Apparatus For Producing Variable High Frequency Vibrations In A Liquid Medium

Abstract

Apparatus and methods to form and utilize pulsating fluid pressures in oil well formation treating of producing wells or as a part of secondary or tertiary recovery processes. Self induced or artificially induced liquid-gas phase changes occur in-situ which are utilized to selectively and variably treat oil wells including but not limited to fracturing, temporary or permanent plugging, cementing, drilling, water block and cone prevention, control over the driving and/or driven fluids in primary, secondary or tertiary recovery techniques.

Parent Case Text

CROSS-REFERENCES TO RELATED APPLICATIONS

This invention comprises novel and useful apparatus for producing variable high frequency vibrations or sonic waves in a liquid or fluid medium and constitutes a continuation-in-part application of copending application Ser. No. 665,995, filed June 17, 1957, now U. S. Pat. No. 3,302,720, which in turn is a continuation-in-part of original applications Ser. No. 296,038, filed June 27, 1952, now U. S. Pat. No. 2,866,509, and Ser. No. 241,647, filed Aug. 13, 1951, now U. S. Pat. No. 2,796,129.

As to the basic apparatus and methods, the first disclosure appears in application Ser. No. 241,647, filed Aug. 13, 1951, aforementioned.

Description

BACKGROUND OF THE INVENTION

Broadly this invention involves above and below ground well treatment apparatus generally in class 166 of the present U.S. Pat. classification definition, and includes subject matter which has been copending since Aug. 13, 1951 portions of which have been divided or otherwise carved therefrom into the aforesaid issued patents and applications.

The prior art prior to applicant's above filing date is typified by the Sherborne Pat. No. 2,670,801, Bodine Pat. No. 2,355,618 and subsequent Bodine Pat. Nos. 2,667,932, 2,871,943, 3,016,093, 3,016,095, and Re. 23,381. All of these references have as a common denominator the creation and utilization of sonic standing waves as a means of increasing oil recovery. "Sonic standing waves" meaning waves, whether symmetrical or not which are repetitive or reoccurring without change. This invention, on the other hand, provides for apparatus for creating sonic waves wherein said wave characteristics are variable or changeable at the will of the operator depending upon the function desired.

SUMMARY AND OBJECTS

The primary object of this invention is to provide an apparatus and method for producing high frequency vibrations in a liquid medium and one wherein the apparatus may be extremely susceptible of adjustment in order to control with great accuracy and precision the force and also both the amplitude and the frequency of the vibrations produced in the medium.

The primary specific object of this invention is to provide an apparatus for treating oil bearing formations with fluid pressure and/or high frequency vibrations and producing an energy carrying wave in a medium, and wherein all of the characteristics of such wave can be controllably varied and applied to widely diversified uses such as to tunneling, drilling, mining of various minerals, reductions of ores, pumping, oil well use, various pressing applications, extrusion of materials, recrystallization of materials to increase strength, ice breaking, structure deforming, prestressing or compacting of materials, quarrying, dying of fibers and many other uses.

A very important object of this invention is to provide an apparatus specifically adapted for use in oil and gas wells and effectively treating the same by fracturing, acidizing, cementing, cleaning, water and gas flooding for the secondary recovery of fluids from producing formations, drilling and for testing operations relative to any of the above.

Another very important object of this invention is to provide an apparatus having extreme adjustability as to all of its phases of operation whereby to facilitate testing as to ranges of pressure, high frequency vibrations, character of high frequency vibrations and the like for determining effective treating of oil bearing formations and for treatment of other objects.

An additional object of this invention is to provide a means for generating energy carrying waves for treating an oil bearing formation and for other uses, and wherein the characteristics of said generated waves may be widely and controllably varied and whereby said means shall be highly compact and mobile in nature.

A more specific object of the invention is to provide a variable stroke pump for generating in a liquid medium energy carrying waves of various predetermined characteristics.

Another specific object is to provide an energy wave generator wherein the energy content of the generated wave may be increased or decreased by applying or withdrawing heat from the medium supplied to the wave generator.

A still more specific object is to provide an apparatus for producing energy carrying waves by means of a variably reciprocated piston and wherein a pair of variably timed crankshafts are each adjustably connected to a rocker and slide mechanism driving said piston in order to controllably vary thereby the stroke of the latter.

