Heat exchanger

Abstract: Poor heat exchange in a heat exchanger between a flue gas passing through the heat exchanger and air being forced through the heat exchanger can be improved in a heat exchanger and combustor (30) for exchanging heat between a forced air stream and a flue gas generated by a plurality of spaced, parallel burners (44) with a construction including spaced, upper and lower headers (32, 34), a plurality of tubes (50), one for each burner (44) extending in parallel between and mounted to the headers (32, 34). Each tube (50) has a first section (56) of enlarged cross section adapted to serve as a combustor for fuel to generate the flue gas and a narrowed, second section (70) for exchanging heat between the flue gas and the forced air stream. Each second section includes generally flat, parallel spaced walls (58, 60) with each of the walls (58, 60) having dimples (74) therein which are directed toward the other of the walls (58. 60) into substantially contacting or almost contacting relationship therewith.

Description: This invention relates to furnaces such as so-called "unit heaters", and more specifically, to an improved heat exchanger for use in such furnaces. So called "unit heaters" have seen extensive use in commercial and industrial settings. They are relatively easy to install and provide relatively high quantities of heat for the space that they occupy. In the usual case, such heaters include a heat exchanger made up of several parallel tubes. The tubes are typically arranged vertically and their lower sections are of relatively large cross section to be aligned with a burner or the like and act as a combustor. The resulting flue gases resulting from combustion then travel upwardly within each of the tubes through a narrowed section. After the flue gas has exited the tubes, it is typically conducted away to a vent. Air flowing past either section of the tube on the exterior thereof is heated by the hot walls of the tube. GB-A-2019549 describes a heater including a housing having an air inlet, an air outlet, a fan for driving air from the inlet to the outlet through a flow path, a plurality of parallel spaced burners within the housing below the flow path, and a heat exchanger in the flow path above the burners. The heat exchanger comprises a plurality of flattened generally vertical tubes, one for each burner; each tube having a relatively wide open lower end overlying an associated burner and a relatively narrow upper end having spaced parallel sides. FR-A-1520628 describes a furnace including a housing having an air inlet, an air outlet, a fan for driving air from the inlet to the outlet through a flow path, a pair of parallel spaced burners within the housing and a heat exchanger in the flow path generally above the burners. The heat exchanger comprises a pair of flattened, generally vertical tubes, one for each burner, with each tube having a relatively wide lower end and a relatively narrow upper end having spaced parallel sides; each side having a plurality of dimples directed toward the other side and aligned with the dimples formed in the other side. The present invention is directed to a furnace comprising a new and improved tube construction for use in a heat exchanger of the sort mentioned and which is particularly suited for use in an improved unit heater to provide improved heat transfer efficiency. According to a first aspect of the invention there is provided a furnace including a housing having an air inlet; an air outlet; a fan or blower for driving air from the inlet to the outlet through a flow path; a plurality of parallel, spaced burners within the housing just below the flow path and a heat exchanger in the flow path and just above the burners and including a plurality of flattened, generally vertical tubes, one for each burner; each tube having a wide lower end and a narrower, upper end having spaced, nominally parallel sides, each having a plurality of dimples directed toward the other side and aligned with the dimples formed in the other side and characterised in that the lower end of each tube is open and overlies the associated burner, by some of the dimples being contacting and others of the dimples being slightly spaced, and by there being more contacting dimples near the upper ends of the tubes than at a lower level thereon. In a preferred embodiment, the dimples substantially fill the sides above the relatively wide lower end. Preferably, each of the lower ends, on both sides thereof, includes a convex dimple extending toward and nominally engaging a corresponding convex dimple on the adjacent side of the adjacent tube. It is preferred that at least some of the contacting dimples are secured to each other. In a highly preferred embodiment, the dimples are arranged in a zig-zag pattern from top to bottom of the tube. Preferably, the zig-zag pattern is a honeycomb pattern. Other objects and advantages will become apparent from the following specification taken in connection with the accompanying drawings in which: Fig. 1 is a side elevation of a unit heater made according to the invention: Fig. 2 is an enlarged, side elevation of a heat exchanger employed in the unit heater; Fig. 3 is a side elevation of the heat exchanger taken from the right of Fig. 2; Fig. 4 is a further enlarged elevation of a tube used in the heat exchanger; Fig. 5 is an enlarged, fragmentary sectional view of one type of dimple employed in the tube; and Fig. 6 is a view similar to Fig. 5, but showing another type of dimple employed in the tube. An exemplary embodiment of a unit heater made according to the invention is illustrated in Fig. 1 and is seen to include a cabinet or housing, generally designated 10, of conventional construction. However, it is to be appreciated that the principles of the