United States Patent (19)
`Grable
`
`(62)
`
`(54) METHOD FOR FABRICATING A
`RECIPROCATING PSTON PUMP
`76 Inventor:
`William A. Grable, Box O, Wayne,
`Okla. 73095
`21 Appl. No.: 634,357
`22 Filed:
`Jul. 25, 1984
`Related U.S. Application Data
`Division of Ser. No. 376,698, May 10, 1982, Pat. No.
`4,477,237.
`51) int. Cl* .............................................. B23P 15/00
`52 U.S. C. .............................. 29/156.4 R; 29/281.1;
`29/281.5; 29/464; 29/559; 29/DIG. 48;
`227/152
`58) Field of Search ............ 29/156.4 R, 281:1, 281.5,
`29/462, 464, 559, DIG. 48; 227/152; 228/160,
`170; 269/43, 246; 417/454, 521, 534, 539
`References Cited
`U.S. PATENT DOCUMENTS
`1,111,943 9/1914 Bennett ................................. 269/43
`1,604,483 10/1926 Roberts ..
`... 269/43X
`1,673,943 6/1928 Herr ...
`29/156.4 R
`2,331,513 10/1943 Stahl ............................... 417/539 X
`2,444,963 7/1948 Taylor ................................. 417/539
`3,935,633 2/1976 Bunker .................................. 29/559
`Primary Examiner-Howard N. Goldberg
`Assistant Examiner-Ronald S. Wallace
`
`56)
`
`Patent Number:
`(11
`45) Date of Patent:
`
`4,553,298
`Nov. 19, 1985
`
`Attorney, Agent, or Firm-Hubbard, Thurman, Turner
`& Tucker
`ABSTRACT
`(57)
`A fabricated reciprocating piston pump having a power
`end frame characterized by spaced apart elongated
`precut steel plate members forming the frame sidewalls
`and forming bearing support members for supporting
`the jackshaft and eccentric shaft bearings. The shaft
`bearings are mounted in cylindrical sleeves which are
`supported by respective pairs of the frame plate mem
`bers. The pump includes crossheads which are of rect
`angular cross-sectional shape having flat parallel bear
`ing surfaces and which are supported in the frame by
`elongated crosshead slide plates which may be adjusted
`laterally and vertically to align the crossheads with the
`axis of reciprocation of the pump piston rods. The pump
`fluid end is made up of premachined cylindrical tube
`and bar stock sections which are welded together into a
`unitary assembly including the pump cylinders, the
`suction and discharge valve housings, and the suction
`and discharge fluid manifolds. The power end frame is
`fabricated using a fixture for supporting precut steel
`plate members and premachined bearing support sleeve
`members whereby the power end frame may be fabri
`cated by welding the frame members together in a fix
`ture so that upon removal of the frame from the fixture,
`no further machining of the shaft bearing bores or the
`crosshead bearing surfaces is required.
`6 Claims, 11 Drawing Figures
`
`
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`1.
`
`5
`
`10
`
`15
`
`METHOD FOR FABRICATING A
`REC PROCATING PSTON PUMP
`This application is a division of application Ser. No.
`376,698, filed May 10, 1982, now U.S. Pat. No.
`4,477,237, issued Oct. 16, 1984.
`BACKGROUND OF THE INVENTION
`1. Field of the Invention
`The present invention pertains to a reciprocating
`multi-cylinder piston pump of the type generally used
`for oil field mud and injection fluid pumping and which
`is of a fabricated substantially all welded construction of
`both the fluid end section and the power end section.