An additional specific object is to provide a reciprocating piston type of pump, especially adapted for use as a generator of an energy carrying wave wherein a more perfect and self compensating counterbalancing of the pump pistons and the various moving parts thereof is obtained.

Still another specific object is to provide a wave generating pump having means for storing energy therein from the fluid medium with which the pump is associated.

Yet another specific object is to provide a wave generating pump assembly having a means for adjustably preloading pump and/or counterbalance cylinders with an adjustable fluid pressure.

A further specific object is to provide a reciprocating piston pump assembly specifically adapted for the generation of high frequency energy carrying waves in a liquid medium and wherein a pump cylinder and piston and a counterbalance cylinder and piston are interconnected and are each operatively connected with said liquid medium whereby to balance out pulsations and vibrations in the mechanism.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a top plan view of a satisfactory embodiment of apparatus incorporating therein the principles of this invention and showing in particular the relative arrangement and the location of the various sub-assemblies of this apparatus upon its mobile base;

FIG. 2 is a side elevational view of the right side of the apparatus of FIG. 1, but with the Y-tube assembly removed therefrom, and showing the instrument and control panel of the energy wave generator;

FIG. 3 is a side elevational view of the left side of the apparatus of FIG. 1 showing the Y-tube assembly thereof;

FIG. 4 is a rear elevational view taken on an enlarged scale of the apparatus of FIG. 1, part of the Y-tube assembly being broken away;

FIG. 5 is a top plan view on an enlarged scale of a portion of the apparatus of FIG. 1, some of the covers and enclosing housings being removed to show the structure of some of the power transmission mechanism for the pumping unit;

FIG. 6 is an enlarged view taken in transverse section substantially upon the plane indicated by the section line 6--6 of FIG. 3 and showing in front elevation the pump unit with the cover of one of the valve mechanism compartments and that of the rocker compartment being removed therefrom and with part of the Y-tube assembly broken away;

FIG. 7 is a front end elevational view of the base for the pump and transmission components of the wave generating apparatus, concealed parts being shown in dotted lines therein;

FIG. 8 is an elevational view of the left side of the base of FIG. 7, concealed parts thereof being shown in dotted lines;

FIG. 9 is a bottom plan view of the base of FIG. 7;

FIG. 10 is an enlarged fragmentary top plan view of Y-tube assembly showing the Y-tubes of the fluid pressure delivery conduit system of the apparatus;

FIG. 11 is an elevational view of the right side of the arrangement of FIG. 10;

FIG. 12 is a vertical transverse sectional view through the Y-tube assembly taken upon an enlarged scale substantially upon the plane indicated by the broken section line 12--12 of FIG. 11;

FIG. 13 is a perspective view, parts being broken away and showing the Y-tube assembly operatively associated with a test chamber of other apparatus with which the invention may be used;

FIG. 14 is a vertical longitudinal sectional view through the pump unit showing the parallel crankshaft arrangement, upon an enlarged scale taken substantially upon the plane indicated by the section line 14--14 in FIG. 6;

FIG. 15 is a vertical transverse sectional view through the pump unit showing the crankshaft, rocker and crosshead arrangement of a pump unit taken substantially upon the plane of the section line 15--15 of FIG. 14;

FIG. 16 is an enlarged detailed view in horizontal longitudinal section showing the rocker wristpin construction taken substantially upon the plane of the section line 16--16 of FIG. 15;

FIG. 17 is a schematic and diagrammatic view showing in vertical section the relative angular position of the crank throws of either crankshaft;

FIG. 18 is a perspective view of the right or main section of the upper crankshaft of FIG. 14;

FIG. 19 is a group perspective view of the two angularly adjustable sections of the upper crankshaft of FIG. 14, parts being broken away and showing the operative connection with the lower crankshaft, the differential gearing between the two sections being omitted;

FIG. 20 is a perspective view, parts being broken away, of a rocker and connecting rod assembly forming a part of the means operatively and adjustably connecting the piston crossheads to the crankshafts;

FIG. 21 is a perspective view of a connecting rod for a counterbalance cylinder piston;

FIG. 22 is a view in vertical longitudinal section showing the crosshead assembly, being taken upon an enlarged scale substantially in a plane indicated by the broken section line 22--22 of FIG. 5, parts being broken away;

