US20100253083A1

US20100253083A1 - In-pipe hydro-electric power system, turbine and improvement

Info

Publication number: US20100253083A1
Application number: US12/661,566
Authority: US
Inventors: Roderic A. Schlabach; Mark Rydell Cosby; Edward Kurth; Igor Palley; Greg Smith
Original assignee: Nothwest Pipe Co; Lucid Energy Technologies LLP
Current assignee: Nothwest Pipe Co; Lucid Energy Technologies LLP; Northwest Pipe Co
Priority date: 2009-04-07
Filing date: 2010-03-19
Publication date: 2010-10-07
Also published as: JP2012523522A; JP5694291B2; CN102317618A; AU2010234956B2; WO2010117621A2; KR20110134933A; CL2011002428A1; CL2013002508A1; TW201042139A; EP2417350A4; US20110204640A1; BRPI1015287A2; AU2010234956A2; JP2014159815A; US8360720B2; CL2013002509A1; JP5882398B2; CA2758162A1; AU2010234956A1; US7959411B2

Abstract

A helical turbine configured to rotate transversely within a cylindrical pipe under the power of fluid flowing either direction therethrough is operatively coupled with a rotating machine or generator to produce work or electricity. The twisted blades of the turbine define a right circular cylinder when the shaft mounting them rotates under the influence of fluid flow through the pipe. In one embodiment, baffles are provided at least upstream of the cylindrical turbine and within the cylindrical pipe to control flow through the cylindrical turbine. The twisted blades of the helical turbine are airfoil in cross section, as are the radial struts or spokes that mount the twisted blades to the rotatable shaft, thereby to optimize hydrodynamic flow, to minimize cavitation, and to maximize conversion from axial to rotating energy.

Description

RELATED APPLICATIONS

This is a continuation-in-part of and claims the benefit of priority from U.S. patent application Ser. No. 12/384,765 filed Apr. 7, 2009, the contents of which are incorporated herein in their entirety by this reference.

FIELD OF THE INVENTION

The invention relates generally to the field of hydro-electric power generation. More particularly, the invention relates to hydro-electric power generation via fluid flow past a turbine.

BACKGROUND OF THE INVENTION

U.S. Pat. Nos. 5,451,137; 5,642,984; 6,036,443; 6,155,892; 6,253,700 B1; and 6,293,835 B2 to Gorlov disclose various cylindrical turbines for power systems, the blades of the turbines extending helically to sweep out an open cylinder. The patents disclose mounting such turbines in rectangular and/or square cross-sectional channels or ducts capable of conveying water that rotates the turbines to generate hydro-electric power. Gorlov's cylindrical turbine has helically curved/twisted blades or vanes mounted to a central shaft by radial struts or spokes of seemingly arbitrary or at least non-airfoil, e.g. circular, cross section. PCT/US00/35471 describes and illustrates a cylindrical turbine having helically twisted blades each with airfoil cross sections of variable sizes along their extents. Each twisted blade is mounted to a central rotating hub by a blade support member also having an airfoil cross section. Two or more radial blades “uniformly distributed” on some or all of the twisted blades make use of deviated transverse flow in an axial direction parallel with the turbine's shaft.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is an isometric exploded assembly drawing of a first embodiment of the invention featuring an un-baffled cylindrical turbine.

FIG. 2 is a front elevation of the assembled first embodiment.

FIG. 3 is an isometric exploded assembly drawing of a second embodiment of the invention featuring a baffled cylindrical turbine.

FIG. 4 is a side elevation of the assembled second embodiment.

FIG. 5 is an isometric exploded assembly drawing of the cylindrical turbine of FIG. 1.

FIG. 6 is an isometric view of the assembled cylindrical turbine.

Details A and B are fragmentary side elevations of the turbine-containing pipe of FIG. 1 showing a side-by-side comparison of two different embodiments of the circular plate shown therein. Specifically, Detail A shows a flat circular plate and Detail B shows a spherically concave circular plate for mounting a proximal end of the turbine's shaft.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

