U.S. patent application number 14/624374 was filed with the patent office on 2015-08-20 for multiplex pump systems and associated methods of use with waterjet systems and other high pressure fluid systems.
The applicant listed for this patent is OMAX Corporation. Invention is credited to Chidambaram Raghavan, Darren Stang, Scott D. Veenhuizen.
Application Number | 20150233361 14/624374 |
Document ID | / |
Family ID | 53797694 |
Filed Date | 2015-08-20 |
United States Patent
Application |
20150233361 |
Kind Code |
A1 |
Raghavan; Chidambaram ; et
al. |
August 20, 2015 |
MULTIPLEX PUMP SYSTEMS AND ASSOCIATED METHODS OF USE WITH WATERJET
SYSTEMS AND OTHER HIGH PRESSURE FLUID SYSTEMS
Abstract
High pressure pump systems for use with waterjet systems and
other systems are described herein. A pump system configured in
accordance with a particular embodiment includes a first
multi-cylinder pump having a first crankshaft and a second
multi-cylinder pump having a second crankshaft. The first and
second crankshafts are operably coupled together (via, e.g., a
common drive system) so that the reciprocation cycles of the
corresponding pistons or plungers are spaced apart from each other
in equal intervals of crankshaft rotation.
Inventors: |
Raghavan; Chidambaram;
(Seattle, WA) ; Stang; Darren; (Covington, WA)
; Veenhuizen; Scott D.; (Covington, WA) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
OMAX Corporation |
Kent |
WA |
US |
|
|
Family ID: |
53797694 |
Appl. No.: |
14/624374 |
Filed: |
February 17, 2015 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
61941238 |
Feb 18, 2014 |
|
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|
Current U.S.
Class: |
417/62 ;
29/888.02 |
Current CPC
Class: |
F04B 1/146 20130101;
F04B 9/02 20130101; B24C 5/02 20130101; F04B 1/16 20130101; F04B
23/06 20130101; F04B 11/005 20130101; F04B 1/02 20130101; F04B
53/006 20130101 |
International
Class: |
F04B 11/00 20060101
F04B011/00; F04B 9/02 20060101 F04B009/02; F04B 19/04 20060101
F04B019/04; F04B 53/14 20060101 F04B053/14; F04B 23/06 20060101
F04B023/06; F04B 53/00 20060101 F04B053/00; F04B 53/16 20060101
F04B053/16; F04B 1/02 20060101 F04B001/02; B24C 5/02 20060101
B24C005/02 |
Claims
1-12. (canceled)
13. A fluid pressurizing system comprising: a first pump, the first
pump having: a first crankcase; a first crankshaft operably
disposed within the crankcase; at least first and second
pressurizing members operably coupled to the first crankshaft; and
at least first and second cylinders mounted to the first crankcase,
wherein the first pressurizing member is operably disposed in the
first cylinder and the second pressurizing member is operably
disposed in the second cylinder; a second pump, the second pump
having: a second crankcase; a second crankshaft operably disposed
within the crankcase; at least third and fourth pressurizing
members operably coupled to the second crankshaft; and at least
third and fourth cylinders mounted to the second crankcase, wherein
the third pressurizing member is operably disposed in the third
cylinder and the fourth pressurizing member is operably disposed in
the fourth cylinder; a drive system, wherein the first and second
crankshafts are operably coupled to the drive system in a fixed
phase relationship, and wherein the first, second, third and fourth
pressurizing members reciprocate in the corresponding first,
second, third and fourth cylinders in cycles spaced apart by equal
phase angles during simultaneous rotation of the first and second
crankshafts; a first manifold in fluid communication with the first
and second cylinders; a second manifold in fluid communication with
the third and fourth cylinders; and a fluid junction operably
coupled in fluid communication with the first manifold via a first
conduit and the second manifold via a second conduit, wherein the
first conduit is substantially equivalent to the second conduit in
length, internal flow area, or both.
14. The fluid pressurizing system of claim 13 wherein the first
conduit has a first length and the second conduit has a second
length that is substantially equivalent to the first length.
15. The fluid pressurizing system of claim 13 wherein the first
conduit has a first length and a first internal flow area, and
wherein the second conduit has a second length that is
substantially equivalent to the first length and a second internal
flow area that is substantially equivalent to the first internal
flow area.
16. The fluid pressurizing system of claim 13, wherein the first
crankshaft includes first and second journals offset from each
other by a phase angle of 180 degrees, and wherein the first and
second pressurizing members are operably coupled to the first and
second journals, respectively; wherein the second crankshaft
includes third and fourth journals offset from each other by a
phase angle of 180 degrees, and wherein the third and fourth
pressurizing members are operably coupled to the third and fourth
journals, respectively; and wherein the first and second
crankshafts are operably coupled to the drive system so that the
reciprocation cycles of the first, second, third and fourth
pressurizing members occur sequentially at 90 degree intervals
during synchronized rotation of the first and second
crankshafts.
17. The fluid pressurizing system of claim 13, wherein the first
pump further includes: a fifth pressurizing member operably coupled
to the first crankshaft; and a fifth cylinder mounted to the first
crankcase, wherein the fifth pressurizing member is operably
disposed in the fifth cylinder; wherein the second pump further
includes: a sixth pressurizing member operably coupled to the
second crankshaft; and a sixth cylinder mounted to the second
crankcase, wherein the sixth pressurizing member is operably
disposed in the sixth cylinder; wherein the first crankshaft
includes first, second and third journals offset from one another
by crankshaft angles of 120 degrees, and wherein the first, second
and fifth pressurizing members are operably coupled to the first,
second and third journals, respectively; wherein the second
crankshaft includes fourth, fifth and sixth journals offset from
one another by crankshaft angles of 120 degrees, and wherein the
fourth, fifth and sixth pressurizing members are operably coupled
to the fourth, fifth and sixth journals, respectively; and wherein
the first and second crankshafts are operably coupled to the drive
system at a fixed phase angle of 60 degrees.
18. The fluid pressurizing system of claim 13 wherein the first and
second pumps provide process fluid to the junction at pressures
greater than 30,000 psi with a fixed crankshaft phase angle of 60
degrees between pressure pulses when driven by the drive
system.
19. The fluid pressurizing system of claim 13 wherein the first and
second pumps provide process fluid at pressures greater than 60,000
psi and less than 150,000 psi with a fixed crankshaft phase angle
of 60 degrees between pressure pulses when driven by the drive
system.
20. The fluid pressurizing system of claim 13 wherein the drive
system includes a motor having first and second output shaft
portions, wherein the first crankshaft is operably coupled to the
first output shaft portion by a first drive member, and wherein the
second crankshaft is operably coupled to the second output shaft
portion by a second drive member.
21. The fluid pressurizing system of claim 13 wherein the
pressurizing members are plungers.
22. The fluid pressurizing system of claim 13 wherein the
pressurizing members are pistons.
23-27. (canceled)
28. A method of assembling a waterjet system, the method
comprising: operably coupling a first crankshaft of a first pump to
a drive system, the first pump having at least a first high
pressure fluid outlet; operably coupling a second crankshaft of a
second pump to the drive system, the second pump having at least a
second high pressure fluid outlet; operably coupling the first high
pressure fluid outlet to a fluid junction via a first conduit, the
first conduit having a first length and a first internal
cross-sectional area; operably coupling the second high pressure
fluid outlet to the fluid junction via a second conduit, the second
conduit having a second length that is at least substantially
equivalent to the first length and a second internal
cross-sectional area that is at least substantially equivalent to
the first internal cross-sectional area; and operably coupling a
third conduit between the fluid junction and a waterjet nozzle
assembly, wherein the third conduit is configured to convey high
pressure fluid from the fluid junction to the nozzle assembly for
directing onto a workpiece by a cutting head.
