US20190162455A1 - Microchannel heat exchanger - Google Patents
Microchannel heat exchanger Download PDFInfo
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- US20190162455A1 US20190162455A1 US15/825,201 US201715825201A US2019162455A1 US 20190162455 A1 US20190162455 A1 US 20190162455A1 US 201715825201 A US201715825201 A US 201715825201A US 2019162455 A1 US2019162455 A1 US 2019162455A1
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- microchannel
- ports
- heat exchanger
- refrigerant
- manifold
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- 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
- F25B39/04—Condensers
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- 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
- F28F9/0202—Header boxes having their inner space divided by partitions
- F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
- F28F9/0209—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/14—Heat exchangers specially adapted for separate outdoor units
- F24F1/18—Heat exchangers specially adapted for separate outdoor units characterised by their shape
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- 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
- F28D1/0233—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 air flow channels
- F28D1/024—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 air flow channels with an air driving element
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- 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
- F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
- F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
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- 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
- F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
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- 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
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- 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
- F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
-
- 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
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
-
- 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
- F28F9/0202—Header boxes having their inner space divided by partitions
- F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
- F28F9/0209—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions
- F28F9/0212—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions the partitions being separate elements attached to header boxes
-
- 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
- F28F9/0243—Header boxes having a circular cross-section
-
- 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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of 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
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2210/00—Heat exchange 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
- 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
- HVAC heating, ventilation, and air conditioning
- HVAC systems can be used to regulate the environment within an enclosed space.
- Various types of HVAC systems such as residential and commercial, may be used to provide cool air, for example during hot times of the year, and/or provide heat, for example, during cooler times of the year.
- Providing heating and/or cooling may be important for user comfort levels. If adequate heating and/or cooling is not provided, a user may be uncomfortable in the enclosed space.
- a condenser cools refrigerant by heat exchange with ambient air drawn or blow across a condenser coil by a fan.
- Microchannel heat exchangers may be used within the condenser to sufficiently cool the refrigerant. Current microchannel heat exchanger designs are limited.
- a microchannel heat exchanger includes at least one manifold and at least one a microchannel tube.
- the microchannel tube includes a plurality of ports, and the microchannel tube extends from the at least one manifold.
- the plurality of ports each have a width and a height.
- the microchannel heat exchanger further includes at least one fin extending from the at least one manifold. The fins are arranged between the at least one microchannel tube and a second microchannel tube.
- the microchannel heat exchanger further includes a refrigerant arranged to flow through the microchannel tube. At least one port of the plurality of ports has a cross-section area less than 0.35 millimeters squared.
- a condenser in some embodiments, includes an enclosure and a microchannel heat exchanger enclosed within the enclosure.
- the microchannel heat exchanger includes at least one manifold and at least one a microchannel tube.
- the microchannel tube includes a plurality of ports, and the microchannel tube extends from the at least one manifold.
- the plurality of ports each have a width and a height.
- the microchannel heat exchanger further includes at least one fin extending from the at least one manifold. The fins are arranged between the at least one microchannel tube and a second microchannel tube.
- the microchannel heat exchanger further includes a refrigerant arranged to flow through the microchannel tube. At least one port of the plurality of ports has a cross-section area less than 0.35 millimeters squared.
- a heating, ventilation, and air conditioning (HVAC) system includes a condenser and a microchannel heat exchanger.
- the microchannel heat exchanger includes at least one manifold and at least one a microchannel tube.
- the microchannel tube includes a plurality of ports, and the microchannel tube extends from the at least one manifold.
- the plurality of ports each have a width and a height.
- the microchannel heat exchanger further includes at least one fin extending from the at least one manifold. The fins are arranged between the at least one microchannel tube and a second microchannel tube.
- the microchannel heat exchanger further includes a refrigerant arranged to flow through the microchannel tube. At least one port of the plurality of ports has a cross-section area less than 0.35 millimeters squared.
- Certain embodiments of the present disclosure may provide one or more technical advantages. For example, increasing the aspect ratio of ports of a microchannel tube increases the tubeside heat transfer coefficient, and provides for better cooling for a refrigerant with low global warming potential (low-GWP refrigerant).
- low-GWP refrigerant low global warming potential
- the decrease in the cross-section area increases the heat transfer rate due to higher refrigerant velocities.
- reducing the cross-section area of the ports results in increased heat transfer rates, which are beneficial for low-GWP refrigerants and may reduce the width of the condenser tubes.
- reducing the port width compared to convention microchannel tubes, and maintaining fixed port height may allow a low-GWP refrigerant flowing through a microchannel tube to transfer as much or more heat than a conventional refrigerant flowing through a conventional microchannel tube (e.g., in FIG. 3A ). Consequently, a condenser with the same or lower size and weight can be used for applications involving the use of low GWP refrigerants.
- reducing both the height and the width of the ports of microchannel tubes reduces the cross-section area of the port, and the refrigerant velocity increases, which increases the tubeside heat transfer coefficient.
- Another advantage of this embodiment is the reduction in airside pressure drop due to the reduced tube height, resulting in reduced fan power consumption. This embodiment may allow for increased condenser heat rejection per unit area.
