EP1809958B1 - Parallelflussverdampfer mit variabler kanaleinsatztiefe - Google Patents

Parallelflussverdampfer mit variabler kanaleinsatztiefe Download PDF

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Publication number
EP1809958B1
EP1809958B1 EP05817473.1A EP05817473A EP1809958B1 EP 1809958 B1 EP1809958 B1 EP 1809958B1 EP 05817473 A EP05817473 A EP 05817473A EP 1809958 B1 EP1809958 B1 EP 1809958B1
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EP
European Patent Office
Prior art keywords
channels
inlet manifold
flow
manifold
depths
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Not-in-force
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EP05817473.1A
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English (en)
French (fr)
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EP1809958A4 (de
EP1809958A2 (de
Inventor
Michael F. Taras
Allen C. Kirkwood
Robert A. Chopko
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Carrier Corp
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Carrier Corp
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Publication of EP1809958A4 publication Critical patent/EP1809958A4/de
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Publication of EP1809958B1 publication Critical patent/EP1809958B1/de
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Classifications

    • 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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0282—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry of conduit ends, e.g. by using inserts or attachments for modifying the pattern of flow at the conduit inlet or outlet
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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

  • This invention relates generally to air conditioning and refrigeration systems and, more particularly, to parallel flow evaporators thereof.
  • a definition of a so-called parallel flow heat exchanger is widely used in the air conditioning and refrigeration industry now and designates a heat exchanger with a plurality of parallel passages, among which refrigerant is distributed and flown in the orientation generally substantially perpendicular to the refrigerant flow direction in the inlet and outlet manifolds. This definition is well adapted within the technical community and will be used throughout the text.
  • Refrigerant maldistribution in refrigerant system evaporators is a well-known phenomenon. It causes significant evaporator and overall system performance degradation over a wide range of operating conditions. Maldistribution of refrigerant may occur due to differences in flow impedances within evaporator channels, non-uniform airflow distribution over external heat transfer surfaces improper heat exchanger orientation or poor manifold and distribution system design. Maldistribution is particularly pronounced in parallel flow evaporators due to their specific design with respect to refrigerant routing to each refrigerant circuit. Attempts to eliminate or reduce the effects of this phenomenon on the performance of parallel flow evaporators have been made with little or no success. The primary reasons for such failures have generally been related to complexity and inefficiency of the proposed technique or prohibitively high cost of the solution.
  • parallel flow heat exchangers and brazed aluminum heat exchangers in particular, have received much attention and interest, not just in the automotive field but also in the heating, ventilation, air conditioning and refrigeration (HVAC&R) industry.
  • HVAC&R heating, ventilation, air conditioning and refrigeration
  • the primary reasons for the employment of the parallel flow technology are related to its superior performance, high degree of compactness and enhanced resistance to corrosion.
  • Parallel flow heat exchangers are now utilized in both condenser and evaporator applications for multiple products and system designs and configurations.
  • the evaporator applications although promising greater benefits and rewards, are more challenging and problematic. Refrigerant maldistribution is one of the primary concerns and obstacles for the implementation of this technology in the evaporator applications.
  • refrigerant maldistribution in parallel flow heat exchangers occurs because of unequal pressure drop inside the channels and in the inlet and outlet manifolds, as well as poor manifold and distribution system design.
