U.S. patent application number 17/010540 was filed with the patent office on 2020-12-31 for fluid pumping system with a continuously variable transmission.
The applicant listed for this patent is Kevin Ralph Younker. Invention is credited to Kevin Ralph Younker.
Application Number | 20200408215 17/010540 |
Document ID | / |
Family ID | 1000005080018 |
Filed Date | 2020-12-31 |
United States Patent
Application |
20200408215 |
Kind Code |
A1 |
Younker; Kevin Ralph |
December 31, 2020 |
FLUID PUMPING SYSTEM WITH A CONTINUOUSLY VARIABLE TRANSMISSION
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.
Inventors: |
Younker; Kevin Ralph;
(athabasca, CA) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Younker; Kevin Ralph |
athabasca |
|
CA |
|
|
Family ID: |
1000005080018 |
Appl. No.: |
17/010540 |
Filed: |
September 2, 2020 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
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15535705 |
Jun 13, 2017 |
10801501 |
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PCT/CA2016/050665 |
Jun 10, 2016 |
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17010540 |
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14800546 |
Jul 15, 2015 |
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15535705 |
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Current U.S.
Class: |
1/1 |
Current CPC
Class: |
A62C 27/00 20130101;
F16H 55/56 20130101; F04D 13/021 20130101; A62C 3/07 20130101; F04B
17/06 20130101; F16H 9/16 20130101 |
International
Class: |
F04D 13/02 20060101
F04D013/02; F16H 9/16 20060101 F16H009/16; A62C 27/00 20060101
A62C027/00; F04B 17/06 20060101 F04B017/06; A62C 3/07 20060101
A62C003/07; F16H 55/56 20060101 F16H055/56 |
Claims
1. A pumping system comprising: a) a motor with a rotary output
shaft; b) a rotodynamic pump with a fluid input, that is fluidly
connected, when the pump is in use, to a fluid source that is
external to the pumping system, a fluid output and an impeller
positioned inside the pump between the fluid input and the fluid
output; and a continuously variable transmission (CVT) that is
operatively connected to the rotary output shaft and to the
impeller for providing rotary power from the rotary output shaft to
the impeller, wherein the CVT is adjustable to maintain a steady
state operating speed of the motor in response to a fluctuation of
head exerted on the fluid output.
2. The pumping system of claim 1, wherein the CVT is a belt drive
CVT comprising a variable width drive pulley operatively connected
to the rotary output shaft of the motor; a variable width driven
pulley operatively connected to the impeller shaft; and a belt
positioned about opposing sheave portions of each of the drive
pulley and driven pulley and contacting the opposing sheave
portions of each of the drive pulley and driven pulley to turn
therewith, wherein in operation: tensioning of the belt to engage
each pulley is by only the variable widths of the drive pulley and
the driven pulley by increasing or deceasing the distance
separating the opposing sheave portions; when the motor is at idle
the opposing sheaves of the drive pulley are spaced substantially a
maximum distance apart and the opposing sheaves of the driven
pulley are spaced substantially a minimum distance apart or not at
all; and when the motor increases a rotational speed of the rotary
output shaft, the distance separating the opposing sheaves of the
drive pulley decreases and the distance separating the opposing
sheaves of the driven pulley increases.
3. The pumping system of claim 1, wherein the pumping system can
provide a fluid output between 1 to 5000 Imperial gallons per
minute with about 1 to about 500 feet of static pressure head.
4. The pumping system of claim 1, wherein the impeller is one of an
axial-flow impeller, a mixed-flow impeller, a radial-flow impeller
or a centrifugal impeller.
5. The pumping system of claim 1, wherein the pump comprises a
housing for defining the fluid input and fluid output and for
housing the impeller.
6. The pumping system of claim 5, wherein the housing further
comprises a deflector ring that extends from an inner surface of
the housing, the deflector ring is positioned between an inlet of
the fluid input and the impeller.
7. The pumping system of claim 1, further comprising a motorized
vehicle for carrying and transporting the motor, the pump and the
CVT.
8. The pumping system of claim 7, wherein the motorized vehicle is
a side-by-side vehicle.
9. The pumping system of claim 7, wherein the motor, the pump and
the CVT are removably mountable upon a skid for the carrying and
transporting upon the motorized vehicle.
10. The pumping system of claim 1, wherein the pump is one of a
centrifugal pump, an axial-flow pump or a mixed-flow pump.
11. The pumping system of claim 1, wherein the impeller is an
axial-flow impeller.
12. The pumping system of claim 11, wherein the axial-flow impeller
comprises 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 pumping system of claim 11, wherein the impeller has a
maximum diameter in a range of between about 4 inches and about 12
inches.
14. The pumping system of claim 1, wherein the fluid output
comprises an elbow outlet turning away from a rotational axis of
the impeller.
15. The pumping system of claim 14, wherein said elbow outlet
decreases in cross-sectional area over its length away from the
impeller.
16. The pumping system of claim 1, wherein the motor is a
non-diesel, gasoline internal combustion engine.
17. The pumping system of claim 1, wherein the pumping system can
provide a fluid output between about 2,000 and about 10,000
Imperial gallons per minute.
18. The pumping system of claim 1, wherein the pumping system can
provide a fluid output between about 6,000 and about 11,000
Imperial gallons per minute.
19. The pumping system of claim 1: a) wherein the CVT transfers
power between the rotary output shaft of the motor and the impeller
shaft in accordance with a variable turn ratio, the CVT being
responsive to a change in rotary output shaft speed and impeller
shaft speed to adjust the variable turn ratio; b) wherein the CVT
is adjustable in response to mechanical resistance caused by a head
increase of the pump; and c) wherein in response to the mechanical
resistance, the CVT adjusts the variable turn ratio to maintain
regulation of motor rotational speed relative to a target operating
point while slowing rotation of the impeller to decrease fluid
capacity output from the pump while increasing a torque imposed on
the impeller for generating a head pressure output that is greater
than when the torque is not increased.
20. A continuously variable transmission (CVT) pump for conveying a
fluid from a fluid source external to the pump to a selected
destination, the CVT pump comprising: a) a rotodynamic pump having
an inlet connected, when in use, to the fluid source for receiving
the fluid, and an outlet for delivering the fluid, and an impeller
positioned therebetween; b) a rotary power source; and c) a belt
drive CVT for transferring rotary power provided by the rotary
power source to the rotodynamic pump, the CVT comprising: i) a
variable width drive pulley operatively connected to a rotary
output shaft of the rotary power source, the drive pulley
comprising opposing sheave portions that are configured to decrease
in distance from each other as rotation of the drive pulley
increases; ii) a variable width driven pulley operatively connected
to an impeller shaft of the impeller, the driven pulley comprising
opposing sheave portions that increase in distance from each other
as rotation of the driven pulley increases; and iii) a belt
positioned about the opposing sheave portions of each of the drive
pulley and driven pulley and in contact with the opposing sheave
portions of each of the drive pulley and driven pulley to turn
therewith, the belt tensioned by adjustment of distance between the
opposing sheave options of each of the drive pulley and driven
pulley: wherein the CVT is adjustable to maintain a steady state
operating speed of the rotary power source in response to a
fluctuation of head exerted on the fluid output.
Description
TECHNICAL FIELD
[0001] The present disclosure relates to techniques, systems,
methods, processes, apparatus, devices, combinations, and equipment
for pumping fluids. More particularly, the present disclosure
relates to pumping techniques for fighting fire, mitigating
flooding, moving fluids from one location to another and similar
applications. More particularly, the present disclosure relates to
pumping equipment that comprises a rotary power source, a
continuously variable transmission and a rotodynamic pump.
BACKGROUND
[0002] This section provides background information to facilitate a
better understanding of the various aspects of the disclosure. It
should be understood that the statements in this section of this
document are to be read in this light, and not as admissions of
prior art.
