EP2310786B1 - Mikrokanal-wärmetauscher mit verbesserter kältemittelverteilung - Google Patents

Mikrokanal-wärmetauscher mit verbesserter kältemittelverteilung Download PDF

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Publication number
EP2310786B1
EP2310786B1 EP09747084.3A EP09747084A EP2310786B1 EP 2310786 B1 EP2310786 B1 EP 2310786B1 EP 09747084 A EP09747084 A EP 09747084A EP 2310786 B1 EP2310786 B1 EP 2310786B1
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EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
manifold
set forth
distributor insert
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.)
Active
Application number
EP09747084.3A
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English (en)
French (fr)
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EP2310786A4 (de
EP2310786A2 (de
Inventor
Michael F. Taras
Alexander Lifson
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.)
Carrier Corp
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Carrier Corp
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Publication date
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Publication of EP2310786A4 publication Critical patent/EP2310786A4/de
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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
    • 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 microchannels heat exchangers of refrigerant systems that utilize a distributor insert mounted within a manifold, and more particularly to heat exchangers incorporating dividing elements separating the manifold into a plurality of chambers, each associated with at least one heat exchange tube.
  • JP-6-159983 discloses a heat exchanger as defined in the preamble of claim 1.
  • 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.
  • the present invention provides a microchannel heat exchanger comprising: a plurality of heat transfer tubes; a manifold for communicating refrigerant into said plurality of heat transfer tubes; and a distributor insert connectable to a source of refrigerant and having a plurality of orifices in an outer periphery of said distributor insert, characterised by dividing elements on an outer wall of said distributor insert such that a plurality of distribution chambers are defined and associated with said plurality of heat transfer tubes, wherein the plurality of orifices are arranged to uniformly direct the refrigerant into the plurality of distribution chambers.
  • 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.
  • 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.
  • FIG. 2 A portion of the evaporator 30, that includes an inlet refrigerant manifold 34 incorporating the present invention, is illustrated in Figure 2 .
  • the evaporator 30 is a microchannel heat exchanger, such heat exchangers particularly benefit from this inventive design and construction.
  • the benefits of this invention can extend to other applications, such as, for instance, condenser applications.
  • 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.
  • An outer periphery of the dividing elements 44 is tightly received within an inner wall of the inlet manifold 34. Similarly, an inner periphery of the dividing elements 44 is closely received on an outer wall of the insert 32. In this manner, adjacent separation chambers 46 are maintained predominantly isolated from each other preventing refrigerant migration from one separation chamber 46 to another. Therefore, the overall characteristics of the refrigerant flow into the heat exchange tubes 36 can be controlled such that the effects of phase separation and/or refrigerant migration can be eliminated or minimized.
  • Figure 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). Both attachment processes can be performed, for instance, during furnace brazing of the entire heat exchanger 30.
  • Figures 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)

Claims (14)