FIG. 23 is an exploded perspective view of one of the crosshead guides;

FIG. 24 is a vertical longitudinal sectional view through one of the crosshead units showing the association of the crosshead guide and slide, being taken substantially in the plane indicated by section line 24--24 of FIG. 5, parts being broken away;

FIG. 25 is an exploded perspective view of one of the crosshead slides;

FIG. 26 is an enlarged horizontal sectional view showing a differential gear assembly for varying the phase or angular relationship between the two crankshafts, taken substantially in the plane indicated by the section line 26--26 of FIG. 14;

FIG. 27 is a vertical sectional view taken substantially upon the plane indicated by the section line 27--27 of FIG. 26;

FIG. 28 is a horizontal sectional view taken upon an enlarged scale substantially upon the plane indicated by the section line 28--28 of FIG. 27, certain shaft bearings being omitted for clarity;

FIG. 29 is an elevational view from the right side of FIG. 28 showing the indicator gauge of the crankshaft phase adjusting mechanism;

FIG. 30 is a vertical sectional view of the interior surface of the closure plate for a crosshead guide, being taken substantially in the plane indicated by the section line 30--30 of FIG. 24;

FIG. 31 is a view in vertical longitudinal central section, with parts in vertical elevation, of the pump counterbalance unit showing the counterbalance cylinder and piston and its adjustable pressure chamber;

FIG. 31A is a view in vertical central section of an accumulator, of the construction employed with both the pump working cylinder and the pump counterbalance cylinder, being taken substantially upon the plane indicated by the section line 31A--31A of FIG. 4;

FIG. 32 is a longitudinal vertical sectional view of a working pump or wave generator cylinder and piston construction, taken upon an enlarged scale substantially upon the plane indicated by the section line 32--32 of FIG. 5;

FIG. 33 is a central longitudinal sectional view upon a slightly enlarged scale of the generator or working pump cylinder, piston and piston rod of FIG. 32, parts being broken away;

FIG. 34 is an exploded perspective view of the working pump piston valve assembly;

FIG. 35 is a perspective view of the packing sleeve of the working pump piston assembly;

FIG. 36 is a longitudinal, central view in vertical section of the counterbalance pump cylinder and piston assembly of FIG. 31, being taken upon an enlarged scale substantially upon the plane indicated by section line 36--36 of FIG. 5.

FIG. 37 is a detailed view in vertical longitudinal section showing the connection securing the piston rod of the counterbalance of cylinder to its crosshead slide;

FIG. 38 is a horizontal sectional detail view illustrating the manner in which the counterbalance unit cylinder and also the pump cylinders are keyed to the supporting base, being taken substantially upon the plane indicated by the section line 38--38 of FIG. 36;

FIG. 39 is a schematic view illustrating the conduit connections of the nitrogen supply of the counterbalance pump and the bleed system of the apparatus;

FIGS. 40-43 are diagrammatic views of the rocker mechanism for varying the stroke of the pump and counterbalance pistons.

DESCRIPTION OF PREFERRED EMBODIMENTS

GENERAL ORGANIZATION

(FIGS. 1-13)

The general organization of this apparatus, specifically adapted for carrying out the purposes and methods of this invention, is disclosed in FIGS. 1-13. Referring first to FIGS. 1 to 3, it will be seen that the apparatus consists of a mobile supporting frame which may comprise the bed of a truck or a trailer, being illustrated in the drawings as consisting of a trailer bed 10 of any suitable design which has at its forward end a vertically offset or raised portion 12 which as shown in FIG. 2 is adapted to be supported and secured as by a conventional fifth wheel assembly 14 to the rear end portion 16 of a tractor vehicle. It is upon the trailer bed 10 that all of the elements and sub-combinations, forming the preferred form of the apparatus in accordance with the invention, are permanently mounted and secured in an operative relation for use or in a compact, stored condition for ready transportation.

Briefly, the elements and the sub-organizations forming a part of this invention and which are mounted upon the trailer bed and which will be referred to more specifically hereafter comprise an energy wave generator consisting of variable stroke pumping unit 20, an internal combuation engine 22, comprising the prime mover or power plant of the apparatus, a storage tank 24 for L.P.G. such as butane, propane or the like and which constitutes the fuel for the internal combustion engine. In addition, there is mounted upon the trailer bed a feed pump unit 26 together with a tank 28 constituting a reservoir for fluid to be supplied to the feed pump. A Y-tube assembly 30 is operatively detachably connected to the variable pump unit 20 for delivering the high frequency wave generated by the pump unit to the surface or object to be treated and for receiving the fluid discharged from the variable pump unit.