29. The method of claim 28 wherein operably coupling the first and
second crankshafts to the drive system includes operably coupling
the first and second crankshafts to the drive system in a fixed
phase relationship.
30. The method of claim 28 wherein operably coupling the first and
second crankshafts to the drive system includes operably coupling
the first and second crankshafts to the drive system in a fixed
phase relationship that causes the first and second pumps to
provide the high pressure fluid to the fluid junction with
uniformly spaced pressure pulsations during operation of the drive
system.
31. The method of claim 28 wherein operably coupling the first and
second crankshafts to the drive system includes operably coupling
the first and second crankshafts to the drive system in a fixed
phase relationship that causes the first and second pumps to
provide the high pressure fluid to the fluid junction at a pressure
greater than 30,000 psi and less than 150,000 psi, and with
uniformly spaced pressure pulsations, during operation of the drive
system.
32. The method of claim 28 wherein the first pump is a first
triplex pump and the second pump is a second triplex pump.
33. The method of claim 28 wherein the first pump is a first duplex
pump and the second pump is a second duplex pump, and wherein
operably coupling the first and second crankshafts to the drive
system includes operably coupling the first and second crankshafts
to the drive system at a fixed phase angle of 90 degrees.
34. The method of claim 28 wherein the first pump is a first
triplex pump and the second pump is a second triplex pump, and
wherein operably coupling the first and second crankshafts to the
drive system includes operably coupling the first and second
crankshafts to the drive system at a fixed phase angle of 60
degrees.
35-86. (canceled)
87. A method of producing a fluid pressurizing system, the method
comprising: operably coupling a first crankshaft of a first
multiplex pump to a drive system; and operably coupling a second
crankshaft of a second multiplex pump to the drive system in a
fixed phase relationship to the first crankshaft.
88. The method of claim 87: wherein the first multiplex pump
includes a first plurality of compression members operably coupled
to the first crankshaft; wherein the second multiplex pump includes
a second plurality of compression members operably coupled to the
second crankshaft; and wherein operably coupling the second
crankshaft to the drive system includes positioning the second
crankshaft relative to the first crankshaft so that the first and
second pluralities of compression members reciprocate in evenly
spaced apart cycles during simultaneous rotation of the first and
second crankshafts by the drive system.
89. The method of claim 87, further comprising operating the drive
system to pressurize and discharge process fluid from the first and
second multiplex pumps at pressures greater than 20,000 psi and
less than 150,000 psi.
90-111. (canceled)
Description
CROSS-REFERENCE TO APPLICATION(S) INCORPORATED BY REFERENCE
[0001] This application claims the benefit of U.S. Provisional
Application No. 61/941,238, filed Feb. 18, 2014. U.S. Provisional
Application No. 61/941,238, and U.S. patent application Ser. No.
14/164,062, filed on Jan. 24, 2014, are incorporated herein by
reference in their entireties.
TECHNICAL FIELD
[0002] The present disclosure is directed generally to high and
ultrahigh pressure pump systems and associated methods for use with
fluid-jet systems and other systems.
BACKGROUND
[0003] There are various commercial and industrial uses for high
pressure fluid pump systems operating at pressures greater than
20,000 psi. Such pump systems can be used in, for example,
fluid-jet cutting systems, fluid-jet cleaning systems, etc.
Fluid-jet cutting systems often use reciprocating, positive
displacement pumps (e.g., crankshaft-driven plunger pumps).
Crankshaft-driven plunger pumps, such as triplex plunger pumps
(i.e., pumps having three cylinders and associated plungers)
operating at outlet pressures of 20,000 psi or more produce
pressure pulsations caused by the cyclic output from the pump
cylinders. These pressure pulsations can produce undesirably high
levels of pressure ripple downstream from the pump. The pressure
ripple can be partially mitigated by use of a pump output manifold
that contains a volume of the high pressure fluid before it flows
to downstream applications.
[0004] Conventional low pressure crankshaft-driven, reciprocating
positive displacement pumps operating at outlet pressures of 7,500
psi or less typically use pistons instead of plungers. One reason
for this is that piston pumps generally have much higher volumetric
efficiencies that plunger pumps. Piston pumps, however, can also
create significant pressure pulsation during operation. As a
result, such pumps are typically used with pulsation dampeners to
reduce pressure ripple downstream of the pump. Pulsation dampeners
typically include a vessel having a resilient diaphragm with a gas
(such as nitrogen) on one side of the diaphragm and the media being
pumped (e.g., water) on the opposite side of the diaphragm. In
operation, water discharged from the pump flows into the dampener
vessel, with the diaphragm alternatingly expanding and compressing
the gas as the water pressure increases, and then contracting and
letting the gas expand against the water as the water flows out of
the vessel and the pressure decreases. Pulsation dampeners are
usually attached directly to the output manifold of the pump. In
this way, dampeners can reduce pressure pulsations in the water
downstream from the pump.
[0005] Gas filled pulsation dampeners tend to lose effectiveness as
output pressures increase and the gas begins to go through a phase
change to a liquid or supercritical fluid. As noted above, high
pressure pumps typically rely primarily on the volume of fluid in
the output manifold to reduce pressure ripple. Pressure attenuators
can also be used to mitigate pump pressure ripple. Pressure
attenuators are essentially pressure vessels that accumulate the
high pressure water from the pump cylinders to dampen pressure
fluctuations in the water as it is provided to, for example, a
fluid-jet cutting head or other downstream application. Pressure
attenuators are generally placed as close to the pump as possible,
but even with relatively large attenuators, these systems can still
experience relatively large pressure fluctuations during pump
operation that results in downstream pressure ripple.
[0006] Fluid-jet systems (e.g., waterjet or abrasive jet systems)
are one of the areas of technology that utilize ultrahigh pressure
pumps. Fluid-jet systems can be used in precision cutting, shaping,
carving, reaming, and other material-processing applications. The
liquid most frequently used to form the jet is water, and the
high-velocity jet may be referred to as a "water jet" or
"waterjet." In operation, waterjet systems typically direct a
high-velocity jet of water toward a workpiece to rapidly erode
portions of the workpiece. Abrasive material can be added to the
fluid to increase the rate of erosion. When compared to other
shape-cutting systems (e.g., electric discharge machining (EDM),
laser cutting, plasma cutting, etc.), waterjet systems can have
significant advantages. For example, waterjet systems often produce
relatively fine and clean cuts, typically without heat-affected
zones around the cuts. Waterjet systems also tend to be highly
versatile with respect to the material type of the workpiece. The
range of materials that can be processed using waterjet systems
includes very soft materials (e.g., rubber, foam, leather, and
paper) as well as very hard materials (e.g., stone, ceramic, and
hardened metal). Furthermore, in many cases, waterjet systems are
capable of executing demanding material-processing operations while
generating little or no dust, smoke, and/or other potentially toxic
byproducts.
[0007] In a typical waterjet system, a pump pressurizes water to a
high pressure (e.g., up to 60,000 psi or more), and the water is
routed from the pump to a cutting head that includes an orifice.
