US20170016448A1

US20170016448A1 - Fluid pumping system with a continuously variable transmission

Info

Publication number: US20170016448A1
Application number: US14/800,546
Authority: US
Inventors: Kevin Ralph Younker
Original assignee: Individual
Current assignee: Individual
Priority date: 2015-07-15
Filing date: 2015-07-15
Publication date: 2017-01-19
Also published as: EP3322490A4; WO2017008145A1; AU2016292965B2; US20200408215A1; US10801501B2; EP3322490A1; AU2016292965A1; US20180001123A1

Abstract

A technique for providing a water pumping system suitable for fighting wildfire, flood mediation, sewage transport, and the like is revealed. The system includes an internal combustion engine, a CVT with an input shaft and an output shaft, and a pump with an axial flow impeller. In one variation, multiple impeller stages are used and/or several systems are daisy-chained to provide for suitable delivery of water from its source. In another form, the system is carried by an all-terrain vehicle, side-by-side, or the like, to reach remote areas that need to move water to address a hazardous condition.

Description

BACKGROUND

The present application relates generally to unique techniques, systems, methods, processes, apparatus, devices, combinations, and equipment for pumping water-containing liquids and slurries; and more specifically, but not exclusively, relates to unique pumping techniques to fight fire, mitigate flooding, and similar applications. Additionally or alternatively, the present application relates to unique pumping equipment that includes a rotary power source, a continuously variable transmission, a rotodynamic pump, and/or arrangement of such equipment that is uniquely mobile.
Existing pumping systems are ill-suited to transport to remote locations to fight wildfire, flooding, and address other conditions hazardous to the environment and/or well-being of people. Frequently, these existing systems weigh considerably more than can be readily carried by vehicles over rough terrain. So-called pump trucks, commonly found in fire truck fleets, are generally incapable of travel over such terrain and typically provide poor return under such situations. Likewise, airdrops of water and/or fire retardants to fight fire are typically very inefficient from a cost-benefit standpoint. The water flow generated by existing schemes often leaves a lot to be desired, and such systems often have various shortcomings sometimes to the point of being ineffectual. Thus, there remains a need for further contributions in this area of technology.
By way of transition from this Background to subsequent sections of the present application, one or more abbreviations, acronyms, and any definitions thereof, are set forth below and supplemented by example or further explanation where deemed appropriate. Among other things, these definitions are provided to: (a) resolve meaning sometimes subject to ambiguity and/or dispute in the applicable technical field(s) and/or (b) exercise the lexicographic discretion of any named inventor(s), as applicable:
1. “Water” broadly refers to a liquid compound in which a molecule consists of two hydrogen (H) atoms covalently bonded to a single oxygen (O) atom (dihydrogen monoxide or H₂O), inclusive of any isotope of hydrogen or oxygen and inclusive of its temporary ionic forms of the proton (H⁺) and hydroxyl ion (OH⁻). Further, as used herein “water” is inclusive not only of liquid H₂O in pure form, but also any nongaseous fluid mixture including liquid H₂O and one or more other substances in a gas, liquid, and/or solid state. By way of nonlimiting example, water includes a nongaseous fluid in which liquid H₂O is mixed with: (a) one or more different gases, liquids, and/or solids (solutes) in solution each with some nonzero degree of dissolution/solubility where the liquid H₂O is the solvent; (b) any gas or combination of different gases to form foam(s); (b) solid matter dispersed in a slurry, suspension, or colloid; (c) one or more other liquids immiscible with the liquid H₂O, taking either a heterogeneous form or a more dispersed homogeneous form (like in an emulsion); and/or (d) one or more different biochemical compounds, biotic substances, or organisms. Correspondingly, water as used herein may be from any artificial or natural source if of a nongaseous fluid form including liquid H₂O, such as: a potable or unpotable liquid, freshwater or seawater, and/or water from any lake, loch, river, reservoir, canal, channel, public utility, water tower, well, pool, stream, brook, creek, pond, spring, swamp, marsh, bayou, estuary, lagoon, bay, harbor, gulf, fjord, sea, and/or ocean—to name just a few.
2. “Water Capacity” as used herein means the volumetric flow rate of water (see definition above) relative to time in imperial Gallons Per Minute (GPM).
3. “Head” or “Hydraulic Head” (alternatively designated by the variable “H”) means the distance in elevation between two points in a body of fluid. This distance corresponds to the resulting pressure of the fluid at the lower point. For liquid pump arrangements, the lower point is typically an arbitrary datum relative to the point of pump discharge and the higher point is the point of liquid output of a conduit connected to the pump discharge.
4. “Static Head” or “Discharge Head” or “Static Height” or “Static Pressure Head” (all alternatively designated by the variable “SH”) means the maximum height a pump can deliver a liquid above an arbitrary datum relative to the pump discharge. While expressed in terms of elevational distance (height), like the more general term “Head” this measurement directly corresponds to liquid pressure.
5. “Hydrostatic Pressure” (alternatively designated by the variable “HP”) in a liquid can be expressed as the product of the multiplicand variables: height of the liquid column or “hydraulic head” (H), density of the liquid (ρ), and gravitational acceleration (g); such that HP=Hρg and conversely H=HP/(ρg). Frictional loss, turbulence, cavitation, and other factors may influence the determination of head H and hydrostatic pressure HP in a given application.
6. “CVT” is an abbreviation for “Continuously Variable Transmission.” A “Constantly Variable Transmission” is hereby defined to have the same meaning as continuously variable transmission.
7. “Axial Flow Impeller” means a pump rotor turning about an axis of rotation to impart a fluid flow velocity with a magnitude greatest along a direction approximately parallel to the axis of rotation.
8. “Radial Flow Impeller” means a pump rotor turning about an axis of rotation to impart a fluid flow velocity with a magnitude greatest along a direction approximately perpendicular to the axis of rotation.
9. “Mixed Flow Impeller” means a pump rotor turning about an axis of rotation to impart a fluid flow velocity with magnitude greatest along a direction approximately oblique to the axis of rotation.
10. “Rotodynamic Pump” or “Velocity Pump” means a pump that imparts kinetic energy to a fluid in the form of a flow velocity increase with a radial flow impeller, an axial flow impeller, a mixed flow impeller, or other rotor. This increase in kinetic energy may be converted to potential energy (pressure) by subsequently reducing the flow velocity (i.e., within the pump, at the pump discharge, or otherwise downstream of the pump). In principle, energy is continuously imparted to a rotodynamically pumped fluid and consistently added in a kinetic form (velocity increase), but actual practice may be somewhat less ideal. Optionally, a rotodynamic pump may include corresponding vanes, blades, guides, shrouds, volutes, diffusers, or the like suitable to the particular type of impeller/rotor and casing employed; and/or may optionally include multiple stages with the same or different impeller/rotor types arranged in series (daisy-chain), in parallel, or a combination of both. In contrast to the rotodynamic pump/velocity pump, a positive displacement pump captures/traps a fixed fluid amount and discharges it to provide a constant fluid flow at a given speed that in theory is independent of pump discharge pressure (although practical implementation may fall short of such theory). It should be appreciated that a “centrifugal pump” is a type of rotodynamic pump that consistently encompasses the radial flow impeller type, but the meaning of this term is less consistent as to the inclusion or exclusion of axial or mixed flow impeller types.
11. “Endless Loop” means a closed ring structured to encircle, surround, enclose, circumscribe, and/or fit around at least two pulleys making contact with each one to transfer mechanical power therebetween. An endless loop may be formed from a belt, chain, band, cord, cable, strap, rope, fiber, filament, or other structure suitable to contact the corresponding pulleys for power transfer. A pulley may or may not define a groove, track, race, edge, channel, notch, fluting, furrow, shoulder, rail, ridge, step, ledge, score, or the like therealong to contact or receive an endless loop.
12. “Effective Diameter” means the distance a straight line segment extends across a pulley with two opposing segment endpoints coincident to two points of contact between such pulley and an endless loop (defined above) that drives and/or is driven by the pulley; such points of contact (segment endpoints) coinciding with where the endless loop last touches the pulley just before separating therefrom, such segment being approximately perpendicular to a fixed axis of rotation about which the pulley turns, and such pulley being variable to change the distance while rotating about such axis. For a circular type of pulley, such segment may correspond to a diameter (segment intersecting the axis of rotation) or chord of a circle (segment not intersecting the axis of rotation). However, this definition also applies to any other variable pulley shape with an effective diameter range and turns about a fixed rotational axis as it drives or is driven by an endless loop. In correspondence, this definition applies to pulleys provided by a number of radially extending spokes to engage an endless loop (with or without a rim connecting the spokes), interlaced cones, a cage-like structure patterned with edges and vertices corresponding to a circular or cone type of geometric shape, and a single bar-like structure rotating at its center with ends configured to engage an endless loop—just to name a few examples. The change in effective diameter with the change in distance over the operative range may or may not be proportional, continuous, smooth, and/or linear in a mathematical sense. In one form, pulley variability to change effective diameter corresponds to change in pulley width by increasing or decreasing the distance separating opposing sheave portions (defined below) along the axis of rotation; however, in other forms, variability may be realized through a different adjustment.
13. “Nonferrous” means any material composed of no more than about one-half percent (0.5%) iron (Fe) by weight.
14. “Sheave Portion” means a part of a variable pulley that contacts an endless loop for at least a portion of the variable pulley effective diameter operating range—such endless loop driving and/or being driven by such pulley. A sheave portion may or may not completely or partly define a groove, track, race, edge, channel, notch, fluting, furrow, shoulder, rail, ridge, step, ledge, score, or the like along its circumference or its side to guide or make endless loop contact.
The above listing of one or more abbreviations, acronyms, and/or definitions apply to any reference to the subject terminology herein unless explicitly set forth to the contrary, and shall apply whether set forth in lower case, upper case, or capitalized letters. Any acronym, abbreviation, or terminology defined in parentheses, quotation marks, or the like elsewhere in the present application likewise shall have the meaning imparted thereby throughout the present application unless expressly stated to the contrary or unless identical to an entry of the immediately preceding numerical listing of abbreviations, acronyms, and/or definitions, in which case such listing prevails.