FIG. 1 is an isometric exploded assembly drawing of a first embodiment of the invented in-pipe hydro-electric power system 10 featuring an un-baffled cylindrical turbine. System 10 in accordance with one embodiment of the invention includes a T-section fluid (broadly encompassing a liquid such as water or a gas such as air or the like material exhibiting useful flow characteristics) pipe 12, a bulkhead or generator assembly 14, and a cylindrical turbine assembly 16. Those of skill in the art will appreciate, by brief reference to FIG. 2, that when assembled and driven by fluid flow through pipe 12, turbine assembly 16 rotates and system 10 produces hydro-electric power that can be stored, consumed, or fed into a power grid.
Pipe 12 is generally cylindrical, having a generally circular cross section, although within the spirit and scope of the invention it can be slightly oval in cross section. Pipe 12 typically is a part of a longer and perhaps more complex fluid conveyance or pipe system, and it will be appreciated that an existing pipe system can readily be retrofitted with invented power system 10 by sectioning and replacing the removed section with power system 10. Thus, pipe 12 is equipped with circular flanges 12 a and 12 b for bolting on either end to upstream and downstream pipe ends (not shown). Pipe 12 is provided with a small opening 12 c in a first region of the sidewall and a large opening 12 d in a diametrically opposed region thereof. As will be seen, small opening 12 c accommodates a shaft of the turbine therethrough, while large opening 12 d accommodates turbine assembly 16 therethrough. Pipe 12 also is equipped with a flanged T-intersection pipe section (a so-called “tee”) that effectively mates with large opening 12 d at a right angle to the long axis of pipe 12.
Generator cap assembly 14 includes a circular arched plate 18 that effectively acts to close larger opening 12 d when system 10 is assembled. Arched plate 18 provides a contiguous round wall inside pipe 12 for the fluid to flow past, thereby avoiding cavitation or other smooth fluid flow disruption within what would otherwise act as a pocket volume within the tee section. A 3-vaned, cylindrical spacer 20 holds arched plate 18 in place within the tee section when a cover plate 22 including an annular seal 22 a and a circular plate 22 b is bolted onto flange 12 e. Circular plate 22 b has an opening 22 ba therein with a mounting block 24 extending therearound. A first mount 26 including a roller bearing assembly mounts a proximal end of the shaft of turbine assembly 16 for smooth rotation therethrough. A flat shim 22 bb can be provided between mounting block 24 and circular plate 22 b.
A generator sub-assembly 28 bolts through a circular hole arrangement within circular plate 22 b. Generator sub-assembly 28 includes an annular spacer or standoff 30 for housing a generator 32 couple-able with the turbine's shaft, an annular rim 34 with a first mechanical-lift tab 34 a, and a cap 36 having a second mechanical-lift tab 36 a. Those of skill in the art will appreciate that tabs 34 a and 36 a provide convenient tabs for lifting all or part of the assembled tee-section electrical power generation components during assembly, disassembly, or maintenance. Those of skill will appreciate that the generator can be direct or alternating current (DC or AC) and single-phase or 3-phase, synchronized 120VAC or 240VAC, etc. and/or can be converted from one to the other, depending upon the power requirements.
A mounting plate 12 f is welded to pipe 12 around small opening 12 c and a second mount 38 including a roller-bearing assembly that mounts a distal end of the shaft of turbine assembly 16 for smooth rotation therein. Those of skill in the art will appreciate that, to accommodate the circular cross section of cylindrical pipe 12, first mount 26 in accordance with one embodiment of the invention includes a shim (not shown in pertinent detail but believed to be understood from this brief description by those of skill in the art) having an exterior planar surface and an inner cylindrical surface for mating with the exterior cylindrical surface of the pipe. The shim can be machined or formed by any suitable process and of any suitable material that ensures conformingly sealing engagement between the shaft and the pipe opening through which the shaft extends. Either shim described and/or illustrated herein will be understood to be optional, as either can readily be incorporated into the corresponding mounting block or plate.
Finally, generator assembly 14 includes mounting plate 12 f around small opening 12 c of pipe 12 and a second mount 38 including a roller-bearing assembly that mounts a distal end of the shaft of turbine assembly 16 for smooth rotation therein. First and second mounts 26 and 38 can take alternative forms, within the spirit and scope of the invention, but it is believed that axial and radial thrust handling is best achieved using spherical roller bearings producing only rolling friction rather, for example, than sleeve bearings or other sliding friction arrangements. The roller bearing mounts described herein are believed to enable system 10 to operate safely, reliably and durably to produce electricity with a fluid flow rate through pipe 12 of as little as approximately 3-4 feet/second (fps).
Those of skill in the art will appreciate that turbine assembly 16 is slipped through large opening 12 d of pipe 12 and the proximal end of its shaft is secured to second mount 38. Generator assembly 14 is bolted onto flange 12 e of pipe 12 and the hydro-electric power system 10 is ready to operate. Power system 10 is fitted into or otherwise connected to a part of a pipe system (not shown). When fluid flows through pipe 12, power system 10 generates electricity.
