Condensing Heat Exchanger for Gas Furnaces
A condensing heat exchanger (100, 100a) is disclosed that includes a pair of opposing half shells (145, 145a) connected together. The half shells (145, 145a) define an inlet (111) at one end and at least one outlet (112, 113) at an opposing end of the heat exchanger. The pair of opposing half shells (145, 145a) also defines a central axis (133). Each half shell (145, 145a) includes a plurality of elongated angled beads (117, 117a, 119) that extend inwardly towards the other half shell. The elongated angled beads (117, 117a, 119) of each half shell (145, 145a) extend traversely across the central axis (133) at an angle θ with respect to the central axis (133). The beads of one half shell (145, 145a) also extend traversely across one or more beads of the other half shell. The half shells (145, 145a) form two side channels (121, 121a, 122, 122a) for collecting condensate disposed opposite the plurality of elongated angled beads (117, 117a, 119) from one another and between the inlet (111) and at least one outlet (112, 113).
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This application is a non-provisional patent application claiming priority under 35 USC §119(e) to U.S. Provisional Patent Application Ser. No. 61/247,328 filed on Sep. 30, 2009.
BACKGROUND1. Technical Field
This disclosure relates to heat exchangers. More specifically, this disclosure relates to heat exchangers for gas furnaces in which water vapor present as a combustion gas product in flue gas is condensed and the latent heat of vaporization is transferred to another medium, such as air of an interior space. Still more specifically, this disclosure relates to enhanced internal flow barriers within condensing heat exchangers for improved heat transfer.
2. Description of the Related Art
Condensing heat exchangers are typically plate-type heat exchangers made from two opposing halves or half shells. Heat is transferred from the inside, between the half shells, to the exterior of the heat exchanger. The external fluid is air; the internal fluid is flue gas from hydrocarbon gas combustion (e.g., natural gas), which includes carbon dioxide and water vapor. One purpose of condensing heat exchangers is to condense the water vapor to liquid water thereby releasing the latent heat of vaporization of the water in the flue gas and the transfer this latent heat, along with other heat, to the air disposed the outside the heat exchanger.
Typically, the internal designs of condensing heat exchangers include barriers to flow which force the flue gas to travel through a tortuous path inside the heat exchanger before exiting the heat exchanger. The barriers cause the flow to change direction slightly or dramatically, which is intended to increase the total flow path length and residence time inside the heat exchanger, and increase contact between the flue gas and the interior walls of the heat exchanger. In current designs, the barriers to flow are often referred to as beads. Matching beads are disposed in each opposing half of the heat exchanger and the matching beads meet in a center plane dividing the two heat exchanger halves to form a barrier disposed normal or perpendicular to the general flue gas flow direction. The flue gas flow is diverted around the beads to the ends of the opposing beads and continues to flow through the heat exchanger through the path of least resistance. Typically, two paths of least resistance are created in the form of two channels extending along the top and bottom of the heat exchanger. As a result, a large portion of the flue gas bypasses the circuitous pattern created by the bead pattern.
In satisfaction of these needs, an improved condensing heat exchanger is disclosed that comprises a pair of opposing half shells connected together. The half shells define an inlet at one end and at least one outlet at an opposing end of the heat exchanger. The pair of opposing half shells also defines a central axis. Each half shell comprises a plurality of elongated angled beads that extend inwardly towards the other half shell. The elongated angled beads of each half shell extend traversely across the central axis at an angle θ with respect to the central axis. The beads of one half shell also extend traversely across one or more beads of the other half shell. The half shells form two side channels for collecting condensate disposed opposite the plurality of elongated angled beads from one another and between the inlet and at least one outlet.
A method of reducing the size of a condensing heat exchanger as described above is also disclosed. The method comprises providing elongated angled beads in the opposing half shells that extend across the central core areas of the half shells between the side channels of the heat exchanger. The elongated angled beads of one half shell are not in matching registry with the elongated angled beads of the other half shell. Further, the elongated angled beads of one half shell extend traversely across the elongated angled beads of the other half shell. By incorporating these design features, the size of the heat exchanger can be reduced as a result of the improved efficiency.
Other advantages and features will be apparent from the following detailed description when read in conjunction with the attached drawings.
For a more complete understanding of the disclosed methods and apparatuses, reference should be made to the embodiments illustrated in greater detail in the accompanying drawings, wherein:
It should be understood that the drawings are not necessarily to scale and that the disclosed embodiments are sometimes illustrated diagrammatically and in partial views. In certain instances, details which are not necessary for an understanding of the disclosed methods and apparatuses or which render other details difficult to perceive may have been omitted. It should be understood, of course, that this disclosure is not limited to the particular embodiments illustrated herein.