- microchannel heat exchanger with a low-GWP refrigerant allows a microchannel heat exchanger with a low-GWP refrigerant to maintain the effectiveness of a microchannel heat exchanger with a conventional refrigerant, without increasing the size, weight, cost, or complexity of the microchannel heat exchanger.
- Certain embodiments of the disclosure may include none, some, or all of the above technical advantages.
- One or more other technical advantages may be readily apparent to one skilled in the art from the figures, descriptions, and claims included herein.
- various embodiments may include all, some, or none of the enumerated advantages.
- FIG. 1 is a diagram illustrating an example microchannel heat exchanger, according to some embodiments.
- FIG. 2 is a diagram illustrating an example microchannel heat exchanger, according to some embodiments.
- FIGS. 3A, 3B, and 3C illustrate example microchannel tubes, according to some embodiments.
- FIG. 4 is a diagram illustrating outdoor an HVAC unit comprising a microchannel heat exchanger.
- Microchannel heat exchangers may consist of several tubes, with each tube containing multiple ports that the refrigerant may flow through.
- microchannel heat exchangers have been used with a conventional refrigerant (e.g., hydrofluorocarbons such as R-410A), which have significant global warming potential (GWP) when released into the atmosphere.
- GWP refrigerants e.g., hydrofluorocarbons such as R-410A
- HVAC systems may use microchannel heat exchangers as condensers. Due to the poor condensing heat transfer characteristics of low GWP refrigerants, it may be necessary to increase the surface area of the heat exchangers.
- low-GWP refrigerants may have lower specific heat, lower enthalpy, and/or lower evaporation/condensation heat transfer coefficients.
- current microchannel heat exchangers have a narrow range of port sizes that are not well suited to these new, low-GWP refrigerants. Thus, heat transfer occurs at a reduced rate in these low-GWP refrigerants.
- Increasing the size of the microchannel heat exchanger using a low GWP refrigerant may provide the same system performance as with a conventional refrigerant. However increasing the size further increases cost, expense, and space required to house the microchannel heat exchanger, while further requiring additional fan power consumption, thus reducing the system efficiency.
- there is a need for a microchannel heat exchanger design that increases the tubeside heat transfer coefficient, to compensate for the poor thermal properties associated with low-GWP refrigerant.
- an improved microchannel heat exchanger using refrigerants with poor thermal properties may include an increased number of ports in a microchannel tube, a reduced port hydraulic diameter, a reduced port cross-section area, and an increased aspect ratio of the ports due to reduction in the width.
- This improved microchannel heat exchanger may facilitate increasing the heat transfer coefficient of the microchannel heat exchanger, in some embodiments. This improvement creates a more compact and efficient microchannel heat exchanger for low-GWP refrigerants.
- FIGS. 1 through 4 of the drawings like numerals being used for like and corresponding parts of the various drawings.
- FIG. 1 is a diagram illustrating example microchannel heat exchanger 101 according to some embodiments.
- Microchannel heat exchanger 101 comprises manifolds 140 , a plurality of microchannel tubes 110 , and a plurality of fins 120 .
- Microchannel heat exchanger 101 comprises manifold 140 and 141 .
- Manifolds 140 and 141 may be in communication with the overall air-conditioning system.
- Manifold 140 introduces refrigerant to microchannel heat exchanger 101 through inlet tubing (e.g., flow 191 ) and releases refrigerant from microchannel heat exchanger 101 through outlet tubing (e.g., flow 194 ).
- inlet tubing e.g., flow 191
- outlet tubing e.g., flow 194
- manifolds 140 and 141 are shown of a cylindrical configuration, they may be of a rectangular, half of a cylinder or any other shape, as well as have a single chamber or multi-chamber design, depending on the refrigerant path arrangement.
- Microchannel tubes 110 are generally elongated and substantially flat, and extend from one or more manifolds 140 , providing a path for refrigerant to flow. Each microchannel tube 110 has a first end mounted to manifold 140 and a second end mounted to manifold 141 , and at least one flow channel extending longitudinally, thereby providing a flow path between manifold 140 and manifold 141 . Microchannel tubes 110 generally extend in a horizontal direction between manifolds 140 , providing a plurality of parallel refrigerant flow paths between manifolds 140 . Each microchannel tube 110 may include any number of ports within. In some embodiments, microchannel tubes may be made of aluminum. The heat exchanger refrigerant pass arrangement may be of a multi-pass configuration, such as depicted in FIG. 1 , or of a single-pass configuration, depending on particular application requirements.
- a plurality of fins 120 may be arranged between microchannel tubes 110 , and parallel to each other. Fins 120 extend from microchannel tubes 110 such that the surface area is increased and configured to transfer heat efficiently. Fins 120 may be straight or angled. Fins 140 may have flat, wavy, corrugated or louvered design and typically form triangular, rectangular, offset or trapezoidal airflow passages. In operation, air may below across fins 120 in order to remove heat from refrigerant flowing through microchannel tubes 110 .
- a refrigerant flows through microchannel tubes 110 in various directions.
- Refrigerant may be introduced to microchannel heat exchanger 101 at manifold 140 through flow 191 .