FIG. 2 is a side elevation of assembled system 10, and is believed to be largely self-explanatory. Those of skill in the art will appreciate that cylindrical turbine assembly 16 is generally square in cross section, while the interior of pipe 12 is generally circular in cross section. Thus, fluid within pipe 12 flows not only through turbine assembly 16 to cause it to rotate and to generate electricity via generator assembly 14, but also around turbine assembly 16, with little electricity generation effect. Nevertheless, efficient electricity generation is possible with the un-baffled cylindrical turbine system shown in FIGS. 1 and 2, since the cylindrical turbine assembly in accordance with the present invention has a relatively small cross-sectional ‘solidity’ (e.g. flow-restricting and energy-producing ratio between closed and total confronting surface area) effect on the flow of fluid therethrough. Importantly, as will be seen by reference to FIGS. 5 and 6, cylindrical turbine assembly 16 is an extremely efficient hydrofoil by virtue of an improved overall airfoil cross-sectional design of the blades that extend rectilinearly from a central, rotating shaft.
Those of skill in the art will appreciate now that helically twisted and helically (or spirally) extending and cylindrically arcing blades of turbine assembly 16 ensure that a portion of at least one of the plural blades thereof is always optimally aligned with the flow of the fluid through pipe 12. Indeed, in accordance with the embodiments of the invention described and illustrated herein, a portion of each of the plural blades thereof is always so optimally aligned. Moreover, all such portions of each blade present an extremely hydrodynamic airfoil cross section to the flowing fluid, thereby virtually eliminating undesirable cavitation. Surprisingly, it has been discovered that turbine assemblies such as those described and illustrated herein rotate at fluid flow rates as low as approximately 3-4 feet per second (fps).
FIG. 3 is an isometric exploded assembly drawing of a second embodiment of the invented in-pipe hydro-electric power system 10′ featuring a baffled cylindrical turbine. System 10′ includes nearly all the component parts of system 10 in the same configuration but omits arched plate 18, includes a higher spacer 20′, and includes a baffle assembly 40 that extends around turbine assembly 16 within pipe 12. Those of skill in the art will appreciate that interiorly rectilinear and exteriorly curvilinear baffle assembly 40 effectively “squares the circle” within circular cross-sectional pipe 12, thereby increasing and improving flow characteristics and electrical generation efficiencies with the cylindrical turbine embodiment of the invention.
Those of skill in the art will appreciate from FIG. 3 that four baffles 42, 44, 46, and 48 are provided on one end of turbine assembly 16, while four more baffles 50, 52, 54, and 56 are provided on the other end thereof. The baffles are rectilinear in their interior or proximal regions to mate with a rectilinear (e.g. rectangular) open channel 58 (defined by four peripheral planar sidewalls) that surrounds turbine assembly 16, while the baffles are curvilinear, e.g. parabolic, in their exterior or distal regions to mate with the interior of circularly cross-sectional cylindrical pipe 12. Those of skill also will appreciate that the baffles and rectangular channel can be made of any suitable material, e.g. steel, and can be dimensioned and oriented for any desired fluid flow adjustment at either end. In accordance with one embodiment of the invention, each of baffles 42-56 is inclined relative to the long central axis of pipe 12 at an angle θ (refer briefly to FIG. 4) of approximately 10 degrees. Other inclined angles are contemplated as being within the spirit and scope of the invention. (For example, incline angles θ of between approximately 5 degrees and 15 degrees can be used, although it will be understood that a more gradual incline may require a longer pipe 12 and a more abrupt incline may cause undue turbulence.)
Thus, baffle assembly 40 can be described as a plurality of structural inserts that effectively narrows the cross section of the round pipe, each insert having a rectangular cross section transverse to the pipe, the inserts collectively smoothly directing essentially all of the fluid that would otherwise flow through the round pipe instead through the rectangular, e.g. square, cross-sectional turbine, i.e. within the turbine's perimeter.
Those of skill in the art also will appreciate from FIG. 3 (and also from FIG. 4) that each of the eight baffles that form a part of baffle assembly 40 is equipped with a notch or vent 60 at its distal extremity, the notch creating a small opening between the baffles and their corresponding interior mating surfaces of cylindrical pipe 12. These notches and the resulting openings provide fluid flow through pipe 12 exterior to baffle assembly 40, thus filling what would otherwise be a void and providing a relatively static and stable fluid pressure outside the baffle assembly but within the pipe. The notches thus avoid incidental formation in that otherwise void region of pipe 12 of a no- or low-fluid-pressure condition that might otherwise undesirably stress or deform baffle assembly 40. Thus, the notches may be referred to herein as pressure-equilibrium-promoting features.
Those of skill in the art will appreciate that baffle assembly 40 may be thought of as having a so-called Venturi effect on the fluid flow through the pipe and thus on the rotation of turbine assembly 16. By reducing the cross section of the pipe, the baffles effectively direct the fluid and increase its flow rate through the cylindrical turbine. It has been determined that flow rate increases significantly (and power thus even more significantly) through baffle assembly 40 over those typical fluid flow rates (e.g. approximately 15 fps) through configurations having no baffle assembly.
