VERTICAL BUNDLE AIR-COOLED HEAT EXCHNAGER, METHOD OF MANUFACTURING THE SAME, AND POWER GENERATION PLANT IMPLEMENTING THE SAME

Abstract

A vertical bundle air-cooled heat exchanger. In one embodiment, the invention can be a vertical bundle air-cooled condenser comprising: at least one tube bundle assembly comprising: a tube bundle comprising a plurality of finned tubes arranged in a substantially vertical and side-by-side orientation, each of the plurality of finned tubes comprising a cavity; a top header pipe comprising an inlet header cavity operably coupled to a source of steam; a bottom header pipe comprising an outlet header cavity for collecting condensate; top ends of the plurality of finned tubes coupled to the top header pipe and the bottom ends of the plurality of finned tubes coupled to the bottom header pipe; and a shell having an open top end and open bottom end, the at least one tube bundle assembly positioned within the shell.

Claims

1. An air-cooled condenser comprising: a shell defining an internal cavity having an open top end and open bottom end; a tube bundle assembly disposed in the cavity of the shell; the tube bundle assembly comprising a horizontally elongated top header pipe, a horizontally elongated bottom header pipe, and a plurality of vertical heat exchange tubes each fluidly coupled to the top and bottom pipes by respective upper and lower feeder pipes.

2. The air-cooled condenser according to claim 1 wherein the top and bottom header pipes are spaced apart and vertically axially aligned with each other in a common vertical plane.

3. The air-cooled condenser according to claim 2, wherein the top and bottom header pipes are oriented parallel to each other.

4. The air-cooled condenser according to claim 2, wherein the tubes are arranged in a horizontally aligned first row of tubes above the bottom header pipe and below the top header pipe.

5. The air-cooled condenser according to claim 4, wherein the tubes are oriented parallel to each other.

6. The air-cooled condenser according to claim 5, wherein tops of each tube lie in a common upper horizontal plane and bottoms of each of the tubes lie in a common lower horizontal plane.

7. The air-cooled condenser according to claim 4, wherein the first row of tubes includes an outermost peripheral pair of tubes each laterally offset from the top and bottom header pipes and the common vertical plane, and a central tube extending linearly between the top and bottom header pipes along the common vertical plane.

8. The air-cooled condenser according to claim 7, wherein the peripheral pair of tubes are each fluidly coupled to the top and bottom header pipes by L-shaped upper and lower feeder pipes.

9. The air-cooled condenser according to claim 8, wherein the central tube is fluidly coupled to the top and bottom header pipes by straight upper and lower feeder pipes.

10. The air-cooled condenser according to claim 9, further comprising an intermediate pair of tubes, one each of the intermediate pair of tubes arranged between one of the peripheral tubes and the central tube.

11. The air-cooled condenser according to claim 10, wherein the intermediate pair of tubes are each fluidly coupled to the top and bottom header pipes by L-shaped upper and lower feeder pipes.

12. The air-cooled condenser according to claim 11, wherein each of the top and bottom header pipes has a vertically elongated obround transverse cross-sectional shape defining a minor axis oriented perpendicular to the common vertical plane and a major axis oriented parallel to the common vertical plane.

13. The air-cooled condenser according to claim 12, wherein each of the top and bottom header pipes comprises a pair of opposing flat vertical sides, an arcuate top extending between the vertical sides, and an arcuate bottom extending between the vertical sides.

14. The air-cooled condenser according to claim 13, wherein the upper and lower feeder pipes of each of the peripheral and intermediate tubes are fluidly connected to one of the flat vertical sides of the top and bottom header pipes.

15. The air-cooled condenser according to claim 14, wherein the upper feeder pipes of the intermediate tubes are fluidly connected to one of the flat vertical sides of the top header pipe below the upper feeder pipes of the peripheral tubes.

16. The air-cooled condenser according to claim 15, wherein the lower feeder pipes of the intermediate tubes are fluidly connected to one of the flat vertical sides of the bottom header pipe above the upper feeder pipes of the peripheral tubes.

17. The air-cooled condenser according to claim 11, wherein the upper and lower feeder pipes of the intermediate tubes are nested inside the upper and lower feeder pipes of the peripheral tubes.

