Note: Descriptions are shown in the official language in which they were submitted.
89149618
VALVE FOR RECIPROCATING PUMP ASSEMBLY
Cross-Reference to Related Applications
This application claims the benefit of the filing date of, and priority to,
U.S. Application No.
62/188,245, filed July 2, 2015.
This application also claims the benefit of the filing date of, and priority
to, U.S. Application
No. 62/300,343, filed February 26, 2016.
This application claims priority to U.S. Application No. 29/556,055, filed
February 26, 2016.
Technical Field
This disclosure relates in general to pump assemblies and, in particular,
valves for
reciprocating pump assemblies.
Background of the Disclosure
Reciprocating pump assemblies typically include fluid end blocks and inlet and
outlet valves
disposed therein. During operation, the inlet and outlet valves typically
experience high loads and
frequencies. In some cases, valve seats of the inlet and outlet valves, as
well as the corresponding valve
members adapted to be engaged therewith, may be subjected to highly
concentrated cyclic loads and
thus may suffer wear and damage, and fatigue to failure. Therefore, what is
needed is an apparatus or
method that addresses one or more of the foregoing issues, and/or other
issue(s).
Summary
In a first aspect, there is provided a valve member for an inlet or outlet
valve of a reciprocating
pump assembly. The valve member includes a valve body defining first and
second frusto-conical
surfaces; an outside annular cavity formed in the valve body; and a seal
extending within the outside
annular cavity, the seal defining a tapered and circumferentially-extending
surface adapted to sealingly
engage a tapered surface of a valve seat of the inlet or outlet valve; wherein
the second frusto-conical
surface defined by the valve body extends angularly between: the first frusto-
conical surface defined
by the valve body; and the tapered and circumferentially-extending surface of
the seal.
In an exemplary embodiment, the seal further includes an annular bulbous
protrusion from
which the tapered and circumferentially-extending surface angularly extends,
the extension ending at,
or proximate, the second frusto-conical surface defined by the valve body.
1
Date Recue/Date Received 2022-05-13
89149618
In another exemplary embodiment, the valve body defines a top surface; wherein
the
seal further includes a channel formed in the exterior thereof; and wherein
the channel is
positioned between the top surface of the valve body and the annular bulbous
protrusion.
la
Date recue / Date received 2021-11-29
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In yet another exemplary embodiment, the outside annular cavity defines first
and second
angularly-extending surfaces; and wherein the valve member further includes:
an annular groove formed
in the valve body at the intersection of the first and second angularly-
extending surfaces; and an annular
element disposed in the annular groove and engaging the seal.
3 In certain exemplary embodiments, the valve member includes a base
from which the valve body
extends, wherein the first frusto-conical surface of the valve body extends
angularly between the base and
the second frusto-conical surface of the valve body; and a plurality of
circumferentially-spaced legs
extending from the base and away from the valve body, wherein the legs are
adapted to slidably engage
another surface of the valve seat.
In an exemplary embodiment, the base is a disk-shaped base that defines a
circumferentially-
extending convex surface.
In another exemplary embodiment, the valve member defines a first axis adapted
to be coaxial
with a second axis of the valve scat; wherein the first frusto-conical surface
of the valve body defines a
first angle from the first axis; and wherein the second frusto-conical surface
of the valve body defines a
3 second angle from the second axis.
In yet another exemplary embodiment, the first angle is greater than the
second angle.
In certain exemplary embodiments, the second angle is adapted to be
substantially equal to a taper
angle defined by the tapered surface of the valve scat and measured from the
second axis of the valve
seat; and wherein the second angle is about 50 degrees.
In an exemplary embodiment, the valve body defines a first surface area
adapted to contact the
tapered surface of the valve seat; wherein the seal defines a second surface
area adapted to contact the
tapered surface of the valve seat: and wherein a ratio of the first surface
area to the second surface ranges
from about 0.9 to about 1.2.
In another exemplary embodiment, the ratio is about 1.
In another exemplary embodiment, an offset distance is defined between the
second frusto-
conical surface defined by the valve body, and at least a portion of the
tapered and circumferentially-
extending surface defined by the seal.
In yet another exemplary- embodiment, the offset distance extends in a
direction that is
perpendicular to at least the second fnisto-conical surface.
In certain exemplary embodiments, the offset distance ranges from greater than
zero inches to
about 0.1 inch.
In an exemplary embodiment, the second frusto-conical surface defined by the
valve body and at
least a portion of the tapered and circumferentially-extending surface defined
by the seal are spaced in a
parallel relation; wherein an offset distance is defined between the parallel
spacing between the second
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frusto-conical surface defined by the valve body, and the at least a portion
of the tapered and
circumferentially-extending surface defined by the seal.
In another exemplary embodiment, the offset distance extends in a direction
that is perpendicular
to at least the second frusto-conical surface.
3 In yet another exemplary embodiment, the offset distance ranges from
greater than zero inches to
about 0.1 inch.
In certain exemplary embodiments, the valve member defines a first axis
adapted to be coaxial
with a second axis of the valve seat; wherein a first angle, as measured from
the first axis, is defined by
the second frusto-conical surface defined by the valve body; wherein a second
angle, as measured from
the first axis, is defined by at least a portion of the tapered and
circumferentially-extending surface
defined by the seal; wherein the first and second angles are substantially
equal; and wherein each of the
first and second angles is adapted to be substantially equal to a taper angle
defined by the tapered surface
of the valve scat and measured from the second axis of the valve scat.
In an exemplary embodiment, the seal further defines another tapered and
circumferentially-
extending surface, which angularly extends from the first-mentioned tapered
and circumferentially-
extending surface defined by the seal.
In another exemplary embodiment, the extension of the another tapered and
circumferentially-
extending surface of the seal ends at, or proximate, the second frusto-conical
surface defined by the valve
body.
In yet another exemplary embodiment, an annular contact portion of the seal is
defined by the
intersection between the first-mentioned and the another tapered and
circumferentially-extending surfaces
of the seal, the annular contact portion including at least a portion of the
first-mentioned tapered and
circumferentially-extending surface of the seal.
In certain exemplary embodiments, the valve member defines a first axis
adapted to be coaxial
3 with a second axis of the valve scat; wherein a first angle, as
measured from the first axis, is defined by
the second frusto-conical surface defined by the valve body; wherein a second
angle, as measured from
the first axis, is defined by the first-mentioned tapered and
circumferentially-extending surface defined by
the seal; wherein a third angle, as measured from the first axis, is defined
by the another tapered and
circumferentially-extending surface defined by the seal; wherein the first and
second angles are
substantially equal; and wherein the third angle is greater than each of the
first and second angles.
In an exemplary embodiment, the valve member includes a rupture disc assembly
engaged with
the valve body.
In another exemplary embodiment, the valve member defines a first axis adapted
to be coaxial
with a second axis of the valve seat; wherein a counterbore is formed in the
valve body and is generally
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coaxial with the first axis, the counterbore including an enlarged-diameter
portion and a reduced-diameter
portion, the reduced-diameter portion defining a fluid passage; wherein the
counterbore defines an
internal shoulder extending radially between the enlarged-diameter and reduced-
diameter portions; and
wherein the rupture disc assembly includes a rupture disc disposed in the
enlarged-diameter portion and
engaging the internal shoulder; and an annular seal sealingly engaging at
least the rupture disc and the
internal shoulder.
In yet another exemplary embodiment, the rupture disc includes an annular
mounting portion
disposed in the enlarged-diameter portion, an end of the annular mounting
portion engaging the internal
shoulder; a domed rupture portion about which the annular mounting portion
circumferentially extends;
) and an annular channel formed in the end of the annular mounting portion
engaging the internal shoulder;
wherein the annular seal extends within the annular channel and sealingly
engages at least the annular
mounting portion and the internal shoulder.
In a second aspect, there is provided a valve member for an inlet or outlet
valve of a reciprocating
pump assembly, the valve member including a valve body; an outside annular
cavity formed in the valve
5 body; and a seal extending within the outside annular cavity, the seal
defining a tapered and
circumferentially-ex-tending surface adapted to sealingly engage a tapered
surface of a valve seat of the
inlet or outlet valve: wherein the seal includes an annular bulbous protrusion
from which the tapered and
circumferentially-extending surface angularly extends.
In an exemplary embodiment, the valve body defines a top surface; wherein the
seal further
) includes a channel formed in the exterior thereof; and wherein the
channel is positioned between the top
surface of the valve body and the annular bulbous protrusion.
In another exemplary embodiment, the outside annular cavity defines first and
second angularly-
extending surfaces; and wherein the valve member further includes: an annular
groove formed in the
valve body at the intersection of the first and second angularly-extending
surfaces: and an annular
5 element disposed in the annular groove and engaging the seal.
In yet another exemplary embodiment, the valve body defines first and second
frusto-conical
surfaces; wherein the second frusto-conical surface defined by the valve body
extends angularly between:
the first frusto-conical surface defined by the valve body; and the tapered
and circumferentially-extending
surface of the seal; and wherein the valve member further includes: a base
from which the valve body
) extends, wherein the first frusto-conical surface of the valve body
extends angularly between the base and
the second frusto-conical surface of the valve body; and a plurality of
circumferentially-spaced legs
extending from the base and away from the valve body, wherein the legs are
adapted to slidably engage
another surface of the valve seat.
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In certain exemplary embodiments, the base is a disk-shaped base that defines
a
circumferentially-extending convex surface.
In an exemplary embodiment, the valve member defines a first axis adapted to
be coaxial with a
second axis of the valve seat; wherein the first frusto-conical surface of the
valve body defines a first
5 angle from the first axis; and wherein the second frusto-conical surface
of the valve body defines a second
angle from the second axis.
In another exemplary embodiment, the first angle is greater than the second
angle.
In yet another exemplary embodiment, the second angle is adapted to be
substantially equal to a
taper angle defined by the tapered surface of the valve scat and measured from
the second axis of the
) valve seat; and wherein the second angle is 50 degrees.
In certain exemplary embodiments, the valve body defines a first surface area
adapted to contact
the tapered surface of the valve seat; wherein the seal defines a second
surface area adapted to contact the
tapered surface of the valve seat; and wherein a ratio of the first surface
area to the second surface ranges
from about 0.9 to about 1.2.
5 In an exemplary embodiment, the ratio is about 1.
In another exemplary embodiment, the valve body defines a fi-usto-conical
surface; wherein the
tapered and circumferentially-extending surface defined by the seal extends
angularly between the
annular bulbous protrusion and the fmsto-conical surface defined by the valve
body; wherein an offset
distance is defined between the frusto-conical surface defined by the valve
body, and at least a portion of
) the tapered and circumferentially-extending surface defined by the seal.
In yet another exemplary embodiment, the offset distance extends in a
direction that is
perpendicular to at least the frusto-conical surface.
In certain exemplary embodiments, the offset distance ranges from greater than
zero inches to
about 0.1 inch.
5 In an exemplary embodiment, the frusto-conical surface defined by the
valve body and at least a
portion of the tapered and circumferentially-extending surface defined by the
seal are spaced in a parallel
relation; wherein an offset distance is defined between the parallel spacing
between the frusto-conical
surface defined by the valve body, and the at least a portion of the tapered
and circumferentially-
extending surface defined by the seal.
In another exemplary embodiment, the offset distance extends in a direction
that is perpendicular
to at least the frusto-conical surface.
In yet another exemplary embodiment, the offset distance ranges from greater
than zero inches to
about 0.1 inch.
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In certain exemplary embodiments, the valve member defines a first axis
adapted to be coaxial
with a second axis of the valve seat; wherein a first angle, as measured from
the first axis, is defined by
the frusto-conical surface defined by the valve body; wherein a second angle,
as measured from the first
axis, is defined by at least a portion of the tapered and circumferentially-
extending surface defined by the
seal; wherein the first and second angles are substantially equal; and wherein
each of the first and second
angles is adapted to be substantially equal to a taper angle defined by the
tapered surface of the valve seat
and measured from the second axis of the valve seat.
In an exemplary embodiment, the seal further defines another tapered and
circumferentially-
extending surface, which angularly extends from the first-mentioned tapered
and circumferentially-
) extending surface defined by the seal.
In another exemplary embodiment, the extension of the another tapered and
circumferentially-
extending surface of the seal ends at, or proximate, the frusto-conical
surface defined by the valve body.
In yet another exemplary embodiment, an annular contact portion of the seal is
defined by the
intersection between the first-mentioned and the another tapered and
circumferentially-extending surfaces
5 of the seal, the annular contact portion including at least a portion of
the first-mentioned tapered and
circumferentially-ex-tending surface of the seal.
In certain exemplary embodiments, the valve member defines a first axis
adapted to be coaxial
with a second axis of the valve seat; wherein a first angle, as measured from
the first axis, is defined by
the frusto-conical surface defined by the valve body; wherein a second angle,
as measured from the first
) axis, is defined by the first-mentioned tapered and circumferentially-
extending surface defined by the
seal; wherein a third angle, as measured from the first axis, is defined by
the another tapered and
circumferentially-extending surface defined by the seal; wherein the first and
second angles are
substantially equal; wherein the third angle is greater than each of the first
and second angles.
In an exemplary embodiment, the valve member includes a rupture disc assembly
engaged with
5 the valve body.
In another exemplary embodiment, the valve member defines a first axis adapted
to be coaxial
with a second axis of the valve seat; wherein a counterbore is formed in the
valve body and is generally
coaxial with the first axis, the counterbore including an enlarged-diameter
portion and a reduced-diameter
portion, the reduced-diameter portion defining a fluid passage; wherein the
counterbore defines an
) internal shoulder extending radially between the enlarged-diameter and
reduced-diameter portions; and
wherein the rupture disc assembly includes: a rupture disc disposed in the
enlarged-diameter portion and
engaging the internal shoulder; and an annular seal sealingly engaging at
least the rupture disc and the
internal shoulder.
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In yet another exemplary embodiment, the rupture disc includes an annular
mounting portion
disposed in the enlarged-diameter portion, an end of the annular mounting
portion engaging the internal
shoulder; a domed rupture portion about which the annular mounting portion
circumferentially extends;
and an annular channel formed in the end of the annular mounting portion
engaging the internal shoulder;
wherein the annular seal extends within the annular channel and sealingly
engages at least the annular
mounting portion and the internal shoulder.
