U.S. patent application number 13/756715 was filed with the patent office on 2013-08-08 for pump fluid cylinder including load transfer shoulder and valve seat for same.
The applicant listed for this patent is S.P.M. FLOW CONTROL, INC.. Invention is credited to Jacob A. Bayyouk, Joseph H. Byrne, Mark Christopher Dille.
Application Number | 20130202458 13/756715 |
Document ID | / |
Family ID | 48903045 |
Filed Date | 2013-08-08 |
United States Patent
Application |
20130202458 |
Kind Code |
A1 |
Byrne; Joseph H. ; et
al. |
August 8, 2013 |
PUMP FLUID CYLINDER INCLUDING LOAD TRANSFER SHOULDER AND VALVE SEAT
FOR SAME
Abstract
According to one aspect, a pump assembly includes a fluid
cylinder, and the fluid cylinder includes a fluid passage that
defines a tapered internal shoulder of the fluid cylinder. The
tapered internal shoulder defines a first frusto-conical surface. A
valve controls flow of fluid through the fluid passage. The valve
includes a valve seat, which includes a seat body disposed in the
fluid passage, and a bore formed through the seat body and through
which fluid flows. The seat body includes inlet and outlet end
portions, wherein the fluid flows into the bore at the inlet end
portion and flows out of the bore at the outlet end portion. The
inlet end portion of the seat body defines a second frusto-conical
surface. In one embodiment, the second frusto-conical surface
engages the first frusto-conical surface to distribute and transfer
loading.
Inventors: |
Byrne; Joseph H.; (Hudson
Oaks, TX) ; Dille; Mark Christopher; (Fort Worth,
TX) ; Bayyouk; Jacob A.; (Richardson, TX) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
S.P.M. FLOW CONTROL, INC.; |
Fort Worth |
TX |
US |
|
|
Family ID: |
48903045 |
Appl. No.: |
13/756715 |
Filed: |
February 1, 2013 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
61594493 |
Feb 3, 2012 |
|
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|
Current U.S.
Class: |
417/279 |
Current CPC
Class: |
F04B 7/02 20130101; F04B
53/162 20130101; F04B 53/10 20130101 |
Class at
Publication: |
417/279 |
International
Class: |
F04B 7/02 20060101
F04B007/02 |
Claims
1. A pump assembly, comprising: a fluid cylinder having a first
axis and a second axis perpendicular thereto, the fluid cylinder
comprising a first fluid passage through which fluid flows along
the first axis, the first fluid passage defining a first tapered
internal shoulder of the fluid cylinder, the first tapered internal
shoulder defining a first frusto-conical surface, the first
frusto-conical surface defining a first angle from the second axis;
and a first valve to control flow of fluid through the first fluid
passage, the first valve comprising a first valve seat disposed in
the first fluid passage, the first valve seat comprising: a seat
body comprising an inlet end portion and an outlet end portion
opposed thereto along the first axis, the inlet end portion of the
seat body defining a second frusto-conical surface, the second
frusto-conical surface defining a second angle from the second
axis; and a bore formed through the seat body and through which
fluid flows in a direction along the first axis and perpendicular
to the second axis; wherein the fluid flows into the bore at the
inlet end portion of the seat body and flows out of the bore at the
outlet end portion of the seat body; wherein each of the first and
second angles ranges from about 10 degrees to about 45 degrees
measured from the second axis; and wherein the second
frusto-conical surface of the inlet end portion engages the first
frusto-conical surface of the fluid cylinder to distribute and
transfer loading between the second and first frusto-conical
surfaces.
2. The pump assembly of claim 1, wherein the second axis intersects
the seat body at an intersection, the intersection defining a first
diameter of the seat body; wherein the seat body defines an
axially-extending outside surface extending along the first axis
from the inlet end portion to the outlet end portion, the
axially-extending outside surface defining a second diameter of the
seat body; wherein the second diameter of the seat body is greater
than the first diameter of the seat body; and wherein the second
frusto-conical surface extends between the intersection and the
axially-extending outside surface.
3. The pump assembly of claim 2, wherein the second frusto-conical
surface extends from the intersection to the outside surface in an
angular direction, an axial component of which extends axially
towards the outlet end portion.
