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`S 20050200081A1
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`(19} United States
`{12) Patent Application Publication (10) Pub. No.: US 2005/0200081 A1
`(43) Pub. Date: Sep. 15, 2005
`
`Stanton ct al.
`
`(54}
`
`{'75}
`
`l’ACKI NG CARTRIDGES AN I)
`PRESSURE-DAMPEN [NG ELEMENTS F()R
`PLUNGER-TYPE PUMPS
`
`Inventors: Eddie N. Stanton. Odessa. TX (US);
`Michael L. Strickland, Odessa, TX
`(US)
`
`Correspondence Address:
`CRUTSINGER & BOOTH
`1601 ELM STREET
`SUITE 1950
`DALLAS, TX 752014744
`
`Assignee: CL Packing Solutions, Inc.. Odessa. TX
`
`Appl. No;
`
`lllt798,693
`
`Filed:
`
`Mar. 11, 2004
`
`Publication Classification
`
`Int. CL" ...................................................... F16] 1538
`
`{52) U.S. CI.
`
`.............................................................. 277510
`
`(57)
`
`ABSTRACT
`
`A package cartridge is provided for use in the maintenance
`of a packing. bore for :- plunger-type pump. According to one
`aspect, a packing cartridge includes: a generally-cylindrical
`sleeve adapted to he at
`least partially positioned in the
`packing bore, a first abutment ring positioned in the sleeve,
`and a second abutment ring positioned in the sleeve and
`Cit-axially spaced apart from the first abutment ring. Tele-
`scoping structures are operativelv positioned hetwuen the
`first abutment ring and the second abutment ring. According
`to another aspect, a structure forming a circumferential
`pressure—ring groove is provided. A pressure ring is posi—
`tioned in the pressure—ring groove. the pressure ring having
`at
`least one smaller external dimension than an internal
`dimension of the pressure-ring groove, whereby at least one
`clearance is provided between the pressure-ring groove and
`the pressure ring. These aspects can be advantageously
`practiced together.
`
`
`
`Vulcan
`Vulcan
`Ex. 1033
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`Patent Application Publication Sep. 15, 2005 Sheet 22 01‘23
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`US 2005/0200081 A1
`
`Sep. 15, 2005
`
`PACKING CARTRIDGES AND
`PRESSURE-DAMPENING ELEMENTS FOR
`PLUNGER-TYPE PUMPS
`
`(TROSS-REl'iERIjNCE 'I‘() REI._ATED
`APPLICATIONS
`
`[0001] Not applicable
`
`STATEMENT REGARDING FEDERALIX
`SPONSORED RESEARCH OR DEVELOPMENT
`
`[0002] Not applicable
`
`REFERENCE TO MICROFICHE APPENDIX
`
`[0003] Not applicable
`
`TECHNICAL FI ELD
`
`[0004] The present invention generally related to positive-
`displacement pumps, and, more particularly, to pin nger—Iype
`pumps. More particularly still, the invention related to the
`packing seals and assemblies for reciprocating piungers in
`such pumps. The invention also related to the maintenance
`and use of such fluid pumps.
`
`BACKGROUN D
`
`[0005] A positive-displacement pump, sometimes referred
`to as a reciprocating Iluid pump or as a reciprocating power
`pump, is a type of fluid pump driven by pDWer from an
`outside source applied to the pump.
`
`types of reciprocating power
`[0006] There are several
`pumps. Typically, the pumps are classified as being plunger
`pumps or piston pumps. A plunger pump is differentiated
`from a piston pump in that a plunger moves past stationary
`packing, whereas a piston carries packing with it. A major
`problem amociated with positive-displacement fluid pumps.
`especially high-pressure pumps, is that of providing a sat-
`isfactory seal for the piston or plunger.
`
`[0007] The pumps are also classified as either single acting
`or double acting. In a single-acting pump, liquid is dis—
`charged only during the forward stroke of the plunger or
`piston,
`that
`is, during one-half of the revolution.
`In a
`double-acting pump, liquid is discharged during both the
`forward and return strokes of the piston or pair of opposed
`plungers. That is, discharge takes place during the entire
`revolution.
`
`[0008] Further, the pumps are often classified as being
`horizontal or vertical. In a horizontal pump, the axial cen-
`terline of the cylinder is horizontal. In a vertical pump, the
`axial centcrline of the cylinder is vertical.