Passing the water through the orifice converts the static pressure
of the water into kinetic energy, which causes the water to exit
the cutting head as a jet at high velocity (e.g., up to 2,500 feet
per second or more) and impact a workpiece. In many cases, a jig
supports the workpiece. The jig, the cutting head, or both can be
movable under computer and/or robotic control such that complex
processing instructions can be executed automatically.
[0008] The pressure ripple produced by conventional
crankshaft-driven plunger pumps used in waterjet systems have a
number of disadvantages. For example, the pulsations can cause
vibration and fatigue in the fluid conduits and other components
that make up the high pressure fluid circuit between the pump and
the cutting head. Additionally, the pressure pulses can cause
vibration of the cutting head, which adversely affects the waterjet
cutting quality. As discussed above, methods for mitigating
pressure ripple typically include increasing the volume of the pump
manifold or adding a pressure attenuator to the system. Although
somewhat effective, neither approach is an ideal solution. Pressure
manifolds typically have cross-bores that receive the output flow
from each pump cylinder. The cross-bores within the manifold can
create areas of high stress concentrations that limit component
life due to eventual fatigue failure. In addition, pressure
manifolds can be relatively expensive to manufacture, and the cost
generally increases as the size of the manifold increases. As
noted, some pumps are fitted with pressure attenuators to reduce
pressure ripple and mitigate the disadvantages discussed above. As
with pressure manifolds, however, large pressure attenuators can
also be costly to manufacture due to component size. Although
attenuators do not have cross-bores, they are also subject to
fatigue failure. In addition, increasing the volume of pressurized
water stored in a pressure manifold or attenuator has the downside
of increasing stored energy within the pump system. Moreover,
neither output manifolds nor pressure attenuators provide the full
extent of pulse attenuation desired. Accordingly, it would be
desirable to have waterjet pump systems that produce less pressure
ripple than conventional pump systems to reduce fatigue failures
and enhance cutting quality.
BRIEF DESCRIPTION OF THE DRAWINGS
[0009] Many aspects of the present disclosure can be better
understood with reference to the following drawings. The components
in the drawings are not necessarily to scale. Instead, emphasis is
placed on clearly illustrating the principles of the present
technology. For ease of reference, throughout this disclosure
identical reference numbers may be used to identify identical or at
least generally similar or analogous components or features.
[0010] FIG. 1 is a graph illustrating pump manifold pressure ripple
versus mean output pressure for different multi-cylinder pump
configurations assuming water compressibility and non-ideal check
valves.
[0011] FIGS. 2A-2D are a series of graphs illustrating pump
pressure ripple versus crankshaft angle for the four pump
configurations of FIG. 1 operating at a mean output pressure of
60,000 psi.
[0012] FIGS. 3A-3C are a series of left isometric, right isometric,
and top views, respectively, of a multiplex pump system configured
in accordance with an embodiment of the present technology.
[0013] FIG. 4A is a partially schematic top view of the multiplex
pump system of FIGS. 3A-3C, and FIG. 4B is a schematic end view of
a portion of a drive system of the multiplex pump system of FIG.
4A, configured in accordance with an embodiment of the present
technology.
[0014] FIGS. 5A and 5B are end and side views, respectively, of a
phased multiplex pump crankshaft arrangement configured in
accordance with an embodiment of the present technology.
[0015] FIG. 6 is a partially schematic top view of a multiplex pump
having phased crankshafts configured in accordance with another
embodiment of the present technology.
[0016] FIG. 7 is a partially schematic perspective view of a
waterjet system including a multiplex pump configured in accordance
with an embodiment of the present technology.
DETAILED DESCRIPTION
[0017] The following disclosure describes various embodiments of
pump systems for use with, e.g., water, aqueous solutions, etc.,
that can provide high and ultrahigh pressure fluid with lower
magnitude pressure pulses or ripples than conventional pump
systems. As used herein, the term "ultrahigh pressure" can refer to
pressures of 30,000 psi and higher. In some embodiments of the
present technology, the pump systems described herein include a
first multi-cylinder pump (e.g., a first crankshaft-driven,
positive displacement triplex pump) operably coupled to a second
multi-cylinder pump (e.g., a second crankshaft-driven, positive
displacement triplex pump) in a manner that arranges the respective
crankshafts to provide equal, or at least approximately equal,
spacing between pressure pulses in the combined output flow from
both pumps. For example, as described in greater detail below, in
the case of two triplex pumps, each of which has three compression
members (e.g., plungers or pistons) that reciprocate in cycles
spaced apart by 120 degree phase angles, the two crankshafts (one
from each pump) can be operably coupled to the same drive system so
that the six compression members reciprocate in cycles spaced apart
by 60 degree phase angles. This arrangement produces six evenly
spaced apart pressure ripples occurring during each revolution of
the coupled crankshafts, and results in output pressure ripples of
substantially less magnitude than would otherwise be achieved if
the two pumps were coupled together without regard for the phase
relationship between the two crankshafts. Accordingly, the present
disclosure describes methods and systems for operably coupling two
pumps together to efficiently increase (e.g., double) pump output
while simultaneously reducing the magnitude of downstream pressure
ripple.
[0018] The different pump systems and associated methods described
herein can be used in a wide variety of commercial, industrial,
and/or home applications including, for example, fluid-jet cutting
systems (e.g., waterjet or abrasive-jet systems), fluid-jet
cleaning systems, etc. Although the embodiments are disclosed
herein primarily or entirely with respect to waterjet applications,
other applications in addition to those disclosed herein are within
the scope of the present technology. For example, pump systems and
related methods configured in accordance with at least some
embodiments of the present technology can be useful in various
other high-pressure fluid-conveyance systems. Furthermore, waterjet
systems configured in accordance with embodiments of the present
technology can be used with virtually any liquid media pressurized
to 20,000 psi or more, such as water, aqueous solutions,
hydrocarbons, glycol, and liquid nitrogen, among others. As such,
although the term "waterjet" is used herein for ease of reference,
unless the context clearly indicates otherwise, the term refers to
a jet formed by any suitable fluid and is not limited exclusively
to water or aqueous solutions.
[0019] Certain details are set forth in the following description
and in FIGS. 1-7 to provide a thorough understanding of various
systems and methods embodying this fluid pressurizing innovation.
Other details describing well-known aspects of pressurizing devices
and systems (e.g., positive displacement pump systems,
reciprocating plunger pump systems, intensifier pumps, etc.) and
waterjet systems are not set forth in the following disclosure,
however, to avoid unnecessarily obscuring the description of the
various embodiments. Many of the details, dimensions, angles and
other features shown in the Figures are merely illustrative of
particular embodiments. Accordingly, other embodiments can have
other details, dimensions, angles and features without departing
from the spirit or scope of the present technology. In addition,
further embodiments can be practiced without several of the details
described below. To facilitate the discussion of any particular
element, the most significant digit or digits of any reference
number generally refers to the Figure in which that element is
first introduced. For example, element 100 is first introduced and
discussed with reference to FIG. 1.
