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WO2009139998A2 - Échangeur de chaleur à microcanaux a distribution amélioré du réfrigérant - Google Patents

Échangeur de chaleur à microcanaux a distribution amélioré du réfrigérant Download PDF

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Publication number
WO2009139998A2
WO2009139998A2 PCT/US2009/040314 US2009040314W WO2009139998A2 WO 2009139998 A2 WO2009139998 A2 WO 2009139998A2 US 2009040314 W US2009040314 W US 2009040314W WO 2009139998 A2 WO2009139998 A2 WO 2009139998A2
Authority
WO
WIPO (PCT)
Prior art keywords
manifold
refrigerant
heat exchanger
set forth
transfer tubes
Prior art date
Application number
PCT/US2009/040314
Other languages
English (en)
Other versions
WO2009139998A3 (fr
Inventor
Michael F. Taras
Alexander Lifson
Original Assignee
Carrier Corporation
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 Carrier Corporation filed Critical Carrier Corporation
Priority to US12/921,414 priority Critical patent/US20110000255A1/en
Priority to CN2009801177453A priority patent/CN102027308A/zh
Priority to EP09747084.3A priority patent/EP2310786B1/fr
Priority to ES09747084.3T priority patent/ES2511036T3/es
Publication of WO2009139998A2 publication Critical patent/WO2009139998A2/fr
Publication of WO2009139998A3 publication Critical patent/WO2009139998A3/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
    • F28F2260/02—Heat exchangers or heat exchange elements having special size, e.g. microstructures having microchannels

