RADIATOR HAVING A REVERSE FLOW MANIFOLD

Abstract

Disclosed herein is a radiator comprising a heat exchanger that includes a plurality of fluid conduits for carrying a thermal fluid. Each fluid conduit extends along a longitudinal axis between a first end and a second end. At least some of the fluid conduits are laterally offset from each other. The radiator also comprises a direct-flow manifold and, a reverse-flow manifold. The direct flow manifold is for conveying the thermal fluid along a first flow direction between the first ends of the fluid conduits and a first radiator line. The reverse-flow manifold is for conveying the thermal fluid along a second flow direction between the second ends of the fluid conduits and an elbow passageway, and along a third flow direction between the elbow passageway and a second radiator line. The third flow direction is opposite to the second flow direction.

Description

TECHNICAL field

The embodiments disclosed herein relate generally to radiators for heating rooms and other spaces, and, in particular to radiators having a plurality of fluid conduits for carrying a thermal fluid such as water.

INTRODUCTION

The following paragraphs are not an admission that anything discussed in them is prior art or part of the knowledge of persons skilled in the art.

Radiators are used to heat rooms within buildings. Some heating systems have boilers that heat water and circulate hot water through the radiators. In these cases, the radiator may have one or more pipes or fluid conduits for carrying the hot water. Fins can be attached to the pipes, which may enhance heating capabilities.

Conventional radiators are generally configured to operate using supply water at temperatures of at least 140° F., and usually around 180° F. or more. This poses a problem because recently developed high-efficiency condensing boilers supply water at much lower temperatures of 128° F. or less. Conventional radiators tend to perform poorly when using this low temperature water.

One way of improving performance of conventional radiators is to increase the operating temperature of the condensing boilers in order to supply hotter water (e.g. at temperatures of 140° F. to 180° F.). While this can improve performance of the radiator, it significantly decreases efficiency of the condensing boiler, which can be undesirable.

Accordingly, there is a need for a new or improved radiator, and in particular, there is a need for a radiator that is capable of operating with low temperature water.

SUMMARY

According to some embodiments, there is a radiator comprising a heat exchanger that includes a plurality of fluid conduits for carrying a thermal fluid. Each fluid conduit extends along a longitudinal axis between a first end and a second end. At least some of the fluid conduits are laterally offset from each other. The radiator also comprises a direct-flow manifold and a reverse-flow manifold. The direct flow manifold is for conveying the thermal fluid along a first flow direction between the first ends of the fluid conduits and a first radiator line. The reverse-flow manifold is for conveying the thermal fluid along a second flow direction between the second ends of the fluid conduits and an elbow passageway, and along a third flow direction between the elbow passageway and a second radiator line. The third flow direction is opposite to the second flow direction.

According to some embodiments, there is a radiator comprising a heat exchanger that includes a plurality of fluid conduits for carrying a thermal fluid. Each fluid conduit extends along a longitudinal axis between a first end and a second end. At least some of the fluid conduits are vertically offset from each other. The radiator also comprises a direct-flow manifold and a reverse-flow manifold. The direct-flow manifold is coupled to the first ends of the fluid conduits. The direct-flow manifold has a first fluid passageway that is in fluid communication with the fluid conduits and that extends downward for connection to a first radiator line. The reverse-flow manifold is coupled to the second ends of the fluid conduits. The reverse-flow manifold has a second fluid passageway and a third fluid passageway. The second fluid passageway is in fluid communication with the fluid conduits and extends upward. The third fluid passageway is in fluid communication with the second fluid passageway and extends downward for connection to a second radiator line.

