USOO9500 195B2
`
`(12) United States Patent
`Blume
`
`(10) Patent No.:
`(45) Date of Patent:
`
`US 9,500,195 B2
`Nov. 22, 2016
`
`(54) INTEGRATED DESIGN FLUID END
`SUCTION MANIFOLD
`
`(56)
`
`References Cited
`U.S. PATENT DOCUMENTS
`
`(71) Applicant: George H. Blume, Austin, TX (US)
`
`(72) Inventor: George H. Blume, Austin, TX (US)
`(*) Notice:
`Subject to any disclaimer, the term of this
`patent is extended or adjusted under 35
`U.S.C. 154(b) by 223 days.
`
`(21) Appl. No.: 14/078,366
`
`(22) Filed:
`
`Nov. 12, 2013
`
`(65)
`
`O
`O
`Prior Publication Data
`US 2014/O137963 A1
`May 22, 2014
`
`Related U.S. Application Data
`rial application No. 61/727.289, filed on Nov.
`
`(60)
`
`(2006.01)
`(2006.01)
`(2006.01)
`(2006.01)
`
`(51) Int. Cl.
`F04B 53/16
`F04B 9/09
`F04B 23/06
`F04B 53/10
`(52) U.S. Cl.
`CPC ............. F04B 53/16 (2013.01); F04B 9/1095
`(2013.01); F04B 23/06 (2013.01); F04B 53/10
`(2013.01); Y10T 137/86083 (2015.04)
`(58) Field of Classification Search
`CPC ...... F04B 9/109; F04B 9/1095; F04B 15/04;
`F04B 23/06; F04B 53/16
`USPC ........................... 417/62. 521 568,557 273
`See application file for complete search history.
`
`1, 1945 Smith
`2,366,814 A
`9, 1964 Davidson
`3,146,724. A
`6, 1977 Miller
`4,032,265 A
`4,129,324 A 12, 1978 Jones, Jr.
`3. A 23. R.
`4,512,368 A
`4, 1985 Kaminaka et al.
`4,585,400 A
`4, 1986 Miller
`4,712.578 A 12, 1987 White
`5,311,904 A
`5/1994 Beppu
`5,334,352 A
`8/1994 Johnson
`5,474,102 A 12/1995 Lopez
`5,575,262 A 11/1996 Rohde
`5,765,814 A
`6/1998 Dvorak et al.
`5,960,827 A 10/1999 Rosenberg
`6,418,909 B2
`7/2002 Rossi et al.
`7,506,574 B2 * 3/2009 Jensen .................. F04B 53,007
`417/454
`7,621,728 B2 11/2009 Miller
`2002/10 18660
`8, 2002 Braun et al.
`2010/0322803 A1* 12/2010 Small ...................... FO4B 53/16
`417/454
`* cited by examiner
`Primary Examiner — Devon Kramer
`Assistant Examiner — Chirag Jariwala
`(74) Attorney, Agent, or Firm — Gary W. Hamilton
`(57)
`ABSTRACT
`A fluid end assembly comprising a housing, valve bodies,
`seals, seats, springs, and other associated parts, paired with
`a suction manifold that facilitates bi-directional fluid flow.
`The Suction manifold of this invention is designed to pre
`serve fluid energy that will ensure complete filling of the
`cylinder in extreme pumping conditions. The Suction mani
`fold utilizes a chamber design positioned immediately below
`the Suction valves, eliminating all connecting ducts. Alter
`nate embodiments of this invention include a Suction mani
`fold with an integral fluid dampeners or stabilizers.