DETAILED DESCRIPTION OF THE PRESENTLY PREFERRED EMBODIMENTSAs shown in
Improved heat exchangers 100, 100a are illustrated in
Instead of the conventional beads 17-19 of
By angling the beads 117, 119 at angle θ and having the beads 117, 119 of opposing half shells cross each other as opposed to overlying each other, the beads 117, 119 do not create a barrier to flow over the full length of the beads 117, 119. As a result, flue gas can more easily pass over the center core areas 120a, 120 of the heat exchangers 100a, 100 so that the center core areas 120a, 120 are better utilized for overall heat transfer. The angled beads 117, 119 permit the heat exchangers 100a, 100 to be smaller while accomplishing the same or higher efficiency than the prior art heat exchanger 10, depending on the height or width H (
By allowing the flue gas to flow more freely through the center core areas 120a, 120 of the heat exchangers 100a, 100, the peak velocities 123a, 124a, 123, 124 near the inlets 111 are substantially reduced as compared to the high velocities along the initial flow paths 23, 24 as illustrated in
As illustrated in
Side channels 121, 122 are created by the ends of the beads 117, 119 to permit easy extraction of the condensate. However, in contrast to the prior art design 10, the center core areas 120 of the heat exchanger 100 remain fully open so that the gas flow is not inhibited by the water collecting in the outer channels 121, 122.
Returning to
The performance of the heat exchangers 100, 100a may increase the overall furnace efficiency over the current production heat exchanger 10, at a reduced size thereby making a more efficiency gas furnace at a lower cost for materials.
As a result, the heat exchanger 100 illustrated in FIGS. 5 and 7-11 provide increased efficiency (e.g., about 15% or more), reduced pressure (by about 60% or more), and a reduced height H (by about 30% or more).
While only certain embodiments have been set forth, alternatives and modifications will be apparent from the above description to those skilled in the art. These and other alternatives are considered equivalents and within the spirit and scope of this disclosure and the appended claims.
Claims
1. A condensing heat exchanger (100, 100a) comprising:
- a pair of opposing half shells (145, 145a) connected together, the half shells (145, 145a) defining an inlet (111) at one end and at least one outlet (112, 113) at an opposing end, the pair of opposing half shells (145, 145a) also defining a central axis (133),
- each half shell (145, 145a) comprising a plurality of elongated angled beads (117, 119) that extend inwardly towards the other half shell (145, 145a), the elongated angled beads (117, 119) of each half shell (145, 145a) extending traversely across the central axis (133) at an angle θ with respect to the central axis (133), the beads (117, 119) of one half shell (145, 145a) extending traversely across one or more beads (117, 117a, 119) of the other half shell (145, 145a).
2. The condensing heat exchanger (100, 100a) of claim 1 wherein the half shells (145, 145a) form two side channels (121, 121a, 122, 122a) for collecting condensate disposed opposite the plurality of elongated angled beads (117, 117a, 119) from one another and between the inlet (111) and at least one outlet (112, 113).
3. The condensing heat exchanger (100, 100a) of claim 1 wherein each half shell (145, 145a) further comprises at least one perpendicular bead (141, 142) disposed in close proximity to the inlet (111).
4. The condensing heat exchanger (100, 100a) of claim 3 wherein the perpendicular beads (141, 142) of the half shells (145, 145a) are offset from one another.
5. The condensing heat exchanger (100, 100a) of claim 4 wherein each half shell (145, 145a) comprises from about two to about four perpendicular beads (141, 142) disposed in close proximity to the inlet (111).
6. The condensing heat exchanger (100, 100a) of claim 3 wherein the perpendicular beads (141, 142) do not extend across the central axis (133).
7. The condensing heat exchanger (100, 100a) of claim 1 wherein the elongated angled beads (117, 117a, 119) each comprise an elongated outer surface (138), the elongated outer surfaces (138) of at least some of the elongated angled beads (117, 117a, 119) being arced inwardly away from the opposing half shell (145, 145a) for increasing flow along the central axis (133).
8. The condensing heat exchanger (100, 100a) of claim 1 wherein the elongated angled beads (117, 117a, 119) each comprise two opposite ends (117′, 119′) with an elongated outer surface extending between the opposite ends (117′, 119′),
- the elongated outer surfaces (138) of at least some of the elongated angled beads (117, 117a, 119) being arced inwardly away from the opposing half shell (145, 145a) between the two opposite ends (117′, 119′) so the two opposite ends (117′, 119′) are disposed closer to the opposing half shell (145, 145a) than a remainder of the arced outer surface (138) extending between the two opposite ends (117′, 119′).
