Note: Descriptions are shown in the official language in which they were submitted.
CA 2961914 2017-03-24
The following represents a detailed description of an invention by Gerald J.
Vowles of
Vankleek Hill, ON Canada KOB 1RO. The purpose of this document is to establish
a priority
date with regard to a yet to be completed patent application for the present
invention. The
balance of the documents and materials required to complete the application
process
including the Claims and Summary will be provided in due course in accordance
with the
instructions and time limits provided by the Canadian Intellectual Property
Office (CIPO).
Title
A Valveless Hydraulic Pressure Intensifier Incorporating Energy Recovery and
Self-
Optimizing Energy Use Means
Abstract
A hydraulic pressure intensifier incorporating energy recovery and self-
optimizing
energy use means for use with, but not limited to, semipermeable membrane
based fluid
filtration and separation systems; these capabilities being provided for by a
valveless,
positive displacement rotary pump based apparatus characterized by separate
pumps or
pump sets moving an unequal volume of fluid at a stable ratio within a shared
circuit. The
apparatus functions without the need for valves, cams, sliding fluid control
parts, switches,
timers, regulators, sensors, electrical or electronic circuitry or any other
similarly acting flow
control, restricting and/or distribution means. It can be driven by a variety
of prime movers
such as rotary or ratcheting cranks, wind turbines, water wheels, wave
followers and
motors, as well as by a relatively low pressure fluid in-feed provided by
either incorporated
or external feed pumps or any other suitable low pressure fluid in-feed means.
Flushing,
backwashing or purging may be accomplished by simply reversing the pumps
rotation.
Technical field
This invention relates generally to hydraulic pressure intensifiers typically
designed for
use with but not limited to crossf low type semipermeable membrane based fluid
filtration
and separation systems. More particularly, it refers to devices of this type
which
incorporate pressure intensification, energy recovery and self-optimizing
energy use
means. Immediate applications include seawater and brackish water
desalination,
freshwater purification and reclamation, the processing of harmful industrial
effluents that
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could otherwise pollute the environment or cause illness and death and a
growing range of
commercial, industrial, institutional, scientific, and military applications.
Background
The growing, global crisis in the need for lower cost, more widely available
potable
water for drinking, food preparation, basic sanitation and, by extension,
disease control is
well known and documented by organizations such as the United Nations and
World
Health Organization who have labelled it the single greatest challenge of the
twenty-first
century. In response, the desalination of seawater and brackish water by
reverse osmosis
has become the primary means of addressing this global crisis for those
coastal regions
and states having access to the significant finances and other resources
required to
implement it. In addition, reverse osmosis and other semipermeable membrane
based
processes such as nano-filtration, ultra-filtration and micro-filtration are
increasingly being
used to process groundwater, industrial, commercial and institutional waste
waters and
effluents, bottled and residential water and for the filtration and separation
of a growing
number of commercial, industrial, institutional, scientific, and military
applications.
Fortunately, ongoing progress in the design, engineering and production
methods of
semi-permeable membranes continues to result in significant improvements in
their
efficiency and range of use as well as in cost reduction.
Unfortunately, driven by such factors as lack of innovation, high production
costs due to
complexity, the need for demanding manufacturing tolerances requiring high
cost
production machinery and a primary focus on utility scale systems, the same
cannot be
said for the devices, systems and processes of which these membranes are the
heart.
The primary goal of the present invention is to provide a solution to these
issues.
Prior Art
The following review of patent applications and grants focuses mainly on prior
art that
incorporates notable similarities of design and/or function to the present
invention.
Numerous, less similar examples were also reviewed but are not included
because major
differences exist. In all these cases, no example of prior art teaches an
apparatus of such
simplicity, while still providing pressure intensification, energy recovery
and self-optimizing
energy use means and prime mover flexibility.
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As shall become apparent in the discussion that follows, the use of valves and
other
hydraulic flow control means provides the most useful way of comparing the
advantages of
apparatus of the present invention over the prior art. Specifically, all of
the prior art
apparatus studied depend for their operation on some combination of valves
and/or flow
control means, whether these be primary control valves, directional control
valves such as
check (non-return), spool, poppet or sliding valves or valve designs that are
unique to the
inventors. In some cases, externally controlled solenoid valves, pressure
control, relief,
and reducing valves and flow (volume) control valves as well as electro
hydraulic, servo,
and proportional valves are used. Other non-valve flow control and/or
restricting means
were also encountered.
By way of comparison, the apparatus of the present invention does not require
the use
of any of these components which, besides adding unnecessary complexity,
introduce
varying degrees of flow resistance, whether from turbulence, disruption or
restriction,
thereby leading to a loss of efficiency. Their inclusion also increases the
potential for
fouling related blockages, component failure due to fatigue or corrosion and
leakage due to
uneven wear of precision machined or polished sliding and mating surfaces. Any
of these
can lead to reduced life cycle, premature failure and/or more frequent
maintenance and, in
combination, this potential only increases. Complexity also invariably adds to
manufacturing and quality assurance costs and increases supply chain
requirements.
As shall become apparent, these significant disadvantages are addressed and
overcome by the simplicity and the unique and novel aspects of the present
invention.
US 8,449,771 Philip David Giles:
This rotary type device incorporates one or more oscillating partitions that
sweep back
and forth around an axis, that being a centre shaft. These serve the same
purpose as do
impellers in rotating pumps or pistons in reciprocating pumps, however, the
sweep
alternates back and forth rather than being continuous as with the present
invention. The
device also incorporates low pressure and high pressure pumps and a spool
valve in
addition to the two oscillating pumps. While the device does provide for
energy recovery, it
is not an energy intensifier.
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US 8,025,157 Shigeo Takita:
Like that of US 8,449,771 Giles discussed above, this rotary type device
incorporates
energy recovery means but does not function as an energy intensifier. It also
incorporates
an electric motor driven high pressure pump, which the apparatus of the
present invention
does not require. While its power recovery module is a rotary device with two
pumps
mounted on a common shaft, it uses a turbine rather than a positive
displacement pump
like the apparatus of the present invention. In a second embodiment an
additional positive
displacement piston pump and a control valve are incorporated, adding further
to the
complexity of the system. In several other variations a plurality of other
valves and
controllers are employed adding further to its complexity.
US 2006/0,037,895; Appl. No. 10/922,284 Scott Shumway:
This rotary type device is comprised of three main sections, those being a
high pressure
boost pump, a pressure exchanger and a low pressure boost pump, all mounted on
a
common shaft running coaxially through the three sections and attached to a
prime mover
such as a motor. The apparatus of the present invention is comprised of only
two sections.
The high pressure boost pump uses one or more spinning impellers to further
boost an
already high pressure fluid stream whereas the present invention is capable of
drawing in
unpressurized fluid and converting it to high pressure. The pressure exchanger
incorporates another two spinning rotors and the low pressure boost pump
incorporates
what is defined as "a series of impellers". This amounts to a minimum of six
spinning
members versus as little as one but typically two or four in the apparatus of
the present
invention with it being noted that the present invention's impellers may be
rotated at low
speed. The operating principles are also different, this made more evident by
the fact that a
fully functioning filtration system incorporating this pressure exchange
device requires an
additional reservoir pump, that being a low pressure feed pump as well as a
high pressure
pump. The apparatus of the present invention, when incorporated into an
equivalent fully
functioning filtration system requires neither of these additional pumps. This
significantly
more complex device only boosts what is already a high pressure fluid stream
by about 20
psi according to the inventor.
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US 4,632,754 Robert S. Wood:
A reversing cycle device wherein a first embodiment incorporates a reservoir
employing a
reciprocating piston and three valves cooperating with mechanical linkages. In
a second
embodiment of thd device, the three valves used in the first embodiment are
replaced with
a rotary plate valve, the reciprocating piston based reservoir is replaced
with a flexible
membrane based reservoir and a second pump is added to provide liquid
recirculation
through the filtering means. Variations of this embodiment additionally
incorporate either a
vane type reciprocating pump or a gear box driven cam. Unlike the continuous
rotation of
the apparatus of the present invention the various embodiments of this device
operate on
reversing cycles and they incorporate valves and other flow control means.
US 3,369,667 George B. Clark:
Similar to the apparatus of the present invention in physical design, this
rotary type device
incorporates a set of two rotating positive displacement impellers located in
separated
casings, both of which are fixedly attached to a common shaft such that they
rotate in
unison. However the operating principles and fluid flow within the two
apparatus are very
dissimilar. Rather than acting as a pressure intensifier, this apparatus is
designed to
continuously recirculate the flow of high pressure fluid across the filtering
element in order
to increase the ratio of permeate to waste fluid. On the other hand, the
apparatus of the
present invention functions primarily as an pressure intensifier and energy
recovery device,
rather than primarily as a fluid recirculator. This difference can be seen in
terms of the fluid
flow paths and pressure differences between the two devices with the most
obvious
difference being that the feed fluid flows freely and at the same pressure
between the two
casings of the device while neither of these conditions is true for the
apparatus of the
present invention. It is also noted that the device requires both a feed pump
and a
pressure valve in order to operate within a fully functioning filtration
system whereas the
apparatus of the present invention requires neither to accomplish the same.
US 7,828,972 B2 Young-Bog Ham:
This reciprocating piston, dual cylinder based apparatus incorporates an
assembly wherein
a primary valve, called a concentrated water control valve block, includes a
concentrated
water chamber cover functioning as a hydrostatic bearing using the pressure of
supplied
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water, a concentrated water inlet/outlet cover and a fluctuating plate-like
concentrated
water valve, the latter part being required to rotate between the covers. In
order for the
valve to rotate a plurality of pinion gear teeth are located on its outer
peripheral surface.
These teeth are enmeshed with teeth on two rack gears located in separate,
opposite
spools which in turn interact with a plurality of pilot valves. A plurality of
check valves are
also incorporated into the apparatus.
US 7,297,268 B2 Rodney E. Herrington:
This dual head, single acting, reciprocating diaphragm pump incorporates a
primary valve
called a differential pressure activated (DPA) valve, which requires the
presence of
additional check valves to function. The pump's cycle involves a suction
stroke that
requires work and time but during which production does not occur, unlike the
continuous
flow and production from the rotary cycle of the present invention. As with
the apparatus of
the present invention, the device provides for energy recovery.
US 2009/0194471 Al Antonio Pares Criville:
This double-acting,reciprocating piston based apparatus incorporates two
primary valves
comprised of sliding members, clips and springs with protective sheaths. The
clips connect
the sliding pieces to thicker sections of two piston rods which, in turn, drag
the sliding
pieces with them as they approach the end of their stroke, causing the shift
in the position
of the two primary valves needed to reverse the pistons. It is based upon an
earlier, single
pressure intensifier design (US 6,604,914 B2 Criville) discussed below. This
apparatus
incorporates two pressure intensifier units operating in opposition, rather
than just one as
with the apparatus of the present invention.