`4 Claims, 14 Drawing Sheets
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`Page 1 of 19
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`U.S. Patent
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`Nov. 22, 2016
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`Sheet 1 of 14
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`US 9,500,195 B2
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`POWer
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`Fluid
`End
`Discharge
`Manifold
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`Suction
`Manifold
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`External
`Piping
`Connection
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`Figure 1
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`Page 2 of 19
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`U.S. Patent
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`Nov. 22, 2016
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`Sheet 2 of 14
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`US 9,500,195 B2
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`Tubular
`Connection
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`l.-- B
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`Suction
`Manifold
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`Figure 2A
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`Page 3 of 19
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`U.S. Patent
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`US 9,500,195 B2
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`Power End
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`U.S. Patent
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`Nov. 22, 2016
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`Sheet 4 of 14
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`US 9,500,195 B2
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`Figure 3A
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`Page 5 of 19
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`U.S. Patent
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`NOV. 22, 2016
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`Sheet S of 14
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`US 9,500,195 B2
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`Figure 3B
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`Page 6 of 19
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`U.S. Patent
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`Nov. 22, 2016
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`Sheet 6 of 14
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`US 9,500,195 B2
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`Figure 4
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`Page 7 of 19
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`U.S. Patent
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`Nov. 22, 2016
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`Sheet 7 of 14
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`Bi-Directional Flow
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`Suction Valve
`Duct
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`Sharp Corners:
`Turbulence Areas
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`Assumed
`Uni-Directional
`Flow
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`Zoomie Style Suction Manifold
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`Actual
`Bi-Directional
`Flow
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`Figure 5
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`Page 8 of 19
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`U.S. Patent
`U.S. Patent
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`Nov. 22, 2016
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`Sheet 8 of 14
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`US 9,500,195 B2
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`U.S. Patent
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`Nov. 22, 2016
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`Sheet 10 of 14
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`Figure 6C
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`Page 11 of 19
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`U.S. Patent
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`Nov. 22, 2016
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`Sheet 11 of 14
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`US 9,500,195 B2
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`33
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`Page 12 of 19
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`U.S. Patent
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`NOV. 22, 2016
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`Sheet 12 of 14
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`U.S. Patent
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`Nov. 22, 2016
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`Sheet 13 of 14
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`US 9,500,195 B2
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`Page 14 of 19
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`U.S. Patent
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`Nov. 22, 2016
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`US 9,500,195 B2
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`Figure 8B
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`Page 15 of 19
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`

`

`1.
`INTEGRATED DESIGN FLUID END
`SUCTION MANIFOLD
`
`US 9,500,195 B2
`
`2
`resort to "enhanced recovery methods to insure that an oil
`well is producing at a rate that is profitable. And one of the
`most common methods of enhancing recovery from an oil
`well is known as fracturing. During fracturing, cracks are
`created in the rock of an oil bearing formation by application
`of high hydraulic pressure. Immediately following fractur
`ing, a slurry comprising sand and/or other particulate mate
`rial is pumped into the cracks under high pressure so they
`will remain propped open after hydraulic pressure is
`released from the well. With the cracks thus held open, the
`flow of oil through the rock formation toward the well is
`usually increased.
`The industry term for particulate material in the slurry
`used to prop open the cracks created by fracturing is the
`propend. And in cases of very high pressures within a rock
`formation, the propend may comprise extremely small alu
`minum oxide spheres instead of sand. Aluminum oxide
`spheres may be preferred because their spherical shape gives
`them higher compressive strength than angular sand grains.
`Such high compressive strength is needed to withstand
`pressures tending to close cracks that were opened by
`fracturing. Unfortunately, both sand and aluminum oxide
`slurries are very abrasive, typically causing rapid wear of
`many component parts in the positive displacement plunger
`pumps through which they flow. Accelerated wear is par
`ticularly noticeable in plunger seals and in the Suction (i.e.,
`intake) and discharge valves of these pumps.
`Back pressure tends to close each individual valve
`sequentially when downstream pressure exceeds upstream
`pressure. For example, back pressure is present on the
`Suction valve during the pump plunger's pressure stroke
`(i.e., when internal pump pressure becomes higher than the
`pressure of the intake slurry stream. During each pressure
`stroke, when the intake slurry stream is thus blocked by a
`closed suction valve, internal pump pressure rises and slurry
`is discharged from the pump through a discharge valve. For
`a discharge valve, back pressure tending to close the valve
`arises whenever downstream pressure in the slurry stream
`(which remains relatively high) becomes greater than inter
`nal pump pressure (which is briefly reduced each time the
`pump plunger is withdrawn as more slurry is sucked into the
`pump through the open Suction valve).
