WO2016036732A1 - Échangeur de chaleur à microcanaux tolérant au gel pour pompe à chaleur et applications de réfrigération - Google Patents

Échangeur de chaleur à microcanaux tolérant au gel pour pompe à chaleur et applications de réfrigération Download PDF

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Publication number
WO2016036732A1
WO2016036732A1 PCT/US2015/047925 US2015047925W WO2016036732A1 WO 2016036732 A1 WO2016036732 A1 WO 2016036732A1 US 2015047925 W US2015047925 W US 2015047925W WO 2016036732 A1 WO2016036732 A1 WO 2016036732A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
tube
slab
fin density
fins
Prior art date
Application number
PCT/US2015/047925
Other languages
English (en)
Inventor
Michael F. Taras
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
Publication of WO2016036732A1 publication Critical patent/WO2016036732A1/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
    • 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
    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0475—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 bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
    • F28D1/0476—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 bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F28F19/006—Preventing deposits of ice
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/14—Safety or protection arrangements; Arrangements for preventing malfunction for preventing damage by freezing, e.g. for accommodating volume expansion

Definitions

  • This invention relates generally to heat pump and refrigeration applications and, more particularly, to a microchannel heat exchanger configured for use in a heat pump or refrigeration system.
  • HVAC&R Heating, ventilation, air conditioning and refrigeration
  • a microchannel heat exchanger includes two or more containment forms, such as tubes, through which a cooling or heating fluid (i.e. refrigerant or a glycol solution) is circulated.
  • the tubes typically have a flattened cross-section and multiple parallel flow channels.
  • Fins are typically arranged to extend between the tubes to assist in the transfer of thermal energy between the heating/cooling fluid and the surrounding environment.
  • the fins have a corrugated pattern, incorporate louvers to boost heat transfer, and are typically secured to the tubes via brazing.
  • microchannel heat exchangers commonly have substantially identical fins throughout the heat exchanger core.
  • moisture present in the airflow provided to the heat exchanger for cooling may condense and then freeze on the external heat exchanger surfaces.
  • the ice or frost formed may block the flow of air through the heat exchanger, thereby reducing the efficiency and functionality of the heat exchanger and HVAC&R system.
  • Microchannel heat exchangers tend to freeze faster than the round tube and plate fin heat exchangers and therefore require more frequent defrosts, reducing useful heat exchanger utilization time and overall performance. Consequently, it is desirable to construct the microchannel heat exchanger with improved frost tolerance and enhanced performance.
  • a heat exchanger including a fluidly coupled first heat exchanger slab and second heat exchanger slab.
  • the first heat exchanger slab includes at least one first tube segment and the second heat exchanger slab includes at least one second tube segment.
  • the second heat exchanger slab is arranged downstream from the first heat exchanger slab relative to airflow.
  • a plurality of first fins having a first fin density extends from the first heat exchanger slab.
  • a plurality of second fins having a second fin density extends from the second heat exchanger slab. The first fin density is different than the second fin density.
  • the first fin density is lower than the second fin density.
  • the first fin density is between about 6 fins per inch and about 18 fins per inch.
  • the second fin density is between about 12 fins per inch and 23 fins per inch.
  • the second heat exchanger slab is arranged at an angle to the first heat exchanger slab.
  • the second heat exchanger slab is arranged at a 180° angle to the first heat exchanger slab.
  • first heat exchanger slab includes a first tube bank and the second heat exchanger slab includes a second tube bank.
  • first tube segments and the second tube segments are integrally formed.
  • the at least one first tube segment and the at least one second tube segment are microchannel tubes having a plurality of discrete flow channel formed therein.
  • At least one of the first tube segment and second tube segment includes a first heat exchanger tube and a second heat exchanger tube connected by a web extending therebetween.
  • a microchannel heat exchanger including a first manifold, a second manifold separated from the first manifold, and a plurality of tube segments arranged in a spaced parallel relationship and fluidly coupling the first and second manifold.
  • Each of the plurality of tube segments includes a bend defining a first section and a second section of each tube segment. The second section is arranged at an angle to the first section.
  • a plurality of first fins having a first fin density extends from the first section of the tube segments.
  • a plurality of second fins having a second fin density extends from the second section of the tube segments. The first fin density is different than the second fin density.
  • the first fin density is lower than the second fin density.
  • the first fin density is between about 6 fins per inch and about 18 fins per inch.
  • the second fin density is between about 12 fins per inch and 23 fins per inch.
  • the bend is formed about an axis perpendicular to a longitudinal axis of the plurality of tube segments.
  • each tube segment includes a ribbon fold.