In a third aspect, there is provided an inlet or outlet valve for a
reciprocating pump assembly, the
inlet or outlet valve including a valve seat defining a first axis, the valve
seat including a tapered surface;
and a valve member adapted to be engaged with the valve scat, the valve member
defining a second axis
) that is adapted to be coaxial with the first axis, the valve member
including: a valve body defining a first
surface area adapted to contact the tapered surface of the valve seat; an
outside annular cavity formed in
the valve body; and a seal extending within the outside annular cavity, the
seal defining a second surface
area adapted to contact the tapered surface of the valve seat; wherein the
ratio of the first surface area to
the second surface area ranges from about 0.9 to about 1.2.
5 In an exemplary embodiment, the valve body defines first and second
frusto-conical surfaces;
wherein the seal defines a -tapered and circumferentially-extending surface
adapted to sealingly engage
the tapered surface of the valve seat: and wherein the second frusto-conical
surface defined by the valve
body extends angularly between: the first fmsto-conical surface defined by the
valve body; and the
tapered and circumferentially-extending surface of the seal.
In another exemplary embodiment, the seal further includes an annular bulbous
protrusion from
which the tapered and circumferentially-extending surface angularly extends,
the extension ending at, or
proximate, the second frusto-conical surface defined by the valve body.
In yet another exemplary embodiment, the valve body defines a top surface;
wherein the seal
further includes a channel formed in the exterior thereof; and wherein the
channel is positioned between
5 the top surface of the valve body and the annular bulbous protrusion.
In certain exemplary embodiments, the valve member further includes: a base
from which the
valve body extends, wherein the first frusto-conical surface of the valve body
extends angularly between
the base and the second fnisto-conical surface of the valve body; and a
plurality of circumferentially-
spaced legs extending from the base and away from the valve body, wherein the
legs slidably engage
) another surface of the valve seat.
In an exemplary embodiment, the first frusto-conical surface of the valve body
defines a first
angle from the first axis; and wherein the second frusto-conical surface of
the valve body defines a second
angle from the second axis.
In another exemplary embodiment, the first angle is greater than the second
angle.
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In yet another exemplary embodiment, the second angle is adapted to be
substantially equal to a
taper angle defined by the tapered surface of the valve seat and measured from
the second axis of the
valve seat; and wherein the second angle is 50 degrees.
In certain exemplary embodiments, the outside annular cavity defines first and
second angularly-
extending surfaces; and wherein the valve member further includes: an annular
groove formed in the
valve body at the intersection of the first and second angularly-extending
surfaces; and an annular
element disposed in the annular groove and engaging the seal.
In an exemplary embodiment, the seal defines a tapered and circumferentially-
extending surface
adapted to scalingly engage the tapered surface of the valve scat; and wherein
the seal includes an annular
) bulbous protrusion from which the tapered and circumferentially-extending
surface angularly extends.
In a fourth aspect, there is provided a valve member for a reciprocating pump
assembly, the valve
member including a valve body including a first frusto-conical surface, the
valve body defining an outside
annular cavity foinied therein; and a seal extending within the outside
annular cavity, the seal including a
first tapered and circumferentially-extending surface adapted to sealingly
engage a tapered surface of a
valve seat of the reciprocating pump assembly; and an annular bulbous
protrusion from which the first
tapered and circumferentially-extending surface angularly extends, the first
tapered and circumferentially-
extending surface extending between the annular bulbous protrusion and the
first frusto-conical surface of
the valve body.
In an exemplary embodiment, the seal further includes a channel formed in the
exterior thereof,
) the channel being positioned between the annular bulbous protrusion of
the seal and a top surface of the
valve body.
In another exemplary embodiment, the valve member defines a first axis adapted
to be coaxial
with a second axis defined by the valve seat; the first frusto-conical surface
of the valve body defines a
first angle, as measured from the first axis; and the tapered surface of the
valve seat defines a taper angle,
5 as measured from the second axis, the taper angle being substantially
equal to the first angle.
In yet another exemplary embodiment, the valve body further includes a second
frusto-conical
surface, the first frusto-conical surface of the valve body extending
angularly between the second frusto-
conical surface of the valve body and the first tapered and circumferentially-
extending surface of the seal;
and the second frusto-conical surface of the valve body defines a second
angle, as measured from the first
) axis, the second angle being greater than the first angle.
In certain exemplary embodiments, the valve body and the seal define first and
second surface
areas, respectively, adapted to contact the tapered surface of the valve seat;
and a ratio of the first surface
area to the second surface area ranges from about 0.9 to about 1.2.
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In an exemplary embodiment, an offset distance is defined between the first
frusto-conical surface
of the valve body and at least a portion of the first tapered and
circumferentially-extending surface of the
seal, the offset distance extending in a direction that is perpendicular to at
least the first frusto-conical
surface of the valve body.
In another exemplary embodiment, the first frusto-conical surface of the valve
body defines a first
angle, as measured from a first axis defined by the valve member, the first
axis being adapted to be
coaxial with a second axis defined by the valve seat; the at least a portion
of the first tapered and
circumferentially-extending surface of the seal defines a second angle, as
measured from the first axis, the
second angle being substantially equal to the first angle; and the first and
second angles are substantially
) equal to a taper angle defined by the tapered surface of the valve seat
and measured from the second axis.
In yet another exemplary embodiment, the seal further includes a second
tapered and
circumferentially-extending surface extending angularly between the first
tapered and circumferentially-
extending surface of the seal and the first frusto-conical surface of the
valve body; and an annular contact
portion defined by an intersection between the first and second tapered and
circumferentially-extending
5 surfaces, the annular contact portion including at least a portion of the
first tapered and circumferentially-
extending surface.
In certain exemplary embodiments, the first frusto-conical surface of the
valve body defines a
first angle, as measured from a first axis defined by the valve member, the
first axis being adapted to be
coaxial with a second axis defined by the valve seat; the first and second
tapered and circumferentially-
extending surfaces of the seal define second and third angles, respectively,
as measured from the first
axis, the second angle being less than the third angle and substantially equal
to the first angle.
In an exemplary embodiment, the valve body further defines a counterbore
formed along a first
axis of the valve body, the first axis being adapted to be coaxial with a
second axis defined by the valve
seat, the counterbore defining an enlarged diameter portion, a reduced-
diameter portion, and an internal
5 shoulder in the valve body, the reduced-diameter portion defining a fluid
passage; and the valve member
further includes a rupture disc disposed in the enlarged-diameter portion of
the counterbore and engaging
the internal shoulder of the valve body.
In a fifth aspect, there is provided a valve member for a reciprocating pump
assembly, the valve
member including a valve body including a first frusto-conical surface, the
valve body defining an outside
) annular cavity formed therein; and a seal extending within the outside
annular cavity, the seal including a
first tapered and circumferentially-extending surface adapted to sealingly
engage a tapered surface of a
valve seat of the reciprocating pump assembly; wherein an offset distance is
defined between the first
frusto-conical surface of the valve body and at least a portion of the first
tapered and circumferentially-
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extending surface of the seal, the offset distance extending in a direction
that is perpendicular to at least
the first frusto-conical surface of the valve body.
In an exemplary embodiment, the first fnisto-conical surface of the valve body
defines a first
angle, as measured from a first axis defined by the valve member, the first
axis being adapted to be
5 coaxial with a second axis defined by the valve seat; the at least a
portion of the first tapered and
circumferentially-extending surface of the seal defines a second angle, as
measured from the first axis, the
second angle being substantially equal to the first angle: and the first and
second angles are substantially
equal to a taper angle defined by the tapered surface of the valve seat and
measured from the second axis.
In another exemplary embodiment, the seal further includes a second tapered
and
) circumferentially-extending surface extending angularly between the
first tapered and circumferentially-
extending surface of the seal and the first frusto-conical surface of the
valve body; and an annular contact
portion defmed by an intersection between the first and second tapered mid
circumferentially-extending
surfaces, the annular contact portion including at least a portion of the
first tapered and circumferentially-
extending surface.
5 In yet another exemplary embodiment, the first frusto-conical surface
of the valve body defmes a
first angle, as measured from a first axis defined by the valve member, the
first axis being adapted to be
coaxial with a second axis defined by the valve seat; the first and second
tapered and circumferentially-
extending surfaces of the seal define second and third angles, respectively,
as measured from the first
axis, the second angle being less than the third angle and substantially equal
to the first angle.
In certain exemplary embodiments, the seal further includes an annular bulbous
protrusion from
which the first tapered and circumferentially-extending surface angularly
extends, the first tapered and
circumferentially-extending surface extending between the annular bulbous
protrusion and the first frusto-
conical surface of the valve body; and a channel formed in the exterior
thereof, the channel being
positioned between the annular bulbous protrusion of the seal and a top
surface of the valve body.
5 In an exemplary embodiment, the valve member defines a first axis
adapted to be coaxial with a
second axis defined by the valve seat; the first frusto-conical surface of the
valve body defines a first
angle, as measured from the first axis; and the tapered surface of the valve
seat defines a taper angle, as
measured from the second axis, the taper angle being substantially equal to
the first angle.
In another exemplary embodiment, the valve body further includes a second
frusto-conical
) surface, the first frusto-conical surface of the valve body extending
angularly between the second frusto-
conical surface of the valve body and the first tapered and circumferentially-
extending surface of the seal;
and the second frusto-conical surface of the valve body defines a second
angle, as measured from the first
axis, the second angle being greater than the first angle.
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In yet another exemplary embodiment, the valve body and the seal define first
and second
surface areas, respectively, adapted to contact the tapered surface of the
valve seat; and a ratio of the
first surface area to the second surface area ranges from about 0.9 to about
1.2.
In certain exemplary embodiments, the valve body further defines a counterbore
formed along
a first axis of the valve body, the first axis being adapted to be coaxial
with a second axis defined by
the valve seat, the counterbore defining an enlarged diameter portion, a
reduced-diameter portion, and
an internal shoulder in the valve body, the reduced-diameter portion defining
a fluid passage.
In an exemplary embodiment, the valve member further includes a rupture disc
disposed in the
enlarged-diameter portion of the counterbore and engaging the internal
shoulder of the valve body; and
an annular seal sealingly engaging at least the rupture disc and the internal
shoulder.
In a further exemplary embodiment, there is provided a valve member for a
reciprocating pump
assembly, the valve member comprising: a valve body comprising a first frusto-
conical surface, the
valve body defining an outside annular cavity formed therein; and a seal
extending within the outside
annular cavity, the seal comprising: a first tapered and circumferentially-
extending surface defining a
first acute angle and being adapted to sealingly engage a tapered surface of a
valve seat of the
reciprocating pump assembly; and a second tapered and circumferentially-
extending surface defining a
second acute angle and extending angularly between the first tapered and
circumferentially-extending
surface of the seal and the first frusto-conical surface of the valve body;
wherein the valve member
defines a first axis from which the first and second acute angles are
measured, the first acute angle being
measured in a first angular direction from the first axis, the second acute
angle being measured in a
second angular direction from the first axis, said second angular direction
being the same as the first
angular direction; and wherein an offset distance is defined between the first
frusto-conical surface of
the valve body and at least a portion of the first tapered and
circumferentially-extending surface of the
seal, the offset distance extending in a direction that is perpendicular to at
least the first frusto-conical
surface of the valve body.
Other aspects, features, and advantages will become apparent from the
following detailed
description when taken in conjunction with the accompanying drawings, which
are a part of this
disclosure and which illustrate, by way of example, principles of the
inventions disclosed.
11
Date Recue/Date Received 2022-05-13
89149618
Description of Figures
The accompanying drawings facilitate an understanding of the various
embodiments.
Figure 1 is an elevational view of a reciprocating pump assembly according to
an exemplary
embodiment, the pump assembly includes a fluid end.
Figure 2 is a section view of the fluid end of Figure 1 according to an
exemplary embodiment,
the fluid end including a fluid end block and inlet and outlet valves, the
inlet and outlet valves each
including a valve seat.
Figure 3 is an enlarged view of a portion of the section view of Figure 2,
according to an
exemplary embodiment.
Figure 4 is a section view of respective portions of the valve seat and the
fluid end block,
according to another exemplary embodiment.
Figure 5 is a section view of respective portions of the valve seat and fluid
end block, according
to yet another exemplary embodiment.
Figure 6 is a section view of a valve according to another exemplary
embodiment, the valve
including a valve seat.
Figure 7 is a perspective view of the valve seat of Figure 6, according to an
exemplary
embodiment.
Figure 8 is a sectional view of the valve seat of Figures 6 and 7, according
to an exemplary
embodiment.
Figure 9 is a sectional view of the valve of Figure 6 disposed within the
fluid end block of
Figure 2, according to an exemplary embodiment.
1 1 a
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Figure 10 is a sectional view of a valve according to an exemplary embodiment,
the valve
including a valve seat and a valve member.
Figure 11 is an enlarged view of a portion of the valve member of Figure 10,
according to another
exemplary embodiment.
Figure 12 is a view of experimental steel contact pressures experienced by a
finite element model
of' the valve of Figure 10, according to an exemplary experimental embodiment.
Figure 13 is a view of experimental stresses experienced by a finite element
model of the valve of
Figure 10, according to an exemplary experimental embodiment.
Figure 14 is a view of experimental urethane contact pressures experienced by
a finite element
model of the valve of Figure 10, according to an exemplary experimental
embodiment.
Figure 15 is a perspective view of a valve member according to an exemplary
embodiment.
Figure 16 is an elevational view of the valve member of Figure 15.
Figure 17 is a sectional view of the valve member of Figures 15 and 16 taken
along line 17-17 of
Figure 16, according to an exemplary- embodiment.
5 Figure 18 is an enlarged view of a portion of Figure 17, according to
an exemplary embodiment.
Figure 19 is a perspective view of a valve member according to an exemplary
embodiment.
Figure 20 is an elevational view of the valve member of Figure 19.
Figure 21 is a sectional view of the valve member of Figures 19 and 20 taken
along line 21-21 of
Figure 20, according to an exemplary embodiment.
Figure 22 is a perspective view of a valve member according to an exemplary
embodiment.
Figure 23 is an elevational view of the valve member of Figure 22.
Figure 24 is a sectional view of the valve member of Figures 22 and 23 taken
along line 24-24 of
Figure 23, according to an exemplary embodiment.