`The suction manifold plays a vital role in the smooth
`operation of the pump and valve performance and life. All
`fluid entering the pump passes through the Suction manifold.
`If the Suction manifold is poorly designed, incomplete filling
`of the cylinder may result, which in turn leads to valves
`closing well after the end of the suction stroke, which in turn
`results in higher valve impact loads. High valve impact loads
`in turn result in high stress in the fluid end housing and
`ultimate premature failure of the valves, seats, and/or hous
`1ng.
`To insure complete filling of the cylinder requires fluid
`energy in the Suction manifold and fluid energy in the
`cylinder during the Suction stroke. The pumped fluid typi
`cally acquires fluid energy from the fluid pressure from a
`Small Supercharging pump immediately upstream from the
`pump of this invention. The fluid energy can be dissipated by
`turbulence or friction within the suction filling plumbing or
`line and in the suction manifold. Thus the design of the
`Suction manifold is critical to maintaining fluid energy.
`Fracturing pumps typically pump a very heavy and Viscous
`fluid as the fluid is composed of heavy sand Suspended in a
`gel type fluid. With this type of fluid it is very easy to lose
`fluid energy to friction and/or turbulence.
`A traditional design Suction Manifold is illustrated in
`FIGS. 2A and 2B. The fluid end Sectional view of FIG. 2B
`
`RELATED APPLICATION DATA
`
`This Patent Application claims priority to Provisional
`Patent Application No. 61/727.289, filed on Nov. 16, 2012,
`which, by this reference is incorporated for all purposes.
`
`FIELD OF THE INVENTION
`
`The invention generally concerns high-pressure plunger
`type pumps useful, for example, in oil well hydraulic
`fracturing. More specifically, the invention relates to pump
`Suction manifolds designed to properly feed Suction valves
`utilized in rapid open-close cycling when pumping abrasive
`fluids, such as sand slurries at high pressures.
`BACKGROUND OF THE INVENTION
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`Engineers typically design high-pressure oil field plunger
`pumps in two sections; the (proximal) power section and the
`(distal) fluid section which are connected by multiple stay
`rods. The power section, illustrated in FIG. 1, usually
`comprises a crankshaft, reduction gears, bearings, connect
`25
`ing rods, crossheads, crosshead extension rods, etc. Com
`monly used fluid sections usually comprise a plunger pump
`housing having a Suction valve in a Suction bore, a discharge
`valve in a discharge bore, an access bore, and a plunger in
`a plunger bore, plus high-pressure seals, retainers, etc. FIG.
`1 illustrates a typical fluid section showing its connection to
`a power section by stay rods. A plurality of fluid cylinders
`similar to that illustrated in FIG. 1 may be combined, as
`Suggested in the Quini-plex or five cylinder fluid section
`housing illustrated in FIG. 1. Fluid sections also include a
`suction manifold to supply fluid to the suction bore and
`Suction valve. The Suction manifold is typically attached to
`the fluid section by bolts. The suction manifold is typically
`connected to external piping used to Supply fluid to the
`manifold by a tubular connection on either end of the suction
`manifold. The discharge manifold which allows for the exit
`of the pumped high pressure fluid is usually integral to the
`fluid section.
`Valve terminology varies according to the industry (e.g.,
`pipeline or oil field service) in which the valve is used. In
`Some applications, the term “valve' means just the valve
`body, which reversibly seals against the valve seat. In other
`applications, the term “valve' includes components in addi
`tion to the valve body, such as the valve seat and the housing
`that contains the valve body and valve seat. A valve as
`described herein comprises a valve body and a correspond
`ing valve seat, the valve body typically incorporating an
`elastomeric Seal within a peripheral seal retention groove.
