United States Patent (19)
`Rambin, Jr.
`
`(54) PUMP AND ENGINE ASSEMBLY
`75 Inventor:
`Leroy M. Rambin, Jr., Houston, Tex.
`73) Assignee:
`The Ellis Williams Company,
`Houston, Tex.
`21 Appl. No.: 44,172
`22 Filed:
`May 31, 1979
`51) Int. Cl. .............................................. FO4B 23/06
`52 U.S. C. ..................................... 417/426; 417/539
`58 Field of Search ........................ 417/238, 426-429,
`417/539, 567
`
`56)
`
`References Cited
`U.S. PATENT DOCUMENTS
`1,596,037 8/1926 Warner ........................... 417/567 X
`2,651,258 9/1953 Pierce ............................. 47/426X
`2,821,698 1/1958 Richardson ..................... 417/426X
`3,304,869 2/1967 Blume ................................. 417/429
`3,364,871 1/1968 Wilson ............................ 417/539 X
`Primary Examiner-Edward L. Roberts
`57
`ABSTRACT
`A pump and engine assembly according to the present
`
`11
`45)
`
`4,341,508
`Jul. 27, 1982
`
`invention is adapted for skid mounting and incorporates
`a pair of engines positioned in side to side relationship
`and having rotary output shafts thereof positioned in
`substantially parallel relation. A pair of piston type
`pumps are also positioned in side by side relationship
`with the fluid ends thereof facing in the same direction
`and with pump drive shafts arranged in substantially
`parallel relation with the rotary output shafts of the
`engines. The pump housing of a first one of the pumps
`incorporates a pair of shaft receptacles receiving a pair
`of rotary drive shafts. One of the drive shafts is pro
`vided with a pinion gear having meshing gear engage
`ment with the primary gear of the first pump while the
`second drive shaft extends from opposed sides of the
`first pump. The second pump is provided with a drive
`shaft that is adapted to be coupled to the second drive
`shaft of the first pump. Both drive shafts of the first
`pump are coupled to respective ones of the output shafts
`of the engines.
`
`23 Claims, 12 Drawing Figures
`
`
`
`Page 1 of 14
`
`

`

`Sheet 1 of 6
`Sheet 1 of 6
`
`4,341,508
`
`U.S. Patent
`sul. 27, 1982
`U.S. Patent Jul 27, 1982
`
`4,341,508
`
`
`
`Page 2 of 14
`
`Page 2 of 14
`
`

`

`U.S. Patent
`jul.27, 1982
`U.S. Patent Jul 27, 1982
`
`
`
`4,341,508
`4,341,508
`
`Sheet 2 of 6
`Sheet 2 of 6
`
`FIG.4
`
`Page 3 of 14
`
`Page 3 of 14
`
`

`

`U.S. Patent
`
`Jul. 27, 1982
`Jul. 27, 1982
`
`
`
`Sheet 3 of 6
`Sheet 3 of 6
`
`4,341,508
`4,341,508
`
`U.S. Patent
`
`?||||||||
`filiiiiiiiiiiiiiiiiiii
`
`| * G
`
`Page 4 of 14
`
`Page 4 of 14
`
`

`

`Sheet 4 of 6
`Sheet 4 of 6
`
`4,341,508
`4,341,508
`
`U.S. Patent
`jul. 27, 1982
`U.S. Patent Jul. 27, 1982
`
`<UE
`
`
`
`
`
`Page 5 of 14
`
`Page 5 of 14
`
`

`

`U.S. Patent
`sul. 27, 1982
`U.S. Patent Jul. 27, 1982
`
`Sheet 5 of 6
`Sheet 5 of 6
`
`4,341,508
`4,341,508
`
`
`
`128
`
`&
`120
`
` FIG.100
`
`8
`
`S
`
`S
`
`Page 6 of 14
`
`Page 6 of 14
`
`

`

`U.S. Patent
`U.S. Patent
`
`Jul. 27, 1982
`Jul. 27, 1982
`
`Sheet 6 of 6
`Sheet 6 of 6
`
`4,341,508
`4,341,508.
`
`
`
`
`
`OG/
`
`89/
`
`
`
`Page 7 of 14
`
`Page 7 of 14
`
`