4. The pump assembly of claim 3, wherein the inlet end portion of
the seat body defines an end surface that faces axially away from
the outlet end portion; wherein the second axis is coplanar with
the end surface; and wherein the second frusto-conical surface
extends from the end surface to the outside surface.
5. The pump assembly of claim 3, wherein the inlet end portion
comprises an annular portion that extends from the intersection in
an axial direction away from the outlet end portion.
6. The pump assembly of claim 2, wherein the second frusto-conical
surface extends from the intersection to the outside surface in an
angular direction, an axial component of which extends axially away
from the outlet end portion.
7. The pump assembly of claim 6, wherein the inlet end portion
comprises an annular portion that extends from the intersection in
an axial direction away from the outlet end portion.
8. The pump assembly of claim 1, wherein the fluid passage
comprises: a first passage portion defining a first inside diameter
of the fluid cylinder; and a second passage portion defining a
second inside diameter of the fluid cylinder; wherein the second
inside diameter is less than the first inside diameter; wherein the
valve seat body is disposed in the second passage portion; and
wherein at least a portion of the second passage portion is
positioned along the first axis between the first passage portion
and the first tapered internal shoulder.
9. A valve seat adapted to be disposed within a fluid cylinder of a
pump assembly, the valve seat having a first axis and a second axis
perpendicular thereto, the valve seat comprising: a seat body
comprising an inlet end portion and an outlet end portion opposed
thereto along the first axis, the inlet end portion of the seat
body defining a frusto-conical surface, the frusto-conical surface
defining an angle from the second axis; and a bore formed through
the seat body and through which fluid flows in a direction along
the first axis and perpendicular to the second axis; wherein the
fluid flows into the bore at the inlet end portion of the seat body
and flows out of the bore at the outlet end portion of the seat
body; and wherein the angle ranges from about 10 degrees to about
45 degrees measured from the second axis.
10. The valve seat of claim 9, wherein the second axis intersects
the seat body at an intersection, the intersection defining a first
diameter of the seat body; wherein the seat body defines an
axially-extending outside surface extending along the first axis
from the inlet end portion to the outlet end portion, the
axially-extending outside surface defining a second diameter of the
seat body; wherein the second diameter of the seat body is greater
than the first diameter of the seat body; and wherein the
frusto-conical surface extends between the intersection and the
axially-extending outside surface.
11. The valve seat of claim 10, wherein the frusto-conical surface
extends from the intersection to the outside surface in an angular
direction, an axial component of which extends axially towards the
outlet end portion.
12. The valve seat of claim 11, wherein the inlet end portion of
the seat body defines an end surface that faces axially away from
the outlet end portion; wherein the second axis is coplanar with
the end surface; and wherein the frusto-conical surface extends
from the end surface to the outside surface.
13. The valve seat of claim 11, wherein the inlet end portion
comprises an annular portion that extends from the intersection in
an axial direction away from the outlet end portion.
14. The valve seat of claim 10, wherein the frusto-conical surface
extends from the intersection to the outside surface in an angular
direction, an axial component of which extends axially away from
the outlet end portion.
15. The valve seat of claim 14, wherein the inlet end portion
comprises an annular portion that extends from the intersection in
an axial direction away from the outlet end portion.
16. A fluid cylinder for a pump assembly, the fluid cylinder having
a first axis and a second axis perpendicular thereto, the fluid
cylinder comprising: a first fluid passage in which a first valve
is adapted to be disposed and through which fluid flows along the
first axis, the fluid passage comprising: a first passage portion
defining a first inside diameter of the fluid passage; and a second
passage portion extending from the first passage portion, the
second passage portion defining a second inside diameter of the
fluid passage; wherein the second inside diameter is less than the
first inside diameter; a tapered internal shoulder defined by the
fluid passage, the tapered internal shoulder defining a
frusto-conical surface, the frusto-conical surface defining an
angle from the second axis; wherein the angle ranges from about 10
degrees to about 45 degrees measured from the second axis; and
wherein at least a portion of the second passage portion is
positioned along the first axis between the first passage portion
and the first tapered internal shoulder; and a pressure chamber in
fluid communication with the first fluid passage.