According to some embodiments, there is a radiator comprising a heat exchanger that includes a plurality of fluid conduits for carrying a thermal fluid. Each fluid conduit extends along a longitudinal axis between a first end and a second end. At least some of the fluid conduits are laterally offset from each other. The radiator also comprises a direct-flow manifold and a reverse-flow manifold. The direct-flow manifold is coupled to the first ends of the fluid conduits. The direct-flow manifold has a first fluid passageway that is in fluid communication with the fluid conduits and that extends along a first lateral direction for connection to a first radiator line. The reverse-flow manifold is coupled to the second ends of the fluid conduits. The reverse-flow manifold has a second fluid passageway and a third fluid passageway. The second fluid passageway is in fluid communication with the fluid conduits and extends along a second lateral direction that is opposite to the first lateral direction. The third fluid passageway is in fluid communication with the second fluid passageway and extends along a third lateral direction for connection to a second radiator line. The third lateral direction is generally opposite to the second lateral direction.

The fluid conduits may be arranged in a grid having a plurality of columns and a plurality of rows.

The first fluid passageway of the direct-flow manifold may be centrally and symmetrically aligned between the columns of the fluid conduits, and the second fluid passageway of the reverse-flow manifold may be centrally and symmetrically aligned between the columns of the fluid conduits.

At least one of the first and second fluid passageways may have a cross-sectional area that changes between the rows of the fluid conduits. The change in the cross-sectional area between adjacent rows of fluid conduits may generally correspond to cross-sectional fluid flow area of the fluid conduits within each row.

The reverse-flow manifold may have an elbow passageway providing fluid communication between the first fluid passageway and the second fluid passageway.

The heat exchanger may include a plurality of fins arranged along the fluid conduits. Each fin may include a main plate arranged transverse to the fluid conduits. The main plate may have a plurality of openings for receiving the fluid conduits therethrough. Each fin may also include a plurality of collars that project outward from the main plate. Each collar may circumscribe one of the openings and may provide thermal contact between the main plate and one of the fluid conduits.

The main plate may have a plurality of indentations.

The main plate may be 5.5-inches long and 2.7-inches wide.

The openings may be arranged in a grid having two columns and three rows. The columns may be spaced apart by about 1.2-inches, and the rows may be spaced apart by about 1.8-inches.

The collars may have a depth of about 0.2-inches.

The heat exchanger may be at least about 3-feet long.

The radiator may further comprise an enclosure containing the heat exchanger, the direct-flow manifold, and the reverse-flow manifold. The enclosure may include a back portion and at least one support bracket for supporting the heat exchanger on the back portion. The support bracket may include: an upper bracket portion mounted to the back portion above the heat exchanger; a lower bracket portion mounted to the back portion below the heat exchanger; and a cage removably coupled to the upper bracket portion and the lower bracket portion for holding the heat exchanger in place. The radiator may also comprise a vibration isolator between the support bracket and the heat exchanger.

Other aspects and features will become apparent, to those ordinarily skilled in the art, upon review of the following description of some exemplary embodiments.

BRIEF DESCRIPTION OF THE DRAWINGS

The drawings included herewith are for illustrating various examples of articles, methods, and apparatuses of the present specification. In the drawings:

FIG. 1 is an exploded perspective view of a radiator according to one embodiment;

FIG. 2 is a perspective view of the radiator of FIG. 1 with an enclosure and some fins removed for clarity;

FIG. 3 is a partial cross-sectional view of the radiator of FIG. 2 taken along line 3-3 showing a direct-flow manifold and a reverse-flow manifold; and

FIG. 4 is a perspective view of a fin of the radiator of FIG. 1.

DETAILED DESCRIPTION

Various apparatuses or processes will be described below to provide an example of an embodiment of each claimed invention. No embodiment described below limits any claimed invention and any claimed invention may cover processes or apparatuses that differ from those described below. The claimed inventions are not limited to apparatuses or processes having all of the features of any one apparatus or process described below or to features common to multiple or all of the apparatuses described below. It is possible that an apparatus or process described below is not an embodiment of any claimed invention. Any invention disclosed below that is not claimed in this document may be the subject matter of another protective instrument, for example, a continuing patent application, and the applicants, inventors or owners do not intend to abandon, disclaim or dedicate to the public any such invention by its disclosure in this document.