`

`PUMP AND ENGINE ASSEMBLY
`
`5
`
`10
`
`5
`
`20
`
`30
`
`FIELD OF THE INVENTION
`This invention relates generally to engine driven
`pump assemblies and, in particular, piston type pump
`assemblies incorporating crank shafts, bull gears and
`pistons for the purpose of achieving compression of a
`fluid medium that is being pumped. Even more specifi
`cally, the present invention is directed to an engine and
`pump assembly, allowing a pair of engines mounted in
`side by side relationship in close proximity to one an
`other to be adapted for driving a pair of pumps that are
`also positioned in side by side relationship in close prox
`imity to one another. Even more specifically, the pres
`ent invention is directed to a dual engine and dual pump
`assembly that is adapted to be positioned in compactly
`oriented relationship on a relatively small skid thereby
`enabling the engine and pump assembly to be located in
`a limited space.
`BACKGROUND OF THE INVENTION
`In many cases, engine and pump assemblies are
`mounted on skids that enable the engine and pump
`assemblies to be easily transported to a desired location
`25
`and placed into operation with a minimum of labor.
`Typically, the engines and pumps of a skid mounted
`engine and pump assembly are fixed relative to skid
`structure that forms a supporting base therefor. In cases
`where space for such engine and pump assemblies is
`critical, for example in the case of oil well drilling rigs
`and offshore drilling rigs in particular, it is especially
`desirable to achieve optimum positioning of the engines
`and pumps on a skid of limited size. It is also considered
`especially desirable to mount two engines and two
`35
`pumps on a skid structure where the pumps are to be
`utilized for the purpose of pumping drilling mud to thus
`insure that complete circulation of drilling mud will not
`be lost in the event one of the pumps should fail during
`service due to malfunction of either the engine or the
`pump mechanism.
`Most pumps that are utilized for the purpose of
`pumping drilling fluid, typically referred to as mud
`pumps, are piston energized pump mechanisms incorpo
`rating gear driven crank shafts and piston rods that are
`45
`operative to impart reciprocating movement of the
`pistons of the pump mechanism. The drive shafts of
`piston type pump mechanisms are typically oriented
`transversely to the longitudinal axis of such pump
`mechanisms and the drive shafts of the mud pumps are
`50
`oriented in parallel relation with the rotary output
`shafts of the engines. This allows a direct coupling rela
`tionship to be established between the output and drive
`shafts of the respective pumps and engines.
`One arrangement for engine and pump assemblies has
`been to locate the engines in closely spaced side by side
`relationship and to reverse one of the pumps relative to
`the other in order that a directly coupled relationship
`may be established between the output shafts of each of
`the engines and the drive shafts of the respective pumps.
`60
`This manner of engine and pump orientation is not
`satisfactory because it places the fluid ends of the pumps
`at opposing sides of the skid and, therefore, it is not
`possible for personnel to simultaneously inspect the
`fluid ends of both pumps. Moreover, unless suitable
`65
`gearing arrangement is provided, the drive shafts of one
`of the pumps must rotate in opposite direction to the
`drive shaft of the other pump. In this case, the power
`
`4,341,508
`2
`stroke of the crank shaft and connecting rod intercon
`nection with the pump piston system may be oriented
`upwardly in one of the pumps. It is considered disad
`vantageous to orient the power stroke other than down
`wardly from the standpoint of operational service life of
`the pump mechanism.
`In some cases, it is necessary to elevate one of the
`pumps relative to the other in order that an output
`shaftdrive shaft interconnection may pass beneath the
`first of the mud pumps in order to achieve operation of
`the second one of the mud pumps. In this case, one of
`the engines may also require elevation in order that the
`output shaft thereof may be properly oriented with
`respect to the drive shaft of the pump to be connected
`thereto. Elevation of the engines and pumps on the skid
`obviously requires the skid structure to be of complex
`nature, thus increasing the cost of the engine and pump
`assembly to the point that cost becomes adverse to the
`commercial feasability of the pumping operation. An
`other disadvantage that is created when engines and
`pumps are elevated relative to the skid structure is the
`overall increase in height of the engine and pump as
`sembly. Obviously, in many cases the overall height of
`the engine and pump assembly becomes quite critical
`because of the limited vertical space that is allowable
`for engine and pump installation.
`In many cases, it becomes desirable to move engine
`and pump assemblies through restricted openings or to
`place the same in locations where it may not be possible
`to introduce an entire dual engine and dual pump skid
`assembly without removing other structure. It is desir
`able, therefore, to provide a skid mounted engine and
`pump assembly that may be transported in modular
`components to a desirable location and may be moved
`through openings of restricted dimension, after which
`the modules of the system may be simply intercon
`nected, thereby placing the engine and pump assembly
`in operation without undue delay.
`It is therefore a primary feature of the present inven
`tion to provide an engine and pump assembly that incor
`porates a pair of engines that are interconnected in
`driving relation with a pair of piston type fluid pumps
`with the engines and pumps being arranged in efficient,
`compact relationship on a single level skid structure.
`It is also a feature of the present invention to provide
`a novel engine and pump assembly incorporating a pair
`of engines and first and second pump mechanisms with
`the drive shaft of the second one of the pumps being
`interconnected to one of the engines by means of a drive
`shaft extending through the first one of the pumps.
`It is another feature of the present invention to pro
`vide a novel engine and pump assembly wherein each of
`the pumps is formed to define a pair of drive shaft re
`ceptacles and with the first one of the pumps incorpo
`rating a pair of drive shafts received within the recepta
`cles while the second pump incorporates a single shaft
`received within one of the drive shaft receptacles
`thereof and with the shaft of the second pump adapted
`for interconnection with one of the drive shafts of the
`first pump.
`It is an even further feature of the present invention
`to provide a novel engine and pump assembly wherein
`the drive shaft or shafts of each of the pumps are selec
`tively positionable within selected ones of a pair of
`drive shaft receptacles provided for each of the pumps.
`Among the several features of the present invention is
`noted the contemplation of a novel pump and engine
`
`40
`
`55
`
`Page 8 of 14
`
`