18. The air-cooled condenser according to claim 4, further comprising a horizontally aligned second row of vertical heat exchange tubes, the tubes in the second row each fluidly coupled to the top and bottom pipes by respective upper and lower feeder pipes oriented parallel to the upper and lower feeder pipes of the first row of tubes.

19. The air-cooled condenser according to claim 1, wherein the shell of the air-cooled condenser has a rectangular cuboid form with rectilinear transverse cross section.

20. The air-cooled condenser according to claim 1, wherein the shell further comprises a plurality of laterally open air entry windows arranged between the top and bottom ends of the shell to draw ambient cooling air transversely through the tubes into the internal cavity.

21. The air-cooled condenser according to claim 20, further comprising a blower disposed in the internal cavity at the top end of the shell, the blower operable to draw ambient cooling air into the internal cavity from the bottom end and air entry windows, and discharge the ambient cooling air through the top end.

22. The air-cooled condenser according to claim 21, wherein steam flows from the top header pipe downward through the tubes, exchanges heat with the ambient cooling air to condense the steam, and the steam condensate is collected in the bottom header pipe from the tubes.

23. The air-cooled condenser according to claim 1, wherein: each of the heat exchanger vertical tubes comprises a first finned tube section comprising a first plurality of vertically-extending external longitudinal fins protruding radially outward from an outer surface of the tube, and a second finned tube section comprising a second plurality of vertically-extending external longitudinal fins protruding radially outward from the outer surface of the tube; wherein the first finned tube section and the second finned tube section are discrete structural elements; wherein a first end of the first finned section is abutted to a second end of the second finned tube section; and the discrete first finned tube section and the second finned tube section arranged and rotated relative to each other so that the first and second plurality of longitudinal fins are angularly offset from one another.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0022] The present invention will become more fully understood from the detailed description and the accompanying drawings, wherein:

[0023] FIG. 1 is a schematic of a prior art air-cooled condenser unit;

[0024] FIG. 2 is a perspective view of an extruded find tube section according to an embodiment of the present invention;

[0025] FIG. 3 is a transverse cross-section of the extruded find tube section of FIG. 2 taken along view III-III;

[0026] FIG. 4 is a perspective view of three finned tubes, each of the finned tubes formed by a plurality of the finned tube sections of FIG. 2 according to an embodiment of the present invention;

[0027] FIG. 5 is a schematic of an air-cooled condenser comprising a tube bundle assembly according to an embodiment of the present invention positioned within a shell and coupled to a source of steam generated in a Rankine cycle of a power generation plant;

[0028] FIG. 6 is a top view of the air-cooled condenser of FIG. 5 wherein multiple tube bundle assemblies are shown coupled to an inlet manifold at a single point or juncture;

[0029] FIG. 7 is a perspective view of a shell according to an embodiment of the present invention;

[0030] FIG. 8 is a perspective view of an inner tube being slid into two finned tube sections during an initial step of a finned tube formation method according to another embodiment of the present invention;

[0031] FIG. 9 is a perspective view of the inner tube extending through the two finned tube sections during a subsequent step of a finned tube formation method according to another embodiment of the present invention; and

[0032] FIG. 10 is a transverse cross-section of the finned tube assembly of FIG. 9 taken along view X-X, wherein the inner tube has not yet been expanded.

DETAILED DESCRIPTION OF THE DRAWINGS

[0033] The following description of the illustrated embodiment(s) is merely exemplary in nature and is in no way intended to limit the invention, its application, or uses.

[0034] Referring first to FIGS. 2 and 3 concurrently, a finned tube section 100A according to an embodiment of the present invention is exemplified. The finned tube section 110A extends from a first end 115A to a second end 116A along a longitudinal axis A-A. In the exemplified embodiment, the finned tube section 100A is an elongated tubular structure that is substantially linear and particularly suitable for creating a vertical tube bundle for an air-cooled condenser of a power generation plant. As discussed below, in certain embodiments, a plurality of the finned tube sections 100A can be formed and coupled together in axial alignment to form a single finned tube. In one such embodiment, the finned tube sections 100A have a length between 4 to 8 feet and are installed vertically in such sections. The invention, however, is not so limited and, in certain embodiment, the finned tube section 100A can be formed of a sufficient length such that a single finned tube section 100A forms a single finned tube. In such an embodiment, the first end 115A of the finned tube section 100A will be the top end of the finned tube while the second end 116A of the finned tube section 100A will be the bottom end of the finned tube (or vice versa). As discussed below, the finned tube section 100A is a heat exchange tube in that it effectively transfers thermal energy from a tube-side fluid, such as steam, that is flowing inside of the finned tube section 100A to a shell-side fluid, such as air, that is flowing adjacent the finned tube section 100A on the exterior thereof.