US 6,604,914 B2 Antonio Pares Criville:
This design teaches a double acting, self-reversing piston design. It utilizes
both a primary
valve, called a directional valve and a separate pilot valve. The directional
valve
incorporates two sliding blocks with flat, polished sliding surfaces that mate
with adjacent
sliding surfaces to seal against passage of pressurized fluid. The separate
pilot valve also
incorporates these mating, flat, polished sliding surfaces. These valves then
interact
cooperatively in order to accomplish the cyclical reversing of the double
acting piston.
Unlike the present invention, an additional chamber is also needed. As stated
in the
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discussion of US 2009/0194471 Al Criville, this design was the basis for
certain marine
water maker models sold but later withdrawn from the market by companies
called HRO
and Sea Recovery Corp. Based on unconfirmed end-user comments, this was
apparently
due to unusually high, valve related premature failure and maintenance issues.
US 6,491,813 B2 Riccardo Verde:
This double acting, reciprocating piston design teaches several embodiments.
In the first
embodiment, the primary valve, called an exchange valve, works in cooperation
with four
check valves and also requires micro switches to initiate piston reversal. A
variation of this
first embodiment uses a pilot valve cooperating with a primary valve called a
"power valve,"
as well as still requiring the plurality of check valves. In a second, similar
embodiment a
high pressure feed pump is added to the system, while continuing to use the
low pressure
feed pump. Variations of this embodiment utilize either bypass, throttle or
exhaust valves.
A final embodiment introduces machined grooves into the piston rod, thus
allowing for a
change in fluid flow at certain piston positions as means for shifting the
position of the
power valve and in a variation, the pilot valve is replaced with a ducted
plate that interacts
with the shaft grooves with all in turn interacting in a cooperative manner
with the power
valve. In all of the above configurations, the large number of valves,
whatever the type,
adds significant complexity to the apparatus.
US 6,203,696 B1 Colin Pearson:
This double acting, reciprocating piston design does not rely on a single,
primary valve.
Rather, it incorporates eight valves, all working cooperatively within the
apparatus.
According to the description these are a unique poppet valve design
incorporating an
integrated, secondary bleed valve and springs. Four of these serve as control
valves that
are mechanically actuated by the pistons.
US 6,017,200 Willard D. Childs:
This double acting, reciprocating piston design incorporates a minimum of
eight separate
check valves and a non-hydraulic control unit to control the feed pump as well
as solenoid
actuated water pilot and air pilot valves.
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US 5,628,198 Clark Permar & US 5,462,414 Clark Permar:
The two described apparatus, each being a double acting, reciprocating piston
design
incorporate a primary valve called a re-track valve, that being a two way
spool valve, as
well as four check valves and two pilot valves with the latter interacting
mechanically with
dual, opposed piston heads at each stroke end triggering a shift in the re-
track valves
position that in turn causes the piston to reverse.
US 4,929,347 Masaaki 'mai:
In a first embodiment a single acting, reciprocating piston is powered by a
rod extending
out of the pumping cylinder to a reciprocal drive pump. A spool type primary
valve called a
selector valve interacts cooperatively with check valves, unlike the apparatus
of the
present invention which eliminates the need for valves. In a second
embodiment, a third
partition is added to the selector valve due to a variation in the routing of
the fluid flow. In a
third embodiment, a second single acting, reciprocating pump is arranged in
parallel with
the first pump with their pistons reciprocating in opposite directions. In
fourth and fifth
embodiments, which are also reciprocating single and dual pump variations of
the above,
most of the check valves are eliminated by incorporating second pistons into
each of the
pumping cnambers and adding sub-selector valves.
US 4,913,809 A lwao Sawada:
A double acting, reciprocating piston design where, in a first embodiment, a
pilot valve is
used to control one or more selector valves that cooperate with two check
valves to cause
reversal of the double acting piston. In a second embodiment two additional
check valves
are needed. In both cases, non-pumping pistons are incorporated into either
one or both of
the pilot and control valves, adding further complexity to the design.
US 4,534,713 & US RE 33,135 William F. Wanner:
The apparatus is comprised of an electro-mechanical or hand driven single
acting,
reciprocating piston pump utilizing a spool type primary valve working in
cooperation with
inlet and outlet valve assemblies comprised of seats, poppets, springs and
spring
retainers. The spool valve shuttle is reversed directly by a mechanical
linkage to an
external prime mover. The apparatus is designed specifically for use as a
seawater
desalinator and is similar in design and function to US 4,187,173 Keefer and
US 3,558,242
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Jenkyn-Thomas. A commercial version of the apparatus was embodied in both the
manual
and electric powered PUR brand portable desalinators.
US 4,367,140 A Leslie P. S. Wilson:
This double acting, reciprocating piston design incorporates a valve
controller (whether
electrical, mechanical or hydraulic) in communication with four non-return
valves. These
are in addition to four more non-return valves for a total of eight. A second
embodiment
utilizes a spring loaded pulse pump that responds to pressure pulses by
operating a semi-
rotary reversing switch which, in turn, cooperates with a discrete pressure
intensifier. A
plurality of flow control valves such as check valves are also a requirement
of this
embodiment. A third embodiment replaces the pressure intensifier assembly of
the second
embodiment with an pump assembly comprised of a piston within a cylinder with
rods
extending through seals in the cylinder chambers walls on each side of the
piston to
connected ball valves with it being stated by the inventor that two such
control devices
would be required. Otherwise, the complexity of the second embodiment remains.
A fourth
embodiment incorporates a solenoid switch interacting with a set of opposing
ball valves.
Finally, a fifth embodiment describes a construction wherein the spools of the
spool valve
are located on a rod that serves as an armature for a solenoid switch
cooperating with a
timer or a proximity sensor on the main piston.
US 4,187,173 & US RE 32,144 Bowie G. Keefer &
US 4,288,326 Bowie G. Keefer (continuation in part of US 4,187,173):
In each case, the apparatus incorporates reciprocating, single acting pumping
piston. In
order to maintain a flow of pressurized fluid to an incorporated, semi-
permeable membrane
for the extended time needed to complete the return suction stroke, an
accumulator like
feed surge absorber chamber comprised of a spring driven piston in an
expansion
chamber is employed. The apparatus primary valve is a two position, centre-
closed, three-
way spool valve with a closed intermediate position, this valve working
cooperatively with
two check valves. Both the spool valve and a pumping piston work cooperatively
via
linkages connected to a common drive such as a manual lever or a cam shaft. As
with the
apparatus of the present invention, the device provides for energy recovery.
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US 3,855,794 Kenneth H. Mayer:
While there are similarities to some circuits taught in other prior art
examples described in
this document, the objective of this apparatus is to synchronize the movement
of at least
two reciprocating, hydraulic cylinders rather than to provide an energy
recovering pressure
intensifier. The design incorporates a combination of check valves, relief
valves and a fluid
power control source to accomplish its synchronization objectives.
US 3,558,242 William Dixon Jenkyn-Thomas:
This single acting, reciprocating piston design is similar to US 4,187,173
Keefer but does
not incorporate any accumulator/surge absorption capability. There are two
embodiments,
each employing a spool valve as the primary valve. The first incorporates two
check valves
working in cooperation with a manually operated and controlled 2-port spool
valve while
the second incorporates a manually operated and controlled 3-port spool valve.
In both
embodiments, the spool valve and pumping piston work in fixed cooperation
through a
mechanically connected lever arm and linkage assembly.
US 3,234,746 Lewis T. Cope:
In this case, an apparatus and method for transferring liquid carbon dioxide
from a supply
container to a cylinder under pressure is described. A double acting,
reciprocating piston
with a shared rod operating in two collinear cylinders is employed with the
driven piston
being smaller than the driving piston. A cam located at the centre of the
piston rod
mechanically engages control followers at each end of the reciprocating stroke
in order to
activate the primary valve called a reversing valve. The design also
incorporates a large
number of check valves.
In conclusion and by way of comparison to the prior art, the present invention
teaches a
highly simplified apparatus that is, nonetheless, capable of providing
hydraulic energy
intensification, energy recovery and self-optimizing energy use means, while
overcoming
the complexity related costs and disadvantages of the aforementioned prior art
and does
so in accordance with the following objectives.
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Objectives of the Invention
The objectives of the present invention are to: greatly reduce the build
complexity
typical of the prior art; reduce the servicing requirements and servicing
complexity typically
associated with the prior art; provide at least one embodiment which does not
require the
tight manufacturing tolerances typical of the prior art designs, thereby
reducing the need
for sophisticated production capability and/or supply chain; provide a design
which, not
including the outsourced membranes, could be produced at a low enough cost to
be
considered expendable and preferably also recyclable; provide a design which
is better
suited than the prior art to production by emerging additive manufacturing
means, often
referred to as 3D printing; provide a design which can be powered by a wide
range of
prime movers and in different ways in order to maximize its fitness for use in
differing
situations; provide an apparatus which, when used to produce potable water,
better
addresses local supply chain, knowledge and financial limitations in less
developed
regions where safe, potable water is often scarce; provide an apparatus which
is suitable
for rapid deployment and simple operation during times of natural disaster.
As shall become apparent in the following description of the present
invention, these
objectives, as well as the significant disadvantages or limitations of the
prior art, are
addressed and overcome by the simplicity, flexibility and novelty of the
present invention.
Summary of the Invention
The Summary and Claims will be provided in due course in accordance with the
instructions and time limits provided by the Canadian Intellectual Property
Office (CIP0).
Brief Description of the Drawings
Figure 1 provides a schematic side view of a first embodiment of the present
invention
wherein a prime mover, that being a manually operated rotary crank handle in
this
particular case, is employed to rotate two positive displacement pumps of
different
volumetric displacement mounted onto a common shaft. An optional belt and
pulley
assembly is employed to provide a mechanical advantage.
Figure 2 provides a schematic side view of the first embodiment of the present
invention
wherein the rotation of the apparatus is reversed as a means of flushing,
backwashing or
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purging those semi-permeable membranes and pre-filters typically associated
with the
systems within which the apparatus of the present invention is intended to
operate.
Figure 3 provides a schematic side view of a variation of Fig's 1 and 2
wherein the
individual pumps are replaced with same acting pump sets such that the pumps
within
each set are connected in either series or parallel.
Figure 4 provides a schematic side view of an embodiment of the invention
equivalent to
those above except that the prime mover employed to rotate the pumps is an
external
source of pressurized fluid acting directly upon the first pump's impeller(s).
Certain non-
essential features are removed in this more basic embodiment.
Figure 5 provides a schematic side view of a typical single shaft, gerotor
type positive
displacement pump, it being an example of a pump type capable of producing the
high
pressure required for the application taught in the detailed description of
Fig. 18.
Figure 6 provides a schematic side view of a flexible impeller, vane type
positive
displacement pump which, in this case, incorporates certain unique features
designed to
increase the pump's pressure handling capability, particularly with regard to
the apparatus
of the present invention.
Figure 7 provides a schematic side view of a typical external gear type
positive
displacement pump design commonly used in high pressure applications and which
could
be incorporated into the apparatus of the present invention.
Figure 8 provides a schematic side view of a typical vane type positive
displacement pump
design. Conventional units are available with both spring and hydraulically
actuated vanes
and either could be incorporated into the apparatus of the present invention.