`

`5
`
`10
`
`15
`
`4,341,508
`4.
`3
`coupling device that connects the second drive shaft of
`assembly wherein a pair of piston type fluid pumps are
`the first pump and the drive shaft of the second pump in
`positioned in side by side relationship, each pump incor
`driving relationship. The drive shaft of the second
`porating a drive shaft supported pinion gear in driving
`pump may be selectively positioned at either of the
`interconnection with a primary gear of the pump and
`drive shaft receptacles defined by the pump housing
`with the drive shaft supporting the pinion gear being
`and, in either case, establishes meshing gear driving
`selectively positionable within one of a pair of drive
`relationship between the pinion gear and bull gear of
`shaft receptacles provided in the pump mechanism.
`the pump. Thus, depending upon the selective position
`It is an even further feature of the present invention
`of the first and second drive shafts of the first pump, the
`to provide a novel skid mounted engine and pump as
`shaft of the second pump may be selectively positioned
`sembly whereby each engine and each pump of the skid
`so as to be driven by energy transferred through the
`assembly is mounted on a skid module and the various
`second drive shaft of the first pump.
`skid modules may be individually transported to an
`Driving interconnection between the first and second
`installation site and subsequently assembled to define an
`drive shafts of the first pump and respective ones of the
`integrated engine and pump assembly.
`rotart output shafts of the engines is established by
`Other and further objects, advantages and features of
`means of appropriate one to one rotary energy transfer
`the invention will become obvious to one skilled in the
`mechanisms. If desired, simple one to one chain drive
`art upon an understanding of the illustrative embodi
`systems may be employed to establish driving intercon
`ment about to be described and various advantages, not
`nection between respective ones of the output shafts of
`referred to herein, will occur to one skilled in the art
`the engines and respective ones of the first and second
`upon employment of the invention in practice.
`drive shafts of the first pump.
`SUMMARY OF THE INVENTION
`It is also within the scope of this invention to utilize
`the drive-through concept hereof for accomplishing
`The present invention is directed to a pump and en
`driving of a second pump by means of a driving inter
`gine assembly that is mounted on a skid structure en
`connection between the drive shafts of the pumps. In
`abling the engine and pump assembly to be simply trans
`25
`each case the pumps incorporate drive shafts having at
`ported and installed by means of a skid support, thereby
`least one of the extremities thereof projecting from each
`enabling the same to be placed into service with a mini
`side of the respective pump housings. A drive-through
`mum amount of installation time. In order to enable the
`shaft is incorporated into one of the pump housings and
`development of a dual engine and dual pump engine and
`is coupled in any suitable driving relation to the drive or
`pump assembly, a pair of engines are mounted in side by
`pinion shafts of each of the pumps. Chain drive systems
`side relationship on the skid structure and rotary output
`of other suitable driving means may be utilized to estab
`shafts of the engines are positioned in generally parallel
`lish a driving relation between the drive-through shaft
`relationship and are oriented in a common direction. A
`and one or more of the pinion shafts. The pumps may be
`pair of piston type fluid pumps are also positioned in
`oriented in any suitable manner with respect to one
`side by side relationship on the skid structure with the
`35
`another and the power source.
`longitudinal axes thereof disposed in substantially nor
`The skid structure may be defined by a plurality of
`mal relation to the axes of the output shafts of the en
`skid modules, each supporting one of the major compo
`gines. Such orientation of the pumps, with the fluid ends
`nents of the engine and pump system. The skid modules
`thereof each visible from one side of the skid structure
`may be moved easily through restricted openings and
`for simultaneous inspection by service personnel, causes
`40
`subsequently joined to place the engine and pump as
`the drive shafts of the pumps to be oriented in substan
`sembly in operation with a minimum of delay. More
`tially parallel relation with the output shafts of the en
`over, skid modules may be replaced as necessary to
`glnes.
`maintain the operational integrity of the engine and
`The first one of the fluid pumps incorporates a pair of
`pump assembly.
`drive shafts that are each interconnected by means of a
`45
`suitable power transmission system to the output shafts
`BRIEF DESCRIPTION OF THE DRAWINGS
`of respective ones of the engines. One of the drive shafts
`In order that the manner in which the above-recited
`of the first pump is provided with a pinion gear that
`advantages and objects of the invention are attained and
`meshes with the primary gear or bull gear of the first
`can be understood in detail, more particular description
`pump and therefore imparts rotary motion to the bull
`50
`of the invention, briefly summarized above, may be had
`gear and the crank shaft to which the bull gear is con
`by reference to the specific embodiment thereof that is
`nected. The second drive shaft of the first pump is rotat
`illustrated in the appended drawings, which drawings
`ably supported by the housing structure of the first
`form a part of this specification. It is to be understood,
`pump mechanism with both extremities thereof being
`however, that the appended drawings illustrate only a
`exposed on opposed sides of the housing structure of the
`typical embodiment of this invention and therefore are
`first pump.
`not to be considered limiting of its scope, for the inven
`The pump housing structure of the second pump is
`tion may admit to other equally effective embodiments.
`formed to define a pair of drive shaft receptacles, with
`only one of the receptacles being provided with a drive
`In the Drawings:
`shaft and bearing assembly. The drive shaft of the sec
`60
`FIG. 1 is a schematic plan view of a skid mounted
`ond pump is provided with a pinion gear that establishes
`engine and pump assembly utilizing pumps constructed
`meshing, gear driving relationship with the primary or
`in accordance with the present invention.
`bull gear of the second pump so as to provide power for
`FIG. 2 is a schematic elevational view of the skid
`the second pump through the drive shaft, pinion and
`mounted engine and pump assembly of FIG. 1.
`bull gear interconnection. The drive shaft of the second
`FIG. 3 is a sectional view taken along line 3-3 of
`pump is adapted to be positioned in substantially axially
`FIG. 2 and illustrating a one to one chain drive assen
`aligned relation with the second drive shaft of the first
`bly for establishing interconnection between the output
`pump and is coupled therewith by means of a simple
`
`30
`
`20
`
`55
`
`65
`
`Page 9 of 14
`
`

