refrigerant distribution. The above mentioned components of the evaporator 10 are typically constructed of a heat conductive material such as aluminum.
  • Each of the A-Frame design and ARC design provides an evaporator 10 having at least one apex 18. The A-Frame or ARC design can be installed within a HVAC plenum in various orientations with respect to the direction of gravity, in which the apex 18 may be up, down, horizontal, and any other orientation therebetween. With these varieties of possible orientations, the inlet header 12a may be located above the outlet header 12b, below the outlet header 12b, or horizontal with the outlet header12b. The headers 12a, 12b are typically perpendicular to that of the direction of gravity, but the bottom header may be slightly angled toward the direction of gravity to facilitate condensate drainage.
  • A standard angle designed for the orifices 22 of the distribution tube 20 relative to the refrigerant tube 14 may not necessarily work efficiently when used in all the various potential orientations of the evaporator 10. It was found that only certain range of angles of the orifices 22 of the distribution tube 20 relative to the refrigerant tube 14 are acceptable for each of the various evaporator coil 16 orientations. In other words, orifice angles are application specific; therefore, the desired orifice range of angles has to be calculated for each specific orientation of the evaporator 10.
  • With reference to Figs. 2-4, it is believed that the liquid phase 24 of a two-phase refrigerant flowing through the distributor tube 20 tends to migrate to the bottom of the interior surface 28 of the distributor tube 20 due to gravity. It is suspected that the liquid phase 24 does not necessary puddle on the bottom or low spot of the distribution tube 20, but instead it is pressed against and rides up a portion of the interior surface 28 of the distributor tube 20 by the flow of refrigerant through the distributor tube 20, thereby forming a liquid refrigerant cross-sectional profile 30 much like a crescent moon with its apex on the bottom. The limit would be annular flow where the liquid distributes around the entire peripheral internal surface 28 of the distribution tube 20, but more typically a thicker layer would exist on the bottom.
  • It was found that if the orifices 22 were facing in a direction other than between 45 to 315 degrees with respect to the opposite direction of gravity being 0 degree, mostly vapor phase refrigerant tend to exits the orifices 22 migrating toward the refrigerant tubes 14. This is undesirable because optimal heat transfer efficiency is obtained when the refrigerant entering the refrigerant tubes is in a substantially liquid phase.
  • With reference to Fig. 3, it was surprisingly found that when the orifices 22 are oriented substantially in the direction of gravity, the pressure and momentum of the refrigerant flowing through the distributor tube 20 pushes the liquid phase refrigerant out of the distributor tube 20 through the orifices 22 toward the refrigerant tubes. The refrigerant remains substantially in liquid phase until it reaches the refrigerant tubes 14, at which point the liquid phase refrigerant starts to absorb heat and vaporizes, thereby providing optimum heat transfer and even temperature distribution across the evaporator coil 16. With reference to Fig. 4, during periods of high refrigerant flow, the liquid refrigerant cross-sectional profile 30 occupies the interior surface 28 of the distributor tube 20 from 45 to 315 degrees with respect to the opposite direction of gravity being 0 degree. During normal operating conditions, the liquid refrigerant cross-sectional profile 30 occupies the interior surface 28 of the distributor tube 20 from 90 to 270 degrees.
  • An aspect of the invention provides a means to transport the liquid phase refrigerant from the distributor tube 20 to the refrigerant tubes 14 for efficient boiling and thus improved heat transfer performance regardless of the orientation of the A-Frame or ARC evaporator coil evaporator.
  • Fig. 5 shows a cylindrical refrigerant distributor tube 20 extending along a substantially central axis (A-axis). This embodiment is not part of the invention Pairs of orifices 22 are substantially uniformly spaced along the length of the distributor tube 20, in which each pair of orifices 22 is located about its respective point on the A-axis. Within each pair of orifices 22, one of the orifices 22 may be oriented 90 to 180 degrees apart from the other with respect to the pair's respective point on the A-axis. Furthermore, each pair of orifices 22 may be rotated 90 to 180 degrees from the adjacent pair of orifices 22.
  • Fig. 6 shows a cylindrical refrigerant distributor tube 20 extending along the A-axis. This embodiment is not part of the invention Groups of four (4) orifices 22 are substantially uniformly spaced along the length of the distributor tube 20, in which each group of orifices 22 is located about its respective point on the A-axis. Within each group of four (4) orifices 22, each of the orifices 22 may be oriented 90 degrees apart from the adjacent orifice 22 with respect to the group's respective point on the A-axis. Furthermore, each group of (4) orifices 22 may be rotated 45 degrees from the adjacent group of (4) orifices 22.
  • Fig. 7 shows a cylindrical refrigerant distributor tube 20 according to the invention and having a plurality of orifices 22 spiraled along the tube. With respect to an end view of the A-axis, each succeeding orifice 22 may be offset 45 to 180 degrees from the preceding orifice 22.
  • With the above configurations of orifices 22 on the distributor tube 20 or any configuration that provides at least one orifice 22 in the desired direction regardless of the orientation of the evaporator 10 would improve the distribution of refrigerant though the refrigerant tubes 14. Therefore, if the evaporator coil 16 is positioned in any one of the various possible orientations, at least one of the orifices 22 would be located within the liquid refrigerant cross-sectional profile 30.
  • While this invention has been described in terms of the preferred embodiments thereof, it is not intended to be so limited, but rather only to the extent set forth in the claims that follow.

