EXHIBIT 1 

Case 6:20-cv-00200-ADA Document 46-1 Filed 10/29/20 Page 1 of 27
c12) United States Patent 

Now ell et al. 

(54) SEALING HIGH PRESSURE FLOW DEVICES 

(71) Applicant: Kerr Machine Co., Sulphur, OK (US) 

(72) Inventors: Mark S. Nowell, Ardmore, OK (US); 

Kelcy Jake Foster, Ardmore, OK (US); 

Michael Eugene May, Ardmore, OK 

(US); Brandon Scott Ayres, Ardmore, 

OK (US); Christopher Todd Barnett, 

Stratford, OK (US); Michael Cole 

Thomas, Ardmore, OK (US); Guy J. 

Lapointe, Sulphur, OK (US) 

(73) Assignee: Kerr Machine Co., Sulphur, OK (US) 

( *) Notice: Subject to any disclaimer, the term ofthis 

patent is extended or adjusted under 35 

U.S.C. 154(b) by O days. 

(21) Appl. No.: 16/574,918 

(22) Filed: 

(65) 

Sep. 18, 2019 

Prior Publication Data 

US 2020/0011434 Al Jan. 9, 2020 

Related U.S. Application Data 

(60) Division of application No. 15/719,124, filed on Sep. 

28, 2017, which is a continuation-in-part of 

(51) 

(52) 

Int. Cl. 

F16K 5118 

F15B 7106 

U.S. Cl. 

(Continued) 

(2006.01) 

(2006.01) 

(Continued) 

CPC ............ F16K 51184 (2013.01); F04B 53/164 

(2013.01); F04B 53122 (2013.01); F15B 7106 

(2013.01); 

(Continued) 

230 

~ 

I 1111111111111111 1111111111 111111111111111 IIIII 1111111111 111111111111111111 

US010591070B2 

(IO) Patent No.: US 10,591,070 B2 

(45) Date of Patent: Mar.17,2020 

(58) Field of Classification Search 

CPC ...... F16K 5/184; F16K 5/0492; F16K 5/0471; 

F16K 5/0485; F16K 5/161; F16K 5/0464; 

(Continued) 

(56) References Cited 

U.S. PATENT DOCUMENTS 

3,173,648 A * 3/1965 McGuire ............... Fl6K 5/0673 

251/188 

3,373,695 A * 3/1968 Yohpe ................. F04B 53/1025 

417/569 

(Continued) 

OTHER PUBLICATIONS 

Fluid end assemblies like those disclosed in Figure 11 of the current 

application and Figure 11 of the parent application, U.S. Patent 

Publication No. 2017/0089473, were offered for sale in the United 

States more than 1 year prior to Sep. 28, 2017. 

(Continued) 

Primary Examiner - John Bastianelli 

(74) Attorney, Agent, or Firm - Tomlinson McKinstry, 

P.C. 

(57) ABSTRACT 

Apparatus and method contemplating a high pressure fluid 

end assembly having a body defining a body bore and 

defining a recess in the body intersecting the body bore. A 

closure is joined to the body and forms a sealing surface. A 

seal is mounted to the body in the recess and configured to 

extend from the recess beyond the body bore to seal against 

the sealing surface formed by the closure. 

24 Claims, 17 Drawing Sheets 

238 

254 231 

Case 6:20-cv-00200-ADA Document 46-1 Filed 10/29/20 Page 2 of 27
US 10,591,070 B2 

Page 2 

Related U.S. Application Data 

application No. 15/280,642, filed on Sep. 29, 2016, 

now Pat. No. 10,288,178. 

(60) Provisional application No. 62/346,915, filed on Jun. 

7, 2016, provisional application No. 62/318,542, filed 

on Apr. 5, 2016, provisional application No. 

62/315,343, filed on Mar. 30, 2016, provisional 

application No. 62/234,483, filed on Sep. 29, 2015. 

(51) Int. Cl. 

F16K 5104 

F16J 15106 

F15B 21100 

F16K 5116 

F16K 5102 

F04B 53122 

F04B 53/16 

(2006.01) 

(2006.01) 

(2006.01) 

(2006.01) 

(2006.01) 

(2006.01) 

(2006.01) 

(52) U.S. Cl. 

CPC ............. F15B 21100 (2013.01); F16J 151062 

(2013.01); F16K 510271 (2013.01); F16K 

510464 (2013.01); F16K 510471 (2013.01); 

F16K 510485 (2013.01); F16K 510492 

(2013.01); F16K 51161 (2013.01); F16K 51181 

(2013.01) 

( 58) Field of Classification Search 

(56) 

CPC .......... F16K 5/181; F16K 5/0271; F15B 7/06; 

F15B 21/00; F16J 15/062; F04B 53/22; 

F04B 53/164; F04B 53/162; F04B 53/16 

USPC ................ 251/366-367, 359, 360, 363, 214; 

417/454 

See application file for complete search history. 

References Cited 

U.S. PATENT DOCUMENTS 

3,427,988 A * 2/1969 Schmieman ............ F04B 53/10 

417/569 

4,363,463 A * 12/1982 Moon, Jr. ........... Fl6K31/1262 

251/214 

4,470,771 A * 9/1984 Hall F04B 9/1178 

417/342 

4,520,837 A * 6/1985 Cole ....................... E21B 33/13 

137/68.23 

4,768,933 A * 9/1988 Stachowiak ........ F04B 53/1025 

137/543.13 

4,771,801 A * 9/1988 Crump .................. F04B 49/121 

137/68.26 

5,073,096 A * 12/1991 King ..................... F04B 53/007 

137/516.29 

5,362,215 A * 11/1994 King ....................... F04B 49/10 

137/542 

5,524,902 A * 6/1996 Corvette Fl6J 15/18 

251/214 

6,382,940 Bl * 5/2002 Blume . ................. F04B 53/007 

277/435 

6,641,112 B2 * 11/2003 Antoff ................. F04B 53/1025 

251/363 

7,168,440 Bl* 1/2007 Blume .................. F04B 53/102 

137/15.18 

7,296,591 B2 * 11/2007 Moe ...................... F04B 53/109 

137 /454.4 

7,513,759 Bl* 4/2009 Blume .................. F04B 53/007 

137 /512 

7,963,502 B2 * 6/2011 Lovell ..................... Fl6K41/02 

251/214 

9,732,746 B2 8/2017 Chandrasekaran et al. 