`
`In addition, the pumps can be classified based on
`[0009]
`the number of plungers or pistons. Asimplex pump contains
`only one piston or one plunger or a pair of opposed plungcrs
`driven by one connecting red. A duplex pump contains two
`pistons or two plungers or two pair of opposed plungers
`driven by two connecting rods. A multiplex pump contains
`more than two pistons or two single-acting or opposed
`plungers. For example, a pump having three plungers or
`pairs of opposed plungcrs is commonly referred to as a
`triplex pump, and a pump having five plungers or pairs of
`opposed plungers is commonly referred to as a quintuplex
`pump.
`
`[0010] Generally, a positive-displacement pump has a
`fluid end (sometimes referred to as the liquid end) and a
`power end.
`
`[0011] The fluid end is that portion of the pump that
`handles the fluid. It consists of a pumping chamber (some«
`times referred to as a compression. fluid, or liquid chamber
`or cylinder), and various ports, valves, and other compo-
`nents.
`
`[0012] The pumping chamber is a chamber or plurality of
`chambers in which the motion of the plunger(s) or piston{s)
`is imparted to the liquid (or fluid). A piston or plunger is
`positioned to reciprocate in a cylindrical port, which can be
`considered to be the pumping chamber or a portion of the
`pumping chamber. The cylindrical port for the piston or
`plunger is a heavy-walled structure adapted for withstanding
`the high forces of containing the reciprocating piston or
`plunger.
`
`[0013] A piston is a cylindrical body that is attachable to
`a rod and is capable of exerting pressure upon a liquid within
`the pumping chamber. A piston usually has grooves for
`containing rings that seal against
`the generally smooth
`interior cylindrical wall of the cylindrical port or against a
`replaceable cylinder liner placed in the cylindrical port as
`the piston reciprocates.
`
`[0014] A plunger is a smooth rod that is attachable to a
`crosshead and is capable of exerting pressure upon a liquid
`within the pumping chamber. Sealing rings for a plunger are
`stationary, the plunger sliding within the rings. The cylin-
`drical port for a plunger-type pump typically has two per-
`tions with dilferent diameters, a plunger bore and an axially
`aligned packing bore. The packing bore has a larger diameter
`adapted than the plunger bore, so that the packing bore is
`adapted for accommodating packing between the interior
`cylindrical wall of the packing bore and the outward cylin-
`drical surface of the plunger.
`
`[0015] The pumping chamber can he made integral with a
`suction manifold and discharge manifold or can be made
`with separate manifolds. A suction manifold is a chamber
`that accepts liquid from the suction port(s) and distributes it
`to the suction valves. A discharge manifold is a chamber that
`accepts liquid from the individual discharge valves and
`directs it to the discharge port(s).
`
`[0016] The power end is that portion of the pump in which
`the rotating motion of the crankshaft
`is converted to a
`reciprocating motion through connecting rods and cross-
`heads. The power frame is that portion of the power end that
`contains the crankshaft, connecting rods, crosshead and
`bearings used to transmit power and motion to the fluid end.
`
`[0017] The power frame of the power end is held in a
`substantiaily permanent, stationary position. The fluid end is
`typically bolted to the power frame and is cradled by the
`power frame. Sometimes, a frame extension connects the
`fluid end to the power frame when the fluid end is not bolted
`directly to the power frame. In any case, the fluid end is not
`unbolted and disconnected from the power end except for
`major maintenance overhaul of the fluid end.
`
`fluid end of a plungervtype pump
`[0018] The typical
`includes a fluid—end pump body having at least one pumping
`chamber. The pumping chamber has a suction port (some-
`times referred to as an intake port}, a discharge port, and a
`
`Vulcan
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`Ex. 1033
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`Page 25 of 50
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`US 2005/0200081 A1
`
`Sep. 15, 2005
`
`cylindrical port (or, in the case of a double-acting plunger-
`type pump, a pair of opposed cylindrical ports). The cylin-
`drical port in a plunger—type pump includes a plunger bore
`and an axially aligned packing bore. In some pumps, an
`internal lubrication port is provided for supplying lubricant
`to the packing bore. which lubricant can be distributed
`around an internal circumference of the packing bore by a
`lantern ring, as well know to those skilled in the art. An
`example of the fluid end of this type of pump with original
`packing and parts for the packing bore is illustrated in FIG.
`1.
`
`[0019] A suction valve is positioned in the suction port
`(e.g.,
`in a cylindrical portion of the suction port
`that is
`sometimes referred to as the suction valve deck). and a
`discharge valve is positioned in the discharge port (eg, in
`a cylindrical portion of the discharge port that is sometimes
`referred to as the discharge valve deck).