[0035] The finned tube section 100A generally comprises a tube 110A and a plurality of fins 111A extending radially outward from the tube 110A. The tube 110A comprises an inner surface 112A that forms a cavity 113A and an outer surface 114A from which the plurality of fins 111A protrude/extend. The cavity 113A extends along a longitudinal axis A-A. In certain embodiments (i.e., embodiment in which an inner tube is not needed), the cavity 113A acts as a tube-side fluid path in which the inner surface 112A is exposed to the tube-side fluid. In embodiments in which an inner tube is used (described later with respect to FIGS. 8-11), the tube 110A can be considered an outer tube, the inner surface 112A of which is not exposed to the tube-side fluid (such as steam generated in a Rankine power cycle). In the exemplified embodiment, the tube 110A has a substantially circular transverse cross-section.

[0036] The tube 110A also comprises an outer surface 114A. The plurality of fins 111A protrude radially outward from the outer surface 114A of the tube 110A. In one embodiment, the finned tube section 100A is formed by an extrusion process. As a result, the plurality of fins 111A are integral with the tube 110A. More specifically, in one such embodiment, both the tube 110A and the plurality of fins 11A are simultaneously formed in a single extrusion process using a first material, such as an extrudable metal or metal alloy. In one specific embodiment, the finned tube section 100A (including both the plurality of fins 111A and the tube 110A) are formed of a material having a coefficient of thermal conductivity. Suitable materials include, for example, aluminum or aluminum alloy. The utilization of an extruded finned tube section 100A allows for the compaction and simplification of the overall heat exchanger, as compared with the state of the art cross flow designs.

[0037] While forming the entirety of the finned tube section 100A by a single extrusion step is preferred in certain embodiments, the invention is not so limited in other embodiments. In certain other embodiments, the tube 110A may be extruded in one step and the fins 11A may be extruded subsequently or prior thereto during a separate step, and then subsequently coupled (directly or indirectly) to the tube 110A through brazing, welding, thermal fusion, mechanical coupling, or other processes. In still other embodiments, the tube 110A and the fins 111A can be formed separately by techniques other than extrusion, such as machining, bending, pressing, die-cutting, stamping, and/or combinations thereof.

[0038] In the exemplified embodiment, each of the plurality of fins 111A extends substantially parallel with the longitudinal axis A-A and covers the entire length of the tube 110A, wherein the length is measured from the first end 115A to the second end 116A. Moreover, each of the plurality of fins 111A extends radially outward from the outer surface 114A of the tube 110A in a linear fashion from a base portion 117A to a distal end 118A. The base portions 117A can be thicker than the remaining portions of the fins 11A, thereby promoting stability and conductive heat transfer into the fins 111A. In the illustrated embodiment, the fins 111A are linear in their longitudinal extension. However, in alternate embodiments, the fins 111A may be extruded or otherwise formed with an undulating (wave) geometry to promote heat transfer.

[0039] As can best be seen in FIG. 3, the plurality of fins 111A are arranged about the circumference of the outer surface 114A of the tube 110A at uniform angular intervals. In the illustrated embodiment, the twenty four (24) fins 111A are provided on the tube 110A so that an angular interval of approximately 15 exists between adjacent fins 111A. Of course, the exact number of fins 111A, along with the angular spacing between them can vary as needed. For example, depending on the diameter of the tube 110A and the heat duty demand, the number and height of the radial fins 111A can be selected. The tube 110A can have as many radial fins 111A as the state of the art extrusion technology will allow. In one exemplary embodiment, providing 24 fins 111A on a 1.5 inch nominal ID tube 110A, wherein each fin 111A is 1.5 inch high has been determined to be feasible. A larger number of fins may be achieved if a larger size tube is selected.