9. The condensing heat exchanger (100, 100a) of claim 1 wherein θ ranges from about 20° to about 70°.
10. The condensing heat exchanger (100, 100a) of claim 1 wherein θ is about 40°.
11. The condensing heat exchanger (100, 100a) of claim 1 wherein the inlet (111) is co-axial with the central axis (133) and the heat exchanger (100, 100a) comprises two outlets (112, 113) disposed opposite the central axis (133) from each other.
12. The condensing heat exchanger (100, 100a) of claim 1 wherein the elongated angled beads (117, 117a, 119) of one half shell (145, 145a) are disposed of perpendicularly to the elongated angled beads (117, 117a, 119) of the other half shell (145, 145a).
13. A condensing heat exchanger (100, 100a) comprising:
- a pair of opposing half shells (145, 145a) connected together, the half shells (145, 145a) defining an inlet (111) at one end and at least one outlet (112, 113) at an opposing end, the pair of opposing half shells (145, 145a) also defining a central axis (133),
- each half shell (145, 145a) comprising a plurality of elongated angled beads (117, 117a, 119) that extend inwardly towards the other half shell, the elongated angled beads (117, 117a, 119) of each half shell (145, 145a) extending traversely across the central axis (133) at an angle θ with respect to the central axis (133), the beads of one half shell (145, 145a) extending traversely across one or more beads (117, 117a, 119, 119a) of the other half shell (145, 145a),
- the elongated angled beads (117, 117a, 119) each comprising an elongated outer surface (138), the elongated outer surfaces (138) of at least some of the elongated angled beads (117, 117a, 119) being arced inwardly away from the opposing half shell (145, 145a) for increasing flow along the central axis (133),
- the half shells (145, 145a) forming two side channels (121, 121a, 122, 122a) for collecting condensate disposed opposite the plurality of elongated angled beads (117, 117a, 119) from one another and between the inlet (111) and at least one outlet (112, 113).
14. The condensing heat exchanger (100, 100a) of claim 13 wherein each half shell (145, 145a) further comprises at least one perpendicular bead (141, 142) disposed in close proximity to the inlet (111).
15. The condensing heat exchanger (100, 100a) of claim 14 wherein the perpendicular beads (141, 142) of the half shells (145, 145a) are offset from one another.
16. The condensing heat exchanger (100, 100a) of claim 13 wherein θ ranges from about 20° to about 70°.
17. The condensing heat exchanger (100, 100a) of claim 12 wherein the elongated angled beads (117, 117a, 119) of one half shell (145, 145a) are disposed of perpendicularly to the elongated angled beads (117, 117a, 119) of the other half shell (145, 145a).
18. A method of reducing a size of a condensing heat exchanger (100, 100a) that comprises a pair of opposing half shells (145, 145a) connected together, the half shells (145, 145a) defining an inlet (111) at one end and at least one outlet (112, 113) at an opposing end, the pair of opposing half shells (145, 145a) also defining a central axis (133), the half shells (145, 145a) forming two side channels (121, 121a, 122, 122a) for collecting condensate disposed opposite the central core areas (120, 120a) of the two half shells (145, 145a), the method comprising:
- providing elongated angled beads (117, 117a, 119) in the opposing half shells (145, 145a) that extend across the central core areas (120, 120a) of the half shells (145, 145a) between the side channels (121, 121a, 122, 122a), the elongated angled beads (117, 117a, 119) of one half shell (145, 145a) extending traversely across the elongated angled beads (117, 117a, 119) of the other half shell (145, 145a).
19. The method of claim 18 further comprising increasing flow across central core areas (120) of the opposing half shells (145) by arcing an elongated outer surface of at least some of the elongated angled beads (117) inwardly away from the opposing half shell (145) to increase space between the elongated angled beads (117, 119) of the two opposing half shells (145) and for increasing flow along the central axis (133) of the condensing heat exchanger (100).
20. The method of claim 17 wherein the elongated angled beads (117, 117a, 119) of each half shell (145, 145a) extending traversely across the central axis (133) at an angle θ with respect to the central axis (133), and wherein θ ranges from about 20° to about 70°.
Type: Application
Filed: Sep 30, 2010
Publication Date: Nov 17, 2011
Applicant: Carrier Corporation (Farmington, CT)
Inventors: Paul M. Haydock (Zionsville, IN), Scott A. Beck (Indianapolis, IN)
Application Number: 12/894,764
International Classification: F28F 3/12 (20060101);