[0020] FIG. 1 presents a graph 100 that contains a series of plots
106a-106d illustrating output manifold pressure ripple versus mean
output pressure for a series of multiplex positive displacement
pumps (e.g., reciprocating plunger pumps having more than two
plungers and corresponding cylinders), assuming water
compressibility and non-ideal inlet and outlet check valves (e.g.,
accounting for fluid viscosity and thermal conductivity) associated
with each pump cylinder. Manifold pressure ripple in psi is
measured on a vertical axis 102, and mean output pressure from the
pump manifold (or manifolds) is measured in psi along a horizontal
axis 104. In this embodiment, the first plot 106a illustrates
output pressure ripple for a triplex pump (e.g., a plunger pump
having three plungers and three corresponding cylinders); the
second plot 106b illustrates pressure ripple for a quadruplex pump
(e.g., a plunger pump having four plungers and four corresponding
cylinders); the third plot 106c illustrates pressure ripple for a
quintuplex pump (e.g., a plunger pump having five plungers and five
corresponding cylinders); and the fourth plot 106d illustrates
pressure ripple for a sextuplex pump (e.g., a plunger pump having
six plungers and six corresponding cylinders). As used herein, the
term "manifold pressure ripple" refers to the difference between
the maximum discharge or outlet manifold pressure and the minimum
outlet manifold pressure during a complete operating cycle of the
pump (e.g., during 360 degrees of crankshaft rotation). This
assumes that the high pressure water from each pump cylinder flows
into a common outlet manifold or outlet at which the manifold
pressure is measured. The foregoing plots are based on the pumps
having evenly spaced apart plunger cycles during operation. For
example, the triplex pump has three plunger cycles that occur every
crankshaft rotation, and the cycles are separated by equal phase
angles (or crankshaft angles) of 120 degrees. Similarly, the
quadruplex pump has four plunger cycles that occur every crankshaft
rotation, and the cycles are separated by equal phase angles of 90
degrees; and so on for the quintuplex pump (72 degrees) and the
sextuplex pump (60 degrees).
[0021] The graph 100 illustrates that at pressures of about 7,500
psi or less (e.g., at 4,000 psi), the quadruplex pump (the plot
106b) exhibits slightly higher pressure ripple than the triplex
pump (plot 106a), and both the quintuplex and sextuplex pumps
(plots 106c and 106d, respectively) exhibit substantially lower
pressure ripple. While both the quintuplex and sextuplex pumps
continue this pattern in higher pressure regimes, at pressures
above about 8,000 psi (e.g., about 15,000 psi or more), the
quadruplex pump increasingly produces a pressure ripple of
significantly lower magnitude than that of the comparable triplex
pump.
[0022] Graphs 210a-210d in FIGS. 2A-2D illustrate a series of plots
216a-216d of manifold pressure ripple for the triplex, quadruplex,
quintuplex, and sextuplex pumps, respectively, of FIG. 1 operating
at a mean output pressure of 60,000 psi. As with FIG. 1, the water
is assumed to be compressible and the cylinder inlet and outlet
check valves are assumed to be non-ideal. As shown in FIG. 2A,
manifold outlet pressure is measured along a vertical axis 212 and
crankshaft angle is measured along a horizontal axis 214. The first
plot 216a in FIG. 2A illustrates that the triplex pump produces a
pressure ripple of approximately 2,777 psi when operating at a mean
output pressure of 60,000 psi or about 60,000 psi. In contrast to
the low pressure (e.g., 4,000 psi) performance of the quadruplex
pump as shown by FIG. 1, the second plot 216b in FIG. 2B
illustrates that the quadruplex pump actually produces a pressure
ripple of substantially lower magnitude (i.e., 841 psi) than the
triplex pump at the same mean operating pressure of 60,000 psi. As
shown by the plots 216c and 216d FIGS. 2C and 2D, respectively, the
relative behavior of the quintuplex pump and the sextuplex pump at
60,000 psi is similar to the behavior of these two pumps at 4,000
psi. That is, the sextuplex pump produces slightly lower pressure
ripple than the quintuplex pump. As FIGS. 1-2D illustrate, the
quadruplex, quintuplex, and sextuplex plunger pumps of these
embodiments produce lower magnitude pressure ripple than a
comparable triplex pump at pressures of about 7,500 psi or
more.
[0023] FIGS. 3A-3C are a series of left isometric, right isometric,
and top views, respectively, of a fluid-pressurizing system 340
configured in accordance with an embodiment of the present
technology. In the illustrated embodiment, the fluid-pressurizing
system is a multiplex pump system and, more specifically, a
sextuplex pump system that includes a first positive displacement
triplex pump 343a having three cylinders 342a-c, and a second
positive displacement triplex pump 343b having three cylinders
342d-f. In some embodiments, the first and second triplex pumps
343a, b can the mirror image of each other and identical, or at
least generally similar, in structure and function. For example, in
one embodiment the first and second pumps 343a, b can be at least
generally similar in structure and function to EnduroMAX triplex
plunger pumps (rated at, e.g., 50 HP), available from OMAX
Corporation, 21409 72nd Ave. South, Kent, Wash. 98032. In other
embodiments, sextuplex pump systems configured in accordance with
the present technology can include other types of suitable triplex
pumps having other power ratings.
[0024] As described in greater detail below, each triplex pump
343a, b includes three compression members (e.g., reciprocating
plungers) operably coupled to a corresponding crankshaft via three
connecting rod journals (not shown), and both of the crankshafts
can be simultaneously driven by a single drive system 380. In the
illustrated embodiment, the drive system 380 includes a motor 381
(e.g., a 100 HP, 150 HP, or other capacity electric motor (e.g., an
AC electric motor), an internal combustion engine, or other
suitable motive device) operably coupled to each of the crankshafts
via one or more suitable drive members (e.g., a timing belt, chain,
gear train, etc.; not shown) that can be covered by a corresponding
guard 383a, b (e.g., a belt guard). A motor controller 326 (e.g., a
variable frequency drive) can control electrical power (e.g.,
facility power) provided to the motor 381.
[0025] Referring to FIGS. 3A-3C together, in the illustrated
embodiment the sextuplex pump system 340 further includes a fluid
conditioning unit 320 (e.g., one or more filters), a fluid supply
tank 322, and a low power pump 324 (e.g., a 2 HP pump). In
operation, low pressure process fluid (e.g., water) flows into the
conditioning unit 320 via an inlet conduit 310, and then from the
conditioning unit 320 into the adjacent supply tank 322. The low
power pump 324 distributes water from the supply tank 322 into a
series of inlet conduits 348a-f via a series of corresponding
outlets 328a-f on the supply tank 322 (FIG. 3C). The conduits
348a-f distribute the water to corresponding inlets 358a-f on the
pump cylinders 342a-f, respectively (the conduits 348a-f are shown
in FIG. 3C, but are omitted from FIGS. 3A and 3B for purposes of
illustration). Each inlet 358a-f can include a corresponding check
valve (not shown), e.g., a one-way valve configured to let water
flow into the corresponding cylinder 342a-f but not out. Each of
the cylinders 342a-f can also include a corresponding outlet 368a-f
(FIG. 3A). Each outlet 368a-f can include a corresponding check
valve (not shown), e.g., a one-way valve configured to let water
flow out of the corresponding cylinder 342a-f but not in.
