US20110290465A1 - Orientation insensitive refrigerant distributor tube - Google Patents

Orientation insensitive refrigerant distributor tube Download PDF

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Publication number
US20110290465A1
US20110290465A1 US13/114,405 US201113114405A US2011290465A1 US 20110290465 A1 US20110290465 A1 US 20110290465A1 US 201113114405 A US201113114405 A US 201113114405A US 2011290465 A1 US2011290465 A1 US 2011290465A1
Authority
US
United States
Prior art keywords
orifices
heat exchanger
distributor tube
exchanger assembly
refrigerant
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
US13/114,405
Other languages
English (en)
Inventor
Shrikant Mukund Joshi
Douglas Wintersteen
Russell 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.)
Delphi Technologies Inc
Original Assignee
Delphi Technologies Inc
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 Delphi Technologies Inc filed Critical Delphi Technologies Inc
Priority to US13/114,405 priority Critical patent/US20110290465A1/en
Priority to EP11167680.5A priority patent/EP2392886B1/fr
Priority to CN2011202584714U priority patent/CN202216453U/zh
Priority to BRPI1102318A priority patent/BRPI1102318A8/pt
Priority to KR1020110051898A priority patent/KR20110132273A/ko
Assigned to DELPHI TECHNOLOGIES, INC. reassignment DELPHI TECHNOLOGIES, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: JOHNSON, RUSSELL S., JOSHI, SHRIKANT M., WINTERSTEEN, DOUGLAS C., XIA, YANPING
Publication of US20110290465A1 publication Critical patent/US20110290465A1/en
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
    • 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.
  • 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.
  • 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.
  • a distributor tube in the inlet header To assist in providing uniform refrigerant distribution though the refrigerant tubes.
  • 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.
  • 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.
  • the invention relates to a heat exchanger assembly having an inlet header, an outlet header spaced from the inlet header, a plurality of refrigerant tubes hydraulically connecting the inlet header with the outlet header.
  • a distributor tube having a plurality of orifices disposed in the inlet header, wherein the orifices are arranged along the distributor tube such that at least one orifice is oriented in the liquid phase of a two-phased refrigerant pressed against the internal surface of the distributor tube regardless of the orientation of the evaporator.
  • the orifices may be substantially uniformly spaced along the length of the distributor tube in pairs or groups of four (4).
  • one of the orifices may be oriented 90 to 180 degrees apart from the other with respect to the pair's respective point on a central axis.
  • Each pair of orifices may be rotated 90 to 180 degrees from the adjacent pair of orifices.
  • each of the orifices may be oriented 90 degrees apart from the adjacent orifice with respect to the group's respective point on a central axis.
  • Each group of four (4) orifices may be rotated 45 degrees from the adjacent group of four (4) orifices.
  • the cylindrical refrigerant distributor tube may have a plurality of orifices spiraled along the tube. With respect to an end view of the central axis, each succeeding orifice may be offset 45 to 180 degrees from the preceding orifice.
  • 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 having a plurality of orifices spiraled along the tube at an exemplary 90 degrees between adjacent orifices.
  • 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. 2 and 3 are representations of an end view of an A-Frame design or ARC design residential indoor evaporator 10 having an inlet header 12 a , an outlet header 12 b spaced apart from the inlet header 12 a , and a plurality of refrigerant tubes 14 hydraulically connecting the headers 12 a , 12 b for refrigerant flow.
  • An evaporator coil 16 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 12 a , 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 12 a may be located above the outlet header 12 b , below the outlet header 12 b , or horizontal with the outlet header 12 b .
  • the headers 12 a , 12 b 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.
  • This can be achieved by having orifices 22 at angles from 45 to 315 degrees, preferably between 90 to 270 degrees, with respect to the opposite direction of gravity being 0 degree, along the distributor tube 20 to ensure that at least one, but preferably a group, of orifices 22 is substantially oriented within the liquid refrigerant cross-sectional profile 30 .
  • the refrigerant flowing through the distributor tube 20 will push the liquid phase refrigerant through the orifices 22 and toward the refrigerant tubes.
  • 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. 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.
  • 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 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)
US13/114,405 2010-06-01 2011-05-24 Orientation insensitive refrigerant distributor tube Abandoned US20110290465A1 (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US13/114,405 US20110290465A1 (en) 2010-06-01 2011-05-24 Orientation insensitive refrigerant distributor tube
EP11167680.5A EP2392886B1 (fr) 2010-06-01 2011-05-26 Tube de distributeur réfrigérant insensible à l'orientation
CN2011202584714U CN202216453U (zh) 2010-06-01 2011-05-30 具有方向不敏感的制冷剂分配器管的热交换器装置
BRPI1102318A BRPI1102318A8 (pt) 2010-06-01 2011-05-30 Conjunto de trocador de calor
KR1020110051898A KR20110132273A (ko) 2010-06-01 2011-05-31 방위 비감응성 냉매 분배기 튜브