`

`5
`
`10
`
`15
`
`4,341,508
`6
`5
`service personnel. For purposes of clarity, the platform
`shafts of the engines and the drive shafts of the first
`pump mechanism.
`is illustrated in broken line, allowing the pump and
`FIG. 4 is a side elevational view of a pump such as
`transmission structure to be shown in full line.
`illustrated in FIGS. 1 and 2 and having a portion thereof
`As mentioned above, it is desirable to locate skid
`broken away and illustrating the drive shaft and gear
`mounted pumps in side by side relationship in such
`arrangement of the first pump mechanism in detail.
`manner that the fluid ends thereof face in a single direc
`tion enabling service personnel to simultaneously in
`FIG. 5 is a plan view of the pump mechanism of FIG.
`4 having portions thereof broken away and illustrating
`spect the fluid ends of the pump mechanisms. It is also
`the drive shaft and gear arrangement thereof in broken
`desirable that such pump mechanisms be oriented in
`such manner that the crank shaft and connecting rod
`line.
`system that supplies power to the pistons applies the
`FIG. 6 is an end view of the pump mechanism of
`power stroke to the pistons in a downward direction
`FIGS. 4 and 5 taken along line 6-6 of FIG. 4.
`FIG. 7 is an end view of the pump mechanism of
`toward the base of the pumps. These features are effec
`tively provided by the present invention. As shown in
`FIGS. 4 and 5 taken along lien 7-7 of FIG. 4.
`FIGS. 1 and 2, a pair of piston type high pressure triplex
`FIG. 8 is a fragmentary sectional view of the pump
`structure taken along line 8-8 of FIG. 4 and illustrating
`pumps are illustrated generally at 38 and 40 and are
`the second drive shaft and bearing support assembly of
`connected to the skid structure 12 in any suitable man
`ner. To simplify understanding of the present invention,
`the first pump and its relation to the bull gear.
`pump 38 is referred to herein as the “first pump' while
`FIG. 9 is a plan view of a modular skid structure
`constructed in accordance with the present invention
`pump 40 is referred to as the "second pump.” The first
`20
`illustrating bolted attachment of a plurality of skid seg
`pump is illustrated generally at 38 in FIGS. 4 and 5 and
`includes a pump housing structure 42 that provides
`ments or modules.
`appropriate bearing support for a crank shaft 44 that is
`FIG. 10 is a side elevational view of the skid structure
`rotatable within the housing about an axis 46 and in
`Of FIG. 9.
`FIG. 11 is a schematic plan view illustrating an alter
`duces rotation to eccentric members 48 that are pro
`25
`native embodiment of the present invention wherein the
`vided for each one of a plurality of bearing and connect
`drive-through concept of this invention is employed to
`ing rod members 50. Although the pump mechanism 38
`drive a plurality of pumps from a single power source.
`may be provided with only a single bearing and con
`necting rod structure 50 that is adapted to establish
`FIG. 12 is a schematic plan view of another alterna
`driving engagement with a piston, not shown, in most
`tive embodiment of the invention.
`commercial pumps for pumping drilling fluid under
`DETAILED DESCRIPTION OF PREFERRED
`high pressure, it is typical to employ three bearing and
`EMBODIMENT
`connecting rod assemblies that are driven by eccentric
`Referring now to the drawings and first to FIG. 1, a
`portions of the crankshaft for operation of three pistons
`skid mounted pump and engine assembly is illustrated
`provided within cylinders enclosed within the pump