  • manifolds the difference in length of refrigerant paths, phase separation, gravity and turbulence are the primary factors responsible for maldistribution.
  • variations in the heat transfer rate, airflow distribution, manufacturing tolerances, and gravity are the dominant factors.
  • minichannels and microchannels which in turn negatively impacted refrigerant distribution. Since it is extremely difficult to control all these factors, many of the previous attempts to manage refrigerant distribution, especially in parallel flow evaporators, have failed.
  • the inlet and outlet manifolds or headers usually have a conventional cylindrical shape.
  • the vapor phase is usually separated from the liquid phase. Since both phases flow independently, refrigerant maldistribution tends to occur.
  • the liquid phase (droplets of liquid) is carried by the momentum of the flow further away from the manifold entrance to the remote portion of the header.
  • the channels closest to the manifold entrance receive predominantly the vapor phase and the channels remote from the manifold entrance receive mostly the liquid phase.
  • the velocity of the two-phase flow entering the manifold is low, there is not enough momentum to carry the liquid phase along the header.
  • the liquid phase enters the channels closest to the inlet and the vapor phase proceeds to the most remote ones.
  • the liquid and vapor phases in the inlet manifold can be separated by the gravity forces, causing similar maldistribution consequences. In either case, maldistribution phenomenon quickly surfaces and manifests itself in evaporator and overall system performance degradation.
  • JP 2001-304775 discloses a single phase parallel flow heat exchanger including an inlet manifold into which channels extend a variable distance.
  • the inlet manifold has a constant cross-sectional area, of which a large part is occupied by the channels. This introduces undesirable impedance to the refrigerant flow along the longitudinal axis of the inlet manifold.
  • the insertion depth of the individual parallel channels into the inlet manifold is varied so as to obtain a more uniform refrigerant distribution to the individual channels by way of the differential pressure drop that is created by the variable insertion depth.
  • a two-phase refrigerant mixture is more uniformly distributed among the channels.
  • the variable insertion depth of the individual channels is accommodated by appropriately enlarging the diameter of the inlet manifold. The enlargement is variable such that the portions immediately surrounding the individual channels are larger and the portions therebetween are smaller.
  • the insertion depth of the individual channels is progressively smaller toward the downstream end of the inlet manifold such that the hydraulic resistance to flow is progressively lower toward the downstream channels.
  • the insertion depth of the individual channels into the outlet manifold is also varied to compensate for variable flow impedance in the outlet manifold as well.
  • a parallel flow heat exchanger is shown to include an inlet header or manifold 11, an outlet header or manifold 12 and a plurality of parallel disposed channels 13 fluidly interconnecting the inlet manifold 11 to the outlet manifold 12.
  • the inlet and outlet manifolds 11 and 12 are cylindrical in shape, and the channels 13 are usually tubes (or extrusions) of flattened or round shape.
  • Channels 13 normally have a plurality of internal and external heat transfer enhancement elements, such as fins. For instance, external fins, disposed therebetween for the enhancement of the heat exchange process and structural rigidity, are typically furnace-brazed.
  • Channels 13 may have internal heat transfer enhancements and structural elements as well.
  • the usual manner of attaching the parallel channels 13 to the inlet manifold 11 and the outlet manifold 12 is to insert the channels 13 so that they extend into the internal cavities of the inlet and outlet manifolds 11 and 12 as shown by the dotted lines.
  • the usual practice is to have equal insertion depth for each of the channels 13. They are then fixed in position by way of brazing or the like.
  • two-phase refrigerant flows into the inlet opening 14 and into the internal cavity 16 of the inlet header 11.
  • the refrigerant in the form of a liquid, a vapor or a mixture of liquid and vapor (the most typical scenario) enters the tube openings 17 to pass through the channels 13 to the internal cavity 18 of the outlet header 12.