`Valves can be mounted in the fluid end of a high-pressure
`pump incorporating positive displacement pistons or plung
`ers in multiple cylinders. Such valves typically experience
`high pressures and repetitive impact loading of the valve
`body and valve seat. These severe operating conditions have
`in the past often resulted in leakage and/or premature valve
`failure due to metal wear and fatigue. In overcoming Such
`failure modes, special attention is focused on valve sealing
`Surfaces (contact areas) where the valve body contacts the
`valve seat intermittently for reversibly blocking fluid flow
`through a valve.
`Valve sealing Surfaces are Subject to exceptionally harsh
`conditions in exploring and drilling for oil and gas, as well
`as in their production. For example, producers often must
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`US 9,500,195 B2
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`3
`is defined in FIG. 2A. An alternate sectional view at a right
`angle to the sectional view of FIG. 2B is illustrated in FIG.
`3B; this sectional view is defined in FIG. 3A. Sharp corners
`at the intersection of the horizontal main chamber and the
`vertical suction valve feed ducts result in turbulence and loss
`of fluid energy. The manifold of this design is a bi-direc
`tional flow design.
`Zoomie style suction manifolds illustrated in FIGS. 4 and
`5, have gained some acceptance in the industry. By intuition,
`it is incorrectly assumed that that the long Sweep ell style
`ducts reduce turbulence and that the flow in the manifold is
`uni-directional. However because each Suction valve opens
`and closes at different intervals, flow is actually interrupted
`when the valve is closed. Furthermore flow is reversed
`momentarily as the valve closes. When flow reverses, tur
`bulence is generated at the sharp corner positioned at the
`intersection of the main Suction manifold chamber and the
`ell that functions as a duct for feeding the corresponding
`suction valve. When the flow stops in a portion of the
`manifold, some fluid energy is lost and fluid energy is
`expended to resume flow when the suction valve opens. In
`addition there is considerable frictional loss in the long
`sweep ell ducts that the pumped fluid must travel through
`resulting in even greater loss of fluid energy within the
`Zoomie Style Suction manifold.
`SUMMARY OF THE INVENTION
`
`The present invention continues the integrated design
`approach utilized by the inventor in previous patent appli
`cations. The present invention utilizes a plenum chamber
`suction manifold design without ducts utilized in a tradi
`tional suction manifold. The suction manifold of the present
`invention allows for bi-directional flow in the manifold and
`significantly reduces friction and turbulence while maintain
`ing fluid energy. In the plenum chamber design of this
`invention, the entire suction manifold is located directly
`below the fluid end block, eliminating all vertical ducts used
`to feed the suction valves. The plenum chamber design
`replaces ducts with ports concentric with the Suction valves
`and allows fluid to be fed directly to the suction valve. The
`suction manifold of the present invention is attached to the
`bottom of the fluid housing by bolts and a mounting flange
`located across the top of the chamber. The circumferential
`edges of the duct-less ports have full radii equal to the
`thickness of the mounting flange. The radiused edge allows
`bi-direction flow in the manifold and eliminates turbulence
`at the Suction manifold ports.
`High fluid energy is essential in maintaining complete
`filling of the cylinder during the Suction stroke. Incomplete
`filling of the cylinder results in the suction valve closing well
`past the end of the Suction stroke which in turn causes high
`valve impact loads and associated high stresses on the valve
`seat and fluid end.
`The present invention presents a counter-intuitive
`approach to the Zoomie style Suction manifolds in that the
`present invention allows for bi-directional fluid flow with
`minimum turbulence and frictional fluid drag.
`An alternate embodiment of this invention allows for an
`integral Suction dampener or stabilizer to be installed inter
`nal to the suction manifold. Most traditional suction stabi
`lizers have a gas charge which is contained in a bladder
`inside the stabilizer housing, said stabilizer being positioned
`externally, upstream from the Suction manifold of the pump.