invention are not limited to use solely in unit heaters, but may be employed with efficacy in other types of furnaces as well. At its front side 12, the same includes a hot air outlet, generally designated 14, which may be provided with a series of pivoted louvers 16 for directional air flow as is well-known. At its rear side 18, the housing 10 includes an inlet opening 20. A motor support 22 secured to the rear side 18 mounts a fan motor 24 having a shaft 26 mounting a fan blade 28 within the inlet opening for rotation therein. As is well-known, the fan made up of the motor 24 and blade 28 will force air through the housing 10 and out of the outlet 14. The interior of the housing 10 is, in a large part, occupied by a heat exchanger, generally designated 30. The heat exchanger, to be described in greater detail hereinafter, includes an upper header 32 and a lower header 34 which delimit the top and bottom of a forced air flow path from the inlet 20 to the outlet 14. The upper end of the housing 10 is provided with a vent connector 36 which may be connected to a vent or the like to convey gases of combustion thereto. The vent connector 36 is associated with a flue collector, generally designated 40, within the housing 10 and associated with the upper header 32. A fuel pipe 42, for connection to a source of fuel such as natural gas, LP gas or the like, extends into the housing and is associated with a plurality of elongated, generally parallel burners 44. The association is via a suitable control valve or valves 46 and metering devices or orifices 47 which may be arranged in a conventional fashion. The housing 10 may also mount an electrical junction box 48 which may house controls for the motor 24 and the valve 46 as is well known. Turning now to Figs. 2 and 3, the heat exchanger 30 will be described in greater detail. As best seen in Fig. 2, the heat exchanger is made up of a plurality of tubes 50 extending between the headers 32 and 34 on the centers indicated. As can be ascertained by comparing Figs. 2 and 3, the tubes 50 are of flattened cross section. The same include open lower ends 52 mounted to the lower headers 34 in any desired fashion. The lower ends 52 are relatively wide in comparison to the upper ends 54 and are adapted to overlie a corresponding one of the burners 44 to receive the fuel and primary air mix emanating from the associated burner as well as such secondary air as may enter the open lower end 52. Thus, combustion occurs within the enlarged lower ends 52 of each of the tubes 50 such that the lower ends 52 act as a combustor section in each of the tubes 50. Typically, the configuration of the lower ends 52 will be any one of those well-known, conventional configurations that assures complete combustion of the fuel within the combustor section defined thereby and avoids the generation of carbon monoxide. For ease of reference, the just described combustor sections of the tubes 50 will be given the reference numeral 56 and as can be seen in Figs. 2 and 3, each side wall 58 or 60 of the combustor section 56 includes a convex dimple 62. The dimples 62 are directed toward the adjacent side wall 58 or 60 of the immediately adjacent tube 50 and are in nominal contact with each other as can be seen at the lower left end of Fig. 2. The purpose of the dimples 62 is to maintain spacing between the combustor sections 56 of adjacent tubes 50 during a heat exchange operation. Specifically, as is well-known, the tubes 50 will typically be made of sheet metal and as they heat up or cool down, they may tend to move as a result of thermal expansion. If such were to occur with the side wall 58 of one tube moving toward the adjacent side wall 60 of an adjacent tube, and the dimples 62 were not present, the airflow space between those side walls could become blocked, wholly or partially, and that would impede heat transfer efficiency since the surface associated with the blocked passage would effectively be taken out of the heat transfer operation. Furthermore, it is possible that localized overheating could result in such a situation, raising the possibility of damage to the heat exchanger. These consequences are, however, avoided through the use of the dimples 62 which maintain proper spacing. Above the combustor section 56, each tube 50 includes a heat exchanger section 70. The heat exchanger section 70 is intended to exchange heat between flue gas passing upwardly within the associated tube 50 and air being driven from the inlet 20 to the outlet 14 by the fan 24, 28. The heat exchange section 70 is delimited by that part of each tube 50 extending downwardly from the upper header plate 32 to the point or line 72 in each wall 58 or 60 whereat the walls 58 and 60 begin to diverge to define the combustor section 56. The walls 58 and 60 of each tube 50, in the heat exchanger section 70, are substantially filled with a plurality of concave dimples, the outlines of which are shown at 74 in Fig. 3. The dimples 74 are arranged, from top to bottom of the heat exchanger, in a zig-zag fashion which may be more aptly termed a honeycomb pattern. It bears repeating that the pattern of dimples 74 substantially fills each of the sidewalls 58 and 60 which is to say that there is substantially no room left in such walls for any additional complete dimples. As can be seen in Fig. 4, each tube 50 may be made up of two tube halves 76 that are identical to each other and joined together at 78. In the embodiment illustrated in Figs. 3 and 4, from top to bottom, there are eight horizontal rows of the dimples 74, which rows are designated A, B, C, D, E, F, G and H. Fig. 4 illustrates that both of the sides 58 and 60 of a tube 50 are provided with the dimples 74 with the dimples in one wall 58 being aligned with the dimples 74 in the other wall 