[0003] 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 can be prohibitively
expensive.
SUMMARY
[0004] Embodiments of the present disclosure relate to systems,
apparatus, methods, kits, processes, combinations, equipment, and
devices for pumping liquids. Other embodiments include techniques
to apply, design, prepare, form, make, display, generate, and/or
use pumps with a continuously variable transmission (CVT) to drive
a water pump for ameliorating hazardous conditions, including but
not limited to floods, fires, sewage treatment plant overflows, and
the like.
[0005] A further technique of the present disclosure 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 embodiment, the pump is a rotodynamic type with the rotor
being an axial impeller.
[0006] Another embodiment of the present disclosure 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.
[0007] Still another embodiment of the present disclosure 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.
[0008] Yet another embodiment of the present disclosure 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 embodiment, the
rotor is an axial flow impeller.
[0009] 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.
[0010] A further embodiment includes a pumping system comprising a
motor with an output, a pump with a fluid input, a fluid output and
an impeller positioned inside the pump between the fluid input and
the fluid output. The pumping system also includes a continuously
variable transmission that is operatively connected to the output
of the motor and to the impeller for providing rotary power from
the motor to the impeller. The motor, the pump and the continuously
variable transmission have a collective dry weight between about
200 pounds and 1000 pounds and the pumping system can provide a
fluid output between 1 to 5000 imperial gallons per minute when
about 1 to about 500 feet of static head pressure is exerted on the
impeller.
[0011] 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 claims, drawing, and/or other
information included herein.
BRIEF DESCRIPTION OF THE DRAWINGS
[0012] The disclosure is best understood from the following
detailed description when read with the accompanying figures. It is
emphasized that, in accordance with standard practice in the
industry, various features are not drawn to scale. In fact, the
dimensions of various features may be arbitrarily increased or
reduced for clarity of discussion. As will be understood by those
skilled in the art with the benefit of this disclosure, elements
and arrangements of the various figures can be used together and in
configurations not specifically illustrated without departing from
the scope of this disclosure.
[0013] FIG. 1 is a schematic of a vehicle-carried pumping system of
the present disclosure.
[0014] FIG. 2 is a schematic detailing aspects of the pumping
system of FIG. 1.
[0015] FIG. 3 is a partially-exploded isometric view of certain
details of the pumping system of FIG. 1.
[0016] FIG. 4 is a partially-exploded isometric view of a portion
of one embodiment of the pumping system of FIG. 3.
[0017] FIG. 5 is an exploded elevation view of selected components
of an example CVT of the pumping system of FIG. 1 that details
fixed and variable pulleys for a drive pulley and a driven
pulley.
[0018] FIG. 6 depicts a flowchart directed to a first portion of a
nonlimiting routine for operating the pumping system of FIG. 1.
[0019] FIG. 7 depicts a flowchart directed to a second portion of a
nonlimiting routine for operating the pumping system of FIG. 1.
FIG. 6 and FIG. 7 both 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.
[0020] FIG. 8 is a top plan view of the CVT shown in FIG. 5.
[0021] FIG. 9 is an elevation view of the CVT shown in FIG. 8 taken
along line 9-9 in FIG. 8 with the CVT in a configuration for a
stopped-through-idle speed operation of the CVT 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).
[0022] FIG. 10 is the same view as FIG. 8 but FIG. 10 corresponds
to a configuration for a steady-state speed operation of the CVT 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).
[0023] FIG. 11 is the same view as FIG. 9 taken along line 11-11 in
FIG. 10.
[0024] FIG. 12 is a partially-exploded isometric view of a portion
of another embodiment of the pumping system of FIG. 3.
[0025] FIG. 13 a schematic diagram that depicts a flow of fluids
through a select portion of the pumping system of FIG. 12.
DETAILED DESCRIPTION
[0026] In the following description, various details are set forth
to provide a thorough understanding of the principles and subject
matter of each embodiment 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 described
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.
[0027] Considering the embodiments of this disclosure, those
skilled in the relevant art will recognize that such embodiments
may 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 all embodiments described
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, the description of embodiments should be
seen as illustrative only and not limiting.
Definitions
[0028] Unless defined otherwise, all technical and scientific terms
used herein have the same meaning as commonly understood by one of
ordinary skill in the art to which this disclosure belongs.
[0029] "About" as used herein refers to an approximately +/-10%
variation from a given value. It is to be understood that such a
variation is always included in any given value provided herein,
whether or not it is specifically referred to.
[0030] "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.sub.2O), inclusive
of any isotope of hydrogen or oxygen and inclusive of temporary
ionic forms of the proton (Hi) and hydroxyl ion (OH). Further, as
used herein "water" is inclusive not only of liquid H.sub.2O in
pure form, but also any nongaseous fluid mixture including liquid
H.sub.2O 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 H.sub.2O 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.sub.2O is the solvent; (b) any gas or combination of
different gases to form foam(s); (c) solid matter dispersed in a
slurry, suspension, or colloid; (d) one or more other liquids
immiscible with the liquid H.sub.2O, taking either a heterogeneous
form or a more dispersed homogeneous form (like in an emulsion);
and/or (e) 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 H.sub.2O, 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 contemplated sources.
[0031] "Water Capacity" as used herein means the volumetric flow
rate of water (see definition above) relative to time in imperial
Gallons Per Minute (GPM).
[0032] "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 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 fluid
output of a conduit connected to the pump discharge. Alternatively,
the reverse may be the case with the lower point being the point of
fluid output of the conduit connected to the pump discharge and the
higher point is an arbitrary datum relative to the point of pump
discharge.
[0033] "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 fluid
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 fluid
pressure.
[0034] "Hydrostatic Pressure" (alternatively designated by the
variable "HP") in a liquid can be expressed as the product of the
multiplicand and variables: height of the liquid column or
"hydraulic head" (H), density of the liquid (p), and gravitational
acceleration (g); such that HP=Hpg and conversely H=HP/(pg).
Frictional loss, turbulence, cavitation, and other factors may
influence the determination of H and HP in a given application.
[0035] "CVT" is an abbreviation for the term "Continuously Variable
Transmission" which for the purposes of this disclosure may be used
interchangeably with the term "constantly variable
transmission".
[0036] "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.
[0037] "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.
[0038] "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.
[0039] "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.
[0040] "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.
[0041] "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
embodiment, 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.
[0042] "Nonferrous" means any material composed of no more than
about one-half percent (0.5%) iron (Fe) by weight.
[0043] "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.
[0044] 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 disclosure likewise shall have the meaning imparted
thereby throughout the present disclosure 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.
[0045] Referring to the depicted embodiment of FIG. 1, a mobile
system 20 is illustrated. System 20 includes a vehicle 22 in a form
structured to travel over rough terrain with a Four-Wheel Drive
(FWD) subsystem 24. Correspondingly, the subsystem 24 includes four
ground-engaging wheels 26 (only two of which are shown), however,
more or less than four wheels 26 are also contemplated by the
present disclosure. The FWD subsystem 24 includes any suitable
vehicular propulsion power source 27 (the prime mover for
propulsion/operation of the vehicle 22). The vehicular power source
27 is more particularly depicted in FIG. 1 as an 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. Such transmission for the 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.
The system 20 further includes a pumping system 30. In some
embodiments of the present disclosure, the 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 the pumping system 30 with various subsystems being highly
integrated and all subject to a centralized operator control, a
flatbed or a pick-up truck with space sufficient to carry the
pumping system 30, or the like. In another embodiment, the vehicle
may be a watercraft. In one embodiment, the pumping system 30
requires a vehicle weight-capacity for transport of the pumping
system 30 of between about 100 and about 1000 pounds. In another
embodiment, the pumping system 30 requires a vehicle
weight-capacity for transport of the pumping system 30 of between
about 250 to about 500 pounds. In another embodiment, the pumping
system 30 requires a vehicle weight-capacity for transport of the
pumping system 30 of about 300 pounds.
