US20150322928A1

US20150322928A1 - Ocean Thermal Energy Conversion Cold Water Pipe

Info

Publication number: US20150322928A1
Application number: US14/802,474
Authority: US
Inventors: Andrew Rekret; Henry Sibenaller; William Schulz
Original assignee: Abell Foundation Inc
Current assignee: Abell Foundation Inc
Priority date: 2010-01-21
Filing date: 2015-07-17
Publication date: 2015-11-12
Also published as: US9086057B2; US20110173978A1

Abstract

An offshore power generation structure comprising a submerged portion having heat exchange sections, power generation sections, a cold water pipe and a cold water pipe connection. The cold water pipe comprises a plurality of offset first and second staved portions.

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a continuation application of and claims priority to U.S. application Ser. No. 12/691,655, filed on Jan. 21, 2010. The entire contents of the related application is hereby incorporated by reference.

TECHNICAL FIELD

This invention relates to ocean thermal energy conversion power plants and more specifically to floating, minimum heave platform, multi-stage heat engine, ocean thermal energy conversion power plants.

BACKGROUND

Energy consumption and demand throughout the world has grown at an exponential rate. This demand is expected to continue to rise, particularly in developing countries in Asia and Latin America. At the same time, traditional sources of energy, namely fossil fuels, are being depleted at an accelerating rate and the cost of exploiting fossil fuels continues to rise. Environmental and regulatory concerns are exacerbating that problem.
Solar-related renewable energy is one alternative energy source that may provide a portion of the solution to the growing demand for energy. Solar-related renewable energy is appealing because, unlike fossil fuels, uranium, or even thermal “green” energy, there are few or no climatic risks associated with its use. In addition, solar related energy is free and vastly abundant.
Ocean Thermal Energy Conversion (“OTEC”) is a manner of producing renewable energy using solar energy stored as heat in the oceans' tropical regions. Tropical oceans and seas around the world offer a unique renewable energy resource. In many tropical areas (between approximately 20° north and 20° south latitude) the temperature of the surface sea water remains nearly constant. To depths of approximately 100 ft the average surface temperature of the sea water varies seasonally between 75° F. and 85° F. or more. In the same regions, deep ocean water (between 2500 ft and 4200 ft or more) remains a fairly constant 40° F. Thus, the tropical ocean structure offers a large warm water reservoir at the surface and a large cold water reservoir at depth, with a temperature difference between the warm and cold reservoirs of between 35° F. to 45° F. This temperature difference remains fairly constant throughout the day and night, with small seasonal changes.
The OTEC process uses the temperature difference between surface and deep sea tropical waters to drive a heat engine to produce electrical energy. OTEC power generation was identified in the late 1970′s as a possible renewable energy source having a low to zero carbon footprint for the energy produced. An OTEC power plant, however, has a low thermodynamic efficiency compared to more traditional, high pressure, high temperature power generation plants. For example, using the average ocean surface temperatures between 80° F. and 85° F. and a constant deep water temperature of 40° F., the maximum ideal Carnot efficiency of an OTEC power plant will be 7.5 to 8%. In practical operation, the gross power efficiency of an OTEC power system has been estimated to be about half the Carnot limit, or approximately 3.5 to 4.0%. Additionally, analysis performed by leading investigators in the 1970's and 1980's, and documented in “Renewable Energy from the Ocean, a Guide to OTEC” William Avery and Chih Wu, Oxford University Press, 1994 (incorporated herein by reference), indicates that between one quarter to one half (or more) of the gross electrical power generated by an OTEC plant operating with a AT of 40° F. would be required to run the water and working fluid pumps and to supply power to other auxiliary needs of the plant. On this basis, the low overall net efficiency of an OTEC power plant converting the thermal energy stored in the ocean surface waters to net electric energy has not been a commercially viable energy production option.
An additional factor resulting in further reductions in overall thermodynamic efficiency is the loss associated with providing necessary controls on the turbine for precise frequency regulation. This introduces pressure losses in the turbine cycle that limit the work that can be extracted from the warm sea water. The resulting net plant efficiency would then be between 1.5% and 2.0%.
This low OTEC net efficiency compared with efficiencies typical of heat engines that operate at high temperatures and pressures has led to the widely held assumption by energy planners that OTEC power is too costly to compete with more traditional methods of power production.
Indeed, the parasitic electrical power requirements are particularly important in an OTEC power plant because of the relatively small temperature difference between the hot and cold water. To achieve maximum heat transfer between the warm sea water and the working fluid, and between the cold sea water and the working fluid large heat exchange surface areas are required, along with high fluid velocities. Increasing any one of these factors can significantly increases the parasitic load on the OTEC plant, thereby decreasing net efficiency. An efficient heat transfer system that maximizes the energy transfer in the limited temperature differential between the sea water and the working fluid would increase the commercial viability of an OTEC power plant.
In addition to the relatively low efficiencies with seemingly inherent large parasitic loads, the operating environment of OTEC plants presents design and operating challenges that also decrease the commercial viability of such operations. As previously mentioned, the warm water needed for the OTEC heat engine is found at the surface of the ocean, to a depth of 100 ft or less. The constant source of cold water for cooling the OTEC engine is found at a depth of between 2700 ft and 4200 ft or more. Such depths are not typically found in close proximity to population centers or even land masses. An offshore power plant is required.
Whether the plant is floating or fixed to an underwater feature, a long cold water intake pipe of 2000 ft or longer is required. Moreover, because of the large volume of water required in commercially viable OTEC operations, the cold water intake pipe requires a large diameter (typically between 6 and 35 feet or more). Suspending a large diameter pipe from an offshore structure presents stability, connection and construction challenges which have previously driven OTEC costs beyond commercial viability.
Additionally, a pipe having significant length to diameter ratio that is suspended in a dynamic ocean environment can be subjected to temperature differences and varying ocean currents along the length of the pipe. Stresses from bending and vortex shedding along the pipe also present challenges. And surface influences such as wave action present further challenges with the connection between the pipe and floating platform.
An enormous challenge of OTEC operations has been the need to fully assemble a pipe having a length of 2000 ft to 4000 ft or more and transporting such a pipe to the operational site. Furthermore, a greater challenge has been upending such a pipe for installation to a floating platform and ultimately making a connection to the platform.
Previous OTEC cold water pipe construction has used segmented pipes. A segmented pipe is a pipe constructed of cylindrical segments joined together in series to the obtain the desired length. Segmented pipes are disclosed in “Ocean Thermal Energy Conversion Cold Water Pipe Preliminary Design Project,” TRW Energy Systems Group, Final Report, Nov. 20, 1979 (incorporated by reference herein in its entirety). Segmented pipes can be heavier and less flexible than continuously constructed pipes. Moreover, various connection methods can interfere with the flow of the fluid through the pipe.
A cold water pipe intake system having desirable construction, installation and performance criteria would increase the viability of an OTEC power plant.