60. The dimples 74 thus are directed towards the opposite wall and it is preferred that they extend into contacting or almost contacting relation with the other wall which is to say, the aligned dimple formed in the other wall. Fig. 5 illustrates a typical dimple 74 which may be basically conical or even slightly spherical if desired. Apexes 80 of the aligned dimples 74 are touching or almost touching. Generally, speaking, it will be desired that there be actual contact between the aligned dimples in the higher rows such as rows A, B and C while some spacing between aligned dimples 74 may be present in one or more of the lowermost rows. Thus, in Fig. 4, the dimples in row H are shown to be slightly spaced. In some instances, dimples will be formed with flat bottoms as illustrated at 82. In this case, the flat bottoms 82 of aligned dimples are in engagement with one another and are secured to each other, as, for example, by a spot weld 84. This construction provides dimensional stability during operation in terms of resisting warping or oil-canning of the walls 58, 60 due to internal thermal stress. The location of dimples 74 bearing spot welds 84 is shown in Fig. 3. At each of these locations, in a preferred embodiment of the invention, the depth of each dimple is chosen to be 8.89mm (0.350 inches). This dimension is also held for all of the dimples in rows A, B and C. The dimples 74 in row D that lack spot welds 84 have a corresponding dimension of 8.25mm (0.325 inches) while a return is made to the 8.89mm (0.350 inch) dimension in row E. Dimples in row F that are not flat bottomed dimples (spot welded) have a corresponding dimension of 7.37mm (0.290 inches) while the dimple depth of the dimples in row G, from left to right alternates at 8.89mm to 7.62mm (0.350 to 0.300 inches). All dimples in row H have a depth of 6.1mm (0.240 inches). The purpose of causing the dimples 74 to contact or almost contact the wall that they face is to minimize the area for passage of a flue gas between the apex 80 of a dimple and the wall that it faces. Thus, given the zig-zag configuration of the dimples, the flue gas is forced to pass in a tortuous path, thereby increasing its turbulence and enhancing heat transfer from the gas to the tube 50. The reason that more contact between facing dimples near the upper end of the tubes 50 is provided as a result of the greater depth of each dimple than at a lower level is to occlude somewhat more of the overall cross sectional area of the interior of the tubes with dimples to continue to force the gas in a tortuous path. It will be appreciated that as the gas moves upwardly within the tubes 50, it is cooling and thus its volume will be reduced. The increased contact between dimples at the upper ends of the tubes thus reduces cross sectional area to compensate for the fact that the volume of the gas is simultaneously decreasing as well. A heat exchanger made according to the invention has been determined to increase heat transfer to air being flowed across the tubes 50 in the range of 3 to 8 percent for the same burner setting utilizing conventional tubes heretofore employed in unit heaters manufactured by the assignee of the instant application. The actual percentage within the range depends, of course, on the specific burner setting chosen. It is believed that this increase is due to both the turbulence induced by forcing the flue gas to follow a tortuous path which thus increases the heat transfer coefficient on the flue gas side as well as as a result of the fact that forming the dimples in the walls of the tubes actually increases the surface area exposed to the flue gas to some degree. In any event, it will be appreciated that the use of dimples in a heat exchanger made according to the invention provides a measurable and tangible increase in heat transfer efficiency.

Claims: A furnace including a housing (10) having an air inlet (20); an air outlet (14); a fan or blower (24,28) for driving air from the inlet (20) to the outlet (14) through a flow path; a plurality of parallel, spaced burners (44) within the housing (10) just below the flow path and a heat exchanger (30) in the flow path and just above the burners (44) and including a plurality of flattened, generally vertical tubes (50), one for each burner (44); each tube (50) having a wide lower end (52) and a narrower upper end (54) having spaced, nominally parallel sides (58, 60), each having a plurality of dimples (74) directed toward the other side and aligned with the dimples formed in the other side and characterised in that the lower end of each tube (50) is open and overlies the associated burner (44), by some of the dimples (74) being contacting and others of the dimples being slightly spaced, and by there being more contacting dimples (74) near the upper ends (56) of the tubes (50) than at a lower level thereon. The furnace of Claim 1 wherein said dimples (74) are arranged in a zig-zag pattern from top to bottom of said tube (50). The furnace of Claim 2 wherein said dimples (74) substantially fill said sides (58,60) above said relatively wide lower end (52). The furnace of Claim 3 wherein said dimples are in a honeycomb pattern. The furnace of Claim 1 wherein each of said lower ends (52), on both sides (58,60) thereof, includes a convex dimple (62) extending toward and nominally engaging a corresponding convex dimple (62) on the adjacent side (58,60) of the adjacent tube (50). The furnace of Claim 1 wherein some of said contacting dimples (74) are secured to each other.

Inventors: COOLEY ROBERT S, MATTSON NORMAN E, MIELKE RICHARD A, COOLEY, ROBERT S., MATTSON, NORMAN E., MIELKE, RICHARD A.
Applicants: MODINE MFG CO, MODINE MANUFACTURING COMPANY
Application year: 1992
Main classification: F24H3
IPC codes: F28D9, F24H3, F28F3, F28D1, F28F13