[0040] Referring now to FIG. 4, the formation of a finned tube 200 using a plurality of the finned tube sections 100A-B according to an embodiment of the present invention will be described. FIG. 4 illustrates three of these finned tubes 200, which are identical for the formation and structural purposes described herein, despite their different functionality when incorporated into a tube bundle. The arrows indicating steam flow in the finned tubes 200 results from the arrangement shown in FIGS. 5-6, which will be described later in this document. For purposes of simplicity, only one of the finned tubes 200 will be described with the understanding that the discussion is applicable to all of the finned tubes 200 in FIG. 4 and/or used to form a tube bundle according to the present invention.

[0041] As exemplified, the finned tube 200 comprises two finned tube sections 100A, 100B. Finned tube section 100A is described above with reference to FIGS. 2-3, and is referred to herein as a first finned tube section 100A. Finned tube section 100B (only a portion of which is shown in FIG. 4) is identical to finned tube section 100A in all aspects but is either subsequently or previously formed using one of methods discussed above. The finned tube section 100B is referred to herein as the second finned tube section 100B. Like numbers are used to like parts of the first and second finned tube sections 100A, 100B with the exception that the suffix B is used to denote the parts of the second finned tube section 100B rather than the suffix A, which is used in FIGS. 2-3 to describe the first finned tube section 100A.

[0042] As mentioned above, the finned tube 200 comprises a first finned tube section 100A and a second finned tube section 100B arranged in axial alignment. The first finned tube section 100A and the second finned tube section 100B are aligned adjacent one another so that the longitudinal axes A-A of the first and second finned tube sections 100A, 100B are substantially aligned and coaxial. When so aligned, the first end 115B of the second tube 110B of the second finned tube section 100B abuts the second end 116A of the first tube 110A of the first finned tube section 100A.

[0043] While the first and second finned tube sections 100A, 100B are aligned so that their longitudinal axes A-A are aligned, the first and second finned tube sections 100A, 100B (which are adjacent finned tube sections in the finned tube 200) are rotated relative to one another so that corresponding ones of their fins, 111A, 111B are angularly offset from one another. This can improve heat transfer from the tube-side fluid (e.g., steam) to the shell-side fluid (e.g., air). The angular offset, in one embodiment is 1 to 20. In another embodiment, the angular offset is 5 to 10.

[0044] This concept will be described below with respect to an example to ensure understanding. Assume that the first finned tube section 100A was placed in proper alignment and position in an angular/rotational position in which one of its fins 111A were angularly located at each of the cardinal points (N, S, E, & W). The second finned tube section 100B would then be position in axial alignment with the first finned section 100A in an angular/rotational position in which none of its fins 111B were located at the cardinal points. Rather, the second finned section 100B would be in an angular/rotational position in which one of its fins 111B is offset from each of the cardinal points by the angular offsets described above, such as for example 5 to 10. In alternate embodiments, however, the fins 111A, 111B of the first and second finned sections 100A, 100B may be angularly aligned if desired.

[0045] Once the first finned tube section 100A and second finned tube section 100B are aligned and rotationally oriented as described above, the first and second finned tube sections 100A, 100B are coupled together, thereby forming the finned tube 200. The exact technique used to couple, either directly or indirectly, the first finned tube section 100A and second finned tube section 100B together will depend on the material(s) of which the first finned tube section 100A and second finned tube section 100B are constructed. Suitable connection techniques include mechanical fastening in which gaskets or other materials can be used achieve a hermetic interface, welding, brazing, thermal fusing, threaded connection, use of a coupler sleeve, a tight-fit connection, and/or combinations thereof. As described below with respect to FIGS. 8-10, coupling of the first and second finned tube sections 100A, 100B can also be accomplished using an inner tube.

[0046] While the finned tube 200 is exemplified as having only two finned tube sections 100A, 100B, the finned tube 200 can be formed of more or less finned tube sections 100A as desired. In embodiments of the finned tube 200 in which more than two finned tube sections 100A, 100B are used, the aforementioned rotational offset can be implemented between each pair of adjacent finned tube sections.

[0047] Referring now to FIG. 5, an air-cooled condenser 1000 according to an embodiment of the present invention is illustrated. The air-cooled condenser 1000 is a true counter-current/parallel flow air-cooled condenser that, in one embodiment, is constructed with the finned tubes 200 formed of extruded aluminum or aluminum alloy finned tube section 100A, 100B in a vertical array (or matrix) configuration.