Figure 25 is an enlarged view of a portion of Figure 24, according to an
exemplary embodiment.
5 Figure 26 is a perspective view of a valve member according to an
exemplary embodiment.
Figure 27 is an elevational view of the valve member of Figure 26.
Figure 28 is a sectional view of the valve member of Figures 26 and 27 taken
along line 28-28 of
Figure 27, according to an exemplary embodiment.
Figure 29 is an enlarged sectional view of a valve member, according to an
exemplary
embodiment.
Figure 30 is another enlarged sectional view of a valve member, according to
an exemplary
embodiment.
Detailed Description
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In an exemplary embodiment, as illustrated in Figure 1, a reciprocating pump
assembly is
generally referred to by the reference numeral 10 and includes a power end
portion 12 and a fluid end
portion 14 operably coupled thereto. The power end portion 12 includes a
housing 16 in which a
crankshaft (not shown) is disposed, the crankshaft being operably coupled to
an engine or motor (not
shown), which is adapted to drive the crankshaft. The fluid end portion 14
includes a fluid end block 18,
which is connected to the housing 16 via a plurality of stay rods 20. The
fluid end block 18 includes a
fluid inlet passage 22 and a fluid outlet passage 24, which are spaced in a
parallel relation. A plurality of
cover assemblies 26, one of which is shown in Figure 1, is connected to the
fluid end block 18 opposite
the stay rods 20. A plurality of cover assemblies 28, one of which is shown in
Figure 1, is connected to
) the fluid end block 18 opposite the fluid inlet passage 22. A plunger
rod assembly 30 extends out of the
housing 16 and into the fluid end block 18. In several exemplary embodiments,
the pump assembly 10 is
freestanding on the ground, is mounted to a trailer that can be towed between
operational sites, or is
mounted to a skid.
In an exemplary embodiment, as illustrated in Figure 2 with continuing
reference to Figure 1, the
5 plunger rod assembly 30 includes a plunger 32, which extends through
a bore 34 formed in the fluid end
block 18, and into a pressure chamber 36 formed in the fluid end block 18. In
several exemplary
embodiments, a plurality of parallel-spaced bores may be formed in the fluid
end block 18. with one of
the bores being the bore 34, a plurality of pressure chambers may be formed in
the fluid end block 18,
with one of the pressure chambers being the pressure chamber 36, and a
plurality of parallel-spaced
) plungers may extend through respective ones of the bores and into
respective ones of the pressure
chambers, with one of the plungers being the plunger 32. At least the bore 34,
the pressure chamber 36,
and the plunger 32 together may be characterized as a plunger throw. In
several exemplary embodiments,
the reciprocating pump assembly 10 includes three plunger throws (i.e., a
triplex pump assembly), or
includes four or more plunger throws.
5 As shown in Figure 2, the fluid end block 18 includes inlet and
outlet fluid passages 38 and 40
formed therein, which are generally coaxial along a fluid passage axis 42.
Under conditions to be
described below, fluid is adapted to flow through the inlet and outlet fluid
passages 38 and 40 and along
the fluid passage axis 42. The fluid inlet passage 22 is in fluid
communication with the pressure chamber
36 via the inlet fluid passage 38. The pressure chamber 36 is in fluid
communication with the fluid outlet
) passage 24 via the outlet fluid passage 40. The fluid inlet passage
38 includes an enlarged-diameter
portion 38a and a reduced-diameter portion Mb extending downward therefrom.
The enlarged-diameter
portion 38a defines a tapered internal shoulder 43 and thus a frusto-conical
surface 44 of the fluid end
block 18. The reduced-diameter portion 38b defines an inside surface 46 of the
fluid end block 18.
Similarly, the fluid outlet passage 40 includes an enlarged-diameter portion
40a and a reduced-diameter
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portion 40b extending downward therefrom. The enlarged-diameter portion 40a
defines a tapered internal
shoulder 48 and thus a fnisto-conical surface 50 of the fluid end block 18.
The reduced-diameter portion
40b defines an inside surface 52 of the fluid end block 18.
An inlet valve 54 is disposed in the fluid passage 38, and engages at least
the frusto-conical
surface 44 and the inside surface 46. Similarly, an outlet valve 56 is
disposed in the fluid passage 40, and
engages at least the frusto-conical surface 50 and the inside surface 52. In
an exemplary embodiment,
each of valves 54 and 56 is a spring-loaded valve that is actuated by a
predetermined differential pressure
thereacross.
A counterbore 58 is formed in the fluid end block 18, and is generally coaxial
with the fluid
) passage axis 42. The counterbore 58 defines an internal shoulder 58a and
includes an internal threaded
connection 58b adjacent the internal shoulder 58a. A counterbore 60 is formed
in the fluid end block 18,
and is generally coaxial with the bore 34 along an axis 62. The counterbore 60
defines an internal
shoulder 60a and includes an internal threaded connection 60b adjacent the
internal shoulder 60a. In
several exemplary embodiments, the fluid end block 18 may include a plurality
of parallel-spaced
5 counterbores, one of which may be the counterbore 58, with the quantity
of counterbores equaling the
quantity of plunger throws included in the pump assembly 10. Similarly, in
several exemplary
embodiments, the fluid end block 18 may include another plurality of parallel-
spaced counterbores, one of
which may be the counterbore 60, with the quantity of counterbores equaling
the quantity of plunger
throws included in the pump assembly 10.
A plug 64 is disposed in the counterbore 58, engaging the internal shoulder
58a and sealingly
engaging an inside cylindrical surface defined by the reduced-diameter portion
of the counterbore 58. An
external threaded connection 66a of a fastener 66 is threadably engaged with
the internal threaded
connection 58b of the counterbore 58 so that an end portion of the fastener 66
engages the plug 64. As a
result, the fastener 66 sets or holds the plug 64 in place against the
internal shoulder 58a defined by the
5 counterbore 58, thereby maintaining the sealing engagement of the plug 64
against the inside cylindrical
surface defined by the reduced-diameter portion of the counterbore 58. The
cover assembly 28 shown in
Figures 1 and 2 includes at least the plug 64 and the fastener 66. In an
exemplary embodiment, the cover
assembly 28 may be disconnected from the fluid end block 18 to provide access
to, for example, the
counterbore 58, the pressure chamber 36, the plunger 32, the fluid passage 40
or the outlet valve 56. The
) cover assembly 28 may then be reconnected to the fluid end block 18 in
accordance with the foregoing.
In several exemplary embodiments, the pump assembly 10 may include a plurality
of plugs, one of which
is the plug 64, and a plurality of fasteners, one of which is the fastener 66.
with the respective quantities
of plugs and fasteners equaling the quantity of plunger throws included in the
pump assembly 10.
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A plug 68 is disposed in the counterbore 60, engaging the internal shoulder
60a and sealingly
engaging an inside cylindrical surface defined by the reduced-diameter portion
of the counterbore 60. In
an exemplary embodiment, the plug 68 may be characterized as a suction cover.
An external threaded
connection 70a of a fastener 70 is threadably engaged with the internal
threaded connection 60b of the
5 counterbore 60 so that an end portion of the fastener 70 engages the plug
68. As a result, the fastener 70
sets or holds the plug 68 in place against the internal shoulder 60a defined
by the counterbore 60, thereby
maintaining the sealing engagement of the plug 68 against the inside
cylindrical surface defined by the
reduced-diameter portion of the counterbore 60. The cover assembly 26 shown in
Figures 1 and 2
includes at least the plug 68 and the fastener 70. In an exemplary embodiment,
the cover assembly 26
) may be disconnected from the fluid end block 18 to provide access to, for
example, the counterbore 60,
the pressure chamber 36, the plunger 32, the fluid passage 38, or the inlet
valve 54. The cover assembly
26 may then be reconnected to the fluid end block in accordance with the
foregoing. In several
exemplary embodiments, the pump assembly 10 may include a plurality of plugs,
one of which is the plug
68, and a plurality of fasteners, one of which is the fastener 70, with the
respective quantities of plugs and
5 fasteners equaling the quantity of plunger throws included in the pump
assembly 10.
A valve spring retainer 72 is disposed in the enlarged-diameter portion 38a of
the fluid passage
38. The valve spring retainer 72 is connected to the end portion of the plug
68 opposite the fastener 70.
In an exemplary embodiment, and as shown in Figure 2, the valve spring
retainer 72 is connected to the
plug 68 via a hub 74, which is generally coaxial with the axis 62.
In an exemplary embodiment, as illustrated in Figure 3 with continuing
reference to Figures 1 and
2. the inlet valve 54 includes a valve seat 76 and a valve member 78 engaged
therewith. The valve seat
76 includes a seat body 80 having an enlarged-diameter portion 82 at one end
thereof The enlarged-
diameter portion 82 of the seat body 80 is disposed in the enlarged-diameter
portion 38a of the fluid
passage 38. A bore 83 is formed through the seat body 80. The valve seat 76
has a valve seat axis 84,
5 which is aligned with the fluid passage axis 42 when the inlet valve 54
is disposed in the fluid passage 38,
as shown in Figure 3. Under conditions to be described below, fluid flows
through the bore 83 and along
the valve seat axis 84. The bore 83 defines an inside surface 85 of the seat
body 80. An outside surface
86 of the seat body 80 contacts the inside surface 46 defined by the fluid
passage 38. A sealing element,
such as an 0-ring 88, is disposed in an annular groove 90 formed in the
outside surface 86. The 0-ring
) 88 sealingly engages the inside surface 46. The enlarged-diameter portion
82 includes a tapered external
shoulder 91 and thus defines a frusto-conical surface 92, which extends
angularly upward from the
outside surface 86. The portion 82 further defines a cylindrical surface 94,
which extends axially upward
from the extent of the frusto-conical surface 92. The fmsto-conical surface 92
is axially disposed
between the outside surface 86 and the cylindrical surface 94. The portion 82
further defines a tapered
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surface 96, which extends angularly upward from the inside surface 85, as
viewed in Figure 3. In an
exemplary embodiment, the tapered surface 96 extends at an angle from the
valve seat axis 84. The seat
body 80 of the valve seat 76 is disposed within the reduced-diameter portion
38b of the fluid passage 38
so that the outside surface 86 of the scat body 80 engages the inside surface
46 of the fluid end block 18.
In an exemplary embodiment, the seat body 80 forms an interference fit, or is
press fit, in the portion 38b
of the fluid passage 38 so that the valve seat 76 is prevented from being
dislodged from the fluid passage
38.
The valve member 78 includes a central stem 98, from which a valve body 100
extends radially
outward. An outside annular cavity 102 is formed in the valve body 100. A seal
104 extends within the
) cavity 102, and is adapted to sealingly engage the tapered surface 96 of
the valve seat 76, under
conditions to be described below. A plurality of circumferentially-spaced legs
106 extend angularly
downward from the central stem 98 (as viewed in Figure 3), and slidably engage
the inside surface 85 of
the seat body 80. In several exemplary embodiments, the plurality of legs 106
may include two, three,
four, five, or greater than five, legs 106. A lower end portion of a spring
108 is engaged with the top of
5 the valve body 100 opposite the central stem 98. The valve member 78 is
movable, relative to the valve
seat 76 and thus the fluid end block 18, between a closed position (shown in
Figure 3) and an open
position (not shown), under conditions to be described below.
In an exemplary embodiment, the seal 104 is molded in place in the valve body
100. In an
exemplary embodiment, the seal 104 is preformed and then attached to the valve
body 100. In several
) exemplary embodiments, the seal 104 is composed of one or more materials
such as, for example, a
deformable thermoplastic material, a urethane material, a fiber-reinforced
material, carbon, glass, cotton,
wire fibers, cloth, and/or any combination thereof. In an exemplary
embodiment, the seal 104 is
composed of a cloth which is disposed in a thermoplastic material, and the
cloth may include carbon,
glass, wire, cotton fibers, and/or any combination thereof. In several
exemplary embodiments, the seal
5 104 is composed of at least a fiber-reinforced material, which prevents,
or at least reduces, delamination.
In an exemplary embodiment, the seal 104 has a hardness of 95A durometer or
greater, or a hardness of
69D durometer or greater. In several exemplary embodiments, the valve body 100
is much harder and/or
more rigid than the seal 104.
The outlet valve 56 is identical to the inlet valve 54 and therefore will not
be described in further
) detail. Features of the outlet valve 56 that are identical to
corresponding features of the inlet valve 54 will
be given the same reference numerals as that of the inlet valve 54. The valve
seat axis 84 of the outlet
valve 56 is aligned with each of the fluid passage axis 42 and the valve seat
axis 84 of the inlet valve 54.
The outlet valve 56 is disposed in the fluid passage 40, and engages the fluid
end block 18, in a manner
that is identical to the manner in which the inlet valve 54 is disposed in the
fluid passage 38, and engages
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the fluid end block 18, with one exception. This one exception involves the
spring 108 of the outlet valve
56 more particularly, the upper portion of the spring 108 of the outlet valve
56 is compressed against the
bottom of the plug 64, rather than being compressed against a component that
corresponds to the valve
spring retainer 72, against which the upper portion of the spring 108 of the
inlet valve 54 is compressed.
In operation, in an exemplary embodiment, with continuing reference to Figures
1-3, the plunger
32 reciprocates within the bore 34, reciprocating in and out of the pressure
chamber 36. That is, the
plunger 32 moves back and forth horizontally, as viewed in Figure 2, away from
and towards the fluid
passage axis 42, In an exemplary embodiment, the engine or motor (not shown)
drives the crankshaft
(not shown) enclosed within the housing 16, thereby causing the plunger 32 to
reciprocate within the bore
) 34 and thus in and out of the pressure chamber 36.