FIG. 4 is a front elevation of assembled system 10′. FIG. 4 is thought to be mostly self-explanatory based upon the description above regarding FIG. 3 to which it corresponds. The angle θ of incline of the baffles can be more clearly seen, as can two of the four notches such as notch 60 (which for the sake of clarity is designated only once, although it will be understood that there are eight such notches in accordance with one embodiment of the invention). In accordance with this cylindrical-turbine embodiment of the invention, sufficient clearance around the rotating cylindrical turbine assembly and within the pipe is provided to avoid undue compression of fluid at the turbine sweep boundaries, as shown.
FIG. 5 is an isometric exploded assembly drawing of cylindrical turbine assembly 16. Cylindrical turbine assembly 16 includes an axially (linearly) toothed collar 62 having an inner diameter (ID) slightly greater than an outer diameter (OD) of a shaft 64 around which it extends and to which it is fixedly mounted via upper and lower split shaft couplers 66 and 68. The toothed collar fixedly mounted via upper and lower couplers to the shaft may be collectively referred to herein simply as shaft 70.
Evenly arcuately spaced around and extending radially from shaft 70 are plural (e.g. three, in a so-called 180 degree vertical-axis, helical turbine) upper spokes 72, 74, and 76, and plural (e.g. three) lower spokes 78, 80, and 82. Those of skill in the art will appreciate that the upper and lower spokes are arcuately offset from one another by 60 degrees to mount corresponding plural (e.g. three) helically twisted and arcuately cylindrically extending turbine blades 84, 86, and 88. Corresponding with each of plural spokes 72, 74, 76, 78, 80, and 82 is an inner hub 90, an outer hub 92, and a corner block 94 (which are designated only once in FIG. 5 for the sake of clarity but which will be understood to number the same as the number of blades in the plurality). Those of skill in the art will appreciate that each of the plural airfoil blades mounted on or otherwise connected to or integral with a corresponding airfoil spoke is collectively referred to herein as a blade assembly.
Those of skill in the art will appreciate that each of the plural inner blocks has a correspondingly axially (linearly) toothed inner arcuate surface for a secure grip on toothed collar 62. It will also be appreciated that each of the blades (including the blade portion represented by the spokes) and the corresponding corner blocks have an airfoil cross section, e.g NACA 20 or any other suitable standard. Thus, the blades of cylindrical turbine assembly 16 are of uniformly sized and shaped airfoil cross section over their entire length and substantially all the way to the central shaft that mounts their termini. This represents a striking improvement over prior art helical turbines in which the disks, spokes or struts that mount the helically twisted and arcuate blades generally are not of airfoil cross section and are not of uniform cross sectional size and shape and thus thus are thought by some to cause undesirable cavitation and, more importantly, to lower hydro-electric power generation efficiency. Suitable fasteners such as hex bolts, lock washers, and set screws are used to assemble the component parts of cylindrical turbine assembly 16, as illustrated.
Those of skill in the art will appreciate that more or fewer than three blades can be used in cylindrical turbine assembly 16 in what is referred to herein as an arcuately spaced arrangement, i.e. a uniformly spaced arrangement around the turbine's cross-sectional circumference. For a three-blade cylindrical turbine, the blades may be seen from FIGS. 5 and 6 to be spaced apart 120°, and each blade extends along an arcuate angle Φ of 60° helically around the cylindrical shape (or so-called “sweep”) of the rotating turbine. This three-blade arrangement and airfoil selection produces complete ‘overlap’ of the blades in cross-sectional view and a ‘solidity’ (i.e. the ratio of closed to open cross-sectional area within the pipe) of between approximately 15% and 20%. Those of skill will appreciate that the angle of blade inclination follows from the selected ratio of turbine diameter to height.
Other airfoil configurations and/or other numbers and arrangements of the plurality of blades are contemplated as being within the spirit and scope of the invention. For example, a six-blade cylindrical turbine is contemplated, each blade having a smaller width, to produce a similar solidity configuration and to present smoother operation due to full overlap of the blades within the cylinder (a so-called 360° vertical-axis cylindrical turbine design).
FIG. 6 is an isometric view of assembled cylindrical turbine assembly 16. FIG. 6 is believed to be largely self-explanatory in view of the detailed description above by reference to FIG. 5. FIG. 6 perhaps better illustrates the angles and arrangements and helical curves and twists of the plurality of blades in cylindrical turbine assembly 16. It will be appreciated that the angle of inclination of the blades—i.e. the angle of intersection of a plane in which lies each of the plurality of cylindrical turbine blades (84, 86, and 88) and the central axis of the shaft in accordance with one embodiment of the invention—is approximately 30 degrees, although other helical angles are contemplated as being within the spirit and scope of the invention.
An alternative to the above circular plate 22 b is illustrated in Details A and B, which are fragmentary cut-away side elevations featuring the interior of tee section 12 e. Those of skill in the art will appreciate that absolute and relative dimensions in Details A and B are not to scale, as they are for general structural comparison purposes.