SUMMARY

Among the embodiments of the present application are unique systems, apparatus, methods, kits, processes, combinations, equipment, and devices for pumping liquids. Other embodiments include unique techniques to apply, design, prepare, form, make, display, generate, and/or use pumps with a Continuously Variable Transmission (CVT) to ameliorate hazardous conditions, including but not limited to floods, fires, sewage treatment plant overflows, and the like.
A further technique of the present application includes: (a) delivering a mobile water-pumping system to a selected site proximate to a water source that includes a rotary power source, a CVT with a variable turn ratio, and a pump with a rotor, an intake in fluid communication with the water source, and a discharge outlet in fluid communication with a discharge conduit; (b) driving the CVT with the rotary power source; (c) in response to driving the CVT, turning the rotor to convey water from the water source through the discharge conduit; (d) with the CVT, regulating rotational speed of the rotary power source relative to a selected target as the rotor turns; (e) delivering the water from the delivery conduit to a selected location to ameliorate a hazardous condition; (f) during the delivering of the water, increasing the head developed by the pump; and (g) in response to the increasing of the head, decreasing the turn ratio of the CVT to reduce water capacity provided by the pump while maintaining the rotational speed of the rotary power source relative to the selected target. In one form, the pump is a rotodynamic type with the rotor being an axial impeller.
Another embodiment of the present application includes: (a) a rotary power source with a power source output shaft; (b) a CVT mechanically coupled to the power source output shaft that includes a CVT power output shaft with a variable turn ratio between a CVT input rotational speed maintained by the power source output shaft and a CVT output rotational speed of the CVT power output shaft; and (c) a rotodynamic pump including a rotor driven by the CVT power output shaft, the pump including an intake and an outlet and being structured to convey water from the intake through the outlet over a water capacity range with a varying head. One nonlimiting refinement includes means for maintaining the CVT input rotational speed relative to a target speed and means for decreasing the water capacity range in response to increasing resistance from an increase in the head of the pump.
Still another embodiment of the present application comprises a water pumping system including: (a) means for providing rotational power, (b) means for transmitting rotational power by selectively varying a turn ratio over a desired range, (c) means for pumping water, and (d) means for controlling the turn ratio of the transmitting means. In one nonlimiting form, the rotational power means includes means for internally combusting fuel to rotate a power shaft mechanically coupled to the transmitting means, the transmitting means includes means for continuously varying the turn ratio between a first rotating component and a second rotating component, the pumping means includes means rotodynamically pumping water with a rotor, and the controlling means includes means for mechanically varying the turn ratio in response to a change in head of the pumping means.
Yet another form of the present application comprises: (a) operating a vehicle carrying a water pumping system, the system including an internal combustion engine, a CVT with an input shaft mechanically coupled to a first variable pulley and an output shaft mechanically coupled to a second variable pulley, and a pump; (b) driving the input shaft of the CVT with mechanical power from the internal combustion engine; (c) turning the output shaft of the CVT with a variable turn ratio between the input shaft and the output shaft; (d) turning a rotor of the pump by mechanical coupling to the output shaft; (e) by adjusting the first variable pulley and the second variable pulley, regulating rotational speed of the internal combustion engine by decreasing water capacity of the pump in response to increased head of the pump. In one form, the rotor is an axial flow impeller.
A further embodiment includes a vehicle carrying a water pumping subsystem that comprises: (a) means for driving an input shaft of a CVT with rotary mechanical power; (b) means for turning an output shaft of the CVT with a variable turn ratio relative to rotation of the input shaft and rotation of the output shaft; (c) means for rotating a rotor of a pump; and (d) means for regulating the variable turn ratio with a CVT control mechanism responsive to mechanical resistance generated by head of the pump to correspondingly adjust water capacity of the pump over a target range and regulate rotational speed of the internal combustion engine relative to a steady state target.
The above introduction is not to be considered exhaustive or exclusive in nature. This introduction merely serves as a forward to further advantages, apparatus, applications, arrangements, attributes, benefits, characterizations, combinations, components, compositions, compounds, conditions, configurations, constituents, designs, details, determinations, devices, discoveries, elements, embodiments, examples, exchanges, experiments, explanations, expressions, factors, features, forms, formulae, gains, implementations, innovations, kits, layouts, machinery, materials, mechanisms, methods, modes, models, objects, options, operations, parts, processes, properties, qualities, refinements, relationships, representations, species, structures, substitutions, systems, techniques, traits, uses, utilities, variations, and/or other aspects that shall become apparent from the description provided herewith, and from any claimed invention, drawing, and/or other information included herein.

BRIEF DESCRIPTION OF THE DRAWING(S)

FIG. 1 is a partially schematic view of a vehicle-carried pumping system of the present application.

FIG. 2 is a partially schematic view detailing additional aspects of the pumping system of FIG. 1.

FIG. 3 is a partially diagrammatic, exploded view in perspective of certain details of the pumping system of FIGS. 1 and 2.

FIG. 4 is a partially diagrammatic, exploded view in perspective of the pump of FIG. 3 of the pumping system of FIGS. 1-3.

FIG. 5 is a partially diagrammatic, exploded view of selected components of the CVT in the system of FIGS. 1-4 detailing fixed and variable pulleys for the drive pulley and driven pulley with corresponding control mechanisms.

FIGS. 6 and 7 depict a flowchart directed to one nonlimiting routine for operating the subsystem of FIGS. 1-5 on two separate sheets. FIGS. 6 and 7 utilize inter-sheet identifiers/connectors A6, B5, and C5 to extend arrowhead-directed flow lines from one sheet to another, and correspondingly link flowchart operators on different sheets where appropriate.

FIGS. 8 and 9 are partially diagrammatic top and side views, respectively, corresponding to a configuration for a stopped through idle speed operation of the CVT in the subsystem of FIGS. 1-5 as configured with variable width drive and driven pulleys having a turning ratio of four to one for (drive:driven=4:1) (i.e. four turns of the drive pulley provides just one turn of the driven pulley). The side view of FIG. 9 includes a partial sectional depiction in accordance with the section/view line 9-9 shown in FIG. 8.

FIGS. 10 and 11 are partially diagrammatic top and side views, respectively, corresponding to a configuration for a steady state speed operation of the CVT in the subsystem of FIGS. 1-5 as configured with variable width drive and driven pulleys having a turning ratio of one to one (drive:driven=1:1)(i.e. driven pulley turns once for each turn of the drive pulley). The side view of FIG. 11 includes a partial sectional depiction in accordance with the section/view line 11-11 shown in FIG. 10.

