`
`(12) United States Patent
`Bayyouk et al.
`
`(10) Patent No.:
`(45) Date of Patent:
`
`US 8,662,865 B2
`Mar. 4, 2014
`
`(54) OFFSET VALVE BORE INA
`RECIPROCATING PUMP
`
`(71) Applicant: S.P.M. Flow Control, Inc., Fort Worth,
`TX (US)
`
`(72) Inventors: Jacob A. Bayyouk, Richardson, TX
`(US); Donald Mackenzie, Glasgow
`(GB)
`
`(73) Assignee: S.P.M. Flow Control, Inc., Fort Worth,
`TX (US)
`
`(*) Notice:
`
`Subject to any disclaimer, the term of this
`patent is extended or adjusted under 35
`U.S.C. 154(b) by 0 days.
`(21) Appl. No.: 13/849,228
`
`(22) Filed:
`(65)
`
`Mar. 22, 2013
`Prior Publication Data
`US 2013/0216413 A1
`Aug. 22, 2013
`Related U.S. Application Data
`(63) Continuation of application No. 13/314,831, filed on
`Dec. 8, 2011.
`(60) Provisional application No. 61/421,453, filed on Dec
`9, 2010
`pp
`s
`a- - s
`s
`(51) Int. Cl.
`F04B 27/10
`(2006.01)
`F04B 39/2
`(2006.01)
`(52) U.S. Cl.
`CPC ............... F04B 39/122 (2013.01); F04B 27/10
`(2013.01)
`USPC ........................................... 417/269; 417/415
`(58) Field of Classification Search
`CPC ............................... F04B 27/10; F04B 39/122
`USPC ......... 417/415, 269; 92/61, 76, 1711; D15/7,
`D15F9
`See application file for complete search history.
`
`(56)
`
`References Cited
`U.S. PATENT DOCUMENTS
`
`2,666,026 A
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`
`1/1954 Gibbs
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`(Continued)
`FOREIGN PATENT DOCUMENTS
`
`AR
`AR
`
`5, 2013
`O84230 A1
`5, 2013
`O84231 A1
`(Continued)
`OTHER PUBLICATIONS
`Xie He et al.; Fatigue Prediction for Pump End of High Pressure
`Fracturing Pump; Advanced Materials Research vol. 337 (2011) pp.
`81-86.
`
`(Continued)
`Primary Examiner — Bryan Lettman
`(74) Attorney, Agent, or Firm — Haynes and Boone, LLP
`
`ABSTRACT
`(57)
`A fluid end (15) for a multiple reciprocating pump assembly
`(12) comprises at least three plunger bores (61 or 91) each for
`receiving a reciprocating plunger (35), each plunger bore
`having a plunger bore axis (65 or 95). Plunger bores being
`arranged across the fluid head to define a central plunger bore
`and lateral plunger bores located on either side of the central
`plunger bore. Fluid end (15) has suction valve bores (59 or
`89), each suction valve bore receiving a suction valve (41)and
`having a suction valve bore axis (63 or 93). Discharge valve
`bores (57 or 87), each discharge valve bore receiving a dis
`charge valve (43) and having a discharge valve bore axis (63
`or 93). The axes of at least one of suction (10) and discharge
`valve bores is inwardly offset in the fluid end from its respec
`tive plunger bore axis.
`30 Claims, 12 Drawing Sheets
`
`
`
`Page 1 of 23
`
`
`
`(56)
`
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`* cited by examiner
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`US 8,662,865 B2
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`1.
`OFFSET VALVE BORE INA
`RECIPROCATING PUMP
`
`CROSS-REFERENCE TO RELATED
`APPLICATIONS
`
`This application is a Continuation of U.S. patent applica
`tion Ser. No. 13/314,831 filed Dec. 8, 2011, which claims the
`priority to U.S. Provisional Application No. 61/421,453 filed
`Dec. 9, 2010, the entire disclosures of which is incorporated
`herein by reference.
`TECHNICAL FIELD
`
`10
`
`An arrangement is disclosed whereby a valve bore is offset
`from a plunger bore in a fluid end of a reciprocating pump to
`relieve stress.
