US20100012305A1 - Multi-channel heat exchanger with improved condensate drainage - Google Patents
Multi-channel heat exchanger with improved condensate drainage Download PDFInfo
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- US20100012305A1 US20100012305A1 US12/520,929 US52092909A US2010012305A1 US 20100012305 A1 US20100012305 A1 US 20100012305A1 US 52092909 A US52092909 A US 52092909A US 2010012305 A1 US2010012305 A1 US 2010012305A1
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Images
Classifications
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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
- F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- 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
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F17/00—Removing ice or water from heat-exchange apparatus
- F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
Definitions
- This invention relates generally to refrigerant vapor compression system heat exchangers having a plurality of parallel, flat tubes extending between a first header and a second header with fins positioned between these tubes, and more particularly, to providing for improved drainage of condensate collecting on the external surfaces of the flat tubes and fins.
- Refrigerant vapor compression systems are well known in the art. Air conditioners and heat pumps employing refrigerant vapor compression cycles are commonly used for cooling or cooling/heating air supplied to a climate controlled comfort zone within a residence, office building, hospital, school, restaurant or other facility. Refrigerant vapor compression systems are also commonly used for cooling air, or other secondary media such as water or glycol solution, to provide a refrigerated environment for food items and beverage products with display cases, bottle coolers or other similar equipment in supermarkets, convenience stores, groceries, cafeterias, restaurants and other food service establishments.
- Air conditioners and heat pumps employing refrigerant vapor compression cycles are commonly used for cooling or cooling/heating air supplied to a climate controlled comfort zone within a residence, office building, hospital, school, restaurant or other facility.
- Refrigerant vapor compression systems are also commonly used for cooling air, or other secondary media such as water or glycol solution, to provide a refrigerated environment for food items and beverage products with display cases, bottle coolers or other
- these refrigerant vapor compression systems include a compressor, a condenser, an expansion device, and an evaporator serially connected in refrigerant flow communication.
- the aforementioned basic refrigerant vapor compression system components are interconnected by refrigerant lines in a closed refrigerant circuit and arranged in accord with the vapor compression cycle employed.
- the expansion device commonly an expansion valve or a fixed-bore metering device, such as an orifice or a capillary tube, is disposed in the refrigerant line at a location in the refrigerant circuit upstream, with respect to refrigerant flow, of the evaporator and downstream of the condenser.
- the expansion device operates to expand the liquid refrigerant passing through the refrigerant line, connecting the condenser to the evaporator, to a lower pressure and temperature.
- the refrigerant vapor compression system may be charged with any of a variety of refrigerants, including, for example. R-12, R-22, R-134a, R-404A, R-410A, R-407C, R717, R744 or other compressible fluid.
- the evaporator is a parallel tube heat exchanger having a plurality of tubes extending longitudinally in parallel, spaced relationship between a first generally vertically extending header or manifold and a second generally vertically extending header or manifold, one of which serves as an inlet header/manifold.
- the inlet header receives the refrigerant flow from the refrigerant circuit and distributes the refrigerant flow amongst the plurality of parallel flow paths through the heat exchanger.
- the other header serves to collect the refrigerant flow as it leaves the respective flow paths and to direct the collected flow back to the refrigerant line for return to the compressor in a single pass heat exchanger or to a downstream bank of parallel heat exchange tubes in a multi-pass heat exchanger.
- this header is an intermediate manifold or a manifold chamber and serves as an inlet header to the next downstream bank of parallel heat transfer tubes.
- multi-channel tubes are being used in heat exchangers for refrigerant vapor compression systems.
- Each multi-channel tube generally has a plurality of flow channels extending longitudinally in parallel relationship the entire length of the tube, each channel providing a relatively small flow area refrigerant flow path.
- a heat exchanger with multi-channel tubes extending in parallel relationship between the inlet and outlet headers of the heat exchanger will have a relatively large number of small flow area refrigerant flow paths extending between the two headers.
- such multi-channel heat exchanger constructions are called microchannel or minichannel heat exchangers as well.
- fins are positioned between heat transfer tubes for heat transfer enhancement, structural rigidity and heat exchanger design compactness.
- the heat transfer tubes and fins are permanently attached to each other (as well as to the manifolds) during furnace braze operation.
- the fins may have flat, wavy, corrugated or louvered design and typically form triangular, rectangular, offset or trapezoidal airflow passages.
- the condensate depositing on the heat transfer tubes and associated heat transfer fins inherently drains down the vertically extending tubes under the influence of gravity.
- the draining condensate is typically collected in a drain pan disposed beneath the heat exchanger.
- U.S. Pat. No. 5,279,360 discloses an evaporator heat exchanger having an array of parallel heat exchange tubes of flattened cross-section disposed in spaced relationship with V-shaped fins disposed between the facing flat surfaces of adjacent heat exchange tubes.
- Each heat exchange tube is bent into a V-shape and disposed in a vertical plane with its inlet end connected in fluid communication with a first horizontally extending header and its outlet end connected in fluid communication with a second horizontally extending header.
- the apexes of the arrayed V-shape-bent heat exchange tubes are aligned at a lower elevation than the headers, and a condensate trough is disposed therebeneath. Condensate collecting on the flattened heat exchange tubes and the fins therebetween drains downwardly along the respective fin-free edge surfaces of the flattened heat exchange tubes to the condensate trough.
- condensate collecting on the external surfaces of the heat transfer tubes of the evaporator may be undesirability re-entrained in the air passing through the evaporator and transversely over the flattened tubes. Further, under certain conditions, excessive condensate retention promotes faster frost accumulation and undesirably requires more frequent defrost cycles.
- a heat exchanger having generally flattened heat exchange tubes extending longitudinally between a pair of spaced headers is provided wherein condensate collecting on the flat surfaces of the tubes from an airflow passing over the tubes inherently drains from the external flat surfaces of the flattened heat transfer tubes.