`2. Background Art
`There are many applications for reciprocating piston
`pumps which are particularly adapted for pumping
`relatively large volumes of fluid at pressures of 3,000 to
`5,000 psig. One of the more demanding applications for
`20
`this type of pump is in oil field rotary drilling mud
`circulation service and for pumping fluids used in pro
`cesses for enhanced recovery of subterranean petro
`leum deposits. The historic cyclical demand for oil field
`drilling mud pumps, for example, has made the capital
`25
`investment necessary for producing these types of
`pumps generally unattractive to many machinery manu
`facturers. Oil field mud pumps have traditionally been
`designed as duplex reciprocating types having a double
`acting piston and cylinder arrangement which dictates
`the utilization of a crosshead mechanism for intercon
`necting the piston rod with a crankshaft and connecting
`rod or eccentric assembly. This general design concept
`has resulted in the development of relatively large
`frames or crankcase housings for the crank or eccentric
`35
`shaft and crosshead mechanism, which housings have
`traditionally been formed as large unitary iron or steel
`castings. By the same token, the fluid end or cylinder
`assemblies together with the cylinder heads and valve
`housings have also been formed as relatively large cast
`40
`ings or fabricated from steel billets which have been
`machined to form the necessary cylinder bores and
`connecting fluid passageways. Prior art methods of
`manufacturing large reciprocating piston type pumps
`using cast crankcases or power ends as well as cast fluid
`45
`end or cylinder assemblies have required sizable invest
`ments in machine tools necessary to form the bearing
`bores and the crosshead guide bores. Moreover, the
`capital investment required to manufacture casting pat
`terns and provide the available foundry facilities has
`50
`also contributed to the high cost of oil field type recip
`rocating pumps.
`Notwithstanding the problems associated with the
`cost of capital equipment necessary for fabricating oil
`well drilling mud pumps and the like, the nature of the
`application of this type of pump also requires that the
`pump be moved frequently from one drilling site to
`another. It is therefore also desirable to provide a pump
`which is as lightweight as possible and at the same time
`is able to withstand the mechanical stresses endured in
`pumping relatively large volumes of drilling mud at
`high working pressures. For example, a typical prior art
`drilling mud pump, capable of delivering from 200 gal
`lons per minute to 600 gallons per minute at 1,000 to
`3,000 psig, respectively, may weigh up to 52,000 lbs.
`65
`complete with a standard supporting frame or skid. A
`pump of the aforementioned capacity typically has
`input power requirements ranging from 700 to 800 hp.
`
`4,553,298
`2
`Accordingly, there has been a longfelt need for the
`development of a suitable reciprocating pump which is
`relatively lightweight while yet capable of reliable ser
`vice under the operating specifications such as those
`indicated hereinabove and which may be fabricated
`without the tooling and other capital equipment re
`quirements associated with the manufacture of large
`machines.
`There have been several efforts in the prior art of
`reciprocating pumps to develop pumps of fabricated
`construction such as the manufacture of the crankcase
`using built up construction of welded together or me
`chanically fastened together plate and other structural
`parts. However, prior art efforts have primarily been
`directed to pump structures which merely use fabri
`cated parts instead of cast parts, and the assembled
`power end frames and fluid ends still require extensive
`machining operations with large boring equipment. In
`fact, the configuration of some prior art fabricated
`pump structures actually increases the weight of the
`pump versus the weight of a comparable pump using
`cast crankcase or power end housings as well as cast
`cylinder assemblies. The problems associated with the
`need to provide accurate alignment of the bearings and
`bearing supports for the pump drive mechanism, includ
`ing the jackshaft, the crank or eccentric shaft and the
`crosshead guides, have not been overcome with prior
`art designs. However, several problems associated with
`efforts to design a suitable completely fabricated recip
`rocating piston pump have been overcome with the
`present invention as will be appreciated by those skilled
`in the art.
`SUMMARY OF THE INVENTION
`The present invention provides a substantially com
`pletely fabricated reciprocating piston pump, particu
`larly of the type utilized for pumping large quantities of
`fluids such as well drilling mud and the like at relatively
`high pressures and flow rates, and wherein such a pump
`must be reliable in operation and adapted to be some
`what portable. In accordance with an important aspect
`of the present invention, there is provided a reciprocat
`ing piston pump having a power end or crankcase hous
`ing structure which is formed entirely of structural
`metal components available as standard mill shapes and
`which require a minimum of machining other than that
`which can be accomplished utilizing relatively small
`machine tools such as engine lathes or the like. The
`pump power end frame of the present invention is fabri
`cated of a plurality of longitudinal plate members
`spaced apart to form the outer walls of a casing includ
`ing crosshead guide supporting structure, said casing
`further including additional sets of spaced apart plates
`which form bearing support structure for the pump
`jackshaft and crankshaft bearings.
