Condensate drainage device for heat exchanger

Abstract

A condensate drainage enhancing device is provided for an evaporator. An integrally molded plastic part snap fits around the conventional lower manifold, with rails maintained in tight engagement with the front and rear edges of the refrigerant flow tubes. These interrupt the meniscus films of columns of retained water that would otherwise form and, which instead drains down ribs that depend from the rails.

Claims

1. A cross flow heat exchanger comprising: a plurality of horizontally spaced, parallel and vertically oriented tubes configured to provide a fluid path for an inner fluid flowing at a temperature at which entrained water condenses out of air flowing across and between the tubes, the tubes having front edges being coplanar and rear edges being coplanar, a lower horizontal manifold, into which the front edges and rear edges enter, the lower manifold oriented along a manifold axis with a tube to tube spacing causing condensed water to become entrapped in condensate columns of a height between the tubes with meniscus films on the lower manifold, presented to the front and rear tube edges, and a condensate drainage enhancing device having a horizontal first rail extending along the manifold axis at an uppermost height of the condensate drainage enhancing device and contacting the front edges of the tubes at a location below the height of the condensate columns and contacting the meniscus films, and, a plurality of first drainage ribs depending below and downward from the first rail, evenly spaced apart from each other along the manifold axis by empty gaps, and oriented to extend away from the front edges to provide a drainage path for condensed water out of the columns, a second horizontal rail at the uppermost height of the condensate drainage enhancing device, extending along the manifold axis and contacting the rear edges of the tubes at a location below the height of the condensate columns and having second drainage ribs depending below and downward from the second rail that are oriented to extend away from the rear edges, wherein the first drainage ribs describe a curved path originating from the first rail outward in a direction away from the second drainage ribs.

2. The cross flow heat exchanger according to claim 1, wherein the first drainage ribs that describe the curved path originating from the first rail and extending first outward in the direction away from the axis and from the second drainage ribs, then extend downward, and finally inward toward the second drainage ribs.

3. The cross flow heat exchanger according to claim 1, further comprising a second horizontal rail, extending at the uppermost height along the axis on a second side opposite the first side parallel to the first rail, the second horizontal rail having second drainage ribs depending downward therefrom and below the second horizontal rail, wherein the second drainage ribs describe a curved path, originating from the second rail, first outward in a direction away from the first drainage ribs, then downward, and finally inward toward the first drainage ribs.

4. The cross flow heat exchanger according to claim 3, in which the first and second drainage ribs depending from the first and second rails are joined at their lower ends to a central keel running parallel to and beneath the axis and spaced from the first and second rails by the first and second drainage ribs.

5. The cross flow heat exchanger according to claim 4, in which the lower manifold that has a width greater than the distance between the first and second rails when the condensate drainage enhancing device is not attached to the tubes of the heat exchanger, and in which the drainage ribs are flexibly joined to the keel with a free state separation between the first drainage ribs and the second drainage ribs when the drainage device is not attached to the tubes of the heat exchanger, which is somewhat less than in an installed position so that the horizontal rails may snap fit over the lower manifold.

6. The cross flow heat exchanger according to claim 5, in which at least one edge of the first or second drainage ribs is concave in cross section to enhance drainage.

7. The cross flow heat exchanger according to claim 4, in which at least one edge of the first or second drainage ribs is concave in cross section to enhance drainage.

8. The cross flow heat exchanger according to claim 3, in which at least one edge of the first or second drainage ribs is concave in cross section to enhance drainage.

9. The cross flow heat exchanger according to claim 1, in which at least one edge of the first and second drainage ribs is concave in cross section to enhance drainage.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 is a perspective view of a preferred embodiment of the drainage device of the invention installed on an evaporator;

(2) FIG. 2 is an exploded view of the evaporator and the drainage device of the invention;

(3) FIG. 3 is a cross section of a portion of the drainage device;

(4) FIG. 4 is a cross section of a portion of the evaporator showing the presence of condensed and retained water pockets;

(5) FIG. 5 is similar to FIG. 4, but showing the drainage device installed;

(6) FIG. 6 is an end view of the drainage device in operation, with the manifold end cap removed;

(7) FIG. 7 is an end view of the drainage device installed.

