SUMMARY
The present invention is directed to a fluid end comprising a housing having a longitudinal axis and opposed front and rear surfaces joined by an outer intermediate surface, and a bore formed within the housing and interconnecting the front and rear surfaces. The bore extends along the longitudinal axis of the housing. The housing further comprises a retainer attached to the rear surface of the housing by a plurality of fasteners, a reciprocating plunger disposed within the bore and the retainer, and one and only one packing seal installed within the housing and engaged an outer surface of the plunger.
The present invention is also directed to an apparatus comprising a packing seal assembly. The packing seal assembly is configured to be installed within a housing having a horizontal bore formed therein. The packing seal assembly comprises one and only one packing seal configured to surround and engage an outer surface of a reciprocating plunger. The one and only one packing seal has opposed front and rear surfaces joined by inner and outer surfaces and comprising an energizing component. The energizing component is installed within the seal and is configured to expand the inner and outer intermediate surfaces during operation. The packing seal assembly further comprises a wear ring surrounding the one and only one packing seal, and an annular component installed within the housing and comprising a projecting portion, the projecting portion engaging the energizing component.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a perspective view of one embodiment of a high pressure pump.
FIG. 2 is a cross-sectional view of the fluid end assembly shown in FIG. 1, taken along line A-A.
FIG. 3 is the cross-sectional view of the fluid end assembly shown in FIG. 2, but the plunger has been removed.
FIG. 4 is an enlarged view of area B shown in FIG. 3.
FIG. 5 is a front perspective view of the packing seal shown in FIG. 4.
FIG. 6 is a rear perspective view of the packing seal shown in FIG. 5.
FIG. 7 is a rear elevational view of the packing seal shown in FIG. 5.
FIG. 8 is a cross-sectional view of the packing seal shown in FIG. 7, taken along line C-C.
FIG. 9 is an enlarged view of area D shown in FIG. 8.
FIG. 10 is a front perspective view of the support element shown in FIG. 4.
FIG. 11 is a rear perspective view of the support element shown in FIG. 10.
FIG. 12 is a side elevational view of the support element shown in FIG. 10.
FIG. 13 is a cross-sectional view of the support element shown in FIG. 12, taken along line E-E.
FIG. 14 is an enlarged view of area F shown in FIG. 13.
FIG. 15 is a front perspective view of the support element shown in FIG. 10 engaged with the packing seal shown in FIG. 5.
FIG. 16 is a cross-sectional view of the support element and packing seal shown in FIG. 15, taken along line G-G.
FIG. 17 is an enlarged view of area H shown in FIG. 15.
FIG. 18 is a front perspective and partially exploded view of the fluid end section shown in FIG. 3.
FIG. 19 is a rear perspective and partially exploded view of the fluid end section shown in FIGS. 3 and 18.
FIG. 20 is the rear perspective and partially exploded view of the fluid end section shown in FIG. 19, but fewer components are shown exploded.
FIG. 21 is a front perspective view of the rear retainer shown in FIG. 4.
FIG. 22 is a rear perspective view of the rear retainer shown in FIG. 21.
FIG. 23 is a front elevational view of the rear retainer shown in FIG. 21.
FIG. 24 is a cross-sectional view of the rear retainer shown in FIG. 23, taken along line I-I.
FIG. 25 is a front perspective view of the metal ring shown in FIG. 4.
FIG. 26 is a rear perspective view of the metal ring shown in FIG. 25.
FIG. 27 is a rear elevational view of the metal ring shown in FIG. 25.
FIG. 28 is a cross-sectional view of the metal ring shown in FIG. 27, taken along line J-J.
FIG. 29 is a front perspective view of the packing nut shown in FIG. 4.
FIG. 30 is a rear perspective view of the packing nut shown in FIG. 29.
FIG. 31 is a front elevational view of the packing nut shown in FIG. 29.
FIG. 32 is a cross-sectional view of the packing nut shown in FIG. 31, taken along line 32.