`In accordance with another aspect of the present
`invention, there is provided a pump casing or power
`end frame in which bearing support members for the
`jackshaft and crankshaft bearings are formed from steel
`tube or cylindrical rod stock and are prebored before
`assembly with the power end frame structure so that,
`upon assembly of the power end frame, no further ma
`chining is necessary.
`In accordance with another important aspect of the
`present invention, there is provided an improved cross
`head and crosshead guide configuration which does not
`require precision machining of an integral part of the
`power end frame of the pump. The crosshead configu
`
`30
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`55
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`Page 10 of 17
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`

`

`4,553,298
`4.
`3
`port members for the pump jackshaft and eccentric
`ration of the present invention contemplates the provi
`shaft may be prebored and assembled with the addi
`sion of a crosshead member having a rectangular or
`square cross-sectional configuration forming substan
`tional frame structure so that, upon fabrication of the
`power end frame, no further machining of the frame
`tially flat bearing surfaces which are in sliding engage
`structure is required. The improved method of fabricat
`ment with longitudinal crosshead guides. The crosshead 5
`guides are advantageously formed as a plurality of
`ing a pump power end frame also includes the provision
`of a unique fixture or support structure for supporting
`platelike members which may be adjusted to provide
`the components of the power end frame so that they
`accurate alignment of the crosshead with the linear
`may be welded together to form a unitary frame struc
`reciprocating line of action of the piston rod and
`ture which may then be conveniently removed from the
`wherein the crosshead guides may be easily removed 10
`supporting fixture.
`and new crosshead guides may be inserted and adjusted,
`Those skilled in the art of reciprocating piston pumps,
`as needed, to provide the desired alignment. In accor
`particularly of the type designed for well drilling fluid
`dance with the improved crosshead guide arrangement,
`service, will recognize the superior and unexpected
`there is also provided an improved means for adjusting
`improvements provided by the present invention upon
`the position of the crosshead guides to provide the 15
`proper alignment of the crosshead and to adjust the
`reading the detailed description which follows in con
`junction with the drawings.
`clearances between the bearing surfaces of the cross
`head and the crosshead guides.
`BRIEF DESCRIPTION OF THE DRAWINGS
`Another important aspect of the present invention
`pertains to a reciprocating piston pump having a built 20
`FIG. 1 is a longitudinal side elevation of the recipro
`cating piston pump of the present invention;
`up crankshaft or eccentric shaft assembly including a
`cylindrical shaft to which are removably mounted ec
`FIG. 2 is a plan view, partially broken away, of the
`centrics or crank throw members having connecting
`pump illustrated in FIG. 1;
`rod shaft or crank pin portions which are also sepa
`FIG. 3 is a transverse end view, partially sectioned, of
`the pump illustrated in FIGS. 1 and 2;
`rately fabricated as cylindrical shaft elements and are 25
`FIG. 4 is a longitudinal section view taken substan
`force fitted into bores in the eccentric members. The
`pump jackshaft and eccentric shaft are supported in
`tially along the line 4-4 of FIG. 2;
`self-aligning rolling element type bearings, preferably
`FIG. 5 is a section view taken substantially along the
`spherical roller bearings, whereby minor misalignment
`line 5-5 of FIG. 1;
`of the bearing supports may be easily accommodated 30
`FIG. 6 is a perspective view of the crosshead and
`crosshead guide arrangement;
`without imposing undue stress or friction on the rotat
`ing parts.
`FIG. 7 is a section view taken substantially along the
`In accordance with a still further aspect of the present
`line 7-7 of FIG. 1;
`FIG. 8 is a detail plan view of one of the crossheads;
`invention, the crank mechanism of the pump includes
`fabricated connecting rod and eccentric elements which 35
`FIG. 9 is a side elevation of a fabrication fixture for
`manufacturing the power end frame of the pump illus
`may be conveniently cut from steel mill plate or billets
`trated in FIGS. 1 through 8;
`and which may be conveniently machined on relatively
`FIG. 10 is a plan view of the fixture illustrated in
`small machine tools to provide suitable bores for mount
`ing the eccentric on the eccentric shaft and for mount
`FIG. 9; and
`ing the connecting rods on the crank pin portions.