[0026] In operation, the reciprocating plungers suck water into the
cylinders 342a-f through the inlets 358a-f, and then pressurize the
water and discharge it out of the cylinders 342a-f through the
outlets 368a-f. More specifically, in the illustrated embodiment
the cylinders 342a-c of the first triplex pump 343a cyclically
discharge the high pressure water to a first manifold 352a via
corresponding outlet conduits 369a-c, and the cylinders 342d-f of
the second triplex pump 343b cyclically discharge the high pressure
water to a second manifold 352b via corresponding outlet conduits
369d-f. In the illustrated embodiment, the manifolds 352a, b are
pressure vessels that act as reservoirs of the high pressure water
cyclically output from the individual pump cylinders. In this
regard, the manifolds 352a, b can be sized to reduce the pressure
ripple caused by the cyclical output when the high pressure water
is provided to, for example, a fluid-jet cutting head or other
downstream application. One advantage of the present technology,
however, is that it enables the manifolds 352a, b to be
substantially smaller than would otherwise be required in the
absence of this technology. Moreover, in some embodiments it is
contemplated that the pump phasing technology disclosed herein can
enable the manifolds 352a, b to be omitted from the sextuplex pump
system 340 and/or replaced by a much smaller manifold, with the
result that the sextuplex pump system 340 would still provide high
pressure water with sufficiently low magnitude pressure ripple for
satisfactory use with waterjet processing systems and other
downstream applications.
[0027] The first manifold 352a can provide high pressure water to a
first inlet 359a on a fluid junction 356 via a first conduit 355a,
and the second manifold 352b can similarly provide high pressure
water to a second inlet 359b on the fluid junction 356 via a second
conduit 355b. The junction 356 in turn discharges the combined
water output into a conduit 357 from an outlet 361. The high
pressure water can flow through the conduit 357 to a downstream
application (e.g., a waterjet cutting system) via. Additionally, in
the illustrated embodiment the conduit 357 is also coupled in fluid
communication to a safety valve 353 and a relief valve 354. More
specifically, the high pressure fluid from the junction 356 is
provided to both the safety valve 353 and the relief valve 354 as
well as the downstream conduit 357. In operation, the safety valve
353 can be configured to open and release pressure in the system if
the fluid exceeds a maximum safe operating pressure. The relief
valve 354 can be at least generally similar in structure and/or
function to one or more of the relief valves described in U.S.
patent application Ser. No. 13/969,477, titled "CONTROL VALVES FOR
WATERJET SYSTEMS AND RELATED DEVICES, SYSTEMS, AND METHODS," filed
on Aug. 16, 2013, and incorporated herein in its entirety by
reference.
[0028] In some embodiments, the junction 356 is preferably
positioned equidistant between the first manifold 352a and the
second manifold 352b so that the pressure pulses in the water
flowing into the junction 356 from the respective pumps 343a, b
occur at evenly spaced apart intervals. More specifically, in these
embodiments the first and second conduits 355a, b should have the
same configuration (e.g., equivalent internal diameters or
cross-sectional flow areas, equivalent lengths L.sub.1 and L.sub.2,
etc.) so that the pressure ripple characteristics of the two water
flows entering the fluid junction 356 are the same, except for the
phase shift of 60 degrees (in the case of a sextuplex pump) between
the two pressure profiles. Without wishing to be bound by theory,
it is expected that maintaining the uniform phase shift between
these two water flows facilitates the improved downstream pressure
ripple characteristics of the present technology. In some
embodiments, the pump cylinders 342a-f can provide high and/or
ultrahigh pressure water to the junction 356 at a pressure suitable
for, e.g., waterjet processing. The pressure can be, for example,
greater than 20,000 psi (e.g., within a range from 20,000 psi to
150,000 psi), greater than 30,000 psi (e.g., within a range from
30,000 psi to 150,000 psi), greater than 60,000 psi (e.g., within a
range from 60,000 psi to 150,000 psi). In other embodiments, the
pump cylinders 342a-f can provide water at a pressure greater than
another suitable threshold pressure or within another suitable
pressure range.
[0029] FIG. 4A is a partially schematic top view of the sextuplex
pump system 340 of FIG. 3, and FIG. 4B is a schematic end view of a
portion of the drive system 380 of FIG. 3, configured in accordance
with an embodiment of the present technology. In the illustrated
embodiment, the first triplex pump 343a includes a first crankcase
444a that supports the three cylinders 342a-c, and the second
triplex pump 343b includes a second crankcase 444b that supports
the three cylinders 342d-f. The first triplex pump 343a further
includes three plungers 466a-c configured to operably reciprocate
within the cylinders 342a-c, respectively, and the second triplex
pump 343b further includes three plungers 466d-f configured to
operably reciprocate within the cylinders 342d-f, respectively.
More specifically, the first, second, and third plungers 466a-c are
operably coupled (e.g., by connecting rods, etc.) to corresponding
first, second, and third rod journals 448a-c on a first crankshaft
446a rotatably supported in the first crankcase 444a, and the
fourth, fifth, and sixth plungers 466d-f are operably coupled to
corresponding fourth, fifth, and sixth journals 448d-f on a second
crankshaft 446b rotatably supported in the second crankcase 444b.
In the illustrated embodiment, the journals 448a-c on the first
crankshaft 446a are positioned 120 degrees out of phase from each
other, and the journals 448d-f on the second crankshaft 446b are
also positioned 120 degrees out of phase from each other. Although
the triplex pumps 343a, b include plungers, in other embodiments
multiplex pumps configured in accordance with the present
technology can utilize other types of suitable compression members,
such as pistons. Accordingly, the present technology is not limited
to use with plunger pumps, and extends to other types of positive
placement pumps, including at least high pressure piston pumps.
[0030] In the illustrated embodiment, the motor 381 includes a
first output shaft portion 484a and an opposite second output shaft
portion 484b. In some embodiments, the first and second output
shaft portions 484a, b can be opposing end portions of a unitary
output shaft (e.g., the motor 381 can be a dual-shaft motor). As a
result, the two shaft portions 484a, b rotate in unison at the same
RPM. In the illustrated embodiment, the drive system 380 includes
first pulleys 488a, b (e.g., toothed pulleys, sprockets, etc.)
fixedly mounted to the output shaft portions 484a, b, respectively.
Similarly, each of the triplex pumps 343a, b can include a second
pulley 486a, b (e.g., a toothed pulley, sprocket, etc.) fixedly
mounted to an end portion of the crankshaft 446a, b, respectively.
Referring to FIGS. 4A and 4B together, the first output shaft
portion 484a can be operably coupled to the first crankshaft 446a
by means of a first timing belt 482a that operably engages the
first and second pulleys 488a and 486a, respectively, and the
second output shaft portion 484b can be operably coupled to the
second crankshaft 446b by means of a second timing belt 482b that
operably engages the first and second pulleys 488b and 486b,
respectively. In some embodiments, the timing belts 482a, b are
flexible belts having teeth molded onto their inner surfaces which
are configured to match complementary teeth on the pulleys 488a, b
and 486a, b. The belts can be made of, for example, a flexible
polymer over a fabric reinforcement. The toothed engagement between
the timing belts 482a, b and the respective pulleys 488a, b and
486a, b can ensure that the belts 482a, b transfer power to the
crankshafts 446a, b without slippage and maintain the desired
timing or indexing of the first crankshaft 446a relative to the
second crankshaft 446b, as described herein. In other embodiments,
the motor 381 can be operably coupled to the crankshafts 446a, b
with other direct drive devices for maintaining simultaneous
rotation of the crankshafts 446a, b. These devices can include, for
example, drive chains and toothed sprockets, a system of gears, or
other suitable drive members.