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 (1)

Publication Number Publication Date
US20110290465A1 true US20110290465A1 (en) 2011-12-01

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ID=44583632

Family Applications (1)

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

Country Status (5)

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

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130020061A1 (en) * 2010-04-09 2013-01-24 Ingersoll-Rand Company Formed microchannel heat exchanger
WO2013184522A1 (fr) * 2012-06-08 2013-12-12 Modine Manufacturing Company Échangeur de chaleur, et procédé de distribution de réfrigérant à l'intérieur de celui-ci
WO2014100651A1 (fr) * 2012-12-21 2014-06-26 Trane International Inc. Distributeur de fluide frigorigène d'un échangeur de chaleur à micro-canaux
US20150121950A1 (en) * 2013-11-01 2015-05-07 Delphi Technologies, Inc. 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
US20160076822A1 (en) * 2014-09-16 2016-03-17 Delphi Technologies, Inc. Heat exchanger distributor with intersecting streams
US20160185634A1 (en) * 2013-08-08 2016-06-30 Lotte Chemical Corporation Air diffuser and membrane bio-reactor
US9459057B2 (en) 2013-01-24 2016-10-04 Alcoll USA LLC Heat exchanger
US10551099B2 (en) * 2016-02-04 2020-02-04 Mahle International Gmbh Micro-channel evaporator having compartmentalized distribution
US10563895B2 (en) 2016-12-07 2020-02-18 Johnson Controls Technology Company Adjustable inlet header for heat exchanger of an HVAC system
US20200248974A1 (en) * 2019-02-01 2020-08-06 Mahle International Gmbh Evaporator unit including distributor tube and method thereof
EP3919848A1 (fr) * 2020-06-02 2021-12-08 Hamilton Sundstrand Corporation Évaporateur doté de distributeurs de flux de tubes d'alimentation pour les champs de gravitation et d'accélération aléatoires
US11493277B2 (en) * 2019-11-06 2022-11-08 Carrier Corporation Microchannel heat exchanger
WO2023058179A1 (fr) * 2021-10-07 2023-04-13 三菱電機株式会社 Distributeur de fluide frigorigène, échangeur de chaleur, et climatiseur
WO2023062800A1 (fr) * 2021-10-15 2023-04-20 三菱電機株式会社 Distributeur, échangeur de chaleur et dispositif de thermopompe
EP3619492B1 (fr) * 2017-05-05 2023-07-26 Carrier Corporation Échangeur de chaleur pour applications de pompe à chaleur
US11713931B2 (en) * 2019-05-02 2023-08-01 Carrier Corporation Multichannel evaporator distributor
US11892251B2 (en) * 2018-09-30 2024-02-06 Hangzhou Sanhua Research Institute Co., Ltd. Heat exchanger