[0046] The pumping system 30 includes a rotary power source 40, a
continuously variable transmission (CVT) 60, and a pump 80. The
rotary power source 40 provides power to operate the pump 80 via
the CVT 60 (accordingly, source 40 is the prime mover of pumping
system 30). The pumping system 30 further comprises an intake
conduit 82 having an inlet 81 with an intake filter 120 that is in
fluid communication therewith as provided by a sealed engagement
thereto. The opposite end of the intake conduit 82 is coupled in
sealed engagement with an intake 92 as defined by an intake plate
96 (shown in FIG. 3 and FIG. 4), which draws water into the
remainder of pump 80 (see, FIG. 2-4) from source W. Water intake
from source W occurs when the pump 80 generates suction/lift
through the intake filter 120 submerged in source W and the conduit
82 is in fluid communication with the filter 120. The pump 80
pressurizes water for output through an outlet 94 that is in fluid
communication with an output conduit 84. The source W may be a
natural body of water, such as a river, lake, pond, an aquifer and
the like or the source W may be an artificial enclosure that is
holding water such as a retaining pond, a reservoir, a mine, a
holding tank or the like. In other embodiment, the source W may be
a holding tank on another vehicle, such as a truck, and the pumping
system 30 may be employed without or without the mobile system
20.
[0047] Accordingly, the pumping system 30 is structured to
convey/transfer water from the 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. The output conduit 84 may discharge water
through a manifold 85 that terminates in a nozzle 86. 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 appreciated that in other applications of the pumping
system 30, the 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.
Alternatively, or additionally, the water output from the output
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.
[0048] Referring to FIG. 2, the pump 80 may also be configured to
remove flood water from the water source W via the filter 120 that
is in fluid communication with the intake conduit 82 at inlet 81;
where like reference numerals refer to like features previously
described.
[0049] The pumping system 30 pressurizes the water from source W
for discharge through the output conduit 84 by rotating an axial
flow impeller 90 of the pump 80. Such discharge is transported to a
location away from the source W. In certain nonlimiting
alternatives, the configuration of the pumping system 30 in FIG. 2
may also be directed to the exigent prevention of liquid
spills--such as sewage and/or chemical waste spillage or overflow
relative to a designated containment area. In still other
nonlimiting alternatives, the pumping system 30 may be used for the
transfer of liquids between various locations, for example, sewage
between different ponds and/or routine irrigation applications.
[0050] Continuing to refer to both FIGS. 1 and 2, a 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 the pumping system 30--but certain variations at the
vehicle/system level are first considered. In some embodiments, the
rotary power source 40 is structured to propel the vehicle 22 as
well as the power pump 80 via a CVT 60--in which case the engine 28
may be absent, adapted to work in concert with the source 40 and/or
otherwise. 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, as described above a suitable
watercraft may carry the pumping system 30 on a body of water that
may offer a preferred way to reach certain wildfires F rather than
traveling overland. Such body of water may also provide a ready
water source W. In yet another embodiment, the pumping system 30
may be 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).
[0051] Rotary power source 40, and more particularly engine 42,
provides mechanical power with a rotating shaft 58a turning at
speed "n" typically designated in units of Revolutions-Per-Minute
(RPM). In certain embodiments, a CVT power input shaft 58b is
mechanically coupled to the shaft 58a 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 58a and 58b 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 than 1:1 may be provided by a mechanical linkage between
shafts 58a and 58b. 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.
[0052] Engine 42 includes multiple reciprocating pistons 54 (only
one of which is symbolically shown in FIG. 2) coupled to a turn
crankshaft 56. In correspondence, the crankshaft 56 turns to
provide rotary power to a power output shaft 58a. The engine 42 may
be 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. The engine 42 is supplied with combustible fuel
from a fuel source 48. The engine 42 receives intake air through an
air intake 50 to blend with fuel to provide a combustible air/fuel
charge. Optionally, the engine 42 further includes a turbocharger
52 that is 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.
[0053] A 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,
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, which is referred to
as a 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,
an upward exhaust stroke. These four strokes are then repeated in
each cylinder to rotate the crankshaft 56 and correspondingly turn
the shaft 58a with the objective of achieving a steady state
operation at a rotational engine speed (n).
[0054] The exhaust is collected from engine 42 through an exhaust
manifold that is discharged through engine exhaust outlet 53. The
collected exhaust may travel through a catalytic converter and/or
muffler device before exiting through outlet 53. In the depicted
embodiment, engine coolant circulates through one or more engine
cooling jackets. Such jackets are typically formed in the engine
block and cylinder heads, which are interconnected through certain
passages. During operation of the engine 42, the circulating water
is warmed, removing heat from desired portions/components of the
engine 42. Because turbocharging typically increases the
temperature of the boosted, pressurized input air, the turbocharger
52 may include an intercooler/heat exchanger 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). In addition to or in lieu of the use of a
radiator, an external water source may be used to exclusively
provide or supplement engine cooling.
[0055] For the 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 a 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 5 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 5 BHpeak). In some 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 5 n 5 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.
[0056] Engine 42 further includes an engine controller 55 that is
adjustable to determine an acceptable steady state target speed n
(such as BHpeak) and that 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 the controller 55. In one
embodiment, the controller 55 is a standard type of electronic
Engine Control Module (ECM). While the controller 55 regulates the
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 the 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 the engine 42 and the controller 55 responds
to a load transient by limiting the magnitude and/or duration
effectively realized by the engine 42 and/or the controller 55.
Among other things, the CVT 60 may compensate for transients as
more fully described below.
[0057] The CVT 60, which may also be referred to as a single speed
transmission, a stepless transmission or a pulley transmission
allows for a transition through a range of gear ratios between a
rotational output, for example from the engine 42, and the
rotational input of the pump 80. In one embodiment, the CVT 60 uses
the rotational output from the engine 42 to provide a variable
output speed and torque to the pump 80. In one embodiment, the CVT
60 is a variable-diameter pulley, which may also be referred to as
a Reeves drive. In this embodiment, the CVT 60 includes a variable
width pulley 62 that is fixed to rotate with the CVT power input
shaft 58b, and a variable width pulley 68 is fixed to rotate a CVT
power output shaft 70. An endless loop 66 fits about both pulleys
62 and 68, frictionally engaging each so that as the pulley 62
turns, the endless loop 66 rotates about both pulleys 62 and 68,
driving rotation of the pulley 68 and the CVT power output shaft 70
fixed thereto. The endless loop 66 is formed from a belt 67 that
fits about the pulleys 62 and 68 and frictionally engages each one.
The CVT 60 also includes a CVT drive mechanism 75 to govern the
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 embodiment, the
distance between the two pulleys 62 and 68 does not materially
change during operation of the pumping system 30 but the effective
diameters of the two pulleys 62 and 68 may change at substantially
the same time to change a gear ratio between the two pulleys 62 and
68. In one such embodiment, the effective diameter of one or both
of the pulleys 62, 68 decreases with an increasing width.
Accordingly, adjusting the pulleys 62 and 68 to different widths
corresponds to different effective diameters and the turn ratio
(TR) between the CVT power input shaft 58b and the CVT power output
shaft 70 can be varied over a selected range. In FIG. 2, the CVT
drive mechanism 75 includes a width control mechanism 64 connected
to the pulley 62, while a width control mechanism 68d for the
pulley 68 is not shown except in FIG. 5, FIG. 9, and FIG. 11 to be
discussed later. The absence of the width control mechanism 68d
results because it is not visible in an assembled top view like
that in FIG. 2, FIG. 8, and FIG. 10 and depiction of the width
control mechanism 68d in phantom or schematically in these figures
would obscure other features. As will be appreciated by those
skilled in the art, the CVT 60 may be employed in other forms.