A side-by-side comparison of Detail A, which features flat circular plate 22 b described above, and Detail B, which features a spherically concave circular plate 22 b′, reveals some important advantages of alternative plate 22 b′. Flat circular plate 22 b must be formed of relatively thick material, thereby rendering it heavy and difficult to handle. Spherically concave circular plate 22 b′ on the other hand may be seen to be formed of relatively thin material, thereby rendering it significantly lighter in weight and significantly easier to handle.
This is by virtue of the curvature of alternative plate 22 b′.
Moreover, the central region of flat circular plate 22 b may be seen to be farther from the turbine assembly, thus undesirably extending the length of the turbine's shaft. Conversely, the central region of spherically concave circular plate 22 b′ may be seen to be closer to the turbine assembly, thereby desirably shortening the required length or vertical span of the turbine's shaft.
This too is by virtue of the curvature of alternative plate 22 b′.
From Detail B, concave plate 22 b′ will be understood to be of generally spherical shape with the concavity extending inwardly from generator assembly (not shown for the sake of simplicity and clarity in this view) and toward the turbine assembly 16′ (shown only schematically in these detailed views by way of dash-dot-dot outlines, and the only difference from turbine assembly 16 being the provision of a shorter shaft 64′). This inward or downwardly oriented concave circular plate may be thought of and described herein as an inverted dome (or inverted cupola). While a spherically concave shape is illustrated and described, those of skill in the art will appreciate that suitable modifications can be made thereto without departing from the spirit and scope of the invention. For example, an inverted dome featuring a parabolic rather than a semi-circular cross section is possible, as are other curvilinear cross sections of various aspect ratios (i.e. of various depth-to-width ratios only one of which is shown with some intentional depth exaggeration for the sake of clarity). Also, the cupola-shaped plate in cross section can have a more rounded upper shoulder, producing what might be thought of as complex curvature. All such suitable alternative configurations are contemplated as being within the spirit and scope of the invention.
Those of skill in the art will appreciate that mounting details in such an alternative embodiment are modified straightforwardly to accommodate inverted cupola-shaped circular plate 22 b′ and its bolted assembly through annular seal 22 a onto standard flange 12 e of pipe 12. For example, mounting block 24′ may include a shim 22 bb′ that is spherically convexly curved to mate and seal the spherically concave curvature of the inside of the inverted cupola. A rotor or other moving part of generator 32 will be understood to mount to, for rotation with, the distal end of the turbine's shaft directly above the opening in the central region of spherical concave plate 22 b′. Other components and techniques for accommodating alternative spherically concave circular plate 22 b′ are contemplated as being within the spirit and scope of the invention.
The embodiment illustrated herein is a three-blade cylindrical turbine assembly, but as few as two blades and as many as twenty blades are contemplated as being within the spirit and scope of the invention. More preferably, between approximately two and eleven blades are contemplated. Most preferably, between approximately three and seven blades are contemplated. Other numbers and configurations of helically arced cylindrical turbine blades are contemplated as being within the spirit and scope of the invention. Those of skill in the art will appreciate best perhaps from FIG. 5 that the blades of the cylindrical turbine assembly are characterized along their entire length by airfoil cross sections. This provides the turbine's hydrodynamics and efficiency at generating hydro-electric power. In accordance with this cylindrical-turbine embodiment of the invention, sufficient clearance around the rotating cylindrical turbine assembly and within the pipe is provided to avoid undue compression of fluid at the turbine sweep boundaries (see FIGS. 2 and 4).
Those of skill will appreciate that the helical turbine blades, within the spirit and scope of the invention, can be made of any suitable material and by any suitable process. For example, the blades can be made of aluminum, a suitable composite, or a suitable reinforced plastic material. The blades can be made by rotational or injection molding, extrusion, pultrusion, bending, or other forming techniques consistent with the material used and consistent with the cost-effective production of elongated bodies having substantially constant cross sections. These and other useful materials and processes are contemplated as being within the spirit and scope of the invention.
The dynamic sweep (central diameter) of the rotating cylindrical turbine assembly is greater than its static dimension (central diameter) due to centrifugal forces impinging on the turbine blades. This fact is accommodated by slightly under-sizing the cylindrical turbine relative to the ID of the pipe, e.g. by providing a small but preferably constant clearance of between approximately 0.5 centimeters and 5 centimeters and preferably between approximately 1 centimeter and 3 centimeters, depending upon the diameter of pipe 12 and other application specifics. These spacings are illustrative only, and are not intended to be limiting, as alternative spacings are contemplated as being within the spirit and scope of the invention.