Figure 9 provides a schematic side view of a typical peristaltic type positive
displacement
pump design that might be incorporated into the apparatus of the present
invention for low
pressure applications.
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Figure 10 provides a schematic side view of a peristaltic type positive
displacement pump
similar to that of Fig. 9 but with attention drawn to the option of mounting
two peristaltic
hoses into a shared cavity.
Figure 11 provides a schematic side view of a rotating wind turbine type prime
mover that
could be employed to rotate the apparatus pumps, whether by direct attachment
or through
a speed changing means.
Figure 12 provides a schematic side view representative of a rotating water
wheel or water
turbine type prime mover that could be employed to rotate the apparatus pumps,
whether
by direct attachment or through a speed changing means.
Figure 13 provides a schematic side view of a ratchet handle type prime mover
that could
be employed to rotate the apparatus pumps whether continuously or in
incremental steps
and whether by direct attachment or through a speed changing means.
Figure 14 Removed - to be filed under a separate application.
Figure 15 provides a schematic side view representative of any motor type
prime mover,
whether it be electric, hydraulic, pneumatic, fuel powered or otherwise, that
could be
employed to rotate the apparatus pumps, whether by direct attachment or
through a speed
changing means.
Figure 16 provides a schematic side view representative of any pressurized
fluid bearing
conduit such as a pipe or hose that could be employed to provide external,
prime mover
capability to the apparatus through direct interaction with an pump's
impeller(s) rather than
via a rotating drive shaft.
Figure 17 provides a schematic side view of an optional flywheel with over-
riding clutch
assembly. Such an arrangement would typically be incorporated between the
apparatus
drive shaft and the prime mover as an input smoothing and sustaining means and
employed when irregular input prime movers such as the wave follower Fig. 14
are
employed. It could also be employed as a higher capacity input energy storage
means.
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Figure 18 provides a schematic side view of the apparatus of the present
invention
integrated into a semi-permeable membrane based fluid filtering system, in
this case being
an integrated, portable, manually powered reverse osmosis type water
purification system.
Figure 19 provides a schematic side view of a simple setup used to facilitate
flushing,
backwashing and/or purging of the system shown in Fig. 18.
Figure 20 provides a schematic side view of an optional manifold assembly
representative
of how various accessories deemed by the user to be useful or adding
convenience may
be attached to the apparatus, whether permanently or only as needed.
Figure 21 provides a schematic side view of a highly simplified embodiment of
the present
invention wherein the two separate positive displacement pumps of previous
embodiments
are replaced with a single, positive displacement impeller module
incorporating
circumferential fluid sealing means that divide a single, shared cavity into
separate
pumping chambers of different volumetric displacement.
Figure 22 provides a partially rotated three dimensional (3D) view of the
impeller module
incorporated into the apparatus described in Fig. 21.
Figure 23 provides a schematic end view of the apparatus taught in Fig's 1 and
2 with
attention focused on the pumps that are incorporated into this preferred
embodiment of the
present invention.
Figure 24 provides a partially rotated three dimensional (3D) view of the
impeller module
incorporated into the apparatus described in Fig. 23.
Figure 25 provides a schematic end view of a rigid but otherwise same acting
impeller for
use in the apparatus seen and described in Fig. 23.
Detailed Description
Referring to the figures in general, all of the fluid conduit means
incorporated into the
apparatus of the present invention, whether they be channels, pipes, tubes or
other
equivalent means and including their inflow and outflow ports, are
unrestricted. That is to
say that they do not incorporate or require the direct or indirect use of any
flow restricting
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means such as valves, regulators or other flow control means.
In practice, these fluid conduit means are sized and laid out in a fashion
that minimizes
resistance to flow and unevenness of flow due such factors as friction,
directional turns or
conduit size. In fact, as shall be seen, the apparatus of the present
invention provides the
means by which a complete fluid filtration or separation system including all
necessary
connectors and couplings may be assembled wherein the only significant
restrictions to
fluid flow are the pump's impellers and the unavoidable resistance associated
with fluids
passing through the filtration media.
While discrete fluid sealing components are incorporated into the apparatus
described
herein, other embodiments may be produced with tight enough clearances and
tolerances
that these or similarly acting sealing components are either minimally or not
at all required,
particularly for those intended to be expendable and/or recyclable in nature.
Because the positive displacement pumps incorporated into the apparatus of the
present invention variably function as pumps, hydraulic motors, circulators
and flow
resistors depending on their rotation direction, position within the fluid
circuit, prime mover
means and because a variety of pump types and designs may be incorporated into
different embodiments of the apparatus, the following description uses the
term pump
interchangeably when referring to these components. In similar fashion, the
term cavity is
understood to have the same meaning as the term chamber, which is also
commonly used
in describing different pumps types and features.
A key operating principle of the apparatus of the present invention, is the
existence of a
stable, volumetric difference in the amount of fluid displaced by each of two
positive
displacement pumps or pump sets operating within the same closed circuit such
that the
greater flow volume from the upstream pump encounters a back pressure from the
downstream pump, resulting in a rise in pressure in that part of the closed
circuit
incorporating a cross-flow, semipermeable membrane means located between the
two
pumps. This can be implemented in at least three ways. The first, being the
preferred
implementation, employs two pumps or pump sets with different internal
displacement
rotating at the same speed such that their output volumes differ at a stable
ratio or ratio
range. The second employs two pumps or pump sets with the same internal
displacement
rotating at different speeds such that their output volumes differ at a stable
ratio or ratio
Page 15 of 43
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range. The third employs two pumps or pump sets with different internal
displacement
rotating at different speeds such that their output volumes differ but still
at a stable ratio or
ratio range. In any of these cases it is understood that the ratio could be
adjusted but that
would require adding complexity. Other variations may also be possible but
regardless of
which approach is taken, the operating principle remains essentially the same.
However,
for the benefit of greater clarity and ease of understanding, only the first
of these
implementations forms the basis for the preferred embodiment and its variants
presented
herein, with the understanding that with the addition of varying degrees of
complexity and
cost, typically involving at least the use of external control means and/or
more complex
prime mover requirements, those other implementations mentioned above could be
employed to achieve the same outcome employing essentially the same core
operating
principles. Therefore, it is understood that while the description of the
embodiments taught
herein refers specifically to pumps or pump sets of different internal
displacement due to
the opportunity for least complexity, this is not meant to limit this
inventor's claims to only
that particular means or arrangement of parts for providing a displacement
volume
differential between two positive displacement pumps or pump sets.
Referring now to Fig. 1, a first preferred embodiment of the present
invention, hereafter
referred to as the core module 1, a rotational speed changing means, hereafter
referred to
as the pulley assembly 2 and one of numerous prime mover possibilities, a
crank handle 3
are shown. The crank handle 3 is telescopic in nature in order to provide the
user with an
adjustable mechanical advantage means and, in this embodiment, is used to
drive the core
module 1 in a generally continuous rotation. The crank handle 3 is fixedly
attached by
means of a female spline bore 4 to a freely rotating, splined shaft 5 that is
rotatably
attached to a main body 6 of the core module 1. A first pulley 7 is fixedly
mounted to the
freely rotating splined shaft 5. A second pulley 8 is fixedly mounted to a
second splined
shaft, hereafter referred to as the common shaft 9, running horizontally
through the main
body 6. A drive belt 10 connects the two pulleys 7 and 8 in typical fashion
such that rotating
the crank handle 3 causes the common shaft 9 to rotate. The pulley assembly 2
incorporates an adjustable, belt tensioning idler sub-assembly hereafter
called the idler
pulley 11, shown here being mountable to the core module 1 with a mounting
plate 12.
It is noted at this time that the use of the pulley assembly 2 and associated
freely
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rotating spline shaft 5 or of any similarly acting rotational speed changing
means such as a
gearbox is not required in all cases for the operation of the apparatus and so
is deemed to
be optional. For example, the crank handle 3 may be mounted directly to the
common
shaft 9. Also, as shall be seen, the crank handle 3 is only one of many prime
mover means
that may be employed to power the apparatus. It is also noted that the pulley
and belt
system could be replaced with such similarly acting means as a gearbox, or a
gearbox and
flywheel combination.
Focus is now directed specifically to the non-optional, core aspects of the
embodiment
of the present invention shown here in Fig. 1 but, which are understood to
also apply to
those other embodiments taught herein. With that in mind, the major components
of the
core module 1 include the main body 6, which incorporates first and second
circular
shaped access ports with fluid sealed covers, hereafter referred to as a front
port and
cover 13 and a rear port and cover 14; the previously mentioned common shaft
9; a first
positive displacement pump with a displacement of 1.0 volumetric units (VU),
hereafter
referred to as the 1.0 VU pump 15; a second positive displacement pump with a
displacement of 0.9 volumetric units (VU), hereafter referred to as the 0.9 VU
pump 16;
four essential fluid conduits, these being an in-feed conduit 17 and an output
conduit 18,
communicating with the 1.0 VU pump 15; an in-feed conduit 19 and output
conduit 20,
communicating with the 0.9 VU pump 16; and a non-essential but recommended
flushing
conduit 21 and associated port 39 that become involved only if and when the
apparatus is
driven in reverse rotation for the purpose of flushing, backwashing or purging
feed fluid
from various components of those systems which the apparatus may be integrated
into ¨
otherwise this normally blocked flushing conduit 21 could be eliminated. It is
noted that all
of these conduits will be referred to by the term conduit and its associated
number.
Other components of the core module 1 include suitable, fluid pressure sealed
bearings
or bushings into which the common shaft 9 is rotatably mounted, these
hereafter being
referred to as shaft bearings 22 and 23; spring-lock washers 24 and 25 fitted
into grooves
in the common shaft 9 in order to hold it in place; a suitable fluid seal, in
this case being an
0-ring 26 mounted into a groove 27 in that portion of the main body 6
separating the
chambers of the 1.0 VU pump 15 and 0.9 VU pump 16; any suitable fluid seals,
in this
case being an 0-ring 28 inserted into a groove 29 in the front port and cover
13 and an 0-
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ring 30 inserted into a groove 31 in the rear port and cover 14. Fastening
means suitable
for holding the port and covers 13 and 14 affixed to the main body 6 such that
they are
sealed against the loss of pressurized fluid as well as suitable for the
chosen in-situ
environment are employed in whatever quantities needed for the purpose. In
this case
these fastening means are comprised of a suitable number of non-corroding
machine
screws, but are hereafter more generally referred to as port fasteners 32
while recognizing
that other suitable means such as cam lock mechanisms could also be employed
for the
purpose. The freely rotating, splined shaft 5 incorporated into the main body
6 is rotatably
mounted into a bore hole 33 in the main body 6 and held in place by an
appropriate
retaining means 34.
While conduits 17, 18, 19 and 20 are open ported at their intake and output
ends such
that they do not incorporate any flow-restricting elements or components, it
is understood
that suitably mated connectors may be employed outside the apparatus of the
present
invention in order to integrate the core module 1 into various processing
systems such as
that taught in the description of Fig. 17. They too should be of the non-flow-
restricting type
whenever those systems allow. In the case of the apparatus taught herein,
these external
connectors are understood to compatible with the ports 35, 36, 37, 38 and 39,
even though
their type and design would be dependant on the associated system's design.