[0058] The CVT power output shaft 70 is mechanically coupled to an
impeller shaft 108 of pump 80 (FIG. 4). The impeller 90 is fixed to
the shaft 108 to rotate therewith at a rotational speed p. This
mechanical coupling of the shafts 70 and 108 may be a direct
connection with a one-to-one (1:1) turn ratio. As in the case of
the shafts 58a and 58b, the 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 the 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. Consequently, the CVT 60 mechanically connects engine 42 to
pump 80 to supply rotary power thereto subject to a variable turn
ratio TR over a selected range. The variation of turn ratio TR is
regulated by the CVT drive 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
the pump 80. The CVT 60 generally provides for this priority as
will be more fully described in text accompanying FIG. 5 through
FIG. 11.
[0059] With reference to FIG. 2, FIG. 3 and FIG. 4, the impeller 90
may, for example, be a tri-vane (or tri-blade) axial flow type
(shown in schematic form in FIG. 2). With this form of a kinetic
pump rotor 91, the pump 80 is alternatively designated a type of
rotodynamic pump 88 (previously defined). Pump 80 is comprised of a
pump housing 35 (see FIG. 3 and FIG. 4). The housing 35 includes
constituent housing parts, such as a plate 96, a housing 98, and an
elbow 100 to be further described hereinafter. The housing 98 has
an interior surface 102 in the general shape of a right circular
cylinder that contains the impeller 90 (see FIG. 3 and FIG. 4). The
surface 102 defines the margin of a rotor passage 102a through the
housing 98. The impeller 90 may form a seal 104 at an impeller
outer leading edge 106 and the surface 102, which may be caused by
a nonferrous, self-lubricious seal 104 that is present along each
outer leading edge 106 of the impeller 90 that is mechanically
arranged to moves outward with impeller 90 rotation such that it
meets inner surface 102 of housing 98. This may provide a type of
variable geometry blade. In certain embodiments, the 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. Alternatively, the seal 104 comprises a polymer-based
material. 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.
[0060] Specific to FIG. 3, the pump 80 is shown in a partially
diagrammatic, perspective view that is in an assembled form except
for an intake plate 96, which is shown in an exploded view (see
FIG. 4) to better illustrate features of the impeller 90 relative
to the housing 98 in which the impeller 90 resides; while the
engine 42 and the CVT 60 are shown in a schematic form to preserve
clarity. Specific to FIG. 4, the pump 80 is shown in more detail
with the pulley 68 of the 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 FIG. 3 and FIG. 4, the
intake 92 is further defined by one or more flow guide ribs 109
that extend from an outer circumferential ring 111 to coaxially
locate a plate bearing/seal 110 along the rotational axis R-R of
the shaft 108. When assembled, the bearing/seal 110 slides over the
impeller bearing/seal 114 within the housing 98 near the intake 92,
providing a journal bearing with a seal that prevents water from
reaching the main impeller shaft 108 at the upstream end of the
impeller 90. As specifically labeled in FIG. 4, the downstream end
of the impeller 90 slides over the bearing 116, engaging an O-ring
friction seal 118 when assembled within the housing 98.
Accordingly, water is also prevented from reaching the main
impeller shaft 108 through this route. The shaft 108 extends
through a portion of an output elbow 100 along rotational axis R-R
to engage the CVT power output shaft 70 at the bearing 130. The
shaft 70 extends through the variable width pulley 68 to engage the
CVT support bearing 112 (shown in FIG. 4 only). The pulley 68, the
CVT output power shaft 70, the impeller shaft 108, and the impeller
90 all rotate together about the rotational axis R-R when driven by
the endless loop 66 (loop 66 is not shown in FIG. 4 to preserve
clarity). Correspondingly, the intake plate 96, the axial impeller
pump housing 98, and the 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.
[0061] During operation, as the impeller 90 (a form of kinetic pump
rotor 91) turns about the rotational axis R-R, it receives water
through the intake 92 of the plate 96 and pressurizes the water
with a primary velocity component approximately parallel to the
rotational axis R-R as it exits the impeller 90. As a form of a
rotodynamic pump 88, kinetic energy is also stored as potential
energy in the form of pressure in housing 98. Soon after exiting
the impeller 90, the pressurized water is turned by the elbow 100
away from axis R-R to exit through an elbow outlet 94 generally
perpendicular thereto. The elbow outlet 94 has a cross-section that
is less, or smaller, 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 elbow
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 FIG. 1 and FIG. 2, the pump output
conduit 84 is in sealed engagement with the 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 the CVT 60. In contrast, a non-negligible decrease in
head H reduces loading on the impeller 90 and correspondingly the
CVT 60. FIG. 5 provides a partially diagrammatic, exploded view of
the CVT 60. FIG. 8 and FIG. 9 provide partially diagrammatic top
and side views of the CVT 60, respectively, for one exemplary turn
ratio, and FIG. 10 and FIG. 11 provide partially diagrammatic top
and side views of the 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.
[0062] The CVT drive mechanism 75 may respond to a mechanical
resistance change from a transient by adjusting width of the pulley
68, which also referred to herein a driven pulley 65, with a
control mechanism 68d that changes the turn ratio TR. The control
mechanism 68d may be in the form of a helical/coil spring
positioned about an end portion 70c of the shaft 70.
Correspondingly, a control mechanism 64 responds to an initial
speed change in the rotational speed of shaft 58b to adjust the
width of pulley 62, which is also referred to as a drive pulley 63,
to the extent that any speed change of shaft 70 is transferred
through loop 66 to shaft 58b. For some minor transients, it is
possible that such transients may be sufficiently addressed by
adjustment of the control mechanism 68d without a noticeable change
caused by the control mechanism 64; however, for more significant
transients, the change in effective diameter of driven pulley 65 as
caused by control mechanism 68d likely will result in a width
adjustment of drive pulley 63 by control mechanism 64 changing its
effective diameter. In turn, further refinement in the effective
diameter of the driven pulley 65 by the mechanism 68d may occur as
a result of the change to the pulley 63 as it is "communicated" by
the 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 the CVT drive 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.
[0063] While engine speed n tends to remain at or near the steady
state target operating point as head H significantly fluctuates,
there may be a trade off because the adjustment of the 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 the pump 80 to correspondingly
fluctuate. Under steady state conditions, the 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 pumping 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).
[0064] With reference to FIG. 2 through FIG. 5 and FIG. 8 through
FIG. 11 collectively, the variable width pulley 62 includes a
sheave portion 62a fixed to the shaft 58b and a moveable sheave
portion 62b. The moveable sheave portion 62b translates along an
end portion 58c of the shaft 58b relative to the sheave portion 62a
under certain conditions. FIG. 8 depicts a pulley width W1 that is
greater than a pulley width W3 depicted in FIG. 10. As the variable
width pulley 62 is turned by the shafts 58a, 58b it receives rotary
mechanical power (torque) from the engine 42 and accordingly is a
form of the drive pulley 63. The variable width pulley 62 is
mechanically linked by the endless loop 66 to the variable width
pulley 68. As a result, the variable width pulley 68 turns in
response to the drive pulley 63 via loop 66 making it a form of a
driven pulley 65 where the pulley 65 is driven by drive pulley 63.
The 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, the pulleys 62, 68 may include surface features to
promote frictional engagement with the endless loop 66 such as
teeth of either an intermeshing or non-meshed variety, tapering,
surface roughening, like surface spikes, grit coating, or the
like.
