TURBINE EXHAUST DUCT DESIGN FOR AIR COOLED CONDENSERS

Abstract

A double turbine exhaust duct design and an inline V turbine exhaust duct design that both eliminate the need for the standard T-piece in a turbine exhaust duct assembly, substantially reducing the steam-side pressure drop, minimizing the sub-cooling in the steam cycle (the temperature difference between ACC condensate temperature out and turbine steam temperature), thus improving the overall efficiency of the steam cycle plant heat rate.

Claims

1. A turbine exhaust duct assembly configured to provide steam to a field-assembled air-cooled condenser having a plurality of parallel condenser section streets, said turbine exhaust duct assembly comprising a first set of two or more turbine exhaust ducts configured to receive steam from a turbine, directly or indirectly, and to approach said air cooled condenser substantially parallel to one-another and to said streets of said air cooled condenser, a second set of two or more turbine exhaust ducts configured to run approximately perpendicular to said streets of said air cooled condenser, each said turbine exhaust duct in said second set configured to receive steam from a single turbine exhaust duct in said first set of turbine exhaust ducts via an exhaust duct elbow unit, wherein said second set of two or more turbine exhaust ducts are each connected to one or more riser duct assemblies, each of which are configured to supply steam to a single street of said air cooled condenser.

2. (canceled)

3. (canceled)

4. (canceled)

5. A turbine exhaust duct assembly according to claim 1, wherein said turbine exhaust duct assembly has reduced steam-side pressure drop, reduced temperature differences between the air cooled condenser condensate temperature out and turbine steam temperature, and which operates at increased efficiency, as compared to an air-cooled condenser supplied by a single turbine exhaust duct assembly including a three-port T-piece.

6. A method for substantially reducing steam-side pressure drop, minimizing sub-cooling in the steam cycle, and improving steam cycle plant heat rate of an air-cooled condenser system, comprising delivery of spent plant steam to an air cooled condenser using the turbine exhaust duct assembly of claim 1.

7. A method of reducing required size of an air cooled condenser for a specified plant steam output, comprising delivery of spent plant steam to an air cooled condenser using the turbine exhaust duct assembly of claim 1.

8. A method for lowering the fan horsepower requirements of an ACC, comprising delivery of spent plant steam to an air cooled condenser using the turbine exhaust duct assembly of claim 1.

9. A method for facilitating de-aeration of a steam condensate, reducing corrosion in the steam cycle and for increasing the life of a power plant, comprising delivery of spent plant steam to an air cooled condenser using the turbine exhaust duct assembly of claim 1.

10. (canceled)

11. A turbine exhaust duct assembly according to claim 1, wherein said first set of two or more turbine exhaust ducts approach said field-assembled air-cooled condenser between a first riser and a second riser parallel to one-another, parallel to a longitudinal axis of streets of said air-cooled condenser, and perpendicular to said second set of two or more turbine exhaust ducts.

Description

DESCRIPTION OF THE DRAWINGS

[0022] The subsequent description of the preferred embodiments of the present invention refers to the attached drawings, wherein:

[0023] FIG. 1 is a perspective schematic view of a prior art air cooled condenser (ACC) turbine exhaust duct including T-piece with guide vanes.

[0024] FIG. 2 is a perspective schematic view of a prior art air cooled condenser (ACC) turbine exhaust duct for a two-street ACC including T-piece with guide vanes.

[0025] FIG. 3 is a reverse perspective schematic view of a prior art air cooled condenser (ACC) turbine exhaust duct shown in FIG. 2.

[0026] FIG. 4 shows arcuate shell plates used to assemble a prior art turbine exhaust duct and T-Piece, stacked on a shipping palette.

[0027] FIG. 5 shows arcuate shell plates welded to one-another into annular sections, which in turn are stacked on top of one-another and welded to form a prior art turbine exhaust duct, in vertical assembly orientation.

[0028] FIG. 6 shows a partially assembled T-piece, including guide vanes.

[0029] FIG. 7 shows another partially assembled T-piece.

[0030] FIG. 8 is a perspective schematic view of an embodiment of a double duct turbine exhaust duct design according to an embodiment of the invention.

[0031] FIG. 9 is a perspective schematic view of an embodiment of an inline V turbine exhaust duct design according to an embodiment of the invention.

[0032] FIG. 10 is another perspective schematic view of the inline V turbine exhaust duct design shown in FIG. 9.

[0033] FIG. 11 is a perspective schematic view of a round to oval reducer for use with an inline V turbine exhaust duct.