Referring to FIG. 1, there is a radiator 10, which may be used to heat a space such as a room within a building. In some embodiments, the radiator 10 may be configured to operate with low temperature fluids. For example high-efficiency condensing boilers may output water or another thermal fluid at a temperature of less than about 140° F., or more particularly about 128° F. or less. These temperatures are much lower than water used with conventional boilers and radiators. Based on the ability to operate at with low temperature fluids, the radiator 10 may be referred to as a “low-temperature” radiator.

As shown in FIG. 1, the radiator 10 may include an enclosure 14. The enclosure 14 may include a back portion 16 and a front portion 18, which may also be referred to as a “cover”. The front portion 18 may be removably secured to the back portion 16.

The radiator 10 includes a heat exchanger 20, which may be contained within the enclosure 14. Referring to FIG. 2, the heat exchanger 20 includes a plurality of fluid conduits 22 for carrying a thermal fluid such as water or glycol. The fluid conduits 22 may be made from a metal such as brass or copper, or another thermally conductive material. A plurality of fins 24 may be arranged along the fluid conduits 22. The fins 24 may be thermal contact with the fluid conduits 22 for conducting thermal energy therebetween. For example, the fins 24 may be press-fit onto the fluid conduits 22. In some embodiments, the fins 24 may be welded or brazed on to the fluid conduits 22.

Each fluid conduit 22 extends along a longitudinal axis A between a first end 26 and a second end 28. As shown, some of the fluid conduits 22 are laterally offset from each other along one or more lateral directions that are generally transverse or perpendicular to the longitudinal axis A. For example, the fluid conduits 22 may be vertically offset, horizontally offset, or both.

In the illustrated embodiment, the fluid conduits 22 are arranged in a grid. More particularly, the fluid conduits 22 are arranged in a grid of two columns and three rows. In other embodiments, there may be a different number of columns or rows.

Referring still to FIG. 2, the radiator 10 includes a first manifold 30, and a second manifold 32. Each manifold 30, 32 is coupled to an end 26, 28 of the fluid conduits 22. The manifolds 30, 32 may also be referred to as “end caps”. The manifolds 30, 32 may be made from a metal such as brass, or another suitable material.

As shown, the first manifold 30 may be coupled to a first radiator line 34, and the second manifold 32 may be coupled to a second radiator line 36. The first radiator line 34 may be a supply line, and the second radiator line 36 may be a return line. Accordingly, thermal fluid may flow left to right as shown in FIG. 2.

With reference now to FIG. 3, the first manifold 30 conveys thermal fluid along a first flow direction D1 between the first radiator line 34 and the fluid conduits 22. As shown, the first flow direction D1 may be an upward direction. Since thermal fluid flows directly between the first radiator line 34 and the fluid conduits 22 along the first flow direction D1, the first manifold 30 may be referred to as a “direct-flow manifold”.

In contrast to the first manifold 30, the second manifold 32 conveys thermal fluid along two different directions. In particular, the second manifold 32 conveys fluid along a second flow direction D2 between the fluid conduits 22 and a reversing point 38, and along a third flow direction D3 between the reversing point 38 and the second radiator line 36. As shown, the third flow direction D3 may be generally opposite to the second flow direction D2 (e.g. the second flow direction may be upward, and the third flow direction may be downward). Since thermal fluid flows along two opposing directions, the second manifold 32 may be referred to as a “reverse-flow manifold”.

As described above, the first manifold 30 may be coupled to the supply line 34 and the second manifold 32 may be coupled to the return line 36. Accordingly, the first flow direction D1 may be a forward or upward direction from the supply line 34 to the fluid conduits 22. Furthermore, the second flow direction D2 may be a forward or upward direction from the fluid conduits 22 to the reversing point 38, and the third flow direction D3 may be a reverse or downward direction from the reversing point 38 to the return line 36. In other embodiments, the directions D1, D2 and D3 could be different. For example, if the first manifold 30 were coupled to the return line and the second manifold 32 were coupled to the supply line, the thermal fluid would flow in the opposite direction (i.e. right to left) and the directions D1, D2 and D3 would be opposite to that described above.