17. The fluid cylinder of claim 16, wherein the second axis
intersects the fluid passage at an intersection, the intersection
defining a third diameter of the fluid passage; wherein the second
passage portion defines an axially-extending cylindrical inside
surface extending along the first axis, the axially-extending
cylindrical inside surface having the second diameter; wherein the
second diameter of the fluid passage is greater than the third
diameter of the fluid passage; and wherein the frusto-conical
surface extends between the intersection and the axially-extending
cylindrical inside surface.
18. The fluid cylinder of claim 17, wherein the frusto-conical
surface extends from the intersection to the cylindrical inside
surface in an angular direction, an axial component of which
extends axially towards the first passage portion.
19. The valve seat of claim 10, wherein the frusto-conical surface
extends from the intersection to the outside surface in an angular
direction, an axial component of which extends axially away from
the outlet end portion.
20. The valve seat of claim 16, further comprising: a second fluid
passage in which a second valve is adapted to be disposed and
through which fluid flows along the first axis; and a fluid outlet
passage in fluid communication with the pressure chamber via the
second fluid passage.
Description
CROSS-REFERENCE TO RELATED APPLICATION
[0001] This application claims the benefit of the filing date of
U.S. provisional patent application No. 61/594,493, filed Feb. 3,
2012, the entire disclosure of which is incorporated herein by
reference.
TECHNICAL FIELD
[0002] This disclosure relates in general to pump assemblies and,
in particular, a reciprocating pump assembly including a fluid
cylinder and valve seats.
BACKGROUND OF THE DISCLOSURE
[0003] Reciprocating pump assemblies typically include fluid end
blocks or fluid cylinders 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 portions of the fluid
cylinder engaged therewith, may be subjected to highly concentrated
cyclic loads and thus may fatigue to failure. Therefore, what is
needed is an apparatus or method that addresses one or more of the
foregoing issues, among others.
SUMMARY
[0004] In a first aspect, there is provided a pump assembly that
includes a fluid cylinder having a first axis and a second axis
perpendicular thereto. The fluid cylinder includes a first fluid
passage through which fluid flows along the first axis, the first
fluid passage defining a first tapered internal shoulder of the
fluid cylinder, the first tapered internal shoulder defining a
first frusto-conical surface, the first frusto-conical surface
defining a first angle from the second axis; The pump assembly
further includes a first valve to control flow of fluid through the
first fluid passage. The first valve includes a first valve seat
disposed in the first fluid passage. The first valve seat includes
a seat body that includes an inlet end portion and an outlet end
portion opposed thereto along the first axis, the inlet end portion
of the seat body defining a second frusto-conical surface, the
second frusto-conical surface defining a second angle from the
second axis; and a bore formed through the seat body and through
which fluid flows in a direction along the first axis and
perpendicular to the second axis; wherein the fluid flows into the
bore at the inlet end portion of the seat body and flows out of the
bore at the outlet end portion of the seat body; wherein each of
the first and second angles ranges from about 10 degrees to about
45 degrees measured from the second axis; and wherein the second
frusto-conical surface of the inlet end portion engages the first
frusto-conical surface of the fluid cylinder to distribute and
transfer loading between the second and first frusto-conical
surfaces.
[0005] In an exemplary embodiment, the second axis intersects the
seat body at an intersection, the intersection defining a first
diameter of the seat body; wherein the seat body defines an
axially-extending outside surface extending along the first axis
from the inlet end portion to the outlet end portion, the
axially-extending outside surface defining a second diameter of the
seat body; wherein the second diameter of the seat body is greater
than the first diameter of the seat body; and wherein the second
frusto-conical surface extends between the intersection and the
axially-extending outside surface.
[0006] In certain exemplary embodiments, the second frusto-conical
surface extends from the intersection to the outside surface in an
angular direction, an axial component of which extends axially
towards the outlet end portion.
[0007] In another exemplary embodiment, the inlet end portion of
the seat body defines an end surface that faces axially away from
the outlet end portion; wherein the second axis is coplanar with
the end surface; wherein the second frusto-conical surface extends
from the end surface to the outside surface.
[0008] In certain exemplary embodiments, the inlet end portion
includes an annular portion that extends from the intersection in
an axial direction away from the outlet end portion.