Except for their differing volumetric displacement, the 1.0 VU pump 15 and 0.9
VU
pump 16 are otherwise typically identical. Preferably, this also includes the
radial alignment
of their impellers whether they be gears, vanes, rollers or other fluid moving
parts, this in
order to maintain the best possible pressure and flow matching between the two
pumps as
their impellers rotate in unison.
As shall also be seen with other embodiments of the apparatus the chambers of
the 1.0
VU pump 15 and the 0.9 VU pump 16 in which the impellers move fluid are
actually
cavities within the main body 6. In that regard, it is seen here that the
section of the main
body 6 located between the two pump cavities serves as a pressure and fluid
sealed
divider wherein the 0-ring 26 serves to prevent the passage of pressurized
fluid along the
bore 40 through which the common shaft 9 passes. It is noted however, that
other
embodiments of the present invention could employ discrete pumps incorporating
their
own housings.
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While specific design and structural details of the 1.0 VU pump 15 and the 0.9
VU pump
16 are not shown in Fig's 1 to 4 because a variety of positive displacement
pump designs
may be used depending on their suitability for the intended application,
several examples
of are provided in Fig's 5 to 10, including a more detailed description of one
type
understood to be employed in the preferred embodiments of the apparatus.
While the direction of rotation is ultimately tied to any given pump's design,
the flows
and pressures associated with the normal production cycle of any of the
apparatus taught
herein are, for convenience, assumed to be based on the clockwise rotation of
the 1.0 VU
pump 15 and the 0.9 VU pump 16. With that in mind and with the aid of flow
direction
arrows, it is seen here that feed fluid first enters the apparatus through the
port 35 into the
conduit 17 which opens into the 1.0 VU pump 15. It is noted that in this
embodiment, the
1.0 VU pump 15 also serves as the feed pump for the apparatus by virtue of
it's ability to
draw in feed fluid by creating a partial vacuum when rotated, thereby having
the advantage
of eliminating the need for an external feed pump in most cases.
Having been drawn into and propelled through the 1.0 VU pump 15, the fluid
flows into
the open ended conduit 18 and on out of the core module 1 through the port 36
from where
it continues on via any suitably connected, fluid sealed and preferably
unrestricted conduit
into whatever system the core module 1 has been integrated into, that
typically being a
cross-flow, semi-permeable membrane based filtration or separation system.
Noting that because the focus here is on Fig. 1 and to facilitate
understanding, a
detailed tracking of the flow path within those circuits and aspects of the
filtration or
separation system beyond the core module 1 is provided later in the
description associated
with Fig's 18 to 20. However, a key aspect in understanding the functionality
of the
apparatus of the present invention seen here in Fig.1 relates to how fluid
pressure
intensification occurs and how the energy stored in the resultant, more highly
pressurized
fluid is then used by the apparatus to greatly reduce its own energy
requirements, rather
than being wasted as is often the case. Therefore, rather than looking ahead
at this time to
the description of Fig. 18, it is noted now for the benefit of clarity that
after passing
through the connected filtration or separation system (a) 0.9VU of the fluid
that was
propelled out of the core module 1 by the 1.0 VU pump 15 through the port 36
returns via
any suitably connected, fluid sealed and preferably unrestricted conduit,
there re-entering
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the core module 1 through a port 37 into a conduit 19 that in turn opens into
the smaller
displacement 0.9 VU pump 16 and (b) the fluid within that part of the circuit
located
between the pumps 15 and 16 is now under high pressure for reasons that shall
become
apparent in the description of Fig. 18.
Finally, upon passing through the 0.9 VU pump 16 where the energy stored in
the high
pressure fluid is recovered and transmitted via the common shaft 9 to the 1.0
VU pump 15,
the now depressurized fluid is expelled from the core module 1 through the
output conduit
20 and the port 38, in most cases without any significant pressure but in
somewhat more
concentrated form. That then defines the path of the fluid from the time it
initially enters the
the core module 1 as raw feed fluid until, after having passed through and
returning from
the connected filtration or separation system, it finally exits the core
module 1 for the
second time, now in moderately more concentrated form due to 0.1 VU having
been
processed and drawn off outside the apparatus of the present invention in a
manner that
too shall become apparent in the description of Fig. 18.
However, it is noted that the port 39 and conduit 21 remain unaccounted for in
this flow.
This is due to the fact that they are not involved in the normal production
phase that takes
place during the just described clockwise rotation of the apparatus and so,
are addressed
later on in the description. In that regard, it is also understood that while
the port 39 and
conduit 21 are non-essential for the basic operation of the apparatus, they
have been
incorporated into the apparatus described herein as an innovative means of
facilitating
system cleaning and servicing and a convenient means by which optional
components
such as monitoring devices may be attached, all without adding complexity.
Reference is now made to Fig. 2, which focuses on the effect on fluid flows
and pressures
within the core module 1 when rotation of the pumps 15 and 16 is reversed by
rotating the
common shaft 9 counterclockwise. This is done for the purpose of flushing and
backwashing those semi-permeable membranes and pre-filters typically
associated with
the systems within which the apparatus of the present invention is intended to
operate, as
well as for purging these same systems of unprocessed feed fluids and
replacing them
either with purified permeate that the system has already produced, whether
with or
without added constituents, or with some other suitable fluid for the purpose
of maintaining
the system in good condition during periods of non-use including storage.
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Recalling that in Fig.1 the flows and pressures were based on the clockwise
rotation of
the impellers or similarly acting fluid moving elements of 1.0 VU pump 15, the
0.9 VU
pump 16 and the common shaft 9 to which they were fixedly attached, it is
shown here in
Fig. 2 with the aid of directional arrows that upon reversing the rotation of
these elements
to counter-clockwise, a reversal of the fluid flow occurs. Fluid is now first
drawn through
port 38 and conduit 20 into the smaller displacement 0.9 VU pump 16 from
whence it is
propelled back out of the core module 1 through the conduit 19 and the port
37. Following
the same circuit as before but in reverse, the fluid then flows on into the
connected filtration
or separation system and from there back into the core module 1 through port
36 and
conduit 18 into the larger displacement 1.0 VU pump 15 from where it is
expelled through
the conduit 17 and port 35 as waste, having taken on accumulated residue from
the outer
surface of the semi-permeable membrane. Assuming the likely presence of one or
more
intake pre-filters being connected in some way to the port 35, as shall be
seen later in Fig.
17, the reverse flow of fluid may also be utilized to backwash these, thereby
extending
their useful life and mitigating the gradual loss of efficiency that would
occur as a result of
residue buildup on the surface of the intake pre-filters. It is understood
that these residues
are the materials whose passage has been blocked by the semi-permeable
membranes
and pre-filters during the clockwise rotation based production phase.
In effect, this represents a simple reversal of flow along the same path as
that taken in
clockwise rotation mode. However, in practice, this is not practical for two
reasons. Firstly,
in the case of clockwise rotation, fluid is moved from the larger displacement
1.0 VU pump
15, through the connected filtration or separation system and on back to the
smaller
displacement 0.9 VU pump 16, giving up within the filtration or separation
module a portion
of the fluid equal to the difference in volumetric displacement of the pumps
15 and 16. It is
noted that being an enclosed circuit and due to the resistance imparted by the
semi-
permeable membrane through which the given-up portion of fluid must pass, this
results in
a steep fluid pressure increase in the portion of the circuit between the
pumps 15 and 16,
the details and understanding of which shall become apparent in the
description of Fig. 18.
However, in counter-clockwise mode, the flow now moves from the smaller
displacement 0.9 VU pump 16 to the larger displacement 1.0 VU pump 15. Being
that
these fixedly linked pumps 15 and 16 are of the positive displacement type
moving an
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essentially incompressible/non-expandable fluid within an enclosed circuit,
this means that
makeup fluid must be found to fulfil the greater demand of the larger
displacement 1.0 VU
pump 15 in order to address such potential issues as cavitation, pressure
lock, stressing or
damaging of connected semi-permeable membranes, increased resistance to the
prime
mover or any other possible issues that could be associated with starving the
larger
displacement pump 15. By providing the apparatus with the optional access port
39 and
conduit 21, shown here feeding into the conduit 19, the required makeup fluid
can be
drawn in, as needed, by the larger displacement 1.0 VU pump 15, thereby
setting up a
self-adjusted fluid volume condition between the pumps 15 and 16 and, in so
doing,
eliminating the potential issues indicated above. This also eliminates the
need to draw
permeate in reverse through the semi-permeable membrane as the means of
addressing
this volumetric difference. This also removes the question of suitability that
would arise
when using standard, off-the-shelf semi-permeable membrane cartridges that are
not
designed for reversed permeate flow but, nonetheless, still require downtime
related
flushing and/or purging. As resistance from fluid needing to pass through the
membrane is
no longer a factor, there is the added benefit that rotation is easier,
thereby offering the
opportunity to increase the reverse flow volume and velocity, with the same
amount of
effort resulting in better flushing.
In consideration of its simplicity and of the opportunity to eliminate the
added complexity
otherwise required to build this capability elsewhere into such complete
filtration or
separation systems as the apparatus may be integrated into, this becomes a
highly
desirable, albeit optional feature. Nonetheless, if reversing is not
desirable, whether due to
pump type limitations or otherwise, a one-way clutch, brake or other such
mechanism may
be incorporated into the apparatus as needed to prevent counter-clockwise
rotation.
Referring now to Fig. 3, the core module 1 of an embodiment of the present
invention
similar to that taught in Fig's 1 and 2 is shown wherein the single 1.0 VU
pump 15, is
replaced with a series connected 1.0 VU pump set 15A and 15B and the single
0.9 VU
pump 16 is replaced with a series connected 0.9 VU pump set 16A and 16B.
However, it is
noted that the number of pumps within the sets need not be limited to two as
shown here.
The 15A and 15B pumps are separated by a fluid sealed divider 41 and the 16A
and 16B
pumps are separated by a fluid sealed divider 42 such that while they act
cooperatively
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and in unison, they are still independent. It is noted, however, that in other
embodiments,
depending on operating requirements and design advantages for specific
applications, the
pumps within each of these independent sets may also be connected in parallel.
Inflows and outflows are routed and linked either through conduits within the
main body
6 as shown here within manifolding zones 43 and 44 but may alternatively be
connected in
like fashion through other equivalent means. This is arranged such that the
combined flows
of pumps 15A and 158 move into and out of the conduits 17 and 18 in the same
way as
was taught for the apparatus described in Fig's 1 and 2 and likewise, the
combined flows
of pumps 16A and 16B move into and out of the conduits 19, 20 and 21.
While the combined volumetric displacement of the pump sets 15A/15B and
16A/166
may or may not be the same as that of the single pumps they replaced depending
on
needs, it is understood that there remains a differential between the larger
combined
volumetric displacement of the pump set 15A/156 and the smaller combined
volumetric
displacement of the pump set 16A/166, in the same way as was taught with the
apparatus
previously described in Fig's 1 to 3.