`35
`generally at 10 and incorporates a skid structure 12 that
`housing structure. These types of pumps are typically
`defines a support base for engines, pumps and other
`known as triplex pumps and each of the eccentric struc
`apparatus that enables the pumping of fluid by the
`tures is positioned in 120 offset relation to one another,
`pumps.
`thereby positioning the eccentric mechanisms equidis
`For purposes of simplicity, the engines are shown as
`tantly about the axis of the crankshaft. The pump mech
`40
`typical internal combustion engines having rotary out
`anism is also provided with a primary gear 52 which is
`put shafts and the pumps are shown and discussed
`also typically referred to as a bull gear and which is
`herein particularly from the standpoint of piston ener
`provided with peripheral gear teeth 54 having gear
`gized pump systems such are typically employed for
`meshing engagement with gear teeth 56 of a pinion gear
`pumping liquid under high pressure. It is not intended to
`structure 58. The pinion gear teeth 56 may be formed on
`45
`limit the present invention to utilization of internal com
`an enlarged intermediate portion of a first drive shaft 60
`having one extremity 62 thereof extending through the
`bustion engines, nor is it intended to restrict the inven
`tion specifically to piston type pumps mechanisms, it
`side wall structure 64 of the pump housing 42. Drive
`being within the spirit and scope of the present inven
`shaft 60 is suitably mounted relative to side wall struc
`tion to employ other power and pumping systems as
`tures 64 and 66 of the pump housing by means of bear
`ing and lubricant seal assemblies like those in FIG. 8 for
`well.
`A pair of internal combustion engines 13 and 14 are
`Shaft 68.
`shown to be mounted upon the skid structure 12 in
`Rotation of the drive shaft 60 by a power source
`closely spaced, side by side relationship. The engines 13
`coupled to the extremity 62 thereof causes consequent
`and 14 incorporate transmission systems 16 and 18 hav
`rotation of the pinion gear structure 58 and thus induces
`55
`ing rotary output shafts 20 and 22, respectively. The
`rotation of the primary or bull gear 52 which induces
`particular engine and pump assemblies typically are
`rotation of the crankshaft 44 to drive the pistons by
`employed for the purpose of high pressure pumping of
`means of the crank shaft, eccentric and connecting rod
`drilling fluid, typically referred to as drilling mud, and,
`arrangement that is typical to such pumps and shown in
`the engine pump and skid structure will typically incor
`FIG. 4.
`60
`porate a pair of liquid tanks 24 and 26 that provide a
`It is desirable to mount the second pump mechanism
`supply of drilling mud. Typically, the tanks 24 and 26
`40 at the same elevation as the first pump 38 and to
`are elevated on the skid structure 12 by means of sup
`provide for simple driving connection between one of
`the engines and a drive shaft of the second pump. In
`port legs such as shown at 28 and 30 and a platform
`structure 32 rests upon a platform support structure 34,
`accordance with the present invention, this feature is
`65
`thus providing a work platform for use by pump service
`effectively accomplished by providing the first pump
`personnel. A guard rail structure 36 is also typically
`mechanism with a second drive shaft that may be inter
`provided to provide safe working conditions for the
`connected both with the drive shaft of the second pump
`
`30
`
`50
`
`Page 10 of 14
`
`