SUMMARY

Aspects of the present invention are directed to a power generation plant utilizing ocean thermal energy conversion processes.
Further Aspects of the invention relate to an offshore OTEC power plant having improved overall efficiencies with reduced parasitic loads, greater stability, lower construction and operating costs, and improved environmental footprint. Other aspects include large volume water conduits that are integral with the floating structure. Modularity and compartmentation of the multi-stage OTEC heat engine reduces construction and maintenance costs, limits off-grid operation and improves operating performance. Still further aspects provide for a floating platform having integrated heat exchange compartments and provides for minimal movement of the platform due to wave action. The integrated floating platform may also provide for efficient flow of the warm water or cool water through the multi-stage heat exchanger, increasing efficiency and reducing the parasitic power demand. Aspects of the invention can promote an environmentally neutral thermal footprint by discharging warm and cold water at appropriate depth/temperature ranges. Energy extracted in the form of electricity reduces the bulk temperature to the ocean.
Still further aspects of the invention relate to a cold water pipe for use with an offshore OTEC facility, the cold water pipe being an offset staved, continuous pipe.
An aspect relates to a pipe that comprises an elongate tubular structure having an outer surface, a top end and a bottom end. The tubular structure comprises a plurality of first and second staved segments, each stave segment has a top portion and a bottom portion, wherein the top portion of the second stave segment is offset from the top portion of the first staved segment.
A further aspect relates to a pipe comprising a ribbon or a strake at least partially wound around the pipe on the outside surface of the tubular structure. The ribbon or strake can be circumferentially wound around the outer surface of the top portion of the pipe, the middle portion of the pipe, or the lower portion of the pipe. The ribbon or strake can be circumferentially wound around the entire length of the pipe. The ribbon or strake can be a be attached so as to lay substantially flat against the outer surface of the pipe. The ribbon or strake can be attached so as to protrude outwardly from the outer surface of the pipe. The ribbon or strake can be made of the same or different material as the pipe. The ribbon or strake can be adhesively bonded to the outer surface of the pipe, mechanically bounded to the outer surface of the pipe, or use a combination of mechanical and adhesive bonds to attach to the outer surface of the pipe.
Further aspects of the invention relate to an offset staved pipe wherein each stave segment further comprises a tongue on a first side and a groove on a second side for mating engagement with an adjacent stave segment. The offset stave pipe can include a positive locking system to mechanically couple a first side of one stave to the second side of a second stave. Stave can be joined vertically from the top portion of one stave to the bottom portion of an adjacent stave using biscuit joinery. In an alternative embodiment, the top portion of a stave and the bottom portion of a stave can each include a joining void, such that when the top portion of a first stave is joined with the bottom portion of a second stave, the joining voids align. A flexible resign can be injected into the aligned joining voids. The flexible resign can be used to fill gaps in any joined surfaces. In aspects of the invention the flexible resign is a methacrylate adhesive.
Individual staves of the current invention can be of any length. In aspects each stave segment is between 20 feet and 90 feet measured from the bottom portion to the top portion of the stave. Stave segments can be sized to be shipped by standard inter-modal container. Individual stave segments can be between 10 inches and 120 inches wide. Each stave segment can be between 1 inch and 24 inches thick.
In aspects of the invention stave segments can be pultruded, extruded, or molded. Stave segments can comprise polyvinyl chloride (PVC), chlorinated polyvinyl chloride (CPVC), fiber reinforced plastic (FRP), reinforced polymer mortar (RPMP), polypropylene (PP), polyethylene (PE), cross-linked high-density polyethylene (PEX), polybutylene (PB), acrylonitrile butadiene styrene (ABS); polyester, fiber reinforced polyester, nylon reinforced polyester, vinyl ester, fiber reinforced vinyl ester, nylon reinforced vinyl ester, concrete, ceramic, or a composite of one or more thereof.
In further aspects of the invention the materials selected can provide neutral buoyancy of the fully assembled pipe.
In further aspects of the invention, a stave segment can comprise at least one internal void. At least one void can be filled with water, resin, adhesive, polycarbonate foam, or syntactic foam.
In aspects of the invention, the pipe is a cold water intake pipe for an OTEC power plant.
A still further aspect of the invention relates to an offshore power generation structure comprising a submerged portion, the submerged portion further comprises: a heat exchange portion; a power generation portion; and a cold water pipe comprising a plurality of offset first and second stave segments.
Yet another aspect of the invention relates to a method of forming a cold water pipe for use in an OTEC power plant, the method comprises: forming a plurality of first and second stave segments joining alternating first and second stave segments such that the second stave segments are offset from the first stave segments to form a continuous elongated tube.
A further aspect of the invention relates to a submerged vertical pipe connection comprising: a floating structure having a vertical pipe receiving bay, wherein the receiving bay has a first diameter; a vertical pipe for insertion into the pipe receiving bay, the vertical pipe having a second diameter smaller than the first diameter of the pipe receiving bay; a partially spherical or arcuate bearing surface; and one or more movable detents, pinions or lugs operable with the bearing surface, wherein the detents define a diameter that is different than the first or second diameter when in contact with the bearing surface.
An additional aspect of the invention relates to a method of connecting a submerged vertical pipe to a floating platform comprising: providing a floating structure having a vertical pipe receiving bay, wherein the pipe receiving bay has a first diameter, providing a vertical pipe having a top end portion that has a second diameter that is less than the first diameter; inserting the top end portion of the vertical pipe into the receiving bay; providing a bearing surface for supporting the vertical pipe; extending one or more detents such that the one or more detents have a diameter that is different from the first or second diameters; contacting the one or more detents with the bearing surface to suspend the vertical pipe from the floating structure.
Aspects of the invention may have one or more of the following advantages: a continuous offset staved cold water pipe is lighter than segmented pipe construction; a continuous offset staved cold water pipe has less frictional losses than a segmented pipe;
individual staves can be sized to for easy transportation to the OTEC plant operational site; staves can be constructed to desired buoyancy characteristics; mass produced uniform parts (i.e., staves) are ultimately cheaper and provide quality control assurance than single unitary pipe (i.e. spiral wound pipes); OTEC power production requires little to no fuel costs for energy production; the low pressures and low temperatures involved in the OTEC heat engine reduce component costs and require ordinary materials compared to the high-cost, exotic materials used in high pressure, high temperature power generation plants; plant reliability is comparable to commercial refrigeration systems, operating continuously for several years without significant maintenance; reduced construction times compared to high pressure, high temperature plants; and safe, environmentally benign operation and power production. Additional advantages may include, increased net efficiency compared to traditional OTEC systems, lower sacrificial electrical loads; reduced pressure loss in warm and cold water passages; modular components; less frequent off-grid production time; minimal heave and reduced susceptibility to wave action; discharge of cooling water below surface levels, intake of warm water free from interference from cold water discharge.
The details of one or more embodiments of the invention are set forth in the accompanying drawings and the description below. Other features, objects, and advantages of the invention will be apparent from the description and drawings, and from the claims.

DESCRIPTION OF DRAWINGS

FIG. 1 illustrates an exemplary prior-art OTEC heat engine.

FIG. 2 illustrates an exemplary prior-art OTEC power plant.

FIG. 3 illustrates OTEC structure of the present invention.

FIG. 4 illustrates an offset staved pipe of an OTEC structure of the present invention.

FIG. 5 illustrates a detailed image of an offset stave pattern of the present invention.

FIG. 6 illustrates a cross sectional view of an offset staved cold water pipe of the present invention.

FIGS. 7A-C illustrate various views of individuals staves of the present invention.

FIG. 8 illustrates a tongue and groove arrangement of an individual stave of the present invention.

FIG. 9 illustrates a positive snap lock between two staves of the present invention.

FIG. 10 illustrates an offset staved cold water pipe incorporating a reinforcing strake of the present invention.

FIG. 11 illustrates a method of cold water pipe construction of the present invention.

FIGS. 12A and 12B illustrate an exemplary OTEC heat engine of the present invention.

Like reference symbols in the various drawings indicate like elements.