In some embodiments, the first and second flow directions D1 and D2 may be generally similar to one another. For example, in the illustrated embodiment, the first and second flow directions D1 and D2 are parallel to each other and point in the same general direction. In other embodiments, the first and second flow directions D1 and D2 could be different and might be angled with respect to each other.

Referring still to FIG. 3, the structure of the direct-flow manifold 30 and the reverse-flow manifold 32 will now be described in greater detail.

The direct-flow manifold 30 is coupled to the first ends 26 of the fluid conduits 22. For example, the direct-flow manifold 30 may have a plurality of fluid couplings coupled to the fluid conduits 22 (e.g. inlet couplings 41A, 41B, 41C).

The direct-flow manifold 30 has a first fluid passageway 40 in fluid communication with the fluid conduits 22 (e.g. via the couplings 41A, 41B, 41C). The first fluid passageway 40 extends along a first lateral direction for connection to the first radiator line 34. The first lateral direction may be generally parallel to the first flow direction D1 and may extend downward from the fluid conduits 22 to the supply line 34.

The reverse-flow manifold 32 is coupled to the second ends 28 of the fluid conduits 22. For example, the reverse-flow manifold 32 may have a plurality of fluid couplings coupled to the fluid conduits 22 (e.g. outlet couplings 43A, 43B, 43C).

The reverse-flow manifold 32 has two fluid passageways, namely, a second fluid passageway 42 and a third fluid passageway 44. The second and third fluid passageways may extend in generally opposite directions. An elbow passageway 46 may provide fluid communication between the second fluid passageway 42 and the third fluid passageway 44. The elbow passageway 46 may define the reversing point 38.

As shown, the second fluid passageway 42 is in fluid communication with the fluid conduits 22 and extends along a second lateral direction, which may be generally similar to the second flow direction D2 and may extend upward from the fluid conduits 22. The third fluid passageway 44 is in fluid communication with the second fluid passageway 42 and extends along a third lateral direction for connection to the second radiator line 36. The third lateral direction may be generally similar to the third flow direction D3 and may extend downward for connection to the second radiator line 36.

As shown, the first, second, and third lateral directions of the fluid passageways 40, 42, 44 are generally transverse to the longitudinal axis A. For example, as shown, the first, second, and third lateral directions may be generally perpendicular to the longitudinal axis A. Alternatively, the first, second, and third lateral directions could be at oblique angles to the longitudinal axis A.

Using the direct-flow manifold 30 and the reverse-flow manifold 32 might enhance thermal performance of the radiator 10. This can be particularly beneficial when using low temperature water of 128° F. or less (e.g. as supplied by a high-efficiency condensing boiler). One possible reason for enhanced thermal performance is that that each row of fluid conduits 22 might have a more uniform fluid flow distribution in comparison to conventional radiators that have direct-flow manifolds on each end of the fluid conduits 22. Having a more evenly distributed flow fluid within the fluid conduits 22 might provide a more uniform temperature gradient across the heat exchanger 20, and thus, might enhance thermal performance.

The even flow distribution might be due to reducing or equalizing flow restrictions through the fluid conduits 22. For example, with reference to FIG. 3, the first, second, and third fluid conduits 22A, 22B, 22C might each receive a portion of total fluid flow. Fluid flow through the first fluid conduit 22A might be associated with a first inlet flow restriction through the first inlet coupling 41A, and a first outlet flow restriction through the first outlet coupling 43A. Furthermore, fluid flow through the second fluid conduit 22B might be associated with a second inlet flow restriction through the second inlet coupling 41B, and a second outlet flow restriction through the second outlet coupling 43B. Finally, fluid flow through the third fluid conduit 22C might be associated with a third inlet flow restriction through the third inlet coupling 41C, and a third outlet flow restriction through the third outlet coupling 43C.