`In addition, a
`plunger is positioned to reciprocate in the cylindrical port
`having the packing bore and the plunger bore.
`
`[0020] The suction valve is usually a spring-loaded check
`valve for allowing the flow of fluid from the low-pressure
`side of the pump through the suction port into the pumping
`chamber while preventing the backflow of fluid through the
`snetion port. The discharge valve is usually a spring-loaded
`check valve for allowing the flow of fluid from the liquid
`cylinder through the discharge port to the high-pressure side
`of the pump with preventing backflow of fluid through the
`discharge port. Preferably, although not necessarily,
`the
`suction and discharge valves are vertically disposed in the
`pump, that is, the axis of each of the generally cylindrical
`valves is vertically oriented in the pump body. Furthermore,
`the vertical axes of the suction and discharge valves are
`preferably, although not necessarily, co-axially aligned.
`
`[0021] The plunger of the pump is positioned to recipro-
`cate back and forth in the cylindrical port of the pumping
`chamber. The cylindrical port consists of a heavy-walled
`structural body defining the plunger bore and the packing
`bore, of which at least the interior cylindrical volume of the
`plunger bore can be considered to be at least a portion of the
`pumping chamber. The heavy-walled cylinder of the cylin-
`drical port is designed to withstand the high-reciprocating
`and high-pressure forces to accommodate the plunger. Typi-
`cally, at the limit of its stroke, the plunger lills nearly the full
`length of the cylindrical port, and in some designs exceeds
`the full length of the cylindrical port and extends into
`another portion of the plumping chamber.
`
`[0022] During the back stroke of the plunger, the with-
`drawal of the plunger increases the volume of the pumping
`chamber, which creates decreasing fluid pressure or suction
`in the chamber. This causes the suction valve in the suction
`
`port to open to draw fluid from the low-pressure side of the
`pump into the pumping chamber. The decreased fluid pres-
`sure in the chamber also causes the discharge valve in the
`discharge port
`to close. preventing fluid from the high-
`pressure side of the discharge port from backing up into the
`pumping chamber.
`
`the
`[0023] During the forward stroke of the plunger,
`insertion ofthe plunger decreases the volume of the pump-
`ing chamber, which creates increasing fluid pressure in the
`chamber. This causes the discharge valve in the discharge
`port to open to pump fluid through the discharge valve to the
`high-pressure side of the pump. The increased fluid pressure
`
`in the chamber also causes the suction valve to close,
`preventing high-pressure fluid from the pumping chamber
`from being discharged through the suction port.
`
`[0024] As mentioned above, a “packing bore" is provided
`adjacent the plunger bore in the cylindrical port. The pack-
`ing bore has a generally cylindrical interior wall with an
`internal diameter (“11).”) that
`is larger than an internal
`diameter of the plunger bore and that is co-axially aligned
`with the plunger bore. An annular space is defined between
`the interior wall of the packing bore and a plunger extending
`through the packing bore into the plunger bore.
`in other
`words, the annular space is also substantially the same as the
`difference between the Ll). of the packing bore and the [.D.
`of the plunger bore.
`
`[0025] The packing bore typically has a “seat" (sometimes
`referred to as a “land“} adjacent
`the high-pressure end
`thereof, which is toward the plunger bore. The seat
`is
`generally annular in shape, presenting an annular Surface
`generally facing the low-pressure end of the packing bore,
`which is away from the plunger bore. The annular surface of
`the seat is preferably at a substantially perpendicular angle
`relative to the axis of the interior wall of the packing bore,
`but it can be at an oblique angle. The central opening in the
`seat allows for insertion of the plunger through seat. The seat
`of the packing bore can be formed as a shoulder between the
`interior wall of the packing bore and the plunger bore.
`
`[0026] A removable “gland” (sometimes referred to as a
`“top gland” or “top piece") is typically positioned adjacent
`the low-pressure end of the packing bore. which is away
`from the plunger bore. The gland is for axially capturing and
`squeezing the packing material or packing set positioned in
`the annular space within the interior wall ofthe packing bore
`against the seat ofthe packing bore. Acentral opening in the
`gland allows for insertion of the piston rod or plunger
`through the gland.
`
`[0027] The gland is generally annular in shape, presenting
`an annular surface generally facing the high-pressure end of
`the packing bore, which is toward the plunger bore. The
`annular surface of the gland is preferably at a substantially
`perpendicular angle relative to the axis of the interior wall of
`the packing bore, but it can he at an oblique angle.