FIG. 33 is a cross-sectional and enlarged view of another embodiment of a packing seal assembly.
DETAILED DESCRIPTION
High pressure reciprocating pumps typically comprise a power end assembly attached to a fluid end assembly. Fluid end assemblies are typically used in oil and gas operations to deliver highly pressurized corrosive and/or abrasive fluids to piping leading to the wellbore. Fluid end assemblies are attached to power ends typically run by engines. The power end comprises a crankshaft configured to reciprocate a plurality of plungers within the fluid end assembly to pump fluid throughout the fluid end.
Fluid may be pumped throughout the fluid end assembly at pressures that range from 5,000-15,000 pounds per square inch (psi). However, the pressure may reach up to 22,500 psi. Power ends typically have a power output of at least 2,250 horsepower during hydraulic fracturing operations. A single fluid end typically delivers a fluid volume of about 185-690 gallons per minute or 4-16 barrels per minute during a fracking operation. When a plurality of fluid ends are used together, the fluid ends collectively deliver about 4,200 gallons per minute or 100 barrels per minute to the wellbore. The present invention improves the performance and life of the various components included in the fluid end assembly.
Turning now to FIG. 1, one embodiment of a high pressure pump 10 is shown. The pump 10 comprises a fluid end assembly 12 joined to a power end assembly 14. The power end assembly 14 is described in more detail in U.S. patent application Ser. No. 17/884,691, authored by Keith, et al., and filed on Aug. 10, 2022, the entire contents of which are incorporated herein by reference. In alternative embodiments, the fluid end assembly 12 may be attached to other power end designs known in the art.
Continuing with FIG. 1, the fluid end assembly 12 comprises a plurality of individual fluid ends, or fluid end sections 16 positioned in a side-by-side relationship. Each fluid end section 16 is attached to the power end assembly 14 using a plurality of stay rods 18.
Turning to FIGS. 2 and 3, each fluid end section 16 comprises a housing 20 having a longitudinal axis 22 and opposed front and rear surfaces 24 and 26 joined by an outer intermediate surface 28 and a horizontal bore 30 formed therein. The horizontal bore 30 interconnects the front and rear surfaces 24 and 26 of the housing 20. The housing 20 comprises multiple sections joined together by fasteners 32. In alternative embodiments, the housing 20 may be of single-piece construction.
Continuing with FIGS. 2 and 3, fluid enters the housing 20 through upper and lower suction bores 34 and 36. Fluid exits the housing 20 through upper and lower discharge bores 38 and 40. Fluid is routed throughout the housing 20 by a fluid routing plug 42 and suction and discharge valves 44 and 46. Movement of the valves 44 and 46 is guided by a suction valve guide 48 and a discharge plug 50. The front surface 24 of the housing 20 is sealed by a front retainer 52.
Continuing with FIG. 2, a reciprocating plunger 54 is installed within the horizontal bore 30 and projects from the rear surface 26 of the housing 20. As the plunger 54 retracts from the housing 20, fluid is pulled from the suction bores 34 and 36 into the horizontal bore 30. As the plunger 54 extends into the housing 20, the plunger 54 forces fluid towards the discharge bores 38 and 40. The construction of the housing 20 and its above mentioned inner components are described in more detail in U.S. patent application Ser. No. 17/844,712, authored by Thomas et al., and filed on Aug. 10, 2022, the entire contents of which are incorporated herein by reference.
In traditional fluid ends, fluid is prevented from leaking from the rear surface of the housing by a plunger packing installed within the housing and surrounding the plunger. The plunger packing comprises a plurality of packing seals stacked on top of one another. A tight seal is created by compressing the plurality of stacked seals together longitudinally. During operation, the packing seals require continuous maintenance to make sure they are adequately compressed and sealing against the plunger. Over time, the components of the plunger packing wear against the walls of the housing, causing erosion and eventual failure of the housing.