As the plunger 32 reciprocates out of the pressure chamber 36, the inlet valve
54 is opened. More
particularly, as the plunger 32 moves away from the fluid passage axis 42, the
pressure inside the pressure
chamber 36 decreases, creating a differential pressure across the inlet valve
54 and causing the valve
member 78 to move upward, as viewed in Figures 2 and 3, relative to the valve
scat 76 and the fluid end
5 block 18. As a result of the upward movement of the valve member 78, the
spring 108 is compressed
between the valve body 100 and the valve spring retainer 72, the seal 104
disengages from the tapered
surface 96, and the inlet valve 54 is thus placed in its open position. Fluid
in the fluid inlet passage 22
flows along the fluid passage axis 42 and through the fluid passage 38 and the
inlet valve 54, being drawn
into the pressure chamber 36. To flow through the inlet valve 54, the fluid
flows through the bore 83 of
) the valve seat 76 and along the valve seat axis 84. During the fluid flow
through the inlet valve 54 and
into the pressure chamber 36, the outlet valve 56 is in its closed position,
with the seal 104 of the valve
member 78 of the outlet valve 56 engaging the tapered surface 96 of the valve
seat 76 of the outlet valve
56. Fluid continues to be drawn into the pressure chamber 36 until the plunger
32 is at the end of its
stroke away from the fluid passage axis 42. At this point, the differential
pressure across the inlet valve
5 54 is such that the spring 108 of the inlet valve 54 is not further
compressed, or begins to decompress and
extend, forcing the valve member 78 of the inlet valve 54 to move downward, as
viewed in Figures 2 and
3, relative to the valve seat 76 and the fluid end block 18. As a result, the
inlet valve 54 is placed in, or
begins to be placed in, its closed position, with the seal 104 sealingly
engaging, or at least moving
towards, the tapered surface 96.
As the plunger 32 moves into the pressure chamber 36 and thus towards the
fluid passage axis 42,
the pressure within the pressure chamber 36 begins to increase. The pressure
within the pressure chamber
36 continues to increase until the differential pressure across the outlet
valve 56 exceeds a predetermined
set point, at which point the outlet valve 56 opens and permits fluid to flow
out of the pressure chamber
36, along the fluid passage axis 42 and through the fluid passage 40 and the
outlet valve 56, and into the
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fluid outlet passage 24. As the plunger 32 reaches the end of its stroke
towards the fluid passage axis 42
(i.e., its discharge stroke), the inlet valve 54 is in, or is placed in, its
closed position, with the seal 104
sealingly engaging the tapered surface 96.
The foregoing is repeated, with the reciprocating pump assembly 10
pressurizing the fluid as the
fluid flows from the fluid inlet passage 22 to the fluid outlet passage 24 via
the pressure chamber 36. In
an exemplary embodiment, the pump assembly 10 is a single-acting reciprocating
pump, with fluid being
pumped across only one side of the plunger 32.
In an exemplary embodiment, during the above-described operation of the
reciprocating pump
assembly 10, the taper of each of the surfaces 44 and 92 balances the loading
forces applied thereagainst.
) In an exemplary embodiment, the loading is distributed across the surface
44 and 92, reducing stress
concentrations. In an exemplary embodiment, the stresses in the valve seat 76,
in the vicinity of the fillet
interface between the surfaces 86 and the 92, are balanced with the stresses
in the fluid end block 18, in
the vicinity of the round interface between the surfaces 46 and 44. As a
result, these stresses are reduced.
In an exemplary embodiment, the taper of each of the surfaces 44 and 92
permits the outside diameter of
5 the seat body 80 of the inlet valve 54 to be reduced, thereby also
permitting a relatively smaller service
port, as well as relatively smaller cross-bore diameters within the fluid end
block 18. In an exemplary
embodiment, the taper of each of the surfaces 44 and 92 reduces the extraction
force necessary to remove
the valve seat 76 from the fluid passage 38.
In an exemplary embodiment, as illustrated in Figure 4 with continuing
reference to Figures 1-3,
) a taper angle 110 is defined by the tapered external shoulder 91 and thus
the frusto-conical surface 92. A
taper angle 112 is defined by the tapered internal shoulder 43 and thus the
fiusto-conical surface 44. Each
of the taper angles 110 and 112 may be measured from the fluid passage axis 42
and the valve seat axis
84 aligned therewith. In an exemplary embodiment, the taper angles 110 and 112
are equal, and range
from about 10 degrees to about 45 degrees measured from the fluid passage axis
42 and the valve seat
5 axis 84 aligned therewith. In an exemplary embodiment, the taper angles
110 and 112 range from about
20 degrees to 40 degrees measured from the fluid passage axis 42 and the valve
seat axis 84 aligned
therewith. In an exemplary embodiment, the taper angles 110 and 112 range from
about 25 to 35 degrees
measured from the fluid passage axis 42 and the valve seat axis 84 aligned
therewith. In an exemplary
embodiment, the taper angles 110 and 112 are equal, and each of the taper
angles 110 and 112 is about 30
) degrees measured from the fluid passage axis 42 and the valve seat axis
84 aligned therewith. In an
exemplary embodiment, the taper angles 110 and 112 are not equal. As shown in
Figure 4, a flusto-
conical gap or region 114 may be defined between the surfaces 44 and 92.
Moreover, a radial clearance
116 is defined between the outside cylindrical surface 94 of the valve seat 76
and an inside surface 118 of
the fluid end block 18, the surface 118 being defined by the enlarged-diameter
portion 38a of the fluid
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passage 38. In an exemplary embodiment, the region 114 may be omitted and the
surface 92 may abut
the surface 44. In an exemplary embodiment, material may be disposed in the
region 114 to absorb,
transfer and/or distribute loads between the surfaces 44 and 92.
As shown in Figure 4, at least the end portion of the body 80 opposite the
enlarged-diameter
portion 82 is tapered at a taper angle 120 from the fluid passage axis 42 and
the valve seat axis 84 aligned
therewith. In an exemplary embodiment, the taper angle 120 ranges from about 0
degrees to about 5
degrees measured from the fluid passage axis 42 and the valve seat axis 84
aligned therewith. In an
exemplary embodiment, the taper angle 120 ranges from about 1 degree to about
4 degrees measured
from the fluid passage axis 42 and the valve scat axis 84 aligned therewith.
In an exemplary embodiment,
the taper angle 120 ranges from about 1 degree to about 3 degrees measured
from the fluid passage axis
42 and the valve seat axis 84 aligned therewith. In an exemplary embodiment,
the taper angle 120 is
about 2 degrees measured from the fluid passage axis 42 and the valve seat
axis 84 aligned therewith. In
an exemplary embodiment, the taper angle 120 is about 1.8 degrees measured
from the fluid passage axis
42 and the valve scat axis 84 aligned therewith. In an exemplary embodiment,
instead of, or in addition to
5 the end portion of the body 80 opposite the enlarged-diameter portion 82
being tapered; the inside surface
46 of the fluid end block 18 is tapered at the taper angle 120. In an
exemplary embodiment, an
interference fit may be formed between the body 80 and the inside surface 46,
thereby holding the valve
seat 76 in place in the fluid end block. In several exemplary embodiments,
instead of using an
interference fit in the fluid passage 38, a threaded connection, a threaded
nut, and/or a snap-fit mechanism
may be used to hold the valve seat 76 in place in the fluid end block 18.
In an exemplary embodiment, during the operation of the pump assembly 10 using
the
embodiment of the inlet valve 54 illustrated in Figure 4, the surfaces 92 and
44 provide load balancing,
with loading on the enlarged-diameter portion 82 of the valve seat 76 being
distributed and transferred to
the surface 44 of the fluid end block 18, via either the pressing of the
surface 92 against the surface 44 or
5 intermediate material(s) disposed therebetween.
In an exemplary embodiment, as illustrated in Figure 5 with continuing
reference to Figures 1-4,
a fillet surface 122 of the fluid end block 18 is defined by the enlarged-
diameter portion 38a of the fluid
passage 38. The fillet surface 122 extends between the frusto-conical surface
44 and the inside surface
118. As shown in Figure 5, each of the frusto-conical surfaces 92 and 44 is
tapered at a taper angle 123,
which may be measured from the fluid passage axis 42 and the valve seat axis
84 aligned therewith. In an
exemplary embodiment, the taper angle 123 ranges from about 10 degrees to
about 45 degrees measured
from the fluid passage axis 42 and the valve seat axis 84 aligned therewith.
In an exemplary embodiment,
the taper angle 123 ranges from about greater than 10 degrees to about 30
degrees measured from the
fluid passage axis 42 and the valve seat axis 84 aligned therewith. In an
exemplary embodiment, the taper
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angle 123 ranges from about 12 degrees to about 20 degrees measured from the
fluid passage axis 42 and
the valve seat axis 84 aligned therewith. In an exemplary embodiment, the
taper angle 123 is about 14
degrees measured from the fluid passage axis 42 and the valve seat axis 84
aligned therewith. In an
exemplary embodiment, the surface 92 and 44 may be tapered at respective
angles that are not equal. The
5 surface 92 abuts the surface 44. As shown in Figure 5, the groove 90 and
the 0-ring 88 are omitted in
favor of an annular groove 124 and an 0-ring 126, respectively. The annular
groove 124 is formed in the
frusto-conical surface 92, and the 0-ring 126 is disposed in the annular
groove 124. The 0-ring 126
sealingly engages the frusto-conical surface 44.
In an exemplary embodiment, during the operation of the pump assembly 10 using
the
) embodiment of the inlet valve 54 illustrated in Figure 5, loads applied
to the valve seat 76 are distributed
and transferred to the fluid end block 18 via, at least in part, the load
balancing provided by the abutment
of the surface 92 against the surface 44.
In an exemplary embodiment, during the operation of the pump assembly 10 using
any of the
foregoing embodiments of the inlet valve 54, downwardly directed axial loads
along the fluid passage
5 axis 42 are applied against the top of the valve body 100. This loading
is usually greatest as the plunger
32 MOWS towards the fluid passage axis 42 and the outlet valve 56 opens and
permits fluid to flow out of
the pressure chamber 36, through the fluid passage 40 and the outlet valve 56,
and into the fluid outlet
passage 24. As the plunger 32 reaches the end of its stroke towards the fluid
passage axis 42 (its
discharge stroke), the inlet valve 54 is in, or is placed in, its closed
position, and the loading applied to the
) top of the valve body 100 is transferred to the seal 104 via the valve
body 100. The loading is then
transferred to the valve seat 76 via the seal 104, and then is distributed and
transferred to the tapered
internal shoulder 43 of the fluid end block 18 via either the engagement of
the surface 92 against the
surface 44 or intermediate material(s) disposed therebetiveen. The tapering of
the surfaces 92 and 44
facilitates this distribution and transfer of the downwardly directed axial
loading to the fluid end block 18
5 in a balanced manner, thereby reducing stress concentrations in the fluid
end block 18 and the valve seat
76.
In an exemplary embodiment, as illustrated in Figures 6-8 with continuing
reference to Figures 1-
5, an inlet valve is generally referred to by the reference numeral 128 and
includes several parts that are
identical to corresponding parts of the inlet valve 54, which identical parts
are given the same reference
) numerals. The inlet valve 128 includes a valve seat 129. The valve seat
129 includes several features that
are identical to corresponding features of the valve seat 76, which identical
features are given the same
reference numerals. An annular notch 130 is formed in the valve seat 128 at
the intersection of the
surfaces 86 and 92.
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As shown in Figure 8, a taper angle 132 is defined by the external tapered
shoulder 91 and thus
the fnisto-conical surface 92. The taper angle 132 may be measured from the
valve seat axis 84. In an
exemplary embodiment, the taper angle 132 is about 30 degrees measured from
the valve seat axis 84. In
an exemplary embodiment, the taper angle 132 ranges from about 10 degrees to
about 45 degrees
measured from the valve seat axis 84. In an exemplary embodiment, the taper
angle 132 ranges from
about 20 degrees to about 40 degrees measured from the valve seat axis 84. In
an exemplary
embodiment, the taper angle 132 ranges from about 25 to about 35 degrees
measured from the valve seat
axis 84. The cylindrical surface 94 defined by the enlarged-diameter portion
82 of the valve seat 129
defines an outside diameter 134. In an exemplary embodiment, the outside
diameter 134 is about 5
inches. In an exemplary embodiment, the outside diameter 134 is about 5.06
inches. The inside surface
85 of the seat body 80 defined by the bore 83 formed therethrough defines an
inside diameter 136. In an
exemplary embodiment, the inside diameter 136 ranges from about 3 inches to
about 3.5 inches. In an
exemplary embodiment, the inside diameter 136 is about 3.27 inches. An annular
surface 138 of the seat
body 80 is defined by the annular groove 90. A groove diameter 140 is defined
by the annular surface
5 138. In an exemplary embodiment, the groove diameter 140 ranges from
about 4 inches to about 4.5
inches. In an exemplary embodiment, the groove diameter 140 is about 4.292
inches. In an exemplary
embodiment, an outside diameter 142 is defined by the outside surface 86 of
the seat body 80 at an axial
location therealong adjacent the annular notch 130, or at least in the
vicinity of the intersection between
the surfaces 86 and 92. In an exemplary embodiment, the outside diameter 142
ranges from about 4
inches to about 5 inches. In an exemplary embodiment, the outside diameter 142
ranges from about 4.5
inches to about 5 inches. In an exemplary embodiment, the outside diameter 142
ranges from about 4.5
inches to about 4.6 inches. In an exemplary embodiment, the outside diameter
142 is about 4.565 inches.
The outside surface 86 is tapered radially inward beginning at the axial
location of the outside diameter
142 and ending at the end of the body 80 opposite the enlarged-diameter
portion 82, thereby defining a
5 taper angle 144 from the valve seat axis 84. In an exemplary embodiment,
the taper angle 144 ranges
from about 0 degrees to about 5 degrees measured from the valve seat axis 84.
In an exemplary
embodiment, the taper angle 144 ranges from greater than 0 degrees to about 5
degrees measured from the
valve seat axis 84. In an exemplary embodiment, the taper angle 144 is about 2
degrees measured from
the valve seat axis 84. In an exemplary embodiment, the taper angle 144 is
about 1.8 degrees measured
from the valve seat axis 84.