[0048] The air-cooled condenser 1000 generally comprises a shell 300 and a tube bundle assembly 400. The tube bundle assembly 400 is positioned within an internal cavity 301 of the shell 300. The shell 300 has an open top end 302 and an open bottom end 303 As a result, cool air can flow into the open bottom end 302, flow through the internal cavity 301 where it flows adjacent the finned tubes 200 and becomes warmed, and exists the shell 300 as warmed air. A blower 304, in the form of a fan or other mechanism capable of inducing air flow, can be provided either above and/or below the tube bundle assembly 400. While a single blower 304 is illustrated, more blowers can be implemented as desired to meet functional demands. In other embodiments, the blower may be omitted.

[0049] The tube bundle assembly 400 generally comprises a tube bundle 500 formed by a plurality of the finned tubes 200, a top header pipe 410, a bottom header pipe 420, and a plurality of feeder pipes 430. Each of the plurality of the finned tubes 200 of the tube bundle 500 are oriented in a substantially vertical orientation so that the longitudinal axes A-A (FIG. 2) thereof extend substantially vertical. The finned tubes 200 of the tube bundle 500 may be arrayed in a triangular, rotated triangular, rectangular or another suitable layout that provides for a uniformly distributed flow area across the tube bundle. In the exemplified embodiment, the finned tubes 200 of the tube bundles 500 are arrayed in 35 rectangular arrays (see FIG. 6). A desired feature of the tube bundle layout geometry is the ability to make a closely packed bundle of the finned tubes 200 such that the air flowing axially along the finned tubes 200 is in close proximity to the finned tubes' 200 outer surfaces. Factory assembled modules can be delivered and connected into the steam distribution network of a Rankine cycle fluid circuit of a power generation planet, thereby providing an economical heat rejection alternative for small and large scale applications.

[0050] Each of the finned tubes 200 of the tube bundle 500 is coupled to and fed steam from the top header pipe 410, which is in turn operably coupled to a source of steam, such as turbine in a Rankine cycle power generation circuit. Similarly, each of the finned tubes 200 of the tube bundle 500 is coupled to the bottom header pipe 420 so that condensate can gather and be fed back into the Rankine cycle fluid circuit of the power generation plant. In the exemplified embodiment, a top end 201 of each of the finned tubes 200 of the tube bundle 500 is fluidly coupled to the top header pipe 410 by a separate upper feeder pipe 430. Similarly, a bottom end 202 of each of the finned tubes 200 of the tube bundle 500 is fluidly coupled to the bottom header pipe 420 by a separate lower feeder pipe 430. As a result, a hermetic fluid path is formed through the cavity 113A (FIG. 2) of each of the finned tubes 200 from the inlet header cavity 411 of the top header pipe 410 to the outlet header cavity 421 of the bottom header pipe 420. The top header pipe 410 is located at an elevation that is greater than the elevation at which the bottom header pipe 420 is located. The top header pipe 410 and the upper feeder pipes 430 can be collectively considered a top network of pipes 470 while the bottom header pipe 420 and lower feeder pipes 430 can be collectively considered a bottom network of pipes 480.

[0051] The top header pipe 410 extends along a longitudinal axis B-B (FIG. 5) that is substantially horizontal. Similarly, the bottom header pipe 420 also extends along a longitudinal axis that is substantially horizontal. In other embodiments, the top and bottom header pipes 410, 420 may be inclined.