DETAILED DESCRIPTION OF REPRESENTATIVE EMBODIMENTS

In the following description, various details are set forth to provide a thorough understanding of the principles and subject matter of each invention described and/or claimed herein. To promote this understanding, the description refers to representative embodiments—using specific language to communicate the same accompanied by any drawing(s) to the extent the description subject matter admits to illustration. In other instances, when the description subject matter is well-known, such subject matter may not be described in detail and/or may not be illustrated by any drawing(s) to avoid obscuring information to be conveyed hereby.
Considering the invention(s) defined by the description and/or the claim(s) further, those skilled in the relevant art will recognize that such invention(s) can be practiced without one or more specific details included in the description. It is also recognized by those skilled in the relevant art that the full scope of an invention described and/or claimed herein can encompass more detail than that made explicit herein. Such unexpressed detail can be directed to apparatus, applications, arrangements, combinations, components, compositions, compounds, conditions, configurations, constituents, designs, devices, elements, embodiments, features, forms, formulae, implementations, kits, modifications, materials, mechanisms, methods, modes, operations, parts, processes, properties, qualities, refinements, relationships, structures, systems, techniques, and/or uses—just to name a few. Accordingly, this description of representative embodiments should be seen as illustrative only and not limiting the scope of any invention described and/or claimed herein.
Referring to the depicted embodiment of FIG. 1, mobile system 20 is illustrated. System 20 includes vehicle 22 in a form structured to travel over rough terrain with Four-Wheel Drive (FWD) subsystem 24. Correspondingly, subsystem 24 includes four ground-engaging wheels 26 (only two of which are shown). FWD subsystem 24 includes any suitable vehicular propulsion power source 27 (the prime mover for propulsion/operation of vehicle 22). Vehicular power source 27 is more particularly depicted in FIG. 1 as internal combustion engine 28 with standard supporting components and subordinate subsystems like a fuel reservoir, a corresponding drive train with a transmission, operator controls, cooling circuit, and/or other auxiliary devices (not shown). Such transmission for vehicle 22 may be structured with a fixed number of speeds (each corresponding to a number of different engine-to-wheel turn ratios or “gears”) that is responsive to an operator controlled clutch (manual), an automatic, hydraulic (i.e. torque converter) variety with multiple discrete speeds/gears that change in accordance with a selected operational curve (targeting greatest engine output torque, power, efficiency, or the like), an electronically-controlled clutch or clutches operating similar to the hydraulic discrete gear type in the alternative or in addition. System 20 further includes pumping system 30. In certain embodiments, vehicle 22 may be a side-by-side (sometimes called a Utility Task Vehicle (UTV) or Recreational Off-Highway Vehicle (ROV)), a ruggedized/customized all-terrain conveyance dedicated to the transport and application of system 30 with various subsystems being highly integrated and all subject to centralized operator control, a flatbed or pick-up truck with space sufficient to carry system 30, or the like. In one form, system 30 only requires a vehicle weight capacity of about 300 pounds.
Pump system 30 includes rotary power source 40, Continuously Variable Transmission (CVT) 60, and pump 80. Rotary power source 40 provides power to operate pump 80 via CVT 60 (accordingly, source 40 is the prime mover of system 30). System 30 further comprises intake conduit 82 having an inlet 81 with intake filter 120 in fluid communication therewith as provided by a sealed engagement thereto. The opposite end of intake conduit 82 is coupled in sealed engagement with intake 92 as defined by intake plate 96 (not shown until FIGS. 3 and 4), which draws water into the remainder of pump 80 (see, FIGS. 2-4) from source W. Water intake from source W occurs when pump 80 generates suction/lift through intake filter 120 submerged in source W and conduit 82 in fluid communication with filter 120. Pump 80 pressurizes water for output through outlet 94 in fluid communication with output conduit 84.
Accordingly, system 30 is structured to convey/transfer water from water source W to a selected destination for various desired purposes, including, but not limited to the mitigation of a hazardous conditions to persons and/or the environment, such as fighting the depicted wildfire F, among other things. Conduit 84 discharges water through manifold 85 that terminates in nozzles 86 proximate to wildfire flames F. One example of hydraulic head H for pump 80 is illustrated in FIG. 1 with respect to the elevational extension of output conduit 84. It should be appreciate that in other firefighting applications, manifold 85 may be of a type that divides/splits water flow among multiple water hoses with or without separate nozzles. These hoses may be routed to different areas (not shown). Alternatively or additionally, the water output from conduit 84 may be directed to wet-down selected areas to provide a form of firebreak and/or otherwise retard/prevent the spread of fire.
Referring additionally to FIG. 2, pump 80 is configured to remove flood water from the water source W via filter 120 in fluid communication with intake conduit 82 at inlet 81; where like reference numerals refer to like features previously described. This flood water is pressurized for discharge through output conduit 84 by rotation of axial flow impeller 90 of pump 80. Such discharge is transported to a location away from the flooded area without threat of further flooding via output conduit 84 (location and water output from conduit 84 not specifically not shown). In certain nonlimiting alternatives, the configuration of system 30 in FIG. 2 may be directed to the exigent prevention of sewage and/or chemical waste spillage or overflow relative to a designated containment area. In still other nonlimiting alternatives, system 30 may be used for the routine transfer of sewage between different ponds and/or routine irrigation applications (not shown).
Continuing to refer to both FIGS. 1 and 2, rotary power source 40 is provided in the form of an internal combustion engine 42 as shall be further described hereinafter along with other aspects of system 30—but certain variations at the vehicle/system level are first considered. In certain other embodiments, rotary power source 40 is structured to propel vehicle 22 as well as power pump 80 via CVT 60—in which case engine 28 may be absent, adapted to work in concert with source 40 and/or otherwise be applied. In a complementary fashion, still other alternative embodiments structures engine 28 of FWD subsystem 24 to both propel vehicle 22 and power pump 80—in which case, rotary power source 40 may be eliminated, adapted to work in concert with engine 28 for vehicle propulsion or pump operation, and/or differently applied. In still another embodiment, a suitable watercraft carries system 30 on a body of water that offers a better way to reach certain wildfires F than traveling overland. Such body of water may also provide a ready water source W (not shown). In yet another embodiment, system 30 is transported at least partway by air to the shore area of a selected lake, pond, pool, stream, or river, and suitably positioned to address wildfire F or other hazardous condition(s). Air transport may take place by suitable fixed wing float planes, other fixed wing aircraft, and/or rotary wing aircraft (e.g. helicopters) (not shown).
Rotary power source 40, and more particularly engine 42, provides mechanical power with a rotating shaft 58 a turning at speed “n” typically designated in units of Revolutions Per Minute (RPM). In certain embodiments, CVT power input shaft 58 b is mechanically coupled to shaft 58 a of engine 42 in a one-to-one (1:1) turn ratio relationship by direct connection of the two. For such direct 1:1 connection, shafts 58 a and 58 b may be joined by splining, a keyway/key joint, sleeve coupler, flange coupling, clamp/split-muff coupling, or such other manner as would be known to those of ordinary skill in the art. Alternatively, a turn ratio other 1:1 may be provided by a mechanical linkage between shafts 58 a and 58 b (not shown). Such linkage may be comprised of different diameter meshed spur gears, different diameter pulleys with an endless loop around them to transfer mechanical power therebetween, a torque converter, or the like (not shown).
Engine 42 includes multiple reciprocating pistons 54 (only one of which is symbolically shown in FIG. 2) coupled to turn crankshaft 56. In correspondence, crankshaft 56 turns to provide rotary power to power output shaft 58 a. Engine 42 is of an internal combustion type with intermittent combustion of an air/fuel charge in each of a number of cylinders. More particularly, the depicted engine 42 is a multiple cylinder/piston type (typically six or more cylinders/pistons), four-stroke (four-cycle), spark-ignition (SI), gasoline fuel-injected type with multi-valve design. Engine 42 is supplied combustible fuel from fuel source 48. Engine 42 receives intake air through air intake 50 to blend with fuel to provide a combustible air/fuel charge. Engine 42 further includes turbocharger 52 structured to apply boost pressure to intake air—particularly increasing the presence/density of oxygen available to mix with the fuel to form the air/fuel charge with relatively greater energy content—and correspondingly increase engine combustion performance.
Four-stroke operation of engine 42 is next briefly described. During the first stroke, piston 54 moves downward in the cylinder to draw compressed air from turbocharger 52 through one or more open intake valves and into the cylinder. Concurrently, fuel is injected by port and/or direct injection into the cylinder to mix with the compressed air, resulting in selected air/fuel mixture characteristics. The fuel injection timing may follow a specified profile relative to the downward intake stroke (first stroke) and/or the subsequent second stroke (compression stroke). During the compression stroke, all cylinder valves are typically closed (not shown), trapping the air/fuel mixture in the cylinder, and piston 54 moves upward to further compress this mixture. The resulting combustible charge is fully formed by completion of the compression stroke at or near top dead center of the second stroke. The compressed charge is then spark ignited to convert chemical energy of the charge to mechanical energy through the chemical reaction of combustion. This combustion results in expanding gases that push against piston 54, forcing it downward during the third stroke (power stroke). During the power stroke, piston 54 moves downward through cylinder until it reaches bottom dead center. As the power stroke occurs, all valves are closed and the effective volume of the cylinder expands, containing the combustion products (exhaust). This exhaust is pushed out of the cylinder through one or more opened exhaust valves during the fourth and final stroke, the upward exhaust stroke. These four strokes are then repeated indefinitely in each cylinder to rotate crankshaft 56 and correspondingly turn shaft 58 a with the objective of achieving a steady state operation at rotational engine speed n.
The exhaust is collected from engine 42 through an exhaust manifold (not shown) that is discharged through engine exhaust outlet 53. The collected exhaust may travel through a catalytic converter and/or muffler device (not shown) before exiting through outlet 53. In the depicted embodiment, engine coolant circulates through one or more engine cooling jackets (not shown). Such jackets are typically formed in the engine block and cylinder heads, which are interconnected through certain passages. During operation of engine 42, the circulating water is warmed, removing heat from desired portions/components of engine 42. Because turbocharging typically increases the temperature of the boosted, pressurized input air, the turbocharger 52 may include an intercooler/heat exchanger (not shown) through which the coolant is also circulated. Heat is removed from the circulating coolant with a radiator that may include a cooling fan and/or other heat exchanger(s) (not shown). In addition to or in lieu of the use of a radiator, external water source W may be used to exclusively provide or supplement engine cooling (not shown).
For internal combustion engine 42, the operating point/range is often targeted relative to a particular engine speed range—designated as the engine powerband. Typically, the engine powerband is specific to the engine design and various operating parameters thereof (such parameters including but not limited to: fuel quality, intake air constitution, ambient temperature/humidity, coolant/lubrication effectivity, engine wear, and/or certain maintenance factors, or the like). Certain engine speeds n are often of particular interest: (a) speed n corresponding to the best engine efficiency designated as BEpeak (n=BEpeak), (b) speed n corresponding to greatest output torque designated as Qpeak (n=Qpeak), and (c) speed n corresponding to the greatest output power that is typically expressed as brake horsepower and designated as BHpeak (n=BHpeak) herein. It is not unusual for each of these three rotational speeds to differ from one another (BEpeak≠Qpeak≠BHpeak). Commonly, the engine powerband encompasses all three of these speeds with Qpeak and BHpeak being at or near the minimum and maximum extremes of the powerband, respectively, for typical multiple cylinder, four-stroke engine designs that use common commercially available fuels. Likewise, for such designs, BEpeak is often somewhere in between Qpeak and BHpeak (i.e. Qpeak≦BEpeak≦BHpeak). Indeed, the engine powerband is often defined with Qpeak at or near its minimum and BHpeak at or near its maximum (i.e. engine powerband Qpeak≦n≦BHpeak). In racing cars, a powerband in excess of 14,000 RPM is not unusual. In a more typical engine design dedicated to sustained operation of pump 80 via CVT 60, the powerband may extend from about 8700 RPM through about 10,800 RPM (Qpeak≈8700 RPM≦n≦10,800 RPM≈BHpeak); and the target steady state operating point is set to about the peak output brake horsepower, BHpeak≈n≈10,800 RPM. These parameters may be associated with a four-stroke, multi-valve, turbocharged SI engine type that uses common gasoline and has heavy-duty cooling. In another gasoline-fueled example of similar design, a flat Qpeak range is established: 3500≦Qpeak≦6000 RPM with a more “peaked” BHpeak≈7000 RPM. It should also be appreciated that engine designs and performance parameters can be adjusted to some extent to provide one or more wider, flatter engine powerband parameters or to provide for a more pronounced higher peak of one or more powerband parameters. For roadworthy diesel-fueled engines, powerbands are generally lower and the peaks more pronounced compared to gasoline-fueled engines. For one typical diesel example 1500 RPM≦Qpeak≦2000 RPM and 3500 RPM≦BHpeak≦4500 RPM.