2004/0234404 Al * 11/2004 Vicars ................... F04B 53/102 

417/571 

2008/0006089 Al * 1/2008 Adnan .................... F04B 51/00 

73/587 

2010/0243255 Al* 9/2010 Luharuka .............. E21B 21/062 

166/308.1 

2011/0079302 Al * 4/2011 Hawes .................. Fl6K 25/005 

137 /538 

2012/0141308 Al* 6/2012 Saini. C08G 18/10 

417/452 

2012/0187321 Al* 7/2012 Small .................. F04B 53/1032 

251/321 

2014/0127062 Al* 5/2014 Buckley .................. F04B 53/10 

417/439 

OTHER PUBLICATIONS 

Exhibit "A" includes cross-sectional views of fluid end assemblies 

known in the art prior to Sep. 29, 2015. 4 pages. 

Exhibit "B" includes side views of valve seats known in the art prior 

to Sep. 29, 2015. 2 pages. 

Exhibit "C" is a cross-sectional view of a plunger end of a fluid 

assembly known in the art prior to Sep. 29, 2015. 1 page. 

Exhibit "D" includes an engineering drawing and pictures of a mud 

pump known in the art prior to Sep. 29, 2015. 4 pages. 

* cited by examiner 

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U.S. Patent Mar. 17,2020 Sheet 1 of 17 US 10,591,070 B2 

100 

\ 

104 

130b 

FIG. 1 

PRIOR ART 

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U.S. Patent Mar. 17, 2020 Sheet 2 of 17 US 10,591,070 B2 

106b' 

FIG. 2 

PRIOR ART 

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U.S. Patent Mar.17,2020 Sheet 3 of 17 US 10,591,070 B2 

100 

\ 

148 

110 _ ___.,__ 

142 

FIG. 3 140 

PRIOR ART 

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U.S. Patent Mar. 17,2020 Sheet 4 of 17 US 10,591,070 B2 

FIG. 4 

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U.S. Patent Mar. 17, 2020 Sheet 5 of 17 US 10,591,070 B2 

152 

FIG. 5 

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170 

\ 

180 

FIG. 6 

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140 

108 

FIG. 7 

PRIOR ART 

Sheet 7 of 17 

Vs 10,59

171 
U.S. Patent Mar.17,2020 Sheet 8 of 17 US 10,591,070 B2 

108' ----t~tt-H52' 

FIG. 8 154' 

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U.S. Patent Mar.17,2020 Sheet 9 of 17 

200 

~ 

220 

221 

2 8 

219 

202 

201 \ 

224 

PRIOR ART 

FIG. 9 

US 10,591,070 B2 

227 

208 

226 

229 

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1202 

208 

FIG. 10 

PRIOR ART 

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U.S. Patent 

...-

lO 

N 

Mar.17,2020 Sheet 11 of 17 US 10,591,070 B2 

. 

(!) 

LL 

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235 

I 

234 

FIG. 12 

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257 

FIG. 13 

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272 

FIG. 14 

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268 

FIG. 15 

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286 

250 

254 

FIG. 16 

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230 

~ 238 

FIG. 17 

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US 10,591,070 B2 

1 

SEALING HIGH PRESSURE FLOW DEVICES 

BACKGROUND 

2 

ing downtime and operating cost. What is needed is a 

solution that transfers the erosion (corrosion and abrasion) 

from the high pressure fluid device body to the component 

sealed with the body. It is to those improvements that 

This technology relates generally to sealing fluid flow 

passages inside flow control devices, such as those particularly suited for use in high pressure oil and gas production 

and processing systems. 

5 embodiments of this technology are directed as described in 

the illustrative embodiments and contemplated within the 

scope of the claims. 

One such type of flow control device is a valve. Generally, 

a valve forms a flow passage and has a selectively operable 10 

closure to open or close the flow passage in order to control 

a flow of fluid through the valve. The sealing integrity of 

high pressure valves must withstand not only high operating 

fluid pressures, presently 15,000 pounds per square inch and 

higher, but also must do so while controlling the flow of 15 

corrosive and/or abrasive fluids that are notorious for eroding the valve internal components in the oil and gas industry. 

Preferably, the valves can withstand pressures up to at least 

22,500 pounds per square inch. 

Illustrative embodiments herein are directed to a plug 20 

valve although the contemplated embodiments are not so 

limited. In a plug valve the flow passage typically includes 

a valve body in fluid communication with two or more 

openings, typically an inlet opening and an outlet opening, 

forming a flow passage through the valve body. A valve plug 25 

and insert segments, one type of a valve closure that is 

described herein, are disposed in a valve body bore between 

the inlet and outlet openings where sealing occurs between 

the plug, the insert, and the bore. The valve plug defines a 

through-opening and is selectively rotatable to an open 30 

position where the through-opening is aligned with the flow 

passage to permit a flow of fluid through the valve (from the 

inlet to the outlet), or to a closed position where the 

through-opening is misaligned with the flow passage to 

prevent the flow of fluid through the valve. Operating a 35 

valve in the harsh oilfield conditions can cause erosion of the 

valve body bore where the seal in the insert abrades against 

the bore, often resulting in leakage in a short amount of time. 

Repairing the valve body, such as by a weld build-up and 

machining operation, is a cumbersome and disruptive repair 40 

in the oilfield. 

The illustrative embodiments of this technology directed 

SUMMARY OF THE INVENTION 

The present invention is directed to a fluid end assembly 

comprising a housing having an external surface and an 

internal chamber, and a first conduit formed in the housing 

and having first and second sections, each section independently interconnecting the internal chamber and the external 

surface. The fluid end assembly further comprises a second 

conduit formed in the housing, intersecting the first conduit 

and independently interconnecting the internal chamber and 

the external surface, and an endless groove formed in the 

wall or walls defining one of the conduits and extending 

concentrically around that conduit. 

The present invention is also directed to a fluid end 

assembly comprising a housing having an internal chamber 

and a conduit that intersects the internal chamber and opens 

at a first surface of the housing, a plunger that reciprocates 

within the housing, and a seal positioned within an annular 

groove formed in the housing. 

The present invention is further directed to a method for 

manufacturing a fluid end assembly. The method comprises 

the steps of providing a housing having an external surface, 

an internal chamber, a first conduit formed in the housing 

having first and second sections, and a second conduit 

formed in the housing, intersecting the first conduit and 

having third and fourth sections independently interconnecting the internal chamber and the external surface, and 

forming an endless groove in the walls or walls defining one 

of the sections such that the groove extends concentrically 

around that section. 