- the heat exchanger includes first and second spaced apart and generally vertical longitudinally extending headers, and at least one heat exchange tube having a generally flattened cross-section and defining at least one fluid flow path extending along a longitudinal axis thereof.
- the flattened heat exchange tube extends longitudinally in a horizontal direction between the first and second headers and has an inlet to the fluid flow path opening in fluid communication to the first header and an outlet to the fluid flow path opening in fluid communication to the second header.
- the flattened heat exchange tube has a transverse axis extending from its leading edge to its trailing edge, the leading edge being disposed upstream with respect to airflow of the trailing edge.
- the transverse axis of the flatted heat exchange tube is disposed at an acute angle with the horizontal with the leading edge preferably disposed vertically higher than the trailing edge. In one embodiment, the transverse axis of the flattened heat exchange tube is disposed at an acute angle with the horizontal in the range of from about 5 degrees to about 10 degrees.
- the heat exchanger includes a plurality of flattened heat exchange tubes disposed in parallel, spaced relationship in a generally vertical array. Additionally, the heat exchanger may include a plurality of heat transfer fins extending between adjacent tubes of the parallel tube array. In an embodiment, the plurality of fins extends from a position aft of the leading edges of adjacent tubes of the parallel tube array to a position forward of the trailing edges of adjacent tubes of the tube array.
- the plurality of fins extends from a position aft of the leading edges of adjacent tubes of the parallel tube array to a position aft of the trailing edges of adjacent tubes of the tube array and that portion of each of the fins extending aft of the trailing edges of adjacent tubes of the tube array may include a lip portion extending behind the trailing edge of tube of the parallel array of tubes lying subadjacent the fin.
- the plurality of fins may comprise a plurality of generally vertical plate-like fins extending between adjacent tubes of said parallel tube array.
- corrugated serpentine fins may be disposed between the tubes.
- the fins may have a flat, wavy, offset strip or louvered design and form triangular, rectangular, or trapezoidal airflow passages.
- each flattened heat exchange tube defines a plurality of parallel fluid flow paths extending parallel to a longitudinal axis thereof, with each fluid flow path of the plurality of parallel fluid flow paths having an inlet to the fluid flow path opening in fluid communication to the first header and an outlet to the fluid flow path opening in fluid communication to the second header.
- the plurality of the channels defining the flow paths within each heat transfer tube may be of circular, oval, rectangular, triangular or trapezoidal cross-section.
- each of the fluid flow paths may comprise a refrigerant flow path.
- FIG. 1 is a schematic diagram of a refrigerant vapor compression system incorporating a heat exchanger as an evaporator;
- FIG. 2 is a perspective view of an exemplary embodiment of an evaporator heat exchanger in accordance with the invention
- FIG. 3 is a partially sectioned, elevation view taken along line 3 - 3 of FIG. 2 ;
- FIG. 4 is a partially sectioned, elevation view of another exemplary embodiment of an evaporator heat exchanger in accordance with the invention.
- FIG. 5 is a partially sectioned, elevation view of an alternate exemplary embodiment of an evaporator heat exchanger in accordance with the invention.
- the heat exchanger of the invention will be described herein in use as an evaporator in connection with a simplified air conditioning cycle refrigerant vapor compression system 100 as depicted schematically in FIG. 1 .
- a simplified air conditioning cycle refrigerant vapor compression system 100 as depicted schematically in FIG. 1 .
- the exemplary refrigerant vapor compression cycles illustrated in FIG. 1 is a simplified air conditioning cycle, it is to be understood that the heat exchanger of the invention may be employed in refrigerant vapor compression systems of various designs, including, without limitation, heat pump cycles, economized cycles, cycles with tandem components such as compressors and heat exchangers, chiller cycles, cycles with reheat and many other cycles including various options and features.
- the refrigerant vapor compression system 100 includes a compressor 105 , a condenser 110 , an expansion device 120 , and the heat exchanger 10 , functioning as an evaporator, connected in a closed loop refrigerant circuit by refrigerant lines 102 , 104 and 106 .
- the compressor 105 circulates hot, high pressure refrigerant vapor through discharge refrigerant line 102 into the inlet header of the condenser 110 , and thence through the heat exchanger tubes of the condenser 110 wherein the hot refrigerant vapor is desuperheated, condensed to a liquid and typically subcooled as it passes in heat exchange relationship with a cooling fluid, such as ambient air, which is passed over the heat exchange tubes by the condenser fan 115 .
- a cooling fluid such as ambient air
- the refrigerant predominantly in a vapor thermodynamic state, collects in the outlet header 30 of the evaporator heat exchanger 10 and passes therefrom through suction refrigerant line 106 to return to the compressor 105 through the suction port thereto.
- the air flow traversing the evaporator heat exchanger 10 passes over the heat exchange tubes 40 and heat transfer fins 50 in heat exchange relationship with the refrigerant flowing through the heat exchange tubes 40 , the air is cooled and the moisture in the air flowing through the evaporator heat exchanger 10 and over the external surface of the refrigerant conveying tubes 40 and heat transfer fins 50 of the evaporator heat exchanger 10 condenses out the air and collects of the external surface of the tubes and fins.
- a drain pan 45 is provided beneath the evaporator heat exchanger 10 for collecting condensate that drains from the external surface of the tubes 40 and fins 50 .
- the parallel flow heat exchanger 10 will be described herein in general with reference to the illustrative embodiments of the heat exchanger 10 depicted in FIGS. 2-4 .
- the heat exchanger 10 includes a plurality of heat exchange tubes 40 arranged in a generally vertical array, each of which extends in a horizontal direction along its longitudinal axis between a generally vertically extending first header 20 and a generally vertically extending second header 30 , thereby providing a plurality of refrigerant flow paths between the two headers.