[0031] In one aspect of the present technology, the timing belts
482a, b are installed on the corresponding pulleys 486a and 488a so
that the reciprocation cycles of the six plungers 466a-f are evenly
spaced apart to occur 60 degrees out of phase from each other
during the simultaneous rotation of the crankshafts 446a, b. More
specifically, in the illustrated embodiment the first crankshaft
446a is coupled to the first output shaft portion 484a, and the
second crankshaft 446b is coupled to the second output shaft
portion 484b, so that the two crankshafts are operationally offset
from each other by a phase angle of 60 degrees (this arrangement
can also be referred to as "clocking" the first crankshaft by 60
degrees relative to the second crankshaft). This arrangement also
positions the three individual journals 448a-c on the first
crankshaft 446a at 60 degree angles relative to the three journals
448d-f on the second crankshaft 446b. As a result, the individual
reciprocation cycles of the plungers 466a-f will occur at equal (or
at least approximately equal) 60 degree timing intervals during
simultaneous rotation of the coupled crankshafts 446a, b about
their respective longitudinal axes 492a, b.
[0032] As stated above, in operation the motor 381 drives the
crankshafts 446a, b, and the reciprocating plungers 466a-f
sequentially suck process fluid (e.g., water) into the cylinders
342a-f through the inlets 358a-f, respectively, and then
sequentially pressurize the water and discharge it out of the
cylinders 342a-f through the outlets 368a-f. The high pressure
water from the cylinders 342a-c flows into the first manifold 352a
via outlets 368a-c, and the high pressure water from the cylinders
342d-f similarly flows into the second manifold 352b via outlets
368d-f. Because of the evenly spaced plunger reciprocation cycles
discussed above, the sextuplex pump system 340 provides the same
(or generally the same) favorable pump pressure ripple
characteristics or profile as represented by the plots 106d and
216d discussed above with reference to FIGS. 1 and 2D,
respectively. Moreover, phasing the crankshafts 446a, b in the
foregoing manner reduces the pressure ripple or pressure
fluctuations in output water pressure produced by the sextuplex
pump system 340, as compared to, for example, two triplex pumps
that are operably coupled together in random fashion without
respect to crankshaft relationship. Another advantage of the
multiplex pump configuration discussed above, as compared to a
sextuplex pump having six cylinders coupled to a single crankshaft
housed in a single crankcase, is that the technology disclosed
herein enables a sextuplex pump to be assembled from two
commercially available triplex pumps at less expense.
[0033] FIG. 5A is an end view of the arrangement of the crankshafts
446a, b of the sextuplex pump system 340 of FIGS. 3A-4B, and FIG.
5B is a corresponding side view of the crankshaft arrangement, for
the purpose of graphically illustrating the positional relationship
of the connecting rod journals 448a-f provided by the 60 degree
crankshaft phase relationship described in detail above. As
described above, the two crankshafts 446a, b are operably coupled
together in the illustrated relationship via the motor output shaft
portions 484a, b (FIG. 4A). Referring to FIGS. 5A and 5B together,
in this embodiment the crankshaft longitudinal axes 492a, b are
coaxially aligned so that they operationally rotate about a common
longitudinal axis of rotation 582. As shown by the end view of FIG.
5A, in this example the second connecting rod journal 448b is
positioned at an angle of 0/360 degrees, the first connecting rod
journal 448a is positioned at an angle of 120 degrees, and the
third connecting rod journal 448c is positioned at an angle of 240
degrees relative to a center point 584 of the longitudinal axes of
rotation 582. Turning next to the second crankshaft 446b, the sixth
connecting rod journal 448f is located at an angle of 60 degrees,
the fifth connecting rod journal 448e is located at an angle of 180
degrees, and the fourth connecting rod journal 448d is located at
an angle of 300 degrees relative to the center point 584. As the
foregoing discussion illustrates, the 60 degree phase angle between
the two crankshafts 446a, b provides an even 60 degree angular
spacing between the individual connecting rod journals 448a-f and,
as a result, provides an even spacing between corresponding pump
output pressure pulses during pump operation.
[0034] In operation, the individual reciprocation cycles of the six
plungers 466a-f (FIG. 4A) occur at equal 60 degree intervals during
simultaneous rotation of the coupled crankshafts 446a, b. As a
result, each of the individual triplex pumps 343a, b produces a
pulse of water into the high pressure output stream three times for
every revolution of the corresponding crankshaft 446a, b, and when
the two triplex pumps 343a, b are operably coupled together as
described above, the resulting sextuplex pump system 340 produces
six equally (or at least approximately equally) spaced pressure
pulses (also referred to herein as ripples) for every simultaneous
revolution of the crankshafts 446a, b, as illustrated by, for
example, the graph 210d of FIG. 2D. As illustrated by, for example,
the graph 100 of FIG. 1, the sextuplex pump system 340 favorably
produces output (e.g., "manifold") pressure ripple of lower
magnitude than comparable triplex, quadruplex, and quintuplex pumps
at mean output pressures ranging from, e.g., 15,000 psi up to
60,000 psi and higher.
[0035] Although the longitudinal axes 492a, b of the individual
crankshafts 446a, b are coaxially aligned in FIGS. 5A and 5B for
purposes of illustration, axial alignment of the crankshafts is not
required to practice the technology described herein. It is
contemplated, for example, that two triplex pumps can be operably
coupled together with their two crankshafts operably positioned
parallel to each other. The parallel crankshafts of such a system
can be operably coupled together by, for example, one or more
timing belts, chains, or gears driven by a single motor. Moreover,
the particular angular and/or longitudinal positions of the
individual rod journals 448a-c on the first crankshaft 446a, and/or
the individual rod journals 448d-f on the second crankshaft 446b,
are not limited to the particular embodiment illustrated in FIGS.
5A and 5B. In other embodiments, for example, the rod journals
448a-c can be in different angular positions on the first
crankshaft 446a, and/or the rod journals 448d-f can be in different
angular positions on the second crankshaft 446b. As set forth
above, however, one underlying aspect of this embodiment of the
technology disclosed herein is that the six rod journals 448a-f are
arranged on their respective crankshafts 446a, b, and the
crankshafts 446a, b are phased with respect to each other, so that
the corresponding plungers 466a-f (FIG. 4A) reciprocate in evenly
spaced apart cycles that occur every 60 degrees of simultaneous
rotation of the two crankshafts. This plunger timing can be
accomplished with crankshaft arrangements that differ from that
illustrated in FIGS. 5A and 5B, without departing from the present
technology. By way of example, it is contemplated that the first
connecting rod journal 448a can be positioned at an angle of 0/360
degrees, the second connecting rod journal 448b can be positioned
at an angle of 60 degrees, and the third connecting rod journal
448c can be positioned at an angle of 120 degrees. Turning next to
the second crankshaft 446b of this example, the fourth connecting
rod journal 448d can be located at an angle of 180 degrees, the
fifth connecting rod journal 448e can be located at an angle of 240
degrees, and the sixth connecting rod journal 448f can be located
at an angle of 300 degrees. It should be noted, however, that
although the crankshaft arrangement of this particular example may
produce evenly spaced apart plunger cycles of 60 degrees, it may
not be practical due to dynamic imbalance of the crankshafts and/or
other considerations.