[0052] The top header pipe 410 is located above the tube bundle 500 while the bottom header pipe 420 is located below the tube bundle 500. The top and bottom header pipes 410, 420, however, are specifically designed so as to create minimal impedance and/or obstruction to the vertical flow of air entering and exiting the tube bundle 500. In order to accomplish this, each of the top and bottom header pipes 410, 420 is designed to have a transverse cross-section having a major axis A.sub.MAJ and a minor axis A.sub.MIN. Moreover, each of the top and bottom header pipes 410, 420 is oriented so that the minor axis A.sub.MIN extends substantially perpendicular to the direction of the air flow through the tube bundle 500. Thus, in the exemplified embodiment, the minor axis A.sub.MIN extends substantially horizontal while the major axis A.sub.MAJ extend substantially vertical. The major axis A.sub.MAJ has a length that is larger than the length of the minor axis A.sub.MIN for both the top and bottom header pipes 410, 420. In one such embodiment, the major axis A.sub.MAJ has a length that is at least twice the length of the minor axis A.sub.MIN for both the top and bottom header pipes. By designing and orienting the transverse cross-sections of the top and bottom header pipes 410, 420 to have the aforementioned major axis A.sub.MAJ and minor axis A.sub.MIN, the top and bottom header pipes 410, 420 achieve two criteria: (1) adequate flow area for the tube side fluid; and (2) maximum opening between the adjacent headers to minimize friction loss to the entering (bottom header) and exiting (top header) air (see FIG. 6 also). While not visible from the drawings, each of the horizontal sections of the feeder pipes 430 may also be designed to have a transverse cross-section comprising a major axis A.sub.MAJ and a minor axis A.sub.MIN, and be oriented, as discussed above and below with respect to the top and bottom headers 410, 420.

[0053] In one embodiment, the top and bottom header pipes 210, 220 (along with the horizontal sections of the feeder pipes 430) each have an obround transverse cross-section. The obround shape allows for a large internal flow area for steam while affording ample space for the air to enter and exit the tube bundle 500 via spaces between the header pipes 410, 420 (and horizontal sections of the feed pipes 430). The obround transverse cross section with the flat (long) sides vertical is a preferred arrangement when the tube side fluid is low pressure steam or vapor. As mentioned above, the top header pipe 510 serves as the inlet for the vapor (exhaust steam) (see FIG. 3 for a typical inlet header profile).

[0054] As can be seen in FIG. 6, the air-cooled condenser can comprises a plurality of tube bundles 500 housed in separate shells 300. In other embodiments, more than one tube bundle 500 can be housed in a single shell 300. All of the inlet header pipes 410 are preferably manifolded from a single point 450 of a main steam supply line 440. Furthermore, each of the tube bundles 500, along with the shell 300 may be positioned atop a fan deck, which is in turn positioned atop a frame structure (as shown in FIG. 1).

[0055] Referring back to FIG. 5, the up flowing cooling air may be sprayed with a mist of coolant generated by spray nozzles 550 located within the shell 300 at a height between the top header pipe 410 and the bottom header pipe 420. The spray nozzles 550 are operably and fluidly coupled to coolant reservoirs 551 and further configured to atomize the liquid coolant into a fine mist that is introduced into the air flowing through the tube bundles 500. Spaying the mist into the air flow at intermediate height(s) increases the LMTD and promotes heat rejection from the tube side fluid (i.e. the steam). This form of cooling augmentation is unique to this heat exchanger design and results in substantial performance gains of 25 to 30% depending on the ambient conditions. These performance gains can be realized in improved warm weather performance or capital cost reduction and smaller plot area constraints.

[0056] Referring now to FIG. 7, a housing 300 suitable for use in the air-cooled condenser 1000 of FIGS. 5 and 6 is illustrated. Depending on the available height, a chimney space 305 above the bundle can be incorporated in the unit to increase the natural draft height. This will reduce the amount of electrical energy required to pump the cooling air through the bundle. In designs where the blower 304 is located above the tube bundle 500, it is possible to provide for additional entry windows 310 for air to enter the tube bundle 500, which will promote increased heat transfer from the tube-side fluid.

[0057] Referring now to FIGS. 8-10, an alternative construction of the finned tube 2000 is described in which the final finned tube 2000 comprises the finned tube sections 100A, 100B and an inner tube 700. Such an arrangement is particularly useful in power plants where the condensing steam is not permitted to come in contact with aluminum or aluminum alloy of the finned tube sections 100A, 100B. The finned tube 2000 can be sued in the air-cooled condenser 1000 described above in lieu of or in addition to the finned tubes 200.

[0058] Referring first to FIG. 8, the first and second finned tube sections 100A, 100B are formed, aligned and oriented as described above with respect to FIGS. 2-4. Once this is done, an inner tube 700 is provided and axially aligned with the cavities 113A, 113B of the first and second finned tube sections 100A, 100B along a longitudinal axis C-C. The inner tube 700 is formed of a material that is different than the material of which the first and second finned tube sections 100A, 100B are formed. In one embodiment, the inner tube 700 is formed of a material having a high yield strength, is non-corrosive, and is weldable. A suitable material includes steels, with stainless steel being preferred.