`In the alternate embodiment of this invention the gas bladder
`is positioned inside the Suction manifold. The gas charge is
`obviously more compressible than the liquid being pumped
`
`4
`and provides a capacitance or spring effect which in turn will
`absorb the pulsation created by the abrupt flow change as the
`pump Suction valves open and close. During the Suction
`stroke of the pump, each plunger stroke must overcome the
`inertia of the columns of fluid in the suction manifold ducts.
`At the end of each stroke, this inertia must again be
`overcome to bring the fluid columns to rest. Devastating
`damage may occur in the Suction piping as a result of fluid
`cavitation. One common cause of fluid cavitation that can be
`easily remedied is acceleration head losses in the Suction
`piping causing the Net Positive Suction Head (NPSH)
`available to fall below the value required for the pump.
`NPSH is the difference between the total pressure on the
`inlet side of the pump less the vapor pressure of the liquid
`and the friction losses of the suction pipe work. If there is
`insufficient NPSH, the suction stroke of the pump may cause
`the fluid pressure to fall below the vapor pressure of the
`process fluid causing local boiling of the fluid and producing
`vapor bubbles which come out of solution. Once the pres
`Sure increases again, the bubbles collapse producing pres
`Sure waves of high intensity. These pressure waves are
`extremely damaging to the interior of the pump fluid section
`and the valves and seats contained therein.
`Recently cellulous bladders have replaced gas bladders in
`Some applications; in cellulous bladders, the gas is
`entrapped within closed cells inside a near Solid elastomer
`bladder. An elastomeric cellulous bladder consists of mil
`lions of nitrogen filled micro-cells, which are compressible
`to absorb pressure variations. Cellulous bladders have the
`advantage of being maintenance free in that the gas does not
`require routine maintenance by charging with replacement
`gas. Gas bladder style stabilizers require routine charging to
`maintain the required pressure for efficient performance.
`Because gas bladders seek a circular shape when pressur
`ized, gas bladders require simple geometric cross sections
`Such as circles or ellipses. A gas bladder with a circular cross
`section would have a cylindrical Volume. Multiple gas
`bladders can be installed to increase the overall volume of
`the dampener/stabilizer.
`A disadvantage of cellulous bladders is that cellulous
`bladders require more Volume than gas bladders because of
`the Volume elastomers Surrounding each closed cell. Fortu
`nately this disadvantage is offset because cellulous bladders
`constructed of elastomeric materials can be molded into
`complex shapes and thus the overall exterior dimensions can
`be designed to be similar to the exterior dimensions of gas
`bladder stabilizers.
`For optimum performance, the Suction dampener or sta
`bilizer should be located as close to the suction valve of the
`fluid section as possible. The duct-less design of the present
`invention allows for the optimum placement of the Suction
`dampener or stabilizer in very close proximity of the Suction
`valve.
`
`BRIEF DESCRIPTION OF THE DRAWINGS
`
`FIG. 1 is an exterior orthogonal view of a typical plunger
`pump showing the power end section and the fluid section
`with the two ends connected by stay rods. A typical Suction
`manifold is also illustrated.
`FIG. 2A is an exterior view of a typical plunger pump;
`view is taken looking toward the fluid end and Suction
`manifold of the pump.
`FIG. 2B schematically illustrates cross-section B-B of a
`typical high-pressure pump and Suction manifold of FIG.
`2A.
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`US 9,500,195 B2
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`FIG. 3A is an exterior side view of a typical plunger
`pump.
`FIG. 3B schematically illustrates cross-section B-B of a
`typical high-pressure pump and Suction manifold of FIG.
`3A.
`FIG. 4 schematically illustrates an end view from the fluid
`end of a typical high-pressure pump similar to view of FIG.
`2A with the alternate Zoomie style suction manifold.
`FIG. 5 schematically illustrates cross-section of a typical
`high-pressure pump and Zoomie style Suction manifold of 10
`FIG. 4
`FIG. 6A schematically illustrates a cross-sectional view
`through one cylinder of a typical high-pressure pump and
`Suction manifold of the present invention.
