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US20170016448A1 - Fluid pumping system with a continuously variable transmission - Google Patents

Fluid pumping system with a continuously variable transmission Download PDF

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Publication number
US20170016448A1
US20170016448A1 US14/800,546 US201514800546A US2017016448A1 US 20170016448 A1 US20170016448 A1 US 20170016448A1 US 201514800546 A US201514800546 A US 201514800546A US 2017016448 A1 US2017016448 A1 US 2017016448A1
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US
United States
Prior art keywords
cvt
water
pulley
pump
drive
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US14/800,546
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English (en)
Inventor
Kevin Ralph Younker
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to US14/800,546 priority Critical patent/US20170016448A1/en
Priority to AU2016292965A priority patent/AU2016292965B2/en
Priority to CA2946840A priority patent/CA2946840C/fr
Priority to US15/535,705 priority patent/US10801501B2/en
Priority to EP16823580.2A priority patent/EP3322490B1/fr
Priority to PCT/CA2016/050665 priority patent/WO2017008145A1/fr
Publication of US20170016448A1 publication Critical patent/US20170016448A1/en
Priority to US17/010,540 priority patent/US20200408215A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • A—HUMAN NECESSITIES
    • A62—LIFE-SAVING; FIRE-FIGHTING
    • A62C—FIRE-FIGHTING
    • A62C27/00—Fire-fighting land vehicles
    • A—HUMAN NECESSITIES
    • A62—LIFE-SAVING; FIRE-FIGHTING
    • A62C—FIRE-FIGHTING
    • A62C3/00—Fire prevention, containment or extinguishing specially adapted for particular objects or places
    • A62C3/02—Fire prevention, containment or extinguishing specially adapted for particular objects or places for area conflagrations, e.g. forest fires, subterranean fires
    • A—HUMAN NECESSITIES
    • A62—LIFE-SAVING; FIRE-FIGHTING
    • A62C—FIRE-FIGHTING
    • A62C3/00—Fire prevention, containment or extinguishing specially adapted for particular objects or places
    • A62C3/07—Fire prevention, containment or extinguishing specially adapted for particular objects or places in vehicles, e.g. in road vehicles
    • A—HUMAN NECESSITIES
    • A62—LIFE-SAVING; FIRE-FIGHTING
    • A62C—FIRE-FIGHTING
    • A62C31/00—Delivery of fire-extinguishing material
    • A62C31/28—Accessories for delivery devices, e.g. supports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/06—Mobile combinations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0066—Control, e.g. regulation, of pumps, pumping installations or systems by changing the speed, e.g. of the driving engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/181—Axial flow rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D3/00—Axial-flow pumps
    • F04D3/005—Axial-flow pumps with a conventional single stage rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/52—Pulleys or friction discs of adjustable construction
    • F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
    • F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
    • F16H9/12—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members
    • F16H9/16—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts
    • A—HUMAN NECESSITIES
    • A62—LIFE-SAVING; FIRE-FIGHTING
    • A62C—FIRE-FIGHTING
    • A62C25/00—Portable extinguishers with power-driven pumps