Other than for the use of pump sets rather than single pumps, the operating
principles
and general design of this embodiment is the same as that incorporating single
pumps as
taught in the descriptions of Fig's 1 and 2.
Referring now to Fig. 4, the core module 1 of an embodiment of the present
invention
similar to that taught in Fig. 1 is shown wherein the prime mover function is
provided by
the relatively low pressure inflow of the feed fluid 45, as signified here by
the symbol "P"
into the port 35, rather than by a force rotating the common shaft 9 as shown
in Fig. 1.
In this case the 1.0 VU pump 15, and the 0.9 VU pump 16 are fixedly attached
to a
freely rotating, common shaft 46 shown here without the need for a splined
extension as
seen on the common shaft 9 in Fig. 1 but otherwise mounted in the same
fashion.
Attention is also drawn to the fact that while they would generally be
incorporated into
the apparatus, the conduit 21 and port 39 as seen in Fig's 1 and 2 have not
been
incorporated into this embodiment in order to signify a design choice that
could be taken if
and when an integrated flushing, backwashing and purging means is not
required. By
extension, if it is determined that having this capability is not required in
certain
implementations, then it follows that the apparatus as shown here in Fig. 4
may optionally
Page 23 of 43
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replace the reversible pumps 15 and 16 with non-reversing but otherwise
equivalent
positive displacement pumps 15N and 16N . Otherwise, the apparatus general
design,
function and operating principle are the same as that taught in Fig. 1.
Referring first to Fig.'s 5 to 10 in general terms, a variety of positive
displacement pump
types are shown for the purpose of highlighting that any number of pump types
may be
incorporated into the apparatus of the present invention, whether aspects of
their structure,
such as the housing, are incorporated into the core module, or they are
connected or
attached as fully discrete devices. All of these pump types are well known and
commercially available in both standard and custom configurations. With the
exception of
certain added features of the flexible impeller vane pump described in Fig. 6,
and the
peristaltic pump described in Fig. 10, these pump types are not in themselves
claimed as
new and inventive aspects of the present invention and thus need not all be
fully taught
here. However, a more detailed description will be provided with regard to the
added,
unique features of the otherwise typical flexible impeller pump shown in Fig.
6 and the
otherwise typical peristaltic pump shown in Fig. 10.
Referring more specifically now to Fig. 5, it is noted that while other pump
types may be
used, the design, capabilities and characteristics of the Gerotor type
positive displacement
pump, including its Geroler variant, make it particularly well suited for use
with the
apparatus of the present invention. They provide a constant, even discharge,
have the
ability to handle the higher pressures required for applications such as
seawater reverse
osmosis filtration, are bidirectional, provide for prime mover flexibility,
are simple in design
with few moving parts and offer the opportunity for comparatively easy
servicing. They also
offers flexibility of design, are relatively low in cost and are widely
available in either
standard or custom configurations if outsourced as a discrete components. In
cases
where higher circuit pressure is involved, the use of pump sets in series
configuration is
anticipated as a means of reducing the the amount of leakage (also known as
slip or
slippage) past the fluid seals within the the pumps, particularly for low rpm
apparatus such
as those manually operated.
A gear-toothed inner rotor 47 and a gear-toothed outer rotor 48 are assembled
in a
gear-within-a-gear arrangement mounted into a shared, fluid cavity 49 within a
housing 50
such that the round, outer circumference of the outer rotor 48 forms a close
but sliding fit
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with the inner circumference of the fluid cavity 49. The housing 50
incorporates an
unrestricted intake port 51 and an unrestricted discharge port 52 leading into
and out of the
fluid cavity 49. The inner rotor 47 is fixedly mounted to a rotating shaft 53
and, due to the
meshing of their respective teeth, draws the outer rotor 48 around with it
such that both
rotate in the same direction. A close tolerance exists between the two rotors
teeth, which
are most fully messed at location 54, thereby providing a fluid seal there.
As is standard with gerotor type pumps, the smaller diameter inner rotor 47
has one
less tooth than the larger diameter outer rotor 48 with the centre line of the
inner rotor 47
being located at a fixed eccentricity from the centre line of the outer rotor
48 such that an
increasing large gap is formed within that part of the fluid cavity 49 between
the rotors with
the gap being widest at location 55 opposite location 54, where the rotors
most fully mesh,
the latter being equidistant between the intake port 51 and discharge port 52.
As the rotors turn in unison, their teeth begin to diverge near the intake
port 51, thereby
creating an expanding gap or volume between them. This results in a partial
vacuum being
formed at the intake port 51, thus drawing fluid in from its source and
subsequently
trapping it in the expanding gaps that continuously form between the teeth as
the rotors 47
and 48 rotate. At that location 55 where the gap between the rotors reaches
it's maximum,
volume expansion shifts to volume contraction as the teeth now begin to
converge, this
resulting in the progressive reduction or shrinking of the spacing and
corresponding
volume between the teeth. Because the pump is sealed against fluid leakage,
also know
as slip or slippage, between the rotors respective teeth where they most fully
mesh at
location 54, this then results in the fluid being forced out of the discharge
port 52.
As was seen in Fig's 1 to 4 which, it may be assumed, teach the use of same
acting but
more fully integrated gerotor pumps, it is understood that in this figure, the
shaft 53 upon
which the inner rotor 47 is fixedly attached is rotatably mounted into
suitable, fluid sealed
bearings located in the housing 50 on each side of the cavity 49 and, by the
same
reference, it is also understood that one or more fluid sealed access ports
are typically
located within the housing 50 for the purpose of accessing and servicing the
rotors.
In certain embodiments of the apparatus of the present invention, the housing
50, fluid
cavity 49, intake port 51 and discharge port 52 that are shown here as
separate elements
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may all be comprised of a single cavity formed within a main body, whether
that body be
machined, moulded, 3D printed or otherwise produced.
Referring now to Fig. 6, an example of a flexible impeller type vane pump is
shown
wherein a flexible impeller 56 is fixedly mounted to a shaft 57 understood to
be rotated by
means of an external prime mover. As is standard with this type of pump, the
flexible
impeller 56 rotates within a fluid cavity 58 located within a housing 59 with
fluid entering
the cavity 58 via an intake port 60 and exiting via a discharge port 61. As is
also standard
with this type of pump, the flexible vanes being jointly represented here by
the vane 62 are
all in continuous contact with both the circumferential and the side walls of
the cavity 58
such that a continuous fluid seal is formed by each so that as the impeller 56
rotates, fluid
is driven ahead of each of the vanes 62.
Because these are positive displacement pumps, they create the partial vacuum
needed to draw fluid into the pump through the intake port 60. This is
accomplished by
creating a narrowing of the gap between the impeller's hub 63 and a region of
the
circumferential inner wall of the cavity 58 located between the intake port 60
and discharge
port 61 as the impeller rotates. This is done by adding thickness to that
region, hereafter
being referred to as the cam 64, by a suitable means such as, but not limited
to forming the
otherwise circular cavity 58 so that the cam 64 is more oval or elliptical in
shape.
As a result, the volume within the gaps between the vanes 62 becomes
progressively
larger as the vanes 62 rotate away from the cam 64, thereby creating the
partial vacuum
needed to draw fluid into the cavity 58 through the intake port 60. As the
impeller 56
continues to rotate, the vanes re-encounter the cam 64 where it is now
increasing rather
than diminishing in thickness. This results in a progressive reduction in the
gap between
the impeller hub 63 and the cam 64, thereby producing a corresponding
reduction of
volume between the vanes, which causes fluid to be forced out of the discharge
port 61.
It is noted that with exception of a unique combination of design aspects
described
below, the general features and operating principles of this type of pump are
not aspects of
the inventiveness to be claimed herein. However, with regard to the unique
aspects, it is
seen that the thickness of the vanes tips 65, whatever their shapes may be, is
such that
when passing through the narrowest part of the gap between the impeller hub 63
and the
cam 64 as seen at locations 66 and 67, the vanes tips 65 are in full contact
with the
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surfaces of both the impeller hub 63 at location 66 and the cam at location 67
such that a
snug, sliding fit fluid seal is formed and noted that the durometer and/or
reinforcing of the
vanes tips 65 is such that the ability of this unique combination of design
features
enhances the pressure handling capability of any apparatus of this type
incorporating
flexible vane type pumps.
Referring now to Fig's 7 to 9, a further selection of pump types is shown only
for the
purpose of reinforcing the fact that various other types and designs of
positive
displacement pumps may also be integrated into any number of embodiments of
the
present invention. To that end, it is sufficient to say that the generic
drawings of the
external gear pump shown in Fig. 7, the vane pump shown in Fig. 8 and the
peristaltic
pump shown in Fig. 9, all represent well known pump types that, depending upon
requirements, could be incorporated into those various semi-permeable membrane
based
filtration or separation systems that the apparatus of the present invention
may be
connected to or an integral part of.
Referring now to Fig. 10, a peristaltic pump similar to that of Fig. 9 is seen
wherein two
peristaltic hoses 15D and 16D, these being functionally equivalent to the
pumps 15 and 16
seen in Fig.1, may optionally be mounted into a single, common cavity as long
as their
inside diameters and, therefore, their volumetric displacements differ in like
fashion to
those previously discussed, pressure within the 16D hose does not cause
diameter
expansion to negate the volumetric differential between the two hoses and
proper
occlusion is maintained for both.
Referring now to Fig's 11 to 16, a selection of prime movers is shown only for
the
purpose of reinforcing the fact that various types of prime movers may be used
to drive the
apparatus of the present invention. To that end, it is sufficient to say that
the generic
drawings of the wind turbine shown in Fig. 11, the water wheel shown in Fig.
12, and the
telescopic ratcheting handle shown in Fig. 13 all shown with generic
couplings, (Fig.14
has been removed for filing under a separate application), as well as the
motor shown in
Fig. 15, whether it be electric, hydraulic, pneumatic or otherwise, are all
representative
examples of prime movers that could be used to drive the apparatus of the
present
invention. In the case of Fig. 16, the drawing relates to prime movers that
act directly upon
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the pump's impellers as opposed to acting upon the rotating shafts to which
the impellers
are attached. In this example, an externally sourced flow of low pressure
fluid is delivered
to the apparatus of the present invention by a conduit such as but not limited
to a hose or
pipeline. Particular attention is drawn to the fact that the fluid stream
driving the apparatus
is often the same fluid stream being processed by the various filtration or
separation
systems into which the apparatus of the present invention may be incorporated.
Referring now to Fig. 17, a representative drawing of an optional flywheel 68
with over-
riding clutch 69 assembly is shown for the purpose of highlighting that
various prime
movers, or the apparatus of the present invention itself, could incorporate
this or other
similarly acting means by which the driving force is smoothed, stored in
reserve, or both.
One example of where this would be beneficial is with the wave follower shown
in Fig. 14
wherein the intermittent force of the slowly reciprocating wave follower,
which is assumed
to be one-way acting in this example, is transmitted to a flywheel via an
overriding clutch.