`FIG. 6B schematically illustrates an enlargement of area
`B-B of the suction manifold of FIG. 6A.
`FIG. 6C schematically illustrates cross-section C-C of the
`fluid end and suction manifold of FIG. 6A.
`FIG. 6D schematically illustrates cross-section D-D of the
`fluid end and suction manifold of FIG. 6C.
`FIG. 7 schematically illustrates a cross-sectional view
`through one cylinder of a typical high-pressure pump and
`suction manifold of the present invention with multiple
`integral gas bladder fluid dampeners.
`FIG. 8A schematically illustrates a cross-sectional view
`through one cylinder of a typical high-pressure pump and
`Suction manifold of the present invention with an integral
`cellulous Suction fluid dampener.
`FIG.8B schematically illustrates cross-section B-B of the
`fluid end and suction manifold with integral cellulous fluid
`dampener of FIG. 8A.
`
`6
`FIG. 6B schematically illustrates an enlargement of area
`B-B of the suction manifold 30 of FIG. 6A. Suction mani
`fold 30 has mounting flange 34 and a port 33 to facilitate
`transfer of pumped fluid from the suction suction manifold
`central chamber 38 into the suction valve bore 3 of fluid end
`housing 12 and then through the Suction valve 13 and seat
`15. Central passage Suction manifold central chamber 38 is
`utilized to distribute fluid to ports 33. Circumferential edge
`35 of the port 33 is radiused with radius R; radius R is
`approximately equal to mounting flange 34 thickness T.
`FIG. 6C schematically illustrates cross-section C-C of the
`fluid end and suction manifold 30 of FIG. 6A. The cross
`section of FIG. 6C is transverse across all cylinders of the
`housing 12 of the pump fluid section 10. FIG. 6B illustrates
`a Suction manifold 30 of the present invention, comprising
`exterior walls 31 of an undefined shape and substantially
`tubular sections 32 located at either or both ends of the
`suction manifold 30. Tubular section 32 is utilized to con
`nect the Suction manifold 30 to external piping Supplying
`fluid to the pump fluid section 10. Suction manifold 30 also
`comprises a mounting flange 34 usually attached to the fluid
`end housing 12 with bolts (not shown.) Suction manifold 30
`also contains multiple ports 33 located concentric to corre
`sponding suction valve 13. The number of ports in the
`suction manifold 30 being equal to the number of suction
`valves 13 in the pump fluid section. The circumferential
`edge 35 of each port 33 is machined with a radius R that is
`approximately equal to the thickness T of the mounting
`flange 34. Suction dampener central chamber 38 is utilized
`to distribute fluid to ports 33.
`FIG. 7 schematically illustrates an alternate embodiment
`of the suction manifold of the present invention with one or
`more integral gas bladder dampeners or stabilizers 36. FIG.
`7 illustrates a plunger pump fluid section 10" made using a
`housing 12', and having Suction valve bore 3, discharge bore
`5, access bore 9 suction valve 13, seat 15, discharge valve
`17, seat 19, plunger 11 present in a plunger bore 7, inner
`Volume 2. Suction valve spring 23. Suction valve spring
`retainer 27, discharge valve spring 21, discharge cover and
`spring retainer 25 according to some embodiments of the
`disclosure. In FIG. 7 the springs and retainers function to
`provide a mechanical bias to the Suction valve and discharge
`valve, towards a closed position.
`FIG. 7 illustrates a suction manifold 30' of the present
`invention, comprising exterior walls 31' of an undefined
`shape and substantially tubular sections 32 located at either
`or both ends of the suction manifold 30'. Tubular section 32
`is utilized to connect the suction manifold 30' to external
`piping with a corresponding tubular configuration utilized
`for supplying fluid to the pump fluid section 10'. Suction
`manifold 30' also comprises a mounting flange 34' usually
`attached to the fluid end housing 12' with bolts (not shown.)