`
`[0028] The removable gland typically is formed as a part
`of a body adapted to be removahly secured to the body
`forming the interior wall of the packing bore. For example,
`the gland can have a circumferential flange or flange lobes
`through which bolts can be secured to the body forming the
`interior wall of the packing bore.
`In another design,
`the
`gland can have a circumferential threaded connector adapted
`to screw with a corresponding circumferential
`threaded
`connector on the body forming the interior wall of the
`packing bore, in which case the gland is sometimes referred
`to as a "gland out."
`
`[0029] The packing bore is for accommodating relatively
`soft “packing" in the annular space between the interior wall
`of the packing bore and the plunger. The packing is for
`sealingly engaging the plunger to help prevent fluid leakage
`from around the plunger as it reciprocates in the plunger
`bore, which enables the compression of fluids in the pump-
`ing chamber.
`
`[0030] The packing bore can accommodate various styles
`of packing. l-Iistorically, loose packing material was simply
`
`Vulcan
`Vulcan
`Ex. 1033
`Ex. 1033
`Page 26 of 50
`Page 26 of 50
`
`

`

`US 2005/0200081 A1
`
`Sep. 15, 2005
`
`“stull’ed” into the packing bore. Early on, packing material
`was formed into ring-shaped packing elements. The packing
`elements can be formed into rings having a rectangular or
`square cross-section. The packing rings can be split rings to
`facilitate assembly or removal of the packing rings from the
`packing bore. Because the packing material is relatively soft,
`a plurality ofsuch packing elements is often hacked-up with
`intermediate rigid washer-shaped rings or spacers. More
`recently,
`the engineering of the packing rings and other
`associated parts of the packing set has become increasingly
`sophisticated. The stack ofthe plurality ol’ packing clemean,
`intermediate spacers, and other pieces that can be used in the
`packing bore are collectively referred to as a "packing stack"
`or "packing set" or “packing assembly.
`
`[0031] The seal of the packing bore provides a land area
`for the packing set, including the packing and associated
`parts and pieces. With the packing rings and other pieces of
`a packing set are positioned in place in the packing bore
`against the seat, the plunger inserted through the packing set.
`Then the gland is then positioned in place over the packing
`set. The gland, when tightened, axially compresses and
`squeezes the packing set. This action causes the shape ofsoft
`packing material
`to distort, creating a tight sealing area
`between the packing bore and the outside diameter of the
`plunger, preventing any substantial leak of internal com~
`pressed fluids from around the plunger.
`
`[0032] The packing material (or packing set) is axially
`captured and retained within the interior wall of the packing
`bore between the seat of the packing bore and the gland,
`which is positioned and tightened over the packing. Overv
`tightening of the gland on the packing can cause excessive
`friction as the plunger reciprocates through the packing
`elements, causing exeess wear, heat, and even breakage of
`the plunger.
`
`[0033] As mentioned above, a major problem associated
`with positive-displace ment
`fluid pumps. especially high-
`pressure pumps, is that of providing a satisfactory seal for
`the plunger. This seal has normally been in the form of soft,
`nonabrasivc packing elements adapted to seal the annular
`space between the pump plunger and the bore of the packing
`bore. During the power stroke of the plunger, the internal
`pump pressure acting axially on the packing set helps the
`packing rings to deform or dellect into sealing engagement
`between the reciprocating plunger and the packing here.
`
`[0034] Of course, the packing seals wear as the plunger
`reciprocates, and the fluid pumps require periodic mainte-
`nance to replace the worn seals. The wear on the plunger
`packing is a particularly serious problem when the fluid
`being pumped contains suspended particles of silt, clay,
`sand, or other abrasive material. The abrasive material tends
`to erode the packing causing early and frequent failure.
`Packing failure is normally evidenced by the leakage of fluid
`past the packing. Asmall amount of leakage can be tolerated,
`but when this becomes excessive, the pumping operation
`must be stopped to permit replacement of the packing.
`
`[0035] The typical packing needs to be replaced ever few
`months of pump operation. This maintenance involves
`tedious and time-consuming operations, including removal
`of the packing gland, removal of the worn packing elements
`from the packing bore, re-assembly of new packing ele—
`merits in the packing bore, and replacement and proper
`tightening of the gland.