`40
`FIG. 11 is an end view of the fixture.
`In accordance with yet another aspect of the present
`DESCRIPTION OF THE PREFERRED
`invention there is provided a reciprocating piston pump
`EMBODIMENTS
`of the so-called duplex type having a fabricated fluid
`end cylinder structure comprising a pair of spaced a
`In the description which follows, like parts are gener
`ally marked throughout the specification and drawings
`part cylinder members which are interconnected by 45
`with the same reference numerals, respectively.
`structure forming the fluid inlet and outlet manifolds
`Referring to drawing FIGS. 1, 2 and 3, there is illus
`together with housing members for the suction and
`trated an improved reciprocating piston pump in accor
`discharge valves and wherein all of the aforementioned
`dance with the present invention which is particularly
`structure may be fabricated using standard structural
`adapted for pumping circulation fluid or "mud' in the
`metal tubing or cylindrical bar stock shapes. Accord- 50
`ingly, the fluid end structure may be prefabricated from
`drilling or oil wells and the like. The pump according to
`generally cylindrical tube and bar components by ma
`the present invention, generally designated by the nu
`chining the cylinder bores, the cylinder liner tubes, and
`meral 14, includes a power end frame or casing, gener
`the suction and discharge valve bores, on relatively
`ally designated by the numeral 16, and a fluid end sec
`tion which is removably bolted to the power end frame
`small machine tools, such as engine lathes, and whereby 55
`and is generally designated by the numeral 18. The
`these components are then subsequently assembled into
`power end frame 16 comprises a casing for an elongated
`a unitary fluid end structure by welding processes.
`In accordance with a still further aspect of the present
`shaft 20, FIG. 2, which is characterized as a crankshaft
`invention, there is provided a reciprocating piston
`or, in the art of reciprocating pumps, sometimes known
`pump of the duplex type which is relatively lightweight 60
`as an eccentric shaft. The shaft 20 is mounted within a
`crankcase portion 22 of the power end frame on suitable
`and wherein the power end frame or casing is formed
`bearings as will be explained in detail further herein.
`integral with a supporting substructure or skid of the
`type typically used for oil well drilling pumps and the
`The eccentric shaft 20 is adapted to be connected to a
`like, and wherein the supporting skid comprises struc
`pair of spaced apart connecting rods 24 and 26, which in
`ture which strengthens the power end frame.
`turn are connected to respective crosshead members 28
`and 30 for converting the oscillating connecting rod
`The present invention also provides an improved
`method of fabricating a reciprocating piston pump, in
`motion to linear reciprocating motion for reciprocating
`particular the power end frame, wherein bearing sup
`respective pump pistons 32 and 34 which are disposed
`
`65
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`Page 11 of 17
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`4,553,298
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`6
`within respective bores 36 and 38 formed within a pair
`head support portions 19 and 21 are provided with
`of spaced apart cylinder assemblies 40 and 42. The cyl
`suitable access openings 89, 91 and 93, the first two of
`inders 40 and 42 comprise a major portion of the fluid
`which are covered by removable cover plates 92 and
`end section 18 and will also be described in further
`94, to provide access to the crossheads 28 and 30 and
`detail herein.
`the crosshead or pony rods. The power end frame 16 is
`The power end frame 16 is also adapted to rotatably
`also provided with suitable strengthening web members
`support a jackshaft 44 having a distal end portion 46
`96, 97, 98 and 99 which extend between the crosshead
`projecting from one side of the crankcase portion 22.
`support portions 19 and 21.
`The jackshaft 44 is adapted to include suitable means for
`The power end frame 16 is fabricated in accordance
`drivably engaging the eccentric shaft 20 such as a
`with a unique method, including a novel fabrication
`sprocket and endless chain arrangement or a pinion and
`fixture according to the present invention, to comprise
`drive gear arrangement in accordance with conven
`a unitary assembly made up of high strength steel plate
`tional practice in the art of reciprocating piston pumps.