Claims (1)

  1. A heat exchanger assembly (10) for use with a two-phase refrigerant, comprising;
    an inlet header (12a);
    an outlet header (12b) spaced from said inlet header (12a);
    a plurality of refrigerant tubes (14) hydraulically connecting said inlet header (12a) to said outlet header (12b);
    a distributor tube (20) having a plurality of orifices (22) disposed in said inlet header (12a), wherein said orifices (22) are arranged along said distributor tube (20) such that at least one orifice (22) is oriented in the liquid phase (24) of the refrigerant pressed against said internal surface of said distributor tube (20) regardless of orientation of said heat exchanger assembly (10), characterized in that
    said plurality of orifices (22) is spirally positioned along said distributor tube (20) about a substantially center axis and wherein,
    each of said plurality of orifices (22) is off-set 90 degrees or 180 degrees from adjacent orifices (22).
EP11167680.5A 2010-06-01 2011-05-26 Orientation insensitive refrigerant distributor tube Not-in-force EP2392886B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US35012310P 2010-06-01 2010-06-01
US13/114,405 US20110290465A1 (en) 2010-06-01 2011-05-24 Orientation insensitive refrigerant distributor tube

Publications (3)

Publication Number Publication Date
EP2392886A2 EP2392886A2 (en) 2011-12-07
EP2392886A3 EP2392886A3 (en) 2014-07-02
EP2392886B1 true EP2392886B1 (en) 2016-08-24

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP11167680.5A Not-in-force EP2392886B1 (en) 2010-06-01 2011-05-26 Orientation insensitive refrigerant distributor tube

Country Status (5)

Country Link
US (1) US20110290465A1 (en)
EP (1) EP2392886B1 (en)
KR (1) KR20110132273A (en)
CN (1) CN202216453U (en)
BR (1) BRPI1102318A8 (en)