`

`10
`
`25
`
`4,341,508
`8
`7
`100 of a power transmission mechanism 102. The power
`and with the rotary output shaft of one of the engines.
`transmission mechanism may incorporate a pair of chain
`As shown in FIGS. 4, 5 and 8, a second drive shaft 68 is
`drive sprockets 104 and 106 that are interconnected by
`rotatably supported by bearing structures 70 and 72 by
`the coupling structures 94 and 96 in driving relation
`side walls 64 and 66 of the pump housing structure 42.
`with the output shafts 20 and 22 of the engines. Other
`As shown at the left hand portion of FIG. 8, each of the
`chain drive sprockets 108 and 110 may be intercon
`bearing structures incorporates a bearing retainer ele
`nected with the drive shafts 60 and 68 of the first pump
`ment 74 adapted to receive a roller bearing 76 therein
`mechanism 38. Chain elements 112 and 114 may be
`having an inner bearing race that receives a bearing
`employed to drive the sprocket members 108 and 110
`portion 78 of the second drive shaft 68. A snap ring 80
`responsive to rotation of sprocket members 104 and 106
`or any other suitable retainer device is provided for
`by the output shafts of the engines. The sprocket ele
`retaining the roller bearing 76 in appropriate assembly
`ments may be of identical or differing diameter and
`with the bearing retainer 74. The bearing retainer struc
`incorporate an appropriate number of teeth to establish
`ture is formed to define an outer flange portion 82
`a desired drive ratio relationship that allows the drive
`through which bolts may extend for the purpose of
`shafts of the first pump mechanism 38 to be rotated at
`establishing bolted interconnection of the bearing re
`15
`the same or differing speed as the output shafts 20 and
`tainer to the wall structure of the pump housing. As
`22 of the engines.
`shown at the right hand portion of FIG. 8, each of the
`It may be desirable to selectively position the drive
`bearing retainers is formed to receive a lubricant seal
`shafts of the pump mechanisms, depending upon the
`element 84.
`particular manner in which the drive through relation
`With the second drive shaft 68 positioned in the man
`20
`ship is to be established between the first and second
`ner illustrated in FIG. 8, it should be borne in mind that
`pumps. Accordingly, each of the pump mechanisms is
`a driving engagement between the drive shaft 68 and
`provided with a pair of appropriately positioned bear
`the bull gear 52 is not established. Rather, the drive
`ing receptacles, enabling bearing assemblies such as
`shaft 68 merely extends through the housing structure,
`shown in FIG. 8 to be interconnected into the side wall
`is supported for efficient low friction rotation by the
`structure of the pump housings for the purpose of estab
`roller bearing assemblies 70 and 72. Further, extremities
`lishing rotatable support for one or more drive shafts.
`86 and 88 of the second drive shaft 68 extend from the
`Moreover, each of the bearing receptacles and bearing
`housing structure in such manner as to allow efficient
`assemblies is of identical size and configuration, thereby
`coupling of the second drive shaft to other rotatable
`enabling the various drive shafts to be interchangeable.
`structures. For example, shaft extremity 86 may be
`30
`For example, the first and second drive shafts 60 and 68
`coupled in driven relationship to the output shaft of one
`of the first pump are of substantially identical size and
`of the engines by means of a suitable energy transmis
`differ only in that drive shaft 68 is provided with an
`sion system as will be discussed hereinbelow. The oppo
`extension defining extremity 88. Drive shafts 60 and 68
`site extremity 88 of the second drive shaft 68 also ex
`may be interchanged with one another thereby position
`tends beyond the housing wall structure 66 and may be
`35
`ing the drive through shaft 68 more toward the center
`coupled in driving relationship with the drive shaft of
`of the pump structure in the event such positioning is
`the second pump mechanism 4.0. This feature allows one
`desired. In the event it is not desired to employ two
`of the engines to accomplish driving of the second