[0009] In an exemplary embodiment, the second frusto-conical
surface extends from the intersection to the outside surface in an
angular direction, an axial component of which extends axially away
from the outlet end portion.
[0010] In another exemplary embodiment, the inlet end portion
includes an annular portion that extends from the intersection in
an axial direction away from the outlet end portion.
[0011] In yet another exemplary embodiment, the fluid passage
includes a first passage portion defining a first inside diameter
of the fluid cylinder; and a second passage portion defining a
second inside diameter of the fluid cylinder; wherein the second
inside diameter is less than the first inside diameter; wherein the
valve seat body is disposed in the second passage portion; and
wherein at least a portion of the second passage portion is
positioned along the first axis between the first passage portion
and the first tapered internal shoulder.
[0012] In a second aspect, there is provided a valve seat adapted
to be disposed within a fluid cylinder of a pump assembly. The
valve seat has a first axis and a second axis perpendicular
thereto. The valve seat includes a seat body that includes an inlet
end portion and an outlet end portion opposed thereto along the
first axis, the inlet end portion of the seat body defining a
frusto-conical surface, the frusto-conical surface defining an
angle from the second axis; and a bore formed through the seat body
and through which fluid flows in a direction along the first axis
and perpendicular to the second axis; wherein the fluid flows into
the bore at the inlet end portion of the seat body and flows out of
the bore at the outlet end portion of the seat body; and wherein
the angle ranges from about 10 degrees to about 45 degrees measured
from the second axis.
[0013] In certain exemplary embodiments, the second axis intersects
the seat body at an intersection, the intersection defining a first
diameter of the seat body; wherein the seat body defines an
axially-extending outside surface extending along the first axis
from the inlet end portion to the outlet end portion, the
axially-extending outside surface defining a second diameter of the
seat body; wherein the second diameter of the seat body is greater
than the first diameter of the seat body; and wherein the
frusto-conical surface extends between the intersection and the
axially-extending outside surface.
[0014] In an exemplary embodiment, the frusto-conical surface
extends from the intersection to the outside surface in an angular
direction, an axial component of which extends axially towards the
outlet end portion.
[0015] In another exemplary embodiment, the inlet end portion of
the seat body defines an end surface that faces axially away from
the outlet end portion; wherein the second axis is coplanar with
the end surface; and wherein the frusto-conical surface extends
from the end surface to the outside surface.
[0016] In yet another exemplary embodiment, the inlet end portion
includes an annular portion that extends from the intersection in
an axial direction away from the outlet end portion.
[0017] In certain exemplary embodiments, the frusto-conical surface
extends from the intersection to the outside surface in an angular
direction, an axial component of which extends axially away from
the outlet end portion.
[0018] In another exemplary embodiment, the inlet end portion
includes an annular portion that extends from the intersection in
an axial direction away from the outlet end portion.
[0019] In a third aspect, there is provided a fluid cylinder for a
pump assembly, and the fluid cylinder has a first axis and a second
axis perpendicular thereto. The fluid cylinder includes a first
fluid passage in which a first valve is adapted to be disposed and
through which fluid flows along the first axis. The fluid passage
includes a first passage portion defining a first inside diameter
of the fluid passage; and a second passage portion extending from
the first passage portion, the second passage portion defining a
second inside diameter of the fluid passage; wherein the second
inside diameter is less than the first inside diameter. A tapered
internal shoulder is defined by the fluid passage, the tapered
internal shoulder defining a frusto-conical surface, the
frusto-conical surface defining an angle from the second axis;
wherein the angle ranges from about 10 degrees to about 45 degrees
measured from the second axis; and wherein at least a portion of
the second passage portion is positioned along the first axis
between the first passage portion and the first tapered internal
shoulder. A pressure chamber is in fluid communication with the
first fluid passage.
[0020] In an exemplary embodiment, the second axis intersects the
fluid passage at an intersection, the intersection defining a third
diameter of the fluid passage; wherein the second passage portion
defines an axially-extending cylindrical inside surface extending
along the first axis, the axially-extending cylindrical inside
surface having the second diameter; wherein the second diameter of
the fluid passage is greater than the third diameter of the fluid
passage; and wherein the frusto-conical surface extends between the
intersection and the axially-extending cylindrical inside
surface.