Turning to FIGS. 3 and 4, the present application discloses a packing seal assembly 60 that comprises one and only one packing seal 62. By using one and only packing seal 62, a much smaller surface area of the housing 20 is subject to potential wear from the seal 62. Further, the single packing seal 62 is much easier to install than a plurality of packing seals used with a traditional plunger packing. As will be described in more detail herein, only one packing seal 62 is needed because the packing seal 62 comprises an energizing component 66. The energizing component 66 expands the packing seal 62 during operation, ensuring a tight seal against an outer surface of the plunger 54.
Turning to FIGS. 5-9, traditional packing seals are solid and comprise only an elastomeric body. The packing seal 62 comprises the energizing component 66 installed within an elastomeric body 63. The body 63 is annular and has opposed front and rear surfaces 68 and 70 joined by inner and outer intermediate surfaces 72 and 74. The energizing component 66 is installed within the front surface 68 of the packing seal 62 and is configured to expand radially when compressed longitudinally. Such expansion causes the inner intermediate surface 72 of the packing seal 62 to tightly seal against the outer surface of the plunger 54, and the outer intermediate surface 74 to tightly seal against the walls of the housing 20 or another component installed therein, as shown in FIG. 2.
Turning back to FIG. 3, one example of another component installed within the housing 20 is a wear ring 64 shown installed within the housing 20 and surrounding the packing seal 62. The wear ring 64 is positioned between the walls of the housing 20 and the packing seal 62 and is configured to protect the walls of the housing 20 from wear from the packing seal 62 during operation. The wear ring 64 is annular and is a made of a harder and more wear resistant material than the housing 20. For example, if the housing 20 is made of steel, the wear ring 64 may be made of tungsten carbide. Another example of another component installed within the housing 20 may be a stuffing box or sleeve known in the art. The stuffing box or sleeve may be installed within the housing and the packing seal 62 installed within the stuffing box or sleeve.
Continuing with FIG. 9, the energizing component 66 comprises a plurality of stacked metal pieces 80 having a V-shaped cross-section that function as a spring. Specifically, the packing seal 62 is known in the art as a multi-contact V-nested spring seal. In alternative embodiments, the energizing component may comprise other components known in the art that expand radially when compressed longitudinally. In further alternative embodiments, the energizing component may comprise one or more coiled springs configured to expand the seal regardless of any longitudinal compression.
Continuing with FIG. 9, the inner and outer surfaces 72 and 74 of the packing seal 62 comprise a plurality of seal lips 82. The seal lips 82 help effectuate sealing during operation. As the seal lips 82 wear over time, the energizing component 66 expands, pushing the lips 82 tighter against the plunger 54 and the wear ring 64.
With reference to FIGS. 10-17, the packing seal assembly 60 further comprises a support element 86. The support element 86 comprises an annular base 88 joined to an annular protrusion 90. The base 88 comprises opposed front and rear surfaces 92 and 94 joined by a tapered outer surface 96 and a cylindrical inner surface 98. The protrusion 90 projects from the rear surface 94 and has a tapered outer surface 100, as shown in FIG. 14. The rear surface 94 of the support element 86 is configured to engage the front surface 68 of the packing seal 62 such that the protrusion 90 projects into the energizing component 66, as shown in FIG. 17. In operation, the protrusion 90 helps keep the energizing component 66 expanded so as to maintain a tight seal against the plunger 54. However, the packing seal assembly 60 may be used without the support element 86, if desired.
Turning back to FIGS. 3 and 4, the horizontal bore 30 comprises a counterbore 84 that opens on the rear surface 26 of the housing 20. The counterbore 84 joins a uniform diameter section 102 of the horizontal bore 30 by a tapered surface 104, as shown in FIG. 4. The support element 86 is installed within the housing 20 such that the tapered outer surface 96 engages the tapered surface 104 of the housing 20. The packing seal 62 and the wear ring 64 are installed within the counterbore 84 such that the wear ring 64 engages the walls of the counterbore 84 and the packing seal 62 engages the support element 86. When the components are installed within the housing 20, the rear surface 70 of the packing seal 62 and a rear surface 106 of the wear ring 64 are flush with the rear surface 26 of the housing 20.