- the refrigerant headers 20 and 30 are shown of a cylindrical configuration, the may be of a rectangular, half of cylinder or any other shape as well as have a single chamber or multi-chamber design, depending on the refrigerant path arrangement.
- Each heat exchange tube 40 has a first end mounted to the first header 20 , a second end mounted to the second header 30 , and a plurality of parallel flow channels 42 extending longitudinally, i.e. along the generally horizontally disposed longitudinal axis of the tube, the entire length of the tube, whereby the each of the individual flow channels 42 provides a flow path in refrigerant flow communication between the first header and the second header.
- the internal refrigerant pass arrangement may be a single-pass configuration or a multi-pass configuration, depending on particular application requirements.
- each multi-channel heat exchange tube 40 has a generally flattened cross-section, for example, a rectangular cross-section or oval cross-section, and defines an interior that may be subdivided to form a side-by-side array of independent flow channels 42 .
- Each flattened multi-channel tube 40 may have a width as measured along a transverse axis extending from the leading edge 44 to the trailing edge 46 of, for example, fifty millimeters or less, typically from ten to thirty millimeters, and a height of about two millimeters or less, as compared to conventional prior art round tubes having a diameter of 1 ⁇ 2 inch, 3 ⁇ 8 inch or 7 mm.
- each multi-channel tube 40 may typically have from about ten to about twenty flow channels 42 .
- each flow channel 42 will have a hydraulic diameter, defined as four times the cross-sectional flow area divided by the “wetted” perimeter, in the range generally from about 200 microns to about 3 millimeters.
- the channels 42 may have a rectangular, triangular, oval or trapezoidal cross-section, or any other desired non-circular cross-section.
- heat transfer tubes 40 may have other internal heat transfer enhancement elements, such as mixers and boundary layer destructors.
- the heat exchanger 10 includes a plurality of external heat transfer fins 50 extending between each set of the parallel-arrayed tubes 40 .
- the fins are brazed or otherwise securely attached to the external surfaces of the adjoining tubes 40 to establish heat transfer contact, by heat conduction, between the fins 50 and the external surface of the flat heat transfer tubes 40 .
- the external surfaces of the heat transfer tubes 40 and the surfaces of the fins 50 together form the external heat transfer surface that participates in heat transfer interaction with the air flowing through the heat exchanger 10 .
- the external heat transfer fins 50 also provide for structural rigidity of the heat exchanger 10 and quite often assist in air flow redirection to improve heat transfer characteristics.
- the fins 50 constitute a plurality of plates disposed in parallel, spaced relationship and extending generally vertically between the heat transfer tubes 40 .
- other fin configurations such as, for example, generally corrugated serpentine wavy, offset or louvered fins forming triangular, rectangular, or trapezoidal airflow passages may be used instead of generally vertical fins in the evaporator heat exchanger of the invention.
- the tubes 40 are aligned with their transverse axes at an slight angle with respect to the horizontal so that the trailing edge 46 of each tube 40 is positioned lower than the leading edge 44 of each tube 40 .
- the leading edge 44 is the edge of the heat exchange tube 40 disposed at the air flow inlet side of the heat exchanger 10 and the trailing edge 46 is the edge of the heat exchange tube 40 disposed at the air flow outlet side of the heat exchanger 10 .
- both gravity and the airflow passing over the external surface of the heat exchange tubes 40 serve to facilitate drainage of condensate deposited on the external surfaces of the tubes 40 .
- the transverse axis of the flattened heat exchange tubes 40 is disposed at an acute angle with the horizontal in the range of from about 5 degrees to about 10 degrees, facilitating condensate drainage, while not compromising the airflow pattern.
- the trailing edges 56 of the fins 50 extend beyond the trailing edges 46 of the respective heat exchange tubes 40 .
- the condensate may simply drain off the trailing edge 46 of each heat exchange tube 40 to drip into the drain pan 45 , or the condensate may flow along the lower surface of the portion of the trailing edge 56 extending beyond the trailing edges 46 of the heat exchange tubes 40 to drip into the drain pan 45 .
- FIG. 1 depicted in FIG.
- the trailing edge 56 of each of the fins 50 includes a lower extension 58 that extends downwardly aft of the trailing edge 46 of the heat exchange tube 40 subadjacent that fin to the fin 50 positioned next below.
- the lower extension 58 further facilitates drainage of condensate by providing a downwardly extending surface along which the condensate will flow to the fin next below and eventually drain from the extension 58 of the lower most fin 50 into the condensate drain pan 45 .
- a lip 59 may be provided extending outwardly from the lower extension 58 and beneath the trailing edge 46 of the subadjacent tube 40 to provide a surface for directing condensate draining off the trailing edge 46 of that tube 40 .
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Abstract
A heat exchanger includes a first generally vertical header and a second generally vertical header and a generally vertical array of a plurality of generally flat heat exchange tubes extending in a horizontal direction therebetween. Each heat exchange tube has a plurality of channels extending longitudinally in parallel relationship from its inlet end to its outlet end, each channel defining a discrete refrigerant flow path. A plurality of fins extends between parallel-arrayed tubes. To facilitate drainage of the collected condensate from the external surfaces of the flat heat exchange tubes, the tubes are aligned at a slight angle with respect to the horizontal so that the trailing edge of each tube is positioned lower than the leading edge of each tube. To further assist in the condensate drainage, the trailing edge of each of the fins may extend beyond the trailing edge of the associated heat transfer tubes and a lower extension lip may extend downwardly from the trailing edge of each of the fins.
Description
- This invention relates generally to refrigerant vapor compression system heat exchangers having a plurality of parallel, flat tubes extending between a first header and a second header with fins positioned between these tubes, and more particularly, to providing for improved drainage of condensate collecting on the external surfaces of the flat tubes and fins.