`
`15
`
`BACKGROUND OF THE DISCLOSURE
`
`In oil field operations, reciprocating pumps are used for
`various purposes. Reciprocating pumps are used for opera
`tions such as cementing, acidizing, or fracturing of a Subter
`ranean well. These reciprocating pumps run for relatively
`short periods of time, but they operate on a frequent basis and
`oftentimes at extremely high pressures. A reciprocating pump
`is mounted to a truck or a skid for transport to various well
`sites and must be of appropriate size and weight for road and
`highway regulations.
`Reciprocating pumps or positive displacement pumps for
`oil field operations deliver a fluid or slurry, which may carry
`solid particles (for example, a sand proppant), at pressures up
`to 20,000 psi to the wellbore. A known pump for oilfield
`operations includes a power end driving more than one
`plunger reciprocally in a corresponding fluid end or pump
`chamber. The fluid end may comprise three or five plunger
`bores arranged transversely across a fluid head, and each
`plunger bore may be intersected by Suction and discharge
`valve bores. In a known reciprocating pump, the axis of each
`plunger bore intersects perpendicularly with a common axis
`of the Suction and discharge valve bores
`In a mode of operating a known three plunger bore recip
`rocating pump at high fluid pressures (for example, around or
`greater than 20,000 psi), a maximum pressure and thus stress
`can occur within a given pump chamber as the plunger moves
`longitudinally in the fluid end towards top dead center (TDC),
`compressing the fluid therein. One of the other pump cham
`bers will be in discharge and thus at a very low pressure, and
`the other pump chamber will have started to compress the
`fluid therein.
`It has been discovered that, in a given pump chamber, the
`areas of highest stress occur at the intersection of each
`plunger bore with its suction and discharge valve bores as the
`plunger moves to TDC. The occurrence of high stress at these
`areas can shorten the life of the fluid end.
`JP 2000-170643 is directed to a multiple reciprocating
`pump having a small size. The pump has three piston bores in
`which the pistons reciprocate but, so that a compact pump
`configuration can be provided, the axis of each Suction valve
`bore is arranged perpendicularly to its respective discharge
`valve bore (that is, so that there is a laterally directed dis
`charge from the fluid end).
`JP 2000-170643 also teaches that a limit as to the volume of
`fluid that can be pumped by a small reciprocating pump is the
`size of Suction and discharge valve bores. Contrary to the
`embodiments disclosed herein, the teaching of JP 2000
`170643 is not concerned with reducing stresses arising at the
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`intersection of piston, Suction and discharge bores. Rather, JP
`2000-170643 teaches moving the axes of each of the outside
`Suction and discharge valve bores outwardly with respect to
`their plunger bore axis, to enable the volume of each of the
`Suction and discharge valve bores to be increased. Thus, with
`an increased pump speed, an increased Volumetric flow can be
`achieved with a pump that still has a similar overall dimen
`sional profile. In addition, JP 2000-170643 teaches that the
`valve bores are moved outwardly without increasing the
`amount of material between the Suction and discharge bores.
`This is because the reconfiguration of the pump in JP 2000
`170643 is not concerned with reducing stresses within the
`pump in use.
`
`SUMMARY
`
`In a first aspect there is disclosed a fluid end for a multiple
`reciprocating pump assembly. The multiple reciprocating
`pump assembly may, for example, comprise three or five
`plunger bores, and may find application in oilfield operations
`and/or may operate with fluids at high pressures (for example
`as high as 20,000 psi or greater).
`When the fluid end comprises at least three plunger bores
`(for example, three or five plunger bores), each can receive a
`reciprocating plunger, and each can have a plunger bore axis.
`The plunger bores can be arranged across the fluid head to
`define a central plungerbore and lateral plungerbores located
`on either side of the central plungerbore (for example, one or
`two lateral plunger bores located on either side of the central
`plunger bore to define a fluid end with three or five plunger
`bores respectively).
`At least three respective suction valve bores (for example,
`three or five suction valve bores) can be provided for and be
`in fluid communication with the plunger bores. Each Suction
`valve bore can receive a suction valve and have a Suction valve
`bore axis.