- the refrigerant may split such that a portion flows through one or more microchannel tubes 110 until it reaches manifold 140 at flow 192 .
- fins 120 facilitate a heat transfer such that the refrigerant is cooled.
- the refrigerant continues to flow 193 in manifold 141 where the refrigerant again may split such that a portion flows through one or more microchannel tubes 110 from flow 193 to flow 194 at manifold 140 .
- refrigerant then exits microchannel heat exchanger 101 .
- refrigerant may be cooled to a lower temperature than when it entered microchannel heat exchanger 101 at flow 191 .
- microchannel heat exchanger 101 may include any number of manifolds 140 , microchannel tubes 110 , and fins 120 .
- the components may be integrated or separated.
- the operations may be performed by more, fewer, or other components.
- FIG. 2 is a diagram illustrating example microchannel heat exchanger 201 , according to some embodiments.
- manifolds 240 and 241 operate as manifolds 140 and 141 of FIG. 1 .
- microchannel tubes 210 and fins 220 operate as microchannel tubes 110 and fins 120 of FIG. 1 .
- Ports 230 may be individual channels of microchannel tube 210 , providing a path for refrigerant to flow through microchannel tube 210 from manifold 240 to manifold 241 .
- Microchannel tubes 210 may include any number of ports 230 . As the size of ports 230 varies, the size of microchannel tubes 210 may increase or decrease, thus affecting the number of required microchannel tubes 210 in a microchannel heat exchanger (e.g., microchannel heat exchanger 101 of FIG. 1 ), in order to sufficiently cool the refrigerant.
- a microchannel heat exchanger e.g., microchannel heat exchanger 101 of FIG. 1
- FIGS. 3A, 3B, and 3C illustrate example microchannel tubes 310 a , 310 b , and 310 c , according to some embodiments.
- microchannel tubes 310 a - c may be similar to microchannel tubes 110 and 210 of FIG. 1 and FIG. 2 , respectively.
- refrigerant may flow through microchannel tubes 310 a - c using ports 330 a - c from one manifold to another in order to transfer heat from the refrigerant.
- microchannel tube 310 a represents an embodiment used in a microchannel heat exchanger with conventional refrigerant.
- Port 330 a has height 331 a and width 331 b .
- the aspect ratio of port 330 a is height 331 a divided by width 331 b .
- the aspect ratio of port 330 may range from 0.4-1.8, with width 331 b ranging from 0.50 mm-1.9 mm, height 331 a ranging from 0.50 mm-1.40 mm, and cross-section areas ranging from 0.35 mm 2 -1.4 mm 2 .
- an improved microchannel heat exchanger may alter the microchannel ports to provide a more efficient heat transfer.
- the improved microchannel heat exchanger of this disclosure may reduce the width, height, port cross-section area (i.e. width times height), and/or increased aspect ratio of the ports.
- the width of a port may be reduced.
- the height of the port may be reduced.
- both the width and the height of the ports may be reduced. Reducing the width, height, or both the width and the height of the ports (e.g., compared to a convention microchannel heat exchanger) creates a smaller cross-section area of the port.
- This improved microchannel heat exchanger may facilitate increasing the heat transfer coefficient of the microchannel heat exchanger, in some embodiments. This improvement creates a more compact and efficient microchannel heat exchanger for low-GWP refrigerants.
- Microchannel heat exchangers may be air-cooled and therefore may have a high airside thermal resistance.
- the overall heat transfer coefficient of the microchannel heat exchanger is a function of the airside convection coefficient, which is usually the lowest, the effective conduction heat transfer coefficient, which is typically the highest, and the refrigerant side heat transfer coefficient.
- the heat transfer coefficient for traditional refrigerants is high enough, such that further reduction in the cross-section area of the port would not significantly increase the overall heat transfer coefficient of the traditional microchannel heat exchanger.
- creating a smaller cross-section area would create a pressure drop, such that the compressor requires more power, and the system efficiency decreases.
- the improved microchannel heat exchanger of this disclosure uses a refrigerant with low thermal properties and a low heat transfer coefficient.
- reducing the cross-section area of the port would provide a significant increase in the heat transfer coefficient, thus resulting in a more compact condenser and providing a more efficient system because the airside pressure drop across the coil is lower, which may reduce the fan power required.
- FIGS. 3B and 3C illustrate improved microchannel heat exchangers, according to some embodiments. These embodiments are illustrative rather than limiting in nature, and a wide range of variations, modifications, changes, and substitutions may be contemplated.
- microchannel tube 310 b may be an embodiment of the present disclosure, where the width of ports may be reduced to compensate for the low-GWP refrigerant's poor thermal qualities.
- microchannel tube 310 b includes ports 330 b .
- Port 330 b may have width 332 b ranging from 0.3 mm-0.6 mm and height 331 b ranging from 0.3 mm-0.6 mm.
- Port 330 b may include any combination of width 332 and height 331 b .
- port 330 b has a smaller width 332 b than width 332 a of port 330 a , thus creating a more rectangular shape for port 330 b than port 330 a .
- port 330 b may have width 331 b of 0.3 mm, 0.4 mm, or 0.5 mm.