Definitions

  • 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.
  • 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 H 2 O), inclusive of any isotope of hydrogen or oxygen and inclusive of its temporary ionic forms of the proton (H + ) and hydroxyl ion (OH ⁇ ).
  • water is inclusive not only of liquid H 2 O in pure form, but also any nongaseous fluid mixture including liquid H 2 O and one or more other substances in a gas, liquid, and/or solid state.
  • water includes a nongaseous fluid in which liquid H 2 O 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 H 2 O 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 H 2 O, 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.
  • liquid H 2 O 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 H 2 O is the solvent; (b) any gas or combination of different gases to form foam(s); (
  • water as used herein may be from any artificial or natural source if of a nongaseous fluid form including liquid H 2 O, 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.
  • a potable or unpotable liquid freshwater or seawater
  • Water Capacity as used herein means the volumetric flow rate of water (see definition above) relative to time in imperial Gallons Per Minute (GPM).
  • 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.
  • 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.
  • “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.
  • CVT Continuous Variable Transmission
  • a “Constantly Variable Transmission” is hereby defined to have the same meaning as continuously variable transmission.
  • 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.
  • Ring 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.
  • Mated 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.
  • “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.
  • 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.
  • 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).
  • 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.
  • 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.
  • 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.
  • 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).
  • 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.
  • 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.
  • 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.
  • Nonferrous means any material composed of no more than about one-half percent (0.5%) iron (Fe) by weight.
  • 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.
  • CVT Continuously Variable Transmission
  • 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
  • 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.
  • 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
  • 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.
  • 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.
  • 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 A 6 , B 5 , and C 5 to extend arrowhead-directed flow lines from one sheet to another, and correspondingly link flowchart operators on different sheets where appropriate.
  • the side view of FIG. 9 includes a partial sectional depiction in accordance with the section/view line 9 - 9 shown in FIG. 8 .
  • the side view of FIG. 11 includes a partial sectional depiction in accordance with the section/view line 11 - 11 shown in FIG. 10 .
  • System 20 includes vehicle 22 in a form structured to travel over rough terrain with Four-Wheel Drive (FWD) subsystem 24 .
  • 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 .
  • 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.
  • UUV Utility Task Vehicle
  • ROV Remote Off-Highway Vehicle
  • 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 .
  • 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.
  • 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).
  • 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.
  • 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).
  • 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.
  • system 30 may be used for the routine transfer of sewage between different ponds and/or routine irrigation applications (not shown).
  • 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.
  • 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.
  • 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.
  • 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).
  • 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).
  • 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.
  • 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.
  • 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.
  • 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.
  • 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).
  • 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).
  • piston 54 moves downward through cylinder until it reaches bottom dead center.
  • 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.
  • 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 .
  • 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.
  • 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).
  • a radiator may include a cooling fan and/or other heat exchanger(s) (not shown).
  • external water source W may be used to exclusively provide or supplement engine cooling (not shown).
  • the operating point/range is often targeted relative to a particular engine speed range—designated as the engine powerband.
  • 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).
  • 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.
  • BEpeak is often somewhere in between Qpeak and BHpeak (i.e. Qpeak ⁇ BEpeak ⁇ BHpeak).
  • 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.
  • 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.
  • a flat Qpeak range is established: 3500 ⁇ Qpeak ⁇ 6000 RPM with a more “peaked” BHpeak ⁇ 7000 RPM.
  • 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.
  • powerbands are generally lower and the peaks more pronounced compared to gasoline-fueled engines.
  • 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 .
  • 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.
  • 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 .
  • pulley width variation causes the pulley's effective diameter to change.
  • the effective diameter decreases with increasing width.
  • 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.
  • 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 .
  • 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 .
  • 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.
  • 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).
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 .
  • 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 .
  • 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).
  • 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.
  • 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 .
  • kinetic energy is also stored as potential energy in the form of pressure in housing 98 .
  • 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 .
  • 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
  • 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 .
  • 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 .
  • 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 .
  • 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.
  • FIG. 8 depicts a pulley width W 1 that is greater than pulley width W 3 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 .
  • 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.
  • 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 .
  • the width of pulley 62 changes in response to the control mechanism 64 (compare pulley 62 width W 1 in FIG. 9 to pulley 62 width W 3 in FIG. 11 ), so does the actual pulley diameter considering a circular pulley profile (compare pulley 62 diameter 51 in FIG.
  • the effective diameter of pulley 62 is smaller when the pulley 68 is wider (width W 1 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 W 3 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 C 2 extending between points P 3 and P 4 . In this case, segment C 2 is close to if not collinear with a diameter intersecting a rotational axis of pulley 62 and opposing points of contact P 3 , P 4 of the circular section shown in FIG. 11 .
  • 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 .
  • 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) 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.
  • 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).
  • 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.
  • pulley 68 width W 2 is illustrated, which in comparison is less than pulley 68 width W 4 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 W 2 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 .
  • width control mechanism spring 68 d 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 W 4 . 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.
  • an effective diameter of pulley 68 with endless loop 66 engaged thereto is the segment/chord C 1 shown between endpoints P 1 and P 2 ; where C 1 is oriented, and P 1 and P 2 are selected based on the definition of effective diameter.
  • 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 .
  • the effective diameter is smaller when pulley 68 is wider (width W 4 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 .
  • the effective diameter defined with pulley 68 is larger when pulley 68 is narrower (i.e. width W 2 of FIG. 8 ) because the loop 66 is positioned farther away from shaft end portion 70 c .
  • 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.
  • ATVs All Terrain Vehicles
  • UTVs side-by-sides
  • smaller motor bikes/scooters smaller motor bikes/scooters
  • variable speed drill presses and rotary mills certain golf carts
  • one or more types of small/personal watercraft 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.
  • ATVs All Terrain Vehicle
  • 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.
  • TR turn ratio
  • 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.
  • 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.
  • A is the “numerator” term
  • the proportion (colon) representation is typically used herein to express turn ratio TR.
  • 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.
  • A variable
  • a turn ratio TR of 4:1 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.
  • 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 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).
  • 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).
  • 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.
  • drive pulley 63 has a small effective diameter with sheave portions 62 a and 62 b being at or near maximum open.
  • driven pulley 65 has a large effective diameter with sheave portions 68 a and 68 b at or near closure.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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).
  • 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.
  • 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 .
  • engine 42 speeds up from the trigger point 35%-40% of the engine operating point speed to 100% of its operating point speed.
  • 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
  • continuous shifting between turn ratios TRs result from about 4:1 to about 1:1 that corresponds to upshifting of CVT 60 .
  • 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.
  • 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 A 6 appearing on each figure.
  • 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 .
  • 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.
  • 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.
  • routine 320 continues with conditional 336 .
  • Conditional 336 tests whether there is a non-negligible increase in head H of the pump 80 .
  • 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 .
  • 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.
  • 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.
  • the result is a reduction in the turn rate of shaft 70 and shaft 108 (the “driven” rate) via CVT 60 .
  • 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 .
  • 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 ).
  • water capacity output increases a corresponding amount.
  • Routine 320 continues from operation 342 to conditional 344 .
  • 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 C 5 present on each figure to representatively bridge the flow line thereacross, ceasing operation of system 30 and waiting until conditional 326 is affirmative.
  • routine 320 continues with downshift operation 350 , returning to FIG. 6 from FIG. 7 , as indicated by connection flags B 5 present on each figure to representatively bridge the flow line thereacross.
  • 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.
  • 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 C 5 .
  • 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
  • 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
  • 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 pulle
  • 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.
  • 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.
  • multiple stage impellers of such type may be integrally formed together.
  • 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.
  • 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.
  • 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. . . .
  • 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.
  • 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.
  • 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.
  • the pump system operates in a standalone mode that may or may not include any means of transport or otherwise be suitably mobile.
  • 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 .
  • control mechanism 64 and control mechanism spring 68 d are responsive to the rotational speed of respective shafts 58 a and 70 .
  • 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.
  • opposing sheaves screw together to correspondingly adjust width.
  • 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.
  • 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.
  • engine 42 and/or engine 28 may be adapted to perform other operations, such as generate electric power, supplement one another, or the like.
  • rotary power source may be a different type of internal combustion engine other than that shown and described as engine 42 .
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the material resulting from application of the immediately preceding sentence further comprises at least one of: BaF 2 , CaF 2 , CeF 3 , 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.
  • 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.
  • 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.
  • 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.
  • 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, BaF 2 /CaF 2 ,W ⁇ ; ⁇ Ni, Al, Ag, Mo, BaF 2 /CaF 2 ⁇ ; ⁇ Ti, Al, V, N/Ti, Al, N ⁇ ; ⁇ Ti, Al, N/V, N ⁇ ; ⁇ Ti, Al, C, N/V, C, N ⁇ ; ⁇ Ni, Al, Ag, BaF 2 /CaF 2 , Ag, Cr ⁇ ; ⁇ Ni, Al, Ag, BaF 2 /CaF 2 , Ag, Cr ⁇ ; ⁇ Ni, Al, Ag, BaF 2 /CaF 2 , Ag, Cr ⁇ ; ⁇ Mo 2 N/Ag ⁇ ; ⁇ Mo 2 N/Cu ⁇ ; ⁇ Mo, N/Cu
  • 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.
  • method claim scope including order/sequence
  • method/process claim as written merely recites one feature before or after another;
  • 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;
  • 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.
  • 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.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Health & Medical Sciences (AREA)
  • Public Health (AREA)
  • Business, Economics & Management (AREA)
  • Emergency Management (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Biodiversity & Conservation Biology (AREA)
  • Ecology (AREA)
  • Forests & Forestry (AREA)
US14/800,546 2015-07-15 2015-07-15 Fluid pumping system with a continuously variable transmission Abandoned US20170016448A1 (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
US14/800,546 US20170016448A1 (en) 2015-07-15 2015-07-15 Fluid pumping system with a continuously variable transmission
AU2016292965A AU2016292965B2 (en) 2015-07-15 2016-06-10 Fluid pumping system with a continuously variable transmission
CA2946840A CA2946840C (fr) 2015-07-15 2016-06-10 Systeme de pompage de liquide dote d'une transmission variable en continu
US15/535,705 US10801501B2 (en) 2015-07-15 2016-06-10 Fluid system with a continuously variable transmission
EP16823580.2A EP3322490B1 (fr) 2015-07-15 2016-06-10 Système de pompage de fluide comprenant une transmission à variation continue
PCT/CA2016/050665 WO2017008145A1 (fr) 2015-07-15 2016-06-10 Système de pompage de fluide comprenant une transmission à variation continue
US17/010,540 US20200408215A1 (en) 2015-07-15 2020-09-02 Fluid pumping system with a continuously variable transmission