Engine 42 further includes engine controller 55 that is adjustable to determine an acceptable steady state target speed n (such as BHpeak) and regulates various operating parameters such as engine fueling, ignition timing, and the like to keep speed n at or near its target steady state operating point (speed). This operating point is selectable with controller 55. In one form, controller 55 is a standard type of electronic Engine Control Module (ECM). While controller 55 regulates engine 42 relative to its target operating point, engine load changes (i.e. load transients) could potentially vary engine speed n to a significant degree before controller 55 returns engine 42 to steady state operation. Transient recovery may be improved by using a number of techniques such as negative feedback, feed-forward control, load change prediction, prognostics, load sensing/monitoring, and the like. Also, performance can improve if equipment external to engine 42/controller 55 responds to a load transient by limiting the magnitude and/or duration effectively realized by engine 42/controller 55. Among other things, CVT 60 compensates for transients as more fully described in connection with FIG. 2 first and later FIGS. 5-11.
CVT 60 further includes variable width pulley 62 that is fixed to rotate with CVT power input shaft 58 b, and variable width pulley 68 fixed to rotate with CVT power output shaft 70. Endless loop 66 fits about both pulleys 62 and 68, frictionally engaging each so that as pulley 62 turns, endless loop 66 rotates about both pulleys 62 and 68, driving rotation of pulley 68 and CVT power output shaft 70 fixed thereto. Endless loop 66 is formed from a belt 67 that fits about pulleys 62 and 68 and frictionally engages each one. CVT 60 also includes CVT drive mechanism 75 to govern width presented by pulleys 62 and 68. For certain embodiments, it should be appreciated that pulley width variation causes the pulley's effective diameter to change. In one form of such embodiments, the effective diameter decreases with increasing width. Accordingly, by adjusting pulleys 62 and 68 to different widths corresponding to different effective diameters, the turn ratio TR between CVT power input shaft 58 b and CVT power output shaft 70 can be varied over a selected range. In FIG. 2, CVT drive mechanism 75 includes width control mechanism 64 connected to pulley 62, while width control mechanism 68 d for pulley 68 is not shown except in FIGS. 5, 9, and 11 to be considered later. The absence of control mechanism 68 d results because it is not visible in an assembled top view like that in FIGS. 2, 8, and 10 and depiction of mechanism 68 d in phantom or schematically in these figures would obscure other features.
CVT power output shaft 70 is mechanically coupled to impeller shaft 108 of pump 80. Impeller 90 is fixed to shaft 108 to rotate therewith at a rotational speed p. This mechanical coupling of shafts 70 and 108 may be a direct connection with a one-to-one (1:1) turn ratio. As in the case of shafts 58 a and 58 b, shafts 108 and 70 may be joined to form this direct connection by splining, a keyway/key joint, sleeve coupler, flange coupling, clamp/split-muff coupling, or such other manner as would be known to those of ordinary skill in the art. Alternatively a different turn ratio may be provided in other embodiments by a coupling linkage between shafts 70 and 108. In certain further refinements, this linkage may take the form of meshed spur gears of different diameters, pulleys of different diameters linked by an endless loop, a torque converter, or the like (not shown). Consequently, CVT 60 mechanically connects engine 42 to pump 80 to supply rotary power thereto subject to a variable turn ratio TR over the selected range. The variation of turn ratio TR is regulated by mechanism 75 to maintain the rotational output engine speed n at or near a steady state target operating point. The regulation of engine speed n takes priority over other operating parameters, such as those associated with operation of pump 80. CVT 60 generally provides for this priority as will be more fully described in text accompanying FIGS. 5-11.
With reference to FIGS. 2-4, Impeller 90 is of a tri-vane (or tri-blade) axial flow type (shown in schematic form in FIG. 2); where like reference numerals refer to like features previously described. With this form of kinetic pump rotor 91, pump 80 is alternatively designated a type of rotodynamic pump 88 (previously defined). Pump 80 is comprised pump housing 35 (see FIGS. 3 and 4). Housing 35 includes its constituent housing parts, such as plate 96, housing 98, and elbow 100 to be further described hereinafter. Pump impeller housing 98 has an interior surface 102 in the general shape of a right circular cylinder that contains impeller 90 (see FIGS. 3 and 4 especially). Surface 102 defines the margin of rotor passage 102 a through housing 98. Impeller 90 includes a nonferrous, self-lubricious seal 104 along each outer leading edge 106 that is mechanically arranged to moves outward with impeller 90 rotation such that it meets inner surface 102 of housing 98—providing a type of variable geometry blade. In certain embodiments, seal 104 along outer leading edge 106 of impeller 90 forms a tight clearance with surface 102 that can improve impeller performance and correspondingly pump 80 efficiency. Typically, the self-lubricious, nonferrous material comprising seal 104 is selected to be harder than ferrous-based alloys and to be less subject to abrasion and wear. Nonetheless, it is recognized that replacement of seal 104 and correspondingly impeller 90 may be desired from time-to-time to maintain desired performance/efficiency enjoyed by mating seal 104 to surface 102. Even so, the variable-geometry of impeller 90 decreases the need for such replacement and does not necessarily result in the desire to replace housing 98 with the same frequency due to concomitant wear rates.
Specific to FIG. 3, the pump 80 is shown in a partially diagrammatic, perspective view that is in assembled form except for intake plate 96, which is shown in an exploded view to better illustrate features of impeller 90 relative to housing 98 in which impeller 90 resides; while engine 42 and CVT 60 are shown in schematic form to preserve clarity, too. Specific to FIG. 4, pump 80 is shown in more detail with pulley 68 of CVT 60 in a more fully exploded view with certain aspects being schematically depicted so as not to detract from certain details. As shown in both FIGS. 3 and 4, intake 92 is further defined by flow guide ribs 109 that extend from outer circumferential ring 111 to coaxially locate plate bearing/seal 110 along rotational axis R-R of shaft 108. When assembled, bearing/seal 110 slides over impeller bearing/seal 114 within housing 98 near intake 92, providing a journal bearing with a seal that prevents water from reaching the main impeller shaft 108 at the upstream end of impeller 90. As specifically labeled in FIG. 4, the downstream end of impeller 90 slides over bearing 116, engaging O-ring friction seal 118 when assembled within housing 98. Accordingly, water is also prevented from reaching the main impeller shaft 108 through this route. Shaft 108 extends through output elbow 100 along rotational axis R-R to engage CVT power output shaft 70 at bearing 130. Shaft 70 extends through variable width pulley 68 to engage CVT support bearing 112 (shown in FIG. 4 only). Pulley 68, CVT output power shaft 70, impeller shaft 108, and impeller 90 all rotate together about rotational axis R-R when driven by endless loop 66 (loop 66 is not shown in FIG. 4 to preserve clarity). Correspondingly, intake plate 96, axial impeller pump housing 98, and pump output elbow 100 are all joined together by fasteners (such as bolts) with appropriate gaskets, washers, O-rings or other sealing mechanisms therebetween to prevent water loss through the corresponding connections.
During operation, as impeller 90 (a form of kinetic pump rotor 91) turns about rotational axis R-R, it receives water through intake 92 of plate 96 and pressurizes it with a primary velocity component approximately parallel to rotational axis R-R as it exits impeller 90. As a form of rotodynamic pump 88, kinetic energy is also stored as potential energy in the form of pressure in housing 98. Soon after exiting impeller 90, the pressurized water is turned by elbow 100 away from axis R-R to exit through outlet 94 generally perpendicular thereto. Outlet 94 has a cross-section less than that defined by housing 98 or provided at the input to elbow 100. This decrease in cross-sectional area correspondingly increases water flow velocity as it exits outlet 94 at the expense of converting a corresponding amount of potential energy in the form of pressure to kinetic energy. The increase in kinetic energy is in the form of increased water flow velocity. As best shown in FIGS. 1 and 2, pump output conduit 84 is in sealed engagement with elbow outlet 94 to direct the water flow in a desired manner. During steady state operation of engine 42 at speed n, load transience typically occurs with a non-negligible change in head H of pump 80. This change in head H causes rotational speed p of impeller 90 to change along with shaft 70 coupled thereto. A non-negligible increase in head H results in an increase in the effective weight of water bearing down on impeller 90 pushing against it to cause rotational speed p to slow, which imposes an increase in mechanical resistance realized by CVT 60. In contrast, a non-negligible decrease in head H reduces loading on impeller 90 and correspondingly CVT 60. FIG. 5 provides a partially diagrammatic, exploded view of CVT 60. FIGS. 8-9 provide partially diagrammatic top and side views of CVT 60, respectively, for one exemplary turn ratio, and FIGS. 10-11 provide partially diagrammatic top and side views of CVT 60, respectively, for another exemplary turn ratio; where like reference numbers refer to like features. It should be understood that section line 9-9 shown in the top view of FIG. 8 corresponds to the side view of FIG. 9; and section line 11-11 shown in the top view of FIG. 10 corresponds to the side view of FIG. 11.
CVT drive mechanism 75 responds to the mechanical resistance change from a transient by adjusting width of pulley 68 (alternatively designated driven pulley 65) with control mechanism 68 d, changing the turn ratio TR. Control mechanism 68 d is in the form of a helical/coil spring positioned about end portion 70 c of shaft 70. Correspondingly, control mechanism 64 responds to an initial speed change in the rotational speed of shaft 58 b to adjust width of pulley 62 (alternatively designated drive pulley 63)—to the extent that any speed change of shaft 70 is transferred through loop 66 to shaft 58 b. For some minor transients, it is possible that such transients may be sufficiently addressed by the control mechanism 68 d adjustment without noticeable change caused by control mechanism 64; however, for more significant transients, the change in effective diameter of driven pulley 65 as caused by control mechanism 68 d likely will result in a width adjustment of drive pulley 63 by control mechanism 64 through loop 66, changing its effective diameter. In turn, further refinement in effective diameter of driven pulley 65 by mechanism 68 d may occur as a result of the change to pulley 63 as it is “communicated” by loop 66. This back-and-forth refinement may continue for a few iterations, tending to quickly stabilize without significant risk of persistent oscillation, ringing, or otherwise being unresolvable. With these adjustments by mechanism 75, the operating point engine speed is quickly recovered to the extent there is even a noticeable deviation from the steady state target n.
While engine speed n tends to remain at or near the steady state target operating point as head H significantly fluctuates, there is a tradeoff because the adjustment of CVT drive mechanism 75 in response to head H fluctuation, changes impeller 90 rotational speed p. This variation in impeller 90 speed p causes water capacity output from pump 80 to correspondingly fluctuate. Under steady state conditions, variable CVT drive mechanism 75 provides a drive pulley 63 to driven pulley 65 turn ratio (drive:driven=Turn Ratio=TR) that changes along with speed p. Consequently, among the control laws of system 30, are that maintenance of a steady state engine speed n takes priority over steady state provision of water capacity of pump 80 when adjustments of head H result in transients and/or load changes. Accordingly, the CVT 60 turn ratio TR is varied to maintain a steady state target engine speed n by responding to changes to resistance/loading from pump 80 with dynamic turn ratio changes that may be continuously variable as needed to adjust to changing conditions of pump 80 (such as head H). Further details of this methodology are explained in connection with FIGS. 5 and 8-11.
With reference to FIGS. 2-5 and 8-11 collectively, variable width pulley 62 includes sheave portion 62 a fixed to shaft 58 b and moveable sheave portion 62 b. Moveable sheave portion 62 b translates along end portion 58 c of shaft 58 b relative to sheave portion 62 a under certain conditions. For variable width pulley 62, FIG. 8 depicts a pulley width W1 that is greater than pulley width W3 depicted in FIG. 10. As variable width pulley 62 is turned by shafts 58 a, 58 b it receives rotary mechanical power (torque) from engine 42 and accordingly is a form of drive pulley 63. Variable width pulley 62 is mechanically linked by endless loop 66 to a variable width pulley 68. As a result, variable width pulley 68 turns in response to drive pulley 63 via loop 66 making it a form of driven pulley 65—where pulley 65 is driven by drive pulley 63. Endless loop 66 may or may not include inward teeth, kerf, tapering, and/or surface roughening, like spikes, grit coating, or the like to assist with frictional engagement. Additionally or alternatively, pulleys 62, 68 may include surface features to promote frictional engagement such as teeth of either an intermeshing or non-meshed variety, tapering, surface roughening, like surface spikes, grit coating, or the like.