As set forth hereinafter, the Y-tube assembly 30 is readily detachably and operatively secured to the pump unit 20 and is supported upon tractor bed 10 in such a manner as to permit ready removability therefrom in order to reduce the over-all height and width of the apparatus to thereby facilitate transportation of the same.

The over-all purpose of this apparatus is to provide a variable stroke and variable capacity pump capable of imparting high frequency vibrations and energy carrying waves upon the fluid medium operatively contacting and/or discharged by the pump whereby such vibrations and waves may be transmitted by the fluid medium to a surface or object to be treated by the same.

Although the invention is to be understood as being in no way limited thereto, one especially useful application of the principles of this invention is to oil wells and oil bearing formations or horizons whereby to impart a water drive to the oil bearing formation for effecting a secondary recovery of oil and gases therefrom; for fracturing such formations; for more effectively promoting and controlling the flow of fluids in such formations; for cleansing well bores and the horizon adjacent the same and the like. Accordingly, the disclosure of the present application has been particularly directed to the manner in which the apparatus and method is utilized in oil recovery.

More generally, the apparatus constitutes a means for generating energy carrying high frequency waves and for producing desired characteristics therein as to amplitude, frequency and strength; for transmitting such waves by a liquid medium to any desired surface or object to be treated by the pressure and vibrations of the same; and for pumping said medium during any of the foregoing.

Referring now more specifically to FIGS. 7-9, and in general to FIGS. 4-6, it will be seen that there is provided a suitable crankcase and supporting base assembly upon which are mounted in a convenient and compact manner the pump unit and the power transmission mechanism operatively connected thereto and which is driven from the power plant 22. The crankcase and supporting base of the pump unit is designated generally by the numeral 50 and consists of a suitable support base comprising a housing or casing of requisite strength having a substantially flat bottom wall 52 which is adapted to rest directly upon the bed 10 of the trailer together with suitable side and end walls.

Carried by the side and end walls of the support base, and upon the top surface thereof, are a pair of parallel, slightly inclined and vertically spaced platforms 56 and 58 serving to support the transmission assembly and the pump unit assembly respectively as set forth hereinafter. Suitable vertical supporting webs such as those indicated in dotted lines in FIGS. 7 and 8 at 60 constitute reinforcements and are disposed within the casing 50 to strengthen and brace the platforms 56 and 58. As will be more readily understood from FIG. 9, the webs 60 are relatively diagonally disposed and welded at their joints with each other and with the side and end walls 62 and 64 and the bottom surfaces of the platforms 56 and 58. The spaces between the webs are open at the lower ends of the latter which terminate along a line 54 which is parallel to the platforms 56 and 58. A longitudinal vertical rib 68 extends the full length of the casing and a transversely disposed lubricating communicative conduit 66 extends there-across. Laterally extending flanges 72 and 74 project from the sides and ends of the base for engagement of fastening means.

As will be best apparent from FIGS. 1-6, support base 50 extends transversely of the truck bed with a supporting platform 56 for the transmission assembly being disposed at the other side thereof. Indicated by the numeral 80 is a casing or housing for the power transmission assembly which actuates the pump unit 20. As will be observed, the housing 80 is disposed upon that portion of platform 56 which is adjacent to platform 58.

Disposed below the pump unit 20 and mounted upon the opposite sides of the crankcase 50 are discharge valve assemblies, indicated generally by the numeral 82, and which are best shown in FIGS. 1, 3-6, 10 and 12. These, together with the pump units, are operatively connected with the transmission assembly and with the Y-tube assembly in a manner and for a purpose to be set forth hereinafter. Also supported upon platform 56 in an instrument and control panel 84 (see FIGS. 2, 4-6), the same having end walls 86 together with reinforcing webs 88.

As shown in FIG. 4, the end wall of the housing 80 of the transmission assembly, which is adjacent to the rear of the truck, is provided with a pair of closure and access plates 90 and 92. A suitable removable cover is provided for various portions of the housing 80 for obtaining access to the transmission mechanism and other assemblies enclosed therein.