DETAILED DESCRIPTION

This invention relates to electrical power generation using Ocean Thermal Energy Conversion (OTEC) technology. Aspects of the invention relate to a floating OTEC power plant having improved overall efficiencies with reduced parasitic loads, greater stability, lower construction and operating costs, and improved environmental footprint over convention OTEC power plants. Other aspects include large volume water conduits that are integral with the floating structure. Modularity and compartmentation of the multi-stage OTEC heat engine reduces construction and maintenance costs, limits off-grid operation and improves operating performance. Still further aspects provide for a floating platform having integrated heat exchange compartments and provides for minimal movement of the platform due to wave action. The integrated floating platform may also provide for efficient flow of the warm water or cool water through the multi-stage heat exchanger, increasing efficiency and reducing the parasitic power demand. Aspects of the invention promote a neutral thermal footprint by discharging warm and cold water at appropriate depth/temperature ranges. Energy extracted in the form of electricity reduces the bulk temperature to the ocean.
OTEC is a process that uses heat energy from the sun that is stored in the Earth's oceans to generate electricity. OTEC utilizes the temperature difference between the warmer, top layer of the ocean and the colder, deep ocean water. Typically this difference is at least 36° F. (20 C). These conditions exist in tropical areas, roughly between the Tropic of Capricorn and the Tropic of Cancer, or even 20° north and south latitude. The OTEC process uses the temperature difference to power a Rankine cycle, with the warm surface water serving as the heat source and the cold deep water serving as the heat sink. Rankine cycle turbines drive generators which produce electrical power.
FIG. 1 illustrates a typical OTEC Rankine cycle heat engine 10 which includes warm sea water inlet 12, evaporator 14, warm sea water outlet 15, turbine 16, cold sea water inlet 18, condenser 20, cold sea water outlet 21, working fluid conduit 22 and working fluid pump 24.
In operation, heat engine 10 can use any one of a number of working fluids, for example commercial refrigerants such as ammonia. Other working fluids can include propylene, butane, R-22 and R-134a. Other commercial refrigerants can be used. Warm sea water between approximately 75° F. and 85° F., or more, is drawn from the ocean surface or just below the ocean surface through warm sea water inlet 12 and in turn warms the ammonia working fluid passing through evaporator 14. The ammonia boils to a vapor pressure of approximately 9.3 atm. The vapor is carried along working fluid conduit 22 to turbine 16. The ammonia vapor expands as it passes through the turbine 16, producing power to drive an electric generator 25. The ammonia vapor then enters condenser 20 where it is cooled to a liquid by cold sea water drawn from a deep ocean depth of approximately 3000 ft. The cold sea water enters the condenser at a temperature of approximately 40° F. The vapor pressure of the ammonia working fluid at the temperature in the condenser 20, approximately 51° F., is 6.1 atm. Thus, a significant pressure difference is available to drive the turbine 16 and generate electric power. As the ammonia working fluid condenses, the liquid working fluid is pumped back into the evaporator 14 by working fluid pump 24 via working fluid conduit 22.
The heat engine 10 of FIG. 1 is essentially the same as the Rankine cycle of most steam turbines, except that OTEC differs by using different working fluids and lower temperatures and pressures. The heat engine 10 of the FIG. 1 is also similar to commercial refrigeration plants, except that the OTEC cycle is run in the opposite direction so that a heat source (e.g., warm ocean water) and a cold heat sink (e.g., deep ocean water) are used to produce electric power.
FIG. 2 illustrates the typical components of a floating OTEC facility 200, which include: the vessel or platform 210, warm sea water inlet 212, warm water pump 213, evaporator 214, warm sea water outlet 215, turbine-generator 216, cold water pipe 217, cold sea water inlet 218, cold water pump 219, condenser 220, cold sea water outlet 221, working fluid conduit 22, working fluid pump 224, and pipe connections 230. OTEC facility 200 can also include electrical generation, transformation and transmission systems, position control systems such as propulsion, thrusters, or mooring systems, as well as various auxiliary and support systems (for example, personnel accommodations, emergency power, potable water, black and grey water, fire fighting, damage control, reserve buoyancy, and other common shipboard or marine systems.).
Implementations of OTEC power plants utilizing the basic heat engine and system of FIGS. 1 and 2 have a relatively low overall efficiency of 3% or below. Because of this low thermal efficiency, OTEC operations require the flow of large amounts of water through the power system per kilowatt of power generated. This in turn requires large heat exchangers having large heat exchange surface areas in the evaporator and condensers.
Such large volumes of water and large surface areas require considerable pumping capacity in the warm water pump 213 and cold water pump 219, reducing the net electrical power available for distribution to a shore-based facility or on board industrial purposes. Moreover, the limited space of most surface vessels, does not easily facilitate large volumes of water directed to and flowing through the evaporator or condenser. Indeed, large volumes of water require large diameter pipes and conduits. Putting such structures in limited space requires multiple bends to accommodate other machinery. And the limited space of typical surface vessels or structures does not easily facilitate the large heat exchange surface area required for maximum efficiency in an OTEC plant. Thus the OTEC systems and vessel or platform have traditional been large and costly. This has lead to an industry conclusion that OTEC operations are a high cost, low yield energy production option when compared to other energy production options using higher temperatures and pressures.
Aspects of the invention address technical challenges in order to improve the efficiency of OTEC operations and reduce the cost of construction and operation.
The vessel or platform 210 requires low motions to minimize dynamic forces between the cold water pipe 217 and the vessel or platform 210 and to provide a benign operating environment for the OTEC equipment in the platform or vessel. The vessel or platform 210 should also support cold and warm water inlet (218 and 212) volume flows, bringing in sufficient cold and warm water at appropriate levels to ensure OTEC process efficiency. The vessel or platform 210 should also enable cold and warm water discharge via cold and warm water outlets (221 and 215) well below the waterline of vessel or platform 210 to avoid thermal recirculation into the ocean surface layer. Additionally, the vessel or platform 210 should survive heavy weather without disrupting power generating operations.
The OTEC heat engine 10 should utilize a highly efficient thermal cycle for maximum efficiency and power production. Heat transfer in boiling and condensing processes, as well as the heat exchanger materials and design, limit the amount of energy that can be extracted from each pound of warm seawater. The heat exchangers used in the evaporator 214 and the condenser 220 require high volumes of warm and cold water flow with low head loss to minimize parasitic loads. The heat exchangers also require high coefficients of heat transfer to enhance efficiency The heat exchangers can incorporate material and design that may be tailored to the warm and cold water inlet temperatures to enhance efficiency. The heat exchanger design should use a simple construction method with minimal amounts of material to reduce cost and volume.
Turbo generators 216 should be highly efficient with minimal internal losses and may also be tailored to the working fluid to enhance efficiency
FIG. 3 illustrates an implementation of the present invention that enhances the efficiency of previous OTEC power plants and overcomes many of the technical challenges associated therewith. This implementation comprises a spar for the vessel or platform, with heat exchangers and associated warm and cold water piping integral to the spar.
OTEC Spar 310 houses an integral multi-stage heat exchange system for use with an OTEC power generation plant. Spar 310 includes a submerged portion 311 below waterline 305. Submerged portion 311 comprises warm water intake portion 340, evaporator portion 344, warm water discharge portion 346, condenser portion 348, cold water intake portion 350, cold water pipe 351, cold water discharge portion 352, machinery deck portion 354, and deck house 360.
In operation, warm sea water of between 75° F. and 85° F. is drawn through warm water intake portion 340 and flows down the spar though structurally integral warm water conduits not shown. Due to the high volume water flow requirements of OTEC heat engines, the warm water conduits direct flow to the evaporator portion 344 of between 500,000 gpm and 6,000,000 gpm. Such warm water conduits have a diameter of between 6ft and 35 ft, or more. Due to this size, the warm water conduits are vertical structural members of spar 310. Warm water conduits can be large diameter pipes of sufficient strength to vertically support spar 310. Alternatively, the warm water conduits can be passages integral to the construction of the spar 310.
Warm water then flows through the evaporator portion 344 which houses one or more stacked, multi-stage heat exchangers for warming a working fluid to a vapor. The warm sea water is then discharged from spar 310 via warm water discharge 346. Warm water discharge can be located or directed via a warm water discharge pipe to a depth at or close to an ocean thermal layer that is approximately the same temperature as the warm water discharge temperature to minimize environmental impacts. The warm water discharge can be directed to a sufficient depth to ensure no thermal recirculation with either the warm water intake or cold water intake.
Cold sea water is drawn from a depth of between 2500 and 4200 ft, or more, at a temperature of approximately 40° F., via cold water pipe 351. The cold sea water enters spar 310 via cold water intake portion 350. Due to the high volume water flow requirements of OTEC heat engines, the cold sea water conduits direct flow to the condenser portion 348 of between 500,000 gpm and 3,500,000 gpm. Such cold sea water conduits have a diameter of between 6ft and 35 ft, or more. Due to this size, the cold sea water conduits are vertical structural members of spar 310. Cold water conduits can be large diameter pipes of sufficient strength to vertically support spar 310. Alternatively, the cold water conduits can be passages integral to the construction of the spar 310.