- Refrigerant vapor compression systems are well known in the art. Air conditioners and heat pumps employing refrigerant vapor compression cycles are commonly used for cooling or cooling/heating air supplied to a climate controlled comfort zone within a residence, office building, hospital, school, restaurant or other facility. Refrigerant vapor compression systems are also commonly used for cooling air, or other secondary media such as water or glycol solution, to provide a refrigerated environment for food items and beverage products with display cases, bottle coolers or other similar equipment in supermarkets, convenience stores, groceries, cafeterias, restaurants and other food service establishments.
- Conventionally, these refrigerant vapor compression systems include a compressor, a condenser, an expansion device, and an evaporator serially connected in refrigerant flow communication. The aforementioned basic refrigerant vapor compression system components are interconnected by refrigerant lines in a closed refrigerant circuit and arranged in accord with the vapor compression cycle employed. The expansion device, commonly an expansion valve or a fixed-bore metering device, such as an orifice or a capillary tube, is disposed in the refrigerant line at a location in the refrigerant circuit upstream, with respect to refrigerant flow, of the evaporator and downstream of the condenser. The expansion device operates to expand the liquid refrigerant passing through the refrigerant line, connecting the condenser to the evaporator, to a lower pressure and temperature. The refrigerant vapor compression system may be charged with any of a variety of refrigerants, including, for example. R-12, R-22, R-134a, R-404A, R-410A, R-407C, R717, R744 or other compressible fluid.
- In some refrigerant vapor compression systems, the evaporator is a parallel tube heat exchanger having a plurality of tubes extending longitudinally in parallel, spaced relationship between a first generally vertically extending header or manifold and a second generally vertically extending header or manifold, one of which serves as an inlet header/manifold. The inlet header receives the refrigerant flow from the refrigerant circuit and distributes the refrigerant flow amongst the plurality of parallel flow paths through the heat exchanger. The other header serves to collect the refrigerant flow as it leaves the respective flow paths and to direct the collected flow back to the refrigerant line for return to the compressor in a single pass heat exchanger or to a downstream bank of parallel heat exchange tubes in a multi-pass heat exchanger. In the latter case, this header is an intermediate manifold or a manifold chamber and serves as an inlet header to the next downstream bank of parallel heat transfer tubes.
- Historically, such parallel tube heat exchangers used in refrigerant vapor compression systems have used round tubes, typically having a diameter of ½ inch, ⅜ inch or 7 millimeters. More recently, flat, typically rectangular or oval in cross-section, multi-channel tubes are being used in heat exchangers for refrigerant vapor compression systems. Each multi-channel tube generally has a plurality of flow channels extending longitudinally in parallel relationship the entire length of the tube, each channel providing a relatively small flow area refrigerant flow path. Thus, a heat exchanger with multi-channel tubes extending in parallel relationship between the inlet and outlet headers of the heat exchanger will have a relatively large number of small flow area refrigerant flow paths extending between the two headers. Sometimes, such multi-channel heat exchanger constructions are called microchannel or minichannel heat exchangers as well.
- Commonly, fins are positioned between heat transfer tubes for heat transfer enhancement, structural rigidity and heat exchanger design compactness. The heat transfer tubes and fins are permanently attached to each other (as well as to the manifolds) during furnace braze operation. The fins may have flat, wavy, corrugated or louvered design and typically form triangular, rectangular, offset or trapezoidal airflow passages.
- When a heat exchanger is used as an evaporator in a refrigerant vapor compression system, moisture in the air flowing through the evaporator and over the external surface of the refrigerant conveying tubes and associated fins of the heat exchanger condenses out the air and collects on the external surface of the those tubes and fins. In general, condensate naturally drains well from refrigerant vapor compression system evaporators having round heat transfer tubes and plate fins due to the cylindrical outer surface of a round tube and vertically extended plate fins. For evaporator heat exchangers having the flat tubes and serpentine fins arranged in a vertical orientation extending between a pair of horizontally disposed headers, such as, for example, the heat pump evaporator/condenser heat exchanger disclosed in U.S. Pat. No. 5,826,649, the condensate depositing on the heat transfer tubes and associated heat transfer fins inherently drains down the vertically extending tubes under the influence of gravity. The draining condensate is typically collected in a drain pan disposed beneath the heat exchanger.
- U.S. Pat. No. 5,279,360 discloses an evaporator heat exchanger having an array of parallel heat exchange tubes of flattened cross-section disposed in spaced relationship with V-shaped fins disposed between the facing flat surfaces of adjacent heat exchange tubes. Each heat exchange tube is bent into a V-shape and disposed in a vertical plane with its inlet end connected in fluid communication with a first horizontally extending header and its outlet end connected in fluid communication with a second horizontally extending header. The apexes of the arrayed V-shape-bent heat exchange tubes are aligned at a lower elevation than the headers, and a condensate trough is disposed therebeneath. Condensate collecting on the flattened heat exchange tubes and the fins therebetween drains downwardly along the respective fin-free edge surfaces of the flattened heat exchange tubes to the condensate trough.
- However, with respect to prior art heat exchangers having tubes of flattened cross-section disposed horizontally and extending longitudinally in a horizontal direction between a pair of spaced, generally vertical headers, condensate collecting on the upper side of the tubes does not drain therefrom because of the horizontal disposition of the flat external surface of the tube. If the condensate collecting on the external surfaces of the heat exchanger tubes becomes excessive, overall performance of the refrigerant vapor compression system will be adversely impacted. For example, excessive condensate retention of the external surfaces of the heat exchange tubes can result in increased air side pressure drop through the evaporator which causes increased fan power consumption and reduced heat transfer through the heat transfer tubes. Also, condensate collecting on the external surfaces of the heat transfer tubes of the evaporator may be undesirability re-entrained in the air passing through the evaporator and transversely over the flattened tubes. Further, under certain conditions, excessive condensate retention promotes faster frost accumulation and undesirably requires more frequent defrost cycles.