At this point, referring especially to FIGS. 1, 5 and 12, it will be seen that the pump unit includes a pair of pump power cylinders 100 with a counterbalance or compensating cylinder 102 disposed therebetween. The Y-tube assembly 30 is operatively and detachably associated with the power cylinders 100 and with their valve assemblies 82.

The Y-tube assembly consists of a pair of parallel straight conduits 104 having rigidly attached thereto coupling flanges 106 which are adapted to engage with corresponding flanges 108 forming the heads of the power pump cylinders 100 whereby the conduits or pipes 104 may be removably secured to the power cylinders and communicate with the interior thereof. At their opposite ends the conduits 104 are welded to intermediate portions of the pipes or conduits 110 which are disposed to intersect therewith at a slight angle as shown in FIG. 10. At their rearward ends the conduits 110 have end portions 112 which are in generally side by side relation to each other and to the conduits 104, and which likewise are provided with coupling flanges 114 adapted for detachable connection with corresponding flanges 116 of the valve assemblies 82. At their other ends the conduits 110 are provided with a pair of parallel terminal portions 118 likewise terminating in coupling flanges 120.

In order to rigidify the assembly of conduits and support the same in operative position upon the apparatus, the conduits 104 are provided with mounting brackets 122 which are welded thereto and which extend toward each other for engagement by a connecting plate 124. A similar connection serves to rigidly connect the terminal portions 118 of the conduits 110 at the forward ends, comprising laterally projecting lugs 126 together with a connecting plate 128. Welded to the underside of each of the conduits 104 adjacent their rearward end are depending mounting brackets or flanges 130 to which are secured in any suitable manner support members 132 (see FIGS. 11 and 12), the latter at their lower end having mounting flanges 134 by which they may be secured to crankcase 50.

Detachably connected to the outer end of the Y-tube assembly is an extension assembly by which the Y-tube may be coupled to a test chamber 150 as shown in FIG. 13 or may be connected to any other place of use such as a well casing and tubing assembly. The extensional connecting assembly of the Y-tube assembly comprises a pair of pipes 152 having a coupling flange 154 at one end of each by means of which the pipes 152 may be coupled to the terminal portions 118 of the pipes 110 at their coupling flanges 120. At their other ends the pipes 152 are provided with downturned extremities 156 terminating in coupling flanges 158. Bleed and sampling lines 157 are connected to the pipes 152 at their high point where they join to the downturned extremities 156 for a purpose to be subsequently set forth. Also, wave pressure gauge lines 159 are connected to the pipes 110 beyond the junction of the pipes 104 therewith. Suitable brace rods 160 serve to brace and rigidify the end portions 156 and, in addition, a cross brace 162 similar to the constructions 122, 124, and 126, 128 previously described may be employed adjacent the couplings 158.

The flanges 158 are adapted to be selectively coupled to the tubing or a pipe line in a well casing, to the interior of the well casing in any suitable manner, or to the test chamber 150, or to any other object to which the pressures and waves generated by the pump unit 20 are to be applied.

The general organization also includes numerous gauges and control means to be referred to hereinafter.

POWER TRANSMISSION ASSEMBLY

(FIGS. 14-30)

The details of the power transmission assembly whereby power from the internal combustion engine 22 or other source of power is supplied by means of a pair of crankshafts and crosshead assemblies to the pump unit and to an auxiliary or feed pump is illustrated particularly in FIGS. 14-30.

As will be more readily apparent from FIGS. 14 and 15, the power transmission assembly comprises a pair of upper and lower parallel crankshafts 170 and 172, each secured by suitable bearings 174 to the vertical surface of vertically extending ribs 176 in the power transmission casing 80. The two shafts (see also FIG. 19) are geared together by the connecting gears 178 and 180 and the lower shaft 172 may be provided with a flywheel 182 and extend through the end of the transmission casing 80, being provided with a coupling 184 by means of which it is secured to a power output shaft 186 operatively connected to the power plant 22. By means of a suitable belt drive 188 (best shown in FIG. 1) the engine power output shaft 186 is also connected to the driving shaft 190 of the auxiliary or feed pump 26 (best shown in FIG. 1), a housing or guard 192 being provided to enclose this driving connection.