The present invention is also directed to a fluid end 

assembly having a housing having an external surface and 

an internal chamber, a first conduit formed in the housing 

and having first and second sections, and a second conduit 

formed in the housing, intersecting the first conduit. The 

to plug valves are in no way limiting of the contemplated 

embodiments of this technology. The skilled artisan understands that in alternative embodiments this technology can 

be used in other types of valves having differently configured closures. However, an enumeration of all the different 

types of valves that are suited for using this technology is not 

necessary for the skilled artisan to understand the scope of 

the claimed subject matter, so no such enumeration is 

warranted. 

45 fluid end assembly further comprises a recessed comer 

section formed in the wall or walls defining one of the 

conduits and extending concentrically around that conduit. 

The comer element is sized to receive a sealing element 

therein. The fluid end assembly further comprises a stuffing 

Besides valves, other types of high-pressure flow devices 

are also suited for practicing this technology. For example, 

50 box installed in the same conduit within which the comer 

section is formed and having a tubular side wall that fully 

overlies that comer section. Each conduit independently 

interconnects the internal chamber and the external surface. 

BRIEF DESCRIPTION OF THE DRAWINGS 

Details of various embodiments of the present technology 

are described in connection with the accompanying drawings that bear similar reference numerals. 

FIG. 1 is a cross-sectional depiction of a plug valve that 

is constructed in accordance with previously attempted 

solutions. 

a fluid end is used in many well servicing applications to 

contain high pressure, often corrosive and/or abrasive, frac- 55 

turing fluids in the oil and gas industry. A fluid end typically 

has a manifold body and a number of components mounted 

and sealed to the body, such as the suction and discharge 

plugs, suction and discharge valve seats, stuffing box, discharge flange, and suction manifold; with those components 60 

either alone or sleeved as are illustratively described herein. 

Like the valves, operating a fluid end in the harsh oilfield 

conditions can cause erosion of the body resulting in leakage FIG. 2 is a cross-sectional depiction of another plug valve 

that is constructed in accordance with other previously 

65 attempted solutions. 

in a short amount of time. Repairing the body is also 

cumbersome and disruptive in the oilfield. 

Improvements are needed in the internal sealing of high 

pressure flow devices to increase operating life while reducFIG. 3 depicts enlarged portions of the plug valve in FIG. 1. 

Case 6:20-cv-00200-ADA Document 46-1 Filed 10/29/20 Page 21 of 27
US 10,591,070 B2 

3 

FIG. 4 depicts enlarged portions similar to FIG. 3 but of 

a plug valve that is constructed in accordance with embodiments of this technology. 

FIG. 5 depicts more of the plug valve of FIG. 4. 

4 

a powered actuator. The plug 110 also has a bottom journal 

126 that rotates within the body 102 and is sealed by packing 

128. 

FIG. 6 is a cross-sectional depiction of another plug valve 5 

that is constructed in accordance with this technology. 

The body 102 also forms openings 116a, 116b intersecting the bore 104, typically referred to as an inlet and an 

outlet. For illustrative purposes of this description it is a 

given that the fluid flows through the valve 100 from left to 

right, or into the opening 116a and out of the opening 116b. 

FIG. 7 is an isometric depiction of a valve insert in the 

plug valve depicted in FIG. 1. 

FIG. 8 is similar to FIG. 7 but depicting a different 

cross-section through the plug valve. 10 

However, in practice either opening 116 can provide the inlet 

and the other opening 116 the outlet. 

Each insert 106 forms a respective opening 130a, 130b, 

and the inserts 106 are mounted in the valve 100 so that the 

insert openings 130 are aligned with the respective valve 

body opening 116. The plug 110 forms a through-opening 

132 permitting a user to selectively align the opening 132 

with the openings 116. FIG. 1 depicts the closed position of 

FIG. 9 is an isometric depiction of a fluid end that is 

constructed in accordance with embodiments of this technology. 

FIG. 10 is an enlarged depiction of a portion of the fluid 15 

end of FIG. 9. 

FIG. 11 is an exploded cross-sectional depiction of a fluid 

end that is constructed in accordance with embodiments of 

this technology. 

FIGS.12 and 13 are enlarged depictions of portions of the 

fluid end of FIG. 11. 

FIG. 14 is a cross-sectional depiction of another fluid end 

that is constructed in accordance with embodiments of this 

technology. 

FIGS.15 and 16 are enlarged depictions of portions of the 

fluid end of FIG. 14. 

FIG. 17 is the cross-sectional view of FIG. 11 with the 

components shown installed within the fluid end. A plunger 

and a plurality of packing seals are also shown installed 

within the fluid end. 

DETAILED DESCRIPTION 

Initially, this disclosure is by way of example only, not by 

limitation. The illustrative constructions and associated 

methods disclosed herein are not limited to use or application for sealing any specific assembly or in any specific 

environment. That is, the disclosed technology is not limited 

to use in sealing valves and fluid ends as described in the 

illustrative embodiments. Thus, although the instrumentalities described herein are for the convenience of explanation, 

shown and described with respect to exemplary embodiments, the skilled artisan understands that the principles 

herein may be applied equally in sealing other types of high 

pressure flow devices. 

the valve 100, where the plug 110 is rotated so that the 

through-opening 132 is misaligned with the openings 116. 

Namely, in the closed position of the valve 100 depicted 

20 in FIG. 1, pressurized fluid connected to the opening 116a 

(inlet) impacts against the closed plug 110, sealing the 

backside of the plug in a metal-to-metal seal against the 

insert 106b and also sealing between a seal 140 mounted in 

the insert 106b between it and the valve body bore 104. 

25 Thus, in the closed position the pressurized fluid is blocked 

from flowing through the valve 100. By rotating the plug 110 

to the open position (not depicted), its through-opening 132 

comes into alignnient with the openings 116, permitting the 

pressurized fluid to flow through the valve 100 via a flow 

30 passage established collectively by the valve body openings 

116, the insert openings 130, and the valve plug throughopening 132. 