- A heat exchanger having generally flattened heat exchange tubes extending longitudinally between a pair of spaced headers is provided wherein condensate collecting on the flat surfaces of the tubes from an airflow passing over the tubes inherently drains from the external flat surfaces of the flattened heat transfer tubes.
- The heat exchanger includes first and second spaced apart and generally vertical longitudinally extending headers, and at least one heat exchange tube having a generally flattened cross-section and defining at least one fluid flow path extending along a longitudinal axis thereof. The flattened heat exchange tube extends longitudinally in a horizontal direction between the first and second headers and has an inlet to the fluid flow path opening in fluid communication to the first header and an outlet to the fluid flow path opening in fluid communication to the second header. The flattened heat exchange tube has a transverse axis extending from its leading edge to its trailing edge, the leading edge being disposed upstream with respect to airflow of the trailing edge. The transverse axis of the flatted heat exchange tube is disposed at an acute angle with the horizontal with the leading edge preferably disposed vertically higher than the trailing edge. In one embodiment, the transverse axis of the flattened heat exchange tube is disposed at an acute angle with the horizontal in the range of from about 5 degrees to about 10 degrees.
- In an embodiment, the heat exchanger includes a plurality of flattened heat exchange tubes disposed in parallel, spaced relationship in a generally vertical array. Additionally, the heat exchanger may include a plurality of heat transfer fins extending between adjacent tubes of the parallel tube array. In an embodiment, the plurality of fins extends from a position aft of the leading edges of adjacent tubes of the parallel tube array to a position forward of the trailing edges of adjacent tubes of the tube array. In an embodiment, the plurality of fins extends from a position aft of the leading edges of adjacent tubes of the parallel tube array to a position aft of the trailing edges of adjacent tubes of the tube array and that portion of each of the fins extending aft of the trailing edges of adjacent tubes of the tube array may include a lip portion extending behind the trailing edge of tube of the parallel array of tubes lying subadjacent the fin. In an embodiment, the plurality of fins may comprise a plurality of generally vertical plate-like fins extending between adjacent tubes of said parallel tube array. Alternatively, corrugated serpentine fins may be disposed between the tubes. The fins may have a flat, wavy, offset strip or louvered design and form triangular, rectangular, or trapezoidal airflow passages.
- In an embodiment of the heat exchanger, each flattened heat exchange tube defines a plurality of parallel fluid flow paths extending parallel to a longitudinal axis thereof, with each fluid flow path of the plurality of parallel fluid flow paths having an inlet to the fluid flow path opening in fluid communication to the first header and an outlet to the fluid flow path opening in fluid communication to the second header. The plurality of the channels defining the flow paths within each heat transfer tube may be of circular, oval, rectangular, triangular or trapezoidal cross-section. In an embodiment, each of the fluid flow paths may comprise a refrigerant flow path.
- In the following detailed description of the invention, reference will be made to and is to be read in connection with the accompanying drawing, where:
-
FIG. 1 is a schematic diagram of a refrigerant vapor compression system incorporating a heat exchanger as an evaporator; -
FIG. 2 is a perspective view of an exemplary embodiment of an evaporator heat exchanger in accordance with the invention; -
FIG. 3 is a partially sectioned, elevation view taken along line 3-3 ofFIG. 2 ; -
FIG. 4 is a partially sectioned, elevation view of another exemplary embodiment of an evaporator heat exchanger in accordance with the invention; and -
FIG. 5 is a partially sectioned, elevation view of an alternate exemplary embodiment of an evaporator heat exchanger in accordance with the invention. - The heat exchanger of the invention will be described herein in use as an evaporator in connection with a simplified air conditioning cycle refrigerant
vapor compression system 100 as depicted schematically inFIG. 1 . Although the exemplary refrigerant vapor compression cycles illustrated inFIG. 1 is a simplified air conditioning cycle, it is to be understood that the heat exchanger of the invention may be employed in refrigerant vapor compression systems of various designs, including, without limitation, heat pump cycles, economized cycles, cycles with tandem components such as compressors and heat exchangers, chiller cycles, cycles with reheat and many other cycles including various options and features. - The refrigerant
vapor compression system 100 includes acompressor 105, acondenser 110, an expansion device 120, and theheat exchanger 10, functioning as an evaporator, connected in a closed loop refrigerant circuit byrefrigerant lines compressor 105 circulates hot, high pressure refrigerant vapor through discharge refrigerant line 102 into the inlet header of thecondenser 110, and thence through the heat exchanger tubes of thecondenser 110 wherein the hot refrigerant vapor is desuperheated, condensed to a liquid and typically subcooled as it passes in heat exchange relationship with a cooling fluid, such as ambient air, which is passed over the heat exchange tubes by thecondenser fan 115. - The high pressure, liquid refrigerant leaves the
condenser 110 and thence passes through liquidrefrigerant line 104 to theevaporator heat exchanger 10, traversing the expansion device 120 wherein the refrigerant is expanded to a lower pressure and temperature to form a refrigerant liquid/vapor mixture. The now lower pressure and lower temperature, expanded refrigerant thence passes through theheat exchanger tubes 40 of theevaporator heat exchanger 10 wherein the refrigerant is evaporated and typically superheated as it passes in heat exchange relationship with air to be cooled (and, in many cases, dehumidified), which is passed over theheat exchange tubes 40 and associatedheat transfer fins 50 by the evaporator fan 15. The refrigerant, predominantly in a vapor thermodynamic state, collects in theoutlet header 30 of theevaporator heat exchanger 10 and passes therefrom through suctionrefrigerant line 106 to return to thecompressor 105 through the suction port thereto. As the air flow traversing theevaporator heat exchanger 10 passes over theheat exchange tubes 40 andheat transfer fins 50 in heat exchange relationship with the refrigerant flowing through theheat exchange tubes 40, the air is cooled and the moisture in the air flowing through theevaporator heat exchanger 10 and over the external surface of therefrigerant conveying tubes 40 andheat transfer fins 50 of theevaporator heat exchanger 10 condenses out the air and collects of the external surface of the tubes and fins. Adrain pan 45 is provided beneath theevaporator heat exchanger 10 for collecting condensate that drains from the external surface of thetubes 40 andfins 50. - The parallel