- height 331 b may remain the same or lesser than the height shown in 331 a (e.g., 0.50 mm-1.4 mm).
- Creating thinner ports 330 b increases the number of ports 330 b that may fit within microchannel tube 310 b .
- reducing width 331 b may increase the aspect ratio of port 330 b .
- the port cross-section areas are lower than 330 a .
- the aspect ratio of port 330 b may be 1.0-1.80 or higher and areas may range between 0.09 mm 2 and 0.25 mm 2 .
- Reducing the cross-section areas of ports 330 b may reduce the hydraulic diameter of port 330 b , which may increase the tubeside heat transfer coefficient, and provide for better heat transfer with a low-GWP refrigerant.
- a low-GWP refrigerant flowing through microchannel tube 310 b may transfer as much heat as a conventional refrigerant flowing through microchannel tube 310 a.
- microchannel tube 310 c may be an embodiment of the present disclosure, where the width and height of ports may be reduced to compensate for the low-GWP refrigerant's poor thermal qualities.
- microchannel tube 310 b includes ports 330 b .
- Port 330 b may have width 332 b ranging from 0.3 mm-0.6 mm and height 331 b ranging from 0.3 mm-0.6 mm.
- Port 330 b may include any combination of width 332 and height 331 b .
- port 330 c has a smaller width 332 c than width 332 a of port 330 a and a smaller height 331 c than height 331 a of port 330 a .
- port 330 c may remain close to a square shape, (e.g., 0.5 mm by 0.5 mm, 0.55 mm by 0.45 mm, 0.29 mm by 0.31 mm), and the aspect ratio of port 330 c may remain approximately 1.0 (e.g., 0.8-1.2).
- the velocity of the refrigerant increases, which increases the heat transfer coefficient, and allows the low-GWP refrigerant to cool more quickly.
- the smaller ports allow a microchannel heat exchanger with a low-GWP refrigerant to maintain the same effectiveness as a microchannel heat exchanger with a conventional refrigerant without increasing the size, weight, cost, or complexity.
- arranging ports 330 b and 330 c as described in this disclosure would have limited impact on the tubeside resistance of a microchannel heat exchanger using conventional refrigerant.
- the change in size of ports 330 b and 330 c from 330 a may only increase the heat transfer coefficient of a conventional refrigerant by a nominal amount. In general, air-cooled condensers have a higher heat transfer resistance on the airside.
- the tubeside resistance is lower, and the air side resistance is dominant, so even if the heat transfer coefficient of the refrigerant is increased slightly, the air cannot absorb enough heat to affect the actual cooling of the conventional refrigerant.
- the tubeside resistance is higher and an increase in the tubeside heat transfer coefficient may greatly impact the actual cooling of the low-GWP refrigerant.
- low-GWP refrigerants may perform cooling as effectively as a conventional refrigerant in the same type and size of microchannel heat exchanger.
- ports 330 c are a smaller size (e.g., compared to ports 330 a ) such that microchannel tube 310 c may also be reduced in height (e.g., compared to the height of microchannel tube 310 a ).
- microchannel heat exchanger e.g., microchannel heat exchanger 101 of FIG. 1
- microchannel heat exchanger may be made with fewer materials, thus conserving resources and expense.
- microchannel heat exchanger e.g., microchannel heat exchanger 101 of FIG. 1
- microchannel heat exchanger e.g., microchannel heat exchanger 101 of FIG. 1
- additional tubes e.g., tubes 110
- FIG. 4 is a diagram illustrating outdoor HVAC unit or condenser 401 comprising a microchannel heat exchanger 101 of FIG. 1 .
- Outdoor unit 401 may encase microchannel heat exchanger 101 in an enclosure such that it is protected from an external environment.
- outdoor unit 401 may further comprise fan 405 .
- Fan 405 may direct a flow of air across microchannel heat exchanger. Fan 405 provides air flow to microchannel heat exchanger 101 to facilitate cooling the refrigerant flowing through microchannel heat exchanger 101 . Any number of fans may be included.
- microchannel heat exchanger 101 may incorporate ports 330 b and/or 330 c from FIG. 3 .
- ports 330 b and/or 330 c By incorporating smaller ports 330 b and/or 330 c than ports 330 a , heat is transferred from the low-GWP refrigerant more efficiently.
- fan 405 may consume less power for a given air flow. With fan 405 consuming less power, outdoor HVAC unit 401 operates more efficiently, and conserves resources.
- microchannel heat exchanger 101 may include any number of microchannel tubes 110 , fins 120 , manifolds 140 and 141 , and so on, as performance demands dictate.
- microchannel heat exchanger 101 and outdoor HVAC unit 401 can include other components that are not illustrated but are typically included with HVAC systems.
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Abstract
Description
- This disclosure relates generally to a heating, ventilation, and air conditioning (HVAC) system. More specifically, this disclosure relates to an improved microchannel heat exchanger.