FIG. 2 is similar to FIG. 1 but depicting a top entry plug 

valve 100' that is constructed in accordance with other 

35 previously attempted solutions. The plug valve 100' has 

inserts 106a', 106b' that are formed as segments of an open 

hollow cylinder instead of the inserts 106a, 106b in FIG. 1 

that are segments of an open hollow cone. In other words, 

the conical surfaces in FIG. 1 are replaced here with 

40 cylindrical surfaces. Due to this, the inner body of the plug 

valve 100' is not tapered, unlike the plug valve 100. For 

purposes of this description the skilled artisan understands 

that the details of construction and use of this technology 

applies equivalently to both types of these valves, as well as 

45 other types of valves that are used to control highly pressurized fluid. Thus, the skilled artisan understands the scope 

of the claims from this description's comparison to the 

details of construction for just one of the previously 

FIG. 1 is a cross-sectional depiction of a plug valve 100 

that is constructed according to previously attempted solutions. The plug valve 100 has a forged valve body 102 

forming a tapered internal bore 104. Inserts 106a, 106b in 

these illustrative embodiments are segments of an open 50 

hollow cone. Although two inserts 106a, 106b are depicted, 

the contemplated embodiments are not so limited because 

alternatively there can be more than two. Each insert 106a, 

106b has an outer conical surface 108a, 108b forming a 

matching taper to engage against the bore 104 in a close 

mating relationship. 

attempted solutions. 

Continuing with the previously started description in 

comparison to the previously attempted solutions depicted in 

FIG. 1, FIG. 3 is an enlarged portion of it more particularly 

depicting how the high pressure fluid is contained inside the 

valve 100 in part by the seal 140 that is compressed between 

55 the outer conical surface 108b of the insert 106b and the 

valve body bore 104. 

A cylindrical plug 110 has an outer diameter surface 112 

sized to fill the space between the inserts 106, mating with 

an inner diameter surface 114a, 114b of the respective 

inserts 106. The plug 110 has a top journal 118 that is 

rotatable within a retaining nut 120. A packing 122 seals 

against the journal 118 to contain the pressurized fluid inside 

the valve 100 while permitting an external force to rotate the 

journal 118 and, in tum, the plug 110. In these illustrative 

embodiments a handle 124 is connected to the journal 118 to 

permit a user to manually rotate the plug 110. In alternative 

embodiments not depicted the journal 118 can be rotated by 

The insert 106b has a surface 139 defining a recess 144 

intersecting the outer conical surface 108b. The term "intersecting" for purposes of this description and meaning of the 

60 claims means that the recess 144 forms a gap in the outer 

surface 108b of the insert 106b. That intersecting construction of the recess 144 with the surface 108b permits mounting a fixed end 141 of the seal 140 in the recess 144, and 

sizing the seal 140 so that a distal end 143 extends from the 

65 recess 144 beyond the outer conical surface 108b in order to 

seal against the valve body bore 104. Importantly, this 

requires the bore 104 to define a sealing surface 142 against 

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US 10,591,070 B2 

5 6 

nut 164. Unlike the retaining nut 120 in FIG. 3, retaining nut 

164 does not have a seal mounted to it. Instead, the seal 162 

is mounted to the valve body 152 and is sized to extend from 

the recess 160 to seal against the outer diameter surface 166 

which the seal 140 in the insert 106b presses against to effect 

the sealed engagement of the insert 106b against the bore 

104. Corrosive and/or abrasive fluid can become trapped 

between the seal 140 (mounted in the insert 106b) and the 

bore 104 causing erosion of the bore 104. The seal 140 in 

these embodiments is referred to as an axial seal because the 

compressive forces from the surface 108b on one side and 

the bore 104 on the other side act in an axial direction 

relative to the annular seal 140. 

5 of the retaining nut 164. In the same way as described above, 

this technology transfers the erosion wear away from the 

body 152 to the less complex and less expensive mating 

component, in this case the retaining nut 164. 

Although the embodiments of FIG. 3 depict only one 

annular seal 140 surrounding the outlet 116b, the previously 

attempted solutions are not so limited. The skilled artisan 

understands that in alternative constructions more than one 

seal can be used to provide redundancy. The seal 140 can be 

FIG. 5 is a simplified depiction of the valve 150 that is 

10 constructed in accordance with the present technology. The 

skilled artisan understands that variations in construction are 

an elastomeric seal, and in other embodiments other kinds of 15 

seals can be used such as metal seals, spring seals, and the 

like. 

To enclose the valve plug 110 and support the journal 118, 

encompassed within the contemplated embodiments of this 

technology that are represented in the illustrative embodiments. For example, FIG. 6 depicts another valve 170 that 

is constructed in accordance with this technology because 

each of the seals 172, 174, 176 are mounted in respective 

recesses formed in the valve body 184 and intersecting the 

valve body bore 178. The seals 172, 174, 176 are configured 

a retaining nut 120 is threaded to the valve body 102. The to extend away from the respective recesses to seal against 

retaining nut 120 seals to the valve body bore 104 by another 

seal 146. Similar to the insert 106b, the retaining nut 120 has 

20 sealing surfaces of the inserts 180 and the retaining nut 182, 

correspondingly. Unlike the previously attempted solutions, 

this construction eliminates the erosion caused by mounting 

a seal to a mating component that seals against the valve 

a surface 147 defining a recess (sometimes referred to as a 

"gland") 148 intersecting an outer diameter surface 121 of 

the retaining nut 120. The seal 146 is supported in the recess 

148 and is sized to extend beyond the outer surface 121 to 25 

seal against a sealing surface formed by the valve body bore 

104. The seal 146 in these embodiments is referred to as a 

radial seal because the compressive forces from the cap's 

surface 121 on one side and the bore 104 on the other side 

act in a radial direction relative to the annular seal 146. 30 

Although a radial seal is depicted, in alternative embodiments an axial seal or a crush seal and the like can be used 

instead of or in addition to the radial seal. 

In comparison, FIG. 4 is similar to FIG. 3 but depicts a 

portion of a valve 150 that is constructed in accordance with 35 

embodiments of this technology. Here an insert 151 is 

similar in some respects but does not have a seal mounted to 

body bore 178. 

FIG. 7 is an isometric depiction of the insert 106 in the 

previous valve design depicted in FIG. 1. In these embodiments the insert 106 defines slots 171 intersecting the outer 

conical surface 108 of the insert 106. A spring 173 is 

mounted to the insert 106 in each slot 171 and extends from 

the slot 171 to contact the valve body bore 104 (FIG. 1). As 

described above, that construction of the previously 

attempted solutions, by design, makes the valve body bore 

104 the sacrificial member for any erosion caused by the 

springs 173. 

FIG. 8 depicts a portion of the valve 150 (of this technology) in FIG. 5, but at a different cross section that passes 

through a recess 170' defined by a surface 190 formed by the 

valve body 152'. The recess 170' intersects the valve body 

bore 154' so that a spring 172' can be mounted in the recess 

it like the insert 106b (FIG. 3). Particularly, the insert 151 

has an outer conical segment surface 153 that does not form 

a recess for mounting a seal. There is no gap in the surface 

153 where a recess intersects for mounting a seal. Instead, a 

valve body 152 defines a valve body bore 154, and also has 

40 170' at a fixed end and sized to extend from the recess 170' 

a surface 155 defining a recess 156 intersecting the bore 154. 