Cold sea water then flows upward to stacked multi-stage condenser portion 348, where the cold sea water cools a working fluid to a liquid. The cold sea water is then discharged from spar 310 via cold sea water discharge 352. Cold water discharge can be located or directed via a cold sea water discharge pipe to depth at or close to an ocean thermal layer that is approximately the same temperature as the cold sea water discharge temperature. The cold water discharge can be directed to a sufficient depth to ensure no thermal recirculation with either the warm water intake or cold water intake.
Machinery deck portion 354 can be positioned vertically between the evaporator portion 344 and the condenser portion 348. Positioning machinery deck portion 354 beneath evaporator portion 344 allows nearly straight line warm water flow from intake, through the multi-stage evaporators, and to discharge. Positioning machinery deck portion 354 above condenser portion 348 allows nearly straight line cold water flow from intake, through the multi-stage condensers, and to discharge. Machinery deck portion 354 includes turbo-generators 356. In operation warm working fluid heated to a vapor from evaporator portion 344 flows to one or more turbo generators 356. The working fluid expands in turbo generator 356 thereby driving a turbine for the production of electrical power. The working fluid then flows to condenser portion 348 where it is cooled to a liquid and pumped to evaporator portion 344.
The performance of heat exchangers is affected by the available temperature difference between the fluids as well as the heat transfer coefficient at the surfaces of the heat exchanger. The heat transfer coefficient generally varies with the velocity of the fluid across the heat transfer surfaces. Higher fluid velocities require higher pumping power, thereby reducing the net efficiency of the plant. A hybrid cascading multi-stage heat exchange system facilitates lower fluid velocities and greater plant efficiencies. The stacked hybrid cascade heat exchange design also facilitates lower pressure drops through the heat exchanger. And the vertical plant design facilitates lower pressure drop across the whole system. A hybrid cascading multi-stage heat exchange system is described in U.S. patent application Ser. No. 12/691,663, (Attorney Docket No. 2556-0004001), entitled “Ocean Thermal Energy Conversion Plant,” filed on Jan. 21, 2010 and concurrently with the present application, the entire contents of which are incorporated herein by reference.
As described above, OTEC operations require a source of cold water at a constant temperature. Variations in the cooling water can greatly influence the overall efficiency of the OTEC power plant. As such, water at approximately 40° F. is drawn from depths of between 2000 ft and 4200 ft or more. A long intake pipe is needed to draw this cold water toward the surface and into the OTEC power plant.
Such cold water pipes have been an obstacle to commercially viable OTEC operations because of the cost in constructing a pipe of suitable performance and durability. OTEC requires large volumes of water at desired temperatures in order to ensure maximum efficiency in generating electrical power. Previous cold water pipe designs specific to OTEC operations have included a sectional construction. Cylindrical pipe sections were bolted or mechanically joined together in series until a sufficient length was achieved. Pipe sections were assembled near the plant facility and the fully constructed pipe was then upended and installed. This approach had significant drawbacks including stress and fatigue at the connection points between pipe sections. Moreover, the connection hardware added to the overall pipe weight, further complicating the stress and fatigue considerations at the pipe section connections and the connection between the fully assembled CWP and the OTEC platform or vessel.
The cold water pipe (“CWP”) is used to draw water from the cold water reservoir at an ocean depth of between 2000 ft and 4200 ft or more. The cold water is used to cool and condense to a liquid the vaporous working fluid emerging from the power plant turbine. The CWP and its connection to the vessel or platform are configured to withstand the static and dynamic loads imposed by the pipe weight, the relative motions of the pipe and platform when subjected to wave and current loads of up to 100-year-storm severity, and the collapsing load induced by the water pump suction. The CWP is sized to handle the required water flow with low drag loss, and is made of a material that is durable and corrosion resistant in sea water. The material and physical construction of the CWP can at least partially thermally insulate the cold water as it moves from depth to the OTEC plant.
The cold water pipe length is defined by the need to draw water from a depth where the temperature is approximately 40° F. The CWP length can be between 2000 feet and 4000 ft or more. In aspects of the present invention the cold water pipe can be approximately 3000 feet in length.
The CWP diameter is determined by the power plant size and water flow requirements. The water flow rate through the pipe is determined by the desired power output and OTEC power plant efficiency. The CWP can carry cold water to the cold water conduit of the vessel or platform at a rate of between 500,000 gpm and 3,500,000 gpm, or more. Cold water pipe diameters can be between 6 feet and 35 feet or more. In aspects of the present invention, the CWP diameter is approximately 31 feet in diameter.
Referring to FIG. 4 a continuous offset staved cold water pipe is shown. The cold water pipe 451 is free of sectional joints as in previous CWP designs, instead utilizing an offset stave construction. CWP 451 includes a top end portion 452 for connection to the submerged portion of the floating OTEC platform 411. Opposite top end portion 452 is bottom portion 454, which can include a ballast system, an anchoring system, and/or an intake screen.
CWP 451 comprises a plurality of offset staves constructed to form a cylinder. In an aspect the plurality of offset staves can include alternating multiple first staves 465 and multiple second staves 467. Each first stave includes a top edge 471 and a bottom edge 472. Each second stave includes a top edge 473 and a bottom edge 474. In an aspect, second stave 467 is vertically offset from an adjacent first stave portion 465 such that top edge 473 (of second stave portion 467) is between 3% and 97% vertically displaced from the top edge 471 (of first stave portion 465). In further aspects, the offset between adjacent staves can be approximately, 5%, 10%, 15%, 20%, 25%, 30%, 35%, 40%, 45%, 50% or more.
FIG. 5 illustrates a detail view of an offsetting stave pattern of an aspect of the present invention. The pattern includes multiple first staves 465, each having a top edge portion 471, bottom edge portion 472, connected edge 480 and offset edge 478. The pattern also includes multiple second staves 467, each having a top edge portion 473, a bottom edge portion 474, connected edge 480, and offset edge 479. In forming the cold water pipe, first stave section 465 is joined to second stave section 467 such that connected edge 480 is approximately 3% to 97% of the length of first stave section 465 when measured from the top edge 471 to the bottom edge 472. In an aspect, connected edge 480 is approximately 50%, 55%, 60%, 65%, 70%, 75%, 80%, 85%, or 90% of the length of the stave.
It will be appreciated that in a fully constructed pipe, first stave 465 can be joined to second stave 467 along connected edge 480. First stave 465 can also be connected to additional staves along offset edge 478, including an additional first stave portion, an additional second stave portion, or any other stave portion. Similarly, second stave 467 can be joined to first stave portion along connected edge 480. And second stave 467 can be joined to another stave along offset edge 479, including an additional first stave portion, an additional second stave portion, or any other stave portion.
In aspects, the connected edge 480 between the multiple first staves 465 and the multiple second staves 467 can be a consistent length or percentage of the stave length for each stave about the circumference of the pipe. The connected edge 480 between the multiple first staves 465 and the multiple second staves 465 can be a consistent length or percentage of the stave length for each stave along the longitudinal axis of the cold water pipe 451. In further aspects the connected edge 480 can vary in length between alternating first staves 465 and second staves 467.
As illustrated in FIG. 5, first stave 465 and second stave 467 have the same dimensions. In aspects, first stave 465 can be between 30 and 130 inches wide or more, 30 to 60 feet long, and between 1 and 24 inches thick. In an aspect the stave dimensions can be approximately 80 inches wide, 40 feet long, and 4 to 12 inches thick. Alternatively, first stave 465 can have a different length or width from second stave 467.
FIG. 6 illustrates a cross sectional view of cold water pipe 451 showing alternating first staves 465 and second staves 467. Each stave includes an inner surface 485 and an outer surface 486. Adjacent staves are joined along connected surface 480. Any two connected surfaces on opposite sides of a single stave define an angle α. The angle α is determined by dividing 360° by the total number of staves. In an aspect, α can be between 1° and 36°. In an aspect α can be 22.5° for a 16 stave pipe or 11.25° for a 32 stave pipe.
Individual staves of cold water pipe 451 can be made from polyvinyl chloride (PVC), chlorinated polyvinyl chloride (CPVC), fiber reinforced plastic (FRP), reinforced polymer mortar (RPMP), polypropylene (PP), polyethylene (PE), cross-linked high-density polyethylene (PEX), polybutylene (PB), acrylonitrile butadiene styrene (ABS); polyurethane, polyester, fiber reinforced polyester, nylon reinforce polyester, vinyl ester, fiber reinforced vinyl ester, nylon reinforced vinyl ester, concrete, ceramic, or a composite of one or more thereof. Individual staves can be molded, extruded, or pulltruded using standard manufacturing techniques. In one aspect, individual staves are pulltruded to the desired shape and form and comprise a fiber or nylon reinforced vinyl ester. Vinyl esters are available from Ashland Chemical of Covington, Kentucky.