`which may be conveniently precut by known plate
`The general arrangement of the jackshaft, eccentric
`cutting techniques to the respective shapes illustrated in
`shaft, crossheads and pistons as described hereinabove,
`the drawing figures. The plates 50, 52, 54, 56, 58 and 60
`15
`is known in the art of reciprocating piston pumps. How
`are welded along their respective contiguous edges to
`ever, the combination of the various components of the
`the top wall 88, the vertically inclined crankcase wall
`pump 14 is believed to provide a unique fabricated
`part 62, and the crankcase bottom wall parts 82, 84 and
`structure which represents an improvement in the art of
`86. The vertically disposed transverse plate 64 is welded
`reciprocating pumps. In particular, the structural fea
`to the plate members 54, 56, 58 and 60 along respective
`20
`tures of the power end frame 16 are believed to be
`contiguous edges. The flanges 66 and 68 are also welded
`advantageous and superior to prior art pumps in several
`to the respective distal ends of the plate members 50, 52,
`respects.
`54 and 56 also, along their respective contiguous edges.
`Referring now to FIGS. 2, 4 and 7, the power end
`The plate member 78 is welded at its opposite ends to
`frame 16 includes a first pair of spaced apart and gener
`the members 66 and 82, respectively, and the plate
`25
`ally parallel flat plate members 50 and 52 which com
`member 80 is welded at its opposite ends to the plate
`prise the outer walls of the crankcase portion 22, and
`members 68 and 82. Both of the plate members 78 and
`respective crosshead support portions 19 and 21. The
`80 are welded along their longitudinal opposed edges to
`power end frame 16 also includes a second pair of gen
`the respective pairs of plate members 50-54 and 52-56
`erally flat plate members 54 and 56 forming the opposite
`to form the respective crosshead support portions 19
`30
`sidewalls of the respective crosshead support portions
`and 21. The plate members 70 and 74 are also welded to
`19 and 21 and also forming the bearing support means
`the portions of the plate members 50 and 54 comprising
`for supporting the bearings of the eccentric shaft 20 and
`the crosshead support portion 19 and, in a similar fash
`the jackshaft 44. The power end frame 16 further in
`ion, the plate members 72 and 76 are welded to the plate
`cludes a third pair of spaced apart generally flat plate
`members 52 and 56 along the portions of these members
`35
`members 58 and 60 extending parallel to the first and
`comprising the crosshead support portion 21. Webs 96,
`second pairs of plate members described above. As
`97, 98 and 99 are also welded along their respective
`contiguous edges to the adjacent portions of the plates
`shown in FIGS. 2 and 7, the plate members 58 and 60
`are disposed between the plate members 54 and 56 and
`54 and 56, respectively. The webs 97 and 98 are also
`extend from a rear, vertically inclined wall 62 forward
`welded along a transverse edge to the plate member 64.
`The lightweight and substantially rigid power end
`to a vertical, transverse wall 64 which extends between
`the plate members 54 and 56.
`frame structure described herein, is further strength
`The forward ends of the crosshead support portions
`ened by forming the power end frame section 16 inte
`19 and 21 include, respectively, vertical extending plate
`gral with a support skid generally designated by the
`members 66 and 68 which comprise mounting flanges
`numeral 100. Referring particularly to FIGS. 1, 4, 5 and
`45
`for the respective cylinder members 40 and 42. The
`7, the skid 100 comprises a pair of spaced apart and
`crosshead support portions 19 and 21 are also, respec
`parallel longitudinal beam members 102 and 104 which
`tively, provided with transversely extending vertical
`are interconnected at their opposite ends by transverse
`wall sections 70 and 72 spaced from the flanges 66 and
`steel tubular sections 106 and 108. The skid 100 is con
`68, as indicated in FIGS. 2, 4 and 5. The wall portions
`structed in accordance with oilfield equipment practice
`50
`70 and 72 extend downward from integral top cover
`but has been adapted to form an integral part of the
`plate portions 74 and 76 to generally horizontally ex
`power end frame 16 and further strengthens the frame
`tending bottom walls 78 and 80, respectively. The hori
`in accordance with the arrangement described herein
`zontal bottom wall portions 78 and 80 extend from the
`below. The beam members 102 and 104 are preferably
`flanges 66 and 68, respectively, toward the crankcase
`of I beam or H beam construction including, as illus
`portion 22 to a point generally adjacent the vertical
`trated in FIGS. 5 and 7, opposed parallel flanges 105
`and 107 which are integral with a connecting web 109.