- HVAC systems can be used to regulate the environment within an enclosed space. Various types of HVAC systems, such as residential and commercial, may be used to provide cool air, for example during hot times of the year, and/or provide heat, for example, during cooler times of the year. Providing heating and/or cooling may be important for user comfort levels. If adequate heating and/or cooling is not provided, a user may be uncomfortable in the enclosed space. In HVAC systems, a condenser cools refrigerant by heat exchange with ambient air drawn or blow across a condenser coil by a fan. Microchannel heat exchangers may be used within the condenser to sufficiently cool the refrigerant. Current microchannel heat exchanger designs are limited.
- In certain embodiments, a microchannel heat exchanger includes at least one manifold and at least one a microchannel tube. The microchannel tube includes a plurality of ports, and the microchannel tube extends from the at least one manifold. The plurality of ports each have a width and a height. The microchannel heat exchanger further includes at least one fin extending from the at least one manifold. The fins are arranged between the at least one microchannel tube and a second microchannel tube. The microchannel heat exchanger further includes a refrigerant arranged to flow through the microchannel tube. At least one port of the plurality of ports has a cross-section area less than 0.35 millimeters squared.
- In some embodiments, a condenser includes an enclosure and a microchannel heat exchanger enclosed within the enclosure. The microchannel heat exchanger includes at least one manifold and at least one a microchannel tube. The microchannel tube includes a plurality of ports, and the microchannel tube extends from the at least one manifold. The plurality of ports each have a width and a height. The microchannel heat exchanger further includes at least one fin extending from the at least one manifold. The fins are arranged between the at least one microchannel tube and a second microchannel tube. The microchannel heat exchanger further includes a refrigerant arranged to flow through the microchannel tube. At least one port of the plurality of ports has a cross-section area less than 0.35 millimeters squared.
- In certain embodiments, a heating, ventilation, and air conditioning (HVAC) system includes a condenser and a microchannel heat exchanger. The microchannel heat exchanger includes at least one manifold and at least one a microchannel tube. The microchannel tube includes a plurality of ports, and the microchannel tube extends from the at least one manifold. The plurality of ports each have a width and a height. The microchannel heat exchanger further includes at least one fin extending from the at least one manifold. The fins are arranged between the at least one microchannel tube and a second microchannel tube. The microchannel heat exchanger further includes a refrigerant arranged to flow through the microchannel tube. At least one port of the plurality of ports has a cross-section area less than 0.35 millimeters squared.
- Certain embodiments of the present disclosure may provide one or more technical advantages. For example, increasing the aspect ratio of ports of a microchannel tube increases the tubeside heat transfer coefficient, and provides for better cooling for a refrigerant with low global warming potential (low-GWP refrigerant).
- In certain embodiments where the aspect ratios is close to one, the decrease in the cross-section area increases the heat transfer rate due to higher refrigerant velocities.
- In some embodiments, reducing the cross-section area of the ports results in increased heat transfer rates, which are beneficial for low-GWP refrigerants and may reduce the width of the condenser tubes.
- As another example, reducing the port width compared to convention microchannel tubes, and maintaining fixed port height (as shown in
FIG. 3B ), may allow a low-GWP refrigerant flowing through a microchannel tube to transfer as much or more heat than a conventional refrigerant flowing through a conventional microchannel tube (e.g., inFIG. 3A ). Consequently, a condenser with the same or lower size and weight can be used for applications involving the use of low GWP refrigerants. - As additional example, reducing both the height and the width of the ports of microchannel tubes (e.g.,
FIG. 3C ) reduces the cross-section area of the port, and the refrigerant velocity increases, which increases the tubeside heat transfer coefficient. Another advantage of this embodiment is the reduction in airside pressure drop due to the reduced tube height, resulting in reduced fan power consumption. This embodiment may allow for increased condenser heat rejection per unit area. - As another example, using smaller ports for microchannel tubes allows a microchannel heat exchanger with a low-GWP refrigerant to maintain the effectiveness of a microchannel heat exchanger with a conventional refrigerant, without increasing the size, weight, cost, or complexity of the microchannel heat exchanger. Certain embodiments of the disclosure may include none, some, or all of the above technical advantages. One or more other technical advantages may be readily apparent to one skilled in the art from the figures, descriptions, and claims included herein. Moreover, while specific advantages have been enumerated above, various embodiments may include all, some, or none of the enumerated advantages.
- For a more complete understanding of the present disclosure, reference is now made to the following description, taken in conjunction with the accompanying drawings, in which:
-
FIG. 1 is a diagram illustrating an example microchannel heat exchanger, according to some embodiments; -
FIG. 2 is a diagram illustrating an example microchannel heat exchanger, according to some embodiments; -
FIGS. 3A, 3B, and 3C illustrate example microchannel tubes, according to some embodiments; and -
FIG. 4 is a diagram illustrating outdoor an HVAC unit comprising a microchannel heat exchanger. - Microchannel heat exchangers may consist of several tubes, with each tube containing multiple ports that the refrigerant may flow through. Traditionally, microchannel heat exchangers have been used with a conventional refrigerant (e.g., hydrofluorocarbons such as R-410A), which have significant global warming potential (GWP) when released into the atmosphere. As companies continue to emphasize global warming mitigation, new refrigerants with low global warming potential (low-GWP refrigerants) are being integrated into existing HVAC systems. HVAC systems may use microchannel heat exchangers as condensers. Due to the poor condensing heat transfer characteristics of low GWP refrigerants, it may be necessary to increase the surface area of the heat exchangers. For example, low-GWP refrigerants may have lower specific heat, lower enthalpy, and/or lower evaporation/condensation heat transfer coefficients. Further, current microchannel heat exchangers have a narrow range of port sizes that are not well suited to these new, low-GWP refrigerants. Thus, heat transfer occurs at a reduced rate in these low-GWP refrigerants. Increasing the size of the microchannel heat exchanger using a low GWP refrigerant, may provide the same system performance as with a conventional refrigerant. However increasing the size further increases cost, expense, and space required to house the microchannel heat exchanger, while further requiring additional fan power consumption, thus reducing the system efficiency. Thus, there is a need for a microchannel heat exchanger design that increases the tubeside heat transfer coefficient, to compensate for the poor thermal properties associated with low-GWP refrigerant.