Definitions

  • This application relates to heat exchangers of refrigerant systems that utilize a distributor insert mounted within a manifold, and incorporating dividing elements separating the manifold into a plurality of chambers, each associated with at least one heat exchange tube.
  • Such microchannel heat exchangers are provided with a plurality of parallel heat exchange tubes, among which refrigerant is distributed and flown in a parallel manner.
  • the heat exchange tubes are orientated generally substantially perpendicular to a refrigerant flow direction in the inlet, intermediate and outlet manifolds that are in flow communication with the heat exchange tubes.
  • these heat exchangers may be designed in multi-pass configuration, typically with a plurality of parallel heat exchange tubes within each refrigerant pass, in order to obtain superior performance by balancing and optimizing heat transfer and pressure drop characteristics.
  • Single-pass configurations are typically more desirable in the evaporator applications, since the refrigerant pressure drop plays a dominant role in the evaporator performance.
  • a problem typically occurs in the microchannel heat exchanger manifolds when the two-phase flow enters the manifold.
  • a vapor phase of the two-phase flow has significantly different properties, moves at different velocities and is subjected to different effects of internal and external forces than a liquid phase. This causes the vapor phase to separate from the liquid phase and to flow independently.
  • the separation of the vapor phase from the liquid phase has raised challenges, such as refrigerant maldistribution in parallel flow heat exchangers.
  • Another proposed heat exchanger is constructed of a plurality of plates.
  • the heat exchange refrigerant channels are formed of spaced plates, and remote ends of those spaced plates provide inlet plenums for each refrigerant channel.
  • the plates separate adjacent plenums, and an insert tube extends through the plates and into the plenums.
  • This tube includes a plurality of orifices which direct refrigerant into the individual plenums. This arrangement would not be practical for microchannel heat exchangers, and would only be a practical construction for the one type of heat exchanger formed of the spaced plates.
  • a manifold for a heat exchanger incorporates a distributor insert positioned within a manifold cavity.
  • the distributor insert has multiple refrigerant distribution orifices of a small size protruding through the distributor walls, and also has dividing elements located on its periphery.
  • the dividing elements act as manifold separation members by defining separate chambers within the manifold cavity, with each chamber fluidly communicating with at least one heat exchange tube positioned downstream, with respect to refrigerant flow.
  • the heat exchanger manifold is an inlet manifold of an evaporator and, in another embodiment, the heat exchanger manifold is an intermediate manifold of a condenser or an evaporator.
  • separation chambers may be of an identical size and the distributor dividing elements uniformly spaced, in one embodiment, they are of a variable size to further fine tune refrigerant distribution.
  • the invention is disclosed in relation to a two-phase refrigerant, it is also applicable to a single-phase refrigerant and refrigerant- oil mixtures.
  • Figure 1 schematically shows a basic exemplary refrigerant system.
  • Figure 2 shows a portion of an inlet manifold of an inventive heat exchanger.
  • Figure 3 shows a portion of an intermediate manifold of an inventive heat exchanger.
  • Figure 4 shows an exemplary design of a distributor insert.
  • Figure 5A shows a cross-sectional view of an exemplary heat transfer tube.
  • Figure 5B shows a cross-sectional view of an exemplary dividing element.
  • Figure 5C shows a side view of an exemplary dividing element of Figure 5B.
  • Figure 5D shows a cross-sectional view of another exemplary dividing element.
  • Figure 5E shows a side view of an exemplary dividing element of Figure 5D.
  • a basic exemplary refrigerant system 20 is illustrated in Figure 1 including a compressor 22 compressing a refrigerant and delivering it downstream into a condenser 24. From the condenser 24 the refrigerant passes through an expansion device 26 into an inlet refrigerant pipe 28 leading into an evaporator 30. From the evaporator 30, the refrigerant is returned to the compressor 22 to complete the closed-loop refrigerant circuit.
  • the evaporator 30 is shown as a microchannel heat exchanger, as such heat exchangers would particularly benefit from this inventive design and construction.
  • the benefits of this invention can extend to other types of heat exchangers, such as, for instance, round tube and plate fin heat exchangers, and to various applications, such as, for instance, condenser applications.
  • the benefits of the invention will be disclosed in reference to a two- phase refrigerant flow passing through the heat exchanger, single-phase refrigerant flows and refrigerant- oil mixtures are also within the scope and can benefit from the invention.
  • the inlet refrigerant pipe 28 fluidly communicates with a distributor insert 32, which provides a refrigerant flow path along its longitudinal axis.
  • An inlet manifold 34 of the evaporator 30 receives the distributor insert 32, and in turn fluidly communicates with a plurality of heat exchange tubes 36 positioned generally perpendicular to and downstream, with respect to the direction of refrigerant flow, of the inlet manifold 34.
  • the inlet refrigerant pipe 28 may be positioned at the end of the inlet manifold 34, in the middle of the inlet manifold 34 or at any intermediate location in- between.
  • the inlet refrigerant pipe 28 may comprise two inlet refrigerant pipes connected at the opposite ends of the inlet manifold 34 or at any intermediate locations. Obviously, more than two inlet refrigerant pipes can be utilized, but all of them need to be fluidly connected and provide refrigerant paths into the distributor insert 32.