  • each of the plurality of tube segments is a microchannel tube having a plurality of discrete flow channels formed therein.
  • each of the plurality of tube segments includes at least a first heat exchanger tube and a second heat exchanger tube connected by a web extending
  • first section and the second section are substantially different in length.
  • FIG. 1 is a schematic diagram of an example of a vapor refrigeration cycle of a refrigeration system
  • FIG. 2 is a side view of a microchannel heat exchanger according to an embodiment of the invention prior to a bending operation
  • FIG. 3 is a cross-sectional view of a tube segment of a microchannel heat exchanger according to an embodiment of the invention.
  • FIG. 4 is a cross-sectional view of a tube segment of a microchannel heat exchanger according to an embodiment of the invention.
  • FIG. 5 is a perspective view of a microchannel heat exchanger according to an embodiment of the invention.
  • FIG. 6 is a perspective view of a microchannel heat exchanger according to another embodiment of the invention.
  • FIG. 7 is a cross-sectional view of a microchannel heat exchanger according to yet an embodiment of the invention.
  • FIG. 8 is a cross-sectional view of a microchannel heat exchanger according to yet an embodiment of the invention.
  • a vapor compression refrigerant cycle 20 of an air conditioning or refrigeration system is schematically illustrated.
  • Exemplary air conditioning or refrigeration systems include, but are not limited to, split, packaged, chiller, rooftop, supermarket, and transport refrigeration systems for example.
  • a refrigerant R is configured to circulate through the vapor compression cycle 20 such that the refrigerant R absorbs heat when evaporated at a low temperature and pressure and releases heat when condensed at a higher temperature and pressure.
  • the refrigerant R flows in a counterclockwise direction as indicated by the arrow.
  • the compressor 22 receives refrigerant vapor from the evaporator 24 and compresses it to a higher temperature and pressure, with the relatively hot vapor then passing to the condenser 26 where it is cooled and condensed to a liquid state by a heat exchange relationship with a cooling medium (not shown) such as air.
  • the liquid refrigerant R then passes from the condenser 26 to an expansion device 28, wherein the refrigerant R is expanded to a low temperature two-phase liquid/vapor state as it passes to the evaporator 24.
  • the low pressure vapor then returns to the compressor 22 where the cycle is repeated. It has to be understood that the refrigeration cycle 20 depicted in FIG.
  • the heat pump refrigerant cycle includes a four- way valve disposed downstream of the compressor with respect to the refrigerant flow that allows reversing the refrigerant flow direction throughout the refrigerant cycle to switch between the cooling and heating mode of operation for the environment to be conditioned.
  • the heat exchanger 30 may be used as either a condenser 24 or an evaporator 28 in the vapor compression system 20.
  • the heat exchanger 30 includes at least a first manifold or header 32, a second manifold or header 34 spaced apart from the first manifold 32, and a plurality of tube segments 36 extending in a spaced, parallel relationship between and connecting the first manifold 32 and the second manifold 34.
  • the first header 32 and the second header 34 are oriented generally horizontally and the heat exchange tube segments 36 extend generally vertically between the two headers 32, 34.
  • other suitable heat exchange tube segments 36 extend generally vertically between the two headers 32, 34.
  • first and second headers 32, 34 are arranged substantially vertically are also within the scope of the invention.
  • the tube segment 36 includes a flattened microchannel heat exchange tube having a leading edge 40, a trailing edge 42, a first surface 44, and a second surface 46.
  • the leading edge 40 of each heat exchanger tube 36 is upstream of its respective trailing edge 42 with respect to an airflow A passing through the heat exchanger 36.
  • the interior flow passage of each heat exchange tube segment 36 may be divided by interior walls into a plurality of discrete flow channels 48 that extend over the length of the tubes 36 from an inlet end to an outlet end and establish fluid communication between the respective first and second manifolds 32, 34.
  • the flow channels 48 may have a circular cross-section, a rectangular cross-section, a trapezoidal cross-section, a triangular cross-section, or another non-circular cross-section.
  • the heat exchange tubes 36 including the discrete flow channels 48 may be formed using known techniques and materials, including, but not limited to, extruded or folded.
  • each of the plurality of tube segments 36 includes at least a first heat exchange tube 50 and a second heat exchange tube 52 connected by a web 54 extending at least partially there between.
  • the configuration of the plurality of second heat exchange tubes 40 such as the width thereof or the number and shape of discrete flow channels for example may be substantially identical to, or
  • the heat exchanger 30 has a multi-pass configuration relative to airflow A.
  • the heat exchanger 30 includes a fluidly coupled first tube bank 60 and second tube bank 62, where each tube bank 60, 62 includes at least one heat exchange tube segment 36.
  • the second tube bank 62 is disposed behind the first tube bank 60 and is downstream with respect to the airflow A passing through the heat exchanger 30.
  • the first and second tube banks 60, 62 may be fluidly coupled by piping, one or more manifolds (as shown), or another fluid joint for example.