- This disclosure recognizes that an improved microchannel heat exchanger using refrigerants with poor thermal properties may include an increased number of ports in a microchannel tube, a reduced port hydraulic diameter, a reduced port cross-section area, and an increased aspect ratio of the ports due to reduction in the width. This improved microchannel heat exchanger may facilitate increasing the heat transfer coefficient of the microchannel heat exchanger, in some embodiments. This improvement creates a more compact and efficient microchannel heat exchanger for low-GWP refrigerants.
- Embodiments of the present disclosure and its advantages are best understood by referring to
FIGS. 1 through 4 of the drawings, like numerals being used for like and corresponding parts of the various drawings. -
FIG. 1 is a diagram illustrating examplemicrochannel heat exchanger 101 according to some embodiments.Microchannel heat exchanger 101 comprisesmanifolds 140, a plurality ofmicrochannel tubes 110, and a plurality offins 120. -
Microchannel heat exchanger 101 comprisesmanifold Manifolds Manifold 140 introduces refrigerant tomicrochannel heat exchanger 101 through inlet tubing (e.g., flow 191) and releases refrigerant frommicrochannel heat exchanger 101 through outlet tubing (e.g., flow 194). Althoughmanifolds -
Microchannel tubes 110 are generally elongated and substantially flat, and extend from one ormore manifolds 140, providing a path for refrigerant to flow. Eachmicrochannel tube 110 has a first end mounted tomanifold 140 and a second end mounted tomanifold 141, and at least one flow channel extending longitudinally, thereby providing a flow path betweenmanifold 140 andmanifold 141.Microchannel tubes 110 generally extend in a horizontal direction betweenmanifolds 140, providing a plurality of parallel refrigerant flow paths betweenmanifolds 140. Eachmicrochannel tube 110 may include any number of ports within. In some embodiments, microchannel tubes may be made of aluminum. The heat exchanger refrigerant pass arrangement may be of a multi-pass configuration, such as depicted inFIG. 1 , or of a single-pass configuration, depending on particular application requirements. - A plurality of
fins 120 may be arranged betweenmicrochannel tubes 110, and parallel to each other.Fins 120 extend frommicrochannel tubes 110 such that the surface area is increased and configured to transfer heat efficiently.Fins 120 may be straight or angled.Fins 140 may have flat, wavy, corrugated or louvered design and typically form triangular, rectangular, offset or trapezoidal airflow passages. In operation, air may below acrossfins 120 in order to remove heat from refrigerant flowing throughmicrochannel tubes 110. - In operation, a refrigerant flows through
microchannel tubes 110 in various directions. Refrigerant may be introduced tomicrochannel heat exchanger 101 atmanifold 140 throughflow 191. The refrigerant may split such that a portion flows through one ormore microchannel tubes 110 until it reaches manifold 140 atflow 192. As it flows throughmicrochannel tubes 110,fins 120 facilitate a heat transfer such that the refrigerant is cooled. The refrigerant continues to flow 193 inmanifold 141 where the refrigerant again may split such that a portion flows through one ormore microchannel tubes 110 fromflow 193 to flow 194 atmanifold 140. Atflow 194, refrigerant then exitsmicrochannel heat exchanger 101. After completing its flow throughmicrochannel heat exchanger 101 atflow 194, refrigerant may be cooled to a lower temperature than when it enteredmicrochannel heat exchanger 101 atflow 191. - Modifications, additions, or omissions may be made to the systems described herein without departing from the scope of the disclosure. For example,
microchannel heat exchanger 101 may include any number ofmanifolds 140,microchannel tubes 110, andfins 120. The components may be integrated or separated. Moreover, the operations may be performed by more, fewer, or other components.FIG. 2 is a diagram illustrating example microchannel heat exchanger 201, according to some embodiments. In some embodiments,manifolds manifolds FIG. 1 . In some embodiments,microchannel tubes 210 andfins 220 operate asmicrochannel tubes 110 andfins 120 ofFIG. 1 .Ports 230 may be individual channels ofmicrochannel tube 210, providing a path for refrigerant to flow throughmicrochannel tube 210 frommanifold 240 tomanifold 241.Microchannel tubes 210 may include any number ofports 230. As the size ofports 230 varies, the size ofmicrochannel tubes 210 may increase or decrease, thus affecting the number of requiredmicrochannel tubes 210 in a microchannel heat exchanger (e.g.,microchannel heat exchanger 101 ofFIG. 1 ), in order to sufficiently cool the refrigerant. -
FIGS. 3A, 3B, and 3C illustrateexample microchannel tubes microchannel tubes FIG. 1 andFIG. 2 , respectively. For example, refrigerant may flow through microchannel tubes 310 a-c using ports 330 a-c from one manifold to another in order to transfer heat from the refrigerant. - In