`At least three respective discharge valve bores (for
`example, three or five discharge valve bores) can be provided
`for and be in fluid communication with the plunger bores.
`Each discharge valve bore can receive a discharge valve and
`have a discharge valve bore axis.
`In accordance with the first aspect, at least one of the axes
`of the suction and discharge valve bores, for at least one of the
`lateral plunger bores, is inwardly offset in the fluid end from
`its respective plunger bore axis.
`It has been surprisingly discovered that this inward offset
`ting can reduce stress that would otherwise occur at the inter
`section of each plunger bore with its Suction or discharge
`valve bores as the plunger moves to TDC. The reduction of
`stress can increase the useful operating life of the fluid end.
`In certain embodiments, at least one of the axes of at least
`one of the suction and discharge valve bores for each of the
`lateral plungerbores may be inwardly offset. For example, for
`the lateral plunger bores, the at least one offset axis may be
`inwardly offset to the same extent as the other at least one
`offset axis.
`In certain embodiments, the axes of both the suction and
`discharge valve bores may be inwardly offset for at least one
`of the lateral plunger bores. For example, the axes of both the
`suction and discharge valve bores are inwardly offset to the
`Same eXtent.
`In certain embodiments, for each of the plunger bores, the
`Suction valve bore may oppose the discharge valve bore. This
`arrangement is easier to manufacture, maintain and service
`than, for example, arrangements in which the axis of each
`Suction valve bore is perpendicular to the discharge valve
`
`Page 16 of 23
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`US 8,662,865 B2
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`3
`bore. In addition, the opposing bore arrangement may induce
`less stress in the fluid end in use than, for example, a perpen
`dicular bore arrangement.
`In certain embodiments for each of the plunger bores, the
`axes of the Suction and discharge valve bores may be aligned,
`for even greater ease of manufacture, maintenance and Ser
`vice. In certain embodiments, the at least one axis may be
`inwardly offset in an amount ranging from about 10% to
`about 60% of the diameter of the plungerbore. In certain other
`embodiments, the offset axis may be inwardly offset in an
`amount ranging from about 20% to about 50%, or from about
`30% to about 40%, of the diameter of the plunger bore.
`In other certain embodiments, the at least one axis may be
`inwardly offset in an amount ranging from about 0.5 to about
`2.5 inches. In certain other embodiments, the offset axis may
`be offset in an amount ranging from about 1.5 to 2.5 inches.
`These dimensions may represent an optimal range for many
`bore diameters of fluid end configurations employed infrack
`ing pumps in oilfield and related applications.
`Other aspects, features, and advantages will become appar
`ent from the following detailed description when taken in
`conjunction with the accompanying drawings, which are a
`part of this disclosure and which illustrate, by way of
`example, principles of the fluid end as disclosed herein.
`DESCRIPTION OF THE FIGURES
`
`4
`just the lateral suction valve bores are inwardly offset from
`their respective plunger bores, and not the discharge valve
`bores.
`FIG.9 schematically depicts a first embodiment of a quint,
`being a partial section of FIG. 1A taken on the line 2-2, to
`illustrate the two lateral valve bore pairs on either side of the
`central valve bore pair being offset inwardly from their
`respective plunger bores.
`FIG. 10 is an underside schematic view of the section of
`FIG. 9 to show a bolt pattern on a fluid end of a cylinder.
`FIG. 11 is a similar view of the quint of FIG. 9, but illus
`trates just the outermost lateral valve bore pairs being offset
`inwardly from their respective plunger bore.
`FIG. 12 is a similar view of the quint of FIG. 11, but
`illustrates just one of the outermost lateral valve bore pairs
`being offset inwardly from its respective plunger bore.
`FIG. 13 is a similar view of the quint of FIG.9, but illus
`trates just the innermost lateral valve bore pairs being offset
`inwardly from their respective plunger bore.
`FIG. 14 is a similar view of the quint of FIG. 13, but
`illustrates just one of the innermost lateral valve bore pairs
`being offset inwardly from its respective plunger bore.