Again, the term "intersecting" for purposes of this description and meaning of the claims means that the recess 156 45 

includes a gap in the bore 154. Particularly, a fixed end 157 

of a seal 158 is mounted in the recess 156, and because the 

recess 156 intersects the bore 154, the seal 158 can be sized 

to extend from the recess 156 beyond the bore 154 so that 

a distal end 159 of the seal 158 seals against a sealing surface 50 

formed by the insert 151. 

Corrosive and/or abrasive fluid can become trapped 

between the seal 158 (mounted to the body 152) and the 

insert 151 causing erosion of the outer cylindrical surface of 

the insert 151. Importantly, in comparison to the previously 55 

attempted solutions, the construction of FIG. 4 advantageously transfers the erosion wear from the bore 154 (of the 

body 152) to the insert 151. When erosion has progressed to 

the extent that leakage occurs, repairing or replacing the 

insert 151 is significantly less complex and less expensive 60 

than repairing the body 152. 

The body 152 also has a surface 161 forming another 

recess 160 that intersects the valve body bore 154. A seal 162 

is mounted to the body 152 in the recess 160. Again, because 

of the intersecting construction of the recess 160 and the 65 

bore 154, the seal 162 can be sized to extend beyond the bore 

154 to seal against a sealing surface formed by a retaining 

to pressingly engage against an outer conical surface 108' of 

the insert 106'. Like described above, this technology transfers the wear from the valve body bore 154' to the less 

complex and less expensive insert 106'. 

Returning momentarily to FIG. 5 that depicts the plug 

valve 150 constructed in accordance with embodiments of 

this technology. The skilled artisan having read this description understands that this technology transfers the erosion 

wear from the bore of the body 152 to the outer conical 

surface of the insert 151. As described, leakage can occur 

because the free end of the seal 158 abrades away the outer 

conical surface of the insert 151. In some illustrative 

embodiments the repair procedure can entail resurfacing the 

insert 151 to provide a new sealing surface for the seal 158 

mounted in the body 152. Alternatively, the insert 151 can 

simply be replaced with a new one. 

In yet other alternative embodiments a disposable wear 

member can be provided between the outer conical surface 

of the insert 151 and the bore of the body 152. For purposes 

of this description and the claims the disposable wear 

member can be a disposable liner (not depicted) with one 

surface facing the bore of the body 152 to function effectively the same as the outer conical surface of the insert 151. 

In some embodiments an opposing inner surface of the liner 

can mate directly to the outer conical surface of the insert 

151. Alternatively, a seal can be provided between the inner 

surface of the liner and the outer conical surface of the insert. 

Case 6:20-cv-00200-ADA Document 46-1 Filed 10/29/20 Page 23 of 27
US 10,591,070 B2 

7 

That seal can be mounted to the insert and extending to seal 

against a sealing surface formed by the liner (such as by 

using the insert 106 in FIG. 1), or the seal can be mounted 

to the inner surface of the liner and extending to seal against 

8 

mounted within the recess 207 extends beyond the outer 

surface 215 to pressingly engage against the bore 209 

defining the discharge opening 202. In this construction the 

a sealing surface formed by the outer surface of the insert. 5 

highly-pressurized corrosive and/or abrasive fluid can harsh 

fluid can be injected between the seal 208 and the bore 209, 

Turning to another type of flow device that is well-suited causing erosion of the seal surface formed by the bore 209. 

for practicing this technology, FIG. 9 is a simplified isometric cross-sectional depiction of a hydraulic fracturing fluid 

end 200 that is constructed in accordance with previously 

attempted solutions. The fluid end 200 is generally a mani- 10 

fold 201 used to deliver highly-pressurized corrosive and/or 

abrasive fluids, typically used in hydraulic fracturing processes in the oil and gas industry. Fluid may pass through the 

fluid end 200 at pressures that range from 5,000-15,000 

pounds per square inch (psi). Fluid ends 200 used in high 15 

pressure hydraulic fracturing operations typically move fluid 

This technology transfers that erosion wear from the body 

bore 209 to the less complex and less expensive discharge 

plug 204. 

Fluid end bodies have conventionally been made of 

heat-treated carbon steel, so it was not uncommon for the 

body 201 to crack before any sacrificial erosion of the body 

progressed to the point of creating leakage between the 

discharge plug 204 and the bore 209. However, progress in 

the technology has introduced stainless steel body construction resulting in a significantly longer operating life. As a 

at a minimum of 8,000 psi. However, normally, the fluid end 

200 will move fluid at pressures around 10,000-15,000 psi. 

The manifold body or housing 201 typically has a first 

conduit 220 and a second conduit 221 formed within the 20 

result, this erosion is no longer negligible but is instead a 

consideration for reducing erosion in modem fluid end 

construction. One leading source of bore 209 erosion in 

conventional fluid ends is the seal 208 mounted in the 

discharge plug 204 and extending therefrom to seal against 

a sealing surface formed by the body 201. 

FIG. 11 is an exploded cross-sectional depiction of a fluid 

end 230 that is constructed in accordance with this technology to, in numerous places, transfer the erosion wear from 

the body to the less complex and less expensive component 

that is sealed to the body. A manifold body 232 forms a 

number of interconnected bores or conduits, including a first 

conduit or discharge bore 234 forming a discharge opening 

body 201 that intersect to form an internal chamber 222. The 

first conduit 220 is typically orthogonal to the second 

conduit 221. The first conduit 220 may have aligned first and 

second sections 223 and 224 that are situated on opposite 

sides of the internal chamber 222. Likewise, the second 25 

conduit 221 may have aligned third and fourth sections 225 

and 226 that are situated on opposite sides of the internal 

chamber 222. The sections 223, 224, 225, and 226 each may 

independently interconnect the internal chamber 222 to an 

external surface 227 of the fluid end 200. 30 235 that is similar to the discharge opening 202 in the 

conventional fluid end 200 depicted in FIG. 9. The discharge 

bore 234 further defines an intake opening 231 formed 

opposite the discharge opening 235. The term "discharge 

bore" for purposes of this description means the surface 

A plunger 228 reciprocates within the body 201 to 

increase the pressure of fluid being discharged from the fluid 

end 200. As shown in FIG. 9, the plunger 228 may be 

disposed within the third section 225 of the second conduit 

221. The plunger 228 is disposed within a plurality of 

packing seals 219. The plunger 228 is powered by an engine 

operatively engaged with the fluid end 200. In high pressure 

hydraulic fracturing operations, the engine preferably has a 

power output of at least 2,250 horsepower. Valve seats 229 

are also shown within the first conduit 220. The valve seats 

229 may support valves, such as a ball valve, used to control 

the movement of high pressure fluid within the body 201. 