[0065] The variable width pulley 68 includes a sheave portion 68a
fixed to the shaft 70 and a sheave portion 68b, which moves in
translation relative to the sheave portion 68a along an end portion
70c of the shaft 70 under certain conditions. Because the shaft 70
is mechanically fixed to the shaft 108, which turns the impeller
90, the sheave portion 68a, the shaft 70, the shaft 108, and the
impeller 90 all turn in concert at a pump rotational speed p that
may differ from the engine rotational speed n of the power output
of engine 42 (and input to pulley 62) depending on the turn ratio
TR. The control mechanism 64 fixed to the sheave portion 62b of the
pulley 62 to adjust a width of the pulley 62 along the end portion
58c in correspondence to speed n of the shaft 58a. The sheave
portion 62b/control mechanism 64 moves apart from the sheave
portion 62a in translation along the end portion 58c to increase
the width of the pulley 62. As the width of the pulley 62 changes
in response to the control mechanism 64 (compare pulley 62 width W1
in FIG. 9 to the pulley 62 width W3 in FIG. 11), so does the actual
pulley diameter considering a circular pulley profile (compare the
pulley 62 diameter S1 in FIG. 9 to the pulley 62 diameter S3), as
well as the effective diameter (previously defined). Namely, the
effective diameter of the pulley 62 is smaller when the pulley 68
is wider (width W1 FIG. 8) because the endless loop 66 is riding
closer to shaft end portion 58c in the middle between sheave
portions 62a and 62b (see FIG. 9); and the effective diameter about
the pulley 62 is larger when the pulley 62 is narrower (width W3
FIG. 10) because the endless loop 66 is riding up the sheave
portion(s) 62a and/or 62b (see FIG. 11). One example of the
effective diameter as defined herein is a segment C2 extending
between points P3 and P4. In this case, the segment C2 is close to
if not collinear with a diameter intersecting a rotational axis of
the pulley 62 and opposing points of contact P3, P4 of the circular
section shown in FIG. 11.
[0066] One embodiment of the control mechanism 64 is comprised of
clutch weights 64b (schematically depicted) that are pivotally
connected to pins that are fixed to control mechanism 64. These
weights 64b spin outward with increasing shaft 58b rotation at
speed n. As the weights 64b spin outward, they cause rollers 64a
(schematically depicted) to move along the end portion 58c to
advance the sheave portion 62b towards the sheave portion 62a, and
correspondingly decrease the width of the pulley 62 and increasing
the diameter of the pulley 62. In addition, the arrangement of the
control mechanism 64 typically includes one or more internal
springs coupled to the weights 64b to impose a force that must be
overcome before weights 64b 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 the pulley 62 to its minimum diameter at idle
speed and maintaining that diameter when rotation stops or even
when the engine 42 stops immediately with no controlled speed
decrease down to idle first. Furthermore, weights 64b and the
configuration of the control mechanism 64 otherwise are arranged to
match and effectively provide a corresponding maximum rotational
speed n of shaft (portions) 58a, 58b, and 58c corresponding to the
desired steady state desired operating point speed of the engine
42. This operating point speed may correspond to the peak torque
(Qpeak), the peak brake horsepower (BHpeak), or the peak efficiency
(BEpeak). To maximize the pump 80 performance, the brake horsepower
peak output rotational speed of the 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, the
pulley 68 width W2 is illustrated, which in comparison is less than
the pulley 68 width W4 shown in FIG. 10. The CVT drive mechanism 75
of CVT 60 includes a width control mechanism in the form of a
helical coil spring 68d with a selected spring constant. The spring
68d is oriented about shaft end portion 70c and has one end
connected to the sheave portion 68a and the opposite end fixed
relative to the sheave portion 68b by a hub 68c that collectively
limits the outer width range of the sheave portion 68b along the
end portion 70c-applying a nominal spring force to pull the sheave
portions 68a and 68b towards each other. The hub 68c is integral
with and an alternative designation of support bearing 112
previously introduced (compare FIG. 4 and FIG. 5 and accompanying
description). The width control mechanism spring 68d varies width
of the pulley 68 translationally along the shaft end portion 70c by
controlling separation of the sheave portion 68b from the sheave
portion 68a 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 68d maintains sheave
portions 68a and 68b 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 the shaft end
portion 70c increases past idle, the spring force (as determined at
least in part by the spring constant) of the width control
mechanism spring 68d starts to be overcome so that the rotational
energy of the shaft 70 causes the width control mechanism spring
68d to be pulled with a force sufficient to move the sheave portion
68b away from the sheave portion 68a. Resulting separation of the
sheave portions 68a and 68b may be up to and perhaps beyond, a
steady state rotational speed of the shaft 70 as represented in
FIG. 10 by width W4. Conversely, the width control mechanism spring
68d is configured to pull sheave portion 68b towards the sheave
portion 68a as the rotation slows to return to the narrow,
stopped/idle configuration. In addition, as the width of the pulley
62 changes in response to the width control mechanism spring 68d;
the actual diameter of the pulley 68 changes (compare S2 of FIG. 9
to S4 of FIG. 11); and the effective diameter of the pulley 68
changes. In FIG. 9, an effective diameter of the pulley 68 with the
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 the effective diameter.
Notably, the effective diameter about the pulley 68 is larger when
the pulley 68 is narrower because the endless loop 66 is riding up
on the sheave portion 68a and/or sheave portion 68b as depicted in
FIG. 9. In contrast, the effective diameter is smaller when the
pulley 68 is wider (width W4 FIG. 10) because the endless loop 66
is positioned closer to the shaft end portion 70c and is generally
more closely centered relative to the distance between the sheave
portions 68a and 68b. In contrast, the effective diameter defined
with the pulley 68 is larger when the pulley 68 is narrower (i.e.
width W2 of FIG. 8) because the endless loop 66 is positioned
farther away from the shaft end portion 70c. The variable width
pulley control mechanism 64 may be similar to a primary clutch, and
width control mechanism spring 68d 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.
[0067] Correspondingly, the CVT 60 of the pumping system 30 can be
described by changing turn ratio "TR" between the pulley 62 and the
pulley 68 as the rotational speed of the shaft end portion 58c and
the shaft end portion 70c change relative to each other past the
stopped/idle configuration. Indeed, it should be appreciated that
the arrangement of the control mechanism 64 and the mechanism
spring 68d 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 disclosure, 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
NB, 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
NC=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 the pulley 62 to 1 revolution
of the pulley 68; where A E 118={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 B E
LB. In one embodiment, 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 FIG.
8 and FIG. 9 is representative of a turn ratio TR of 4:1. In
contrast, the turn ratio configuration of CVT 60 in FIG. 10 and
FIG. 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 the pulley 62 increases in response to the width
control mechanism 64 and the effective diameter of the pulley 68
decreases in response to the width control mechanism spring 68d,
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 the CVT 60 operates on a continuous rather than
fixed gear/gear ratio as provided in this comparison. As the
effective diameter of the pulley 62 approaches its minimum and the
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 FIG. 5 and FIG. 8 through FIG.
11. Recognizing that a higher rotational pump speed p of 15,000 RPM
or more may be realized under certain conditions, some
implementations of pumping 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 68d (and/or
dimensioning of certain aspects of the endless loop 66, the sheave
portions 62a, 62b, 68a, 68b and/or the shaft end portions 58c and
70c) to allow an example 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, the shaft 70 turns 15,000 times for every
11,000 turns of the shaft 58b (or equivalently: 73% of a turn of
the shaft 70 for every 1 turn of the shaft 58b or the shaft 70
turns once for every 1.36 turns of the shaft 58b). The governance
of the pumping system 30 relative to turn ratio TR and various
operational aspects of the pump 80 are described further in
connection with FIG. 6 and FIG. 7 as follows.