Surprisingly, it has been discovered that baffles 42, 44, 46, and 48 near an upstream region of turbine assembly 16 can increase the electrical energy production by between approximately 14% and 40% and more likely between approximately 20% and 30% over the nominal output of the cylindrical turbine without such an upstream baffle assembly 40 within the pipe.
Those of skill in the art will appreciate that the ratio between the baffles' coverage and the turbine's sweep can be between approximately 10% and 40% and more likely between approximately 20% and 30%. Those of skill in the art will also appreciate that the amount of baffle coverage may be application specific, as it represents a tradeoff between volumetric flow rate and head drop-off. Thus, alternative ranges of baffle coverage and angle relative to turbine sweep are contemplated as being within the spirit and scope of the invention.
Those of skill in the art will appreciate that the cylindrical turbine can serve in power conversion systems other than electric power generation. For example, axial kinetic energy of a fluid can be converted to rotating kinetic energy for any rotating machinery (e.g. a conveyor, a grinder, a drill, a saw, a mill, a flywheel, etc.) including an electric generator or the like (a like alternative, for example, includes an alternator, a magneto, and any other suitable mechanical-to-electric power conversion device). All such uses of the invented fluid turbine are contemplated as being within the spirit and scope of the invention.
Those of skill in the art will appreciate that orientation of the invented system in its many embodiments is illustrative only and should not be read as a limitation of the scope of the invention. Thus, use of terms like upper and lower will be understood to be relative not absolute, and are interchangeable. In other words, the system can assume either vertical orientation, within the spirit and scope of the invention, with the bulkhead housing the generator and the turbine shaft extending relative to the long axis of the pipe either up or down. Indeed, the system can assume any other suitable angle in which the shaft of the turbine extends approximately perpendicular to the direction of the fluid flow.
Those of skill in the art will appreciate that component parts of the invented systems can be made of any suitable material, including steel, aluminum, and polymers or other composites. Most parts can be steel, for example, as are the turbine shafts, flat plates, and baffles. Remaining parts including spokes, hubs, collars, coupling blocks, and blades can be made of machined, extruded, or pultruded aluminum (the blades then being roll-formed and/or twisted into the desired form) or of injection-molded, reinforced plastic or any other suitable polymer or composite (e.g. carbon or graphite). Any alternative material and any alternative forming process is contemplated as being within the spirit and scope of the invention.
Those of skill will also appreciate that the invented systems are of easily scaled dimension up or down, depending upon their application. So that while dimensions generally are not given herein, dimensions will be understood to be proportionately accurately illustrated, the absolute scale of which can be varied, within the spirit and scope of the invention.
Those of skill in the art will appreciate that two or more hydro-electric power generation systems can be installed at defined intervals (in series) within and along a fluid conveying pipe, thereby to multiply power generation. Those of skill in the art also will appreciate that parallel arrangements of two or more hydro-electric power generation systems can be installed within branches of a fluid conveying pipe, thereby alternatively or additionally to multiply power generation. Those of skill in the art will appreciate that kick-start mechanisms can be added to the hydro-electric power generation systems described and illustrated herein, if needed, for use of such systems in tidal (bidirectional, oscillating) flow applications. Those of skill will also appreciate that fail-safe modes of operation can be achieved in the use of the invented in-pipe hydro-electric power generation systems to prevent self-destruction in the event of bearing failure or the like. Finally, those of skill in the art will appreciate that such hydro-electric power generation systems as are described and illustrated herein can be placed within an exterior sleeve conduit that protects the power generation system from the elements and/or that facilitates power distribution along power cables or other suitable conveyances to nearby storage devices or power grids.
It will be understood that the present invention is not limited to the method or detail of construction, fabrication, material, application or use described and illustrated herein. Indeed, any suitable variation of fabrication, use, or application is contemplated as an alternative embodiment, and thus is within the spirit and scope, of the invention.
It is further intended that any other embodiments of the present invention that result from any changes in application or method of use or operation, configuration, method of manufacture, shape, size, or material, which are not specified within the detailed written description or illustrations contained herein yet would be understood by one skilled in the art, are within the scope of the present invention.
Accordingly, while the present invention has been shown and described with reference to the foregoing embodiments of the invented apparatus, it will be apparent to those skilled in the art that other changes in form and detail may be made therein without departing from the spirit and scope of the invention as defined in the appended claims.