FIG. 3A ,microchannel tube 310 a represents an embodiment used in a microchannel heat exchanger with conventional refrigerant.Port 330 a hasheight 331 a andwidth 331 b. The aspect ratio ofport 330 a isheight 331 a divided bywidth 331 b. For example, the aspect ratio of port 330 may range from 0.4-1.8, withwidth 331 b ranging from 0.50 mm-1.9 mm,height 331 a ranging from 0.50 mm-1.40 mm, and cross-section areas ranging from 0.35 mm2-1.4 mm2. - This disclosure recognizes that an improved microchannel heat exchanger may alter the microchannel ports to provide a more efficient heat transfer. The improved microchannel heat exchanger of this disclosure may reduce the width, height, port cross-section area (i.e. width times height), and/or increased aspect ratio of the ports. In some embodiments, the width of a port may be reduced. In certain embodiments, the height of the port may be reduced. In some embodiments, both the width and the height of the ports may be reduced. Reducing the width, height, or both the width and the height of the ports (e.g., compared to a convention microchannel heat exchanger) creates a smaller cross-section area of the port. This improved microchannel heat exchanger may facilitate increasing the heat transfer coefficient of the microchannel heat exchanger, in some embodiments. This improvement creates a more compact and efficient microchannel heat exchanger for low-GWP refrigerants.
- Reducing the cross-section area of the port in a traditional microchannel heat exchanger would not provide similar benefits when using traditional refrigerants. Microchannel heat exchangers may be air-cooled and therefore may have a high airside thermal resistance. The overall heat transfer coefficient of the microchannel heat exchanger is a function of the airside convection coefficient, which is usually the lowest, the effective conduction heat transfer coefficient, which is typically the highest, and the refrigerant side heat transfer coefficient. Specifically, the heat transfer coefficient for traditional refrigerants is high enough, such that further reduction in the cross-section area of the port would not significantly increase the overall heat transfer coefficient of the traditional microchannel heat exchanger. Further, creating a smaller cross-section area would create a pressure drop, such that the compressor requires more power, and the system efficiency decreases. The improved microchannel heat exchanger of this disclosure uses a refrigerant with low thermal properties and a low heat transfer coefficient. Thus, reducing the cross-section area of the port would provide a significant increase in the heat transfer coefficient, thus resulting in a more compact condenser and providing a more efficient system because the airside pressure drop across the coil is lower, which may reduce the fan power required.
FIGS. 3B and 3C illustrate improved microchannel heat exchangers, according to some embodiments. These embodiments are illustrative rather than limiting in nature, and a wide range of variations, modifications, changes, and substitutions may be contemplated. - In
FIG. 3B ,microchannel tube 310 b may be an embodiment of the present disclosure, where the width of ports may be reduced to compensate for the low-GWP refrigerant's poor thermal qualities. In some embodiments,microchannel tube 310 b includesports 330 b.Port 330 b may have width 332 b ranging from 0.3 mm-0.6 mm andheight 331 b ranging from 0.3 mm-0.6 mm.Port 330 b may include any combination of width 332 andheight 331 b. In some embodiments,port 330 b has a smaller width 332 b than width 332 a ofport 330 a, thus creating a more rectangular shape forport 330 b thanport 330 a. For example,port 330 b may havewidth 331 b of 0.3 mm, 0.4 mm, or 0.5 mm. In this example,height 331 b may remain the same or lesser than the height shown in 331 a (e.g., 0.50 mm-1.4 mm). Creatingthinner ports 330 b increases the number ofports 330 b that may fit withinmicrochannel tube 310 b. Also, reducingwidth 331 b may increase the aspect ratio ofport 330 b. In some embodiments, the port cross-section areas are lower than 330 a. For example, the aspect ratio ofport 330 b may be 1.0-1.80 or higher and areas may range between 0.09 mm2 and 0.25 mm2. Reducing the cross-section areas ofports 330 b may reduce the hydraulic diameter ofport 330 b, which may increase the tubeside heat transfer coefficient, and provide for better heat transfer with a low-GWP refrigerant. Thus, by reducingwidth 331 b, a low-GWP refrigerant flowing throughmicrochannel tube 310 b may transfer as much heat as a conventional refrigerant flowing throughmicrochannel tube 310 a. - In