[0068] Referring to FIG. 6 and FIG. 7 collectively depict a
flowchart of the pumping system 30 operating routine 320; where
like reference numerals refer to like features previously
described. For the purposes of the operating routine 320, 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. Operating routine 320 begins with start stage 322 on
FIG. 6. From start stage 322, operating routine 320 advances to
engine stopped stage 324 (n=0) in which operation of the system 20
is halted and the pumping system 30 is at rest (p=0). In stage 324,
the drive:driven pulley turn ratio is 4:1. Further, the drive
pulley 63 has a small effective diameter with the sheave portions
62a and 62b being at or near maximum open. In addition, the driven
pulley 65 has a large effective diameter with the sheave portions
68a and 68b at or near closure. Also, the engine controller 55 is
configured to operate the 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 the
vehicle 22 is parked or the 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 a remote water source W. 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.
[0069] From stage 324, operating routine 320 continues with a
conditional 326 that tests whether to start the engine 42 or not.
If the outcome of the test of the conditional 326 is negative (No),
the 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 the conditional 326 is affirmative (Yes), then the
engine 42 is started and operating routine advances to engine
42/system 30 idle operation 328. The conditional 326 and an
operation 328 would typically be performed once the vehicle 22 has
stopped at an appropriate location proximate to the water source W
as part of the preparation process to abate a hazardous condition
such as a wildfire, flood, or the like. During the operation 328,
approximately the same effective diameters and sheave
configurations of the drive pulley 63 and the driven pulley 65 as
set forth for stage 324 persist in this operation. It should be
noted that during operation 328, the pumping system 30 is just
coming up to idle speed. The turn ratio TR is approximately 4:1 as
represented in FIG. 8 and FIG. 9. As previously explained the
features of the width control mechanism 64 and the width control
mechanism spring 68d are configured to maintain this 4:1 turn ratio
until operation past idle is initiated. Operating routine 320
proceeds next to trigger an operation 330. The 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 the drive
pulley 63 begins to increase and the sheave portion 62b approaches
the sheave portion 62a; and the effective diameter of the driven
pulley 65 begins to decrease and the sheave portions 68a and 68b
begin to separate. Typically, the operation 330 would be performed
while the vehicle 22 is stationary at a location to ameliorate a
fire, flood, or the like.
[0070] The operating routine 320 advances from the operation 330 to
an upshift operation 332. In the upshift operation 332 the engine
42 speeds up from the trigger point 35%-40% of the engine operating
point speed to 100% of its operating point speed. As the engine 42
speeds up, the drive pulley 63 turns faster so its effective
diameter continues to increase with the sheave portions 62b and 62a
coming together to provide the drive pulley effective diameter
increase, the driven pulley 65 also turns faster so its effective
diameter continues to decrease with the sheave portion 68b
separating from the sheave portion 68a 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 the CVT 60. In certain embodiments, the operations
330 and 332 would be performed after transport of the pumping
system 30 to a remote sight proximate to water source W to prepare
for firefighting, flood amelioration, or the like.
[0071] From the operation 332, the operating routine 320 continues
with a steady state engine operation 334 per a flow line bridging
FIG. 6 and FIG. 7 in the manner indicated by connection flags A6
appearing on each figure. In the operation 334, the 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 FIG. 10 and FIG. 11. To provide this
turn ratio configuration of the CVT 60, the drive pulley 63 is at
or near its maximum effective diameter as provided by the sheave
portions 62a and 62b being at or near closure; and the driven
pulley 65 is at or near its minimum effective diameter as provided
by the sheave portions 68a and 68b being at or near a maximum open
state. Once at the desired remote site proximate to the water
source W, the operation 334 is when water transport from source W
to a desired site with pumping system 30 would begin. A hazardous
condition abatement operation 420 encompasses all the operations
and conditionals circumscribed by the phantom box with the 420
numerical labeling. The operation 420 includes
delivering/transporting water with the pumping system 30 to address
an environmentally hazardous condition, which may be performed
during execution of any of the circumscribed
operations/conditionals. From the operation 334, the operating
routine 320 continues with a conditional 336. The 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 the
operating routine 320 loops around operation 338 to conditional
340--in other words operating 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 the impeller 90 to
slow down, which imparts mechanical resistance to the driven pulley
65 via shafts 108, 70. In response, the driven pulley 65 slows
down, which causes its effective diameter to increase as the sheave
portion 68b starts closing in on the sheave portion 68a. The drive
pulley 63 responds to the slow down by beginning to open the sheave
portions 62a and 62b, which causes its effective diameter to
decrease. Accordingly, the increased load on the CVT 60/engine 42
caused by increasing head H of the 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 the CVT 60. This reduction causes the
impeller 90 rotation to slow down, decreasing the water capacity
output (volumetric flow rate) of pump 80 as a result of the
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 the
driven pulley 65 to be slower, reducing the water capacity output.
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 the pumping system 30. From the operation 338, the
operating routine 320 advances to the conditional 340. The
conditional 340 tests whether a non-negligible head H decrease has
occurred. If the test of conditional 340 is negative (No), it loops
around the operator 342 (skipping it) to the conditional 344. If
the test of conditional 340 is affirmative (Yes), then the
operating routine 320 continues with a non-negligible decreasing of
head H load compensation operation 342. The compensation operation
342 arises most often when an adjustment to water capacity output
(and the CVT 60 turn ratio TR) has already taken place as a result
of execution of the operation 338. The compensation operation 342
operates in the opposite manner of the compensation operation 338.
During execution of the operation 342, the driven pulley 65
responds to a lighter impeller load by opening the sheave portions
68a and 68b and correspondingly increasing the effective diameter
of the variable width pulley 68 (equivalently driven pulley 65),
and the drive pulley 63 responds to the change by closing the
sheave portions 62a and 62b and correspondingly decreasing the
effective diameter of variable width pulley 62 (equivalently drive
pulley 63). As a result of the operation 342, water capacity output
increases a corresponding amount.
[0072] The operating routine 320 continues from the operation 342
to a conditional 344. Upon completion of the operation 342, a water
transfer operation 420 is exited (the operation 420 relates to the
delivery/transfer of water to address an environmentally hazardous
condition in parallel with the execution of the operations 334,
338, 342 and the conditionals 336, 340). The conditional 344 tests
whether to return the pumping system 30 to idle speed. If the test
of the conditional is negative, the operating routine 320 proceeds
to a conditional 352 to determine whether to discontinue operating
the pumping system 30. If the test of the conditional 352 is
negative (No), the operating routine 320 returns to the steady
state engine operation 334, re-entering operation 420. If the test
of conditional 352 is affirmative (Yes), the operating 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 the pumping system 30 and waiting until the
conditional 326 is affirmative.
[0073] Returning to the conditional 344, if the test of the
conditional 344 is affirmative (Yes), the operating routine 320
continues with a 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 the
downshift operation 350, the drive:driven turn ratio TR moves from
1:1 to 4:1 by decreasing the effective diameter of the drive pulley
63 with the sheave portions 62a, 62b parting; and increasing the
effective diameter of the driven pulley 65 with the sheave portions
68a, 68b closing. The operating routine 320 proceeds from an
operation 350 to the engine/system idle operation 328 previously
described. Accordingly all the stages, operations, and conditionals
(collectively operators) of the operating routine 320 have been
described, including the flow line interconnections of all the
operators. The operating routine 320 effectively halts by reaching
the loop on FIG. 6 formed between engine halted/pumping system at
the rest stage 324 and the conditional 326 with a negative test
outcome (No), which is reached by an affirmative answer (Yes) for
the conditional 352 (FIG. 7) via connection flags C5.
[0074] Many different embodiments of the present disclosure 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 a 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.
[0075] In another example, a technique of the present disclosure
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.
[0076] 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.
[0077] In other embodiments, the rotodynamic pump of the present
disclosure 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 embodiment of a multistage pump of the present
disclosure. 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 disclosure 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 present disclosure.
[0078] 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, which is also referred to as fluid output, 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.