In an exemplary embodiment, as illustrated in Figure 9 with continuing
reference to Figures 1-8,
the inlet valve 54 is omitted from the pump assembly 10 in favor of the inlet
valve 128, which is disposed
in the fluid passage 38. The tapered external shoulder 91 of the valve seat
129 engages the tapered
internal shoulder 43 of the fluid end block 18. Thus, the frusto-conical
surface 92 engages the frusto-
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22
conical surface 44. In an exemplary embodiment, the tapered internal shoulder
43 defines a taper angle
from the fluid passage axis 42 that is equal to the taper angle 132. In an
exemplary embodiment, the
tapered internal shoulder 43 defines a taper angle that is equal to the taper
angle 132, and the taper angle
132 ranges from about 10 degrees to about 45 degrees measured from the valve
scat axis 84. In an
exemplary embodiment, the tapered angle 132 ranges from about 20 degrees to 45
degrees measured from
the valve seat axis 84. In an exemplary embodiment, the tapered angle 132
ranges from about 25 degrees
to 35 degrees measured from the valve seat axis 84. In an exemplary
embodiment, the tapered internal
shoulder 43 defines a taper angle that is equal to the taper angle 132, and
the taper angle 132 is about 30
degrees measured from the valve scat axis 84. The 0-ring 88 sealingly engages
the inside surface 46 of
the fluid end block 18. The outside surface 86 of the body 80 of the valve
seat 129 of the inlet valve 128
engages the inside surface 46 of the fluid end block 18. In an exemplary
embodiment, at least the
reduced-diameter portion 38b of the fluid passage 38 is tapered such that an
inside diameter 146 defined
by the portion 38b decreases along the fluid passage axis 42 in an axial
direction away from the enlarged-
diameter portion 38a. In an exemplary embodiment, at an axial location
corresponding to the intersection
5 between the surfaces 46 and 44, the inside diameter 146 ranges from about
4 inches to about 5 inches. In
an exemplary embodiment, at an axial location corresponding to the
intersection between the surfaces 46
and 44, the inside diameter 146 ranges from about 4.5 inches to about 5
inches. In an exemplary
embodiment, at an axial location corresponding to the intersection between the
surfaces 46 and 44, the
inside diameter 146 ranges from about 4.5 inches to about 4.6 inches. In an
exemplary embodiment, at an
axial location corresponding to the intersection between the surfaces 46 and
44, the inside diameter 146 is
about 4.553 inches. In an exemplary embodiment, an interference fit is formed
between the outside
surface 86 and the inside surface 46, thereby preventing the valve seat 129
from being dislodged from the
fluid passage 38
In an exemplary embodiment, the operation of the inlet valve 129 during the
operation of the
5 pump assembly 10 is identical to the operation of the inlet valve 54.
Therefore, the operation of the inlet
valve 129 during the operation of the pump assembly 10 will not be described
in detail.
In an exemplary embodiment, the inlet valve 54 may be omitted from the pump
assembly 10 in
favor of the inlet valve 128, and the outlet valve 56 may be omitted from the
pump assembly 10 in favor
of an outlet valve that is identical to the inlet valve 128. In an exemplary
embodiment, the operation of
the pump assembly 10 using the inlet valve 128, and an outlet valve that is
identical to the inlet valve 128,
is identical to the above-described operation of the pump assembly 10 using
the inlet valve 54 and the
outlet valve 56.
In an exemplary embodiment, as illustrated in Figures 10 and 11 with
continuing reference to
Figures 1-9, an inlet valve is generally referred to by the reference numeral
150 and includes several parts
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that are identical to corresponding parts of the inlet valve 54, which
identical parts are given the same
reference numerals. The inlet valve 150 includes a valve seat 152 and a valve
member 154.
The valve seat 152 includes several features that are identical to
corresponding features of the
valve scat 76, which identical features are given the same reference numerals.
In contrast to the valve
seat 76, however, and as shown in Figure 10, the valve seat 152 does not
include the external tapered
shoulder 91 and thus does not include the frusto-conical surface 92. Instead,
the valve seat 152 includes
an external shoulder 156. which defines an axially-facing and
circumferentially-extending surface 158.
Alternatively, in several exemplary embodiments, the valve seat 152 may be
described as having the
external tapered shoulder 91, but the value of the taper angle 132 defined by
the external tapered shoulder
) 91 is 90 degrees. Moreover, the surface area of the tapered surface 96 is
increased; in particular, the
portion of the surface area of the tapered surface 96 that is adapted to
undergo steel-to-steel contact is
about doubled (2X to 2.2X).
An annular notch 160 is fornied in the valve seat 152 at the intersection of
the surfaces 86 and
158. A taper angle 162 is defined by the tapered surface 96. The taper angle
162 may be measured from
5 the valve seat axis 84. In an exemplary embodiment, the taper angle 162
is about 50 degrees measured
from the vertically¨extending valve seat axis 84 (40 degrees from any
horizontal line as viewed in Figure
10). In an exemplary embodiment, the taper angle 162 ranges from about 40
degrees to about 60 degrees
measured from the valve seat axis 84 (50 degrees to about 30 degrees from any
horizontal line as viewed
in Figure 10). In an exemplary embodiment, the taper angle 162 ranges from
about 45 degrees to about
) 55 degrees measured from the valve seat axis 84 (45 degrees to about 35
degrees from any horizontal line
as viewed in Figure 10).
The valve member 154 includes a central disk-shaped central base 164, which
defines an outside
circumferentially-extending convex surface 166. A valve body 168 extends
axially upwards from the
base 164, along the valve seat axis 84. The valve body 168 also extends
radially outward from the valve
5 seat axis 84. An outside annular cavity 170 is foimed in the valve body
168. A generally tapered and
circumferentially-extending surface 172, which extends angularly downward, is
defined by the outside
annular cavity 170. A generally tapered and circumferentially-extending
surface 174, which extends
angularly upward, is also defined by the outside annular cavity. A lower
circumferentially-extending
channel 176 is formed in the surface 174. Upper circumferentially-extending
channels 178a and 178b are
) formed in the surface 172. An annular groove 180 is formed in the valve
body 168 at the intersection
between the surfaces 172 and 174. An annular element, such as an 0-ring 182,
is disposed in the annular
groove 180.
A seal 184 extends within the outside annular cavity 170, and is adapted to
sealingly engage the
tapered surface 96 of the valve seat 152. The seal 184 extends within the
channels 176, 178a, and 178b.
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The 0-ring 182 engages the seal 184. In an exemplary embodiment, the seal 184
is composed of
urethane. In an exemplary embodiment, the extension of the seal 184 within the
channels 176, 178a, and
178b facilitates in securing the seal 184 to the valve body 168. In an
exemplary embodiment, the
combination of the 0-ring 182, and the extension of the seal 184 within the
channels 176, 178a, and 178b,
facilitates in securing the seal 184 to the valve body 168. The seal 184
defines an outside
circumferentially-extending exterior 186. An annular channel 188 is formed in
the exterior 186. The seal
184 further includes an annular bulbous protrusion 190. The channel 188 is
positioned vertically between
a top surface 192 of the valve body 168 and the bulbous protrusion 190. In an
exemplary embodiment,
the bulbous protrusion 190 is adjacent the channel 188. In an exemplary
embodiment, as shown in Figure
) 10, the channel 188 is positioned vertically between the top surface 192
and the bulbous protrusion 190,
and the bulbous protrusion 190 is adjacent the channel 188. A tapered and
circumferentially-extending
surface 194 extends angularly downward from the bulbous protrusion 190, the
extension of the surface
194 ending at, or proximate, the valve body 168.
In several exemplary embodiments, the seal 184 is a unitary structure and thus
the surface 186,
5 the channel 188, the bulbous protrusion 190, and the surface 194, as well
as the respective portions of the
seal 184 extending within the channels 176, 178a, and 178b, are integrally
formed.
In several exemplary embodiments, the seal 184 is a unitary structure of
urethane, and thus the
surface 186, the channel 188, the bulbous protrusion 190, and the surface 194,
as well as the respective
portions of the seal 184 extending within the channels 176, 178a, and 178b,
are integrally formed using
) urethane.
As shown in Figures 10 and 11, the valve body 168 includes an annular channel
196, about which
the top surface 192 circumferentially extends. An annular ridge 198 is formed
in the valve body 168
adjacent the channel 196, and is radially positioned between the channel 196
and the top surface 192. An
axially-facing surface 200 is defined by the channel 196, and a protrusion 202
extends axially upwards
5 from the surface 200 and out of the channel 196. The lower end portion of
the spring 108 (not shown in
Figures 10 and 11) is engaged with the surface 200. The protrusion 202 extends
within the lower end
portion of the spring 108.
The valve body 168 defines a fnisto-conical surface 204, which extends
angularly upwardly from
the base 164. A frusto-conical surface 206 is also defined by the valve body
168, the frusto-conical
) surface 206 extending angularly between the frusto-conical surface 204 of
the valve body 168 and the
tapered and circumferentially-extending surface 194 of the seal 184.
The plurality of circumferentially-spaced legs 106 extend angularly downward
from the base 164,
and slidably engage the inside surface 85 of the seat body 80 of the valve
seat 152. In several exemplary
embodiments, the plurality of legs 106 may include two, three, four, five, or
greater than five, legs 106.
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An angle 208 is defined by the frusto-conical surface 206. The angle 208 may
be measured from
a valve member axis 210. The valve member axis 210 is aligned, or coaxial,
with valve seat axis 84 when
the inlet valve 150 is disposed in the fluid passage 38 of the fluid end block
18. Thus, the axes 210, 84,
and 42 arc aligned, or coaxial, with each other when the inlet valve 150 is
disposed in the first fluid
5 passage 38 of the fluid end block 18.
In an exemplary embodiment, the angle 208, as measured from the valve member
axis 210, is
substantially equal to the angle 162 defined by the tapered surface 96, as
measured from the valve seat
axis 84. In an exemplary embodiment, the angle 208 is 50 degrees from the
valve member axis 210, and
the angle 162 is 50 degrees from the valve scat axis 84.
An angle 214 is defined by the frusto-conical surface 204. As measured from
the valve member
axis 210, the angle 214 is greater than the angle 208.
An angle 216 (shown most clearly in Figure 11) is defined by the tapered
surface 194 of the seal
184. The angle 216 may be measured from the valve member axis 210. In an
exemplary embodiment,
the angle 216 is substantially equal to the angle 208 when measured from the
valve member axis 210. In
5 an exemplary embodiment, the angle 216 is greater than the angle 208 when
measured from the valve
member axis 210. In an exemplar), embodiment, the angle 216 is substantially
equal to, or greater than,
the angle 208 when measured from the valve member axis 210. In an exemplary
embodiment, the angle
216 is less than, substantially equal to, or greater than, the angle 208 when
measured from the valve
member axis 210.
In an exemplary embodiment, the valve member 154 is composed of AISI 8620
alloy steel
material. In an exemplary embodiment, the valve seat 152 is composed of MST
8620 alloy steel material.
In an exemplary embodiment, the valve seat 152 is composed of AISI 52080 alloy
steel material.
The valve member 154 is movable, relative to the valve seat 152 and the fluid
end block 18,
between a closed position (not shown but described below) and an open position
(shown in Figure 10 and
5 described below).
In an exemplary embodiment, as shown in Figure 11, the seal 184 includes a
circumferentially-
extending upper tab 218, which extends upwardly from the channel 188 and
encircles the top surface 192
of the valve body 168. A top surface 220 is defined by the tab 218. As shown
in Figure 11, the top
surface 220 of the seal 184 and the top surface 192 of the valve body 168 are
substantially flush. An
) annular channel 222 is formed in the tab 218 at the exterior 186 of the
seal 184. In several exemplary
embodiments, as shown in Figure 11, the channels 176, 178a, and 178b may be
omitted from the valve
body 168.
In an exemplary embodiment, the seal 184 is molded in place in the valve body
168. In an
exemplary embodiment, the seal 184 is preformed and then attached to the valve
body 168. In several
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exemplary embodiments, the seal 184 is composed of one or more materials such
as, for example, a
deformable thermoplastic material, a urethane material, a fiber-reinforced
material, carbon, glass, cotton,
wire fibers, cloth, and/or any combination thereof. In an exemplary
embodiment, the seal 184 is
composed of a cloth which is disposed in a thermoplastic material, and the
cloth may include carbon,
glass, wire, cotton fibers, and/or any combination thereof In several
exemplary embodiments, the seal
184 is composed of at least a fiber-reinforced material, which prevents, or at
least reduces, delamination.
In an exemplary embodiment, the seal 184 has a hardness of 95A durometer or
greater, or a hardness of
69D durometer or greater. In several exemplary embodiments, the valve body 168
is much harder and/or
more rigid than the seal 184.
In an exemplary embodiment, with reference to Figures 2, 3, 10, and 11, the
inlet valve 54 is
omitted from the pump assembly 10 in favor of the inlet valve 150, which is
disposed in the fluid passage
38. However, the tapered internal shoulder 43 is omitted from the fluid end
block 18, in favor of an
axially-facing internal shoulder 224 (shown in Figure 10), which is defined by
the enlarged-diameter
portion 38a of the fluid inlet passage 38 of the fluid end block 18.
Alternatively, this exemplary
5 embodiment may be described as including the tapered internal shoulder
43, but the taper angle of the
tapered internal shoulder 43 is 90 degrees when measured from the axis 42.
When the inlet valve 150 is disposed in the fluid passage 38. the external
shoulder 156 of the
valve seat 152 is engaged with the internal shoulder 224 of the fluid end
block 18. The 0-ring 88 (shown
in Figure 3) is disposed in the annular groove 90 and sealingly engages the
inside surface 46 of the fluid
end block 18. The outside surface 86 of the body 80 of the valve seat 152 of
the inlet valve 150 engages
the inside surface 46 of the fluid end block 18. In an exemplary embodiment,
at least the reduced-
diameter portion 38b of the fluid passage 38 is tapered such that its inside
diameter decreases along the
fluid passage 38 in an axial direction away from the enlarged-diameter portion
38a. In an exemplary
embodiment, an interference fit is formed between the outside surface 86 and
the inside surface 46,
5 thereby preventing the valve seat 152 from being dislodged from the fluid
passage 38. The lower portion
of' the spring 108 engages the surface 200 of the valve body 168, while the
upper portion of the spring 108
engages the valve spring retainer 72. The spring 108 of the inlet valve 150 is
thus compressed between
the surface 200 and the valve spring retainer 72.