[0059] The inner tube 700 extends along an axis has an outer surface 702 and inner surface 701, which forms cavity 703. The inner tube 700 extends from a bottom end 705 to a top end 704 along the longitudinal axis C-C.

[0060] Referring now to FIGS. 9 and 10 concurrently, the inner tube 700 is then slid through the cavities 113A, 113B of the finned tube sections 100A, 100B. In the exemplified embodiment, the top end 704 of the inner tube 700 protrudes slightly from the top end of the first finned tube section 100A while the bottom end 705 of the inner tube 700 protrudes slightly from the bottom end of the second finned tube section 100B (FIG. 9). At this stage, the outer diameter of the inner pipe 700 is smaller than the inner diameter of the tubes 110A, 110B. As a result, a interstitial space 750 exists between the outer surface 702 of the inner tube 700 and the inner surfaces 112A, 112B of the tubes 110A, 110B.

[0061] Once the inner tube 700 is so positioned, the inner tube 700 is diametrically expanded by applying a force F. Diametric expansion of the inner tube can be achieved by a variety of methods, including hydraulic pressure.

[0062] The diametric expansion of the inner tube 700 continues until the outer surface 702 of the inner tube 700 is in substantially conformal surface contact with the inner surfaces 112A, 112B of the finned tube sections 100A, 100B, thereby forming the finned tube 2000. As a result the interstitial space 750 disappears and there are substantially no gaps and/or voids between the outer surface 702 of the inner tube 700 and the inner surfaces 112A, 112B of the finned tube sections 100A, 100B. In embodiments using the inner tube 700, the tubes 110A, 110B can be considered outer tubes.

[0063] The inner tube 700 couples the finned tube sections 100A, 100B together and thus can be used instead of or in conjunction with the other coupling techniques discussed above for FIG. 4. When the resulting finned tube 2000 is incorporated into the air-cooled condenser 1000, the inner tube 700 can be sued to make the welded joints between the top pipe network 470 and/or the bottom pipe network 460, as shown in FIG. 5. Additionally, when the inner tube 700 is used, the first and second inner tubes 100A, 100B do not have to be in abutment to effectuate coupling. Because the inner tube 700 (in contact with the condensing steam) is at a higher temperature than the finned tube sections 110A, 100B, the risk of the inter-tube interface becoming loose during service is ameliorated.

EXAMPLE

[0064] Comparison of a conventional (inclined bundle) air-cooled condenser (FIG. 1) and an air-cooled condenser according to the present invention is set forth below in the following table for the performance of the two design concepts:

TABLE-US-00001 Conventional Percent A-Frame ACC HI-VACC Difference Thermal Duty, mmBtu/hr 860 860 Condensing Pressure, HgA 2.0 2.0 Ambient Air Temperature, F. 60 60 Number of Cells Required 20 12 40% ACC Plot Area (L W), ft 238 170 240 80 53% ACC Height, ft 104 79 24% Total Extended Heat Transfer 8,919,200 7,977,250 10% Surface, ft.sup.2 Total Fan Shaft Power, kW 2700 2700

[0065] The design concepts disclosed herein can be used in a wide variety of coolers that seek to employ air as the cooling medium. Its application to design air cooled condensers to condense exhaust steam in power plants will lead to reduced cost and reduced land area requirement. Additional advantages of the present invention are: (1) modular installation; (2) reduced site construction effort compared to the A-frame design; (3) significantly reduced quantity of structural steel required to erect the system; and (4) ability to reduce fan power consumption by adding an exhaust stack (chimney) to the design.

[0066] As used throughout, ranges are used as shorthand for describing each and every value that is within the range. Any value within the range can be selected as the terminus of the range. In addition, all references cited herein are hereby incorporated by referenced in their entireties. In the event of a conflict in a definition in the present disclosure and that of a cited reference, the present disclosure controls.

[0067] While the invention has been described with respect to specific examples including presently preferred modes of carrying out the invention, those skilled in the art will appreciate that there are numerous variations and permutations of the above described systems and techniques. It is to be understood that other embodiments may be utilized and structural and functional modifications may be made without departing from the scope of the present invention. Thus, the spirit and scope of the invention should be construed broadly as set forth in the appended claims.