There are sealing areas in the fluid end 200 that experience the kind of erosion issues described above in plug 

valves. Similar to the conventional plug valve 100 depicted 

in FIG. 1, a number of components seal to the manifold body 

201. Here, again, the sacrificial member for erosion, by 

design, is the body 201 instead of the less complex and less 

expensive mating component. 

For example, the body 201 defines a discharge opening 

202 that opens into the first conduit 220. The discharge 

opening 202 depicted in these embodiments is sealed closed 

by inserting a closure or discharge plug or cover 204 into the 

conduit 220 and securing it by advancing a retaining nut 206 

into the body 201. The discharge plug 204 supports a seal 

208 that seals against the bore defining the discharge opening 202. FIG. 10 is a simplified cross-sectional depiction of 

the discharge plug 204 that has a surface 205 defining a 

recess 207 into which the seal 208 is mounted at an inner 

radial surface 211 of the radial seal 208. 

In these illustrative embodiments the recess 207 is rectangular but the contemplated embodiments are not so limited. The skilled artisan understands that the configuration of 

the recess 207 is largely determined by what shape is 

required to mount the type of seal selected. The recess 207 

intersects an outer surface 215 of the discharge plug 204, 

permitting the seal 208 to be sized so that a portion not 

35 defining the discharge opening 235 into which a closure or 

discharge plug 236 and a retaining nut 238 are installed, and 

the surface defining the intake opening 231. For clarity, 

although FIG. 11 references the discharge bore 234 as 

defining an upper end of the discharge opening 235 where 

40 the retaining nut 238 attaches, the discharge bore 234 also 

references lower portions of the discharge opening 235 

where the discharge plug 236 seals to the body 232 and 

where the valve seat (not depicted) seals to the body 232. 

Likewise, the discharge bore 234 also references upper 

45 portions of the intake opening 231. Generally, for purposes 

of this description the discharge bore 234 forms multidimensional diameters at different longitudinal locations of 

the discharge opening 235 and intake opening 231. 

The discharge opening 235 is sealed closed by inserting 

50 the discharge plug 236 into the discharge opening 235 and 

securing it in place by advancing the retaining nut 238, as 

shown in FIG. 17. Unlike the conventional plug 204 in FIG. 

9, however, the plug 236 does not have a seal mounted to it 

that seals against the bore 234. Instead, the plug 236 defines 

55 a sealing surface 237 for a seal (not depicted in FIG. 11) that 

is mounted in an endless groove or recess formed by a 

surface 239 of the body 232. The sealing surface 237 is 

axially spaced between a first surface 251 and an opposite 

60 

second surface 253 of the plug 236. 

FIG. 12 is a simplified cross-sectional enlargement 

depicting the construction of the seal positioned within the 

surface 239 of the body 232. The surface 239 forms an 

endless groove or recess 240 that intersects the discharge 

bore 234. A seal 242 in these illustrative embodiments is 

65 mounted in the recess 240 to include an outer radial surface, 

and is thereby supported by the body 232. The recess 240 is 

characterized by a pair of parallel sidewalls joined by a base. 

Case 6:20-cv-00200-ADA Document 46-1 Filed 10/29/20 Page 24 of 27
US 10,591,070 B2 

9 

The recess 240 opens towards a centerline of the conduit 

within which it is formed. Alternatively, as shown by recess 

266 in FIGS. 14-15, the recess may open in a direction 

parallel to a centerline of the conduit within which it is 

formed. As above, the rectangular-groove shape of the 5 

recess 240 is merely illustrative and not limiting of the 

contemplated embodiments. Any shape necessary to properly mount a desired seal is contemplated, whether the seal 

is elastomeric, spring, metal, and the like. As above, the 

recess 240 intersects the bore 234 permitting the seal 242 to 10 

be sized so that a portion of the seal 242 not contained in the 

recess 240 extends beyond the recess 240 and beyond the 

bore 234 to pressingly seal against the sealing surface 237 

(FIG. 11) defined by the discharge plug 236. 

This seal construction depicted in FIG. 12 transfers the 15 

erosion wear from the body to the discharge plug. That 

significantly improves fluid end operations because repairs 

involving the discharge plug 236 are significantly less 

complex and less expensive than repairs involving the body 

232, which typically involve weld-repair. Furthermore, 20 

weld-repairing the body 232 makes it susceptible to premature fatigue cracking in the repaired area. Further, even more 

operating life can be achieved by applying an erosionresistant surface treatment to the plug 236, such as a high 

velocity oxygen fuel (HVOF) treatment, a tungsten carbide 25 

coating, material carburizing, and the like. Replacing instead 

10 

sleeve. The plunger 228 and packing seals 219, shown in 

FIG. 9 and FIG. 17, may be disposed within the stuffing box 

sleeve 254. 

The opening 250 is formed in part by the plunger bore 252 

having a surface 257 defining an endless groove or recess 

intersecting the bore 252, into which a seal (not depicted) is 

mounted in these illustrative embodiments. The suction bore 

247 and the plunger bore 252 together form the second 

conduit. Although these illustrative embodiments use a 

radial seal, the contemplated embodiments are not so limited. In alternative embodiments other types of constructions 

are contemplated by this technology employing axial seals, 

crush seals, and the like. 

FIG. 13 is a simplified cross-sectional depiction of the 

body 232 having the surface 257 forming the recess 258. 

Again, the recess 258 intersects the body bore 252 permitting a portion including an outer radial surface of a radial 

seal 260 to be mounted in the recess 258. Another portion of 

the seal 260 not mounted in the recess 258 extends from the 

recess 258 to pressingly seal against the sealing surface 259 

of the sleeve 254. Although in these depicted embodiments 

a radial seal is used, the contemplated embodiments are not 

so limited. The skilled artisan readily understands that other 

types of seals could be used instead of or in addition to the 

radial seal depicted, such as axial seals, crush seals, and the 

like. 