`
`[0036] Eventually, typically after about two-to-three years
`of pump operation, however,
`the packing bore itself will
`require a major overhaul. During the reciprocating action of
`the plunger, the parts and pieces of the packing set have
`slight movement and this, along with corrosion, vibration
`and other factors, will cause the packing bore surface to
`deteriorate. Further, as the packing wears and loosens, the
`packing will in turn will increasingly wear on the interior
`cylindrical wall of the plunger bore. Eventually, the packing
`bore becomes useless as a sealing surface to prevent the
`compressed product from escaping from the pumping cham-
`ber to the pump exterior. Then it becomes necessary to
`recondition the packing bore diameters in a major overhaul
`of the pump. This is usually done by boring out the packing
`bore inside diameter
`to accommodate a sleeve, which
`replaces the original packing bore sealing surfaces with a
`new one.
`
`[0037] Sometimes it is desirable to change the size of the
`plunger. The diameter of the packing bore, however, must be
`in a reasonable proportion to the diameter of the plunger and
`have a su flicient clearance to accommodate the cross-section
`
`of the packing. For example, a plunger having a 2-inch
`diameter can be positioned in a packing bore having 3-inch
`diameter, which provides a typical circumferential clearance
`of 0.5 inch. This allows for a packing material having a 0.5
`inch crossoeetion (if square packing material is used) to fill
`the annular space between the outside diameter of the
`plunger and the internal packing bore diameter.
`
`[0038] When it is desired to change the size of the plunger,
`the packing bore would then he of the wrong proportion.
`Many times, for example, it is desirable to increase pump
`internal pressures. ()ne way of doing this is to decrease the
`plunger diameter. Doing this, of courSe, increases the clear-
`ance between the plunger bore and plunger outer diameter.
`Up to a reasonable extent, the increased clearance can be
`compensated with a packing having a larger cross-section.
`Alternatively, it is possible to rc-bore and sleeve the original
`packing here to reduce the internal diameter of the packing
`bore, and allow for the use of a packing having a more
`appropriate cross-section. However, this alternative requires
`major overhaul of the pump.
`
`the packing bore is integrally
`in many pumps,
`[0039]
`formed as part ofthe fluid-end body. An example of this type
`of prior-art pump is illustrated in FIG. 1, which is herein-
`after describcd in detail.
`
`In a few pumps, a “smiling box” is permanently
`[0040]
`captured in the fluid—end body by the attached power frame,
`in which case this stufling box provides the packing bore. An
`example of this design is the Wheatley®“323“ pump is
`illustrated in FIG. 2, which is hereinafter described in more
`detail. However,
`this stuffing-box design is adapted for
`major overhaul of the fluid end and does not allow for the
`removal of the stutling box without removing the fluid end
`from the power frame. Essentially,
`the packing bore is
`formed in a non-integrally formed. but permanently installed
`stufiing box in a fluid-end body. The packing is routinely
`maintained without removal of this type of permanently
`installed stuffing box.
`
`in other of pumps, 3 “stuffing box" is permanently
`[0041]
`bolted to the fluid-end body of the pump, although it can be
`removed without removal of the fluid end from the power
`frame. Such a separate stuffing hox is massive and expensive
`
`Vulcan
`Vulcan
`Ex. 1033
`Ex. 1033
`Page 27 of 50
`Page 27 of 50
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`

`US 2005/0200081 A1
`
`Sep. 15, 2005
`
`because, in essence, it is a structural portion of the lluid end
`body. Essentially,
`the packing bore is formed in a non-
`integrally formed, but pem‘tancntly attached smiling box to
`a fluid-cnd body. The packing is routinely maintained with
`out removal of this type of permanently attached stuffing
`box. When the packing bore wears to the point
`it needs
`major service, such a stuffing box portion of the fluid-end
`body can be removed for easier re-manufacturing or re-
`sleeving.
`
`[0042] Conventional plunger packings also present design
`problems in packing assemblies that require lubrication. In
`order to avoid excessive wear on the plunger and excessive
`friction,
`it
`is essential in certain high-pressure pumps to
`maintain a lubricant
`film between the plunger and the
`packing. In such pumps, lubricant is normally introduced
`into the center of the packing through ports formed in the
`packing bore. A lubrication system is employed for this
`purpose, including a lubricating ring. frequently referred to
`in the art as a lantern ring,
`is positioned with packing,
`usually between the packing elements and provides space
`for introducing a lubricant such as oil or grease into the
`packing set The lubricant is normally introduced continu-
`ally at a preset pressure into the lantern ring from an external
`source.