[0079] A number of initial field tests were performed, as outlined
in Table 1 below, that resulted in some of the specific embodiments
described above.
TABLE-US-00001 TABLE 1 Summary of initial field tests. Test
Operational Definition Results Definition Component Test #
Description How Result Pass: y/n Engine 1 Engine output 1 lb of
Engine under load, 30 psi = 240 Y boost - 8 hp increase. measure
turbo boost. additional hp Add to spec hp of 165 hp Engine cooling
1 Test main cooling system Run engine at 7000 rpm 1 hour no load
run Y system with no load for 1 hour produced 170 F. temp Intake
cooling 1 Test intake cooling system Run engine at 7000 rpm 1 hour
no load run N system with no load for 1 hour produced higher temps
than anticipated. Intake cooling 2 Test intake cooling system Run
engine at 7000 rpm 1 hour no load run Y system with no load for 1
hour produced acceptable temps. Pump test 1 Test flow by measuring
Run engine at optimal Wouldn't prime N distance water is thrown rpm
see what flow we from a 4'' nozzle, get 300' = pass Pump test 2
Test flow by measuring Run engine at optimal Impeller was destroyed
N distance water is thrown rpm see what flow we by gravel from a
4'' nozzle, get 300' = pass Pump test 3 Test flow by measuring Run
engine at optimal New impeller withstood N distance water is thrown
rpm see what flow we sand gravel. Measured from a 4'' nozzle, get
distance was 60' 300' = pass (2000 gpm) Pump test 4 Test flow by
measuring Run engine at optimal New housing/impeller Y distance
water is thrown rpm see what flow we measured distance was from a
4'' nozzle, get 300' 300' = pass Pump test 5 Test impeller housing
Run pump for 100 hours, New housing/impeller Y materials for wear
measure wear from measured wear was abrasives/cavitation less than
1 thou after 100 hours
[0080] The intake cooling test (1) resulted in using an intake
cooling system that is typically used in 1100 horsepower
turbo-charged engines. For all of the pump tests, the 4'' output
nozzle was set at about a 45.degree. angle from the horizon (plus
or minus 10%). During pump test (1) the system did not prime
because there was too much of a gap between the outer edge of the
impeller blade and the inner surface of the impeller housing. This
was addressed by tightening the tolerance between these two
features. Optionally, this may be further addressed by adding
nonferrous materials to the edge of the impeller blades. The
failure of Pump test (2) resulted in manufacturing the impeller
from harder and more durable materials, as further described below.
Pump test (3) resulted in the development of customized impeller
designs based upon the following standards and calculations:
Standard Conversions:
[0081] 1 sq. inch=about 0.004329 US gallon
[0082] 1 sq. inch=about 0.00360465 Imperial gallon
[0083] 1 cubic meter=about 220 imperial gallons
[0084] 1 inch=about 2.54 centimetres
[0085] 1 foot=12 inches
[0086] 1 pound=about 0.453 kilograms
[0087] 1 Imperial gallon=about 4.5 litres
Calculations:
[0088] 1) 6'' impeller with a 3'' lift.times.3 lifts per
rotation=254.34 cubic inches
.times.10,000 rpm=9,168 Imperial gpm.-764 gpm for center hub
displacement. .times.8,000 rpm=7,334 Imperial gpm.-611 gpm for
center hub displacement. .times.4,000 rpm=3,667 Imperial gpm.-305
gpm for center hub displacement.
[0089] 2) 6.25'' impeller with a 4'' lift.times.2 lifts per
rotation=245.3125 254.34 cubic inches
.times.10,000 rpm=8,842 Imperial gpm.-764 gpm for center hub
displacement. .times.8,000 rpm=7,074 Imperial gpm.-611 gpm for
center hub displacement. .times.4,000 rpm=3,537 Imperial gpm.-305
gpm for center hub displacement.
[0090] 3) 6.25'' impeller with a 3'' lift.times.2 lifts per
rotation=183.984 254.34 cubic inches
.times.10,000 rpm=6,631 Imperial gpm.-764 gpm for center hub
displacement. .times.8,000 rpm=5,305 Imperial gpm.-611 gpm for
center hub displacement. .times.4,000 rpm=2,652 Imperial gpm.-305
gpm for center hub displacement.
[0091] 4) 6.25'' impeller with a 2'' lift.times.2 lifts per
rotation=122.656 254.34 cubic inches
.times.10,000 rpm=4,421 Imperial gpm.-764 gpm for center hub
displacement. .times.8,000 rpm=3,537 Imperial gpm.-611 gpm for
center hub displacement. .times.4,000 rpm=1,768 Imperial gpm.-305
gpm for center hub displacement.
[0092] 5) 6.0'' impeller with a 5'' lift.times.2 lifts per
rotation=282.6 254.34 cubic inches
.times.10,000 rpm=10,186 Imperial gpm.-764 gpm for center hub
displacement. .times.8,000 rpm=8,149 Imperial gpm.-611 gpm for
center hub displacement. .times.4,000 rpm=4,074 Imperial gpm.-305
gpm for center hub displacement.
[0093] 6) 6.0'' impeller with a 3'' lift.times.2 lifts per
rotation=169.56 254.34 cubic inches
.times.10,000 rpm=6,112 Imperial gpm.-764 gpm for center hub
displacement. .times.8,000 rpm=4,889 Imperial gpm.-611 gpm for
center hub displacement. .times.4,000 rpm=2,444 Imperial gpm.-305
gpm for center hub displacement.
[0094] 7) 6.0'' impeller with a 2.5'' lift.times.2 lifts per
rotation=141.3 254.34 cubic inches
.times.10,000 rpm=5,093 Imperial gpm.-764 gpm for center hub
displacement. .times.8,000 rpm=4,074 Imperial gpm.-611 gpm for
center hub displacement. .times.4,000 rpm=2,037 Imperial gpm.-305
gpm for center hub displacement.
[0095] 8) 8'' impeller with a 3'' lift.times.3 flights=452.16
254.34 cubic inches
.times.10,000 rpm=16,299 Imperial gpm.-764 gpm for center hub
displacement. .times.8,000 rpm=13,039 Imperial gpm.-611 gpm for
center hub displacement. .times.6,000 rpm=9,779 Imperial gpm.-470
gpm for center hub displacement. .times.4,000 rpm=6,519 Imperial
gpm.-305 gpm for center hub displacement.
[0096] In one embodiment of the present disclosure, the engine 42,
the CVT 60 and the pump 80 of the pumping system 30 has a total,
dry weight of about 290 to about 310 pounds and it is suitable to
be secured to and transported upon a side-by-side recreational
vehicle. Due to the arrangement of the engine 42, the CVT 60 and
the pump 80, the pumping system 30 can achieve a fluid output of
about 6,000 to about 11,000 Imperial gpm. The engine 42 can achieve
a maximum operating rpm of about 13,200 with a maximum horsepower
of about 600 horsepower was achieved at about 10,800 rpm and a
maximum 1,300 pound foot of torque was imparted onto the impeller
90 at about 8,700 rpm. Most components of the CVT 60 were machined
from billet aluminum, with the exception of the endless loop 66 and
the bushings that were made from 43/40 steel to provide a
structural integrity to the CVT 60 that was able to withstand the
loads imparted on the CVT 60 when the pumping system 30 was
operating.