The overriding clutch, or any similarly acting device allows the wave follower
to descend
into the incoming wave troughs without imparting a resistance or braking force
to the one-
way motion of the flywheel, while the flywheel's stored energy continues to
drive the
apparatus during those continuously repeating periods in the wave follower's
reciprocating
cycle when no driving force is being applied to cause rotation. Depending on
the
application, this approach may be more practical and cost effective than other
alternatives
such as installing hydraulic accumulators, with or without pulsation dampening
capability.
Referring now to Fig. 18, a detailed description of how the apparatus of the
present
invention such as that taught in the descriptions of Fig's 1 to 4, 21 and 23
may be
incorporated into a complete, semi-permeable membrane based filtration or
separation
system designed for the conversion of raw seawater to potable freshwater by
reverse
osmosis is described in the text that follows. However, it is understood that
by simply
selecting the correct, semi-permeable membrane cartridge from the wide range
of
standard cartridges now available, this same system is also suitable for other
fluid filtration
or separation processes.
As was seen and previously taught in Fig. 1, a core module 1, an optional
speed
changing pulley assembly 2, a crank handle 3 prime mover and their associated,
freely
rotating, splined shaft 5 are shown here with their numbering carried over.
Also seen with
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their numbering carried over are the intake and output conduits 17, 18, 19, 20
and 21 and
their associated port2 35, 36, 37, 38 and 39, all with the understanding that
for reasons of
continuity and improved clarity, the positioning of some has been adjusted and
the depth of
the core body 1 has been extended ¨ all of these adjustments being made with
the
understanding that there is no change to or effect on the fluid routing,
function or operating
principles of the apparatus as it was initially taught in Fig. 1. Also, the
1.0 VU pump 15 and
0.9 VU pump 16, shown in Fig.1 and subsequently taught in the detailed
description of
Fig. 5 are the same pumps as those incorporated into the system taught here in
Fig. 18
and hence, the same numbering is applied.
For improved clarity, the balance of the system as a whole is first broken
down into
logical sub-assemblies, these being a main systems module 70 that is a depth
extended
version of the core body 1 of Fig's 1 to 4, a lower body module 71, a pre-
filter module 72,
first, second, third and fourth quick-connect hose assemblies 73, 74, 75 and
76 and a
standard, commercially available cross-flow type, semi-permeable membrane
based
reverse osmosis cartridge 77 chosen to best suit the location of use
conditions.
As was the case with those earlier descriptions of the apparatus and of the
pumps
incorporated therein, the portable, seawater to potable freshwater reverse
osmosis
filtration system seen here, whether it be land, platform or marine vessel
based, is best
described and understood by following the flow of fluid through it. With that
in mind, the
fluid being raw seawater in this case, is first drawn into the pre-filter
module 72 through a
replaceable strainer 78 that removes sand and other course materials. It then
passes
through a site suitable, pre-filter cartridge 79 located within a filter
housing 80 where finer
particulate matter is removed as is common practice for these types of
systems. In this
setup the pre-filter module 72 is attached via outlet port 81 to a quick-
connect fitted hose
assembly 73 of suitable length and diameter such that the fluid passes
unrestricted
through it and then, via inlet port 35 into the main systems module 70, the
main
components of which are the apparatus of the present invention and a standard,
commercially available, semi-permeable membrane based reverse osmosis
cartridge 77.
Upon entering the port 35 the fluid continues on through the conduit 17 that
opens
unrestricted into the 1.0 VU pump 15 which, as was taught in the description
of Fig. 1, also
serves as its own feed pump by virtue of it's ability to draw in fluid by
creating a partial
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vacuum when rotated. The fluid is then propelled out of the 1.0 VU pump 15
into the open
ended conduit 18 and exits through port 36, which is designed to form a
suitable fluid seal
with the intake fitting 82 built into the reverse osmosis cartridge 77, the
latter being
removably installed into a cavity 83 within the main systems module 70.
At this point, description of the fluid flow path is temporarily interrupted
in order to
remind the reader that the volumetric displacement (VU) of the downstream 0.9
VU pump
16 is approximately 11 percent less than that of the 1.0 VU pump 15, which the
fluid is now
being propelled forward by. The reader is also reminded that the two pumps 15
and 16 are
of the positive displacement type, meaning that they are effectively sealed
against the
forward or backward flow of fluid past their impellers and finally, that those
impellers are
fixedly attached to a shared, common shaft. In other words, the downstream 0.9
VU pump
16 can not rotate faster than the 1.0 VU pump 15 in order to match their
volumetric output.
As has been well established by commercially available devices of this type,
such as the
Spectra Watermaker as taught in the US 5,628,198 (Clark Permar) patent and the
Schenker Watermaker as taught in US 6,491,813 B2 (Riccardo Verde) patent, this
results
in a rapid and continuing pressure rise within the closed hydraulic circuit
between the
pumps 15 and 16 until either (a) the incoming excess fluid from the 1.0 VU
pump 15 can
find a path of escape (b) the 1.0 VU pump 15 stalls because the back pressure
upon it
overcomes the capability of the prime mover, or (c) there is a rupture or
similar failure
within the circuit. As with the above commercially available devices, the
apparatus of the
present invention relies upon (a) where the incoming excess fluid finds a path
of escape, in
all these cases as a means of accomplishing the intended outcome.
Returning now to the description of the fluid flow path from the point where
it entered
the intake fitting 82 built into the reverse osmosis cartridge 77, it can be
seen with the help
of the larger arrows that the fluid flows freely across and around the surface
84 of the
cylindrically shaped cartridge 77, the latter typically being comprised of
layers of semi-
permeable membranes 85 and then exits through the cartridge's built-in
discharge fitting
86 into the a compatible port 87 located in a fixedly attached but removable
lower body
module 71 from where it continues on through the conduit 88, the fitting 89
where it re-
enters the main systems module 70, flows on through the port 37, the conduit
90 and the
port 19 that opens into the smaller displacement 0.9 VU pump 16, whereupon it
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encounters the fluid sealed impeller (inner rotor 47/Fig. 5) that prevents any
further,
unrestricted flow.
In the same manner as with the Spectra and Schenker devices referred to above,
this
results in a rapid and continuing pressure rise within the circuit between the
pumps 15 and
16 until the excess volume of incoming fluid can find a path of escape.
Recalling that the
reverse osmosis cartridge is located within the closed circuit between the 1.0
VU pump 15
and the 0.9 VU pump 16, this path of escape occurs the moment that the fluid
pressure
within the cartridge 77 reaches the point where osmotic pressure is overcome
and the
process of reverse osmosis commences with a volume of fluid equal to the
approximately
11 percent displacement differential between the 1.0 VU pump 15 and the 0.9 VU
pump
16, now passing through the semi-permeable membranes 85 within the cartridge
77 as
filtered "permeate," as shown here by the series of smaller arrows. The
permeate then
flows into a channel 91 within the core of the cartridge 77 and on out through
the
cartridge's built-in discharge fitting 92 into a compatible, fluid sealed port
93 located in the
fixedly attached but removable lower body module 71, from where it continues
on through
the conduit 94 and out through a port 95 ,thus completing its flow within the
apparatus. A
suitable, fitted hose assembly 75 is then employed to carry the typically non-
pressurized
potable freshwater permeate away for collection in a reservoir or other
suitable means.
It is noted that the pressure point at which reverse osmosis self-initiates is
dependent on
a number of factors including but not limited to salinity level in the case of
desalination,
fluid temperature and semi-permeable membrane type and characteristics.
Nonetheless, it
is brought to the readers attention that the process is self-initiating
meaning that the
apparatus of the present invention.
Recalling that taught in the description of Fig 1, the (0.9VU) balance of the
fluid that
was not forced by high pressure through the semi-permeable membranes 85 is
returned to
the 0.9 VU pump 16, such that it provides an energy recovery means, beyond
which it is
expelled through the output conduit 20 and the port 38 to be returned to its
source,
typically no longer under any significant pressure and in somewhat more
concentrated
form via fitted hose assembly 74 or similar other means. This waste fluid is
commonly
known as concentrate or, in the case of seawater desalination, as brine.
With the path of the fluid now described from the time it first enters the
system as 1.0
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volumetric unit (VU) of raw seawater until it leaves the system in two
streams, one being
0.1VU of potable freshwater and the other being 0.9VU of pre-filtered but
otherwise
unprocessed seawater, attention is now drawn to the remaining features seen in
Fig. 18.
While not necessary for the operation of the apparatus, a set of extendable
feet 96 and 97
are provided for the benefit of stability. These are seen here as a pair but
may be installed
in any suitable number. Also, the port 39 and the conduit 21 are not involved
in the
production phase that takes place during the clockwise rotation of the
apparatus and,
therefore, the reader is referred back to the detailed description of Fig. 2,
which describes
their function as well as to their involvement with the items described in
Fig's 19 and 20. In
that regard, the fitted hose assembly 76 is shown here only for the purpose of
highlighting
that the accessories taught in the descriptions of Fig's 19 and 20 are
intended to be
connected to the apparatus seen here in Fig. 18 via the port 39.
Referring now to Fig. 19, we are reminded that when the pumps 15 and 16 in
Fig. 2 are
rotated counter-clockwise, there is a need to provide the larger displacement
1.0 VU pump
15 with makeup fluid, this being drawn into the apparatus through the conduit
21 via the
port 39 that is otherwise blocked off during normal, clockwise operation. As
was seen in
Fig. 18, the conduit 21 feeds unrestricted into the conduit 88, thereby
allowing the makeup
fluid to be drawn in as needed such that when combined within the conduit 88
with the fluid
discharged by the smaller displacement 0.9 VU pump 16, the volumetric need of
the larger
displacement 1.0 VU pump 15 is met with the flow then continuing on in reverse
beyond
the 1.0 VU pump 15, as was taught in the detailed description of Fig. 2.
An important factor however, is to ensure that the fluid being used is
suitable for the
purpose and so it follows that the ideal fluid is that which has been captured
from the
apparatus as permeate. There is shown here a simple means by which to provide
this. As
previously stated, the filtration system used in this example is employed for
converting raw
seawater to potable freshwater so it is reasonable to assume that the
resulting permeate,
here being potable freshwater 98 is being stored, as in a reservoir 99 from
which it can be
drawn off as needed. This is accomplished by first immersing the open end of
the
unrestricted fitted hose assembly 74 into the permeate 98 stored in the
reservoir 99, while
ensuring that its other end is connected to the port 38 as was seen in Fig.
18. In this way,
the fluid needs of the smaller displacement 0.9 VU pump 16 are provided for.
Next, the
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open end of the fitted hose assembly 76 is also immersed into the permeate 98
stored in
the reservoir 99 while ensuring that its fitted end is connected for
unrestricted flow to the
otherwise blocked port 39, as was also discussed in the description of Fig.
18, thus
providing the makeup fluid needs of the larger displacement 1.0 VU pump 15.
In this way, the apparatus of the present invention provides a simple,
convenient and
dependable means for addressing the flushing, backwashing and purging needs
typically
required for maintaining and extending the life of semi-permeable membranes
and pre-
filters used in this fashion, while removing the potential for such possible
issues as pump
cavitation, pressure lock or the stressing of membranes that could be
associated with
starving the larger pump 15 of adequate fluid or by drawing the necessary
makeup fluid
through the semi-permeable membranes in reverse; these benefits all being
accomplished
without adding any appreciable complexity, costs or equipment requirements.