Claims

1. A cylindrical-turbine power generating system that generates power from the movement of fluids, the system comprising:

a rotatable turbine mounted for rotation with a shaft, the shaft configured to be mounted for rotation between diametrically opposing sidewalls of a generally cylindrical pipe in transverse orientation to the long axis of the pipe, the turbine including plural helically twisted blades defining a generally cylindrical sweep when rotated on the shaft, and

one or more baffle assemblies, each baffle assembly including plural radially extending and inclined baffles configured between the turbine and the generally cylindrical pipe, each baffle assembly configured to direct a determined volume of fluid flowing within the generally cylindrical pipe through the transversely oriented rotatable turbine to cause rotation of the turbine.

2. The system of claim 1, wherein two or more the baffle assemblies are provided on either side of the turbine within the generally cylindrical pipe, and wherein the rotatable turbine is configured to rotate in the same rotational direction regardless of the direction of generally axial fluid flow within the generally cylindrical pipe.

3. The system of claim 2 further comprising:

two diametrically opposed mounts for rotatationally mounting either end of the turbine shaft; and

a generally cylindrical tee section mounted around an access hole formed in the generally cylindrical pipe, the generally cylindrical tee section axially aligned with the shaft, the generally cylindrical tee section including a concave plate characterized by an inverted spherical dome that effectively covers the access hole, supports one of the mounts, and thereby shortens the distance between the two diametrically opposed rotatable-shaft mounts and thus the length of the rotatable shaft.

4. The system of claim 3 further comprising:

a piece of rotating machinery that sits on top of the concave plate, the piece of rotating machinery mounted to an end of the shaft located within the generally cylindrical tee section for rotation with the shaft.

5. The system of claim 4, wherein the piece of rotating machinery is an electric generator or the like.

6. A power generator system for use in a fluid-conveying pipe, the system comprising:

a turbine comprising:

a central longitudinal shaft configured to rotate within diametrically opposed mounts within a generally cylindrical fluid-conveying pipe, the shaft configured to extend substantially perpendicularly to a long axis of the generally cylindrical pipe, a proximal end of the shaft configured to operatively couple with a piece of rotating machinery;

a pair of mounts, a first one thereof configured to mount a distal end of the shaft for rotation in a first circularly cross-sectional sidewall of a generally cylindrical fluid pipe and a second one thereof configured to mount an intermediate part of the shaft for rotation within the generally cylindrical pipe with the shaft extending through the second one of the mounts; and

a plurality of blade assemblies coupled with the shaft between the pair of mounts and extending radially outwardly from the shaft, the blade assemblies being substantially evenly spaced apart therearound, the blade assemblies collectively defining a generally cylindrical shape.

7. The system of claim 6, wherein each of the plurality of blade assemblies includes a helically curved blade mounted on opposite spokes extending radially from a central hub.

8. The system of claim 7, wherein each of the plurality of blades has an airfoil cross section.

9. The system of claim 6, wherein each of the plurality of blades assemblies includes a helically curved blade having an airfoil cross section along substantially the entire length of each blade.

10. The system of claim 9, wherein the overall shape of the turbine is generally cylindrical.

11. The system of claim 10 further comprising:

a pair of opposing hubs coupled with the shaft at the distal and intermediate ends thereof, wherein

each blade assembly includes opposing spoke portions radially extending from each of the opposing hubs, each spoke portion having an airfoil cross section, and wherein each blade assembly further includes an intermediate helically curved and twisted blade portion extending helically between the opposing spoke portions.

12. The system of claim 11, wherein the plural blades number three, and wherein an angle of inclination of each of the plurality of blades relative to a central axis of the shaft is approximately 30 degrees.

13. The system of claim 10 further comprising:

four inclined and radially inwardly extending baffles configured on at least one end of the turbine to extend between the perimeter of the plurality of blade assemblies and an interior of a sidewall of a generally cylindrical pipe, thereby to route a volume of fluid in the generally cylindrical pipe smoothly through the generally cylindrical turbine.

14. The system of claim 13, wherein at least one of the baffles is notched at a curved extremity where it meets the sidewall, thereby to route a volume of fluid in the generally cylindrical pipe into a region outside the baffles.

15. The system of claim 14 which further comprises:

a pair of opposing generally circular hubs each including plural mounting brackets at radially spaced intervals therearound, the plural mounting brackets mounting opposing ends of corresponding ones of the plural blade assemblies.

16. The system of claim 9 further comprising:

a generally cylindrical pipe configured with a diameter substantially equal to the distance between the pair of mounts, the generally cylindrical pipe mounting the turbine for rotation therein in response to fluid flow through the generally cylindrical pipe.

17. The system of claim 16 further comprising:

an electric generator operatively coupled with a proximal end of the shaft for rotation therewith to produce hydro-electric power in response to fluid flow through the generally cylindrical pipe.

18. The system of claim 17, wherein the turbine is configured to rotate in the same rotational direction regardless of direction of generally axial fluid flow through the pipe.

19. The system of claim 6 wherein the turbine further comprises:

opposing hub assemblies, each including a plurality of mounting brackets for securely affixing opposite ends of the corresponding plurality of blade assemblies to the shaft.

20. The system of claim 19 further comprising:

opposing shaft couplers for securely affixing the corresponding hub assemblies to the shaft.

21. The system of claim 6, wherein the plurality of blades define a nominal solidity of between approximately 15% and 50%.

22. The system of claim 6, wherein each of the plurality of blades is inclined at angle of approximately 30 degrees relative to a central axis of the shaft.