`transverse plate 64, and extend between the vertical
`sidewalls of the crosshead support portions 19 and 21 to
`The beam members 102 and 104 are spaced apart such
`be contiguous with the respective pairs of plates 50-52
`that the webs 109 are outside the adjacent crankcase
`and 52-56.
`outer wall portions formed by the plates 50 and 52. As
`shown in FIG. 4, by way of example, the longitudinal
`The crankcase portion 22 is also characterized by a
`bottom pan portion comprising inclined sidewall parts
`bottom edges of the plates 50 and 52 extending along
`82 and 84. FIG. 4, which are contiguous along respec
`the crosshead support portions 19 and 21, respectively,
`are disposed along the top edge of the beam flanges 105
`tive edges with a horizontal bottom wall 86. The wall
`parts 82, 84 and 86 extend between the outer sidewalls
`and are welded thereto. The beam flanges 105 are cut
`65
`50 and 52. The crankcase portion 22 is closed by an
`away in the area of the crankcase portion 22 to accom
`integral top wall portion 88 and a removable cover
`modate the bottom wall of the crankcase portion and
`which forms a sump for lubricating oil. The flanges 105
`member 90. As shown in FIGS. 1, 2, 4 and 5, the cross
`
`55
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`Page 12 of 17
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`4,553,298
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`tion is normally immersed in a quantity of oil which is
`may be welded to the bottom wall portions 82, 84 and
`86 along respective contiguous edges and the opposed
`maintained at a level indicated by the numeral 131.
`Accordingly, in operation, the sprocket 126 and the
`plate members 50 and 52 are also welded along contigu
`ous edges with the respective web portions 109 of the
`chain 120 are continually lubricated through immersion
`beam members 102 and 104. Accordingly, the pump 14
`in lubricating oil and a considerable amount of oil is
`is advantageously strengthened by welding the skid 100
`carried with the chain 120 upward and bathes the
`sprocket 118. Oil which drains away from the chain 120
`to the outer sidewalls of the frame 16 to connect the
`and the sprocket 118, in the vicinity of the shaft 44,
`frame to the skid and to strengthen the frame structure
`collects in a trough 133, FIG. 7, extending between the
`itself.
`Referring now to FIGS. 4 and 7, in particular, the
`plates 58 and 60. Additional troughs 135 and 137 extend
`power end frame 16 is also provided with a unique
`between the plates 50-54 and 52-56, as shown in FIG. 7
`arrangement for supporting the bearings which journal
`and also in FIG. 4. Oil collecting in the trough 133
`the jackshaft 44 and the eccentric shaft 20. As illustrated
`accumulates to a level which will allow it to flow
`through the bearing assemblies 114 into the troughs 135
`in FIG. 7, the pair of plates 54 and 58 and the pair of
`and 137. The cross-sectional shape of trough 135 is
`plates 56 and 60 are spaced apart from each other and
`15
`are provided with suitable generally cylindrical open
`typical of the shape of the troughs 133 and 137 also. Oil
`ings 59 and 61 for receiving opposed cylindrical bearing
`accumulating in the troughs 135 and 137 flows through
`support sleeves 110 and 112. The bearing support
`respective conduits 134 to lubricate the crossheads 28
`sleeves 110 and 112 are preferably formed by machining
`and 30. The considerable distribution of oil throughout
`the interior of the crankcase portion 22 from the action
`steel tube stock or the like to provide the sleeve mem
`20
`bers with integral flange portions 111 and 113, respec
`of the sprocket 126 and the chain 120 will also result in
`tively, for locating the sleeve members against the re
`the collection of oil in a small reservoir portion formed
`spective plates 54 and 56 as illustrated. The sleeves 110
`along the top surface of each of the sleeves 112 by a dam
`and 112 are assembled with the other structure compris
`140, one of which is illustrated in FIG. 4. The dams 140
`extend between the respective pairs of plates 54-58 and
`ing the power end frame 16 and are welded in place
`25
`along their surfaces which are contiguous with the
`56-60. Each of the sleeves 112 is also provided with a
`plates 54, 58, 56, and 60, respectively. The jackshaft 44
`passageway 141, shown by way of example in FIG. 4,
`is supported in the sleeves 110 by spaced apart spherical
`which allows oil to drain from the aforementioned re
`self-aligning roller bearing assemblies 114. The bearing
`servior formed by the outer surfaces of the sleeves and
`assemblies 114 are butted against opposed shoulders
`the dams 140 into the eccentric shaft bearings 122.