  • the refrigerant which is now usually in the form of a vapor, passes out the outlet opening 19 and then to the compressor (not shown).
  • the two-phase refrigerant passing from the inlet header 11 to the individual channels 13 do so in a uniform manner (or in other words, with equal vapor quality) such that the full heat exchange benefit of the individual channels can be obtained and flooding conditions are not created and observed at the compressor suction (this may damage the compressor).
  • a non-uniform flow of refrigerant to the individual channels 13 occurs.
  • the applicants have introduced design features that will create different pressure drop for flow of refrigerant from the inlet manifold to the individual channels to thereby bring about a more uniform flow of refrigerant into the channels 13. Additionally, increased velocity of the refrigerant flow in the inlet manifold promotes more homogeneous conditions through mixing and jetting effects.
  • Fig. 2 the present invention is illustrated in accordance with one embodiment.
  • the penetration thereinto is variable, depending on the position along the longitudinal axis A.
  • the channel 21 closest to the inlet 14 penetrates the furthest into the internal cavity 16 and those following (i.e. channels 22 and 23) are so placed and installed with respect to the inlet manifold 11 so as to have progressively smaller insertion depths as shown.
  • the two-phase refrigerant enters the internal cavity 16 by way of the inlet 14 and, because of the limited distance between the penetrating end 24 of tube 21 and the opposing wall 28 of the inlet manifold 11, there would be increased hydraulic resistance and therefore restricted flow into the channel 21.
  • the next channel 22, with its reduced insertion depth, provides a greater distance between the end 26 and the wall 28.
  • the next downstream channel 23 has its end 27 inserted an even smaller distance into the cavity, and any subsequent channels are progressively decreased in their insertion depth. Therefore, the problem of the more upstream tubes receiving a greater portion of the refrigerant is overcome by selectively varying the impedance to the flow at the entrance into each of the channels. Additionally, increased velocity of the refrigerant flow in the inlet manifold 16 may promote more homogeneous conditions through mixing and jetting effects.
  • each individual channel shown in Fig. 2 would represent a section of such channels for a sufficiently large heat exchanger.
  • the insertion depth Li of the first tube 21 would preferably be in the range of 7/8".
  • the next channel 22 would have an insertion depth Of(Li-L2) or (7/8"- 1/16"), and each succeeding tube would have a diminishing insertion depth by L2 1/16".
  • the insertion depth Li of the individual channels depends on many parameters, including the heat exchanger size, channel size and number, typical operating range, refrigerant and oil type circulating through the system, etc.
  • the relatively wide channels 21, 22 and 23, which occupy a large part of the cross-section area of the inlet manifold 11, may each introduce undesired impedance to the refrigerant flow along the longitudinal axis of the inlet manifold 11. In this example, not part of the present invention, this may be accommodated by an increase in the diameter D of the inlet manifold 11.
  • the cross-section area of a header 31 is enlarged only in the immediate vicinity of the insertion points of the channels 21, 22 and 23 into the header 31. In this way, the restriction to the refrigerant flow around the ends of the channels is avoided or limited so as to promote favorable uniform conditions to the refrigerant flow into the channels, as desired.
  • the form and shape of the enlargements may vary, the wavy shape tends to provide a smoother, less disturbed motion of the refrigerant passing along the inlet header and would be preferred.
  • an inlet manifold can be made of an oval or rectangular shape as shown by 37 and 38 respectively, without appreciably increasing its overall cross-section area. This will prevent refrigerant flow velocity reduction and potential undesired phase separation.
  • outlet manifold 41 typically having a single phase refrigerant vapor
  • the outlet manifold has a less pronounced influence on the refrigerant distribution among the channels, such balancing of the flow impedances will further assist in the maldistribution problem resolution.