FIG. 14 depicts a number of additional endless grooves or 

recesses in the body 232 for mounting various seals to 

transfer the wear away from the body 232 to the mating 

of repairing an eroded discharge plug 236 is typically 

feasible, making it advantageously possible to repair a 

leaking valve constructed according to this technology in the 

field and thereby significantly reducing down time. 30 component in accordance with embodiments of this technology. For example, the body 232 has a surface 266 

defining a recess 273 intersecting the body bore that defines 

the discharge opening 235. Consistent with this whole 

Returning to FIG. 11, the body 232 has a surface 241 

defining an endless groove or recess intersecting the bore 

234 and configured to mount a seal (not depicted) that 

extends from the recess to seal against a sealing surface 

formed by a discharge valve seat (not depicted). Similarly, 35 

the body 232 has a surface 243 forming another endless 

groove or recess intersecting the bore 234 and configured to 

mount another seal (not depicted) that is sized to extend 

from the recess to seal against a sealing surface formed by 

a suction valve seat (not depicted). The multiple references 40 

to a same bore 234 is for purposes of ease of description and 

is not narrowing of the contemplated embodiments of this 

technology. Whether the recesses defined by surfaces 241, 

243 are formed in the same bore or different bores does not 

alter the scope of the contemplated embodiments directed to 45 

the recess for mounting the seal is formed in the body, and 

a seal is mounted in the recess and from there seals against 

a sealing surface of a component in a sealing engagement 

there between. 

description, this permits mounting an axial seal 268 (not 

depicted in FIG. 14, see FIG. 15) in the recess 273, the seal 

268 configured to extend from the recess 273 to seal against 

a leading face of the discharge plug 236 (FIG. 11). FIG. 15 

is a simplified enlarged depiction of the body 232 having a 

surface 266 defining the recess 273 into which an axial seal 

268 is mounted. In these illustrative embodiments the seal 

268 is configured to extend beyond the body bore defining 

the discharge opening 235 to seal against the discharge plug 

236 as it is urged downward by advancing the retaining nut 

238 (FIG. 11). 

Importantly, the simplified seal construction depicted in 

FIG. 15 and elsewhere is in no way limiting of the contemplated embodiments and scope of the claimed technology. In 

alternative embodiments a radial seal or a crush seal and the 

like can be employed to transfer the erosion wear from the 

Similarly, a suction bore 247 is sealed closed by inserting 50 body 232 to the mating component. A crush seal refers to a 

seal construction that acts at least to some degree both 

axially and radially. For example, surface 272, shown in 

FIG. 14, forms a recessed comer having two walls that 

extend concentrically around the bore 252 (FIG. 11). The 

a closure or suction plug or cover 244 defining a sealing 

surface 245 and securing it in place by advancing a retaining 

nut 246 in the body 232, as shown in FIG. 17. Like the plug 

236, the sealing surface 245 is axially spaced between a first 

surface 255 and an opposite second surface 261 of the plug 

244. Again, the body 232 in these illustrative embodiments 

has a surface 248 forming an endless groove or recess 

intersecting the bore 247 and configured for mounting a seal 

(not depicted) extending from the recess and sealing against 

the sealing surface 245 of the suction plug 244. That 60 

transfers the wear from the body 232 to the suction plug 244 

in comparison to previously attempted solutions and in 

accordance with the embodiments of this technology. 

The body 232 also forms a plunger opening 250 sized to 

closely receive a stuffing box sleeve 254 that is sealed in 

place by advancing a retaining nut 256, as shown in FIG. 17. 

The stuffing box sleeve 254 is characterized by a tubular 

55 stuffing box sleeve 254 may be formed to have side walls 

that fully overlie the comer section formed by surface 272 

when it is positioned in the bore 252. This allows the seal to 

act as a crush seal because it seals axially and radially 

against the sleeve 254. 

Returning to FIG. 14, the body 232 can have other 

surfaces forming endless grooves or recesses for mounting 

various other seals. For example, surface 270 forms a recess 

for mounting a seal that is configured to seal against a 

sealing surface of a suction plug (not depicted), like in FIG. 

65 15. In the same way the body 232 can have surfaces 272, 

274, 276 forming recesses for mounting seals that are 

configured to seal against sealing surfaces of the stuffing box 

Case 6:20-cv-00200-ADA Document 46-1 Filed 10/29/20 Page 25 of 27
US 10,591,070 B2 

11 12 

this description and meaning of the claims the term "closure" means a component that is attached or otherwise 

joined to the body to provide a high-pressure fluid seal 

between the body and the closure. In some embodiments 

sleeve 254 (FIG. 11), the discharge valve seat (not depicted), 

and the suction valve seat (not depicted), respectively. 

Likewise, the body 232 can have a surface 278 forming a 

recess for mounting a seal that is configured to seal against 

a suction manifold (not depicted). What's common in any 

event is the seal construction of this technology transfers the 

seal wear from the body 232 to the less complex and less 

expensive mating component that is attached to the body 

232. 

5 such as the described valve embodiments "closure" encompasses a moving component that is selectively positionable 

to control the fluid flow through the valve, such as the plug 

described and other components such as but not limited to a 

wedge, a clapper, a ball, a segment, and the like. In some 10 embodiments such as the described fluid end embodiments FIG. 16 depicts the stuffing box sleeve 254 (FIG. 11) 

inserted into the plunger opening 250 so that a seal 260 

mounted in the recess 258 formed by the surface 257 extends 

from that recess 258 and seals against the sealing surface 

259 defined by the stuffing box sleeve 254. As the stuffing 

box sleeve 254 is inserted into this position air pressure 15 

forms in a space defined in the clearance gap between the 

outer diameter of the stuffing box sleeve 254 and the body 

bore defining the plunger opening 250 and between the seal 

260 and a seal 286 at an opposing end of the stuffing box 

sleeve 254. The air pressure exerts a force urging the stuffing 20 

box sleeve 254 out of the plunger opening 250, complicating 

manufacture and degrading the seal integrity at the lower 

end of the stuffing box sleeve 254. A breather opening 284 

can be formed between that space and ambient space above 

the stuffing box sleeve 254 to vent the air pressure. 

"closure" encompasses nonmoving components joined to 

the body to seal an opening such as but not limited to the 

discharge plug, suction plug, discharge valve seat, suction 

valve seat, stuffing box sleeve, discharge flange, suction 

manifold, and the like. The term "means for sealing" means 

the described structures and structural equivalents thereof 

that mount a seal to a body instead of a mating closure to 

transfer the wear in comparison to previously attempted 

solutions from the body to the closure. "Means for sealing" 

expressly does not encompass previously attempted solutions that mount a seal to the closure to extend therefrom and 

seal against the body. 