`30
`Referring further to FIGS. 4 and 7, the eccentric,
`formed on the shaft portion 47 in accordance with con
`connecting rod and crosshead arrangement will be de
`ventional practice, and the shaft 44 is retained in assem
`bly with the bearing assemblies 114 by opposed lock
`scribed in connection with the connecting rod 24 and
`nuts 116 threaded onto spaced apart threaded portions
`crosshead 28. It will be understood that the general
`arrangement is substantially identical for the connecting
`formed on the shaft 44 in a conventional manner. The
`35
`central portion 47 of the shaft 44 is provided with an
`rod 26 and the crosshead 30. The distal ends of the
`elongated keyway 49 for receiving a conventional drive
`eccentric shaft 20 are each adapted to support an eccen
`tric member 142 comprising a steel, generally rectangu
`key, not shown. The shaft 44 is adapted to drivably
`lar plate having a bore 144, FIG. 4, and adapted to have
`support a sprocket 118 for an endless roller drive chain
`a pair of opposed jaw portions 143 and 145 which may
`120.
`be drawn together by bolt and nut assemblies 146 to
`In a similar manner, the eccentric shaft 20 is sup
`ported on a pair of spaced apart spherical roller bearing
`clamp the eccentrics to the ends of the shaft 20, respec
`tively. Cooperable drive key means 147 are also pro
`assemblies 122 which are disposed in respective ones of
`the bearing support sleeves 112. The bearings 114 and
`vided for locating the eccentrics to be out of phase with
`122 are preferably of a type SD manufactured by The
`each other in accordance with the requirements of a
`45
`particular pump. For example, in the duplex piston
`Torrington Company, Torrington, Conn. Each of the
`sleeves 110 and 112 is provided with inwardly project
`pump 14 of the present invention, the eccentrics 142 are
`ing flange portions 115 and 117, respectively, which
`positioned 90 out of phase with each other about the
`may be welded to the sleeves for retaining the bearings
`axis of rotation of the eccentric shaft 20. Accordingly,
`within the sleeves and to prevent lateral displacement of 50
`the eccentrics 142 are preferably fabricated as separate
`the respective shafts 44 and 20. The shaft 20 is also
`members which may be easily mounted on and de
`adapted to be threadedly engaged with opposed bearing
`mounted from the shaft 20. Moreover, the eccentrics
`locknuts 124 to prevent lateral displacement of the shaft
`142 may be conveniently fabricated from standard steel
`plate or billet stock by being cut from stock and ma
`out of the bearing assemblies 122. As shown in FIG. 7,
`the shaft 20 includes a central portion 23 provided with
`chined to form the bore 144 as well as a bore 149, FIG.
`a suitable keyway for receiving a drive key for driv
`7, for receiving stub crank pins 150. The crank pins 150
`ingly engaging a chain sprocket 126 mounted on the
`are separately machined steel members which are pref.
`shaft portion 23 and also drivenly engaged with the
`erably shrink fitted in the respective bores 149 to form
`a substantial interference fit. The crank pins 150 are
`endless chain 120. The distal end 46 of the shaft 44
`extends through the sidewall of the crankcase portion
`adapted to support roller bearing assemblies 152, which
`60
`are preferably of the spherical self-aligning type and,
`22, formed by the plate 50. A removable cover plate 130
`containing a suitable shaft seal 132 is mounted on the
`are retained on the crank pins by suitable bearing retain
`plate 50.
`ing nuts threadedly engaged with the pins.
`Referring to FIG.4, by way of example, the connect
`The bearing assemblies 114 and 122 as well as the
`chain 120, are lubricated by a unique arrangement of oil
`ing rod 24, which is also preferably formed from steel
`65
`plate or billet and flame cut t