Variable width pulley 68 includes sheave portion 68 a fixed to shaft 70 and a moveable sheave portion 68 b, which moves in translation relative to sheave portion 68 a along end portion 70 c of shaft 70 under certain conditions. Because shaft 70 is mechanically fixed to shaft 108, which turns impeller 90, sheave portion 68 a, shaft 70, shaft 108, and impeller 90 all turn in concert at a pump rotational speed p that may differ from engine rotational speed n of the power output of engine 42 (and input to pulley 62) depending on the turn ratio TR. Control mechanism 64 fixed to sheave portion 62 b of pulley 62 to adjust width of pulley 62 along end portion 58 c in correspondence to speed n of shaft 58 a. Sheave portion 62 b/mechanism 64 moves apart from sheave portion 62 a in translation along end portion 58 c to increase width of pulley 62. As the width of pulley 62 changes in response to the control mechanism 64 (compare pulley 62 width W1 in FIG. 9 to pulley 62 width W3 in FIG. 11), so does the actual pulley diameter considering a circular pulley profile (compare pulley 62 diameter 51 in FIG. 9 to pulley 62 diameter S3), as well as the effective diameter (previously defined). Namely, the effective diameter of pulley 62 is smaller when the pulley 68 is wider (width W1 FIG. 8) because endless loop 66 is riding closer to shaft end portion 58 c in the middle between sheave portions 62 a and 62 b (see FIG. 9); and the effective diameter about pulley 62 is larger when the pulley 62 is narrower (width W3 FIG. 10) because endless loop 66 is riding up the sheave portion(s) 62 a and/or 62 b (see FIG. 11). One example of effective diameter as defined herein is segment C2 extending between points P3 and P4. In this case, segment C2 is close to if not collinear with a diameter intersecting a rotational axis of pulley 62 and opposing points of contact P3, P4 of the circular section shown in FIG. 11.
One form of mechanism 64 is comprised of clutch weights 64 b (schematically depicted) that are pivotally connected to pins that are fixed to mechanism 64. These weights 64 b spin outward with increasing shaft 58 b rotation at speed n. As weights 64 b spin outward, they cause rollers 64 a (schematically depicted) to move along shaft end portion 58 c to advance sheave portion 62 b towards sheave portion 62 a, and correspondingly decrease the width of pulley 62 and increasing the diameter of pulley 62. In addition, the arrangement of mechanism 64 typically includes one or more internal springs (not shown) coupled to weights 64 b to impose a force that must be overcome before weights 64 b can move outward, and so maintains the minimum diameter of pulley 62 while turning from zero (0) to an idle speed determined with the springs. The spring(s) (not shown) may also assist in returning pulley 62 to its minimum diameter at idle speed and maintaining that diameter when rotation stops or even when engine 42 stops immediately with no controlled speed decrease down to idle first. Furthermore, weights 64 b and the configuration of mechanism 64 otherwise are arranged to match and effectively provide a corresponding maximum rotational speed n of shaft (portions) 58 a, 58 b, and 58 c corresponding to the desired steady state desired operating point speed of engine 42. This operating point speed may correspond to peak torque (Qpeak), peak brake horsepower (BHpeak), or peak efficiency (BEpeak). To maximize pump 80 performance, brake horsepower peak output rotational speed of engine 42 serves as the selected operating point (BHpeak) with the corresponding idle speed being set to 35%-40% of the operating point speed. In FIG. 8, pulley 68 width W2 is illustrated, which in comparison is less than pulley 68 width W4 shown in FIG. 10. Variable CVT drive mechanism 75 of CVT 60 includes a width control mechanism in the form of helical coil spring 68 d with a selected spring constant. Spring 68 d is oriented about shaft end portion 70 c and has one end connected to sheave portion 68 a and the opposite end fixed relative to sheave portion 68 b by hub 68 c that collectively limit the outer width range of sheave portion 68 b along shaft end portion 70 c—applying a nominal spring force to pull sheave portions 68 a and 68 b towards each other. Hub 68 c is integral with and an alternative designation of support bearing 112 previously introduced (compare FIGS. 4 and 5 and accompanying description). Width control mechanism spring 68 d varies width of pulley 68 translationally along shaft end portion 70 c by controlling separation of sheave portion 68 b from sheave portion 68 a as a function of speed; where width/sheave separation increases with rotational speed—just the opposite of width control mechanism 64 operation that increase pulley width with rotational speed. Namely, width control mechanism spring 68 d maintains sheave portions 68 a and 68 b close together in a narrow orientation (width W2 in FIG. 8) in accord with a corresponding spring force/spring constant. This configuration applies to the stopped through idle rotational speed of FIG. 8. As rotary speed of shaft end portion 70 c increases past idle, the spring force (as determined at least in part by the spring constant) of width control mechanism spring 68 d starts to be overcome so that the rotational energy of shaft 70 causes width control mechanism spring 68 d to be pulled with a force sufficient to move sheave portion 68 b away from sheave portion 68 a. Resulting separation of sheave portions 68 a and 68 b may be up to and perhaps beyond, a steady state rotational speed of shaft 70 as represented in FIG. 10 by width W4. Conversely, width control mechanism spring 68 d is configured to pull sheave portion 68 b towards sheave portion 68 a as the rotation slows to return to the narrow, stopped/idle configuration. In addition, as the width of pulley 62 changes in response to width control mechanism spring 68 d; the actual diameter of pulley 68 changes (compare S2 of FIG. 9 to S4 of FIG. 11); and effective diameter of pulley 68 changes. In FIG. 9, an effective diameter of pulley 68 with endless loop 66 engaged thereto is the segment/chord C1 shown between endpoints P1 and P2; where C1 is oriented, and P1 and P2 are selected based on the definition of effective diameter. Notably, the effective diameter about pulley 68 is larger when pulley 68 is narrower because the belt is riding up on sheave portion 68 a and/or sheave portion 68 b as depicted in FIG. 9. In contrast, the effective diameter is smaller when pulley 68 is wider (width W4 FIG. 10) because loop 66 is positioned closer to shaft end portion 70 c and is generally more closely centered relative to the distance between sheave portions 68 a and 68 b. In contrast, the effective diameter defined with pulley 68 is larger when pulley 68 is narrower (i.e. width W2 of FIG. 8) because the loop 66 is positioned farther away from shaft end portion 70 c. In several respects, variable width pulley control mechanism 64 is similar to a primary clutch, and width control mechanism spring 68 d may correspond to a secondary clutch that together are sometimes utilized in CVTs of snowmobiles, All Terrain Vehicles (ATVs), side-by-sides (i.e. UTVs), smaller motor bikes/scooters, variable speed drill presses and rotary mills, certain golf carts, and one or more types of small/personal watercraft.
Correspondingly, CVT 60 of system 30 can be described by changing turn ratio “TR” between pulley 62 and pulley 68 as the rotational speed of the shaft end portion 58 c and shaft end portion 70 c change relative to each other past the stopped/idle configuration. Indeed, it should be appreciated that the arrangement of mechanism 64 and mechanism spring 68 d are aimed towards providing a generally constant TR (or perhaps only modestly changing) between a rotational speed of zero (0) where the rotary power source 40/engine 42 is not operating, up to the idle rotational speed. To better understand the usage of turn ratio TR in the present application, consider the general case of a ratio of two real number variables A and C and the certain ways a ratio may be expressed. The ratio statement of “A to C” is equivalent to the mathematical fraction expression NC, which in turn is equivalent to the proportion representation of a ratio of the form A:C using a colon (:) operator. For the fractional form A/B, A is the “numerator” term and B is the “denominator” term and equivalently, for the A:C proportion expression, the common mathematical terminology labels A as the “antecedent” term and B as the “consequent” term, (that is in ratio terms A/C=numerator/denominator=A:C=antecedent:consequent). The proportion (colon) representation is typically used herein to express turn ratio TR. In some representations, one of the antecedent (A) or consequent (C) terms is expressed as one with the other being normalized, as appropriate, to provide the correct ratio expression. Regarding such forms, only the antecedent term A varies or consequent term C varies. With A being variable, TR=A:1=the variable A number of revolutions of pulley 62 to 1 revolution of pulley 68; where Aε
={Real Numbers} (A is a real number); and with B being variable, TR=1:B=one revolution of pulley 62 to the variable B number of revolutions of pulley 68; where Bε
. In one form, the turn ratio TR is about 4:1 (A=4, B=1) for a speed of zero (engine 42 stopped) through approximately selected idle speed. A turn ratio TR of 4:1 (drive:driven) means drive pulley 63 rotates four (4) times for every single revolution of driven pulley 65. The turn ratio configuration of CVT 60 in FIGS. 8 and 9 is representative of a turn ratio TR of 4:1. In contrast, the turn ratio configuration of CVT 60 in FIGS. 10 and 11 is representative of a turn ratio TR of 1:1, which is appropriate for engine steady state operation at or near its selected operating point. A turn ratio TR of 1:1 (drive:driven) means drive pulley 63 turns once for every single revolution of driven pulley 65. In between these values, TR changes continuously in accordance with whether the speed is increasing or decreasing (1≦A≦4). As speed n increases above idle, the effective diameter of pulley 62 increases in response to width control mechanism 64 and the effective diameter of pulley 68 decreases in response to width control mechanism spring 68 d, antecedent value A decreases (A<4) such that TR is between the proportion 1:1 and 4:1 (4:1>TR>1:1). The changing TR between 4:1 and 1:1 represents a continuous upshifting if A is decreasing or downshifting if A is increasing, that may be thought of in terms of various intermediate fixed gear ratios common to non-continuous transmissions based on gear ratios (such as simple manual transmissions). In one four gear analogy, first gear may be considered TR=4:1 and fourth gear may be considered TR=1:1, both of which have been previously introduced in terms of turn ratio TR. Considering these lower and upper extreme gear ratios (sometimes referred to in common parlance as just “gears”), common intermediate gears (gear ratios) second and third, are represented by the ratios 2.07:1 and 1.43:1, respectively—with the understanding that CVT 60 operates on a continuous rather than fixed gear/gear ratio as provided in this comparison. As the effective diameter of pulley 62 approaches its minimum and pulley 68 approaches its maximum (A is equal to about 1), then turn ratio TR is equal to about 1:1. In some alternative embodiments, the range and/or endpoints of the turn ratio range TR differs from that described in connection with FIGS. 5 and 8-11. Recognizing that a higher rotational pump speed p of 15,000 RPM may be realized under certain conditions, some implementations of system 30, one alternative to a 1:1 upper/high end extreme of the turn ratio TR range is to adjust control mechanism 64 and/or control mechanism spring 68 d (and/or dimensioning of certain aspects of endless loop 66, sheave portions 62 a, 62 b, 68 a, 68 b and/or shaft end portions 58 c and 70 c) to allow this maximum pump speed p of 15,000 RPM on the driven side (inclusive of driven pulley 65, shaft 70, shaft 108, and impeller 90) while maintaining the engine speed n target. Selecting an engine speed n target operating point of 11,000 RPM for the drive side, the resulting turn ratio TR of drive:driven=11,000:15,000=0.73:1=1:1.36 for this alternative. With this configuration, shaft 70 turns 15,000 times for every 11,000 turns of shaft 58 b (or equivalently: 73% of a turn of shaft 70 for every 1 turn of shaft 58 b or shaft 70 turns once for every 1.36 turns of shaft 58 b). The governance of system 30 relative to turn ratio TR and various operational aspects of pump 80 are described further in connection with FIGS. 6 and 7 as follows.
Referring to FIGS. 6 and 7, a flowchart of pumping system 30 operating routine 320 is depicted; where like reference numerals refer to like features previously described. For the purposes of routine, the power input variable width pulley 62 is alternatively designated drive pulley 63 from time-to-time and the power output variable width pulley 68 is alternatively designated the driven pulley 65 from time-to-time. Routine 320 begins with start stage 322 on FIG. 6. From start stage 322, routine 320 advances to engine stopped stage 324 (n=0) in which operation of system 20 is halted and pump system 30 is at rest (p=0). In stage 324, the drive:driven pulley turn ratio is 4:1. Further, drive pulley 63 has a small effective diameter with sheave portions 62 a and 62 b being at or near maximum open. In addition, the driven pulley 65 has a large effective diameter with sheave portions 68 a and 68 b at or near closure. Also, the engine controller 55 is configured to operate engine 42 at an operating point corresponding to the peak brake horsepower (BHpeak) provided with engine 42. This halt configuration of stage 324 is typical when vehicle 22 is parked or pumping system 30 is being transported. In certain embodiments, transport during stage 324 includes significant off-road, rough terrain travel of 5 miles or more in order to reach water source W to fight a remote wildfire. Fighting the wildfire includes applying water pumped from source W to flames F in the manner shown in FIG. 1 and described in accompanying text. In certain other embodiments, transport during stage 324 includes significant off-road, rough terrain travel of 5 miles or more in order to reach water source W to abate flooding in the manner shown in FIG. 2 and described in accompanying text.