FIG. 3C ,microchannel tube 310 c may be an embodiment of the present disclosure, where the width and height of ports may be reduced to compensate for the low-GWP refrigerant's poor thermal qualities. In some embodiments,microchannel tube 310 b includesports 330 b.Port 330 b may have width 332 b ranging from 0.3 mm-0.6 mm andheight 331 b ranging from 0.3 mm-0.6 mm.Port 330 b may include any combination of width 332 andheight 331 b. In some embodiments,port 330 c has a smaller width 332 c than width 332 a ofport 330 a and asmaller height 331 c thanheight 331 a ofport 330 a. By reducing bothheight 331 c and width 332 a ofport 330 c, the velocity of the refrigerant increases, which may also increase the heat transfer coefficient, and allow the low-GWP refrigerant to cool more quickly. Also, by reducing bothheight 331 c and width 332 a ofport 330 c,additional ports 330 c may be included inmicrochannel tube 310 c thanmicrochannel tube 310 a. In some embodiments, even when reducing bothheight 331 c and width 332 a,port 330 c may remain close to a square shape, (e.g., 0.5 mm by 0.5 mm, 0.55 mm by 0.45 mm, 0.29 mm by 0.31 mm), and the aspect ratio ofport 330 c may remain approximately 1.0 (e.g., 0.8-1.2). By reducing the cross-section area, the velocity of the refrigerant increases, which increases the heat transfer coefficient, and allows the low-GWP refrigerant to cool more quickly. The smaller ports (e.g.,ports 330 b-c) allow a microchannel heat exchanger with a low-GWP refrigerant to maintain the same effectiveness as a microchannel heat exchanger with a conventional refrigerant without increasing the size, weight, cost, or complexity. In some embodiments, arrangingports ports ports 330 b), or smaller ports with aspect ratios close to 1.0 (e.g.,ports 330 c), low-GWP refrigerants may perform cooling as effectively as a conventional refrigerant in the same type and size of microchannel heat exchanger. - In some embodiments,
ports 330 c are a smaller size (e.g., compared toports 330 a) such thatmicrochannel tube 310 c may also be reduced in height (e.g., compared to the height ofmicrochannel tube 310 a). By reducing the height ofmicrochannel tube 310 c, microchannel heat exchanger (e.g.,microchannel heat exchanger 101 ofFIG. 1 ) may be made with fewer materials, thus conserving resources and expense. By reducing the height ofmicrochannel tube 310 c, microchannel heat exchanger (e.g.,microchannel heat exchanger 101 ofFIG. 1 ), may include fins (e.g.,fins 120 ofFIG. 1 ) with an increased height. Larger fins may increase the surface area on which air is blowing, thus increasing the heat transfer and providing better cooling for the low-GWP refrigerant. Also, by reducing the height ofmicrochannel tube 310 c, microchannel heat exchanger (e.g.,microchannel heat exchanger 101 ofFIG. 1 ) may include additional tubes (e.g., tubes 110) to create additional pathways for the low-GWP refrigerant to flow through, and thus increasing the amount heat transfer. -
FIG. 4 is a diagram illustrating outdoor HVAC unit orcondenser 401 comprising amicrochannel heat exchanger 101 ofFIG. 1 .Outdoor unit 401 may encasemicrochannel heat exchanger 101 in an enclosure such that it is protected from an external environment. In some embodiments,outdoor unit 401 may further comprise fan 405. Fan 405 may direct a flow of air across microchannel heat exchanger. Fan 405 provides air flow tomicrochannel heat exchanger 101 to facilitate cooling the refrigerant flowing throughmicrochannel heat exchanger 101. Any number of fans may be included. - In some embodiments,
microchannel heat exchanger 101 may incorporateports 330 b and/or 330 c fromFIG. 3 . By incorporatingsmaller ports 330 b and/or 330 c thanports 330 a, heat is transferred from the low-GWP refrigerant more efficiently. Thus, fan 405 may consume less power for a given air flow. With fan 405 consuming less power,outdoor HVAC unit 401 operates more efficiently, and conserves resources. - Modifications, additions, or omissions may be made to the systems, apparatuses, and methods described herein without departing from the scope of the disclosure. The components of the systems and apparatuses may be integrated or separated. Moreover, the operations of the systems and apparatuses may be performed by more, fewer, or other components. For example,
microchannel heat exchanger 101 may include any number ofmicrochannel tubes 110,fins 120,manifolds microchannel heat exchanger 101 andoutdoor HVAC unit 401 can include other components that are not illustrated but are typically included with HVAC systems. - Although this disclosure has been described in terms of certain embodiments, alterations and permutations of the embodiments will be apparent to those skilled in the art, and it is intended that the present disclosure encompass such changes, variations, alterations, transformations, and modifications as fall within the scope of the appended claims. Accordingly, the above description of the embodiments does not constrain this disclosure. Other changes, substitutions, and alterations are possible without departing from the spirit and scope of this disclosure.
Claims (20)
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EP18208582.9A EP3492853A1 (en) | 2017-11-29 | 2018-11-27 | Microchannel heat exchanger |
CA3025537A CA3025537A1 (en) | 2017-11-29 | 2018-11-28 | Microchannel heat exchanger |
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US15/825,201 US20190162455A1 (en) | 2017-11-29 | 2017-11-29 | Microchannel heat exchanger |
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CN110595111B (en) * | 2019-06-28 | 2021-11-02 | 杭州三花微通道换热器有限公司 | Heat exchanger and multi-refrigerating-system air conditioning unit |
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CA3025537A1 (en) | 2019-05-29 |
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