`Suction manifold mounting flange 34 mates with the bottom
`surface 4 of fluid end housing 12'. Suction manifold mount
`ing flange 34 has thickness T. Suction manifold 30' also
`contains multiple ports 33 located concentric to correspond
`ing suction valve 13. The number of ports in the suction
`manifold 30' being equal to the number of suction valves 13
`in the pump 10'. Suction Manifold 30' contains one or more
`integral fluid stabilizers or dampeners 36 positioned internal
`to the suction manifold wall 31'. Fluid stabilizer 36 is of the
`gas bladder type being cylindrical is shape. Suction mani
`fold 30' is dimensionally larger than suction manifold 30 of
`FIG. 6A due to the inclusion of the one or more fluid
`stabilizers 36. Due to the larger size of manifold 30' mount
`ing flange 34' and fluid end housing bottom surface 4 have
`greater width than similar surfaces in FIG. 6A. Fluid stabi
`
`25
`
`30
`
`DETAILED DESCRIPTION
`
`FIG. 6A schematically illustrates a cross-sectional view
`through one cylinder of a typical high-pressure pump and
`Suction manifold of the present invention. The cross-section
`illustrated of pump fluid section 10 is perpendicular to the
`axes of the suction valve bore 3, discharge bore 5, access
`bore 9, and plunger bore 7. FIG. 6A illustrates a plunger
`pump fluid section 10 made using a housing 12, and having
`suction valve bore 3, discharge bore 5, access bore 9 suction
`valve 13, seat 15, discharge valve 17, seat 19, plunger 11
`present in a plunger bore 7, inner Volume 2. Suction valve
`spring 23, Suction valve spring retainer 27, discharge valve
`spring 21, discharge cover and spring retainer 25 according
`to some embodiments of the disclosure. In FIG. 6A the
`springs and retainers function to provide a mechanical bias
`to the Suction valve and discharge valve, towards a closed
`position. FIG. 6A illustrates a suction manifold 30 of the
`present invention, comprising exterior walls 31 of an unde
`fined shape and substantially tubular sections 32 located at
`either or both ends of the suction manifold 30. Tubular
`section 32 is utilized to connect the suction manifold 30 to
`external piping with a corresponding tubular configuration
`utilized for supplying fluid to the pump fluid section 10.
`Suction manifold 30 also comprises a mounting flange 34
`usually attached to the fluid end housing 12 with bolts (not
`shown.) Suction manifold mounting flange 34 mates with
`the bottom surface 4 of fluid end housing 12. Suction
`manifold mounting flange 34 has a thickness T. Suction
`manifold 30 also contains multiple ports 33 located concen
`tric to corresponding suction valve 13 and suction seat 15.
`The number of ports in the suction manifold 30 is equal to
`the number of suction valves 13 in the pump fluid section 10.
`Suction manifold central chamber 38 is utilized to distribute
`fluid to ports 33.
`
`35
`
`40
`
`45
`
`50
`
`55
`
`60
`
`65
`
`Page 18 of 19
`
`

`

`7
`lizers 36 are located to allow unobstructed fluid passage
`through the manifold 30'. In the preferred embodiment fluid
`stabilizers 36 are positioned near mounting flange 34' in
`close proximity to the ports 33.
`As shown in FIG. 7, manifold 30 has mounting flange 34'
`and multiple ports 33 to facilitate transfer of pumped fluid
`from the suction manifold 30' into the suction valve bore 3
`of fluid end housing 12' and then through the suction valve
`13 and seat 15. Circumferential edge 35 of the port 33 is
`radiused with radius R; radius R is approximately equal to
`mounting flange 34' thickness T, similarly illustrated in FIG.
`6B. Suction manifold central chamber 38' is utilized to
`distribute fluid to ports 33.