From stage 324, operating routine 320 continues with conditional 326 that tests whether to start engine 42 or not. If the outcome of the test of conditional 326 is negative (No), routine loops back to repeat stage 324 in which engine 42 is halted and pumping system is at rest stage 324. If the outcome of the test of conditional 326 is affirmative (Yes), then engine 42 is started and operating routine advances to engine 42/system 30 idle operation 328. Conditional 326 and operation 328 would typically be performed once vehicle 22 has stopped at an appropriate location proximate to water source W as part of the preparation process to abate a hazardous condition such as a wildfire, flood, or the like. In operation 328, approximately the same effective diameters and sheave configurations of drive pulley 63 and driven pulley 65 as set forth for stage 324 persist in this operation. It should be noted that during operation 328, pump system 30 is just coming up to idle speed. The turn ratio TR is approximately 4:1 as represented in FIGS. 8 and 9. As previously explained the features of width control mechanism 64 and width control mechanism spring 68 d are configured to maintain this 4:1 turn ratio until operation past idle is initiated. Routine 320 proceeds next to trigger operation 330. Operation 330 prepares to increase engine speed n beyond idle speed as triggered by reaching a certain trigger point relative to idle (typically 35%-40% of steady state/operating point speed), and prepares to change the turn ratio TR, beginning to decrease the drive:driven ratio from 4:1 (drive:driven≦4:1 turn ratio TR). In support of this turn ratio TR change, the effective diameter of drive pulley 63 begins to increase and sheave portion 62 b approaches sheave portion 62 a; and effective diameter of the driven pulley 65 begins to decrease and sheave portions 68 a and 68 b begin to separate. Typically, operation 330 would be performed while vehicle 22 is stationary at a location to ameliorate a fire, flood, or the like.
Routine 320 advances from operation 330 to upshift operation 332. In upshift operation 332 engine 42 speeds up from the trigger point 35%-40% of the engine operating point speed to 100% of its operating point speed. As engine 42 speeds up, drive pulley 63 turns faster so its effective diameter continues to increase with sheave portions 62 b and 62 a coming together to provide the drive pulley effective diameter increase, driven pulley 65 also turns faster so its effective diameter continues to decrease with sheave portion 68 b separating from sheave portion 68 a to provide a driven pulley effective diameter decrease, and continuous shifting between turn ratios TRs result from about 4:1 to about 1:1 that corresponds to upshifting of CVT 60. In certain embodiments, operations 330 and 332 would be performed after transport of system 30 to a remote sight proximate to water source W to prepare for firefighting, flood amelioration, or the like.
From operation 332, routine 320 continues with steady state engine operation 334 per a flow line bridging FIGS. 6 and 7 in the manner indicated by connection flags A6 appearing on each figure. In operation 334, engine 42 is operating at the target operating point (100% of steady state speed) and the drive:driven turn ratio is 1:1. This 1:1 turn ratio corresponds to that shown in FIGS. 10 and 11. To provide this turn ratio configuration of CVT 60, the drive pulley 63 is at or near its maximum effective diameter as provided by sheave portions 62 a and 62 b being at or near closure; and driven pulley 65 is at or near its minimum effective diameter as provided by sheave portions 68 a and 68 b being at or near a maximum open state. Once at the desired remote site proximate to water source W, operation 334 is when water transport from source W to a desired site with system 30 would begin. The hazardous condition abatement operation 420 encompasses all the operations and conditionals circumscribed by the phantom box with the 420 numerical labeling. Operation 420 includes delivering/transporting water with pump system 30 to address an environmentally hazardous condition, which may be performed during execution of any of the circumscribed operations/conditionals. From operation 334, routine 320 continues with conditional 336. Conditional 336 tests whether there is a non-negligible increase in head H of the pump 80. If the test of conditional 336 is negative (No), then routine 320 loops around operation 338 to conditional 340—in other words routine 320 skips operation 338 if conditional 336 is negative. If the test of conditional 336 is affirmative (Yes), then increasing head load compensation operation 338 is executed. Operation 338 continues by adjusting the turn ratio of CVT 60 to decrease water capacity output of pump 80 while maintaining engine speed n at or near 100% of its operation point speed. The non-negligible head H increase causes impeller 90 to slow down, which imparts mechanical resistance to driven pulley 65 via shafts 108, 70. In response, driven pulley 65 slows down, which causes its effective diameter to increase as sheave portion 68 b starts closing in on sheave portion 68 b. Driven pulley 63 responds to the slow down by beginning to open sheave portions 62 a and 62, which causes its effective diameter to decrease. Accordingly, the increased load on CVT 60/engine 42 caused by increasing head H of pump 80 correspondingly adjusts the drive:driven turn ratio from 1:1 towards 4:1 (1:1<drive:driven<4:1), while engine speed n stays at or near its operating point. With this increase in drive:driven turn ratio TR and maintenance of 100% of engine speed operating point, the result is a reduction in the turn rate of shaft 70 and shaft 108 (the “driven” rate) via CVT 60. This reduction causes impeller 90 rotation to slow down, decreasing the water capacity output (volumetric flow rate) of pump 80 as a result of operation 338. Accordingly, the drive pulley (antecedent) tends to get more turns per turn of the driven pulley (consequent) the further the turn ratio TR moves away from 1:1, with the specific turn ratio depending on the degree of resistance/loading by the head H increase. Because the engine speed n is regulated relative to a target, the increasing turn ratio TR causes the output of driven pulley 65 to be slower, reducing the water capacity. The ratio TR may change all the way to 4:1 if the head H increase is large enough, but would not tend to do so during nominal operation of pump system 30. From operation 338, routine 320 advances to conditional 340. Conditional 340 tests whether a non-negligible head H decrease has occurred. If the test of conditional 340 is negative (No), it loops around operator 342 (skipping it) to conditional 344. If the test of conditional 340 is affirmative (Yes), then routine 320 continues with non-negligible decreasing of head H load compensation operation 342. Compensation operation 342 arises most often when an adjustment to water capacity output (and CVT turn ratio TR) has already taken place as a result of execution of operation 338. Compensation operation 342 operates in the opposite manner of compensation operation 338. During execution of operation 342, driven pulley 65 responds to a lighter impeller load by opening sheave portions 68 a and 68 b and correspondingly decreasing the effective diameter of variable width pulley 68 (equivalently driven pulley 65), and drive pulley 63 responds to the change by closing sheave portions 62 a and 62 b and correspondingly decreasing the effective diameter of variable width pulley 62 (equivalently drive pulley 63). As a result of operation 342, water capacity output increases a corresponding amount.
Routine 320 continues from operation 342 to conditional 344. Upon completion of operation 342, water transfer operation 420 is exited (operation 420 relates to the delivery/transfer of water to address an environmentally hazardous condition in parallel with the execution of operations 334, 338, 342 and conditionals 336, 340). Conditional 344 tests whether to return system 30 to idle speed. If the test of conditional is negative, routine 320 proceeds to conditional 352 to determine whether to discontinue system 30 operation. If the test of conditional 352 is negative (No), routine 320 returns to steady state engine operation 334, re-entering operation 420. If the test of conditional 352 is affirmative (Yes), routine 320 returns to the engine halted stage 324 returning to FIG. 6 from FIG. 7 as indicated by connection flags C5 present on each figure to representatively bridge the flow line thereacross, ceasing operation of system 30 and waiting until conditional 326 is affirmative.
Returning to conditional 344, if the test of conditional 344 is affirmative (Yes), routine 320 continues with downshift operation 350, returning to FIG. 6 from FIG. 7, as indicated by connection flags B5 present on each figure to representatively bridge the flow line thereacross. In downshift operation 350, the drive:driven turn ratio TR moves from 1:1 to 4:1 by decreasing the effective diameter of drive pulley 63 with sheave portions 62 a, 62 b parting; and increasing the effective diameter of driven pulley 65 with sheave portions 68 a, 68 b closing. Routine 320 proceeds from operation 350 to engine/system idle operation 328 previously described. Accordingly all the stages, operations, and conditionals (collectively operators) of routine 320 have been described, including the flow line interconnections of all the operators. Routine 320 effectively halts by reaching the loop on FIG. 6 formed between engine halted/pumping system at rest stage 324 and conditional 326 with a negative test outcome (No), which is reached by an affirmative answer (Yes) for conditional 352 (FIG. 7) via connection flags C5.
Many different embodiments of the present application are envisioned. In one example, a methodology includes: providing a mobile water-pumping system to a selected site proximate to a water source, the system including: (a) an internal combustion engine, (b) a pump including an axial flow impeller positioned within a housing defining an intake and outlet, (c) a delivery conduit in sealed engagement with the outlet, and (d) a CVT including a power input shaft and an power output shaft; driving the power input shaft of the CVT with the internal combustion engine; rotating the axial flow impeller with the power output shaft of the CVT to operate the pump; mechanically governing selected operations of the system with the CVT, the CVT transferring power between the power input shaft and the power output shaft in accordance with a variable turn ratio, the CVT being responsive to change in power input shaft speed and power output shaft speed to adjust the variable turn ratio; and during the rotating of the axial flow impeller shaft, moving water from the water source through the intake and discharging the water through the delivery conduit to perform at least one of: (a) fighting fire with the water discharged from the delivery conduit, (b) wetting flammable matter in a designated area to establish a fire break, and (c) moving the water to abate an existing or threatened flood condition.
In another example, a technique of the present application comprises: moving a vehicle off-road to a position relative to a water source, the vehicle carrying a pumping system including: a rotary power source, a CVT with a power input shaft and a power output shaft, and a rotodynamic pump with an operative kinetic pump rotor, an intake, and an outlet; driving the power input shaft of the CVT with the rotary power source at an input rotational speed; turning the rotor with the power output shaft of the CVT to receive water from the water source through the intake and provide the water to the outlet at a first water capacity; delivering the water at the first water capacity through a conduit in fluid communication with the outlet to abate a hazardous condition including one or more of: a fire and a flood; in response to mechanical resistance from an increase in a hydraulic head of the pump, regulating the input rotational speed relative to a target rotational speed by adjustment of a turn ratio defined with the CVT, while the adjustment slows the turning of the rotor with the power output shaft to reduce the first water capacity to a second water capacity; and providing the water at the second water capacity through the conduit to continue to abate the hazardous condition.
A further example includes: an internal combustion engine with a controller and an engine power shaft, the controller regulating the engine to target a desired operating point speed of the engine power shaft; a pump including a housing and an axial flow impeller positioned in the housing, the housing defining an intake to the impeller and an outlet from the impeller; and a CVT including a power input shaft coupled to the engine power shaft to receive rotary engine power therefrom and a power output shaft coupled to the impeller to provide rotary power thereto, the CVT further including: a drive pulley with a first drive sheave fixed to the power input shaft and a second drive sheave movable relative to the first drive sheave; a driven pulley with a first driven sheave fixed to the power output shaft and a second driven sheave movable relative to the first driven sheave; an endless loop positioned about the drive pulley and the driven pulley and contacting each of the drive pulley and driven pulley to turn therewith; a first mechanism coupled to the drive pulley to move the second drive sheave toward the first drive sheave as drive rotary speed increases to increase drive pulley effective diameter and farther apart as the drive rotary speed decreases to decrease the drive pulley effective diameter; and a second mechanism coupled to the driven pulley to move the second driven sheave away from the first driven sheave as driven rotary speed increases to decrease driven pulley effective diameter and closer together as the driven rotary speed decreases to increase the driven pulley effective diameter.