In an exemplary embodiment, with reference to Figures 2, 3, 10, and 11, the
outlet valve 56 is
omitted from the pump assembly 10 in favor of an outlet valve that is
identical to the inlet valve 150, and
this outlet valve is disposed in the fluid passage 40. However, the tapered
internal shoulder 48 is omitted
from the fluid end block 18, in favor of an axially-facing internal shoulder
(not shown but identical to the
shoulder 224), which is defined by the enlarged-diameter portion 40a of the
fluid outlet passage 40 of the
fluid end block 18. Alternatively, this exemplary embodiment may be described
as including the tapered
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internal shoulder 48, but the taper angle of the tapered internal shoulder 48
is 90 degrees when measured
from the axis 42
The outlet valve; which is identical to the inlet valve 150, is disposed in
the fluid passage 40, and
engages the fluid end block 18, in a manner that is identical to the manner in
which the inlet valve 150 is
disposed in the fluid passage 38, and engages the fluid end block 18, with one
exception. This one
exception involves the spring 108 of the outlet valve that is identical to the
inlet valve 150; more
particularly, the upper portion of the spring 108 of the outlet valve is
compressed against the bottom of
the plug 64, rather than being compressed against a component that corresponds
to the valve spring
retainer 72, against which the upper portion of the spring 108 of the inlet
valve 150 is compressed.
In operation, in an exemplary embodiment, with continuing reference to Figures
1-11, the plunger
32 reciprocates within the bore 34, reciprocating in and out of the pressure
chamber 36. That is, the
plunger 32 moves back and forth horizontally, as viewed in Figure 2, away from
and towards the fluid
passage axis 42, In an exemplary embodiment, the engine or motor (not shown)
drives the crankshaft
(not shown) enclosed within the housing 16, thereby causing the plunger 32 to
reciprocate within the bore
5 34 and thus in and out of the pressure chamber 36.
As the plunger 32 reciprocates out of the pressure chamber 36, the inlet valve
150 is opened.
More particularly, as the plunger 32 moves away from the fluid passage axis
42, the pressure inside the
pressure chamber 36 decreases, creating a differential pressure across the
inlet valve 150 and causing the
valve member 154 to move upward, as viewed in Figures 2, 3, and 10, relative
to the valve seat 152 and
) the fluid end block 18. As a result of the upward movement of the valve
member 154, the spring 108 is
compressed between the valve body 168 and the valve spring retainer 72, the
seal 184 disengages from
the tapered surface 96, and the inlet valve 150 is thus placed in its open
position. Fluid in the fluid inlet
passage 22 flows along the fluid passage axis 42 and through the fluid passage
38 and the inlet valve 150,
being drawn into the pressure chamber 36. To flow through the inlet valve 150,
the fluid flows through
5 the bore 83 of the valve seat 152 and along the valve seat axis 84.
During the fluid flow through the inlet
valve 150 and into the pressure chamber 36, the outlet valve (which is
identical to the inlet valve 150 as
described above) is in its closed position, with the seal 184 of the valve
member 154 of the outlet valve
engaging the tapered surface 96 of the valve seat 152 of the outlet valve.
Fluid continues to be drawn into
the pressure chamber 36 until the plunger 32 is at the end of its stroke away
from the fluid passage axis
) 42. At this point, the differential pressure across the inlet valve 150
is such that the spring 108 of the inlet
valve 54 is not further compressed, or begins to decompress and extend,
forcing the valve member 154 of
the inlet valve 150 to move downward, as viewed in Figures 2, 3, and 10,
relative to the valve seat 152
and the fluid end block 18. As a result, the inlet valve 150 is placed in, or
begins to be placed in, its
closed position, with the seal 184 sealingly engaging, or at least moving
towards, the tapered surface 96.
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As the plunger 32 moves into the pressure chamber 36 and thus towards the
fluid passage axis 42,
the pressure within the pressure chamber 36 begins to increase. The pressure
within the pressure chamber
36 continues to increase until the differential pressure across the outlet
valve (which is identical to the
inlet valve 150) exceeds a predetermined set point, at which point the outlet
valve opens and permits fluid
to flow out of the pressure chamber 36, along the fluid passage axis 42 and
through the fluid passage 40
and the outlet valve, and into the fluid outlet passage 24. As the plunger 32
reaches the end of its stroke
towards the fluid passage axis 42 (i.e., its discharge stroke), the inlet
valve 150 is in, or is placed in, its
closed position, with the seal 184 sealingly engaging the tapered surface 96.
The foregoing is repeated, with the reciprocating pump assembly 10
pressurizing the fluid as the
) fluid flows from the fluid inlet passage 22 and to the fluid outlet
passage 24 via the pressure chamber 36.
In an exemplary embodiment, the pump assembly 10 is a single-acting
reciprocating pump, with fluid
being pumped across only one side of the plunger 32.
In an exemplary embodiment, during the above-described operation of the
reciprocating pump
assembly 10 with the inlet valve 150 and the outlet valve that is identical to
the inlet valve 150, the shape
5 of the seal 184 provides improved contact pressure against the tapered
surface 96, thereby providing a
better seal in the closed position. In particular, in an exemplary embodiment,
the surface 194 provides
improved contact pressure against the tapered surface 96. In an exemplary
embodiment, the combination
of the surface 194 and the bulbous protrusion 190 provides improved contact
pressure against the tapered
surface 96.
In an exemplary embodiment, when the inlet valve 150 is in the closed
position, at least the
surface 194 seals against the tapered surface 96, and at least the surface 206
of the valve body 168
contacts the tapered surface 96 of the valve seat 152. In several exemplary
embodiments, the contact
between the surfaces 206 and 96 is steel-to-steel contact, which may be
susceptible to damage and wear.
However, the combination of the frusto-conical surfaces 204 and 206 greatly
reduces the maximum steel
5 contact pressure between the surfaces 206 and 96, greatly reducing damage
and wear. In several
exemplary embodiments, specifying the angle 162 at 50 degrees from the axis 84
(or 40 degrees from
horizontal), and the angle 208 at 50 degrees from the axis 210 (or 40 degrees
from horizontal), reduces
the maximum steel contact pressure. In several exemplary embodiments, the
steel/urethane ratio reduces
the maximum steel contact pressure. In several exemplary embodiments, the
ratio of the contact area of
) the valve body 168 against the surface 96, to the contact area of the
seal 184 against the surface 96,
reduces the maximum steel contact pressure.
In an exemplary embodiment, when the inlet valve 150 is in the closed
position, the steel-to-steel
contact between the surfaces 206 and 96 results in maximum stress in the valve
body 168 of the valve
member 154, and/or in the seat body 80 of the valve seat 152. However, the
combination of the frusto-
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conical surfaces 204 and 206 greatly reduces this maximum stress. In several
exemplary embodiments,
the steel/urethane ratio reduces the maximum stress. In several exemplary
embodiments, the ratio of the
contact area of the valve body 168 against the surface 96, to the contact area
of the seal 184 against the
surface 96, reduces the maximum stress.
Comparing the valve body 100 of Figure 6 with the valve body 168 of Figure 10,
the filling in of
the valve body 168 with material, to define the surfaces 204 and 206,
increases strength and reduces
turbulence. In several exemplary embodiments, specifying the angle 162 at 50
degrees from the axis 84
(or 40 degrees from horizontal), and the angle 208 at 50 degrees from the axis
210 (or 40 degrees from
horizontal), provides for better fluid flow and contact area.
In several experimental exemplary embodiments, experimental finite element
analyses were
conducted on an Experimental Baseline Embodiment of an inlet valve and an
Experimental Exemplary
Embodiment of the inlet valve 150 illustrated in Figure 10. The Experimental
Baseline Embodiment was
similar in design and configuration to the inlet valve 128 illustrated in
Figure 6, except that the tapered
external shoulder 91 and thus the frusto-conical surface 92 were omitted;
instead, the Experimental
5 Baseline Embodiment included an external shoulder identical to the
external shoulder 156 of the inlet
valve 150, and thus included an axially-facing and circumferentially-extending
surface identical to the
surface 158 of the inlet valve 150. During the experimental finite element
analyses, the Experimental
Baseline Embodiment and the Experimental Exemplary Embodiment of the inlet
valve 150 were of the
same valve size to work in the same size of fluid end block 18, and were
subject to the same operational
) parameters (pressure, force loading, etc.).
In an exemplary experimental embodiment, Figure 12 is a view of experimental
steel contact
pressures experienced by a finite element model of the Experimental Exemplary
Embodiment of the inlet
valve 150 of Figure 10, according to an exemplary experimental embodiment. The
maximum steel
contact pressure between the valve body 168 and the seat body 80 was found to
be in the vicinity of point
5 A in Figure 12, with a value of about 60ksi. The equivalent Experimental
Baseline Embodiment had a
maximum steel contact pressure of about 244ksi. Thus, the inlet valve 150
provides at least a 75%
reduction in maximum steel contact pressure between the valve body 168 and the
seat body 80. This was
an unexpected result. The portion of the surface area of the surface 96
adapted to undergo steel-to-steel
contact was about doubled (2X to 2.2X), yet this doubling provided a 75%
reduction in maximum steel
) contact pressure, rather than just a 50% reduction as might have been
expected. Thus, the 75% reduction
in maximum contact pressure was an unexpected result.
In an exemplary experimental embodiment. Figure 13 is a view of experimental
stresses
experienced by a finite element model of the Exemplary Experimental Embodiment
of the inlet valve 150
of Figure 10, according to an exemplary experimental embodiment. The maximum
stress due to the
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contact between the valve body 168 and the seat body 80 was found to be in the
vicinity of point B in
Figure 13, with a value of about 68ksi. The equivalent Experimental Baseline
Embodiment had a
maximum stress of about 130ksi. Thus, the inlet valve 150 provides at least a
48% reduction in
maximum stress.
5 In an exemplary experimental embodiment, Figure 14 is a view of
experimental urethane contact
pressures experienced by a finite element model of the Exemplary Experimental
Embodiment of the inlet
valve 150 of Figure 10, according to an exemplary experimental embodiment. The
maximum urethane
contact pressure provide by the seal 184 against the surface 96 was found to
be in the vicinity of point C
in Figure 14, and was 500 psi higher than the maximum urethane contact
pressure of the equivalent
) Experimental Baseline Embodiment.
In an exemplary experimental embodiment, the contact area between the seal 184
and the surface
96 of the Exemplary Experimental Embodiment of the inlet valve 150 was 6.388
in2, and the contact area
between the surface 206 and the surface 96 of the Exemplary Experimental
Embodiment was 6.438 in2;
and the contact area between the seal 184 and the surface 96 of the
Experimental Baseline Embodiment
5 was 7.166 in2, and the contact area between the surface 206 and the
surface 96 of the Experimental
Baseline Embodiment was 3.176 in2.
In an exemplary embodiment, the contact area between the seal 184 and the
surface 96 of the inlet
valve 150 is 6.388 in2 (e.g., urethane contact), and the contact area between
the surface 206 and the
surface 96 of the inlet valve 150 is 6.438 in2 (e.g., steel contact). In an
exemplary embodiment, the
) steel/urethane contact ratio of the inlet valve 150 is 6.438/6.388, or
about 1. In an exemplary
embodiment, the steel/urethane contact ratio of the inlet valve 150 is
6.82/6.22, or about 1.1. In an
exemplary embodiment, the steel/urethane contact ratio ranges from about 0.9
to about 1.2. In an
exemplary embodiment, the ratio of the contact area between the surface 206
and the surface 96 of the
inlet valve 150, to the contact area between the seal 184 and the surface 96
of the inlet valve 150, is about
5 1. about 1.1, or ranges from about 0.9 to about 1.2.
In an exemplary embodiment, as illustrated in Figures 15-18, a valve member is
generally
referred to by the reference numeral 230 and includes a central disk-shaped
central base 232, which
defines an outside circumferentially-extending convex surface 234. A valve
body 236 extends axially
upwards from the base 232, along a valve member axis 237. In an exemplary
embodiment, the valve
) member axis 237 is aligned, or coaxial, with the valve seat axis 84 shown
in Figure 10. Thus, in several
exemplary embodiments, the valve member axis 237 is aligned, or coaxial, with
the fluid passage axis 42
shown in Figure 10. The valve body 236 also extends radially outward from the
valve member axis 237.
As shown in Figures 17 and 18, an outside annular cavity 240 is formed in the
valve body 236
and defines a concave surface 241. A generally tapered and circumferentially-
extending surface 242,
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which extends angularly downward to the concave surface 241, is defined by the
outside annular cavity
240. A generally tapered and circumferentially-extending surface 244, which
extends angularly upward
to the concave surface 241, is also defined by the outside annular cavity 240.
As shown in Figures 15 and 17, the valve body 236 includes an annular channel
246, about which
a top surface 248 circumferentially extends. An annular ridge 250 is adjacent
the channel 246, and is
radially positioned between the channel 246 and the top surface 248. An
axially-facing surface 252 is
defined by the channel 246, and a protrusion 254 extends axially upwards from
the surface 252 and out of
the channel 246. In an exemplary embodiment, the surface 252 is engaged with a
lower end portion of a
spring, such as the spring 108 of Figure 3. In an exemplary embodiment, the
protrusion 254 extends
within a lower end portion of a spring, such as the spring 108 of Figure 3.
A seal 256 extends within the outside annular cavity 240, and is adapted to
sealingly engage a
tapered surface of a valve seat, such as the tapered surface 96 of the valve
seat 152 of Figure 10. In an
exemplary embodiment, the seal 256 is composed of urethane. In an exemplary
embodiment, the
extension of the seal 256 within the cavity 240 facilitates in securing the
seal 256 to the valve body 236.
5 The seal 256 defines an outside circumferentially-extending exterior 258.
An annular channel 260 is
formed in the exterior 258. The seal further includes an annular bulbous
protrusion 262. The channel 260
is positioned vertically between the top surface 248 of the valve body 236 and
the bulbous protrusion 262.
In an exemplary embodiment, the bulbous protrusion 262 is positioned adjacent
the channel 260. In an
exemplary embodiment, the channel 260 is positioned vertically between the top
surface 248 and the
bulbous protrusion 262, and the bulbous protrusion 262 is adjacent the channel
260.
The seal 256 also includes a circumferentially-extending upper tab 264, which
extends upwardly
from the channel 260 and encircles the top surface 248 of the valve body 236.
A top surface 266 is
defined by the tab 264. As shown in Figure 17, the top surface 266 of the seal
256 and the top surface
248 of the valve body 236 are substantially flush. An annular channel 268 is
formed in the tab 264 at the
5 exterior 258 of the seal 256. In an exemplary embodiment, the annular
channel 268 is positioned
vertically between the top surface 266 of the seal 256 and the annular channel
260. In an exemplary
embodiment, the annular channel 268 is positioned vertically between the top
surface 266 of the seal 256
and the bulbous protrusion 262.