Families Citing this family (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011126488A2 (en) * 2010-04-09 2011-10-13 Ingersoll-Rand Company Formed microchannel heat exchanger
KR101217454B1 (en) * 2012-05-29 2013-01-02 안정국 Refrigerant distributor of the thermal storage system
WO2013184522A1 (en) * 2012-06-08 2013-12-12 Modine Manufacturing Company Heat exchanger, and method of distributing refrigerant therein
WO2014100651A1 (en) * 2012-12-21 2014-06-26 Trane International Inc. Refrigerant distributor of micro-channel heat exchanger
US9459057B2 (en) 2013-01-24 2016-10-04 Alcoll USA LLC Heat exchanger
US20140224460A1 (en) * 2013-02-08 2014-08-14 Trane International Inc. Microchannel Heat Exchanger
KR20140116626A (en) 2013-03-25 2014-10-06 엘지전자 주식회사 A heat exchanger
JP2016527081A (en) * 2013-08-08 2016-09-08 ロッテ ケミカル コーポレーション Air diffuser and separation membrane bioreactor
US9568225B2 (en) * 2013-11-01 2017-02-14 Mahle International Gmbh Evaporator having a hybrid expansion device for improved aliquoting of refrigerant
US20160061497A1 (en) * 2013-11-01 2016-03-03 Delphi Technologies, Inc. Two-pass evaporator
CN103604254B (en) * 2013-11-12 2016-07-06 清华大学 A kind of built-in biphase gas and liquid flow flow dividing structure
US10072900B2 (en) * 2014-09-16 2018-09-11 Mahle International Gmbh Heat exchanger distributor with intersecting streams
US10551099B2 (en) * 2016-02-04 2020-02-04 Mahle International Gmbh Micro-channel evaporator having compartmentalized distribution
FR3059396B1 (en) 2016-11-30 2020-12-04 Valeo Systemes Thermiques REFRIGERANT FLUID DISTRIBUTION DEVICE INSIDE A COLLECTOR BOX OF A HEAT EXCHANGER
FR3061951B1 (en) 2016-11-30 2019-06-21 Valeo Systemes Thermiques DEVICE FOR DISPENSING A REFRIGERANT FLUID INSIDE A COLLECTOR BOX OF A HEAT EXCHANGER.
FR3059407B1 (en) 2016-11-30 2019-10-18 Valeo Systemes Thermiques DEVICE FOR MIXING A REFRIGERANT FLUID INSIDE A COLLECTOR BOX OF A HEAT EXCHANGER
FR3061281B1 (en) 2016-11-30 2019-07-12 Valeo Systemes Thermiques COLLECTOR BOX OF A REFRIGERANT FLUID COMPRISING AT LEAST ONE DEVICE FOR ANGULAR POSITIONING OF A CONDUIT
FR3059405B1 (en) 2016-11-30 2019-07-12 Valeo Systemes Thermiques DEVICE FOR DISPENSING A REFRIGERANT FLUID INSIDE A COLLECTOR BOX OF A HEAT EXCHANGER
US10563895B2 (en) * 2016-12-07 2020-02-18 Johnson Controls Technology Company Adjustable inlet header for heat exchanger of an HVAC system
EP3619492B1 (en) * 2017-05-05 2023-07-26 Carrier Corporation Heat exchanger for heat pump applications
FR3075347B1 (en) 2017-12-19 2020-05-15 Valeo Systemes Thermiques DEVICE FOR DISTRIBUTING A REFRIGERANT FLUID TO BE HOUSED IN A COLLECTOR BOX OF A HEAT EXCHANGER
FR3075346B1 (en) 2017-12-19 2020-05-22 Valeo Systemes Thermiques COLLECTOR BOX OF A HEAT EXCHANGER PROVIDED WITH A MEMBER FOR HOLDING AND / OR ANGULAR POSITIONING OF A DEVICE FOR DISPENSING A REFRIGERANT FLUID
FR3075345B1 (en) 2017-12-19 2020-12-04 Valeo Systemes Thermiques COLLECTOR BOX OF A HEAT EXCHANGER HOSTING A REFRIGERANT FLUID DISTRIBUTION DEVICE MAINTAINED VIA A CENTERING DEVICE.
CN110966803A (en) * 2018-09-30 2020-04-07 浙江三花智能控制股份有限公司 Heat exchanger
CN110966804B (en) * 2018-09-30 2021-09-24 浙江三花智能控制股份有限公司 Heat exchanger
WO2020063966A1 (en) * 2018-09-30 2020-04-02 浙江三花智能控制股份有限公司 Heat exchanger
DE102018222815A1 (en) * 2018-12-21 2020-06-25 Mahle International Gmbh Receiving box for a heat exchanger
US10890386B2 (en) * 2019-02-01 2021-01-12 Mahle International Gmbh Evaporator unit including distributor tube and method thereof
US11713931B2 (en) * 2019-05-02 2023-08-01 Carrier Corporation Multichannel evaporator distributor
US11493277B2 (en) * 2019-11-06 2022-11-08 Carrier Corporation Microchannel heat exchanger
US11656010B2 (en) 2020-06-02 2023-05-23 Hamilton Sundstrand Corporation Evaporator with feed tube flow distributors for random gravitation and acceleration fields
WO2023058179A1 (en) * 2021-10-07 2023-04-13 三菱電機株式会社 Refrigerant distributor, heat exchanger, and air conditioner
GB2625961A (en) * 2021-10-15 2024-07-03 Mitsubishi Electric Corp Distributor, heat exchanger, and heat pump device

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2770896B1 (en) * 1997-11-10 2000-01-28 Valeo Thermique Moteur Sa AIR CONDITIONING CONDENSER PROVIDED WITH A FLUID TANK WITH INTERCHANGEABLE CARTRIDGE
US7017656B2 (en) * 2001-05-24 2006-03-28 Honeywell International, Inc. Heat exchanger with manifold tubes for stiffening and load bearing
US20030010483A1 (en) * 2001-07-13 2003-01-16 Yasuo Ikezaki Plate type heat exchanger
JP2004278935A (en) * 2003-03-17 2004-10-07 Calsonic Kansei Corp Evaporator
US7806171B2 (en) * 2004-11-12 2010-10-05 Carrier Corporation Parallel flow evaporator with spiral inlet manifold
US7967060B2 (en) * 2005-08-18 2011-06-28 Parker-Hannifin Corporation Evaporating heat exchanger
ES2480015T3 (en) * 2006-11-13 2014-07-25 Carrier Corporation Parallel flow heat exchanger
US20110127023A1 (en) * 2008-07-10 2011-06-02 Taras Michael F Design characteristics for heat exchangers distribution insert

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CN202216453U (en) 2012-05-09
BRPI1102318A8 (en) 2017-10-24
US20110290465A1 (en) 2011-12-01
KR20110132273A (en) 2011-12-07
EP2392886A3 (en) 2014-07-02
EP2392886A2 (en) 2011-12-07

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