Referring now to Fig. 20, it is anticipated that some users may want the
option of
adding further capabilities to their systems, whether for convenience, the
ability to monitor
certain operating parameters, inject cleaning and storage agents or to serve
some other
useful purpose. In that regard, providing access to the otherwise closed fluid
circuit within
the apparatus via the normally blocked port 39 and conduit 21 shown in Fig's
1, 2, 3 and
18 offers a simple and convenient way of attaching a range of such means to
the
apparatus. One example, as seen here in Fig. 20, would be a manifold 100 that
incorporates a fitting 101 compatible with the port 39 so that it can be
readily and directly
attached to the apparatus, whether only as needed or permanently. In this
example, the
manifold 100 has three branches, one with a pressure gauge 102 mounted to an
unrestricted port 103, one with a sensor (S) 104 capable of detecting some
other aspect of
the fluid during the normal processing cycle mounted to an unrestricted port
105 and one,
incorporating a one-way check valve 106 and which is compatible with the
fitted hose
assembly 76 used to provide fluid from the permeate reservoir 99, as was seen
in Fig. 19.
However, it is understood that any number of devices, whether gauges, sensors,
injectors
or other beneficial devices could be attached to the apparatus, whether in
this fashion or
individually to the port 39.
Referring generally to Fig's 21 to 25, two embodiments of the apparatus of the
present
invention that incorporate a hybrid type of positive displacement, single
impeller vane
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pump are described. The term hybrid is used in the sense that while the pump
is a positive
displacement type, it does not incorporate the usual expansion type fluid
moving chambers
that provide vacuum generating/suction capability and, therefore, it depends
for its feed
upon an external source of positive head/lower pressure fluid to keep it
primed, as with
centrifugal type pumps.
This allows for certain novel features that provide significant advantages
over prior art
vane pumps when incorporated into the apparatus of the present invention.
Depending on
whether the prior art is a sliding vane pump or flexible vane pump, these
advantages can
include any combination of (a) greater design simplicity and thus, the
opportunity to
produce lower cost, more dependable apparatus (b) two-way pumping capability
(c)
increased pressure handling capability (d) greater ease of servicing.
However, while not shown in the embodiments described in Fig's 21 and 23, it
is well
understood that a suction-type positive displacement feed pump could simply be
added
onto or incorporated into the apparatus and mounted to the shared, common
shaft or
equivalent rotating means such that it rotates in unison with the 1.0 VU pump
15 and the
0.9 VU pump 16, thereby providing the necessary flow of positive head/lower
pressure fluid
to the apparatus existing non-suction pumps.
Besides the use of non-suction, positive displacement pumps of unequal
displacement
in this type of apparatus, these novel aspects may also include: Firstly, the
use of unique,
flared vane tips 119 designed to cause an increase in fluid sealing capability
as fluid
pressure builds against the vanes 118, this due to the fluid pressure acting
upwardly
against the flared vane tips 119 in addition to the normally occurring
perpendicular fluid
pressure acting upon the lower stalk portion of the vanes 118 (See arrows 124
in Fig. 23).
In this way, the greater the pressure acting upon the vanes 118, the more the
flared vane
tips 119 are forced against the surface of the cavity 109/Fig. 21 and 126/Fig.
23, rather
than away from it, as is typically the case with conventional vane pump
designs. Secondly,
the relatively high rigidity of the vanes 118 compared to those typically
found in
conventional flexible vane pumps prevents excessive bending of the vanes 118
that might
otherwise offset or overcome the upward acting force on the flared vane tips
119.
With regard to where the surfaces of the vane tips 119 come into snug, sliding
contact
with the circumferential surface 127 of the pump cavity 126, it is noted that
in all of the
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Fig's 21 to 24, this surface is understood to be some form of tough,
resilient, essentially
smooth faced material suited to the application and further, that the impeller
modules 108
and 125 including their vanes 118 might, depending on needs and design be a
single, fully
homogenous unit formed of such a material.
Otherwise the operating principles, circuits, unrestricted fluid flow
capability and general
structure of these embodiments remain the same as those taught in the
previously
described embodiments that do incorporate vacuum generating/suction capable
pumps. In
similar fashion also, the impeller is rotated by means of any number of
connected prime
movers such as those described previously. For these reasons, a fully detailed
repetition of
those same aspects is not deemed to be necessary here.
In descriptions that follow, depending on such factors as manufacturing
tolerances and
capabilities, materials of construction, rigidity of the impeller modules and
vanes, the
working pressures involved and whether the impeller incorporates fluid sealing
means or is
a seal-less design, the use of the descriptor "snug, sliding fit" and its
variants is understood
to mean either actual physical contact between the impeller and the cavity
walls or a
clearance or gap of such small dimensions between the surfaces of the
impeller(s) and the
cavity(s) that significant leakage/slip/slippage and corresponding loss of
pressure are
prevented to the degree necessary for the intended application. In either
case, the novel
aspects and operating principles of the apparatus of the present invention do
not differ.
Fig. 21, being a side view of the first of the two embodiments and Fig. 22,
being a
partially rotated 3D view of it's impeller are best viewed together and, in
like manner, Fig.
23 being an end view of the second of the two embodiments and Fig. 24 being a
partially
rotated 3D view of it's impeller are best viewed together. It is noted that
the design concept
and operating principle of both impellers is essentially the same with the
primary difference
being that the one shown in Fig's 21 and 22 relates to an implementation where
the two
pumps continue to function separately but are unified into a single impeller
module rotating
within a single cavity whereas the one shown in Fig's 23 and 24 relates to an
implementation where the two pumps are comprised of separate rotors operating
within
separate cavities but still in like manner as those described in previous
embodiments.
Referring to Fig's 21 and 22 together, a core module 107 incorporates a single
impeller
module 108 centrally located within a single, cylindrical cavity 109 located
within a main
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body 110. The core module 107 differs from the core module 1 of previous
embodiments in
that it has only one access port and cover 13, rather than the two seen
previously.
The impeller module 108 incorporates two circumferential fluid seals 111 and
112, one
at each end of the impeller module 108 and a third circumferential fluid seal
113 located
between them, offset rather than centred such that the impeller module 108 is
partitioned
into two separately acting impellers of unequal width, these being a wider
impeller 114 and
a narrower impeller 115. As the circumferential faces of the fluid seals 111,
112 and 113
are in a snug, sliding, full contact type fit with the circumferential wall of
the cavity 109, this
effectively partitions the cavity 109 into two separately acting sub-cavities
that correspond
with the widths of the wider impeller 114 and a narrower impeller 115.
This effectively results in the existence of a larger displacement 1.0 VU pump
15 and a
smaller displacement 0.9 VU pump 16 whose function, interoperability, fluid
circuit
positioning and operating principles in general are the same as those of the
previously
described embodiments. For example, the 0.9 VU displacement pump 15 limits the
higher
fluid flow of the 1.0 VU displacement pump 16 to 0.9 VU and, just as with the
previously
described embodiments, the resultant back pressure induces a pressure rise in
that portion
of the enclosed fluid circuit located between them, that being an external
filtration or
separation system circuit connected between outlet port 36 and return intake
port 37.
How the fluid is either propelled forward or held back, as the case may be,
within this
particular pump design occurs in the same fashion as with previously described
embodiments, meaning it is accomplished by rotation the impellers 114 and 115
or, more
specifically, by a variable number of horizontally aligned vanes 118 that
protrude from a
hub 120 (see Fig. 22) of the impeller module 108. There are four vanes 118 in
this case, all
being numerically represented by the vane 118. The vanes 118 and hub 120 are a
single
moulded component here but it is understood that other same acting
implementations such
as fully rigid hub and vanes are also anticipated, especially where high
pressures are
involved. For clarity, the areas of the vanes 118 and circumferential fluid
seals 111, 112
and 113 that come in snug, sliding contact with the circumferential wall of
the cavity 109
are marked here with hatching.
A shaft means is integrated into the impeller module 108 such that it is self-
centring
when installed into cavity 109 within the main body 110; this as a way of
further reducing
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complexity, while also facilitating removal and installation during servicing.
This self-
centring capability is achieved through the use of a centrally located,
tapered male
extension 121 of the impeller module 108 being rotatably mounted into a
precisely mated,
tapered female cavity 122 centrally located in the rear side wall of the
cavity 116 on the
one side of the core module 107 and, on the other side, with an extension of
the impeller
module 108 in the form of a shaft 123 extending through a fluid sealed shaft
bearing 22
that is centrally located in the front port cover 13. This results in the
impeller module 108
being mounted, enclosed and sealed within the core module 107 such that it is
centred
within the cavity 109. and in snug, sliding contact in all those locations
where fluid sealing
under pressure is required.
The intake and output conduits 17 and 18 enter and exit the cavity 116 between
the
circumferential fluid seals 111 and 113 and the intake and exit conduits 19
and 20 enter
and exit the cavity 117 between the circumferential fluid seals 112 and 113.
By way of
comparison, it is now seen that the fluid flow within this embodiment matches
that of
previously described embodiments such as that in Fig. 1 as further highlighted
by the
directional arrows associated with the same acting conduits 17, 18, 19, 20 and
21 and their
corresponding intake and outlet ports 35, 36, 37, 38 and 39. Also, in similar
fashion as with
previously described embodiments, the impellers 114 and 115 seen here are
rotated via a
splined shaft 123 powered by any number of previously described external prime
movers.
It is now seen that while this non-suction type, positive displacement pump
based
embodiment depends on a flow of positive head/low pressure feed fluid 45 to
keep it
primed, which in most of the previously described embodiments is not required,
it's core
operating principles do not differ from those previously described
embodiments.
Referring now to Fig's 23 and 24 together, attention is focused on the pumps
that are
incorporated into a preferred embodiment of the present invention, noting that
all aspects
of the apparatus taught in the descriptions of Fig's 1 to 4 apply here so do
not need to be
restated. For example, a first positive displacement pump or pump set with a
displacement
of 1.0 volumetric units (VU) and a second positive displacement pump or pump
set with a
displacement of 0.9 volumetric units are likewise employed here and the two
impeller
modules 125 seen here are mounted to a common shaft 9 such that they rotate in
unison,
as was also the case with Fig's 1 to 4.
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In this case, a version of the impeller described in Fig.s 21 and 22 but
without the
circumferential seals 111, 112 and 113 is employed in each of two separate
pumps and
hereafter referred to as the impeller module(s) 125. This difference is best
seen by
comparing Fig's 22 and 24. As with the impeller module 108 described in Fig's
21 and 22,
the two impeller modules 125 are mounted such that each forms a snug, sliding
fit within
its own cavity. However, in the absence of the circumferential seals 111 and
112 there
remains a need to ensure against leakage down and along the ends of the
impeller module
125. While this might be accomplished by ensuring that very exacting
smoothness and
flatness tolerances exist between the end walls of the impeller module 125 and
the end
walls of the cavity 126, the amount of friction would be high and wear related
servicing of
the impeller impractical. This problem is addressed by mounting one or more 0-
rings 127
into suitable grooves in each end of the impeller module 125, thereby
providing a solution
that allows for extending the useable life of the impeller by simply replacing
the 0-rings if
and when wear occurs. While it is noted that other, same acting
resilient/compressible
seals could be used in place of the 0-rings 127, the overall benefit would be
questionable.