With reference to FIGS. 3, 18, and 19, the packing seal 62 and wear ring 64 are held within the housing 20 by a rear retainer 108 having a metal ring 110 and a packing nut 112 installed therein. The rear retainer 108 is attached to the rear surface 26 of the housing 20 using a plurality of fasteners 114, as shown in FIGS. 18 and 19.
With reference to FIGS. 21-24, the rear retainer 108 comprises opposed front and rear surfaces 116 and 118 joined by an outer intermediate surface 120 and a central passage 122 formed therein. A plurality of passages 124 are formed in the rear retainer 108. Each passage 124 interconnects the front and rear surfaces 116 and 118. The retainer 108 is positioned on the rear surface 26 of the housing 20 such that the passages 124 align with a plurality of threaded openings 126 formed in the rear surface 26 of the housing 20, as shown in FIG. 19.
With reference to FIGS. 18-20, a fastener 114 is received within each pair of aligned openings and passages 126 and 124. When installed therein, a threaded end 128 of each fastener 114 is positioned within a counterbore 130 formed in each passage 124 adjacent the rear surface 118 of the retainer 108, as shown in FIGS. 20 and 24. A threaded nut 132 is installed on each threaded end 128 and turned until the retainer 108 is held firmly against the rear surface 26 of the housing 20. The nuts 132 are each fully disposed within each counterbore 130, such that no nut projects from the rear surface 118 of the retainer 108, as shown in FIG. 20. In alternative embodiments, the passages 122 may not include the counterbore 130 and the nuts 132 may instead engage the rear surface 118 of the retainer 108.
Turning back to FIG. 24, the central passage 122 comprises a first section 134 joined to a second section 136. The first section 134 opens on the front surface 116 of the rear retainer 108, and the second section 136 opens on the rear surface 118 of the rear retainer 108. One or more lube ports 138 are also formed in the retainer 108. The lube port 138 interconnects the outer intermediate surface 120 and the first section 134 of the central passage 122, as shown in FIG. 4.
Continuing with FIGS. 4 and 24, internal threads 140 are formed in the walls of the second section 136 for receiving the packing nut 112. The walls surrounding the first section 134 of the central passage 122 are flat and configured to receive the metal ring 110. When the retainer 108 is attached to the housing 20, the central passage 122 aligns with the counterbore 84 formed in the housing 20, exposing the wear ring 64 and packing seal 62, as shown in FIG. 4.
With reference to FIGS. 25-28, the metal ring 110 comprises opposed front and rear surfaces 142 and 144 joined by inner and outer surfaces 146 and 148. A plurality of passages 15o are formed in the metal ring 110 that interconnect the inner and outer surfaces 146 and 148. The passages 150 open into an annular channel 152 formed in the outer surface 148 of the metal ring 110.
Continuing with FIG. 4, when the metal ring 110 is installed within the central passage 122, the front surface 142 of the metal ring 110 engages the rear surface 70 of the packing seal 62 and the rear surface 106 of the wear ring 64, and the outer surface 148 engages the first section 134 of the central passage 122. The lube port 138 formed in the retainer 108 aligns with the annular channel 152. During operation, lubricant is supplied to the fluid end section 16 through the lube port 138. Lubricant passes through the lube port 138 and into the annular channel 152 and eventually through the passages 150. Lubricant flowing through the passages 150 contacts and lubricates an outer surface of the reciprocating plunger 54.
With reference to FIGS. 4 and 29-32, the metal ring 110 is held within the retainer 108 by the packing nut 112. The packing nut 112 comprises opposed front and rear surfaces 154 and 156 joined by an outer intermediate surface 158 and a central passage 160 formed therein. The intermediate surface 158 comprises a threaded section 162 joined to a flange 164. The threaded section 162 is configured to mate with the internal threads 140 formed in the second section 136 of the central passage 122 of the rear retainer 108, as shown in FIG. 4.