[0021] In another exemplary embodiment, the frusto-conical surface
extends from the intersection to the cylindrical inside surface in
an angular direction, an axial component of which extends axially
towards the first passage portion.
[0022] In certain exemplary embodiments, the frusto-conical surface
extends from the intersection to the outside surface in an angular
direction, an axial component of which extends axially away from
the outlet end portion.
[0023] In other exemplary embodiments, the fluid cylinder includes
a second fluid passage in which a second valve is adapted to be
disposed and through which fluid flows along the first axis; and a
fluid outlet passage in fluid communication with the pressure
chamber via the second fluid passage.
[0024] 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.
DESCRIPTION OF FIGURES
[0025] The accompanying drawings facilitate an understanding of the
various embodiments.
[0026] FIG. 1 is an elevational view of a reciprocating pump
assembly according to an exemplary embodiment, and the pump
assembly includes a fluid cylinder assembly.
[0027] FIG. 2 is a sectional view of the fluid cylinder assembly of
FIG. 1 according to an exemplary embodiment, the fluid cylinder
assembly includes a fluid cylinder and inlet and outlet valves, and
each of the inlet and outlet valves includes a valve seat.
[0028] FIG. 3 is an enlarged view of a portion of the section view
of FIG. 2, according to an exemplary embodiment.
[0029] FIG. 4 is a partial sectional view of respective portions of
the valve seat and the fluid cylinder, according to another
exemplary embodiment.
[0030] FIG. 5 is a partial sectional view of respective portions of
the valve seat and fluid cylinder, according to yet another
exemplary embodiment.
[0031] FIG. 6 is a partial sectional view of respective portions of
the valve seat and fluid cylinder, according to still yet another
exemplary embodiment.
DETAILED DESCRIPTION
[0032] In an exemplary embodiment, as illustrated in FIG. 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 or fluid cylinder
18, which is connected to the housing 16 via a plurality of stay
rods 20. The fluid cylinder 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 FIG. 1, is connected to the fluid cylinder 18 opposite the stay
rods 20. A plurality of cover assemblies 28, one of which is shown
in FIG. 1, is connected to the fluid cylinder 18 opposite the fluid
inlet passage 22. A plunger rod assembly 30 extends out of the
housing 16 and into the fluid cylinder 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.
[0033] In an exemplary embodiment, as illustrated in FIG. 2 with
continuing reference to FIG. 1, the plunger rod assembly 30
includes a plunger 32, which extends through a bore 34 formed in
the fluid cylinder 18, and into a pressure chamber 36 formed in the
fluid cylinder 18. In several exemplary embodiments, a plurality of
parallel-spaced bores may be formed in the fluid cylinder 18, with
one of the bores being the bore 34, a plurality of pressure
chambers may be formed in the fluid cylinder 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.
[0034] As shown in FIG. 2, the fluid cylinder 18 includes inlet and
outlet fluid passages 38 and 40 formed therein, which are generally
coaxial along an 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 38b extending downward therefrom
(the diameter of the enlarged-diameter portion 38a is greater than
the diameter of the reduced-diameter portion 38b). The fluid inlet
passage 38 defines a tapered internal shoulder 43 so that the
reduced-diameter portion 38b is positioned along the axis 42
between the enlarged diameter portion 38a and the tapered internal
shoulder 43. The tapered internal shoulder 43 defines a
frusto-conical surface 44 of the fluid cylinder 18. The
reduced-diameter portion 38b defines an inside surface 46 of the
fluid cylinder 18, the inside surface 46 having the diameter of the
reduced-diameter portion 38b. Similarly, the fluid outlet passage
40 includes an enlarged-diameter portion 40a and a reduced-diameter
portion 40b extending downward therefrom. The fluid outlet passage
40 defines a tapered internal shoulder 48 so that the
reduced-diameter 40b is axially positioned between the
enlarged-diameter portion 40a and the tapered internal shoulder 48.
The tapered internal shoulder 48 defines a frusto-conical surface
50 of the fluid cylinder 18. The reduced-diameter portion 40b
defines an inside surface 52 of the fluid cylinder 18.
[0035] An inlet valve assembly, or 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
assembly, or 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.