The reverse-flow manifold 32 might help balance or match flow restrictions with the direct-flow manifold 30 in reverse order. For example, the combined flow restrictions through the first inlet and outlet couplings 41A, 43A might be similar to that of the second inlet and outlet couplings 41B, 43B, and similar to that of the third inlet and outlet couplings 41C, 43C. It is believed that matching the flow restrictions through the fluid conduits 22 in this way might help equalize pressure drop through each fluid conduit 22, and thus, distribute fluid flow more uniformly, and possibly enhance thermal performance.

In contrast, if two direct-flow manifolds were used, the flow restrictions through the first inlet and outlet couplings 41A, 43A might be different to that of the second inlet and outlet couplings 41B, 43B, and different to that of the third inlet and outlet couplings 41C, 43C. This might result in uneven flow through the fluid conduits 22, which might decrease thermal performance.

Referring again to FIGS. 2 and 3, the manifolds 30, 32 may be symmetrically aligned with the columns of fluid conduits 22 (e.g. along the cross-sectional plane defined by the line 3-3). For example, the first fluid passageway 40 of the direct-flow manifold 30 may be centrally and symmetrically aligned between the two columns of fluid conduits 22. Furthermore, the second fluid passageway 42 of the reverse-flow manifold 32 may be centrally and symmetrically aligned between the at least two columns of fluid conduits. Having the manifolds 30, 32 symmetrically aligned with the fluid conduits 22 in this way might help maintain uniform fluid flow through each fluid conduit within a particular row.

In some embodiments, the fluid passageways 40, 42 of the manifolds 30, 32 might have a cross-sectional area that changes between rows of fluid conduits 22. For example, as shown FIG. 3, the fluid passageway 40 of the direct-flow manifold 30 might have a cross-sectional area that decreases from a proximal row of fluid conduits (e.g. the first fluid conduits 22A) to a distal row of fluid conduits (e.g. the third fluid conduits 22C).

In some embodiments, the change in cross-sectional area of the fluid passageway between adjacent rows of fluid conduits 22 may correspond to cross-sectional fluid flow area of those fluid conduits 22. For example, the decrease in cross-sectional area of the fluid passageway 40 between the first fluid conduit 22A and the second fluid conduit 22B may correspond to the cross-sectional area of the two first fluid conduits 22A. Similarly, the decrease in cross-sectional area of the first fluid passageway 40 between the second fluid conduit 22B and the third fluid conduit 22C may correspond to cross-sectional area of the two second fluid conduits 22B. Configuring the cross-sectional areas in this way might help maintain a fluid flow velocity that is generally similar through the fluid passageways 40, 42 as well as the fluid conduits 22, and thus, help maintain a more uniform fluid flow through the fluid conduits 22.

As described above, the radiator 10 may include a plurality of fins 24. Referring to FIGS. 2 and 4, each fin 24 may include a main plate 50 arranged transverse to the fluid conduits 22. The fin 24 may have a generally rectangular shape. For example, as shown, the main plate 50 may have a length L of about 5.5-inches, and a width W of about 2.7-inches. In other embodiments, the fin 24 could have other shapes and sizes.

The main plate 50 has a plurality of openings 52 for receiving the fluid conduits 22 therethrough. As shown, the openings 52 may be arranged in a grid. For example, there are two columns and three rows of openings 52 in the illustrated embodiment. The columns may be spaced apart by a column spacing 70 (e.g. of about 1.2-inches), and the rows may be spaced apart by a row spacing 72 (e.g. of about 1.8-inches). Furthermore, the first and last columns may be spaced from the edge of the fin 24 by about half of the column spacing 70 (e.g. about 0.6-inches), and the first and last rows may be spaced from the edge of the fin 24 by about half of the row spacing 72 (e.g. about 0.9-inches). In other embodiments, there could be a different number of openings, and the openings could have different spacing and geometric arrangements.