Continuing with FIGS. 4 and 32, a plurality of openings 166 are formed in the flange 164 of the packing nut 112. Each opening 166 interconnects the outer intermediate surface 158 and the central passage 160. The openings 166 are configured to receive a tool used to turn the packing nut 112 within the retainer 108. The packing nut 112 is turned within the central passage 122 until the front surface 154 of the packing nut 112 tightly engages the rear surface 144 of the metal ring 110 and the flange 164 abuts the rear surface 118 of the retainer 108, as shown in FIG. 4. When tightly engaged, the front surface 142 of the metal ring 110 likewise tightly engages the rear surface 70 of the packing seal 62 and the rear surface 106 of the wear ring 64, thereby retaining the packing seal 62 and wear ring 64 within the housing 20.
Continuing with FIGS. 2, 4, and 32, a first groove 170 is formed within the walls of the central passage 160 of the packing nut 112 for housing a first seal 172, as shown in FIG. 2. The first seal 172 engages an outer surface of the plunger 54 and prevents fluid from leaking between the components, as shown in FIG. 2. A second groove 174 is formed in a front surface 176 of the flange 164 of the packing nut 112 for housing a second seal 178, as shown in FIG. 4. When the flange 164 abuts the rear surface 118 of the retainer 108, the second seal 178 engages the rear surface 118 of the retainer 108. The second seal 178 provides friction between the retainer 108 and the packing nut 112 to help prevent the packing nut 112 from backing out of the retainer 108 during operation.
Similarly, a groove 180 is formed in the rear surface 144 of the metal ring 110 for housing a seal 182, as shown in FIGS. 4 and 28. The seal 182 prevents fluid from leaking between the metal ring 110 and packing nut 112 during operation. The seal 182 further provides friction between the metal ring 110 and the packing nut 112 to help prevent the packing nut 112 from backing off during operation.
Turning to FIG. 33, another embodiment of a support element 184 and housing 186 are shown. The housing 186 is identical to the housing 20, but it does not include the tapered surface 104, shown in FIG. 4. Instead, the walls surrounding a horizontal bore 188 of the housing 186 comprise a first counterbore 190 joined to a uniform diameter section 192 by a second counterbore 194. The support element 184 is identical to the support element 86, but a base 196 of the element 184 has a rectangular shaped outer surface 198 configured to be installed within the second counterbore 194 formed in the housing 186. Additionally, a protrusion 200 projecting from the base 196 of the support element 184 has a generally rectangular or uniform diameter outer surface 202, instead of the tapered outer surface 100, shown in FIG. 14. The support element 184 functions in the same manner as the support element 86.
The packing seal assembly 60 disclosed herein may be used with other embodiments of fluid end sections not specifically disclosed herein. For example, the packing seal assembly 60 may be used with the fluid end sections disclosed in U.S. patent application Ser. No. 17/884,712, previously incorporated herein by reference, and U.S. patent application Ser. No. 17/550,552, authored by Thomas et al., the entire contents of which are incorporated herein by reference. Alternatively, the packing seal assembly 60 may be used with traditional block fluid ends known in the art, such as those disclosed in U.S. Pat. No. 10,941,765, issued to Nowell et al., the entire contents of which are incorporated herein by reference. In further embodiments, the packing seal assembly 60 may be used with other embodiments of retaining systems, such as those disclosed in U.S. patent Ser. No. 17/685,936, authored by Foster et al., the entire contents of which are incorporated herein by reference.
The various features and alternative details of construction of the apparatuses described herein for the practice of the present technology will readily occur to the skilled artisan in view of the foregoing discussion, and it is to be understood that even though numerous characteristics and advantages of various embodiments of the present technology have been set forth in the foregoing description, together with 2s details of the structure and function of various embodiments of the technology, this detailed description is illustrative only, and changes may be made in detail, especially in matters of structure and arrangements of parts within the principles of the present technology to the full extent indicated by the broad general meaning of the terms in which the appended claims are expressed.
Patent Application
20230047066