`
`[0043] Over the years, many designs have been tried to
`reduce maintenance costs associated with such fluid pumps.
`however, problems with reliability and maintenance have
`continued to plague the pump technology. It has also been
`desirable to be able to change the size of the plunger used in
`the pumps. Among other designs.
`for example, packing
`cartridges, on Occasion, have been tried as plunger packings
`on reciprocating pumps. The cartridge containing packing
`elements is adapted to be assembled and secured in the
`packing bore. The cartridge. being relatively inexpensive, is
`an expendable member so that when it becomes worn or
`damaged from use, it can be replaced with a new cartridge.
`The packing cartridges of the prior art, however, still have
`various disadvantages.
`
`[0044] US. Pat. No. 3,785,659, entitled "Packing Car-
`tridge for Reciprocating Pump,” issued .Ian. 15, 1974, and
`having for named inventors William C. Maurer and Everett
`I-l. Lock, discloses a packing cartridge for a reciprocating
`pump which includes a sleeve adapted to be connected to a
`recessed end of the fluid end housing and a packing assem-
`bly mounted in the sleeve. A lubricating port formed in the
`sleeve extends from an exposed end thereof to the interior of
`the sleeve and provides means for delivering lubricant to the
`packing assembly. See Abstract. US. Pat. No. 3,785,659 is
`incorporated herein by reference in its entirety.
`
`[0045] U.S. Pat. No. 3,907,307 entitled “Packing Assem-
`bly," issued Sep. 23, 1975, and having for named inventors
`William C. Maurer, Joe K. I-leilhccker, and Everett H. Lock,
`discloses an improved packing assembly for a reciprocating
`pump including from and rear packings, an intermediate
`lubricating ring, and means for preventing the ibrward
`extrusion of the rear packing past the lubricating ring. See
`Abstract. In a described preferred embodiment,
`the anti-
`extrusion means is provided by a backup ring designed to
`cooperate with the rear edge of the lantern ring. A pair of
`outwardly opening and reanvardly extending lip portions are
`formed in a rear edge portion of the lantern ring. The backup
`
`ring is adapted to mate with the rear edge of the lantern ring.
`US. Pat. No. 3,907,307 is incorporated herein by reference
`in its entirety.
`
`[0046] U.S. Pat. No. 4,289,317 entitled "Pump Shaft Clo«
`sure," issued Sep. 15. 1981, and having for named inventor
`I-lenry Kuc, discloses an improved stuffing box to elIect an
`auxiliary static seal with a moveable shaft to allow replace-
`ment of packing elements. The stuffing box includes a
`sealing ring concentrically disposed around the shaft and
`means for mounting the sealing ring radially spaced apart
`from the shaft to permit lubricating fluid to flow between the
`sealing ring and the shaft during movement of the shaft. The
`stufling box also includes a seal container axially moveable
`along the shaft for pressing the sealing ring radially against
`the shaft to form the static seal. See Abstract. U.S. Pat. No.
`
`4,289,317 is incorporated herein by reference in its entirety.
`
`[0047] U.S. Pat. No. 4,758,l35 entitled "Pump Head,”
`issued Jul. 19, 1988, and having for named inventors
`Michael J. Woodward and Robert S. Judson, discloses a
`pump and a stress and fatigue resistant pump head, one
`embodimentofwhich is useful fora high pressure pump and
`having a manifold, a valve cartridge. inlet and outlet valves
`in the valve cartridge, 3 pump fluid cylinder with a recip-
`rocaling plunger therein, a packing cartridge with packing
`for the plunger. The pump head ma)r exhibit one or more of
`the following features: a. increased diameter packing car-
`tridge; b. increased length front bushing; c. inclined inlet
`valve; d. inlet valve spring in valve cartridge on manifold
`side of valve; e. decreased diameter of high pressure seal of
`packing cartridge. See Abstract. US. Pat. No. 4,758,135 is
`incorporated herein by reference in its entirety.
`
`[1.5. Pat. No. 4,878,815 entitled "High Pressure
`[0048]
`Reciprocating Pump Apparatus,” issued Nov. 7. l989, and
`having for named inventor J. Edward Stachowiak discloses
`a high pressure reciprocating pump has a flange plate or
`mounting plate secured to the plunger end of a pump drive
`housing and a suction and discharge manifold is hingedly
`connected therein. A smiling box in bores in the flange plate
`has a central bore receiving one end of the plunger and
`forming a plung