`FIGS. 15 and 16 schematically depict side sectional eleva
`tions as generated by finite elementanalysis (FEA), and taken
`from opposite sides, through a triplex fluid end, to illustrate
`where maximum stress, as indicated by FEA, occurs for the
`intersection of a plunger bore with the Suction and discharge
`valve bores; with FIG. 15 showing no offset and FIG. 16
`showing 2 inches inward offset.
`FIG. 17 is a data point graph that plot Von Mises yield
`criterion (that is, for the maximum stress, in psi, as deter
`mined by FEA) against the amount of valve bore offset (in
`inches) for a single (mono) fluid end and valve bore inward
`offset for a triplex fluid end.
`FIG. 18 is a bar graph that plots Von Mises yield criterion
`(that is, for the maximum stress, in psi, as determined by
`FEA) against different amounts of valve bore offset (in
`inches) for a single (mono) fluid end and a triplex fluid end.
`DETAILED DESCRIPTION OF SPECIFIC
`EMBODIMENTS
`
`Referring to FIGS. 1A and 1B, an embodiment of a recip
`rocating pump 12 housed within a crankshaft housing 13 is
`shown. The crankshaft housing 13 may comprise a majority
`of the outer Surface of reciprocating pump 12. Stay rods 14
`connect the crankshaft housing 13 (the so-called “power
`end') to a fluid end 15. When the pump is to be used at high
`pressures (for instance, in the vicinity of 20,000 psi or
`greater), up to four stay rods can be employed for each
`plunger of the multiple reciprocating pump. The stay rods
`may optionally be enclosed in a housing.
`The pump 12 is a triplex having a set of three cylinders 16,
`each including a respective plungerbore 17. The three (or, in
`the case of a quint, five) cylinders/plunger bores can be
`arranged transversely across the fluid end 15. A plunger 35
`reciprocates in a respective plunger bore 17 and, in FIG. 1A,
`the plunger 35 is shown fully extended at its top dead centre
`position. In the embodiment depicted, fluid is only pumped at
`one side 51 of the plunger 35, therefore the reciprocating
`pump 12 is a single-acting reciprocating pump.
`Each plunger bore 17 is in communication with a fluid inlet
`or suction manifold 19 and a fluid outlet side 20 in commu
`nication with a pump outlet 21 (FIG. 1B). A suction cover
`plate 22 for each cylinder 16 and plunger bore 17 is mounted
`to the fluid end 15 at a location that opposes the plunger bore
`17. The pump 12 can be freestanding on the ground, can be
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`Notwithstanding any otherforms which may fall within the
`scope of the fluid end as set forth in the Summary, specific
`embodiments of the fluid end and reciprocating pump will
`now be described, by way of example only, with reference to
`the accompanying drawings.
`In the Description of the Figures and in the Detailed
`Description of Specific Embodiments, a pump that comprises
`three plunger, Suction and discharge bores is hereafter
`referred to as a “triplex’, and a pump that comprises five
`plunger, Suction and discharge bores is hereafter referred to as
`a “quint', being an abbreviation of “quintuplex.”
`In the drawings:
`FIGS. 1A and 1B illustrate, in sectional and perspective
`40
`views, an embodiment of a reciprocating pump. FIG. 1A may
`depict either a triplex or quint, although FIG. 1B specifically
`depicts a triplex.
`FIG. 2 schematically depicts a first embodiment of a tri
`plex, being a partial section of FIG. 1A taken on the line 2-2,
`to illustrate both lateral (or outside) valve bore pairs being
`offset inwardly from their respective plunger bores.
`FIG. 3 is an underside schematic view of the section of
`FIG. 2 to show a bolt pattern on a fluid end of a cylinder.
`FIG. 4 is a similar view of the triplex to FIG. 2, but illus
`trates just one of the lateral (or outside) valve bore pairs being
`offset inwardly from its respective plunger bore.
`FIG. 5 schematically depicts another embodiment of a
`triplex but using a partial section similar to FIG. 2 to illustrate
`one of the lateral valve bores being inwardly offset to its
`respective plunger bore, as well as the central valve bore
`being offset in a similar direction to its respective plunger
`bores.
`FIG. 6 is an underside schematic view, of the section of
`FIG. 5 to show a bolt pattern on a fluid end of a cylinder.