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

Claims (7)

  1. Parallelflusswärmetauscher, umfassend:
    ein Ansaugrohr (11) mit einer Einlassöffnung zum Leiten eines Flusses eines Zwei-Phasen-Fluids in das Ansaugrohr und eine Vielzahl von Auslassöffnungen zum Leiten des Fluidflusses aus dem Ansaugrohr;
    eine Vielzahl von Kanälen (13), die in einer im Wesentlichen parallelen Beziehung aneinandergereiht und mit der Vielzahl von Auslassöffnungen flussverbunden sind, um den Fluidfluss aus dem Ansaugrohr zu leiten;
    ein Auslassrohr (12), das mit der Vielzahl von Kanälen flussverbunden ist, um den Fluidfluss aus diesem zu empfangen, wobei sich die Vielzahl von Kanälen in verschiedenen Tiefen in das Ansaugrohr erstreckt und in Ebenen quer zu der Längsachse des Ansaugrohrs im Wesentlichen flach sind, dadurch gekennzeichnet, dass die Querschnittsflächen des Ansaugrohrs in der Umgebung der Bereiche, die die flachen Kanäle umgeben, örtlich vergrößert sind, um den Fluidfluss um die Vielzahl von Kanälen herum zu erlauben.
  2. Parallelflusswärmetauscher nach Anspruch 1, wobei sich die Erstreckungstiefen in das Ansaugrohr der Vielzahl von Kanälen in Richtung des nachgelagerten Endes des Ansaugrohrs verringern.
  3. Parallelflusswärmetauscher nach Anspruch 2, wobei die parallelen Kanäle in Abschnitte unterteilt sind, wobei jeder Abschnitt gleiche Erstreckungstiefen aufweist und sich die Erstreckungstiefen in das Ansaugrohr von Abschnitt zu Abschnitt in Richtung des nachgelagerten Endes des Ansaugrohrs verringern.
  4. Parallelflusswärmetauscher nach einem der vorherigen Ansprüche, wobei sich die Vielzahl von Kanälen in verschiedenen Tiefen in das Auslassrohr erstrecken.
  5. Verfahren zur Bedienung eines Parallelflusswärmetauschers, umfassend:
    Bereitstellen eines Ansaugrohrs (11) mit einer Einlassöffnung und einer Vielzahl von Auslassöffnungen;
    Bereitstellen einer Vielzahl von Kanälen (13), die in einer im Wesentlichen parallelen Beziehung aneinandergereiht sind, mit der Vielzahl von Auslassöffnungen flussverbunden sind und sich in verschiedenen Tiefen in das Ansaugrohr erstrecken;
    wobei die Vielzahl von Kanälen an Stellen quer zu der Längsachse des Ansaugrohrs im Wesentlichen flach sind, und
    Bereitstellen eines Auslassrohrs (12), das mit der Vielzahl von Kanälen flussverbunden ist;
    Leiten eines Flusses von Zwei-Phasen-Fluid in das Ansaugrohr durch die Einlassöffnung;
    wobei ein Druckabfall an jedem der Vielzahl von Kanälen, die sich in verschiedenen Tiefen in das Ansaugrohr erstrecken, variiert wird, und wobei die sich in verschiedenen Tiefen in das Ansaugrohr erstreckenden Kanäle das Zwei-Phasen-Fluid mischen und ausstoßen, um homogene Bedingungen zu fördern, gekennzeichnet durch Bereitstellen von Querschnittsflächen des Ansaugrohrs, die in der Umgebung der Bereiche, die die flachen Kanäle umgeben, örtlich vergrößert sind, um den Fluidfluss um die Vielzahl von Kanälen herum zu erlauben.
  6. Verfahren nach Anspruch 5, wobei sich die Erstreckungstiefen in das Einlassrohr für die Vielzahl von Kanälen in Richtung des nachgelagerten Endes des Ansaugrohrs verringern.
  7. Verfahren nach Anspruch 5, wobei die parallelen Kanäle in Abschnitte unterteilt sind, wobei jeder Abschnitt gleiche Erstreckungstiefen aufweist und sich die Erstreckungstiefen in das Ansaugrohr von Abschnitt zu Abschnitt in Richtung des nachgelagerten Endes des Ansaugrohrs verringern.
EP05817473.1A 2004-11-12 2005-11-04 Parallelflussverdampfer mit variabler kanaleinsatztiefe Not-in-force EP1809958B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US10/987,960 US20060101849A1 (en) 2004-11-12 2004-11-12 Parallel flow evaporator with variable channel insertion depth
PCT/US2005/040164 WO2006055297A2 (en) 2004-11-12 2005-11-04 Parallel flow evaporator with variable channel insertion depth

Publications (3)

Publication Number Publication Date
EP1809958A2 EP1809958A2 (de) 2007-07-25
EP1809958A4 EP1809958A4 (de) 2010-11-24
EP1809958B1 true EP1809958B1 (de) 2018-01-03

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EP05817473.1A Not-in-force EP1809958B1 (de) 2004-11-12 2005-11-04 Parallelflussverdampfer mit variabler kanaleinsatztiefe

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US (1) US20060101849A1 (de)
EP (1) EP1809958B1 (de)
ES (1) ES2657624T3 (de)
WO (1) WO2006055297A2 (de)

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ES2657624T3 (es) 2018-03-06
EP1809958A4 (de) 2010-11-24
WO2006055297A2 (en) 2006-05-26
EP1809958A2 (de) 2007-07-25
US20060101849A1 (en) 2006-05-18

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