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US20140224460A1 (en) * 2013-02-08 2014-08-14 Trane International Inc. Microchannel Heat Exchanger
KR20140116626A (ko) 2013-03-25 2014-10-06 엘지전자 주식회사 열교환기
CN103604254B (zh) * 2013-11-12 2016-07-06 清华大学 一种内置气液两相流分流结构
FR3059405B1 (fr) 2016-11-30 2019-07-12 Valeo Systemes Thermiques Dispositif de distribution d'un fluide refrigerant a l'interieur d'une boite collectrice d'un echangeur thermique
FR3059407B1 (fr) 2016-11-30 2019-10-18 Valeo Systemes Thermiques Dispositif de mixage d'un fluide refrigerant a l'interieur d'une boite collectrice d'un echangeur thermique
FR3059396B1 (fr) 2016-11-30 2020-12-04 Valeo Systemes Thermiques Dispositif de distribution d'un fluide refrigerant a l'interieur d'une boite collectrice d'un echangeur thermique
FR3061951B1 (fr) 2016-11-30 2019-06-21 Valeo Systemes Thermiques Dispositif de distribution d'un fluide refrigerant a l'interieur d'une boite collectrice d'un echangeur thermique.
FR3061281B1 (fr) 2016-11-30 2019-07-12 Valeo Systemes Thermiques Boite collectrice d'un fluide refrigerant comprenant au moins un dispositif de positionnement angulaire d'un conduit
FR3075346B1 (fr) 2017-12-19 2020-05-22 Valeo Systemes Thermiques Boite collectrice d'un echangeur thermique munie d'un organe de maintien et/ou de positionnement angulaire d'un dispositif de distribution d'un fluide refrigerant
FR3075347B1 (fr) 2017-12-19 2020-05-15 Valeo Systemes Thermiques Dispositif de distribution d'un fluide refrigerant destine a etre loge dans une boite collectrice d'un echangeur de chaleur
FR3075345B1 (fr) 2017-12-19 2020-12-04 Valeo Systemes Thermiques Boite collectrice d'un echangeur thermique logeant un dispositif de distribution d'un fluide refrigerant maintenu via un organe de centrage.
CN110966804B (zh) 2018-09-30 2021-09-24 浙江三花智能控制股份有限公司 换热器
CN110966803A (zh) * 2018-09-30 2020-04-07 浙江三花智能控制股份有限公司 换热器
DE102018222815A1 (de) * 2018-12-21 2020-06-25 Mahle International Gmbh Aufnahmekasten für eine Wärmeübertrager

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Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130020061A1 (en) * 2010-04-09 2013-01-24 Ingersoll-Rand Company Formed microchannel heat exchanger
US10001325B2 (en) * 2010-04-09 2018-06-19 Ingersoll-Rand Company Formed microchannel heat exchanger with multiple layers
WO2013184522A1 (fr) * 2012-06-08 2013-12-12 Modine Manufacturing Company Échangeur de chaleur, et procédé de distribution de réfrigérant à l'intérieur de celui-ci
CN107166811A (zh) * 2012-12-21 2017-09-15 特灵国际有限公司 微通道热交换器的制冷剂分配器
WO2014100651A1 (fr) * 2012-12-21 2014-06-26 Trane International Inc. Distributeur de fluide frigorigène d'un échangeur de chaleur à micro-canaux
US10228170B2 (en) 2012-12-21 2019-03-12 Trane International Inc. Refrigerant distributor of micro-channel heat exchanger
CN105074377A (zh) * 2012-12-21 2015-11-18 特灵国际有限公司 微通道热交换器的制冷剂分配器
US10852075B2 (en) 2012-12-21 2020-12-01 Trane International Inc. Refrigerant distributor of micro-channel heat exchanger
US9459057B2 (en) 2013-01-24 2016-10-04 Alcoll USA LLC Heat exchanger
US20160185634A1 (en) * 2013-08-08 2016-06-30 Lotte Chemical Corporation Air diffuser and membrane bio-reactor
EP3031781A4 (fr) * 2013-08-08 2017-01-25 Lotte Chemical Corporation Diffuseur d'air et bioréacteur membranaire
US20150121950A1 (en) * 2013-11-01 2015-05-07 Delphi Technologies, Inc. Evaporator having a hybrid expansion device for improved aliquoting of refrigerant
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
CN105387650A (zh) * 2014-08-26 2016-03-09 德尔福技术公司 双通道蒸发器
US10072900B2 (en) * 2014-09-16 2018-09-11 Mahle International Gmbh Heat exchanger distributor with intersecting streams
US20160076822A1 (en) * 2014-09-16 2016-03-17 Delphi Technologies, Inc. Heat exchanger distributor with intersecting streams
US10551099B2 (en) * 2016-02-04 2020-02-04 Mahle International Gmbh Micro-channel evaporator having compartmentalized distribution
US10563895B2 (en) 2016-12-07 2020-02-18 Johnson Controls Technology Company Adjustable inlet header for heat exchanger of an HVAC system
US11506434B2 (en) * 2016-12-07 2022-11-22 Johnson Controls Tyco IP Holdings LLP Adjustable inlet header for heat exchanger of an HVAC system
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Also Published As

Publication number Publication date
EP2392886A2 (fr) 2011-12-07
EP2392886B1 (fr) 2016-08-24
EP2392886A3 (fr) 2014-07-02
BRPI1102318A8 (pt) 2017-10-24
BRPI1102318A2 (pt) 2012-11-20
CN202216453U (zh) 2012-05-09
KR20110132273A (ko) 2011-12-07

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