`FIG. 7 schematically depicts another embodiment of a
`triplex using a partial section similar to FIG. 2, and wherein
`just the lateral discharge valve bores are inwardly offset from
`their respective plunger bores, and not the Suction valve
`bores.
`FIG. 8 schematically depicts another embodiment of a
`triplex using a partial section similar to FIG. 2, and wherein
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`Page 17 of 23
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`5
`mounted, to a trailer that can be towed between operational
`sites, or mounted to a skid such as for offshore operations.
`A crankshaft housing 13 encloses a crankshaft 25, which
`can be mechanically connected to a motor (not shown). The
`motor rotates the crankshaft 25 in order to drive the recipro
`cating pump 12. In one embodiment, the crankshaft 25 is
`cammed so that fluid is pumped from each cylinder 16 at
`alternating times. As is readily appreciable by those skilled in
`the art, alternating the cycles of pumping fluid from each of
`the cylinders 16 helps minimize the primary, secondary, and
`tertiary (et al.) forces associated with the pumping action.
`A gear 24 is mechanically connected to the crankshaft 25,
`with the crankshaft 25 being rotated by the motor (not shown)
`through gears 26 and 24. A crank pin 28 attaches to the main
`shaft 23, shown substantially parallel to axis A of the crank
`shaft 25. A connector rod 27 is connected to the crankshaft 25
`at one end. The other end of connector rod 27 is secured by a
`bushing to a crosshead or gudgeon pin 31, which pivots
`within a crosshead 29 in housing 30 as the crankshaft 25
`rotates at the one end of the connector rod 27. The pin 31 also
`functions to hold the connector rod 27 longitudinally relative
`to the crosshead 29. A pony rod 33 extends from the crosshead
`29 in a longitudinally opposite direction from the crankshaft
`25. The connector rod 27 and the crosshead 29 convert rota
`tional movement of the crankshaft 25 into longitudinal move
`ment of the pony rod 33.
`The plunger 35 is connected to the pony rod 33 for pump
`ing the fluid passing through each cylinder 16. Each cylinder
`16 includes an interior or cylinder chamber 39, which is
`where the plunger 35 compresses the fluid being pumped by
`reciprocating pump 12. The cylinder 16 also includes an inlet
`(or suction) valve 41 and an outlet (or discharge) valve 43.
`Usually the inlet and outlet valves 41, 43 are arranged in an
`opposed relationship in cylinder 16 and may, for example, lie
`on a common axis,
`The valves 41 and 43 are usually spring-loaded and are
`actuated by a predetermined differential pressure. The inlet
`(suction) valve 41 actuates to control fluid flow from the fluid
`inlet 19 into the cylinder chamber 39, and the outlet (dis
`charge) valve 43 actuates to control fluid flow from the cyl
`inder chamber 39 to the outlet side 20 and thence to the pump
`outlet 21. Depending on the size of the pump 12, the plunger
`35 may be one of a plurality of plungers, for example, three or
`five plungers may be utilized.
`The plunger 35 reciprocates, or moves longitudinally,
`toward and away from the chamber 39, as the crankshaft 25
`rotates. As the plunger 35 moves longitudinally away from
`the cylinder chamber 39, the pressure of the fluid inside the
`chamber 39 decreases, creating a differential pressure across
`the inlet valve 41, which actuates the valve 41 and allows the
`fluid to enter the cylinder chamber 39 from the fluid inlet 19.
`The fluid continues to enter the cylinder chamber 39 as the
`plunger 35 continues to move longitudinally away from the
`cylinder 17 until the pressure difference between the fluid
`inside the chamber 39 and the fluid in the fluid inlet 19 is small
`enough for the inlet valve 41 to actuate to its closed position.
`As the plunger 35 begins to move longitudinally into the
`cylinder 16, the pressure on the fluid inside of the cylinder
`chamber 39 begins to increase. Fluid pressure inside the cyl
`inder chamber 39 continues to increase as the plunger 35
`approaches the chamber 39 until the differential pressure
`across the outlet valve 43 is large enough to actuate the valve
`43 and allow the fluid to exit the chamber 39 through the fluid
`outlet 21.
`The inlet valve 41 is located within a suction
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