[0036] A counterbore 58 is formed in the fluid cylinder 18, and is
generally coaxial with the 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 cylinder 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
cylinder 18 may include a plurality of parallel-spaced
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 cylinder 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.
[0037] 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
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 FIGS. 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 cylinder 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 cylinder 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.
[0038] 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 maybe 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 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 FIGS. 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 cylinder 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 cylinder 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 68, and a plurality of fasteners, one of which is the
fastener 70, with the respective quantities of plugs and fasteners
equaling the quantity of plunger throws included in the pump
assembly 10.
[0039] 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 FIG. 2, the valve spring retainer 72 is connected to the plug 68
via a hub 74, which is generally coaxial with the axis 62.
[0040] In an exemplary embodiment, as illustrated in FIG. 3 with
continuing reference to FIGS. 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 inlet end portion 81 and
an outlet end portion 82. The seat body 80 is disposed in the
reduced-diameter portion 38b of the fluid passage 38. A bore 83 is
formed through the seat body 80 and is coaxial with an axis 84,
which is aligned with the axis 42 when the inlet valve 54 is
disposed in the fluid passage 38, as shown in FIG. 3. The outlet
end portion 82 is axially opposed to the inlet end portion 81 along
the axis 84 and thus along the axis 42. 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. In an exemplary embodiment, the outside surface 86 may
be cylindrical. In an exemplary embodiment, the outside surface 86
may be slightly conical. A sealing element, such as an o-ring, may
be disposed in an annular groove formed in the outside surface 86,
and the o-ring may sealingly engage the inside surface 46. The
fluid cylinder 18 and valve seat 76 have axes 88 and 90,
respectively. The axes 88 and 90 are coaxial when the inlet valve
54 is disposed in the fluid passage 38, as shown in FIG. 3. The
axes 88 and 90 are perpendicular to the axes 42 and 84,
respectively.
[0041] A frusto-conical surface 91 is defined by the inlet end
portion 81 of the seat body 80. The frusto-conical surface 91
defines an angle 92 from the axis 90 and thus also from the axis
88. Similarly, the frusto-conical surface 44 defines an angle 93
from the axis 88 and thus also from the axis 90. In an exemplary
embodiment, each of the angles 92 and 93 ranges from about 10
degrees to about 45 degrees measured from the aligned axes 88 and
90. In an exemplary embodiment, each of the angles 92 and 93 ranges
from about 15 degrees to about 45 degrees measured from the aligned
axes 88 and 90. In an exemplary embodiment, the angles 92 and 93
are equal as measured from the aligned axes 88 and 90. In an
exemplary embodiment, each of the angles 92 and 93 is about 30
degrees measured from the aligned axes 88 and 90. In an exemplary
embodiment, the angles 92 and 93 are not equal as measured from the
aligned axes 88 and 90. An end surface 94 is defined by inlet end
portion 81 of the seat body 80. The end surface 94 faces axially
away from the outlet end portion 82. The end surface 94 is coplanar
with the aligned axes 88 and 90. The frusto-conical surface 91
extends from the intersection between the seat body 80 and the
aligned axes 88 and 90, which intersection corresponds to the end
surface 94, to the outside surface 86 in an angular direction, an
axial component of which extends axially towards the outlet end
portion 82. Likewise, the frusto-conical surface 44 extends from
the intersection between the fluid passage 38 and the aligned axes
88 and 90, and to the inside surface 46 in an angular direction, an
axial component of which extends axially towards the
enlarged-diameter portion 38a.
[0042] A diameter 95a is defined by the intersection between the
seat body 80 and the aligned axes 88 and 90; similarly, a diameter
of the fluid passage 38 generally corresponding, or about equal, to
the diameter 95a is defined by the intersection between the fluid
passage 38 and the aligned axes 88 and 90. A diameter 95b is
defined by the outside surface 86; the diameter of the
reduced-diameter portion 38b of the fluid passage 38 generally
corresponds, or is about equal, to the diameter 95b. The diameter
95b is greater than the diameter 95a.
[0043] The outlet end portion 82 defines a tapered surface 96,
which extends angularly upward from the inside surface 85. In an
exemplary embodiment, the tapered surface 96 extends at an angle
relative to the aligned axes 42 and 84, which angle ranges from
about 15 degrees to about 45 degrees.