The impeller seen in Fig. 24 incorporates three additional albeit
optiona/features that
provide the opportunity to (a) reduce sliding friction (b) reduce leakage (c)
reduce tight
manufacturing tolerance requirements, and (d) increase serviceability. The
first of these
features is the use of 0-rings 128, as discussed above, or other similarly
acting means.
The second involves the use of replaceable, linear fluid seals 129, typically
being resilient
but not limited in that respect, mounted into grooves cut or formed into the
circumferential
faces of the vanes 118 such that they, rather than the faces of the vanes
themselves form
the snug, sliding fit with the circumferential surfaces 127 of the cavity 126
and, if required
and as seen here, extend outward from the sides of the impeller module 108 as
far as the
0-rings 128 to eliminate leakage paths there. The third involves the use of
grooves 130 cut
or formed linearly into the circumferential faces of the vanes 118 such that
they increase
the resistance to fluid leakage past the vanes 118. This feature is described
in greater
detail in the description that follows, however, before proceeding, it is
noted that any or all
of these added, optional features may also be applied to the impeller module
108 seen in
Fig's 21 and 22 as well to other pumps used in the apparatus of the present
invention.
As was taught in the description above, the snug, sliding fit between the
impeller
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module 108 and the cavity 109 minimizes the amount of leakage past the vanes.
As
indicated above, this type of leakage can optionally be further reduced, if
required, by the
use of axial grooves 130, whether occurring singly or in groove sets, cut or
otherwise
formed into the faces of the vanes 118 such that they create a turbulence
induced increase
in the amount of pressure drop between the vanes 118 and the walls of the
cavity 126,
thus resulting in a reduction in leakage/slip/slippage and corresponding
pressure loss.
These single grooves or groove sets 130 are cut or formed such that the size,
shape or
other relevant features of the individual grooves as well as the number of
grooves and the
spacing between the individual grooves within a set may vary, this for the
purpose of still
further increasing their effectiveness. Such grooves or groove sets may (a)
extend out from
the side surfaces of the impeller module 125 as seen in Fig. 24, or (b) may
also be applied
separately to the side surfaces of the impeller module 125, whether in radial,
circular or
some other fashion, or (c) may even be cut or formed into the surface of the
cavity 126 if
deemed to be beneficial.
Referring now to Fig. 25, a fully rigid but otherwise same acting impeller 131
for use in
the embodiment taught in Fig. 23 is seen wherein the impeller 131 is comprised
of a
variable number of vanes, all represented by the vane 132 extending outward
from a
central hub 133 in perpendicular fashion. Outer tips 134 of the vanes 132 may
be either
(a) in very close proximity to but not in physical contact with the pump
cavity's walls such
that the minimal clearance/gap 135 between the vane's tips 134 and the
cavity's
circumferential wall 136 and between the vane's sides 137 and the cavity's
side walls
(hidden) minimizes possible leakage/slip/slippage between a series of fluid
moving
chambers 138 located between the vanes 118 such that adequate fluid pressure
can be
both built and maintained, or (b) incorporate a compressible/resilient fluid
sealing means
that is in snug, sliding, full contact with the cavity's circumferential walls
136 and side walls
(hidden) and extending across the width of the circumferential faces of the
vane tips 134,
down the vane sides 137 and around the outer perimeter 139 of the impeller hub
133 side
walls, again minimizing possible leakage/slip/slippage opportunities.
It is noted at this time that while the embodiments taught in the descriptions
of Fig's 21
to 25 are capable of functioning without the need for discrete sealing parts
as aspects of
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CA 2961914 2017-03-24
their impellers, other embodiments incorporating a variety of other fluid
sealing means with
the same effect are anticipated, whether these other means relate to the
impeller vanes or
to/as circumferential seals and whether or not they are fully integrated or
discrete aspects,
two examples being conventional piston ring style means or other
resilient/compressible
materials of suitable thickness and durometer, whether attached, applied or as
a formed
aspect of the impeller.
Finally, the readers attention is drawn to several aspects of the apparatus of
the present
invention that relate to multiple figures or are general in nature. These
include:
- In cases where higher circuit pressure is involved, the use of pump sets in
series
configuration is anticipated as a preferred means of reducing the the amount
of leakage,
also known as slip or slippage, past the fluid seals within the the pumps,
particularly for low
rpm apparatus such as those that are manually operated.
- In those embodiments where pump sets configured in series are employed, the
pumps
within each set are typically matched in terms of their displacement. However,
in
applications where any significant degree of uneven leakage between the pumps
within the
set is anticipated, the displacement of one or more of the pumps, depending on
how many
are in the set, may need to be adjusted to reduce the potential for such
issues as cavitation
or excessive pressure buildup. Otherwise, in the case of excessive pressure
buildup and if
the leakage volumes were unable to self-regulate enough to bring about
balanced flow
volume between the pump in the set, a pressure relief means could be required.
- In the case of most of the embodiments described herein, the pumps are two-
way
acting, although this is not a core requirement for the basic functionality of
the apparatus of
the present invention.
- The flow of fluid within the various circuits of the apparatus of the
present invention is
described in the embodiments herein as being unrestricted with the exception
of where the
fluid encounters or is acted upon by the impellers of the positive
displacement pumps.
However, it is understood that this is a preferred condition - not a
requirement. In other
words, while being able to function without the use of flow restricting
components such as
valves and/or other flow control means is a novel aspect of the present
invention, its core
design and operating principles remain the same, even if a user would choose
to
incorporate such components.
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CA 2961914 2017-03-24
- While the volumetric displacement of the two pumps was defined as being
0.9 VU and
1.0 VU with an effective differential of 11 percent for the purpose of this
description, it is
understood that the differential will vary depending upon the design,
requirements and
capabilities of the semi-permeable membranes and systems which they are a part
of.
- The design, function, operating principles and operating conditions
associated with the
reverse osmosis process as it relates to cross-flow type semi-permeable
membranes and
cartridges is well established and well documented and so, being that these
are not
themselves aspects the apparatus of the present invention and for the sake of
maintaining
focus, further detail regarding these is not deemed to be necessary within
this description.
- Where two-way embodiments are involved, the smaller displacement 0.9 VU
pump
also serves as a feed pump for the apparatus during counter-clockwise rotation
by virtue of
it's ability to draw in feed fluid by creating a partial vacuum, as was the
case during the
clockwise rotation of the 1.0 VU pump.
- Complete filtration or separation systems, whether or not described
herein, need not
be limited to the commercially available cartridge based setups employed with
the
preferred embodiments described herein. In that regard, it is understood that
other semi-
permeable membrane means serving the same purpose, whether custom designed or
not
and including those intended to render a system disposable, may be employed
instead.
- For reasons of clarity, ease of viewing and because a variety of pump
types and
designs can be employed by the apparatus of the present invention, the sizing
and
placement of the ports and circuits seen in the various figures within this
description are
understood to be representative only. For example, in some cases such as the
gerotor type
pump, the ports may typically be found in the cavity side walls whereas, in
the case of
peristaltic types, the ports functions may be made redundant in some cases by
the hoses.
- Certain embodiments of the apparatus of the present invention may be powered
either
by applying force to a rotating drive shaft to which the pump's impellers are
fixedly
attached or by a flow of pressurized fluid acting directly upon the the
impellers themselves
with little or no modification. In the latter case it is further understood
that this same fluid is
typically also the feed fluid to be processed.
- While not a part of the apparatus of the present invention itself or
essential for it's
operation but because positive displacement pumps are employed, it is noted
that for
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CA 2961914 2017-03-24
reasons of safety, some means of pressure relief be integrated into any
connected system
circuits downstream from any point where the apparatus is generating high
pressure.
- While not essential to the functioning of the apparatus of the present
invention,
pulsation dampening means, whether with or without accumulator capacity, may
either be
incorporated into the apparatus itself or installed upstream, depending upon
fluid in-feed
characteristics and in-reserve flow requirements.
- For greater understanding of how fluid pressure is intensified within the
portion of the
circuit located between the two positive displacement pumps/pump sets of
differing
volumetric displacement, attention is drawn to the fact that during the
apparatus production
related rotation, the smaller of the pumps/pump sets is employed primarily to
provide a
resistance based back pressure, rather than only for propelling the fluid
forward, which it
also does. In that regard, as was stated at the outset of the detailed
description, it is noted
that a key operating principle of the apparatus of the present invention, is
the existence of
a stable, volumetric difference in the amount of fluid displaced by each of
two positive
displacement pumps or pump sets operating within the same closed circuit such
that the
greater flow volume from the upstream pump encounters a back pressure from the
downstream pump, resulting in a rise in pressure in that part of the closed
circuit
incorporating a cross-flow, semipermeable membrane means located between the
two
pumps. This can be implemented in at least three ways: The first, being the
preferred
implementation, employs two pumps or pump sets with different internal
displacement
rotating at the same speed such that their output volumes differ at a set
ratio or ratio range.
The second employs two pumps or pump sets with the same internal displacement
but
rotating at different speeds such that their output volumes differ at a
controlled ratio or
ratio range. The third employs two pumps or pump sets with different internal
displacement
rotating at different speeds such that their output volumes differ but still
at a controlled
ratio or ratio range. Other variations may also be possible but regardless of
which
approach is taken, the operating principle remains essentially the same.
However, for the
benefit of greater clarity and ease of understanding, only the first of these
implementations
forms the basis for the preferred embodiment and its variants presented
herein, with the
understanding that with the addition of varying degrees of complexity and
cost, typically
involving at least the use of external control means and/or more complex prime
mover
Page 42 of 43
CA 2961914 2017-03-24
requirements, those other implementations mentioned above could be employed to
achieve the same outcome employing essentially the same core operating
principles.
Therefore, it is understood that while the description of the embodiments
taught herein
refer specifically to pumps or pump sets of different internal displacement
rotating at the
same speed due to the opportunity for least complexity, this is not meant to
limit the
inventor's claims to only that particular means or arrangement of parts for
providing a
displacement volume differential between two positive displacement pumps or
pump sets.
- VOWLES, Gerald J., sole inventor
The preceding represents a detailed description of an invention by Gerald J.
Vow/es of
Vankleek Hill, ON Canada KOB 1 RO. The purpose of this document is to
establish a priority
date with regard to a yet to be completed patent application for the present
invention. The
balance of the documents and materials required to complete the application
process
including the Claims and Summary will be provided in due course in accordance
with the
instructions and time limits provided by the Canadian Intellectual Property
Office (CIP0).
VOWLES, Gerald J., sole inventor
128 Barton Street
Vankleek Hill, Champlain Township
Ontario
KOB 1R0
Tel. 613-678-3253
Cell. 613-847-5687
Canada
March 24, 2017
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