[0036] FIG. 6 is a partially schematic top view of a multiplex pump
system 640 configured in accordance with another embodiment of the
present technology. More specifically, in the illustrated
embodiment the multiplex pump system 640 is a quadruplex pump
system composed of a first duplex pump 643a (i.e., a two-cylinder
pump) and a second duplex pump 643b which have their respective
crankshafts 646a, b operably coupled to a shared drive system 680.
In some embodiments, the duplex pumps 643a, b can be substantially
identical, or at least generally similar, in structure and
function. Many features of the quadruplex pump system 640 can be at
least generally similar in structure and function to corresponding
features of the sextuplex pump system 340 described in detail above
with reference to FIGS. 3A-5B. For example, in the illustrated
embodiment the drive system 680 includes a motor 681 (e.g., an
electric motor of 50 HP, 100 HP or other suitable capacity, an
internal combustion engine, etc.) having two output shaft portions
684a, b that rotate in unison at the same RPM. The first output
shaft portion 684a is operably coupled to the first crankshaft 646a
by means of a first drive member 682a (e.g., a continuous timing
belt, chain, gears or a gear train, etc.), and the second output
shaft portion 684b is operably coupled to the second crankshaft
646b by means of a second drive member 682b.
[0037] In the illustrated embodiment, each of the positive
displacement duplex pumps 643a, b includes two plungers 666a, b and
666c, d, respectively, which reciprocate in corresponding cylinders
642a, b and 642c, d, respectively. The first and second cylinders
642a, b are mounted to a first crankcase 644a, and the second and
third cylinders 642c, d are mounted to a second crankcase 644b. The
first and second plungers 666a, b are operably coupled (e.g., by
connecting rods, etc.) to corresponding first and second rod
journals 648a, b, respectively, on the first crankshaft 646a, and
the third and fourth plungers 666c, d are similarly coupled to
corresponding third and fourth journals 648c, d, respectively, on
the second crankshaft 646b. During pump operation, the cylinders
642a-d can receive relatively low pressure water via a series of
inlets 658a-d, respectively, and provide high pressure water to
manifolds 652a, b in the manner described above for the sextuplex
pump system 340 of FIGS. 3A-5B. For example, the pump cylinders
642a-d can provide high and/or ultrahigh pressure water at a
pressure suitable for, e.g., waterjet processing. The pressure can
be, for example, greater than 20,000 psi (e.g., within a range from
20,000 psi to 150,000 psi), greater than 30,000 psi (e.g., within a
range from 30,000 psi to 150,000 psi), greater than 60,000 psi
(e.g., within a range from 60,000 psi to 150,000 psi). In other
embodiments, the pump cylinders 642a-d can provide water at a
pressure greater than another suitable threshold pressure or within
another suitable pressure range.
[0038] In one aspect of this embodiment, the first and second
crankshafts 646a, b are coupled to the drive system 680 in such a
way that the reciprocation cycles of the four plungers 666a-d occur
90 degrees out of phase from one another during simultaneous
rotation of the crankshafts 646a, b. For example, in the
illustrated embodiment the first and second rod journals 648a, b on
the first crankshaft 646a are spaced apart by angles of 180 degrees
relative to each other, and the third and fourth rod journals 648c,
d on the second crankshaft 646b are also spaced apart by angles of
180 degrees relative to each other. Furthermore, the first
crankshaft 646a is operably coupled to the first output shaft
portion 684a so that it is 90 degrees out of phase from the second
crankshaft 646b when the second crankshaft 646b is operably coupled
to the second output shaft portion 684b. This arrangement positions
both the first and second journals 648a, b on the first crankshaft
646a at 90 degree angles relative to the third and fourth journals
648c, d on the second crankshaft 646b. As a result, the individual
reciprocation cycles of the plungers 666a-d will occur at equal (or
at least approximately equal) 90 degree timing intervals during
simultaneous rotation of the coupled crankshafts 646a, b about
their respective longitudinal axes 690a, b. Accordingly, for
purposes of this discussion the quadruplex pump system 640 can
exhibit the pressure ripple characteristics or profile as
represented by the plots 106b and 216b illustrated in FIGS. 1 and
2B, respectively.
[0039] The concepts described herein of coupling two duplex or
triplex pumps together at fixed phase angles between the respective
crankshafts to produce uniformly spaced plunger (or piston) timing
and reduce pressure ripples can be extended to other pumps with
additional cylinders. For example, the two crankshafts of two
respective quadruplex pumps (i.e., pumps with four cylinders) can
be coupled together in the manner described above at a fixed phase
angle of 45 degrees to produce an eight-cylinder pump having
equally spaced plunger/piston timing of 45 degrees. Similarly, the
two crankshafts of two respective quintuplex pumps (i.e., pumps
with five cylinders) can be coupled together at a fixed phase angle
of 36 degrees to produce a ten-cylinder pump having equally spaced
plunger/piston timing of 36 degrees. Accordingly, it is expected
that other multi-cylinder pumps can be coupled together by phasing
the crankshaft angles in the manner described above to produce
evenly spaced pressure pulses, and thereby reduce pressure ripple
at high and ultrahigh pressures.
[0040] One of the advantages of the methods described above for
producing multiplex pumps is that rather than simply connecting two
pumps together in arbitrary crankshaft relationships, the multiplex
pumps described herein can double the power output of the
individual pumps while at the same time reducing the magnitude of
the output pressure ripple in relatively high pressure regimes.
More specifically, by providing equal (or at least approximately
equal) timing between plunger/piston cycles (and the corresponding
pressure pulses), the multiplex pumps described herein can produce
lower pressure ripple than if the crankshafts of the same two pumps
were coupled together without regard to the phase relationship.
[0041] FIG. 7 is a perspective view of a waterjet system 700
configured in accordance with an embodiment of the present
technology. The waterjet system 700 includes a fluid-pressurizing
system 702 (shown schematically) configured to pressurize a process
fluid (e.g., water) to a pressure suitable for waterjet processing.
In some embodiments, the fluid-pressurizing system 702 can include
a multiplex pump system configured in accordance with the present
technology. For example, the fluid pressurizing system 702 can
include a sextuplex or a quadruplex pump system that is at least
generally similar in structure and/or function to the sextuplex or
quadruplex pump systems 340 and 640 described in detail above with
reference to FIGS. 3A-6. The waterjet system 700 can further
include a waterjet assembly 704 operably connected to the
fluid-pressurizing system 702 via a conduit 706 extending between
the fluid pressurizing system 702 and the waterjet assembly 704. In
the illustrated embodiment, the conduit 706 is also connected in
fluid communication to a safety valve 732 and a relief valve 734.
The safety valve 732 and the relief valve 734 can be at least
generally similar in structure and/or function to the safety valve
353 and the relief valve 354, respectively, described above with
reference to FIGS. 3A-3C.
[0042] The waterjet assembly 704 can include a jet outlet 708 and a
control valve 710 upstream from the jet outlet 708. The control
valve 710 can be at least generally similar in structure and/or
function to one or more of the control valves described in U.S.
patent application Ser. No. 13/969,477, titled "CONTROL VALVES FOR
WATERJET SYSTEMS AND RELATED DEVICES, SYSTEMS, AND METHODS," filed
on Aug. 16, 2013, and incorporated herein in its entirety by
reference. For example, the control valve 710 can be configured to
receive fluid from the fluid-pressurizing system 702 via the
conduit 706 at a pressure suitable for waterjet processing (e.g., a
pressure greater than 30,000 psi) and to selectively reduce the
pressure of the fluid as the fluid flows through the control valve
710 toward the jet outlet 708. For example, in some embodiments the
waterjet assembly 704 can include a first actuator 712 configured
to control the position of a pin (not shown) within the control
valve 710 and thereby selectively reduce the pressure of the
fluid.