  • the first tube bank 60 forms a first slab 70 of the heat exchanger 30 relative to airflow A and the second tube bank 62 forms a second slab 72 of the heat exchanger 30 relative to airflow A.
  • the multi-pass configuration is achieved by forming at least one bend 80 in each tube segment 36 of the heat exchanger 30.
  • the bend 80 is formed about an axis extending substantially perpendicular to the longitudinal axis of the tube segments 36.
  • the bend 80 is a ribbon fold; however other types of bends are within the scope of the invention. .
  • the bend 80 at least partially defines a first section 82 and a second section 84 of each of the plurality of tube segments 36, wherein in the bent configuration, the first section 82 forms a first slab 70 of the heat exchanger 30 relative to airflow A and the second section 84 forms a second slab 72 of the heat exchanger 30 relative to airflow A.
  • the bend 80 is formed at an approximate midpoint of the tube segments 36 between the opposing first and second manifolds 32, 34 such that the first and second sections 82, 84 are generally equal in size.
  • first and second sections 82, 84 are substantially equal in size.
  • other embodiments, such as shown in FIG. 8, where the first section 82 and the second section 84 are substantially different in length are within the scope of the invention.
  • the heat exchanger 30 can be formed such that the first slab 70 is positioned at an obtuse angle with respect to the second slab 72. Alternatively, or in addition, the heat exchanger 30 can also be formed such that the first slab 70 is arranged at either an acute angle or substantially parallel (FIG. 7) to the second slab 72. As a result of the coupling or bend 80 between the first and second slabs 70, 72, the heat exchanger 30 may be formed having a conventional A-coil or V-coil shape. Forming the heat exchanger 30 by bending the tube segments 36 results in a heat exchanger 30 having a reduced bending radius, such as when configured with a 180° bend for example. As a result, the heat exchanger 30 may be adapted to fit within the sizing envelopes defined by existing air conditioning and refrigeration systems.
  • the heat exchanger may have any of a variety of configurations such that refrigerant flows through at least a portion of the first slab 70 before passing through one or more tube segments 36 of the second slab 72.
  • the first slab 70 may function as a first pass relative to the airflow A
  • the second slab 72 may be configured as a second pass relative to the airflow A.
  • other multi-pass configurations such as configurations having multiple passes within each slab 70, 72 are within the scope of the invention.
  • a plurality of first fins 74 extend from the first slab 70 and a plurality of second fins 76 extend from the second section 72 of the heat exchanger.
  • the heat exchanger 30 is formed by bending the plurality of tube segments 36, no fins are arranged within the bend portion 80 of each tube segments 36.
  • the fins 74, 76 may be integrally formed with the tube segments 36 of each slab 70, 72, or alternatively, may be mounted, such as by brazing for example to a surface of the tube segments 36,
  • One or both of the plurality of first fins 74 and second fins 76 may be formed of a fin material tightly folded in a ribbon- like serpentine fashion thereby providing a plurality of closely spaced fins that extend generally orthogonal to the flattened tube segments 36.
  • the plurality of fins 74 mounted to the first slab 70 of the heat exchanger 30 are substantially different from the plurality of fins 76 mounted to the second slab 72 of the heat exchanger 30.
  • the fins 74 mounted to the first slab 70 of the heat exchanger 30 are configured with a lower fin density than the fins 76 mounted to the second slab 72 of the heat exchanger 30 relative to the airflow A.
  • the plurality of fins 74 mounted to the first tube bank 60 or first section 82 configured to form a first pass of the heat exchanger 30 relative to the airflow A has a fin density between about 6 fins per inch about 18 fins per inch, and preferably between 8 and 16 fins per inch.
  • the plurality of fins 76 mounted to the second tube bank 62 or the second section 84 configured to form a second pass of the heat exchanger 30 relative to the airflow A has a fin density between about 12 fins per inch an about 23 fins per inch, and preferably between 16 and 21 fins per inch.
  • Heat exchange between the one or more fluids within the plurality of tube segments 36 and an air flow A occurs through the exterior surfaces 46, 48 of the heat exchange tube segments 36, collectively forming a primary heat exchange surface, and also through the heat exchange surface of the fins 74, 76 which forms a secondary or extended heat exchange surface.
  • the fins 74 having a lower fin density on the first slab 70 of tube segments 36 By positioning the fins 74 having a lower fin density on the first slab 70 of tube segments 36 relative to the airflow A, the heat transfer between airflow A and a fluid flowing through the discrete flow channels thereof is reduced. At the same time, this initial heat transfer between the fluid R and the airflow A causes a significant portion of the moisture within the airflow A to condense and collect on the front slab 70, particularly the fins 74 of the heat exchanger 30. However, because the amount of heat transfer in the front slab 70 is limited, the temperature of the airflow A does not drop appreciably, condensed moisture amount is limited and massive frost formation is delayed. Also, relatively wide spacing between the fins allows for lower performance degradation over time and prolonged intervals between defrosts.
  • the heat transfer within the second slab 72 of the heat exchanger 30 may be increased, specifically by including fins 76 having a higher fin density than the fins 74 of the first slab 70.