Each fin 24 may also include a plurality of collars 54 that project outwardly from the main plate 50. Each collar 54 may circumscribe or define one of the openings 52. The collars 54 may provide thermal contact between the main plate 50 and the fluid conduits 22. The collars may have a collar depth 55 (e.g. of about 0.2-inches).

In some embodiments, the main plate 50 may have a plurality of indentations 56. The indentations 56 may be formed as elongate, wave-like ripples in the main plate 50. The indentations 56 may increase the surface area of the fin 24, which may enhance thermal performance.

Referring again to FIG. 1, the enclosure 14 may contain the heat exchanger 20, the direct-flow manifold 30, and the reverse-flow manifold 32. Furthermore, the enclosure 14 may include one or more support brackets 80 for supporting the heat exchanger 20. More particularly, in the illustrated embodiment, there are two support brackets 80 for supporting the heat exchanger 20 on the back portion 16 of the enclosure 14. Each support bracket 80 may include an upper bracket portion 82 mounted to the back portion 16 above the heat exchanger 20, and a lower bracket portion 84 mounted to the back portion 16 below the heat exchanger 20.

The support bracket 80 may also include a grate or cage 86 that is removably coupled to the bracket portions 82, 84 for holding the heat exchanger 20 in place. The cage 86 may be formed from a wire that is hooked into a slot on the lower bracket portion 84. The wire cage 86 may also have ends 88 that extend through apertures in the upper bracket portion 82. The cage 86 may be removed by squeezing the middle of the wire cage 86 together so as to deflect the cage 86 inwards and pull the wire ends 88 through the apertures in the upper bracket portion 82. The bottom of the cage 86 can then be unhooked from the lower bracket portion 84 to remove the cage 86. After removal, the heat exchanger 20 can be disconnected from the radiator lines 34, 36 and then removed from the enclosure 14. The heat exchanger 20 can be installed by reversing this process.

In some embodiments, the radiator 10 may also include a vibration isolator 90 between the support bracket 80 and the heat exchanger 20. For example, the vibration isolator 90 may be a silicone pad that is pressed between the wire cage 86 and the fins 24 of the heat exchanger 20. This may help reduce noise such as rattling.

The radiator 10 may be made in a variety of lengths. For example, in the illustrated example, the radiator 10 may be approximately 3-feet long. This may allow attachment of the radiator 10 to a supply line 34 and a return line 36 that are approximately 3-feet apart. In other embodiments, the radiator 10 may be longer or shorter. For exemplary purposes only, the radiator 10 may be manufactured in standard lengths ranging from 2-feet to 10-feet (e.g. in one foot increments). Having a variety of lengths can be particularly useful when the radiator is designed for drop-in replacement for existing radiators that are being replaced.

While the above description provides examples of one or more apparatus, methods, or systems, it will be appreciated that other apparatus, methods, or systems may be within the scope of the claims as interpreted by one of skill in the art.

Claims

1. A radiator comprising:

a) a heat exchanger including a plurality of fluid conduits for carrying a thermal fluid, each fluid conduit extending along a longitudinal axis between a first end and a second end, at least some of the fluid conduits being laterally offset from each other;

b) a direct-flow manifold for conveying the thermal fluid along a first flow direction between the first ends of the fluid conduits and a first radiator line;

c) a reverse-flow manifold for conveying the thermal fluid along: i) a second flow direction between the second ends of the fluid conduits and an elbow passageway; and ii) a third flow direction between the elbow passageway and a second radiator line, the third flow direction being opposite to the second flow direction.