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US15/535,705 Continuation US10801501B2 (en) 2015-07-15 2016-06-10 Fluid system with a continuously variable transmission
PCT/CA2016/050665 Continuation WO2017008145A1 (fr) 2015-07-15 2016-06-10 Système de pompage de fluide comprenant une transmission à variation continue

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US15/535,705 Active 2035-07-31 US10801501B2 (en) 2015-07-15 2016-06-10 Fluid system with a continuously variable transmission
US17/010,540 Abandoned US20200408215A1 (en) 2015-07-15 2020-09-02 Fluid pumping system with a continuously variable transmission

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US17/010,540 Abandoned US20200408215A1 (en) 2015-07-15 2020-09-02 Fluid pumping system with a continuously variable transmission

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US (3) US20170016448A1 (fr)
EP (1) EP3322490B1 (fr)
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Also Published As

Publication number Publication date
EP3322490A1 (fr) 2018-05-23
US20180001123A1 (en) 2018-01-04
US10801501B2 (en) 2020-10-13
EP3322490B1 (fr) 2026-01-14
US20200408215A1 (en) 2020-12-31
AU2016292965B2 (en) 2021-05-13
WO2017008145A1 (fr) 2017-01-19
EP3322490A4 (fr) 2019-03-13
AU2016292965A1 (en) 2018-01-18

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