flow heat exchanger 10 will be described herein in general with reference to the illustrative embodiments of theheat exchanger 10 depicted inFIGS. 2-4 . Theheat exchanger 10 includes a plurality ofheat exchange tubes 40 arranged in a generally vertical array, each of which extends in a horizontal direction along its longitudinal axis between a generally vertically extendingfirst header 20 and a generally vertically extendingsecond header 30, thereby providing a plurality of refrigerant flow paths between the two headers. Although therefrigerant headers heat exchange tube 40 has a first end mounted to thefirst header 20, a second end mounted to thesecond header 30, and a plurality ofparallel flow channels 42 extending longitudinally, i.e. along the generally horizontally disposed longitudinal axis of the tube, the entire length of the tube, whereby the each of theindividual flow channels 42 provides a flow path in refrigerant flow communication between the first header and the second header. The internal refrigerant pass arrangement may be a single-pass configuration or a multi-pass configuration, depending on particular application requirements. - Additionally, each multi-channel
heat exchange tube 40 has a generally flattened cross-section, for example, a rectangular cross-section or oval cross-section, and defines an interior that may be subdivided to form a side-by-side array ofindependent flow channels 42. Each flattenedmulti-channel tube 40 may have a width as measured along a transverse axis extending from the leadingedge 44 to the trailingedge 46 of, for example, fifty millimeters or less, typically from ten to thirty millimeters, and a height of about two millimeters or less, as compared to conventional prior art round tubes having a diameter of ½ inch, ⅜ inch or 7 mm. Thetubes 40 are shown in the accompanying drawings, for ease and clarity of illustration, as having tenchannels 42 defining flow paths having a circular cross-section. However, it is to be understood that in applications, eachmulti-channel tube 40 may typically have from about ten to about twentyflow channels 42. Generally, eachflow channel 42 will have a hydraulic diameter, defined as four times the cross-sectional flow area divided by the “wetted” perimeter, in the range generally from about 200 microns to about 3 millimeters. Although depicted as having a circular cross-section in the drawings, thechannels 42 may have a rectangular, triangular, oval or trapezoidal cross-section, or any other desired non-circular cross-section. Also,heat transfer tubes 40 may have other internal heat transfer enhancement elements, such as mixers and boundary layer destructors. - As in conventional practice, to improve heat transfer between the air flowing through the
heat exchanger 10 over the external surface of theheat transfer tubes 40 and the refrigerant flowing through theparallel flow channels 42 of theheat transfer tubes 40, theheat exchanger 10 includes a plurality of externalheat transfer fins 50 extending between each set of the parallel-arrayedtubes 40. The fins are brazed or otherwise securely attached to the external surfaces of the adjoiningtubes 40 to establish heat transfer contact, by heat conduction, between thefins 50 and the external surface of the flatheat transfer tubes 40. Thus, the external surfaces of theheat transfer tubes 40 and the surfaces of thefins 50 together form the external heat transfer surface that participates in heat transfer interaction with the air flowing through theheat exchanger 10. The externalheat transfer fins 50 also provide for structural rigidity of theheat exchanger 10 and quite often assist in air flow redirection to improve heat transfer characteristics. In the exemplary embodiment of theheat exchanger 10 depicted inFIG. 2 , thefins 50 constitute a plurality of plates disposed in parallel, spaced relationship and extending generally vertically between theheat transfer tubes 40. However, it is to be understood that other fin configurations, such as, for example, generally corrugated serpentine wavy, offset or louvered fins forming triangular, rectangular, or trapezoidal airflow passages may be used instead of generally vertical fins in the evaporator heat exchanger of the invention. - To facilitate drainage of the collected condensate from the external surfaces of the flat
heat exchange tubes 40, thetubes 40 are aligned with their transverse axes at an slight angle with respect to the horizontal so that the trailingedge 46 of eachtube 40 is positioned lower than the leadingedge 44 of eachtube 40. The leadingedge 44 is the edge of theheat exchange tube 40 disposed at the air flow inlet side of theheat exchanger 10 and the trailingedge 46 is the edge of theheat exchange tube 40 disposed at the air flow outlet side of theheat exchanger 10. Under the influence of gravity and assisted by the airflow sheer force, with the trailingedge 46 of eachtube 40 in the generally vertical array of horizontally extendingtubes 40 of theheat exchanger 10 being positioned lower than the leadingedge 44, condensate collecting of the external generally flat surfaces of thetubes 40 will flow transversely along the width of eachtube 40 in the direction of the air flow across the generally flat surfaces of the tubes to pass off therespective trailing edges 46 oftubes 40 and drain into thedrain pan 45. Condensate depositing on the surface of each of thefins 50 will drain downwardly unto the upper external surface of thetube 40 subjacent the lower end of the fin and likewise flow to the trailing edge of the tube and drain therefrom into thedrain pan 45. Thus, with respect to theevaporator heat exchanger 10, both gravity and the airflow passing over the external surface of theheat exchange tubes 40 serve to facilitate drainage of condensate deposited on the external surfaces of thetubes 40. In an embodiment, the transverse axis of the flattenedheat exchange tubes 40 is disposed at an acute angle with the horizontal in the range of from about 5 degrees to about 10 degrees, facilitating condensate drainage, while not compromising the airflow pattern. - In the exemplary embodiments of the
evaporator heat exchanger 10 depicted inFIGS. 4 and 5 , the trailingedges 56 of thefins 50 extend beyond the trailingedges 46 of the respectiveheat exchange tubes 40. In these embodiments, the condensate may simply drain off the trailingedge 46 of eachheat exchange tube 40 to drip into thedrain pan 45, or the condensate may flow along the lower surface of the portion of the trailingedge 56 extending beyond the trailingedges 46 of theheat exchange tubes 40 to drip into thedrain pan 45. In the exemplary embodiment depicted inFIG. 5 , the trailingedge 56 of each of thefins 50 includes alower extension 58 that extends downwardly aft of the trailingedge 46 of theheat exchange tube 40 subadjacent that fin to thefin 50 positioned next below. In this embodiment, thelower extension 58 further facilitates drainage of condensate by providing a downwardly extending surface along which the condensate will flow to the fin next below and eventually drain from theextension 58 of the lowermost fin 50 into thecondensate drain pan 45. Additionally, alip 59 may be provided extending outwardly from thelower extension 58 and beneath the trailingedge 46 of thesubadjacent tube 40 to provide a surface for directing condensate draining off the trailingedge 46 of thattube 40. - While the present invention has been particularly shown and described with reference to the preferred mode as illustrated in the drawing, it will be understood by one skilled in the art that various changes in detail may be effected therein without departing from the spirit and scope of the invention as defined by the claims.