In other embodiments, the rotodynamic pump of the present application includes multiple rotor stages in the same pump unit that may or may not be the same type of impeller/rotor. In one example, two axial flow impeller stages of generally the same type/dimensions are aligned coaxially along a common rotational axis to provide one form of a multistage pump of the present application. In a further refinement, multiple stage impellers of such type may be integrally formed together. In some other embodiments, two or more stages may be utilized in a coaxial or non-coaxial configuration, and/or may be a mix of different types of impellers/rotors in the same pump. The different stages of such multistage pumps may be arranged in a serial (daisy-chained) arrangement, a parallel arrangement, or a combination of both. In other applications multiple pumps of a single or multistage variety may be used in a series, parallel, or a combination of the two. These multiple pump arrangements may all have the same impeller/rotor type or may be a mix of different types of impellers/rotors. Such mixes may occur within a multistage pump of the multiple pump arrangement and/or may occur with respect to different pumps in the multiple pump arrangement. In one multiple pump arrangement applicable to long haul transport of water, a spaced-apart series of pumps may utilized in a daisy-chained fashion (the output of one going to the input of the next, etc. . . . ) to move water from a water source to a remotely located fire and/or to sufficiently move water out of and away from a flood zone. In one alternative, multiple pumping subsystems “daisy-chained” together provide for a greater head distance H than a single pump. Daisy chaining can also be utilized to overcome frictional losses that might result from running long distances. It should be appreciated that multistage pumps and multiple pump arrangements are nonlimiting examples that may be covered by the following claims of the present application to the extent such claims read thereon and/or any equivalent(s) thereof. Indeed, these examples are among many different variations, embodiments, examples, forms, and refinements not shown in the figures that may fall under the coverage of the claimed inventions of the present application.
In certain other embodiments, an axial flow impeller particularly suited to remote/mobile firefighting has a maximum diameter in a range from about 5 inches through about 9 inches. Alternatively or additionally, the brake horsepower output by an internal combustion engine suitable for the same is in a range from about 300 horsepower through about 600 horsepower and runs with a target engine speed operating point of about 10,800 RPM. Some of these, as well as different embodiments have a typical water capacity range from about 2000 GPM through about 15000 GPM; where water capacity is generally lower with a higher-valued head H of the pump in order to maintain engine operation at the desired operating point.
In still different embodiments, the pump system may be applied for: (a) the transfer of waste water/diluted sewage between retention ponds and/or to address potential overflow/cleanup of the same; (b) agricultural applications involving watering of animals and/or plants that may include water transfer to or between irrigation channels or the like; rapid bulk removal of water accumulated indoors due to plumbing failure, incursion of rain/melting snow, or the like—such as rapid removal of water from a flooded crawlspace and/or basement; or other liquid/slurry transfers that would benefit from a high volume rate of transfer—especially if any elevational increase is modest. In yet a further embodiment, the pump system operates in a standalone mode that may or may not include any means of transport or otherwise be suitably mobile. It should be appreciated that width adjustment of drive pulley 63 and driven pulley 65 is mechanically implemented with control mechanism 64 and control mechanism spring 68 d, respectively, being responsive to the rotational speed of respective shafts 58 a and 70. In certain embodiments, a different form of speed-responsive mechanical implementation is utilized. Rather than pure mechanical actuation in response to speed, some alternative embodiments actuate adjustment to the width of drive pulley 63 and/or driven pulley 65 by electric motor (linear or rotary), hydraulically, or pneumatically. In a different implementation, opposing sheaves screw together to correspondingly adjust width. In still further embodiments, a CVT is utilized that has substantially different operating parameters, such as different turn ratio ranges, range extremes, one or more differently operating control mechanisms for a variable pulley CVT type or the like; and/or the CVT type is altogether different, instead being one of many potential alternative types, including but not limited to: a toroidal or roller-based CVT (extroid CVT), a magnetic CVT, a ratcheting CVT, a hydrostatic CVT, a naudic incremental CVT, a Cone CVT, a radial roller CVT, and/or a planetary CVT—just to name a few possibilities. In still other embodiments, a single or dual electronic clutch transmission with a suitable number of speeds could be utilized in lieu of or in combination with a CVT. Further CVT alternatives may be based on a non-continuous type of transmission with one or more gear trains, like a standard automatic transmission and/or manual transmission with or without electronic control suitably configured to transfer mechanical power between the rotary power source and pump subject to certain circumstances and conditions.
In further variations of the present application, engine 42 and/or engine 28 may be adapted to perform other operations, such as generate electric power, supplement one another, or the like. For further embodiments, rotary power source may be a different type of internal combustion engine other than that shown and described as engine 42. For instance, source 40 may be provided as a compression-ignited diesel-fueled engine; a traditional carbureted engine type without fuel injection; less traditional fueling with ethanol, natural gas, liquid petroleum gas, and/or liquid propane, or the like; a Wankel-type eccentric rotor type engine; and a gas turbine engine with constant or pulse type ignition—just to name a few. Alternative or additional rotary power sources for various other embodiments (not shown), may include a variable or constant speed electric motor, a wind-powered rotational power source (windmill or wind turbine with corresponding adjustment to TR values/range of CVT), a rotational power source powered by moving water through/over a dam, waterfall, a fast-moving stream, tidal water movement, and/or such other rotary power prime mover—as may depend on the given application of the pump system—just to provide a few examples.
For still other variations of the present application, the rotor/impeller may be of a type that has more or fewer blades/vanes instead of three as described in connection with the depicted embodiments. One particular alternative is directed to a pump system including a bi-vane axial flow impeller. In some embodiments, a pump system comprises: (a) a rotodynamic pump including a rotor and a housing defining an intake, an outlet, and a passage in which the rotor is positioned, the rotor including an outer edge portion comprised of a self-lubricious, nonferrous material having a hardness greater than or equal to 275 on the Brinell hardness scale; (b) a rotary power source; and (c) a power transmission device mechanically coupled to the rotary power source and the pump to transfer mechanical power therebetween. In one specific refinement of this embodiment, the self-lubricious, nonferrous material is comprised of one or more of: Ag, Al, Au, B, Ba, C, Ca, Ce, Co, Cr, Cs, Cu, F, In, Mo, N, Ni, Pb, Re, Sn, Si, Ta, Ti, V, W, Zn, and Zr. In a more particular form of this refinement, the material resulting from application of the immediately preceding sentence further comprises at least one of: BaF₂, CaF₂, CeF₃, and a chalcogenide, the chalcogenide being formed with one or more of: Al, Ba, Ca, Ce, Co, Cr, Cs, Cu, In, Mo, Ni, Pb, Re, Sn, Ta, Ti, V, W, Zn, and Zr. In another more specific refinement, the material includes one or more of: hexagonal boron nitride, chromium carbide, chromium nitride, molybdenum nitride, silicon nitride, titanium carbide, titanium nitride, and tungsten carbide. In an even more specific refinement, the material comprises a combination of at least two different metal elements each selected from a group consisting of: Al, Ba, Ca, Ce, Co, Cr, Cs, Cu, In, Mo, Ni, Pb, Re, Sn, Ta, Ti, V, W, Zn, and Zr. In another even more specific refinement, a group of sets each represent a unique combination of different atomic element constituents, the material including the different atomic element constituents of one or more of the sets selected from the group, the sets consisting of: {Al, Cr, Ni, Mo}; {Cr, Mo, N}; {Cr, Mo, W}; {Cr, N, Ag}; {Cr, Al, V, N}; {Cr, Al, Si, N}; {Ti, Al, C}; {Ti, Al, N}; {Ti, C, N}; {Ti, Al, V, N}; and {Ti, Al, Si, N}; each of the sets being designated by inclusion within a pair of braces without restriction to a stoichiometric or non-stoichiometric relationship between the constituents of any one of the sets or between the sets relative to each other. In yet another even more specific refinement, a group of sets each represent a unique combination of different compositional constituents in each of two layers of the material, the material including the different compositional constituents of one or more of the sets selected from the group, the sets consisting of: {Ni, Al, Ag, BaF₂/CaF₂,W}; {Ni, Al, Ag, Mo, BaF₂/CaF₂}; {Ti, Al, V, N/Ti, Al, N}; {Ti, Al, N/V, N}; {Ti, Al, C, N/V, C, N}; {Ni, Al, Ag, BaF₂/CaF₂, Ag, Cr}; {Ni, Al, Ag, BaF₂/CaF₂, Ag, Cr}; {Mo₂N/Ag}; {Mo₂N/Cu}; {Mo, N/Cu}; and {Mo, N/Si, N}; the compositional constituents of each of the sets being designated by inclusion within a corresponding pair of braces, and the compositional constituents of each of the two layers being on either side of a backslash positioned in between the corresponding pair of braces.
Any experiment, theory, thesis, hypothesis, mechanism, proof, example, belief, speculation, conjecture, guesswork, discovery, investigation, or finding stated herein is meant to further enhance understanding of the present application without limiting the construction or scope of any claim that follows or invention otherwise described herein—except to the extent expressly recited in such claim or invention. For any particular reference to “embodiment” or the like, any aspect(s) described in connection with such reference are included therein, but are not included in nor excluded from any other embodiment absent reasonable description to the contrary. For multiple references to “embodiment” or the like, some or all of such references refer to the same embodiment or to two or more different embodiments depending on corresponding modifier(s) or qualifier(s), surrounding context, and/or related description of any aspect(s) thereof—understanding two embodiments differ only if there is some substantive distinction, including but not limited to any substantive aspect described for one but not included in the other. Any use of the words: important, critical, crucial, significant, essential, salient, specific, specifically, imperative, substantial, extraordinary, especially, favor, favored, favorably, favorable, desire, desired, desirable, desirably, particular, particularly, prefer, preferable, preferably, preference, and preferred indicates that the described aspects being modified thereby may be desirable (but not necessarily the only or most desirable), and further may indicate different degrees of desirability among different described aspects; however, the claims that follow are not intended to require such aspects or different degrees associated therewith except to the extent expressly recited, but the absence of such recitation does not imply or suggest that such aspects are required to be absent from the claim either. For any method or process claim that recites multiple acts, conditionals, elements, gerunds, stages, steps, operations, phases, procedures, or other claimed features; no particular order or sequence of performance of such features is thereby intended unless expressly indicated to the contrary as further explained hereinafter. There is no intention that method claim scope (including order/sequence) be qualified, restricted, confined, limited, or otherwise influenced because: (a) the method/process claim as written merely recites one feature before or after another; (b) an indefinite article accompanies a method claim feature when first introduced and a definite article thereafter (or equivalent for method claim gerunds) absent compelling claim construction reasons in addition; or (c) the claim includes alphabetical, cardinal number, or roman numeral labeling to improve readability, organization, or other purposes without any express indication such labeling intends to impose a particular order. In contrast, to the extent there is an intention to limit a method/process claim to a particular order or sequence of performance: (a) ordinal numbers (1st, 2nd, 3rd, and so on) or corresponding words (first, second, third, and so on) shall be expressly used to specify the intended order/sequence; and/or (b) when an earlier listed feature is referenced by a later listed feature and a relationship between them is of such a type that imposes a relative order because construing otherwise would be irrational and/or any compelling applicable claim construction principle(s) support an order of the earlier feature before the later feature. However, to the extent claim construction imposes that one feature be performed before another, the mere ordering of those two features is not intended to serve as a rationale or otherwise impose an order on any other features listed before, after, or between them. Moreover, no claim is intended to be construed as including a means or step for performing a specified function unless expressly introduced in the claim by the language “means for” or “step for,” respectively. As used herein, “portion” means a part of the whole, broadly including both the state of being separate from the whole and the state of being integrated/integral/contiguous with the whole, unless expressly stated to the contrary. Representative embodiments in the foregoing description and other information in the present application possibly may appear under one or more different headings/subheadings. Such headings/subheadings go to the form of the application only, which while perhaps aiding the reader, are not intended to limit scope or meaning of any embodiments, inventions, or description set forth herein, including any claims that follow. Only representative embodiments have been described, such that: acts, additions, advantages, alterations, apparatus, aspects, benefits, changes, components, compositions, constituents, deletions, devices, embodiments, equivalents, features, forms, implementations, materials, methods, modifications, objects, operations, options, phases, processes, refinements, steps, stages, structures, substitutions, systems, techniques, and variations that come within the spirit, scope, and/or meaning of any inventions defined or described herein, including any of the following claims, are desired to be protected.

