EP2242963B1 - Wärmetauscher mit einem verteiler mit mehreren rohren - Google Patents

Wärmetauscher mit einem verteiler mit mehreren rohren Download PDF

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Publication number
EP2242963B1
EP2242963B1 EP08732511.4A EP08732511A EP2242963B1 EP 2242963 B1 EP2242963 B1 EP 2242963B1 EP 08732511 A EP08732511 A EP 08732511A EP 2242963 B1 EP2242963 B1 EP 2242963B1
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EP
European Patent Office
Prior art keywords
tube
heat exchanger
refrigerant
recited
fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP08732511.4A
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English (en)
French (fr)
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EP2242963A1 (de
Inventor
Robert Hong-Leung Chiang
Pingli Hou
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
Original Assignee
Carrier Corp
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Filing date
Publication date
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Publication of EP2242963A1 publication Critical patent/EP2242963A1/de
Application granted granted Critical
Publication of EP2242963B1 publication Critical patent/EP2242963B1/de
Not-in-force 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • 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
    • 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
    • F25B39/022—Evaporators with plate-like or laminated elements

Definitions

  • This invention relates generally to a heat exchanger including an inlet manifold and a distributor tube according to the preamble of claim 1.
  • a heat exchanger is known from WO 94/14021 .
  • a microchannel heat exchanger (MCHX) includes flat tubes that extend between an inlet manifold and an outlet manifold. Refrigerant flows through the flat tubes and exchanges heat with air that passes over the tubes.
  • a distributor tube can be used to decrease maldistribution of the refrigerant in the inlet manifold.
  • the distributor tube includes an inlet, an outlet and orifices. Refrigerant enters the tube through the inlet, and the outlet is blocked to discharge the refrigerant through the orifices.
  • the build-up of pressure in the distributor tube causes the refrigerant to equally distribute along the length of the distributor tube.
  • the orifices are appropriately sized to cause a pressure drop or build-up in the distributor tube.
  • the distributor tube and the orifices are also sized appropriately to reduce the amount of separation of vapor refrigerant and liquid refrigerant in the two-phase refrigerant flow.
  • the inlet manifold is long (such as greater than 800mm)
  • the pressure drop along the length of the distributor tube will be uneven, and the refrigerant will not equally distribute along the length of the distributor tube.
  • Exemplary embodiments of the invention include a heat exchanger including tubes and an inlet manifold to direct a first fluid into the tubes at a third direction. Heat is exchanged between the first fluid and a second fluid in the tubes.
  • the heat exchanger also includes a distributor tube located within the inlet manifold.
  • the distributor tube includes a short tube including a plurality of first orifices that direct the first fluid into the inlet manifold at a first direction, and a long tube including a plurality of second orifices that direct the first fluid into the inlet manifold at a second direction.
  • a refrigerant system including a compressor for compressing a refrigerant, a condenser for cooling the refrigerant, an expansion device for expanding the refrigerant, and a microchannel evaporator for heating the refrigerant.
  • the microchannel evaporator includes tubes, an inlet manifold to direct the refrigerant into the tubes at a third direction, and a distributor tube located within the inlet manifold.
  • the distributor tube includes a short tube including a plurality of first orifices that direct the refrigerant into the inlet manifold at a first direction and a long tube including a plurality of second orifices that direct the refrigerant into the inlet manifold at a second direction.
  • Figure 1 illustrates a refrigeration system 20 including a compressor 22, a condenser 24, an expansion device 26, and an evaporator 28. Both the condenser 24 and the evaporator 28 are heat exchangers and may be microchannel heat exchangers. In the example shown, the evaporator 28 is the microchannel heat exchanger. Refrigerant circulates through the closed circuit refrigeration system 20.
  • a heat pump 35 can be employed to reverse the flow of the refrigerant through the refrigeration system 20.
  • the evaporator 28 functions as a condenser
  • the condenser 24 functions as an evaporator.
  • the refrigerant exits the compressor 22 at a high pressure and a high enthalpy and flows through the condenser 24.
  • the refrigerant rejects heat to air and exits the condenser 24 at a low enthalpy and a high pressure.
  • a fan 30 directs the air through the condenser 24.
  • the cooled refrigerant then passes through the expansion device 26, expanding the refrigerant to a low pressure.
  • the refrigerant flows through the evaporator 28.
  • the refrigerant accepts heat from air, exiting the evaporator 28 at a high enthalpy and a low pressure.
  • a fan 32 blows air through the evaporator 28.
  • the refrigerant then flows to the compressor 22, completing the cycle.
  • FIG. 2 shows the evaporator 28.
  • the evaporator 28 includes an inlet manifold 40 and an outlet manifold 42 that extend along an axis X.
  • the inlet manifold 40 includes a body portion 43 and openings 41 and has a length d.
  • a plurality of flat tubes 44 having a length c extend between the manifolds 40 and 42 along an axis Y.
  • the axis X is substantially perpendicular to the axis Y.
  • Each of the openings 41 of the inlet manifold 40 aligns with one of the flat tubes 44.
  • Refrigerant from the expansion device 26 flows into the inlet manifold 40.