  1. Mikrokanalwärmetauscher (30), umfassend:
    eine Mehrzahl von Wärmeübertragungsröhren (36);
    einen Verteiler (34) zum Leiten von Kältemittel in die Mehrzahl von Wärmeübertragungs-röhren; und
    einen Verteilungseinsatz (32), der mit einer Quelle von Kältemittel verbindbar ist und eine Mehrzahl von Mündungen (42) an einem Außenumfang des Verteilungseinsatzes aufweist,
    gekennzeichnet durch Teilungselemente (44) an einer Außenwand des Verteilungseinsatzes, derart, dass eine Mehrzahl von Verteilungskammern (46) definiert wird und der Mehrzahl von Wärmeübertragungsröhren zugeordnet wird, wobei die Mehrzahl von Mündungen derart angeordnet ist, dass sie das zweiphasige Kältemittel gleichmäßig in der Mehrzahl von Verteilungskammern verteilt.
  2. Wärmetauscher nach Anspruch 1, wobei der Verteilungseinsatz und die Teilungselemente die Kältemittelverteilung in dem Wärmetauscher verbessern.
  3. Wärmetauscher nach Anspruch 1, wobei die Teilungselemente entlang einer Längserstreckung des Verteilungseinsatzes gleichmäßig beabstandet sind.
  4. Wärmetauscher nach Anspruch 1, wobei die Teilungselemente durch eine von einer mechanischen Anbringung und chemischer Bindung an dem Verteilungseinsatz angebracht sind.
  5. Wärmetauscher nach Anspruch 1, wobei der Verteilungseinsatz eine runde Querschnittform aufweist.
  6. Wärmetauscher nach Anspruch 1, wobei der Verteiler eine Innenbohrung mit einer runden Querschnittform aufweist.
  7. Wärmetauscher nach Anspruch 1, wobei das Kältemittel, das durch den Verteilungseinsatz gelangt, ein zweiphasiges Kältemittel ist.
  8. Kältesystem, umfassend:
    einen Kompressor, wobei der Kompressor zum Verdichten eines Kältemittels und zum Leiten des Kältemittels stromabwärts in einen Kondensator dient, wobei Kältemittel von dem Kondensator durch eine Ausdehnungsvorrichtung und dann in einen Verdampfer gelangt, wobei wenigstens einer von dem Kondensator und dem Verdampfer ein Wärmetauscher nach Anspruch 1 ist.
  9. Kältesystem nach Anspruch 8, wobei sich der Verteilungseinsatz von einem Stromaufwärtsende des Verteilers zu einem Stromabwärtsende des Verteilers erstreckt und die Größe der Trennungskammern, die zwischen benachbarten der Teilungselemente definiert sind, festgelegt ist, um den Fluss von Kältemittel innerhalb der Mehrzahl von Wärmeübertragungsröhren zu optimieren.
  10. Kältesystem nach Anspruch 8, wobei die Mehrzahl von Wärmeübertragungsröhren, die jeweils eine Mehrzahl von Kanälen aufweisen, allgemein senkrecht zu einer Stromaufwärtsstromabwärts-Richtung des Verteilungseinsatzes beabstandet ist.
  11. Wärmetauscher oder Kältesystem nach Anspruch 1 oder 8, wobei der Wärmetauscher ein Verdampfer ist und der Verteiler ein Einlassverteiler ist.
  12. Wärmetauscher oder Kältesystem nach Anspruch 1 oder 8, wobei der Verteiler ein Zwischenverteiler ist.
  13. Wärmetauscher oder Kältesystem nach Anspruch 1 oder 12, wobei der Verteilungseinsatz sich nur an einem Teil des Verteilers entlang erstreckt und nicht an den Wärmeübertragungsröhren ausgerichtet ist, die in den Verteiler eingehen, sondern an den Wärmeübertragungsröhren ausgerichtet ist, die aus dem Verteiler austreten.
  14. Wärmetauscher oder Kältesystem nach Anspruch 1 oder 8, wobei die Teilungselemente flache Platten sind, die an einem Außenumfang einen Aussparungsabschnitt aufweisen, um Platz für die Wärmeübertragungsröhren zu schaffen.
EP09747084.3A 2008-05-16 2009-04-13 Mikrokanal-wärmetauscher mit verbesserter kältemittelverteilung Active EP2310786B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US5367708P 2008-05-16 2008-05-16
PCT/US2009/040314 WO2009139998A2 (en) 2008-05-16 2009-04-13 Microchannel heat exchanger with enhanced refrigerant distribution

Publications (3)

Publication Number Publication Date
EP2310786A2 EP2310786A2 (de) 2011-04-20
EP2310786A4 EP2310786A4 (de) 2013-04-10
EP2310786B1 true EP2310786B1 (de) 2014-09-24

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Country Status (5)

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US (1) US20110000255A1 (de)
EP (1) EP2310786B1 (de)
CN (1) CN102027308A (de)
ES (1) ES2511036T3 (de)
WO (1) WO2009139998A2 (de)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023192442A1 (en) * 2022-04-01 2023-10-05 Goodman Manufacturing Company, L.P. Fixed orifice refrigerant distribution system
US11946676B2 (en) 2022-04-01 2024-04-02 Goodman Manufacturing Company, L.P. Fixed orifice refrigerant distribution system

Also Published As

Publication number Publication date
WO2009139998A3 (en) 2010-01-28
ES2511036T3 (es) 2014-10-22
EP2310786A4 (de) 2013-04-10
WO2009139998A2 (en) 2009-11-19
EP2310786A2 (de) 2011-04-20
CN102027308A (zh) 2011-04-20
US20110000255A1 (en) 2011-01-06

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