[0044] 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 seat body 80 engages the inside surface
46 of the fluid cylinder 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. As noted above, a
sealing element, such as an o-ring, may be disposed in an annular
groove formed in the outside surface 86, and the o-ring may
sealingly engage the inside surface 46.
[0045] 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, 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 the valve body 100 opposite the central
stem 98. As shown in FIG. 2, the upper end portion of the spring
108 is engaged with the valve spring retainer 72. The valve member
78 is movable, relative to the valve seat 76 and thus the fluid
cylinder 18, between a closed position (shown in FIG. 3) and an
open position (not shown), under conditions to be described
below.
[0046] 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 104 is composed
of at least a fiber-reinforced material, which can prevent or at
least reduce delamination. In an exemplary embodiment, the seal 104
has a hardness of 95 A durometer or greater, or a hardness of 69 D
durometer or greater. In another exemplary embodiment, the seal 104
has a hardness of 95 A durometer or lesser. In several exemplary
embodiments, the valve body 100 is much harder and more rigid than
the seal 104.
[0047] 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 outlet valve 56 is disposed in the fluid
passage 40, and engages the fluid cylinder 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 the fluid cylinder 18, with one
exception involving 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.
[0048] In operation, in an exemplary embodiment, with continuing
reference to FIGS. 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 FIG.
2, away from and towards the 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.
[0049] 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 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 FIGS. 2 and 3, relative to the valve seat 76 and the
fluid cylinder 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
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 into the bore 83 at the inlet end portion
81, through the bore 83 and along the aligned axes 42 and 84, and
out of the bore 83 at the outlet end portion 82. During this time,
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 axis 42. At
this point, the differential pressure across the inlet valve 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
FIGS. 2 and 3, relative to the valve seat 76 and the fluid cylinder
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.
[0050] As the plunger 32 moves into the pressure chamber 36 and
thus towards the 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 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 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.
[0051] 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.
[0052] In an exemplary embodiment, during the above-described
operation of the reciprocating pump assembly 10, the taper of each
of the surfaces 44 and 91 balances the loading forces applied
thereagainst. In an exemplary embodiment, the loading is
distributed across the surfaces 44 and 91, reducing stress
concentrations.
[0053] In an exemplary embodiment, as illustrated in FIG. 4 with
continuing reference to FIGS. 1-3, the end surface 94 is omitted
from the inlet end portion 81. Instead, the inlet end portion 81
includes an annular portion 108 that extends from the intersection
between the seat body 80 and the aligned axes 88 and 90 in an axial
direction away from the outlet end portion 82. An end surface 110
is defined by the annular portion 108 of the inlet end portion 81.
The end surface 110 faces axially away from the outlet end portion
82. In an exemplary embodiment, the operation of the pump assembly
10 with the exemplary embodiment of the valve seat 76 illustrated
in FIG. 4 is identical to the operation of the pump assembly 10
with the exemplary embodiment of the valve seat 76 illustrated in
FIG. 3. The annular portion 108 facilitates the removal of the
valve seat 76 from the fluid cylinder 18.
[0054] In an exemplary embodiment, as illustrated in FIG. 5 with
continuing reference to FIGS. 1-4, the tapered internal shoulder 43
and the frusto-conical surface 44 are omitted. Instead, the fluid
inlet passage 38 defines a tapered internal shoulder 43' so that
the majority of the reduced-diameter portion 38b is axially
positioned between the enlarged diameter portion 38a and the
tapered internal shoulder 43'. The tapered internal shoulder 43'
defines a frusto-conical surface 44' of the fluid cylinder 18. The
frusto-conical surface 91 is omitted in favor of a frusto-conical
surface 91', which is defined by the inlet end portion 81 of the
seat body 80. The frusto-conical surface 91' extends from the
intersection between the seat body 80 and the aligned axes 88 and
90, and to the outside surface 86 in an angular direction, an axial
component of which extends axially away the outlet end portion 82.