As shown most clearly in Figures 17 and 18, frusto-conical surfaces 270 and
272 are defined by
the seal 256. In several exemplary embodiments, the frusto-conical surfaces
270 and 272 may be
characterized as first and second tapered and circumferentially-extending
surfaces, respectively. The
frusto-conical surface 270 extends angularly downward from the bulbous
protrusion 262, the extension of
the fmsto-conical surface 270 ending at, or proximate, the fmsto-conical
surface 272. The frusto-conical
surface 272 extends angularly downward from the frusto-conical surface 270
ending at, or proximate, the
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valve body 236. An annular contact portion 274 is defined at the intersection
between the frusto-conical
surface 270 and the frusto-conical surface 272. The contact portion 274
includes at least a portion of the
fmsto-conical surface 270. In an exemplary embodiment, the contact portion 274
includes at least
respective portions of the frusto-conical surfaces 270 and 272.
In several exemplary embodiments, the seal 256 is a unitary structure and thus
the exterior 258,
the upper tab 264, the channel 268, the channel 260, the bulbous protrusion
262, and the surface 266,
including the frusto-conical surfaces 270 and 272, as well as the respective
portions of the seal 256
extending within the channel 240, are integrally formed.
In several exemplary embodiments, the seal 256 is a unitary structure of
urethane, and thus the
) exterior 258, the upper tab 264, the channel 268, the channel 260, the
bulbous protrusion 262, and the
surface 266, including the frusto-conical surfaces 270 and 272, as well as the
respective portions of the
seal 256 extending within channel 240, are integrally formed.
The valve body 236 defines a frusto-conical surface 276, which extends
angularly upwardly from
the base 232. A frusto-conical surface 278 is also defined by the valve body
236, the frusto-conical
5 surface 278 extending angularly between the frusto-conical surface 276 of
the valve body 236 and the
frusto-conical surface 272 of the seal 256.
A plurality of circumferentially-spaced legs 280 extend angularly downward
from the base 232,
and are adapted to slidably engage an inside surface of a seat body of a valve
seat, such as the inside
surface 85 of the seat body 80 of the valve seat 152 of Figure 10. In several
exemplary embodiments, the
) plurality of legs 280 may include two, three, four, five, or greater than
five, legs 280.
An angle 282 is defined by the frusto-conical surface 278. The angle 282 may
be measured from
the valve member axis 237. In an exemplary embodiment, the angle 282, as
measured from the valve
member axis 237, is substantially equal to the angle 162 defined by the
tapered surface 96, as measured
from the valve seat axis 84, as shown in Figure 10. In an exemplary
embodiment, the angle 282 is about
5 50 degrees from the valve member axis 237, and the angle 162 is about 50
degrees from the valve seat
axis 84. In an exemplary embodiment, the angle 282 is substantially equal to,
or greater than (e.g., 51
degrees, 52 degrees, 53 degrees, 54 degrees. 55 degrees, or more), the angle
162 of Figure 10 when
measured from the valve member axis 237. In an exemplary embodiment, the angle
282 is less than (e.g.,
49 degrees, 48 degrees, 47 degrees, 46 degrees, 45 degrees, or less),
substantially equal to, or greater than,
) the angle 162 when measured from the valve member axis 237.
An angle 286 is defined by the frusto-conical surface 276. As measured from
the valve member
axis 237, the angle 286 is greater than the angle 282. In an exemplary
embodiment, the angle 286 is
about 70 degrees when measured from the valve member axis 237. In an exemplary
embodiment, the
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angle 286 ranges from about 60 degrees to about 85 degrees when measured from
the valve member axis
237. In an exemplary embodiment the angle 286 ranges from about 65 degrees to
about 80 degrees.
An angle 288 (shown most clearly in Figure 18) is defined by the fnisto-
conical surface 272 of
the seal 256. The angle 288 may be measured from the valve member axis 237. In
an exemplary
embodiment, the angle 288 is greater than the angle 282 when measured from the
valve member axis 237.
In an exemplary embodiment, the angle 282 is about 62.5 degrees. The angles
282 and 288 define an
angle 290 therebetween. In an exemplary embodiment, the angle 290 is about
12.5 degrees. In an
exemplary embodiment, the angle 290 ranges from about 0 degrees to about 25
degrees. In an exemplary
embodiment, the angle 290 ranges from about 5 degrees to about 20 degrees. In
an exemplary
embodiment, the angle 290 ranges from about 10 degrees to about 15 degrees.
An angle 292 is defined by the frusto-conical surface 270 of the seal 256. The
angle 292 may be
measured from the valve member axis 237. In an exemplary embodiment, the angle
292 is substantially
equal to the angle 282 when measured from the valve member axis 237. In an
exemplary embodiment,
the angle 292 is less than the angle 288 when measured from the valve member
axis 237. As a result, as
5 indicated by the reference numeral DI, the contact portion 274 is offset
a distance DI from the fnisto-
conical surface 278 in a direction perpendicular to the frusto-conical surface
278. In an exemplary
embodiment, the offset distance DI is about .06 inches. In an exemplary
embodiment, the offset distance
DI ranges from about .04 inches to about .08 inches. In an exemplary
embodiment, the offset distance Dt
ranges from greater than 0 inches to about 0.1 inches. In an exemplary
embodiment, the frusto-conical
surfaces 270 and 278 are spaced in parallel relation and the parallel spacing
therebetween defines the
offset distance D.
In an exemplary embodiment, the valve member 230 is adapted and sized to be
used with an SPM
SP4 full open well service seat.
In an exemplary embodiment, the valve member 230 is composed of AISI 8620
alloy steel
5 material.
In an exemplary embodiment, the valve member 230 is movable, relative to a
valve seat, such as
the valve seat 152 of Figure 10, and a fluid end block, such as the fluid end
block 18 of Figure 10,
between a closed position (not shown but described below) and an open position
(not shown but
described below). In such embodiments, the valve seat 152 is offset from the
valve member 230 such that
the tapered surface 96 is offset a distance (not shown) from the valve member
230.
In an exemplary embodiment, the seal 256 is molded in place in the valve body
236. In an
exemplary embodiment, the seal 256 is preformed and then attached to the valve
body 236. In an
exemplary embodiment, the seal 256 is bonded to the valve body 236. As noted
above, in an exemplary
embodiment, the seal 256 is composed of urethane. In several exemplary
embodiments, the seal 256 is
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composed of one or more materials such as, for example, a defomiable
thermoplastic material, a urethane
material, a fiber-reinforced material, carbon, glass, cotton, wire fibers,
cloth, and/or any combination
thereof In an exemplary embodiment, the seal 256 is composed of a cloth which
is disposed in a
thermoplastic material, and the cloth may include carbon, glass, wire, cotton
fibers, and/or any
combination thereof. In several exemplary embodiments, the seal 256 is
composed of at least a fiber-
reinforced material, which prevents, or at least reduces, delamination. In an
exemplary embodiment, the
seal 256 has a hardness of 95A durometer or greater, or a hardness of 69D
durometer or greater. In
several exemplary embodiments, the valve body 236 is much harder and/or more
rigid than the seal 256.
In an exemplary embodiment, the valve member 154 of Figures 10 and 11 is
omitted in favor of
the valve member 230. In operation, in such embodiments, with continuing
reference to Figures 1-18, the
plunger 32 reciprocates within the bore 34, reciprocating in and out of the
pressure chamber 36. That is,
the plunger 32 moves back and forth horizontally, as viewed in Figure 2, away
from and towards the fluid
passage axis 42, In an exemplary embodiment, the engine or motor (not shown)
drives the crankshaft
(not shown) enclosed within the housing 16, thereby causing the plunger 32 to
reciprocate within the bore
5 34 and thus in and out of the pressure chamber 36.
As the plunger 32 reciprocates out of the pressure chamber 36, the inlet valve
150 is opened.
More particularly, as the plunger 32 moves away from the fluid passage axis
42, the pressure inside the
pressure chamber 36 decreases, creating a differential pressure across the
inlet valve 150 and causing the
valve member 230 to move upward, relative to the valve seat 152 and the fluid
end block 18. As a result
of the upward movement of the valve member 230, the spring 108 is compressed
between the valve body
236 and the valve spring retainer 72, the seal 256 disengages from the tapered
surface 96, and the inlet
valve 150 is thus placed in its open position. Fluid in the fluid inlet
passage 22 flows along the fluid
passage axis 42 and through the fluid passage 38 and the inlet valve 150,
being drawn into the pressure
chamber 36. To flow through the inlet valve 150, the fluid flows through the
bore 83 of the valve seat
5 152 and along the valve seat axis 84. During the fluid flow through the
inlet valve 150 and into the
pressure chamber 36, the outlet valve 56 (which is identical to the inlet
valve 150 as described above) is
in its closed position, with the seal 256 of the valve member 230 of the
outlet valve 56 engaging the
tapered surface 96 of the valve seat 152 of the outlet valve 56. Fluid
continues to be drawn into the
pressure chamber 36 until the plunger 32 is at the end of its stroke away from
the fluid passage axis 42.
At this point, the differential pressure across the inlet valve 150 is such
that the spring 108 of the inlet
valve 150 is not further compressed, or begins to decompress and extend,
forcing the valve member 230
of the inlet valve 150 to move downward relative to the valve seat 152 and the
fluid end block 18. As a
result, the inlet valve 150 is placed in, or begins to be placed in, its
closed position, with the seal 256
sealingly engaging, or at least moving towards, the tapered surface 96.
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As the plunger 32 moves into the pressure chamber 36 and thus towards the
fluid passage axis 42,
the pressure within the pressure chamber 36 begins to increase. The pressure
within the pressure chamber
36 continues to increase until the differential pressure across the outlet
valve 56 exceeds a predetermined
set point, at which point the outlet valve 56 opens and permits fluid to flow
out of the pressure chamber
5 36, along the fluid passage axis 42 and through the fluid passage 40 and
the outlet valve 56, and into the
fluid outlet passage 24. As the plunger 32 reaches the end of its stroke
towards the fluid passage axis 42
(i.e., its discharge stroke), the inlet valve 54 is in, or is placed in, its
closed position, with the seal 256
sealingly engaging the tapered surface 96.
In an exemplary embodiment, the configuration of the seal 256 provides
improved scaling
engagement with the tapered surface 96, thereby providing an improved seal
when the inlet valve 150
and/or the identical outlet valve 56 are in respective closed positions. In
particular, in an exemplary
embodiment, the offset distance DI of the contact portion 274 ensures that at
least the annular contact
portion 274 sealingly engages the tapered surface 96 as the valve member 230
moves downward relative
to the valve scat 152. More particularly, the offset distance DI ensures that,
as the valve member 230
5 moves downward, the annular contact portion 274 will contact the tapered
surface 96 before the frusto-
conical surface 278, ensuring the sealing engagement between the seal 256 and
the surface 96. In an
exemplary embodiment, the offset distance DI of the contact portion 274
ensures that at least the contact
portion 274 sealingly engages the tapered surface 96 as the valve member 230
moves downward relative
to the valve seat 152. In an exemplary embodiment, as the valve member 230
moves downward relative
to the valve seat 152, the contact portion 274 engages the tapered surface 96
before other surfaces of the
valve member 230. For example, the contact portion 274 engages the surface 96
before the frusto-conical
surface 278, before the frusto-conical surface 272, and/or before the frusto-
conical surface 270 engages
the tapered surface 96. In an exemplary embodiment, the angle 290 ensures that
at least the contact
portion 274 sealingly engages the tapered surface 96 as the valve member 230
moves downward relative
5 to the valve seat 152. In an exemplary embodiment, the difference between
the angle 292 and the angle
288 and the difference between the angle 282 and the angle 288 ensure that at
least the contact portion
274 sealingly engages the tapered surface 96 as the valve member 230 moves
downward relative to the
valve seat 152.
In an exemplary embodiment, as the valve member 230 moves downward relative to
the valve
seat 152, initially, the contact portion 274 sealingly engages the tapered
surface 96; as noted above, at
least a portion of frusto-conical surface 270, or at least respective portions
of the frusto-conical surfaces
270 and 272 sealingly engage the tapered surface 96. As the valve member 230
continues to move
downward relative to the valve seat 152, the seal 256 deforms radially from
the contact portion 274. As a
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result, in an exemplary embodiment, at least respective additional portions of
the frusto-conical surfaces
270 and 272 also sealinglv engage the surface 96.
The foregoing is repeated, with the reciprocating pump assembly 10
pressurizing the fluid as the
fluid flows from the fluid inlet passage 22 and to the fluid outlet passage 24
via the pressure chamber 36.
In an exemplary embodiment, the pump assembly 10 is a single-acting
reciprocating pump, with fluid
being pumped across only one side of the plunger 32.
In several exemplary embodiments, the valve member 78 of Figure 3 is omitted
in favor of the
valve member 230. In several exemplary embodiments, the valve member 230 is
used with any of the
valve scats, including, but not limited to, the valve scat 76 and the valve
scat 128. In several exemplary
embodiments, the valve member 230 is used with other valve seats having
configurations different from
that of the valve seat 76 and/or the valve seat 128. In several exemplary
embodiments, the valve member
230 is used with any of the inlet and outlet valves, including the inlet valve
54, the inlet valve 128, the
outlet valve 56, and/or other differently configured inlet and outlet valves.
In an exemplary embodiment, as illustrated in Figures 19-21, a valve member is
generally
5 referred to by the reference numeral 294 and includes several parts that
are identical to corresponding
parts of the valve member 230, which identical parts are given the same
reference numerals. As shown in
Figures 19 and 21. the valve member 294 includes a rupture disc assembly 296.
As shown most clearly in Figure 21, a counterbore 298 is formed in the valve
body 236, and is
generally coaxial with the valve member axis 237. The counterbore 298 extends
all the way through the
valve body 236. The counterbore 298 includes an enlarged-diameter portion 298a
and a reduced-diameter
portion 298b. The reduced-diameter portion 298b defines a fluid passage 299
extending axially through
the valve body 236. The counterbore 298 defines an internal shoulder 300.