  • each heat exchange tube 36 of a microchannel heat exchanger (evaporator) 30 typically has a plurality of small internal channels 41 providing multiple parallel refrigerant flow paths along longitudinal axis of each heat exchange tube 36 (see Figure 5A).
  • the internal channels 41 enhance internal heat transfer and also provide structural rigidity for the heat exchanger 30.
  • a plurality of refrigerant distribution orifices 42 of a small size are formed to protrude through the walls of the distributor insert 32 and to provide the refrigerant paths from an internal cavity of the distributor insert 32 into the inlet manifold 34.
  • the distribution orifices 42 can be, for instance, of a round shape, rectangular shape, oval shape or any other shape.
  • the distributor insert 32 has dividing elements 44 located on its periphery and rigidly attached to the outside walls of the distributor insert 32.
  • each separation chamber Upon positioning the distributor insert 32 within the inlet manifold 34 of the evaporator 30, the dividing elements 44 form refrigerant separation chambers 46 within the internal cavity of the inlet manifold 34, with each chamber communicating refrigerant downstream to at least one heat exchange tube 36. Typically, each separation chamber would be fluidly connected to several refrigerant distribution orifices 42 and several heat exchange tubes 46.
  • a plurality of small refrigerant distribution orifices 42 is provided to direct the refrigerant from the distributor insert 34 into a plurality of separation chambers 46 defined by adjacent dividing elements 44 of the distributor insert 32 within the cavity of the inlet manifold 34.
  • the distance between the dividing elements 44 can be uniform or can be adjusted to control the ultimate size of the separation chambers 46 associated with any particular cluster of heat transfer tubes 36. This distance between the dividing elements 44 may vary from one cluster of heat transfer tubes 36 to another, or in an extreme case, from one heat transfer tube 36 to another.
  • the size of the chambers 46 may be uniform along the longitudinal axis of the manifold 34 or, for instance, may decrease from the manifold inlet end to its remote end, where refrigerant velocity is expected to be lower.
  • Any particular configuration of the dividing elements 44 could depend on operational parameters and particular application.
  • the distributor insert 32 receives the two-phase refrigerant from the inlet refrigerant pipe 28 and delivers this refrigerant, through a plurality of small distribution orifices 42, into the heat exchanger manifold 34 that has been divided into the separation chambers 46 by the dividing elements 44 of the distributor insert 32.
  • a relatively small size of the distributor insert 32 provides significant momentum for the refrigerant flow preventing the phase separation of the two-phase refrigerant.
  • the plurality of the distribution orifices 42 uniformly directs the two-phase refrigerant into the plurality of separation chambers 46 of the manifold 34 defined by the spaced dividing elements 44 of the distributor insert 34.
  • the refrigerant liquid and vapor phases do not have conditions and time to separate, as in the prior art, when the two-phase refrigerant was expanded into the entire inlet manifold cavity. Even in cases where some separation of the refrigerant phases occurs, it would be within a relatively small manifold chamber 46, and on average, the refrigerant distribution would be still predominantly uniform across the entire heat exchanger 30. Therefore, the inventive distributor concept having a plurality of small distribution orifices 42 and dividing elements 44 prevents refrigerant maldistribution and assures uniform refrigerant distribution into the heat exchange tubes 36.
  • the refrigerant being delivered into the heat exchange tubes 36 through the distributor insert orifices 42 and separation chambers 46 of the inlet manifold 34 will not have different quantities of vapor and liquid phases flowing through different heat exchange tubes and heat exchanger tube clusters.
  • FIG. 3 shows another embodiment 300, wherein the manifold 301 is an intermediate manifold, downstream of heat exchange tubes 302, and feeding the refrigerant into heat exchange tubes 312.
  • the distributor insert 306 has orifices 308, a top separator plate 304, and intermediate separator plates 310.
  • This embodiment functions as in the prior embodiment to reduce refrigerant phase separation and maldistribution.
  • the heat exchanger could be a condenser, or an evaporator.
  • the dividing elements 44 can be of any shape and form, such as, for instance, flat plates (see Figure 5B), as long as they do not drastically block refrigerant flow into the heat exchange tubes 36 and isolate one separation chamber 46 from another (e.g. by a small clearance or mechanical/chemical bonding). Furthermore, dividing elements 44 may have cutouts 200, in case the heat exchange tubes 36 penetrate inside the inlet manifold 34 (see Figures 5B and 5C).
  • the dividing elements 44 may be attached to the distributor insert 32 mechanically (e.g. snapped into place into small groves manufactured on the outer wall of the distributor insert 32), or by brazing, welding or soldering.
  • the dividing elements 44 may be also attached to the inner wall of the inlet manifold 34 (e.g. by furnace brazing).
  • FIGS. 5D and 5E show another embodiment, wherein the dividing elements 44 do not include the cutout 200, but do include a groove or indentation 202. The purpose of this indentation is to provide a holding cavity for brazing flux such that the distributor insert can be inserted into a manifold and brazed upon construction of the overall heat exchanger
  • each of the disclosed embodiments teaches a distributor insert which will receive refrigerant, and distribute refrigerant through a plurality of orifices into separation chambers defined between dividing elements. Since the insert and the dividing elements are attached to each other as a rigid sub-assembly, the entire assembly can be inserted into a manifold. This will allow the use of this feature without requiring any specific heat exchanger design, as has been the case in the prior art.