  • the refrigerant from the inlet manifold 40 flows through the openings 41, into the plurality of flat tubes 44 and accepts heat from air 46 flowing over the flat tubes 44.
  • the evaporator 28 can also include a plurality of fins 48 having louvers positioned between the flat tubes 44 to aid in heat transfer between the refrigerant and the air.
  • the refrigerant then flows into the outlet manifold 42 through openings 45 and is directed to the compressor 22 through an outlet opening 70.
  • a distributor tube 34 including a short tube 34a and a long tube 34b is located in the body portion 43 of the inlet manifold 40.
  • a y-shaped flow splitter 52 is attached to the distributor tube 34.
  • the flow splitter 52 includes an inlet portion 56 and two parallel outlet portions 54a and 54b.
  • An inlet tube 50 is in fluid communication with the inlet portion 52, and the short tube 34a and the long tube 34b are in fluid communication with the outlet portions 54a and 54b, respectively.
  • the tubes 34a and 34b are parallel to each other and to the inlet tube 50.
  • the tube 34a includes a first end 62a connected to the outlet portion 54a of the flow splitter 52 and an opposing second end 64a that is blocked by a stop 60a.
  • the tube 34b includes a first end 62b connected to the outlet portion 54b of the flow splitter 52 and an opposing second end 64b that is blocked by a stop 60b.
  • the short tube 34a has a first length a
  • the long tube 34b has a second length b. That is, the first length a is less than the second length b.
  • the first length a of the short tube 34a is approximately 30-70% of the second length b of the long tube 34b, considering the pressure balance within the tubes 34a and 34b.
  • the second length b of the long tube 34b is approximately equal to the length d of the inlet manifold 40.
  • the second length b of the long tube 34b can be slightly less than the length d of the inlet manifold 40, such as approximately 94 to 100% of the length d of the inlet manifold 40.
  • the tubes 34a and 34b each include orifices 58a and 58b, respectively.
  • the orifices 58a and 58b are appropriately sized to cause a pressure drop or a pressure build-up in the distributor tube 34 and to reduce the separation of vapor refrigerant and liquid refrigerant in the two-phase refrigerant flow.
  • the orifices 58a of the short tube 34a are linearly aligned and are located in a section 75 defined between the ends 62a and 64a of the short tube 34a.
  • the orifices 58b of the long tube 34b are linearly aligned and are located in a section 73 defined between the location 71 and the end 64b of the long tube 34b.
  • the orifices 58a and 58b are located in different sections 73 and 75 of the distributor tube 34.
  • the orifices 58a and 58b are aligned such that they extend along a straight line substantially parallel to the lengths a and b of the tubes 34a and 34b, respectively.
  • the orifices 58a direct refrigerant flowing through the short tube 34a into the inlet manifold 40 at a first direction E
  • the orifices 58b direct refrigerant flowing through the long tube 34b into the inlet manifold 40 at a second direction F.
  • the refrigerant directed into the inlet manifold 40 is then directed through the openings 41 and into one of the flat tubes 44 for heat exchange with the air at a third direction G.
  • first direction E and the second direction F are oriented at an angle relative to the third direction G.
  • first direction E and the second direction F can be oriented at an angle that is approximately 45° to 315° clockwise from the third direction G.
  • the orifices 58a and 58b can be located at any number of locations and are located in a way that helps to induce and cause additional mixing when the refrigerant is discharged from the tubes 34a and 34b.
  • the second direction F is approximately 135° clockwise relative to the third direction G
  • the first direction E is approximately 225° clockwise (or 135° counter-clockwise) relative to the third direction G.
  • the refrigerant exiting the expansion device 26 is in two phases and includes approximately 80% vapor and approximately 20% liquid by mass.
  • the density of the liquid refrigerant is approximately 10-100 times greater than the density of the vapor refrigerant. Therefore, the vapor refrigerant flows faster than the liquid refrigerant.
  • Refrigerant from the expansion device 26 enters the distributor tube 34 through the inlet tube 50 and flows into the tubes 34a and 34b.
  • the flow splitter 52 divides the refrigerant entering the inlet manifold 40 such that approximately 50% enters the short tube 34a and approximately 50% enters the long tube 34b.
  • the refrigerant is forced through the orifices 58a and 58b and into the inlet manifold 40.
  • the increase in pressure causes the refrigerant to distribute equally along the length d of the inlet manifold 40.
  • the refrigerant entering the short tube 34a is equally distributed to the section 75 through the orifices 58a, and the refrigerant entering the long tube 34b is equally distributed to the section 73 through the orifices 58b.
  • the refrigerant is equally distributed to each section 73 and 75 as half of the refrigerant is provided to each tube 34a and 34b.
  • An equal distribution of refrigerant is possible as half of the refrigerant is provided to each half of the length d of the inlet manifold 40 for distribution to the flat tubes 44.
  • As a portion of the refrigerant is specifically designated for distribution to a specific section 73 and 75 of the inlet manifold 40, a better distribution of refrigerant is possible in each section 73 and 75 of the inlet manifold 40.
  • the length d of the inlet manifold 40 is very long, such as greater than 800 mm.
  • the length d of the inlet manifold 40 is 800 mm
  • half of the refrigerant would be designated to each 400 mm section of the inlet manifold 40, providing a more even distribution of refrigerant in each 400 mm section, as each 400 mm section is designated to receive half of the refrigerant.