`FIG. 8A schematically illustrates another alternate
`embodiment of the suction manifold of the present invention
`with an integral cellulous bladder stabilizer constructed with
`a cellulous bladder versus the gas bladder of FIG. 7. FIG. 8A
`illustrates a plunger pump fluid section 10" made using a
`housing 12', and having Suction valve bore 3, discharge bore
`5, access bore 9 suction valve 13, seat 15, discharge valve
`17, seat 19, plunger 11 present in a plunger bore 7, inner
`Volume 2. Suction valve spring 23. Suction valve spring
`retainer 27, discharge valve spring 21, discharge cover and
`spring retainer 25 according to some embodiments of the
`disclosure. In FIG. 8A the springs and retainers function to
`provide a mechanical bias to the Suction valve and discharge
`valve, towards a closed position.
`FIG. 8A illustrates a suction manifold 30" of the present
`invention, comprising exterior walls 31', tubular sections 32,
`multiple ports 33", mounting flange 34", and radiused cir
`cumferential edge 35 which are identical or nearly identical
`to corresponding features of FIG. 7. Fluid end housing 12'
`and bottom surface 4' are also similar to corresponding
`features in FIG. 7. Suction manifold central chamber 38" is
`utilized to distribute fluid to ports 33'.
`Suction Manifold 30", FIG. 8A, contains one or more
`integral fluid stabilizers or dampeners 37 positioned internal
`to the suction manifold wall 31'. Fluid stabilizers 37 are
`positioned to allow unobstructed fluid passage through the
`manifold 30". In the preferred embodiment fluid stabilizers
`37 are positioned near the mounting flange 34' in close
`proximity to the ports 33'. Suction manifold 30" of FIG. 8A
`utilizes multiple closed cell cellulous bladders 37 as opposed
`to gas bladders in suction manifold 30' of FIG. 7. Unlike gas
`bladder stabilizers 36 in FIG. 7, cellulous bladders stabiliz
`ers 37 can be molded with irregular or complex cross
`sections to optimize performance of the stabilizers 37.
`FIG.8B schematically illustrates cross-section B-B of the
`fluid end and suction manifold 30" of FIG. 8A. The cross
`section of FIG. 8B is transverse across all cylinders of the
`housing 12 of the pump fluid section 10". FIG. 8B illustrates
`a suction manifold 30" of the present invention, comprising
`exterior walls 31' of an undefined shape and substantially
`tubular sections 32 located at either or both ends of the
`suction manifold 30". Suction manifold 30" also comprises
`a mounting flange 34' usually attached to the fluid end
`housing 12 with bolts (not shown.) Suction manifold 30"
`also contains ports 33' located concentric to corresponding
`
`8
`suction valve 13. The number of ports in the suction
`manifold 30" being equal to the number of suction valves 13
`in the pump 10". The circumferential edge 35 of each port
`33' is a radius R that is equal approximately to the thickness
`T of the mounting flange 34", similarly illustrated in FIG. 6B.
`Suction dampener central chamber 38" is utilized to distrib
`ute fluid to ports 33'.
`What is claimed is:
`1. A pump fluid end and a Suction manifold of a design
`that is located immediately below a plurality of suction
`valves in said pump fluid end and preserves fluid energy,
`comprising:
`wherein said Suction manifold has a plurality of ports
`equal to the number of individual Suction valves in said
`plurality of Suction valves,
`wherein each port in said plurality of ports feeds directly
`from a Suction chamber into a corresponding Suction
`valve bore without connecting ducts,
`wherein said suction manifold is constructed with a flat
`top Surface and said Surface also functions as a mount
`ing flange,
`wherein said Suction manifold purls pass through said
`mounting flange; and
`wherein circumferential edges of said ports are radiused
`with a radius approximately equal to a thickness of said
`mounting flange.
`2. A pump fluid end, comprising:
`a plurality of Suction valves;
`a Suction manifold comprising a plenum chamber, said
`suction manifold located immediately below said plu
`rality of suction valves;
`wherein said Suction manifold comprises a plurality of
`ports and wherein the number of ports in said plurality
`of ports is equal to the number of individual suction
`valves in said plurality of Suction valves;
`wherein said each port in said plurality of ports feed
`directly from a suction central chamber into a respec
`tive bore in each individual suction val