In an aspect, staves are bonded to adjacent staves using a suitable adhesive. A flexible resin can be used to provide a flexible joint and uniform pipe performance. In aspects of the invention, staves comprising a reinforced vinyl ester are bonded to adjacent staves using a vinyl ester resin. Methacrylate adhesives can also be used, such as MA560-1 manufactured by Plexis Structural Adhesives of Danvers, Mass.
Referring to FIGS. 7A-7C, various stave constructions are shown wherein an individual stave 465 includes a top edge 471, a bottom edge 472 and one or more voids 475. Void 475 can be hollow, filled with water, filled with a resin, filled with an adhesive, or filled with a foam material, such as syntactic foam. Syntactic foam is a matrix of resin and small glass beads. The beads can either be hollow or solid. Void 475 can be filled to influence the buoyancy of the stave and/or the cold water pipe 451. FIG. 7A illustrates a single void 475. In an aspect multiple voids 475 can be equally spaced along the length of the stave, as illustrated in FIGS. 7B. In an aspect, one or more voids 475 can be placed toward one end of the stave, for example toward the bottom edge 472, as illustrated in FIG. 7C.
Referring to FIG. 8, each individual stave 465 can include a top edge 471, a bottom edge 472, a first longitudinal side 491 and a second longitudinal side 492. In an aspect, longitudinal side 491 includes a joinery member, such as tongue 493. The joinery member can alternatively include, biscuits, half-lap joints, or other joinery structures. Second longitudinal side 492 includes a mating joinery surface, such as groove 494. In use, the first longitudinal side 491 of a first stave mates or joins with the second longitudinal side 492 of a second stave. Though not shown, joining structures, such as tongue and groove, or other structures can be used at the top edge 471 and the bottom edge 472 to join a stave to a longitudinally adjacent stave.
In aspects of the invention, first longitudinal side can include a positive snap lock connection 497 for mating engagement with second longitudinal side 492. Positive snap lock connections or snap lock connections are generally described in U.S. Pat. No. 7,131,242, incorporated herein by reference in its entirety. The entire length of tongue 493 can incorporate a positive snap lock or portions of tongue 493 can include a positive snap lock. Tongue 493 can include snap rivets. It will be appreciated that where tongue 493 includes a snap locking structure, an appropriate receiving structure is provided on the second longitudinal side having groove 494.
FIG. 9 illustrates an exemplary positive snap lock system, wherein male portion 970 includes collar 972. Male portion 970 mechanically engages with receiving portion 975 with include recessed collar mount 977. In use, male portion 970 is inserted into receiving portion 975 such that collar portion 972 engages recessed collar mount 977, there by allowing insertion of the male portion 970 but preventing its release or withdrawal.
Positive snap locking joints between staved portions of the offset staved pipe can be used to mechanically lock two staved portion together. The positive snap lock joints can be used alone or in combination with a resin or adhesive. In an aspect, a flexible resin is used in combination with the positive snap lock joint.
FIG. 10 illustrates a cold water pipe 451 having an offset stave construction comprising multiple alternating first staves 465 and second staves 467 and further comprising a spirally wound ribbon 497 covering at least a portion of the outer surface of cold water pipe 451. In aspects the ribbon is continuous from the bottom portion 454 of cold water pipe 451 to the top portion 452 of the cold water pipe 451. In other aspects the ribbon 497 is provided only in those portions of pipe 451 that experience vortex shedding due to movement of water past the cold water pipe 451. Ribbon 497 provides radial and longitudinal support to cold water pipe 451. Ribbon 497 also prevents vibration along the cold water pipe and reduces vortex shedding due to ocean current action.
Ribbon 491 can be the same thickness and width as an individual stave of cold water pipe 451 or can be two, three, four or more time the thickness and up to 10 times (e.g, 2, 3, 4, 5, 6, 7 8, 9 or 10 times) the width of an individual stave.
Ribbon 491 can be mounted on the outside surface of the cold water pipe so as to lay substantially flat along the outside surface. In an embodiment, ribbon 491 can protrude outwardly from the outside surface of cold water pipe 451 so as to form a spirally wound strake.
Ribbon 491 can be of any suitable material compatible with the material of the multiple staves forming cold water pipe 451, including: polyvinyl chloride (PVC), chlorinated polyvinyl chloride (CPVC), fiber reinforced plastic (FRP), reinforced polymer mortar (RPMP), polypropylene (PP), polyethylene (PE), cross-linked high-density polyethylene (PEX), polybutylene (PB), acrylonitrile butadiene styrene (ABS); polyurethane, polyester, fiber reinforced polyester, vinyl ester, reinforced vinyl ester, concrete, ceramic, or a composite of one or more thereof. Ribbon 491 can be molded, extruded, or pulltruded using standard manufacturing techniques. In one aspect, ribbon 491 is pulltruded to the desired shape and form and comprises a fiber or nylon reinforced vinyl ester similar to that used with the staves of cold water pipe 451. Ribbon 491 can be joined to cold water pipe 451 using a suitable adhesive or resin including the resins of any of the materials above.
In some aspects, ribbon 491 is not continuous along the length of cold water pipe 451. In some aspects, ribbon 491 is not continuous about the circumference of cold water pipe 451. In some aspects, ribbon 491 comprises vertical strips adhered to the outside surface of the cold water pipe 451. In some aspects, where radial or other structural support is required, ribbon 491 can be a circumferential support member around the outside surface of the cold water pipe.
Ribbon 491 can be adhesively bonded or adhered to the outside surface of the cold water pipe, using a suitable flexible adhesive. In an aspect, ribbon 491 can be mechanically coupled to the outside surface of cold water pipe 451 using multiple positive snap locks.
With regard to FIG. 11, an exemplary method of assembling a cold water pipe provides for the efficient transport and assembly of the cold water pipe 451. Vertical cylindrical pipe sections are assembled by aligning 1110 alternating first and second stave portions to have the desired offset as described above. The first and second stave portions are then joined 1120 to form a cylindrical pipe section. The offset first and second staves can be joined using any of a variety of joining methods. In an aspect the multiple offset first and second stave portions are joined using a tongue and groove arrangement and a flexible adhesive. In an aspect the multiple first and second staved portions are joined using a mechanical positive snap lock. A combination of tongue and groove, snap lock mechanisms, and flexible adhesives can be used.
After joining 1120 the multiple first and second stave portions to form a cylindrical pipe section having offset first and second stave portions, a retaining band, inflatable sleeve or other jig can be attached 1122 to the cylindrical pipe section to provide support and stability to the pipe section. The steps of aligning 1110 and joining 1120 multiple offset first and second stave portions can be repeated 1124 to form any number of prefabricated cylindrical pipe sections. It will be appreciated that the cylindrical pipe section can be prefabricated at the OTEC plant facility or remotely and then transported to the OTEC plant facility for additional construction to form the fully assembled cold water pipe 451.
Having assembled at least two cylindrical pipe sections having offset staves, an upper and lower cylindrical pipe sections are joined 1126 and the offset staves of each pipe section are aligned. A flexible adhesive can be applied 1130 to the butt joint of the offset staves of the upper and lower cylindrical pipe sections. The staves of the two pipe sections can be joined using a variety of end butt joints including biscuit joinery. In an aspect, the offset staves of the upper and lower cylindrical pipe portions can be provided with aligning joining voids which in turn can be filled with a flexible adhesive.
Gaps in and joints between pipe sections or between and individual staves can be filled 1132 with additional flexible resin. Once the two pipe sections have been joined and the resin applied where need the two pipe sections are allowed to cure 1134.
The retaining band is then removed 1136 from the lower pipe section and a spirally wound strake is attached thereto. The spirally wound strake can be attached using adhesive bonding, mechanical bonding, for example positive snap locks, or a combination of the adhesive and mechanical bonding.
In an aspect of the method of assembly, after the spiral strake is attached to the lower pipe section, the entire pipe assembly can be shifted, for example lowered, so that the previous upper pipe portion becomes the new lower pipe portion, 1138. Then a new upper cylindrical pipe section is assembled 1140 in a similar manner as described above. That is, first and second stave portions are aligned 1142 to achieve the desired offset. The first and second stave portions are then joined 1144 to form a new cylindrical pipe section, e.g., new upper pipe section. As previously mentioned, a retaining band, inflatable sleeve or other jig can be used to provide support and stability to the cylindrical pipe section during construction of the cold water pipe 451.
Having assembled new upper pipe section 1144, the offset staves of the new lower pipe section and the new upper pipe section are aligned and drawn together 1146. Adhesive or flexible resin is applied 1148 to the end butt joints as described above, for example in conjunction with biscuit joinery or with aligning joining voids. Any gaps between the new lower pipe section and the new upper pipe section or between any two stave portions can be filled 1150 with additional flexible resin. The entire assembly can then be left to cure 1152. The retaining jig can be removed 1154 as before and the spiral strake can be attached to the new lower portion. And as before the entire pipe assembly can be shifted to provide for the next cylindrical pipe section. In this manner, the method can be repeated until the desired pipe length is achieved.
It will be appreciated that joining cylindrical pipe sections having offset staves can be accomplished in a number of manners consistent with the present invention. The method of joining offset staves provides for a continuous pipe without the need for bulky, heavy or interfering joining hardware between the pipe segments. As such a continuous pipe having nearly uniform material properties, including flexibility and rigidity, is provided.