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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)

Claims (15)

  1. Wärmetauscher (28), umfassend:
    mehrere Rohre (44), wobei Wärme zwischen einem ersten Fluid und zweiten Fluid in den mehreren Rohren ausgetauscht wird;
    einen Einlassverteiler (40), um das erste Fluid in einer dritten Richtung in die mehreren Rohre zu leiten; und
    ein Verteilerrohr (34), welches innerhalb des Einlassverteilers (40) angeordnet ist, wobei der Wärmetauscher dadurch gekennzeichnet ist, dass das Verteilerrohr (34) ein kurzes Rohr (34a) umfasst, welches mehrere erste Öffnungen (58a) umfasst, die das erste Fluid in einer ersten Richtung in den Einlassverteiler (40) leiten, und ein langes Rohr (34b), welches mehrere zweite Öffnungen (58b) umfasst, die das erste Fluid in einer zweiten Richtung in den Einlassverteiler leiten.
  2. Wärmetauscher nach Anspruch 1, wobei der Wärmetauscher ein Mikrokanalverdampfer ist.
  3. Wärmetauscher nach Anspruch 1 oder 2, wobei die mehreren Rohre jeweils einen abgeflachten Abschnitt umfassen.
  4. Wärmetauscher nach einem der vorangegangenen Ansprüche, wobei das Verteilerrohr einen Strömungsteiler umfasst, der die Hälfte des ersten Fluids in das kurze Rohr und die andere Hälfte des ersten Fluids in das lange Rohr leitet.
  5. Wärmetauscher nach einem der vorangegangenen Ansprüche, weiterhin umfassend einen Auslassverteiler, wobei die mehreren Rohre den Einlassverteiler und den Auslassverteiler verbinden.
  6. Wärmetauscher nach einem der vorangegangenen Ansprüche, wobei das kurze Rohr und das lange Rohr im Wesentlichen parallel sind.
  7. Wärmetauscher nach einem der vorangegangenen Ansprüche, wobei das erste Fluid in das kurze Rohr und das lange Rohr an einem ersten Ende eintritt, und ein gegenüber liegendes zweites Ende jeweils des kurzen Rohrs und des langen Rohrs mit einer Sperre blockiert ist.
  8. Wärmetauscher nach einem der vorangegangenen Ansprüche, wobei das erste Fluid ein Kältemittel ist und das zweite Fluid Luft ist, und das Kältemittel durch die mehreren Rohre strömt und die Luft über die mehreren Rohre geleitet wird.
  9. Wärmetauscher nach einem der vorangegangenen Ansprüche, wobei die mehreren Öffnungen und die mehreren zweiten Öffnungen in einer linearen Konfiguration angeordnet sind.
  10. Wärmetauscher nach einem der vorangegangenen Ansprüche, wobei ein Winkel zwischen der ersten Richtung und der dritten Richtung im Wesentlichen einem anderen Winkel zwischen der zweiten Richtung und der dritten Richtung entspricht, wobei sich die erste Richtung von der zweiten Richtung unterscheidet, wobei z. B. der Winkel und der andere Winkel jeweils annähernd 45° bis 315° im Uhrzeigersinn von der dritten Richtung sind.
  11. Wärmetauscher nach einem der vorangegangenen Ansprüche, wobei die mehreren ersten Öffnungen in einem Abschnitt des Verteilerrohrs und die mehreren zweiten Öffnungen in einem anderen Abschnitt des Verteilerrohrs angeordnet sind.