The various features and alternative details of construe25 tion 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 

FIG. 16 also depicts a conventional construction of the 

seal 286 that is mounted in a recess formed by the stuffing 

box sleeve 254 and extends from that recess to seal against 

the body bore defining the plunger opening 250. The contemplated embodiments can include combinations of the 30 

conventional construction and the construction of this technology where other matters come into play. For example, 

without limitation, it can be feasible to use a stuffing box 

sleeve 254 depicted in FIG. 16 if it can be manufactured or 

otherwise acquired less expensively than providing the 35 

recess instead in the body 232, and if the particular seal 

location is one that is not necessarily critical in its role for 

the overall design for maintaining the highly-pressurized 

fluid in the flow passage. 

FIG. 16 also depicts employing the open-cylinder-shaped 40 

stuffing box sleeve 254 and securing it in place by advancing 

the retaining nut 256 (FIG. 11). That construction is illustrative and in no way limiting of the contemplated technology. Other configurations can be employed as well. For 

example, the skilled artisan understands that a conventional 45 

stuffing box can be employed that combines the stuffing box 

sleeve 254 and the retaining nut 256, unitarily, into one 

component that has a recess for supporting a seal configured 

to seal against the body bore defining the plunger opening 

235. In other conventional constructions a stuffing box 50 

without that recess is used in combination with a seal carrier 

insert that mates with the stuffing box and provides the 

recess for mounting the seal. In yet other contemplated 

embodiments the stuffing box sleeve 254 can be modified to 

a construction combining a substantially cylindrical-shaped 55 

stuffing box to which is mated a seal surface insert that 

provides the sealing surface 259 (FIG. 11). 

Returning momentarily to FIG. 11, the sleeve 254 also 

protects the bore 252 from erosion by providing an inner 

diameter surface 264 against which the stuffing box packing 60 

219 (shown in FIG. 17) seals. That, again, by design 

transfers the wear from the body 232 to the less complex and 

less expensive sleeve 254. 

Summarizing, this technology contemplates a high pressure fluid flow apparatus constructed of a body defining a 65 

flow passage, a closure mounted to the body, and a means for 

sealing between the body and the closure. For purposes of 

advantages of various embodiments of the present technology have been set forth in the foregoing description, together 

with 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. 

The invention claimed is: 

1. A method of manufacturing the fluid end assembly, 

comprising: 

providing a housing having a first conduit extending 

therethrough, and a second conduit extending therethrough that intersects the first conduit; 

forming an endless groove in the housing such that the 

groove surrounds the second conduit; 

positioning a seal within the groove; 

installing a tubular sleeve within the second conduit such 

that at least a portion of the sleeve engages with the 

seal; 

installing a plurality of packing seals within the sleeve; 

and 

installing a reciprocating plunger at least partially within 

the sleeve and the plurality of packing seals. 

2. The method of claim 1, further comprising: 

forming the groove such that it has a pair of parallel side 

walls joined by a base. 

3. The method of claim 1, further comprising: 

forming the groove such that it opens towards a centerline 

of the second conduit. 

4. The method of claim 1, further comprising: 

installing a plug into the first conduit, in which the plug 

is sized to fully block fluid flow within the first conduit. 

5. The method of claim 1 in which the endless groove is 

characterized as the first groove, further comprising: 

forming a second endless groove in the housing such that 

the groove surrounds the first conduit. 

Case 6:20-cv-00200-ADA Document 46-1 Filed 10/29/20 Page 26 of 27
US 10,591,070 B2 

13 

6. A fluid end assembly, comprising: 

a housing having a first conduit extending therethrough, 

and a second conduit extending therethrough that intersects the first conduit; 

an endless groove formed in the housing such that the 5 

groove surrounds the second conduit; 

a seal positioned within the groove; 

a tubular sleeve installed within the second conduit such 

that at least a portion of the sleeve engages with the 

seal; and 

a plurality of packing seals disposed within the sleeve; 

and 

a reciprocating plunger disposed at least partially within 

the sleeve and the plurality of packing seals. 

10 

:·c1~:u~:::~~;s::::1~~;~~~~~; t~t1:~e~i:c:tsing: 15 

8. The fluid end assembly of claim 7 in which the closure 

element is a plug sized to fully block fluid flow within the 

first conduit. 

9. The fluid end assembly of claim 6 in which the first 

conduit is orthogonal to the second conduit. 20 

10. The fluid end assembly of claim 6 in which the groove 

is characterized by a pair of parallel side walls joined by a 

base. 

11. The fluid end assembly of claim 10 in which the seal 

engages the side walls and the base of the groove. 

12. The fluid end assembly of claim 6 in which the groove 

opens towards a centerline of the second conduit. 

13. The fluid end assembly of claim 6 in which at least a 

portion of the housing is configured to contain a fluid having 

a pressure of at least 8,000 pounds per square inch. 

14. The fluid end assembly of claim 6 in which the 

plunger is configured to engage with an engine having a 

power output of at least 2,250 horsepower. 

15. The fluid end assembly of claim 6 in which the endless 

groove is characterized as the first groove, and further 

comprising: 

25 

30 

35 

14 

a second endless groove formed in the housing such that 

the second groove surrounds the first conduit. 

16. The fluid end assembly of claim 15 in which the seal 

is characterized as the first seal, and further comprising: 

a second seal positioned with the second groove. 

17. The fluid end assembly of claim 6, further comprising: 

a valve positioned with the first conduit. 

18. The fluid end assembly of claim 6 in which the second 

conduit has a first and second section, and in which the 

endless groove is characterized as the first groove and is 

formed in the first section of the second conduit, and further 

comprising: 

a second endless groove formed in the housing such that 

the second groove surrounds the second section of the 

second conduit. 

19. The fluid end assembly of claim 18 in which the seal 

is characterized as the first seal, and further comprising: 

a second seal positioned within the second groove. 

20. A system, comprising: 

the fluid end assembly of claim 6; and 

a fluid having a pressure of at least 8,000 pounds per 

square inch within at least a portion of the internal 

chamber. 

21. A system, comprising: 

the fluid end assembly of claim 6; and 

an engine engaged with the plunger and having a power 

output of at least 2,250 horsepower. 

22. The fluid end assembly of claim 6 in which the sleeve 

has an inner surface and an opposed outer surface, in which 

the plurality of packing seals are engaged with the inner 

surface of the sleeve. 

23. The fluid end assembly of claim 22 in which the seal 

is engaged with the outer surface of the sleeve. 

24. The fluid end assembly of claim 6 in which the sleeve 

is of single piece construction. 

* * * * * 

Case 6:20-cv-00200-ADA Document 46-1 Filed 10/29/20 Page 27 of 27