Example

A cold water pipe assembly is provided that facilitates on site construction of a continuous, offset staved pipe of approximately 3000 feet. Additionally the staved design accounts for adverse shipping and handling loads traditionally experienced by segmented pipe construction. For example towing and upending of traditionally constructed segmented cold water pipes imposes hazardous loads on the pipe.
Staved construction allows offsite manufacturing of multiple staves of 40 to 50 ft lengths. Each stave is approximately 52 inches wide and 4 to 12 inches thick. The staves can be shipped in stacks or containers to the offshore platform and the cold water pipe can then be constructed on the platform from the multiple staves. This eliminates the need for a separate facility to assemble pipe sections.
The stave portions can be constructed from a nylon reinforced vinyl ester having a modulus of elasticity of between about 66,000 psi and 165,000 psi. The stave portions can have an ultimate strength of between about 15,000 psi and 45,000 psi, with a tensile strength between about 15,000 psi to 45,000 psi. In an aspect, the stave portions can have an modulus of elasticity of 150,000 psi, an ultimate strength of 30,000 psi and a yield strength of 30,000 psi, such that the installed CWP behaves similar to a hose rather than a purely rigid pipe. This is advantageous in storm conditions as the pipe is more flexible and avoids cracking or breaking In an aspect, the pipe can deflect approximately two diameters from center at the unconnected lower end. Deflection at the unconnected lower end should not be so great as to interfere with the mooring system of the OTEC power plant or any other underwater systems involved in plant operations. The cold water pipe connects to the bottom portion of the OTEC power plant.
More specifically, the cold water pipe connects using a dynamic bearing with the bottom portion of the OTEC spar of FIG. 3. Cold water pipe connections in OTEC applications are described in Section 4.5 of Avery & Wu, “Renewable Energy from the Ocean, a Guide to OTEC,” Oxford University Press, 1994, incorporated herein by reference in its entirety.
One of the significant advantages of using the spar buoy as the platform is that doing so results in relatively small rotations between the spar itself and the CWP even in the most severe 100-year storm conditions. In addition the vertical and lateral forces between the spar and the CWP are such that the downward force between the spherical ball and its seat keeps the bearing surfaces in contact at all times. Because this bearing, that also acts as the water seal, does not come out of contact with its mating spherical seat there is no need to install a mechanism to hold the CWP in place vertically. This helps to simplify the spherical bearing design and also minimizes the pressure losses that would otherwise be caused by any additional CWP pipe restraining structures or hardware. The lateral forces transferred through the spherical bearing are also low enough that they can be adequately accommodated without the need for vertical restraint of the CWP.
Cold water is drawn through the cold water pipe via one or more cold water pumps such and flows via one or more cold water passages or conduits to the condenser portion of a multi-stage OTEC power plant.

Example

Aspects of the present invention provide an integrated multi-stage OTEC power plant that will produce electricity using the temperature differential between the surface water and deep ocean water in tropical and subtropical regions. Aspects eliminate traditional piping runs for sea water by using the off-shore vessel's or platform's structure as a conduit or flow passage. Alternatively, the warm and cold sea water piping runs can use conduits or pipes of sufficient size and strength to provide vertical or other structural support to the vessel or platform. These integral lsea water conduit sections or passages serve as structural members of the vessel, thereby reducing the requirements for additional steel. As part of the integral sea water passages, multi-stage cabinet heat exchangers provides multiple stages of working fluid evaporation without the need for external water nozzles or piping connections. The integrated multi-stage OTEC power plant allows the warm and cold sea water to flow in their natural directions The warm sea water flows downward through the vessel as it is cooled before being discharged into a cooler zone of the ocean. In a similar fashion, the cold sea water from deep in the ocean flows upward through the vessel as it is warmed before discharging into a warmer zone of the ocean. This arrangement avoids the need for changes in sea water flow direction and associated pressure losses. The arrangement also reduces the pumping energy required.
Multi-stage cabinet heat exchangers allow for the use of a hybrid cascade OTEC cycle. These stacks of heat exchangers comprise multiple heat exchanger stages or sections that have sea water passing through them in series to boil or condense the working fluid as appropriate. In the evaporator section the warm sea water passes through the first stage where it boils off some of the working fluid as the sea water is cooled. The warm sea water then flows down the stack into the next heat exchanger stage and boils off additional working fluid at a slightly lower pressure and temperature. This occurs sequentially through the entire stack. Each stage or section of the cabinet heat exchanger supplies working fluid vapor to a dedicated turbine that generates electrical power. Each of the evaporator stages has a corresponding condenser stage at the exhaust of the turbine. The cold sea water passes through the condenser stacks in a reverse order to the evaporators.
Referring to FIGS. 12A and 12B, an exemplary multi-stage OTEC heat engine 710 utilizing a hybrid cascading heat exchange cycles is provided. Warm sea water is pumped from a warm sea water intake (not shown) via warm water pump 712, discharging from the pump at approximately 1,360,000 gpm and at a temperature of approximately 79° F. All or parts of the warm water conduit from the warm water intake to the warm water pump, and from the warm water pump to the stacked heat exchanger cabinet can form integral structural members of the vessel.
From the warm water pump 712, the warm sea water then enters first stage evaporator 714 where it boils a first working fluid. The warm water exits first stage evaporator 714 at a temperature of approximately 76.8° F. and flows down to the second stage evaporator 715. The warm water enters second stage evaporator 715 at approximately 76.8° F. where it boils a second working fluid and exits the second stage evaporator 715 at a temperature of approximately 74.5°.
The warm water flows down to the third stage evaporator 716 from the second stage evaporator 715, entering at a temperature of approximately 74.5° F., where it boils a third working fluid. The warm water exits the third stage evaporator 716 at a temperature of approximately 72.3° F.
The warm water then flows from the third stage evaporator 716 down to the fourth stage evaporator 717, entering at a temperature of approximately 72.3° F., where it boils a fourth working fluid. The warm water exits the fourth stage evaporator 717 at a temperature of approximately 70.1° F. and then discharges from the vessel. Though not shown, the discharge can be directed to a thermal layer at an ocean depth of or approximately the same temperature as the discharge temperature of the warm sea water. Alternately, the portion of the power plant housing the multi-stage evaporator can be located at a depth within the structure so that the warm water is discharged to an appropriate ocean thermal layer. In aspects, the warm water conduit from the fourth stage evaporator to the warm water discharge of the vessel can be comprise structural members of the vessel.
Similarly, cold sea water is pumped from a cold sea water intake (not shown) via cold sea water pump 722, discharging from the pump at approximately 855,003 gpm and at a temperature of approximately 40.0° F. The cold sea water is drawn from ocean depths of between approximately 2700 and 4200 ft, or more. The cold water conduit carrying cold sea water from the cold water intake of the vessel to the cold water pump, and from the cold water pump to the first stage condenser can comprise in its entirety or in part structural members of the vessel.
From cold sea water pump 722, the cold sea water enters a first stage condenser 724, where it condenses the fourth working fluid from the fourth stage boiler 717. The cold seawater exits the first stage condenser at a temperature of approximately 43.5° F. and flows up to the second stage condenser 725.
The cold sea water enters the second stage condenser 725 at approximately 43.5° F. where it condenses the third working fluid from third stage evaporator 716. The cold sea water exits the second stage condenser 725 at a temperature approximately 46.9° F. and flows up to the third stage condenser.
The cold sea water enters the third stage condenser 726 at a temperature of approximately 46.9° F. where it condenses the second working fluid from second stage evaporator 715. The cold sea water exits the third stage condenser 726 at a temperature approximately 50.4° F.
The cold sea water then flows up from the third stage condenser 726 to the fourth stage condenser 727, entering at a temperature of approximately 50.4° F. In the fourth stage condenser, the cold sea water condenses the first working fluid from first stage evaporator 714. The cold sea water then exits the fourth stage condenser at a temperature of approximately 54.0° F. and ultimately discharges from the vessel. The cold sea water discharge can be directed to a thermal layer at an ocean depth of or approximately the same temperature as the discharge temperature of the cold sea water. Alternately, the portion of the power plant housing the multi-stage condenser can be located at a depth within the structure so that the cold sea water is discharged to an appropriate ocean thermal layer.
The first working fluid enters the first stage evaporator 714 at a temperature of 56.7° F. where it is heated to a vapor with a temperature of 74.7° F. The first working fluid then flows to first turbine 731 and then to the fourth stage condenser 727 where the first working fluid is condensed to a liquid with a temperature of approximately 56.5° F. The liquid first working fluid is then pumped via first working fluid pump 741 back to the first stage evaporator 714.
The second working fluid enters the second stage evaporator 715 at a temperature approximately 53.0° F. where it is heated to a vapor. The second working fluid exits the second stage evaporator 715 at a temperature approximately 72.4° F. The second working fluid then flow to a second turbine 732 and then to the third stage condenser 726. The second working fluid exits the third stage condenser at a temperature approximately 53.0° F. and flows to working fluid pump 742, which in turn pumps the second working fluid back to the second stage evaporator 715.
The third working fluid enters the third stage evaporator 716 at a temperature approximately 49.5° F. where it will be heated to a vapor and exit the third stage evaporator 716 at a temperature of approximately 70.2° F. The third working fluid then flows to third turbine 733 and then to the second stage condenser 725 where the third working fluid is condensed to a fluid at a temperature approximately 49.5° F. The third working fluid exits the second stage condenser 725 and is pumped back to the third stage evaporator 716 via third working fluid pump 743.
The fourth working fluid enters the fourth stage evaporator 717 at a temperature of approximately 46.0° F. where it will be heated to a vapor. The fourth working fluid exits the fourth stage evaporator 717 at a temperature approximately 68.0° F. and flow to a fourth turbine 734. The fourth working fluid exits fourth turbine 734 and flows to the first stage condenser 724 where it is condensed to a liquid with a temperature approximately 46.0° F. The fourth working fluid exits the first stage condenser 724 and is pumped back to the fourth stage evaporator 717 via fourth working fluid pump 744.
The first turbine 731 and the fourth turbine 734 cooperatively drive a first generator 751 and form first turbo-generator pair 761. First turbo-generator pair will produce approximately 25 MW of electric power.
The second turbine 732 and the third turbine 733 cooperatively drive a second generator 752 and form second turbo-generator pair 762. Second turbo-generator pair 762 will produce approximately 25 MW of electric power.
The four stage hybrid cascade heat exchange cycle of FIG. 7 allows the maximum amount of energy to be extracted from the relatively low temperature differential between the warm sea water and the cold sea water. Moreover, all heat exchangers can directly support turbo-generator pairs that produce electricity using the same component turbines and generators.
It will be appreciated that multiple multi-stage hybrid cascading heat exchangers and turbo generator pairs can be incorporated into a vessel or platform design.