[0097] An intake filter 120 that was a 3/4 inch screen was attached
to the intake conduit 82. The inner diameter of the impeller
housing 98 was about 6 inches (about 15 cm) and a deflector ring
200 (as shown in FIG. 11 and FIG. 12) was employed within the
impeller housing 98. The deflector ring 200 has an out diameter
that is substantially the same as the diameter of the inner surface
102. The deflector ring 200 has inner diameter of about 5.5 inches,
with the difference between the inner and outer diameters shown as
X in FIG. 12. The deflector ring 200 was positioned about 6 inches
towards the intake conduit 82 from the impeller 90. Without being
bound by any particular theory, the deflector ring 200 directs any
debris that passed through the intake screen 120 towards the
mid-line center of the impeller housing 98. The deflector ring 200
decreased debris-induced damage and wear to the impeller 90. The
impeller 90 comprised a 43/40 steel hub with QT 100 plate steel
blades that had a pitch of 3 inches with 3 flights.
[0098] A further set of field tests were performed with a first
further test having the following parameters: The pumping system 30
was positioned about 40 feet above a source W with the intake
conduit 82 was about one hundred feet (approximately 30.5 meters)
long, the output conduit 84 was about 1500 feet (about 457 meters)
long with the manifold 85 positioned about 150 feet (about 45.7
meters) above the pumping system 30 (i.e. a static head of 150
feet, about 46 meters). Both of the conduits 82 and 84 were 6 inch
(about 15 cm) diameter polymer line. The engine 42 was operated at
about half throttle (about 6,500 rpm) and the pumping system 30
achieved a flow rate at the manifold 85 of about 2,000 Imperial
gpm. The fuel consumption of the engine 42 was about 5 gallons of
unleaded fuel per hour.
[0099] A second further field test was performed with the following
parameters: the pumping system 30 was positioned within the source
W with a 6 inch intake conduit 82 and a 4 four inch output conduit
84 with the manifold 85 positioned about 340 feet (about 104
meters) above the pumping system 30 (i.e. a static head of 340
feet). The engine 42 was run again at half throttle, again about
6,500 rpm, and the output flow was about 1000 Imperial gpm. The
inventor notes that one limit on this field study was that the
burst rating of the output conduit 84 was 300 pounds per square
inch (psi), which limited the engine throttle to about 6,500 rpm so
that the pressure of the water as it left the pump 80 did not
exceed 300 psi and rupture the output conduit 84.
[0100] The further field-test performance of the pumping system 30
can be contrasted with other known pumping systems that are
commercially available. For example, based upon publicly available
performance information (see online at:
http://www.xylem.com/Assets/Resources/CD250M_Hush-Pac_EMEA-APAC_Flyer_95--
1016-1099-ENG 9.pdf, the disclosure of which is incorporated herein
by reference), a Godwin CD250M series pump, which weighs about
6,700 pounds (about 6050 kg dry weight) and can achieve an output
flow of about 1400 gpm under 150 feet of head H, however, while
running this pump's engine at a maximum rpm of about 2200. In
contrast, the Godwin CD250M series pump can achieve an output flow
of 1600 gpm against a head H of 80 feet, while operating at about
1800 rpm. The Godwin CD250M series pump has a reported fuel
consumption of about BEP 17 litres/hour when the engine is run at
about 2000 rpm. There are other commercially available pumping
systems that can achieve similar or greater flow outputs than the
Godwin CD250M; however, each of these known pumping systems are
multiple thousands of pounds in total weight and have fuel
consumption rates, at optimal engine speeds, that far exceed the
fuel consumption of the embodiments of the present disclosure.
[0101] Some embodiments of the present disclosure provide the
following characteristics and output parameters: [0102] the engine
42, the CVT 60 and the pump 80 of the pumping system 30 has a
total, dry weight of between about 200 pounds to about 600 pounds
and provides a fluid output of about 1 to about 5000 gpm with a
static head of about 1 ft to about 500 ft [0103] the engine 42, the
CVT 60 and the pump 80 of the pumping system 30 has a total, dry
weight of between about 300 pounds to about 500 pounds and provides
a fluid output of about 1 to about 4000 with a static head of about
1 ft to about 500 ft [0104] the engine 42, the CVT 60 and the pump
80 of the pumping system 30 has a total, dry weight of between
about 300 pounds to about 500 pounds and provides a fluid output of
about 1 to about 4000 gpm with a static head of about 1 ft to about
500 ft [0105] the engine 42, the CVT 60 and the pump 80 of the
pumping system 30 has a total, dry weight of about 300 pounds to
about 400 pounds and provides a fluid output of about 1 to about
3000 gpm with a static head of about 1 ft to about 500 ft [0106]
the engine 42, the CVT 60 and the pump 80 of the pumping system 30
has a total, dry weight of about 300 pounds to about 325 pounds and
provides a fluid output of about 1 to about 3000 with a static head
of about 1 ft to about 500 ft [0107] the engine 42, the CVT 60 and
the pump 80 of the pumping system 30 has a total, dry weight of
about 300 pounds to about 325 pounds and provides a fluid output of
about 1 to about 2500 gpm with a static head of about 1 ft to about
350 ft [0108] the engine 42, the CVT 60 and the pump 80 of the
pumping system 30 has a total, dry weight of about 300 pounds to
about 325 pounds and provides a fluid output of about 1 to about
2000 gpm with a static head of about 1 ft to about 200 ft [0109]
the engine 42, the CVT 60 and the pump 80 of the pumping system 30
has a total, dry weight of about 300 pounds to about 325 pounds and
provides a fluid output of about 1 to about 1000 gpm with a static
head of about 1 ft to about 350 ft
[0110] The aforementioned characteristics and output parameters may
be expressed in one or more ratios. For example, a ratio of dry
weight to fluid output when there is a head pressure within a given
range.
[0111] Further embodiments of the present disclosure relate to a
CVT pump that is of a modular design that comprises a high
horsepower high rpm motor that is coupled to an impeller via a belt
drive CVT, which drives the pump at up to about 13,200 rpm. The
pump further comprised of an intake tail plate, an impeller
housing, a main body outlet, and an impeller shaft, which may be is
supported by a four-bearing system or not. The impeller may be a
bi-vane or a tri-vane axial flow impeller with a single-stage, dual
stage or multiple stage design with a nonferrous impeller vane
sealing system that creates tight tolerances between an edge of the
impeller vanes and an inner surface of the impeller housing. The
CVT may operate at or between a 4 to 1 or a 1 to 1 ratio, depending
on the head pressure at the impeller. The pump may provide a fluid
output between 2,000 and 10,000 imperial gallons per minute,
depending on the head pressure and distance for the fluid to
travel. Without being bound by any particular theory, this pump may
multiply the engine torque, via the CVT, in response to increasing
head pressure at the impeller.
[0112] In further embodiments of the present disclosure the pump
system may be used 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 the drive pulley 63 and the driven pulley 65 is
mechanically implemented with the control mechanism 64 and the
control mechanism spring 68d, respectively, being responsive to the
rotational speed of the shafts 58a 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 the drive pulley 63 and/or the driven pulley 65 by an electric
motor (linear or rotary), hydraulically, or pneumatically.
[0113] In a different embodiment, 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.
[0114] In further embodiments of the present disclosure, the engine
42 and/or the engine 28 may be adapted to perform other operations,
such as generate electric power, supplement one another, or the
like. For further embodiments, a rotary power source may be a
different type of internal combustion engine other than that shown
and described as the engine 42. For instance, the 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.
[0115] For still other embodiments of the present disclosure, 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
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 another
embodiment, 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: AI, Ba, Ca, Ce, Co, Cr, Cs, Cu, In, Mo, Ni,
Pb, Re, Sn, Ta, Ti, V, W, Zn, and Zr. In another embodiment, 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
another embodiment, 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 embodiment, 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, AI, V, N}; {Cr, Al, Si, N}; {Ti, AI, 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 embodiment,
a group of sets each represent a 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/Cr}; {Mo, N/Cr}; 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.
[0116] 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 disclosure without
limiting the construction or scope of any portion of the present
disclosure. 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 disclosure
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, 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 meaning of any embodiments defined or described
herein, including any of the following claims, are desired to be
protected.
* * * * *
References