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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)

Abstract

L'invention concerne un échangeur de chaleur comprenant une première plaque d'échangeur de chaleur et une seconde plaque d'échangeur de chaleur en communication fluidique l'une avec l'autre. La première plaque d'échangeur de chaleur comprend au moins un premier segment de tube et la seconde plaque d'échangeur de chaleur comprend au moins un second segment de tube. La seconde plaque d'échangeur de chaleur est agencée en aval de la première plaque d'échangeur de chaleur par rapport à la circulation d'air. Une pluralité de premières ailettes s'étend à partir de la première plaque d'échangeur de chaleur avec une première densité des ailettes. Une pluralité de secondes ailettes s'étend à partir de la seconde plaque d'échangeur de chaleur avec une seconde densité des ailettes. La première densité des ailettes est différente de la seconde densité des ailettes.
PCT/US2015/047925 2014-09-05 2015-09-01 Échangeur de chaleur à microcanaux tolérant au gel pour pompe à chaleur et applications de réfrigération WO2016036732A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201462046381P 2014-09-05 2014-09-05
US62/046,381 2014-09-05

Publications (1)

Publication Number Publication Date
WO2016036732A1 true WO2016036732A1 (fr) 2016-03-10

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11236946B2 (en) 2019-05-10 2022-02-01 Carrier Corporation Microchannel heat exchanger

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1231448A2 (fr) * 2001-02-07 2002-08-14 Modine Manufacturing Company Echangeur de chaleur
EP1519133A2 (fr) * 2003-09-29 2005-03-30 Sanden Corporation Dispositif d'échange de chaleur
WO2006083435A2 (fr) * 2005-02-02 2006-08-10 Carrier Corporation Echangeur thermique a tubes plats multicanaux
WO2008039074A1 (fr) * 2006-09-27 2008-04-03 Spot Cooler Systems As Élément de refroidissement
WO2013116178A2 (fr) * 2012-02-02 2013-08-08 Carrier Corporation Ensemble échangeur de chaleur à faisceaux de tubes multiplex et procédé de fabrication
US20130213073A1 (en) * 2012-02-17 2013-08-22 Steve L. Fritz Microchannel heat exchanger

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1231448A2 (fr) * 2001-02-07 2002-08-14 Modine Manufacturing Company Echangeur de chaleur
EP1519133A2 (fr) * 2003-09-29 2005-03-30 Sanden Corporation Dispositif d'échange de chaleur
WO2006083435A2 (fr) * 2005-02-02 2006-08-10 Carrier Corporation Echangeur thermique a tubes plats multicanaux
WO2008039074A1 (fr) * 2006-09-27 2008-04-03 Spot Cooler Systems As Élément de refroidissement
WO2013116178A2 (fr) * 2012-02-02 2013-08-08 Carrier Corporation Ensemble échangeur de chaleur à faisceaux de tubes multiplex et procédé de fabrication
US20130213073A1 (en) * 2012-02-17 2013-08-22 Steve L. Fritz Microchannel heat exchanger

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11236946B2 (en) 2019-05-10 2022-02-01 Carrier Corporation Microchannel heat exchanger

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