Example

An offshore OTEC spar platform includes four separate power modules, each generating about 25 MWe Net at the rated design condition. Each power module comprises four separate power cycles or cascading thermodynamic stages that operate at different pressure and temperature levels and pick up heat from the sea water system in four different stages. The four different stages operate in series. The approximate pressure and temperature levels of the four stages at the rated design conditions (Full Load—Summer Conditions) are:


	Turbine inlet	Condenser
	Pressure/Temp.	Pressure/Temp.
	(Psia)/(° F.)	(Psia)/(° F.)

1 Stage	137.9/74.7	100.2/56.5
2″ Stage	132.5/72.4	93.7/53
3′ Stage	127.3/70.2	87.6/49.5
4″ Stage	122.4/68	81.9/46

The working fluid is boiled in multiple evaporators by picking up heat from warm sea water (WSW). Saturated vapor is separated in a vapor separator and led to an ammonia turbine by STD schedule, seamless carbon steel pipe. The liquid condensed in the condenser is pumped back to the evaporator by 2×100% electric motor driven constant speed feed pumps. The turbines of cycle-1 and 4 drive a common electric generator. Similarly the turbines of cycle-2 and 3 drive another common generator. In an aspect there are two generators in each plant module and a total of 8 in the 100 MWe plant. The feed to the evaporators is controlled by feed control valves to maintain the level in the vapor separator. The condenser level is controlled by cycle fluid make up control valves. The feed pump minimum flow is ensured by recirculation lines led to the condenser through control valves regulated by the flow meter on the feed line.
In operation the four (4) power cycles of the modules operate independently. Any of the cycles can be shutdown without hampering operation of the other cycles if needed, for example in case of a fault or for maintenance. But that will reduce the net power generation of the power module as a whole module.
Aspects of the present invention require large volumes of seawater. There will be separate systems for handling cold and warm seawater, each with its pumping equipment, water ducts, piping, valves, heat exchangers, etc. Seawater is more corrosive than fresh water and all materials that may come in contact with it need to be selected carefully considering this. The materials of construction for the major components of the seawater systems will be:
Large bore piping: Fiberglass Reinforced Plastic (FRP)
Large seawater ducts & chambers: Epoxy-coated carbon steel
Large bore valves: Rubber lined butterfly type
Pump impellers: Suitable bronze alloy
Unless controlled by suitable means, biological growths inside the seawater systems can cause significant loss of plant performance and can cause fouling of the heat transfer surfaces leading to lower outputs from the plant. This internal growth can also increase resistance to water flows causing greater pumping power requirements, lower system flows, etc. and even complete blockages of flow paths in more severe cases.
The Cold Sea Water (“CSW”) system using water drawn in from deep ocean should have very little or no bio-fouling problems. Water in those depths does not receive much sunlight and lack oxygen, and so there are fewer living organisms in it. Some types of anaerobic bacteria may, however, be able to grow in it under some conditions. Shock chlorination will be used to combat bio-fouling.
The Warm Sea Water (“WSW”) system handling warm seawater from near the surface will have to be protected from bio-fouling. It has been found that fouling rates are much lower in tropical open ocean waters suitable for OTEC operations than in coastal waters. As a result, chemical agents can be used to control bio-fouling in OTEC systems at very low doses that will be environmentally acceptable. Dosing of small amounts of chlorine has proved to be very effective in combating bio-fouling in seawater. Dosages of chlorine at the rate of about 70 ppb for one hour per day, is quite effective in preventing growth of marine organisms. This dosage rate is only 1/20th of the environmentally safe level stipulated by EPA. Other types of treatment (thermal shock, shock chlorination, other biocides, etc.) can be used from time to time in-between the regimes of the low dosage treatment to get rid of chlorine-resistant organisms.
Necessary chlorine for dosing the seawater streams is generated on-board the plant ship by electrolysis of seawater. Electro-chlorination plants of this type are available commercially and have been used successfully to produce hypochlorite solution to be used for dosing. The electro-chlorination plant can operate continuously to fill-up storage tanks and contents of these tanks are used for the periodic dosing described above.
All the seawater conduits avoid any dead pockets where sediments can deposit or organisms can settle to start a colony. Sluicing arrangements are provided from the low points of the water ducts to blow out the deposits that may get collected there. High points of the ducts and water chambers are vented to allow trapped gases to escape.
The Cold Seawater (CSW) system will consist of a common deep water intake for the plant ship, and water pumping/distribution systems, the condensers with their associated water piping, and discharge ducts for returning the water back to the sea. The cold water intake pipe extends down to a depth of more than 2700 ft, (e.g., between 2700 ft to 4200 ft), where the sea water temperature is approximately a constant 40° F. Entrance to the pipe is protected by screens to stop large organisms from being sucked in to it. After entering the pipe, cold water flows up towards the sea surface and is delivered to a cold well chamber near the bottom of the vessel or spar.
The CSW supply pumps, distribution ducts, condensers, etc. are located on the lowest level of the plant. The pumps take suction from the cross duct and send the cold water to the distribution duct system. 4×25% CSW supply pumps are provided for each module. Each pump is independently circuited with inlet valves so that they can be isolated and opened up for inspection, maintenance, etc. when required. The pumps are driven by high-efficiency electric motors.
The cold seawater flows through the condensers of the cycles in series and then the CSW effluent is discharged back to the sea. CSW flows through the condenser heat exchangers of the four plant cycles in series in the required order. The condenser installations is arranged to allow them to be isolated and opened up for cleaning and maintenance when needed.
The WSW system comprises underwater intake grills located below the sea surface, an intake plenum for conveying the incoming water to the pumps, water pumps, biocide dosing system to control fouling of the heat transfer surfaces, water straining system to prevent blockages by suspended materials, the evaporators with their associated water piping, and discharge ducts for returning the water back to the sea.
Intake grills are provided in the outside wall of the plant modules to draw in warm water from near the sea surface. Face velocity at the intake grills is kept to less than 0.5 ft/sec. to minimize entrainment of marine organisms. These grills also prevent entry of large floating debris and their clear openings are based on the maximum size of solids that can pass through the pumps and heat exchangers safely. After passing through these grills, water enters the intake plenum located behind the grills and is routed to the suctions of the WSW supply pumps.