  12. Wärmetauscher nach Anspruch 11, wobei das erste Fluid durch den einen Abschnitt und dann durch den anderen Abschnitt strömt, und wobei sich keine von den mehreren zweiten Öffnungen in dem einen Abschnitt des Verteilerrohrs befindet.
  13. Wärmetauscher nach Anspruch 11 oder 12, wobei das kurze Rohr in dem einen Abschnitt des Verteilerrohrs angeordnet ist, und das lange Rohr sowohl in dem einen Abschnitt als auch in dem anderen Abschnitt des Verteilerrohrs angeordnet ist.
  14. Wärmetauscher nach einem der vorangegangenen Ansprüche, wobei der Einlassverteiler eine Verteilerlänge aufweist, das kurze Rohr eine kurze Länge aufweist und das lange Rohr eine lange Länge aufweist, wobei die lange Länge annähernd der Verteilerlänge entspricht und die kurze Länge annähernd 30-70 % der langen Länge entspricht.
  15. Kühlsystem, umfassend:
    einen Kompressor zum Komprimieren eines Kältemittels;
    einen Kondensator zum Kühlen des Kältemittels;
    eine Expansionsvorrichtung zum Ausdehnen des Kältemittels; und
    einen Mikrokanalverdampfer zum Erwärmen des Kältemittels, wobei der Mikrokanalverdampfer ein Wärmetauscher nach Anspruch 2 oder einem der vorangegangenen Ansprüche 3 bis 14 je nach direkter oder indirekter Abhängigkeit von Anspruch 2 ist.
EP08732511.4A 2008-01-17 2008-03-20 Wärmetauscher mit einem verteiler mit mehreren rohren Not-in-force EP2242963B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN2008100084270A CN101487669B (zh) 2008-01-17 2008-01-17 包括多管式分配器的热交换器
PCT/US2008/057567 WO2009091414A1 (en) 2008-01-17 2008-03-20 Heat exchanger including multiple tube distributor

Publications (2)

Publication Number Publication Date
EP2242963A1 EP2242963A1 (de) 2010-10-27
EP2242963B1 true EP2242963B1 (de) 2015-09-30

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Application Number Title Priority Date Filing Date
EP08732511.4A Not-in-force EP2242963B1 (de) 2008-01-17 2008-03-20 Wärmetauscher mit einem verteiler mit mehreren rohren

Country Status (6)

Country Link
US (1) US20110203308A1 (de)
EP (1) EP2242963B1 (de)
CN (1) CN101487669B (de)
DK (1) DK2242963T3 (de)
ES (1) ES2549120T3 (de)
WO (1) WO2009091414A1 (de)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017211529A1 (de) 2017-07-06 2019-01-10 Mahle International Gmbh Einsatzrohr für den Eintrittskanal eines Plattenwärmetauschers
US10883776B2 (en) 2017-07-06 2021-01-05 Mahle International Gmbh Liner tube for the inlet channel of a plate heat exchanger

Also Published As

Publication number Publication date
WO2009091414A1 (en) 2009-07-23
ES2549120T3 (es) 2015-10-23
CN101487669B (zh) 2012-08-22
CN101487669A (zh) 2009-07-22
US20110203308A1 (en) 2011-08-25
DK2242963T3 (en) 2015-10-26
EP2242963A1 (de) 2010-10-27
HK1149955A1 (zh) 2011-10-21

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