[0043] The waterjet system 700 can further include a user interface
716 supported by a base 714, and a second actuator 718 configured
to move the waterjet assembly 704 relative to the base 714 and
other stationary components of the waterjet system 700 (e.g., the
fluid-pressurizing system 702). For example, the second actuator
718 can be configured to move the waterjet assembly 704 along a
processing path (e.g., cutting path) in two or three dimensions
and, in at least some cases, to tilt the waterjet assembly 704
relative to the base 714. The conduit 706 can include a joint 719
(e.g., a swivel joint or another suitable joint having two or more
degrees of freedom) configured to facilitate movement of the
waterjet assembly 704 relative to the base 714. Thus, the waterjet
assembly 704 can be configured to direct a jet, including the fluid
toward a workpiece (not shown) supported by the base 714 (e.g.,
held in a jig supported by the base 714) and to move relative to
the base 714 while directing the jet toward the workpiece.
[0044] The waterjet system 700 can further include an
abrasive-delivery apparatus 720 configured to feed particulate
abrasive material from an abrasive material source 721 to the
waterjet assembly 704 (e.g., partially or entirely in response to a
Venturi effect associated with a fluid jet passing through the
waterjet assembly 704). Within the waterjet assembly 704, the
particulate abrasive material can accelerate with the jet before
being directed toward the workpiece through the jet outlet 708. In
some embodiments the abrasive-delivery apparatus 720 is configured
to move with the waterjet assembly 704 relative to the base 714. In
other embodiments, the abrasive-delivery apparatus 720 can be
configured to be stationary while the waterjet assembly 704 moves
relative to the base 714. The base 714 can include a diffusing tray
722 configured to hold a pool of fluid positioned relative to the
jig so as to diffuse kinetic energy of the jet from the waterjet
assembly 704 after the jet passes through the workpiece.
[0045] The system 700 can also include a controller 724 (shown
schematically) operably connected to the user interface 716, the
first actuator 712, the second actuator 718, and the relief valve
734. In some embodiments, the controller 724 is also operably
connected to an abrasive-metering valve 726 (shown schematically)
of the abrasive-delivery apparatus 720. In other embodiments, the
abrasive-delivery apparatus 720 can be without the
abrasive-metering valve 726 or the abrasive-metering valve 726 can
be configured for use without being operably associated with the
controller 724. The controller 724 can include a processor 728 and
memory 730 and can be programmed with instructions (e.g.,
non-transitory instructions contained on a computer-readable
medium) that, when executed, control operation of the system 700.
For example, the controller 724 can control operation of the
control valve 710 (via the first actuator 712) in concert with
operation of the relief valve 734 to decrease the pressure of fluid
downstream from the control valve 710 while the pressure of fluid
upstream from the control valve remains relatively constant.
[0046] This disclosure is not intended to be exhaustive or to limit
the present technology to the precise forms disclosed herein.
Although specific embodiments are disclosed herein for illustrative
purposes, various equivalent modifications are possible without
deviating from the present technology, as those of ordinary skill
in the relevant art will recognize. Accordingly, this disclosure
and associated technology can encompass other embodiments not
expressly shown or described herein. In some cases, well-known
structures and functions have not been shown or described in detail
to avoid unnecessarily obscuring the description of embodiments of
the present technology. Although steps of methods may be presented
herein in a particular order, in alternative embodiments, the steps
may have another suitable order. Similarly, certain aspects of the
present technology disclosed in the context of particular
embodiments can be combined or eliminated in other embodiments.
Furthermore, while advantages associated with certain embodiments
may have been disclosed in the context of those embodiments, other
embodiments can also exhibit such advantages, and not all
embodiments need necessarily exhibit such advantages or other
advantages disclosed herein to fall within the scope of the present
technology.
[0047] It should be noted that other embodiments in addition to
those disclosed herein are within the scope of the present
technology. For example, embodiments of the present technology can
have different configurations, components, and/or procedures than
those shown or described herein. Moreover, a person of ordinary
skill in the art will understand that embodiments of the present
technology can have configurations, components, and/or procedures
in addition to those shown or described herein and that these and
other embodiments can be without several of the configurations,
components, and/or procedures shown or described herein without
deviating from the present technology.
[0048] Certain aspects of the present technology may take the form
of computer-executable instructions, including routines executed by
a controller or other data processor. In some embodiments, a
controller or other data processor is specifically programmed,
configured, or constructed to perform one or more of these
computer-executable instructions. Furthermore, some aspects of the
present technology may take the form of data (e.g., non-transitory
data) stored or distributed on computer-readable media, including
magnetic or optically readable or removable computer discs, as well
as media distributed electronically over networks. Accordingly,
data structures and transmissions of data particular to aspects of
the present technology are encompassed within the scope of the
present technology. The present technology also encompasses methods
of both programming computer-readable media to perform particular
steps and executing the steps. The methods disclosed herein include
and encompass, in addition to methods of making and using the
disclosed apparatuses and systems, methods of instructing others to
make and use the disclosed apparatuses and systems.
[0049] Throughout this disclosure, the singular terms "a," "an,"
and "the" include plural referents unless the context clearly
indicates otherwise. Similarly, unless the word "or" is expressly
limited to mean only a single item exclusive from the other items
in reference to a list of two or more items, then the use of "or"
in such a list is to be interpreted as including (a) any single
item in the list, (b) all of the items in the list, or (c) any
combination of the items in the list. Additionally, the terms
"comprising" and the like are used throughout this disclosure to
mean including at least the recited feature(s) such that any
greater number of the same feature(s) and/or one or more additional
types of features are not precluded. Directional terms, such as
"upper," "lower," "front," "back," "vertical," and "horizontal,"
may be used herein to express and clarify the relationship between
various elements. It should be understood that such terms do not
denote absolute orientation. Reference herein to "one embodiment,"
"an embodiment," or similar formulations means that a particular
feature, structure, operation, or characteristic described in
connection with the embodiment can be included in at least one
embodiment of the present technology. Thus, the appearances of such
phrases or formulations herein are not necessarily all referring to
the same embodiment. Furthermore, various particular features,
structures, operations, or characteristics may be combined in any
suitable manner in one or more embodiments.
[0050] References throughout the foregoing description to features,
advantages, or similar language do not imply that all of the
features and advantages that may be realized with the present
technology should be or are in any single embodiment of the
invention. Rather, language referring to the features and
advantages is understood to mean that a specific feature,
advantage, or characteristic described in connection with an
embodiment is included in at least one embodiment of the present
technology. Thus, discussion of the features and advantages, and
similar language, throughout this specification may, but does not
necessarily, refer to the same embodiment.
[0051] From the foregoing, it will be appreciated that specific
embodiments of the invention have been described herein for
purposes of illustration, but that various modifications may be
made without deviating from the spirit and scope of the various
embodiments of the invention. Accordingly, the invention is not
limited, except as by the appended claims. Although certain aspects
of the invention may be presented below in certain claim forms, the
applicant contemplates the various aspects of the invention in any
number of claim forms. Accordingly, the applicant reserves the
right to pursue additional claims after filing this application to
pursue such additional claim forms.
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