Claims (28)
1. A heat exchanger for cooling a flow of air passed therethrough comprising:
first and second spaced apart and generally vertical longitudinally extending headers; and
at least one heat exchange tube having a flattened cross-section and defining at least one fluid flow path extending along a longitudinal axis thereof, said at least one heat flattened exchange tube extending longitudinally in a horizontal direction between said first and second headers and having an inlet to said fluid flow path opening in fluid communication to said first header and an outlet to said fluid flow path opening in fluid communication to the second header, said at least one flattened heat exchange tube having a transverse axis extending from a leading edge of said at least one flattened heat exchange tube to a trailing edge of said at least one flattened heat exchange tube, said leading edge disposed upstream with respect to air flow of said trailing edge, the transverse axis of said at least one flatted heat exchange tube disposed at an acute angle with the horizontal with said leading edge disposed vertically higher than said trailing edge.
2. A heat exchanger as recited in claim 1 wherein said at least one flattened heat exchange tube comprises a plurality of flattened heat exchange tubes disposed in parallel, spaced relationship in a generally vertical array.
3. A heat exchanger as recited in claim 2 further comprising a plurality of fins extending between adjacent tubes of said parallel tube array.
4. A heat exchanger as recited in claim 3 wherein said plurality of fins extends from a position aft of the leading edges of adjacent tubes of said parallel tube array to a position forward of the trailing edges of adjacent tubes of said tube array.
5. A heat exchanger as recited in claim 3 wherein said plurality of fins extends from a position aft of the leading edges of adjacent tubes of said parallel tube array to a position aft of the trailing edges of adjacent tubes of said tube array.
6. A heat exchanger as recited in claim 5 wherein the portion of each of said plurality of fins extending aft of the trailing edges of adjacent tubes of said tube array includes a lip portion extending behind the trailing edge of tube of said parallel array of tubes lying subadjacent said fin.
7. A heat exchanger as recited in claim 3 wherein said plurality of fins comprises a plurality of generally vertical plate-like fins extending between adjacent tubes of said parallel tube array.
8. A heat exchanger as recited in claim 3 wherein said plurality of fins comprises serpentine-like corrugated fins extending between adjacent tubes of said parallel tube array.
9. A heat exchanger as recited in claim 8 wherein said a serpentine-like corrugated fins extending between adjacent tubes of said parallel tube array are forming one of generally triangular, rectangular or trapezoidal airflow passages.
10. A heat exchanger as recited in claim 3 wherein said plurality of fins are at least one of louvered, wavy, offset strip or flat plate configurations.
11. A heat exchanger as recited in claim 1 wherein the transverse axis of said at least one flattened heat exchange tube is disposed at an acute angle with the horizontal in the range of from about 5 degrees to about 10 degrees.
12. A heat exchanger as recited in claim 11 wherein said at least one flattened heat exchange tube comprises a plurality of flattened heat exchange tubes disposed in parallel, spaced relationship in a generally vertical array.
13. A heat exchanger as recited in claim 11 further comprising a plurality of fins extending between adjacent tubes of said parallel tube array.
14. A heat exchanger as recited in claim 13 wherein said plurality of fins extends from a position aft of the leading edges of adjacent tubes of said parallel tube array to a position forward of the trailing edges of adjacent tubes of said tube array.
15. A heat exchanger as recited in claim 13 wherein said plurality of fins extends from a position aft of the leading edges of adjacent tubes of said parallel tube array to a position aft of the trailing edges of adjacent tubes of said tube array.
16. A heat exchanger as recited in claim 15 wherein the portion of each of said plurality of fins extending aft of the trailing edges of adjacent tubes of said tube array includes a lip portion extending behind the trailing edge of tube of said parallel array of tubes lying subadjacent said fin.
17. A heat exchanger as recited in claim 13 wherein said plurality of fins comprises a plurality of generally vertical plate-like fins extending between adjacent tubes of said parallel tube array
18. A heat exchanger as recited in claim 13 wherein said plurality of fins comprises serpentine-like corrugated fins extending between adjacent tubes of said parallel tube array.
19. A heat exchanger as recited in claim 18 wherein said a serpentine-like corrugated fins extending between adjacent tubes of said parallel tube array are forming one of generally triangular, rectangular or trapezoidal airflow passages.
20. A heat exchanger as recited in claim 13 wherein said plurality of fins are at least one of louvered, wavy, offset strip or flat plate configurations.