The rupture disc assembly 296 is disposed in the enlarged-diameter portion
298a of the
counterbore 298. The rupture disc assembly 296 includes a rupture disc 301,
which includes an annular
5 mounting portion 302 and a domed rupture portion 304 about which the
mounting portion 302
circumferentially extends. The mounting portion 302 is disposed in the
enlarged-diameter portion 298a
of the counterbore 298 and engages the internal shoulder 300. The mounting
portion 302 includes an
annular channel 306 formed in an end portion thereof that engages the internal
shoulder 300. One or
more annular seals 308 extend within the annular channel 306 and sealingly
engage at least the mounting
portion 302 and the internal shoulder 300.
In several exemplary embodiments, any of the valve members 78, 154, or 230 are
omitted in
favor of the valve member 294. In several exemplary embodiments, the valve
member 294 is used in an
inlet valve, such as the inlet valve 150 of Figures 10 and 11. In several
exemplary embodiments,
operation of the pump assembly 10 with the valve member 294 is substantially
identical to the operation
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of the pump assembly 10 with the valve member 230, as discussed above with
regard to Figures 15-18,
except for the added operation of the rupture disc assembly 296. More
particularly, in operation, with
reference to Figures 1-21, as the plunger 32 moves into the pressure chamber
36, the inlet valve 150 is in
its closed position and a fluid pressure is exerted in at least an axial
direction generally downwards along
the fluid passage axis 42 on the rupture disc 301 of the rupture disc assembly
296. The sealing
engagement between the one or more annular seals 308 and at least the mounting
portion 302 and the
internal shoulder 300 prevents, or at least resists, the fluid from flowing
from the pressure chamber 36,
around the rupture disc 301, and thus back into the fluid inlet passage 22.
During the operation of the
pump assembly 10, if the fluid pressure within the pressure chamber 36 reaches
or exceeds an acceptable
) predetermined value, causing a predetermined pressure differential across
the rupture disc 301, the
rupture portion 304 of the rupture disc 301 ruptures. As a result, the fluid
passage 299 is in fluid
communication with the pressure chamber 36 via the fluid inlet passage 38, and
the rupture disc assembly
296 permits fluid to flow from the pressure chamber 36, through the fluid
inlet passage 38, through the
mounting portion 302 and thus back into at least the fluid inlet passage 22
and out of the pump assembly
5 10. This fluid flow reduces or relieves the pressure within the pump
assembly 10. During operation, in
several exemplary embodiments, after the rupture disc 301 ruptures, the
diameter of the rupture portion
304 is less than the reduced-diameter portion 298a of the counterbore 298 thus
increasing the likelihood
that shrapnel from the ruptured rupture disc 301 will flow downward and out of
the counterbore 298
without creating a pressure spike.
In several exemplary embodiments, the valve member 294 is used in an outlet
valve, such as the
outlet valve 56 or any other outlet valve. In such embodiments, the operation
of the pump assembly 10
with the valve member 294 is substantially identical to the operation of the
pump assembly 10 with the
valve member 230, as discussed above with regard to Figures 15-18, except for
the operation of the
rupture disc assembly 296. In operation, with reference to Figures 1-21, fluid
in the pressure chamber 36
5 flows along the fluid passage axis 42 and through the fluid passage 40
and the outlet valve 56, and into
the fluid outlet passages 40 and 24. A fluid pressure is exerted on the
rupture disc 301 of the rupture disc
assembly 296 in at least an axial direction generally downwards from the fluid
outlet passage 40 and/or
the fluid outlet passage 24 along the fluid passage axis 42. The sealing
engagement between the one or
more annular seals 308 and at least the mounting portion 302 and the internal
shoulder 300, prevents, or at
) least resists, the fluid from flowing around the rupture disc 300, and
thus into the fluid passage 299 and
back into at least the pressure chamber 36. In an exemplary embodiment, the
outlet valve 56 is in its
closed position and thus the sealing engagement of the seal 256 and the
surface 96 also prevents, or at
least resists, the fluid from flowing around the seal 256 and back into at
least the pressure chamber 36. If
the fluid pressure exerted on the rupture disc 301 reaches or exceeds a
predetermined pressure value,
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causing a predetermined pressure differential across the rupture disc 301, the
rupture portion 304 of the
rupture disc 301 ruptures. As a result, the fluid passage 299 is in fluid
communication with the fluid
outlet passage 40, and the rupture disc assembly 296 permits fluid to flow
from the fluid outlet passage 40
and/or the fluid outlet passage 24, through the rupture disc assembly 296 and
thus back into at least the
pressure chamber 36. This fluid flow reduces or relieves the pressure within
the pump assembly 10.
During operation, in several exemplary embodiments, after the rupture disc 301
ruptures, the diameter of
the rupture portion 304 is less than the reduced-diameter portion 298a of the
counterbore 298 thus
increasing the likelihood that shrapnel from the ruptured rupture disc 301
will flow downward and out of
the counterbore 298 without creating a pressure spike.
As a result, the rupture disc assembly 296, whether in use in an inlet valve
or an outlet valve, such
as inlet valve 150 and/or outlet valve 56, or any other inlet and/or outlet
valve, operates to relieve pressure
within the pump assembly 10, preventing a further increase in pressure so as
to prevent or otherwise
substantially reduce the likelihood of damage to the pump assembly 10, one or
more other components of
the pump assembly, and/or any system(s) and/or component(s) in fluid
communication therewith.
5 In an exemplary embodiment, as illustrated in Figures 22-25, a valve
member is generally
referred to by the reference numeral 310 and includes several parts that arc
identical to corresponding
parts of the valve member 230, which identical parts are given the same
reference numerals. In several
exemplary embodiments, the components of the valve member 310 are sized such
that the valve member
310 is sized and adapted for use in larger inlet valves and outlet valves
and/or larger fluid passages. For
) example, in several exemplary embodiments, the dimensions of parts of the
valve member 310 are greater
than the dimensions of the corresponding parts of the valve member 230. In an
exemplary embodiment,
the respective radii of the channels 268 and 260 are increased. In an
exemplary embodiment, other
dimensions are adjusted such as, for example, the height of the protrusion
254, the diameter of the seal
256, and the diameter of the valve body 236. In several exemplary embodiments,
the height of the valve
5 member 310 is greater than the height of the valve member 230.
The valve member 310 includes a plurality of circumferentially-spaced legs 312
extending from
the base 232 and away from the valve body 236. In an exemplary embodiment, the
legs 312 are larger
than the legs 280 of Figures 15-21. For example, the legs 312 may be longer in
length, thicker in width,
and/or greater in diameter than the legs 280. In an exemplary embodiment, the
legs 312 are adapted to
) slidably engage an inside surface of a larger seat body than, for
example, the seat body 80 of Figure 10.
In an exemplary embodiment, the legs 312 are sized to slidably engage a seat
body having an inner
diameter of about 3.13 inches. In an exemplary embodiment, the legs 312 are
sized to slidably engage a
seat body having an inner diameter ranging in size from about 3 inches to
about 4 inches. In an exemplary
embodiment, the legs 312 are sized to slidably engage a seat body having an
inner diameter ranging in
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39
size from about 3 inches to about 5 inches. In several exemplary embodiments,
the various dimensions,
including at least the radii, diameter, length, and/or height of the
components of the valve member 310 are
adjusted such that the valve member 310 is configured for use in valve seats
and fluid passages having
increased dimensions. For example, in an exemplary embodiment, the valve
member 310 is configured
for use with an SPM SP5 full open well service seat.
In several exemplary embodiments, the valve body 236 defines a step 313 at the
intersection of'
the fnisto-conical surface 278 of the valve body 236 with the frusto-conical
surface 272 of the seal 256.
During the operation of the valve member 310, the step 313 prevents, or at
least reduces, bulging of the
seal 156 into the region between the frusto-conical surface 278 and the
tapered surface 96 of the scat body
) 80.
In an exemplary embodiment, the operation of the valve member 310 is
substantially identical to
the operation of the valve member 230 and therefore will not be described in
detail.
In an exemplary embodiment, as illustrated in Figures 26-28, a valve member is
generally
referred to by the reference numeral 314 and includes several parts that are
identical to corresponding
5 parts of the valve member 310, which identical parts are given the same
reference numerals. The valve
member 314 also includes a rupture disc assembly 316, which includes several
parts that are identical to
corresponding parts of the rupture disc assembly 296 of the valve member 294,
which parts are given the
same reference numerals, except that the corresponding parts of the rupture
disc assembly 316 are sized in
accordance with the increased dimensions of the valve member 314, as discussed
above. The rupture disc
) assembly 316 therefore will not be described in further detail.
In an exemplary embodiment, the operation of the valve member 314 is
substantially identical to
the operation of the valve member 294 and therefore the operation of the valve
member 314 will not be
described in further detail.
In an exemplary embodiment, as illustrated in Figure 29, the frusto-conical
surface 272 of the seal
5 256 is omitted in favor of a pair of frusto-conical surfaces 272a and
272b. The frusto-conical surface
272a extends angularly downward from the frusto-conical surface 270 (not
visible in Figure 29). Thus,
the annular contact portion 274 is defined at the intersection between the
frusto-conical surface 270 and
the fnisto-conical surface 272a. Similarly, the frusto-conical surface 272b
extends angularly downward
from the fnisto-conical surface 272a ending at, or proximate, the frusto-
conical surface 278 of the valve
) body 236. An annular inflection portion 318 is defined at the
intersection between the frusto-conical
surface 272a and the frusto-conical surface 272b.
An angle 320 is defined between the frusto-conical surface 272a and the frusto-
conical surface
278 of the valve body 236. In an exemplary embodiment, the angle 320 is about
12.5 degrees. In an
exemplary embodiment, the angle 320 ranges from about 0 degrees to about 25
degrees. In an exemplary
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embodiment, the angle 320 ranges from about 5 degrees to about 20 degrees. In
an exemplary
embodiment, the angle 320 ranges from about 10 degrees to about 15 degrees. An
angle (not shown) is
defined by the frusto-conical surface 272b of the seal 256. The angle defined
by the fnisto-conical
surface 272b may be measured from the valve member axis 237. In an exemplary
embodiment, the angle
5 defined by the frusto-conical surface 272b is substantially equal to the
angle 282 (shown in Figure 25)
defined by the frusto-conical surface 278 when measured from the valve member
axis 237.
As indicated by the reference numeral D2, the frusto-conical surface 272b
extends for a distance
D2 beyond the fmsto-conical surface 278 of the valve body 236. Thus, the
annular inflection portion 318
is spaced from the frusto-conical surface by the distance D,. In an exemplary
embodiment, the
) configuration of the seal 256 (i.e., the frusto-conical surfaces 272a and
272b and the annular inflection
portion 318) provides improved manufacturing characteristics.
In an exemplary embodiment, as illustrated in Figure 30, the circumferentially-
extending upper
tab 264 of the seal 256 defines a concave annular surface 322 positioned above
the annular channel 268
(as viewed in Figure 30) and adjoining the top surface 266. The concave
annular surface 322 extends
5 vertically for a distance D3 between the top surface 266 and the annular
channel 268. In another
exemplary embodiment, the circumferentially-extending upper tab 218 of the
seal 184 includes the
concave annular surface 322. In an exemplary embodiment, the configuration of
the seal 256 (i.e., the
concave annular surface 322) provides improved manufacturing characteristics.
In several exemplary embodiments, the valves 54, 56, 128, and 150, or the
components thereof,
) such as the valve seats 76, 129, and 152 and the valve members 78, 154,
230, 294, 310, and 314 may be
configured to operate in the presence of highly abrasive fluids, such as
drilling mud, and at relatively high
pressures, such as at pressures of up to about 15,000 psi or greater. In
several exemplary embodiments,
instead of, or in addition to being used in reciprocating pumps, the valves
54, 56, 128, and 150, or the
components thereof, such as the valve seats 76, 129, and 152 and the valve
members 78, 154, 230, 294,
5 310, and 314, may be used in other types of pumps and fluid systems.
Correspondingly, instead of, or in
addition to being used in reciprocating pumps, the fluid end block 18 or
features thereof may be used in
other types of pumps and fluid systems.
In several exemplary embodiments, while different steps, processes, and
procedures are described
as appearing as distinct acts, one or more of the steps, one or more of the
processes, and/or one or more of
) the procedures may also be performed in different orders, simultaneously
and/or sequentially. In several
exemplary embodiments, the steps, processes and/or procedures may be merged
into one or more steps,
processes and/or procedures.
In several exemplary embodiments, one or more of the operational steps in each
embodiment may
be omitted. Moreover, in some instances, some features of the present
disclosure may be employed
CA 02991124 2017-12-29
WO 2017/004572 PCT/US2016/040802
41
without a corresponding use of the other features. Moreover, one or more of
the above-described
embodiments and/or variations may be combined in whole or in part with any one
or more of the other
above-described embodiments and/or variations.
In the foregoing description of certain embodiments, specific terminology has
been resorted to for
the sake of clarity. However, the disclosure is not intended to be limited to
the specific terms so selected,
and it is to be understood that each specific tenn includes other technical
equivalents which operate in a
similar manner to accomplish a similar technical purpose. Terms such as "left"
and right", "front" and
"rear", "above" and "below" and the like are used as words of convenience to
provide reference points
and arc not to be construed as limiting terms.
In this specification, the word "comprising" is to be understood in its "open"
sense, that is, in the
sense of "including", and thus not limited to its "closed" sense, that is the
sense of "consisting only of'.
A corresponding meaning is to be attributed to the corresponding words
"comprise". "comprised" and
"comprises" where they appear.
In addition, the foregoing describes only some embodiments of the
invention(s), and alterations,
5 modifications, additions and/or changes can be made thereto without
departing from the scope and spirit
of the disclosed embodiments, the embodiments being illustrative and not
restrictive.
Furthermore, invention(s) have described in connection with what are presently
considered to be
the most practical and preferred embodiments, it is to be understood that the
invention is not to be limited
to the disclosed embodiments, but on the contrary, is intended to cover
various modifications and
) equivalent arrangements included within the spirit and scope of the
invention(s). Also, the various
embodiments described above may be implemented in conjunction with other
embodiments, e.g., aspects
of one embodiment may be combined with aspects of another embodiment to
realize yet other
embodiments. Further, each independent feature or component of any given
assembly may constitute an
additional embodiment.
5