[0034] FIG. 12 is a reverse perspective schematic view of the round to oval reducer shown in FIG. 11.

[0035] FIG. 13 is a perspective schematic view of an embodiment of an inline V turbine exhaust duct design in which the sloping risers may be bifurcated to supply more than a single street of the air cooled condenser.

DETAILED DESCRIPTION OF THE INVENTION

[0036] In the following description, numerous details are set forth to provide a more thorough explanation of the present invention. It will be apparent, however, to one skilled in the art, that the present invention may be practiced without these specific details.

[0037] FIG. 8 shows a double duct turbine exhaust duct system according to an embodiment of the invention. Prior art turbine exhaust systems approach an industrial air cooled condenser with a single duct and then divide the steam exhaust in opposite directions using a large and complicated T-piece fitted with guide vanes, see, e.g., FIGS. 1-3. In contrast, FIG. 8 shows an embodiment of the invention in which the steam exhaust either leaves the turbine or turbine transition piece in two separate streams or is divided into two separate streams shortly after it leaves the turbine transition piece. Each exhaust stream then separately approaches the ACC in its own turbine exhaust duct, and then is turned, without splitting, to flow perpendicular to the ACC streets before being directed up the riser streets. According to the embodiment shown in FIG. 8, each turbine exhaust duct turns 90, but the angle of the bend and the corresponding elbow piece can vary according to system/layout requirements anywhere from anywhere from 0 (straight through, no bend) up to 90 or even more than 90.

[0038] According to an additional advantage of this embodiment, the size of the exhaust tubes may be reduced by as much as 50% making it feasible to ship circumferentially assembled ducts to the final assembly location, significantly reducing the amount of field assembly and welding required. That is, instead of delivering many individual shell plates to make into a single run of TED (Turbine Exhaust Duct) and T piece at the site, embodiments of the invention provides the alternative of providing two circumferentially whole ducts. While the shipping of circumferentially assembled turbine exhaust ducts to the final assembly location requires break bulk load shipping, resulting in increased shipping costs, as well as increased manufacturing costs due to the shift of welding from the field to the factory, the elimination of significant field assembly and welding, and attendant difficulties, may be sufficient in some cases to offset the additional costs.

[0039] FIG. 9 shows an alternative embodiment according to which a single turbine exhaust duct is diverted directly into a V-piece, featuring two sloping risers, eliminating the T-piece as well as the horizontal transfer tubes shown in FIGS. 2 and 3. Turning vanes are shop installed in the bottom of the riser elbows, and the complete elbows are delivered whole. According to this embodiment, a round-to-oval reducer element may be provided between the primary turbine exhaust duct and the elbows leading to the sloping risers. The round-to-oval reducer splits the exhaust flow in the single turbine exhaust duct into two parallel exhaust streams. The round-to-oval reducer is connected directly or indirectly to two elbow pieces, each of which is joined to a sloping riser duct. With the round-to-oval reducer, the turbine exhaust duct can be delivered in many fewer pieces; it is much lighter, and there is far less field assembly and welding as compared to the traditional intricate T piece design.

[0040] According to both the double-duct and V-shaped duct embodiments described above, the requirement for the T-shaped piece with the complicated guide vane system is eliminated. According to both designs, the overall assembly has fewer parts, is lighter in weight, and will be less expensive to supply and ship. The present designs also result in less field labor required to unload, handle, assemble and weld the turbine duct assemblies as it is delivered in fewer pieces, and reduces the amount of field welding required, reducing the amount of welding sets and welding consumables required at the site. The invention also reduces the risk and exposure to poor quality welding and poor labor efficiency at site. There will also be a resultant reduction of inspection costs as there will be many fewer field welds that need to be inspected. The new designs will, in addition, require less access scaffolding and scissor/JLG lifts. These changes all translate into a much reduced installed cost at site.

[0041] Additionally, by eliminating the T-shaped piece, the steam-side pressure drop is significantly reduced, minimizing the sub-cooling in the steam cycle, that is, the temperature difference between the ACC condensate temperature and the turbine steam temperature. This results in an improvement in the overall efficiency of the steam cycle plant heat rate. In addition, the reduction in steam side pressure drop also results in smaller ACCs and/or lower fan horsepower requirements on the ACC. The former results in lower capital investment costs; the latter results in lower plant operating costs. The reduced sub-cooling also facilitates an easier de-aeration of the condensate. This reduces the corrosion in the complete steam cycle, resulting in an increase in the overall life of the power plant.