DESCRIPTION OF THE PREFERRED EMBODIMENT

(8) Referring first to FIGS. 1 and 2, an evaporator indicated generally at 10 is a typical brazed aluminum design with a lower manifold 12, parallel upper manifolds 14, and, since it is a U flow construction, coplanar pairs of parallel, closely spaced refrigerant flow tubes 16. A single pass construction would have single flow tubes with a similar spacing, but likely greater width. Front and rear tube edges 18 and 20 define parallel front and rear core faces. The lower manifold 12 is typically significantly wider than the tubes 16, leaving a significant upper surface extending out from both the front and rear tube edges 18 and 20. Corrugated fins 22 are brazed between the tubes 16 to enhance heat transfer, but do not extend all the way down to the upper surface of lower manifold 12. The orientation shown is the orientation that evaporator 10 has in operation, substantially vertical, so that when humid ambient air is blown over the tubes in a so called cross-flow fashion, condensed water forms on the tube surfaces and drains and runs down, toward the upper surface of lower manifold 12.

(9) Referring next to FIGS. 1 and 4, the result of the water condensed during operation, in the absence of the subject invention, is illustrated. The combined effect of the close spacing of tubes 16, typical for a compact, high efficiency evaporator, the natural surface tension of water, and the extent of the manifold surface beyond the tube edges 18 and 20 is that condensed water forms retained columns 24 at and between the lower ends of the tubes 16, where they enter the lower manifold 12. While the upper surface of the lower manifold 12 is smooth and even downwardly curved, it presents enough resistance to drainage along its surface that the columns 24 will rise to a characteristic height h before creating enough pressure to drain down and off the edge of lower manifold 12. Water is continually condensing, so the height h is dynamically maintained, though it will rise and fall somewhat with humidity, temperature and other conditions. Another effect of the downward pressure of the columns 24 and the surface tension of the water is that outwardly bulging meniscus films 26 are formed, extending out slightly from both the front and back tube edges 18 and 20, as shown in FIG. 4.

(10) Referring next to FIGS. 2 and 3, a preferred embodiment of the drainage device of the invention is indicated generally at 28. It is an integral, molded plastic part, with a pair of parallel, straight rails 30 joined to a stiff central keel 32 by an evenly spaced plurality of curved ribs 34. As seen in FIG. 2, the free state separation of the rails 30 is just slightly less than the width measured between tube front and rear edges 18 and 20 and, substantially less that the width of lower manifold 12. As best seen in FIG. 3, the inner edges of ribs 34 are concave, specifically semi-cylindrical troughs 36, rather than sharp for a purpose described below.

(11) Referring next to FIGS. 5 and 6, the flexibility of ribs 34 allows the rails 30 to be pulled apart and snapped over the width of lower manifold 12, thereby bringing the rails 30 into tight engagement with the tube front and rear edges 18 and 20, and at a location near the upper surface of lower manifold 12, well below the characteristic column height h described above. The inner surface of the ribs 34 also conforms closely to the outer surface of the lower manifold 12. As a consequence, the water column meniscus films 26 are interrupted by the rails 30 as they attempt to form and run down the ribs 34, through the channels formed by the outer surface of lower manifold 12 and the rib troughs 36, ultimately dripping off of the ribs 34 at the keel 32. This is best illustrated in FIG. 6. As a consequence, the retained water columns 24 described above are prevented from forming, and the problems of air blockage, pressure drop, and potential water spitting avoided.

(12) Referring again to FIGS. 1 and 2, additional structure can be provided to work in cooperation with the drainage device 28, which fairly closely matches the profile of lower manifold 12. A sump or drip pan 38 and a foam seal 40 can cradle the drainage device 28 and lower manifold 12, preventing the blow-by of forced air. A strip seal 42 can be installed between the keel 32 and the underside of lower manifold 12 to also prevent air blow-by. The drip pan 38 can be open on the upstream air side, and closed on the downstream side, as shown, to allow forced air to blow water off of the drainage device 28 without loss from the drip pan 38. One or more end clips 44 can be added to the ends of the lower manifold 12 to confine the drainage device 28 axially, if desired.

(13) Variations in the preferred embodiment 28 could be made. A single rail 30, best situated on the air downstream side and in contact with just the tube rear edges 20, could, in cooperation with the depending ribs 34, provide for condensate drainage, but some other means of installation would have to be provided to maintain the device 28 in position. Rail as used here could encompass an aligned series of separate pieces, each of which touched and intruded into the entrained water columns enough to enhance the drainage as described. The two rails 30 provide more drainage paths and also allow for the self-retention after installation. Differently shaped ribs 34, so long as they depended, could provide drainage paths, but the curved shaped matches well to the shape of manifold 12, as noted, providing effective drainage paths. Localized, inwardly protruding features on rails 30 could be provided between the pairs of adjacent tubes 16, to aid breaking the meniscus films 26. It will be understood that the invention could be used with any heat exchanger in which a cold fluid flow tube has humid air passing over it to cause sufficient retained condensation to necessitate enhanced drainage.