Claims

What is claimed is:

1. A method, comprising:

providing a mobile water-pumping system to a selected site proximate to a water source, the system including: (a) an internal combustion engine, (b) a pump including an axial flow impeller positioned within a housing defining an intake and outlet, (c) a delivery conduit in sealed engagement with the outlet, and (d) a CVT including a power input shaft and an power output shaft;

driving the power input shaft of the CVT with the internal combustion engine;

rotating the axial flow impeller with the power output shaft of the CVT to operate the pump;

mechanically governing selected operations of the system with the CVT, the CVT transferring power between the power input shaft and the power output shaft in accordance with a variable turn ratio, the CVT being responsive to change in power input shaft speed and power output shaft speed to adjust the variable turn ratio; and

during the rotating of the axial flow impeller shaft, moving water from the water source through the intake and discharging the water through the delivery conduit to perform at least one of: (a) fighting fire with the water discharged from the delivery conduit, (b) wetting flammable matter in a designated area to establish a fire break, and (c) moving the water to abate an existing or threatened flood condition.

2. The method of claim 1, in which the CVT includes a variable drive pulley, a variable driven pulley, and an endless loop, and further including:

turning a variable drive pulley with the power input shaft, a drive pulley effective diameter increasing and decreasing in correspondence with drive pulley rotational speed increasing and decreasing;

providing a variable driven pulley connected to the power output shaft, a driven pulley effective diameter increasing and decreasing in correspondence with driven pulley rotational speed decreasing and increasing; and

conveying mechanical power between the drive pulley and the driven pulley with an endless loop encircling the drive pulley and the driven pulley to establish contact with each one, the drive pulley effective diameter and the driven pulley effective diameter collectively establishing the variable turn ratio of the CVT.

3. The method of claim 1, which includes:

opposing CVT operation with mechanical resistance caused by a head increase of the pump in excess of a non-negligible magnitude; and

in response to the resistance, adjusting the variable turn ratio of the CVT to maintain regulation of engine rotational speed relative to a target operating point by increasing turning of the power input shaft relative to each turn of the power output shaft, while the adjusting of the variable turn ratio slows rotation of the impeller to decrease water capacity output from the pump.

4. The method of claim 1, which includes providing the axial flow impeller with a self-lubricious, nonferrous material along one or more edges of the impeller, the one or more edges being structured to meet an inner surface of the housing for the impeller to reduce clearance therebetween to enhance pump efficiency.

5. The method of claim 1, which includes the axial flow impeller having a maximum diameter from about 5 inches through about 9 inches.

6. The method of claim 1, which includes:

carrying the system with a four wheel drive vehicle, the vehicle having a propulsion engine separate from the internal combustion engine carried with the water-pumping system;

traveling off-road over rough terrain at least five miles to reach the selected site proximate to the water source; and

conveying the water from the water source to the intake with an intake conduit, the intake conduit being coupled to the intake at one end and submerged in the water source at another end opposite the one end.

7. A method, comprising:

moving a vehicle off-road to a position relative to a water source, the vehicle carrying a pumping system including: a rotary power source, a CVT with a power input shaft and a power output shaft, and a rotodynamic pump with an operative kinetic pump rotor, an intake, and an outlet;

driving the power input shaft of the CVT with the rotary power source at an input rotational speed;

turning the rotor with the power output shaft of the CVT to receive water from the water source through the intake and provide the water to the outlet at a first water capacity;

delivering the water at the first water capacity through a conduit in fluid communication with the outlet to abate a hazardous condition including one or more of: a fire and a flood;

in response to mechanical resistance from an increase in a hydraulic head of the pump, regulating the input rotational speed relative to a target rotational speed by adjustment of a turn ratio defined with the CVT, while the adjustment slows the turning of the rotor with the power output shaft to reduce the first water capacity to a second water capacity; and

providing the water at the second water capacity through the conduit to continue to abate the hazardous condition.

8. The method of claim 7, in which the CVT includes:

a drive pulley with a first drive sheave portion fixed to the power input shaft and a second drive sheave portion movable relative to the first drive sheave portion;

a driven pulley with a first driven sheave portion fixed to the power output shaft and a second driven sheave portion movable relative to the first driven sheave portion;

an endless loop fit about the drive pulley and the driven pulley and contacting each of the drive pulley and driven pulley to turn therewith;

a first mechanism coupled to the drive pulley to move the second drive sheave portion toward the first drive sheave portion as drive rotary speed increases to increase drive pulley effective diameter relative to the endless loop and farther apart as the drive rotary speed decreases to decrease the drive pulley effective diameter relative to the endless loop; and

a second mechanism coupled to the driven pulley to move the second driven sheave portion away from the first driven sheave portion as driven rotary speed increases to decrease driven pulley effective diameter relative to the endless loop and closer together as the driven rotary speed decreases to increase the driven pulley effective diameter relative to the endless loop.

9. The method of claim 7, in which the adjustment of the turn ratio includes increasing turns of the power input shaft relative to each turn of the power output shaft.

10. The method of claim 7, which includes means for providing the adjustment of the turn ratio.

11. The method of claim 7, in which:

the rotary power source is a form of internal combustion engine having a horsepower rating in a range from about 300 HP through about 600 HP; and

the rotor is a form of axial flow impeller having a maximum diameter in a range from about 5 inches through about 9 inches.

12. The method of claim 11, which includes providing the axial flow impeller with a self-lubricious, nonferrous impeller material along at least a leading edge thereof, the leading edge being structured to meet an inner surface of an impeller housing of the pump to reduce clearance therebetween to enhance pump efficiency.

13. The method of claim 7, in which the vehicle has a propulsion engine separate from the internal combustion engine and the vehicle travels off-road at least 5 miles to reach the water source.

14. An apparatus, comprising:

an internal combustion engine with a controller and an engine power shaft, the controller regulating the engine to target a desired operating point speed;

a pump including a housing and an axial flow impeller positioned in the housing, the housing defining an intake to the impeller and an outlet from the impeller; and

a CVT including a power input shaft coupled to the engine power shaft to receive rotary engine power therefrom and a power output shaft coupled to the impeller to provide rotary power thereto, the CVT further including;

an endless loop positioned about the drive pulley and the driven pulley and contacting each of the drive pulley and driven pulley to turn therewith;

a first mechanism coupled to the drive pulley to move the second drive sheave portion toward the first drive sheave portion as drive rotary speed increases to increase drive pulley effective diameter and farther apart as the drive rotary speed decreases to decrease the drive pulley effective diameter; and

a second mechanism coupled to the driven pulley to move the second driven sheave portion away from the first driven sheave portion as driven rotary speed increases to decrease driven pulley effective diameter and closer together as the driven rotary speed decreases to increase the driven pulley effective diameter.

15. The apparatus of claim 14, which includes a vehicle with a propulsion engine separate from the internal combustion engine, the vehicle carrying the internal combustion engine, the pump, and the CVT.

16. The apparatus of claim 14, which includes means for delivering water from the water source with the pump in a water capacity range from about 2000 GPM through about 15,000 GPM.

17. The apparatus of claim 14, in which the axial flow impeller has a maximum diameter in a range of about 5 inches through about 9 inches.

18. The apparatus of claim 14, in which the axial flow impeller includes a self-lubricious, nonferrous material along at least a leading edge thereof.

19. The apparatus of claim 14, which includes:

means for regulating engine rotary speed relative to the desired operating point despite mechanical resistance caused by a head increase of the pump; and

means for decreasing the water capacity output of the pump in response to mechanical resistance caused by the head increase of the pump to provide power to support performance of the regulating means simultaneously with the decreasing means.

20. The apparatus of claim 14, which includes:

an input conduit operable to sealingly engage with the intake;

an output conduit operable to sealingly engage with the outlet; and

the housing defines an elbow discharge that changes direction of water flow exiting the impeller.