23. A cylindrical turbine power generating system that generates power from the movement of fluids, the system comprising:

a turbine comprising:

a central longitudinal shaft configured to rotate within diametrically opposed mounts within a generally cylindrical pipe, the shaft configured to extend substantially perpendicularly to the fluid flow, with one end of the shaft configured to operatively couple with a piece of rotating machinery;

a plurality of bearings, a first bearing configured to mount a distal end of the shaft farthest from the generator to a first support for rotation and a second bearing configured to mount an intermediate part of the shaft to a support for rotation, with the shaft extending through the second of the bearings; and

a plurality of blades coupled with the shaft between the pair of bearings, the blades extending radially outwardly from the shaft, the blades being substantially evenly spaced apart around the shaft, the blades when rotated around the shaft generally defining a cylinder, the blades being helically twisted and being characterized along their substantial length by an airfoil cross section.

24. The system of claim 23, wherein the plurality of blades is mounted to the shaft with radially extending spokes also characterized along their substantial length by an airfoil cross section.

25. The system of claim 24, wherein the number of blades is three, and wherein each of the plurality of blades of the turbine extends in an approximate 60 degree arc around the defined cylinder's cross-sectionally circular circumference.

26. The system of claim 25, wherein each of the plurality of blades of the turbine includes a uniformly sized and shaped airfoil cross-section along substantially the entire length of each blade.

27. The system of claim 26, which further comprises:

a pair of opposing generally circular hubs attached to the shaft of the generally cylindrical turbine, each hub including plural mounting brackets at radially spaced intervals around their circumference, the plural mounting brackets mounting opposing ends of the plurality of blades via corresponding plural spokes.

28. The system of claim 23, wherein each of the plurality of blades extends in a helical arc around the circumference of the cylinder.

29. The system of claim 28, wherein the plurality of blades define a solidity of between approximately 15% and 30%.

30. The system of claim 29 further comprising:

an electric generator operatively coupled with the proximal end of the shaft for rotation with the shaft to produce electric power in response to fluid flow.

31. The system of claim 30, wherein the turbine is configured to rotate in the same direction, regardless of the direction of fluid flow.

32. The system of claim 23, wherein each of the mounts securing the turbine shaft includes bearings.

33. The system of claim 23 further comprising:

four inclined and radially extending baffles configured on either end of the turbine to extend between the perimeter of the plurality of blades and an interior of a sidewall of a generally cylindrical pipe, thereby to route fluid in the generally cylindrical pipe through the generally cylindrical turbine.

34. The system of claim 33, wherein each of the four baffles is inclined relative to the cylindrical pipe at an angle of between approximately 5 and 15 degrees.

35. The system of claim 34, wherein at least one of the baffles is notched at a curved extremity where it meets the sidewall, thereby to route a volume of the fluid in the generally cylindrical pipe into a region outside the baffles.

36. The system of claim 35, wherein each of the mounts includes spherical roller bearings.

37. The system of claim 36, wherein the shaft includes an axially linearly toothed exterior surface.

38. The system of claim 37 further comprising:

opposing hub assemblies configured to mount the plural blades, the hub assemblies including axially linearly toothed interior surfaces mate-able with the toothed exterior surface of the shaft; and

39. The system of claim 26 further comprising:

a generally cylindrical pipe configured with a diameter slightly greater than the distance between the pair of hubs on the turbine shaft, the generally cylindrical pipe mounting the turbine for rotation therein in response to fluid flow through the generally cylindrical pipe.

40. The system of claim 39, further comprising:

an electric generator or the like operatively coupled with a proximal end of the shaft for rotation therewith to produce electric power in response to fluid flow through the generally cylindrical pipe.

41. The system of claim 40, wherein the turbine is configured to rotate in the same rotational direction, regardless of the direction of generally axial fluid flow through the pipe.

42. The system of claim 41, wherein each of the mounts securing the turbine shaft includes bearings.

43. The system of claim 42, further comprising:

a generally cylindrical tee section configured to mount to an outer sidewall of the generally cylindrical pipe, the tee section housing an electric generator that is operatively coupled for rotation with the shaft of the turbine to produce electric power when the turbine is rotating.

44. The system of claim 43 further comprising:

a cylindrically arched plate configured to cover an access hole in the generally cylindrical pipe to substantially prevent fluid flow into the generally cylindrical tee section.

45. The system of claim 46 further comprising:

a circular flat or concave plate that covers the access hole into the generally cylindrical tee section.

46. The system of claim 45 further comprising:

a generator that sits on top of the circular flat or concave plate.

47. In a cylindrical turbine including a central shaft, opposing hubs, spokes mounted on the opposing hubs and extending radially therefrom, with the spokes mounting helically twisted blades on their distal ends, the improvement comprising:

configuring the spokes and the twisted blades with substantially uniformly sized and shaped airfoil cross sections thereon along the substantial lengths of each.

48. The improvement of claim 47, wherein there is no configuring of any of the spokes or twisted blades with transversely mounted radial blades thereon.