2. A radiator comprising:

a) a heat exchanger including a plurality of fluid conduits for carrying a thermal fluid, each fluid conduit extending along a longitudinal axis between a first end and a second end, at least some of the fluid conduits being vertically offset from each other;

b) a direct-flow manifold coupled to the first ends of the fluid conduits, the direct-flow manifold having a first fluid passageway that is in fluid communication with the fluid conduits and that extends downward for connection to a first radiator line; and

c) a reverse-flow manifold coupled to the second ends of the fluid conduits, the reverse-flow manifold having: i) a second fluid passageway that is in fluid communication with the fluid conduits and that extends upward; and ii) a third fluid passageway that is in fluid communication with the second fluid passageway and that extends downward for connection to a second radiator line.

3. A radiator comprising:

a) a heat exchanger including a plurality of fluid conduits for carrying a thermal fluid, each fluid conduit extending along a longitudinal axis between a first end and a second end, at least some of the fluid conduits being laterally offset from each other;

b) a direct-flow manifold coupled to the first ends of the fluid conduits, the direct-flow manifold having a first fluid passageway that is in fluid communication with the fluid conduits and that extends along a first lateral direction for connection to a first radiator line; and

c) a reverse-flow manifold coupled to the second ends of the fluid conduits, the reverse-flow manifold having: i) a second fluid passageway that is in fluid communication with the fluid conduits and that extends along a second lateral direction opposite to the first lateral direction; and a third fluid passageway that is in fluid communication with the second fluid passageway and that extends along a third lateral direction for connection to a second radiator line, the third lateral direction being generally opposite to the second lateral direction.

4. The radiator of claim 3, wherein the fluid conduits are arranged in a grid having a plurality of columns and a plurality of rows.

5. The radiator of claim 4, wherein

a) the first fluid passageway of the direct-flow manifold is centrally and symmetrically aligned between the columns of the fluid conduits; and

b) the second fluid passageway of the reverse-flow manifold is centrally and symmetrically aligned between the columns of the fluid conduits.

6. The radiator of claim 5, wherein at least one of the first and second fluid passageways has a cross-sectional area that changes between the rows of the fluid conduits.

7. The radiator of claim 6, wherein the change in the cross-sectional area between adjacent rows of fluid conduits generally corresponds to cross-sectional fluid flow area of the fluid conduits within each row.

8. The radiator of claim 3, wherein the reverse-flow manifold has an elbow passageway providing fluid communication between the first fluid passageway and the second fluid passageway.

9. The radiator of claim 3, wherein the heat exchanger includes a plurality of fins arranged along the fluid conduits.

10. The radiator of claim 9, wherein each fin includes:

a) a main plate arranged transverse to the fluid conduits, the main plate having a plurality of openings for receiving the fluid conduits therethrough;

b) a plurality of collars that project outward from the main plate, each collar circumscribing one of the openings and providing thermal contact between the main plate and one of the fluid conduits.

11. The radiator of claim 10, wherein the main plate has a plurality of indentations.

12. The radiator of claim 10, wherein the main plate is 5.5-inches long and 2.7-inches wide.

13. The radiator of claim 10, wherein the openings are arranged in a grid having two columns and three rows, the columns being spaced apart by about 1.2-inches, and the rows being spaced apart by about 1.8-inches.

14. The radiator of claim 10, wherein the collars have a depth of about 0.2-inches.

15. The radiator of claim 3, wherein the heat exchanger is at least about 3-feet long.

16. The radiator of claim 3, further comprising an enclosure containing the heat exchanger, the direct-flow manifold, and the reverse-flow manifold.

17. The radiator of claim 16, wherein the enclosure includes a back portion and at least one support bracket for supporting the heat exchanger on the back portion.

18. The radiator of claim 17, wherein the support bracket includes:

a) an upper bracket portion mounted to the back portion above the heat exchanger;

b) a lower bracket portion mounted to the back portion below the heat exchanger; and

c) a cage removably coupled to the upper bracket portion and the lower bracket portion for holding the heat exchanger in place.

19. The radiator of claim 17, further comprising a vibration isolator between the support bracket and the heat exchanger.