21. A heat exchanger as recited in claim 1 wherein said at least one flattened heat exchange tube defines at least one refrigerant flow path extending along a longitudinal axis thereof.
22. A heat exchanger as recited in claim 1 wherein said at least one flattened heat exchange tubes defines a plurality of parallel refrigerant flow paths extending parallel to a longitudinal axis thereof, each refrigerant flow path of said plurality of parallel refrigerant flow paths having an inlet to said refrigerant flow path opening in fluid communication to said first header and an outlet to said refrigerant flow path opening in fluid communication to the second header.
23. A heat exchanger as recited in claim 22 wherein said plurality of parallel fluid flow paths form at least one of rectangular, triangular, trapezoidal, circular or oval channels for refrigerant flowing herethrough.
24. A heat exchanger as recited in claim 1 wherein said at least one flattened heat transfer tube has internal heat transfer enhancement elements.
25. A heat exchanger as recited in claim 1 wherein said at least one flattened heat transfer tube has one of rectangular or oval cross-section.
26. A heat exchanger as recited in claim 1 wherein said heat exchanger is a refrigerant system evaporator.
27. A heat exchanger as recited in claim 1 wherein said heat exchanger has a single-pass configuration.
28. A heat exchanger as recited in claim 1 wherein said heat exchanger has a multi-pass configuration.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/US2006/049290 WO2008079132A1 (en) | 2006-12-26 | 2006-12-26 | Multi-channel heat exchanger with improved condensate drainage |
Publications (1)
Publication Number | Publication Date |
---|---|
US20100012305A1 true US20100012305A1 (en) | 2010-01-21 |
Family
ID=39562805
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/520,929 Abandoned US20100012305A1 (en) | 2006-12-26 | 2006-12-26 | Multi-channel heat exchanger with improved condensate drainage |
Country Status (4)
Country | Link |
---|---|
US (1) | US20100012305A1 (en) |
EP (1) | EP2097708A4 (en) |
CN (1) | CN101600932B (en) |
WO (1) | WO2008079132A1 (en) |
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US20140007600A1 (en) * | 2012-07-09 | 2014-01-09 | Mark W. Johnson | Evaporator, and method of conditioning air |
US20140049914A1 (en) * | 2010-05-26 | 2014-02-20 | International Business Machines Corporation | Dehumidifying cooling apparatus and method for an electronics rack |
US8739855B2 (en) | 2012-02-17 | 2014-06-03 | Hussmann Corporation | Microchannel heat exchanger |
US9303925B2 (en) | 2012-02-17 | 2016-04-05 | Hussmann Corporation | Microchannel suction line heat exchanger |
CN106255387A (en) * | 2016-08-31 | 2016-12-21 | 深圳绿色云图科技有限公司 | Cooling system and data center |
US20170108288A1 (en) * | 2015-10-14 | 2017-04-20 | Mark Miles | Induced convection heat exchanger |
US9777964B2 (en) | 2011-06-27 | 2017-10-03 | Carrier Corporation | Micro-port shell and tube heat exchanger |
US9890666B2 (en) | 2015-01-14 | 2018-02-13 | Ford Global Technologies, Llc | Heat exchanger for a rankine cycle in a vehicle |
JPWO2019008697A1 (en) * | 2017-07-05 | 2020-02-06 | 三菱電機株式会社 | Heat exchanger, refrigeration cycle device, and method for manufacturing heat exchanger |
US11022382B2 (en) | 2018-03-08 | 2021-06-01 | Johnson Controls Technology Company | System and method for heat exchanger of an HVAC and R system |
JP7229255B2 (en) | 2018-08-23 | 2023-02-27 | 三菱電機株式会社 | Outdoor unit and refrigeration cycle device |
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JP2014139493A (en) * | 2013-01-21 | 2014-07-31 | Toshiba Corp | Heat exchanger of air conditioner |
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US9338924B2 (en) * | 2010-05-26 | 2016-05-10 | International Business Machines Corporation | Dehumidifying cooling apparatus and method for an electronics rack |
US20140049914A1 (en) * | 2010-05-26 | 2014-02-20 | International Business Machines Corporation | Dehumidifying cooling apparatus and method for an electronics rack |
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US9173324B2 (en) * | 2010-05-26 | 2015-10-27 | International Business Machines Corporation | Dehumidifying cooling apparatus and method for an electronics rack |
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US9303925B2 (en) | 2012-02-17 | 2016-04-05 | Hussmann Corporation | Microchannel suction line heat exchanger |
US10514189B2 (en) | 2012-02-17 | 2019-12-24 | Hussmann Corporation | Microchannel suction line heat exchanger |
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CN106255387A (en) * | 2016-08-31 | 2016-12-21 | 深圳绿色云图科技有限公司 | Cooling system and data center |
JPWO2019008697A1 (en) * | 2017-07-05 | 2020-02-06 | 三菱電機株式会社 | Heat exchanger, refrigeration cycle device, and method for manufacturing heat exchanger |
US11022382B2 (en) | 2018-03-08 | 2021-06-01 | Johnson Controls Technology Company | System and method for heat exchanger of an HVAC and R system |
JP7229255B2 (en) | 2018-08-23 | 2023-02-27 | 三菱電機株式会社 | Outdoor unit and refrigeration cycle device |
Also Published As
Publication number | Publication date |
---|---|
EP2097708A1 (en) | 2009-09-09 |
EP2097708A4 (en) | 2013-11-06 |
CN101600932A (en) | 2009-12-09 |
WO2008079132A1 (en) | 2008-07-03 |
CN101600932B (en) | 2013-05-08 |
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Owner name: CARRIER CORPORATION,CONNECTICUT Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:TARAS, MICHAEL F.;LIFSON, ALEXANDER;REEL/FRAME:022862/0952 Effective date: 20061218 |
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STCB | Information on status: application discontinuation |
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