`drive shafts in the second pump mechanism 40, a pair of
`pump mechanism by means of a drive shaft that merely
`cover plates 116 and 118 may be provided for covering
`extends through the first pump mechanism.
`40
`the bearing apertures in the event such is desired. This
`As illustrated in FIGS. 1 and 2, the second pump
`feature enables the pump mechanisms to be inter
`mechanism 40 includes a single drive shaft 90 that is
`changeable and further allows selective positioning of
`mounted in the pump housing structure in the same
`the pump mechanisms and selective interconnection of
`manner as drive shaft 60 of FIG. 5. In fact, drive shaft
`the drive and driven shafts thereof, depending upon the
`60 of pump 38 and drive shaft 90 of pump 40 may be
`45
`particular design of the installation involved.
`interchangeable if desired. Appropriate bearing and seal
`In many cases, it is desirable to place an engine and
`assemblies are providing in pump 40 to provide for
`pump assembly such as shown in FIG. 1 in a suitable
`efficient rotatable support of the pump drive shaft 90 in
`space within a working environment. In particular, it is
`the same manner as disclosed in FIG. 8, with the excep
`sometimes appropriate to install engine and pump as
`tion that drive shaft 90 only has one extremity thereof
`50
`semblies in drilling rigs and, in particular, offshore dril
`extending from the pump housing structure for inter
`ling rigs wherein the allowable space for such installa
`connection with the extremity 88 of drive shaft 68. A
`tion is extremely restricted. Further, it may be neces
`suitable coupling device 92 may be provided for the
`sary to break the engine and pump assembly down into
`purpose of establishing nonrotatable driving intercon
`various components in order to achieve movement of
`55
`nection between drive shafts 68 and 90.
`the engine and pump mechanism into the desired space.
`It is evident that the rotary output shafts 20 and 22 of
`This often requires a considerable amount of time and
`the engines 13 and 14 are positioned in parallel relation
`therefore adversely affects the commercial nature of the
`but the spacing thereof is substantially greater than the
`pumping operation involved. Where offshore drilling
`spacing between the first and second drive shafts 60 and
`rigs are concerned, the downtime necessity for installa
`68 of the first pump mechanism 38. In order to establish
`60
`tion of replacement engine and pump assemblies can be
`driving interconnection between the output shafts of
`extremely expensive. It is therefore desirable to provide
`the engines and the drive shafts of the first pump, a
`an engine and pump assembly that may be efficiently
`simple power transmission may be utilized in the man
`broken down into small modules, which modules may
`ner shown in FIGS. 1, 2 and 3. The power transmission
`be efficiently moved into the space for installation of the
`may be a drive system of one-to-one ratio or other suit
`65
`same and the modules then may be reassembled within
`able ratio appropriate to accomplish the intended result.
`a short period of time to facilitate efficient production.
`Engine output shafts 20 and 22 may be suitably con
`Accordingly, the skid structure of the present invention
`nected by coupling devices 94 and 96 to shafts 98 and
`
`Page 11 of 14
`
`

`

`15
`
`30
`
`35
`
`4,341,508
`10
`9
`engaging the bull gear of the pump. Each extremity of
`may be broken down into a plurality of modules which
`the shaft 156 projects from the pump housing.
`may be referred to as modules A and B, each of which
`may incorporate a single pump drive engine and a mix
`The second pump 150 also incorporates a drive or
`pinion shaft 158 that is rotatably mounted relative to the
`ing or storage tank for drilling mud or the like. Modules
`housing structure of the pump and is mounted with both
`C and D of the skid system are each adapted to provide
`extremities thereof projecting from the pump housing.
`support for one of the first and second pump devices 38
`In the particular pump assembly of FIG. 11, a coupling
`and 40 and the various apparatus connected thereto.
`Additionally, skid module C provides support for the
`structure 160 establishes direct