The WSW pumps are located in two groups on opposite sides of the pump floor. Half of the pumps are located on each side with separate suction connections from the intake plenum for each group. This arrangement limits the maximum flow rate through any portion of the intake plenum to about 1/16th of the total flow and so reduces the friction losses in the intake system. Each of the pumps are provided with valves on inlet sides so that they can be isolated and opened up for inspection, maintenance, etc. when required. The pumps are driven by high-efficiency electric motors with variable frequency drives to match pump output to load.
It is necessary to control bio-fouling of the WSW system and particularly its heat transfer surfaces, and suitable biocides will be dosed at the suction of the pumps for this. The warm water stream may need to be strained to remove the larger suspended particles that can block the narrow passages in the heat exchangers. Large automatic filters or ‘Debris Filters’ can be used for this if required. Suspended materials can be retained on screens and then removed by backwashing. The backwashing effluents carrying the suspended solids will be routed to the discharge stream of the plant to be returned to the ocean. The exact requirements for this will be decided during further development of the design after collection of more data regarding the seawater quality.
The strained warm seawater (WSW) is distributed to the evaporator heat exchangers. WSW flows through the evaporators of the four plant cycles in series in the required order. WSW effluent from the last cycle is discharged at a depth of approximately 175 feet or more below the sea surface. It then sinks slowly to a depth where temperature (and therefore density) of the seawater will match that of the effluent.
Though embodiments herein have described multi-stage heat exchanger in a floating offshore vessel or platform, drawing cold water via a continuous, offset staved cold water pipe, it will be appreciated that other embodiments are within the scope of the invention. For example, the cold water pipe can be connected to a shore facility. The continuous offset staved pipe can be used for other intake or discharge pipes having significant length to diameter ratios. The offset staved construction can be incorporated into pipe sections for use in traditional segmented pipe construction. The multi-stage heat exchanger and integrated flow passages can be incorporated into shore based facilities including shore based OTEC facilities. Moreover, the warm water can be warm fresh water, geo-thermally heated water, or industrial discharge water (e.g., discharged cooling water from a nuclear power plant or other industrial plant). The cold water can be cold fresh water. The OTEC system and components described herein can be used for electrical energy production or in other fields of use including: salt water desalination: water purification; deep water reclamation; aquaculture; the production of biomass or biofuels; and still other industries.
All references mentioned herein are incorporated by reference in their entirety.
Other embodiments are within the scope of the following claims.

Claims

What is claimed is:

1. A pipe comprising:

an elongated tubular structure having an outer surface, a top end and a bottom end, the tubular structure comprising:

a plurality of first and second stave segments, each stave segment having a top portion and a bottom portion, wherein the top portion of the second stave segment is offset from the top portion of the first staved segment.

2. The pipe of claim 1 further comprising a strake at least partially wound around the pipe on the outside surface of the tubular structure.

3. The pipe of claim 2 wherein the strake extends from the bottom end to the top end of the tubular structure and at least partially covers the outer surface thereof.

4. The pipe of claim 2 wherein the strake comprises the same material as the first and second stave segments.

5. The pipe of claim 1 wherein each stave segment further comprises a tongue on a first side and a groove on a second side for mating engagement with an adjacent stave segment.

6. The pipe of claim 1 wherein each stave segment is between 30 feet and 90 feet between the bottom portion and the top portion.

7. The pipe of claim 5 wherein each stave segment is between 10 inches and 120 inches between the first side and the second side.

8. The pipe of claim 1 wherein each stave segment is pulltruded, extruded, or molded.

9. The pipe of claim 1 wherein each stave segment comprises polyvinyl chloride (PVC), chlorinated polyvinyl chloride (CPVC), fiber reinforced plastic (FRP), reinforced polymer mortar (RPMP), polypropylene (PP), polyethylene (PE), cross-linked high-density polyethylene (PEX), polybutylene (PB), acrylonitrile butadiene styrene (ABS); polyester, fiber reinforced polyester, nylon reinforced polyester, vinyl ester, fiber reinforced vinyl ester, nylon reinforced vinyl ester, concrete, ceramic, or a composite of one or more thereof.

10. The pipe of claim 1 wherein each stave segment comprises at least one internal void.

11. The pipe of claim 10 wherein the at least one void is filled with water, polycarbonate foam, or syntactic foam.

12. The pipe of claim 10 wherein the plurality of first and second stave segments are adhesively bonded.

13. The pipe of claim 10 wherein the pipe forms a cold water pipe for an OTEC power plant.

14. An offshore power generation structure comprising a submerged portion, the submerged portion further comprising:

a heat exchange portion;

a power generation portion; and

a cold water pipe comprising a plurality of offset first and second stave segments.

15. The offshore power generation structure of claim 14 wherein each stave segment comprises polyvinyl chloride (PVC), chlorinated polyvinyl chloride (CPVC), fiber reinforced plastic (FRP), reinforced polymer mortar (RPMP), polypropylene (PP), polyethylene (PE), cross-linked high-density polyethylene (PEX), polybutylene (PB), acrylonitrile butadiene styrene (ABS); polyester, fiber reinforced polyester, vinyl ester, reinforced vinyl ester, concrete, ceramic, or a composite of one or more thereof.

16. The offshore power generation structure of claim 14 wherein the first and second stave segments are adhesively bonded.

17. The offshore power generation structure of claim 14 wherein the cold water pipe further comprises a ribbon at least partially rapping the cold water pipe.

18. A method of forming a cold water pipe for use in an OTEC power plant, the method comprising:

forming a plurality of first and second stave segments; and

adhesively bonding alternating first and second stave segments such that the second stave segments are offset from the first stave segments to form a continuous elongated tube.

19. The method of claim 18 wherein each of the stave segments comprises polyvinyl chloride (PVC), chlorinated polyvinyl chloride (CPVC), fiber reinforced plastic (FRP), reinforced polymer mortar (RPMP), polypropylene (PP), polyethylene (PE), cross-linked high-density polyethylene (PEX), polybutylene (PB), acrylonitrile butadiene styrene (ABS); polyester, fiber reinforced polyester, vinyl ester, reinforced vinyl ester, concrete, ceramic, or a composite of one or more thereof.

20. The method of claim 18 wherein comprises a tongue on a first side and a groove on a second side for mating engagement with an adjacent stave segment.