EP2242963B1 - Echangeur de chaleur comprenant un distributeur à plusieurs tubes - Google Patents

Echangeur de chaleur comprenant un distributeur à plusieurs tubes 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
Other languages
German (de)
English (en)
Other versions
EP2242963A1 (fr
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
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of EP2242963A1 publication Critical patent/EP2242963A1/fr
Application granted granted Critical
Publication of EP2242963B1 publication Critical patent/EP2242963B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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. Échangeur de chaleur (28), comprenant:
    une pluralité de tubes (44), dans lequel la chaleur est échangée entre un premier fluide et un deuxième fluide dans la pluralité de tubes ;
    un collecteur d'entrée (40) pour diriger le premier fluide dans la pluralité de tubes à une troisième direction ; et
    un tube de distribution (34) situé à l'intérieur du collecteur d'admission (40), l'échangeur de chaleur étant caractérisé en ce que le tube de distribution (34) comprend un tube court (34a) comprenant une pluralité de premiers orifices (58a) qui dirigent le premier fluide dans le collecteur d'admission (40) dans une première direction et un long tube (34b) comprenant une pluralité de deuxièmes orifices (58b) qui dirigent le premier fluide dans le collecteur d'admission dans une deuxième direction.
  2. Échangeur de chaleur selon la revendication 1, dans lequel l'échangeur de chaleur est un évaporateur à microcanaux.
  3. Échangeur de chaleur selon la revendication 1 ou 2, dans lequel la pluralité de tubes comportent chacun une partie aplatie.
  4. Échangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel le tube de distribution comprend un séparateur de flux qui dirige la moitié du premier fluide dans le tube court et l'autre moitié du premier fluide dans le tube long.
  5. Échangeur de chaleur selon l'une quelconque des revendications précédentes, comprenant en outre un collecteur de sortie, dans lequel la pluralité de tubes connecte en termes de fluide le collecteur d'admission et le collecteur de sortie.
  6. Échangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel le tube court et le long tube sont sensiblement parallèles.
  7. Échangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel le premier fluide pénètre dans le tube court et le long tube à une première extrémité, et une deuxième extrémité opposée de chacun du tube court et du tube long sont bloquées par une butée.
  8. Échangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel le premier fluide est le réfrigérant et le deuxième fluide est de l'air, et le réfrigérant circule à travers la pluralité de tubes et l'air passe au-dessus de la pluralité de tubes.
  9. Échangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel la pluralité de premiers orifices et la pluralité de deuxièmes orifices sont agencées en une configuration linéaire.
  10. Échangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel un angle entre la première direction et la troisième direction est sensiblement égal à un autre angle entre la deuxième direction et la troisième direction, dans lequel la première direction est différente de la deuxième direction, par exemple dans lequel l'angle et l'autre angle sont chacun d'environ 45° à 315° dans le sens horaire à partir de la troisième direction.
  11. Échangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel la pluralité de premiers orifices est située dans une section du tube de distribution et la pluralité de deuxièmes orifices est située dans une autre section du tube de distribution.
  12. Échangeur de chaleur selon la revendication 11, dans lequel le premier fluide circule à travers la première section puis à travers l'autre section, et il n'y a aucune de la pluralité de deuxièmes orifices dans la section unique du tube de distribution.
  13. Échangeur de chaleur selon la revendication 11 ou 12, dans lequel le tube court est situé dans la section d'un tube de distribution et le long tube se trouve à la fois dans la section une et l'autre section du tube de distribution.
  14. Échangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel le collecteur d'entrée a une longueur de collecteur, le tube court a une courte longueur et le long tube présente une grande longueur, dans lequel la grande longueur est approximativement égale à la longueur du collecteur, et la courte longueur est d'environ 30 à 70 % de la grande longueur.
  15. Système de réfrigération comprenant:
    un compresseur pour comprimer un réfrigérant ;
    un condenseur pour refroidir le réfrigérant ;
    un dispositif de détente pour détendre le réfrigérant ; et
    un évaporateur à microcanaux pour chauffer le réfrigérant,
    dans lequel l'évaporateur à microcanaux est un échangeur de chaleur selon la revendication 2 ou l'une quelconque des revendications 3 à 14 dépendant directement ou indirectement de la revendication 2.
EP08732511.4A 2008-01-17 2008-03-20 Echangeur de chaleur comprenant un distributeur à plusieurs tubes Not-in-force EP2242963B1 (fr)

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 (fr) 2008-01-17 2008-03-20 Echangeur de chaleur comprenant un distributeur à plusieurs tubes

Publications (2)

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

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Application Number Title Priority Date Filing Date
EP08732511.4A Not-in-force EP2242963B1 (fr) 2008-01-17 2008-03-20 Echangeur de chaleur comprenant un distributeur à plusieurs tubes

Country Status (7)

Country Link
US (1) US20110203308A1 (fr)
EP (1) EP2242963B1 (fr)
CN (1) CN101487669B (fr)
DK (1) DK2242963T3 (fr)
ES (1) ES2549120T3 (fr)
HK (1) HK1149955A1 (fr)
WO (1) WO2009091414A1 (fr)

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

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