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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)

Abstract

Évaporateur doté d'un collecteur recevant un insert de distribution. Cet insert reçoit le flux de réfrigérant devant être distribué dans le collecteur et présente des ouvertures mettant le réfrigérant en communication avec une pluralité de chambres définies entre des éléments diviseurs de l'insert de distribution à l'intérieur du collecteur. De cette manière, ces chambres sont chacune associées à des tubes de transfert de chaleur distincts, ceci de telle sorte qu'elles sont isolées les unes des autres.
PCT/US2009/040314 2008-05-16 2009-04-13 Échangeur de chaleur à microcanaux a distribution amélioré du réfrigérant WO2009139998A2 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US12/921,414 US20110000255A1 (en) 2008-05-16 2009-04-13 Microchannel heat exchanger with enhanced refrigerant distribution
CN2009801177453A CN102027308A (zh) 2008-05-16 2009-04-13 具有增强的制冷剂分布的微通道热交换器
EP09747084.3A EP2310786B1 (fr) 2008-05-16 2009-04-13 Échangeur de chaleur à microcanaux a distribution amélioré du réfrigérant
ES09747084.3T ES2511036T3 (es) 2008-05-16 2009-04-13 Intercambiador de calor con microcanales con distribución de refrigerante mejorada

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US5367708P 2008-05-16 2008-05-16
US61/053,677 2008-05-16

Publications (2)

Publication Number Publication Date
WO2009139998A2 true WO2009139998A2 (fr) 2009-11-19
WO2009139998A3 WO2009139998A3 (fr) 2010-01-28

Family

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Family Applications (1)

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PCT/US2009/040314 WO2009139998A2 (fr) 2008-05-16 2009-04-13 Échangeur de chaleur à microcanaux a distribution amélioré du réfrigérant

Country Status (5)

Country Link
US (1) US20110000255A1 (fr)
EP (1) EP2310786B1 (fr)
CN (1) CN102027308A (fr)
ES (1) ES2511036T3 (fr)
WO (1) WO2009139998A2 (fr)

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WO2011126488A3 (fr) * 2010-04-09 2012-08-02 Ingersoll-Rand Company Échangeur de chaleur à microcanaux formés
CN104272055A (zh) * 2013-01-24 2015-01-07 阿尔科伊尔美国有限责任公司 热交换器
EP2998137A1 (fr) * 2014-09-16 2016-03-23 Delphi Technologies, Inc. Distributeur d'échangeur de chaleur à flux croisés
CN105944652A (zh) * 2016-06-22 2016-09-21 辽宁石油化工大学 列管式微通道烷基化反应器及其使用方法
CN106076237A (zh) * 2016-06-22 2016-11-09 辽宁石油化工大学 列管与固定床耦合微通道烷基化反应器及其应用
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CN105485972B (zh) * 2014-09-18 2019-12-03 浙江盾安人工环境股份有限公司 一种微通道换热器及安装方法
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EP4246075A3 (fr) * 2017-05-05 2023-12-06 Carrier Corporation Échangeur de chaleur pour applications de pompe à chaleur
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US20220090864A1 (en) * 2019-09-11 2022-03-24 Carrier Corporation Heat exchanger assembly
CN111457621A (zh) * 2020-01-09 2020-07-28 安徽威灵汽车部件有限公司 换热器、换热系统、家用电器和车辆
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CN114340297A (zh) * 2020-09-29 2022-04-12 台达电子工业股份有限公司 水冷装置及其集流器
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WO2011126488A3 (fr) * 2010-04-09 2012-08-02 Ingersoll-Rand Company Échangeur de chaleur à microcanaux formés
US10001325B2 (en) 2010-04-09 2018-06-19 Ingersoll-Rand Company Formed microchannel heat exchanger with multiple layers
US20180231322A1 (en) * 2010-04-09 2018-08-16 Ingersoll-Rand Company Formed microchannel heat exchanger
CN101893403A (zh) * 2010-08-05 2010-11-24 浙江金宸三普换热器有限公司 新型均配结构的平行流式换热器
US9644905B2 (en) 2012-09-27 2017-05-09 Hamilton Sundstrand Corporation Valve with flow modulation device for heat exchanger
CN104272055A (zh) * 2013-01-24 2015-01-07 阿尔科伊尔美国有限责任公司 热交换器
EP2998137A1 (fr) * 2014-09-16 2016-03-23 Delphi Technologies, Inc. Distributeur d'échangeur de chaleur à flux croisés
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EP2310786A4 (fr) 2013-04-10
EP2310786A2 (fr) 2011-04-20
WO2009139998A3 (fr) 2010-01-28
CN102027308A (zh) 2011-04-20
US20110000255A1 (en) 2011-01-06
EP2310786B1 (fr) 2014-09-24
ES2511036T3 (es) 2014-10-22

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