Likewise, the frusto-conical surface 44' extends from the
intersection between the fluid passage 38 and the aligned axes 88
and 90, and to the inside surface 46 in an angular direction, an
axial component of which extends away from the enlarged-diameter
portion 38a. The frusto-conical surface 91' defines an angle 92'
from the axis 90 and thus also from the axis 88. Similarly, the
frusto-conical surface 44' defines an angle 93' from the axis 88
and thus also from the axis 90. In an exemplary embodiment, each of
the angles 92' and 93' ranges from about 10 degrees to about 45
degrees measured from the aligned axes 88 and 90. In an exemplary
embodiment, each of the angles 92' and 93' ranges from about 15
degrees to about 45 degrees measured from the aligned axes 88 and
90. In an exemplary embodiment, the angles 92' and 93' are equal as
measured from the aligned axes 88 and 90. In an exemplary
embodiment, each of the angles 92' and 93' is about 30 degrees
measured from the aligned axes 88 and 90. In an exemplary
embodiment, the angles 92' and 93' are not equal as measured from
the aligned axes 88 and 90. In an exemplary embodiment, the
operation of the pump assembly 10 with the respective exemplary
embodiments of the valve seat 76 and the fluid cylinder 18
illustrated in FIG. 5, is identical to the operation of the pump
assembly 10 with the respective exemplary embodiments of the valve
seat 76 and the fluid cylinder 18 illustrated in FIG. 3. The
annular portion 108 facilitates the removal of the valve seat 76
from the fluid cylinder 18.
[0055] In an exemplary embodiment, during operation of the pump
assembly 10 using any of the foregoing embodiments of the inlet
valve 54, downwardly directed axial loads along the axis 42 are
applied against the top of the valve body 100. This loading is
usually greatest as the plunger 32 moves towards the 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 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
or 43' of the fluid cylinder 18 via the engagement of the surface
91 or 91' against the surface 44 or 44'. The tapering of the
surface 91 or 91' and the surface 44 or 44' facilitates this
distribution and transfer of the downwardly directed axial loading
to the fluid cylinder 18 in a balanced manner, thereby reducing
stress concentrations in the fluid cylinder 18 and the valve seat
76.
[0056] In several experimental exemplary embodiments, experimental
analyses were conducted on two experimental exemplary embodiments
of combinations of the valve seat 76 and the fluid cylinder 18.
Experimental Exemplary Embodiment #1, for which finite element
analysis (FEA) was conducted, was the combination of the valve seat
76 and the fluid cylinder 18 as illustrated in FIG. 6. As shown in
FIG. 6, the tapered internal shoulder 43 of the fluid cylinder 18
is omitted. The seat body 80 of the valve seat 76 includes an
enlarged-diameter portion 112 and a reduced-diameter portion 114
extending downwardly therefrom. An external shoulder 116 defines an
axially-facing surface 118 that faces axially towards the inlet end
portion 81. The axially-facing surface 118 engages an
axially-facing surface 120 of the fluid cylinder 18, which is
defined by the enlarged-diameter portion 38a and faces axially away
from the inlet end portion 81. Experimental Exemplary Embodiment
#2, for which FEA was conducted, was the combination of the valve
seat 76 and the fluid cylinder 18 as illustrated in FIG. 3. Using a
loading of about 17 ksi, the maximum experimental stresses were
determined in each of Experimental Exemplary Embodiments #1 and #2.
For Experimental Exemplary Embodiment #1, the maximum von-Mises
stress in response to the engagement of the valve seat 76 with the
fluid cylinder 18 was about 142 ksi at about Point A shown in FIG.
6. For Experimental Exemplary Embodiment #2, the maximum von-Mises
stress in response to the engagement of the valve seat 76 with the
fluid cylinder 18 was about 78 ksi at about Point B, and about 78
ksi at about Point C (Points B and C are shown in FIG. 3).
[0057] In several exemplary embodiments, variations may be made to
the valve member 100, or the valve member 100 may be omitted in
favor of another valve member that does not include the plurality
of legs 106. In several exemplary embodiments, the valves 54 and 56
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 and 56 or the components
thereof, such as the valve seat 76, 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 cylinder
18 or features thereof may be used in other types of pumps and
fluid systems.
[0058] 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 term 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 are not to be construed as limiting terms.
[0059] 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.
[0060] In addition, the foregoing describes only some embodiments
of the invention(s), and alterations, 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.
[0061] 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.
* * * * *