As so far described, it will now be apparent that power from the power plant is applied to the lower crankshaft 172 for driving the same and that the upper crankshaft 170 is driven from the lower crankshaft in timed relation thereto.

Referring now specifically to FIGS. 18 and 19, in conjunction with FIGS. 14 and 15, it will be seen that the upper crankshaft 170 is provided with a flywheel 194 at its right extremity and that the upper shaft 170 is of lesser length than the lower crankshaft 172. Further, there is provided an angularly adjustable coupling operatively interposed between gear 178 and upper crankshaft 170, which may consist of a differential gear assembly, designated generally by the numeral 196.

For this purpose, there is an aligned shaft extension 198 secured to the gear 178 and terminating in spaced relation to the end of the upper crankshaft 170. The adjacent ends of the shaft 170 and the shaft extension 198 are splined as at 200 and 202, respectively, and these splined extremities are received in the differential assembly 196 whereby, as set forth hereinafter, the crankshaft 170 may be given any desired angular adjustment with respect to the shaft extension 198, and also with respect to the lower crankshaft 172 which is geared to the extension 198.

The lower crankshaft 172 is provided with a gear 204 and intermediate its ends is also provided a gear 206 for a purpose to be later set forth. The two crankshafts are each provided with vertically aligned sets of three crank throws, those of the upper crankshaft 170 being shown in FIG. 14 at 208, 210 and 212, while the lower crankshaft has its three throws indicated at 214, 216 and 218.

As will be seen from FIG. 14, the throws 208 and 214 are in vertical alignment, 210 and 216 are in vertical alignment and 212 and 218 are in vertical alignment. By a rocker mechanism to be subsequently set forth the upper and lower end throws 208 and 214 are operatively connected by one rocker to one of the pump unit pump working cylinders, while the other two end throws 212 and 218 are similarly connected by a second rocker to the other pump unit pump working cylinder. The two middle throws 210 and 216 are connected by a third rocker to the pump compensator cylinder 102.

As shown in the schematic view of FIG. 17, the crank throws 208 and 212 are disposed 90.degree. angular interval, with the crank throw 210 being at an intermediate position and at 135.degree. to each. As shown, the crank throw 208 leads the throw 212 by 90.degree.. It is to be understood that the crank throws 214, 216 and 218 of the lower crankshaft are likewise disposed at such intervals, although by operation of the differential mechanism 196 the annular relationship of the crank throws in the upper crankshaft 170 with respect to the corresponding crank throws of the lower crankshaft 172 can be readily varied to any desired angular relation for the purpose to be subsequently set forth.

Referring next primarily to FIGS. 26-28, together with FIG. 14, it will be seen that the differential assembly 196 is of any conventional and well-known design and receives therein the splined ends of the shaft 170 and its shaft extension 198. Secured in any suitable bearings 220 is an adjusting shaft 222 which extends to the exterior of the casing 80 and is provided with a manual adjusting wheel 224 thereon (see FIG. 4). Secured to the shaft 222 and disposed between bearings 220 is a worm gear 226 which continuously meshes with a ring gear 228 mounted upon the differential assembly housing whereby, upon rotation of the worm and ring gear, the angular relation between the shafts 198 and 170 may be varied.

Associated with the shaft 222 (see FIG. 29) is an indicating means for registering the angular relationship between the two crankshafts. For this purpose a trammel 230 is secured to the wall of the housing 80 and cooperates with a calibrated dial 232 which is secured to a shaft 234. The latter is carried by and extends into a housing 236 and carries within said housing a gear 238. By means of a stub axle 240 within the housing 236 a compound gear consisting of a large gear 242 and a small gear 244 are journaled for rotation, the latter engaging the dial gear 246 formed upon the previously mentioned adjusting shaft 222. By an appropriate gear ratio it is evident that the movement of the adjusting shaft 222 can be utilized to appropriately indicate by the dial and the trammel the angular relation between the two shafts 198 and 170, which is also the angular relationship between the shaft 170 and the shaft 172.

Special reference is now made to FIGS. 20-25 and 30 for an explanation of the rocker guide and slide assembly by which the pistons of the pump unit are operatively connected to the crankshafts. In this connection, reference is also made to FIGS. 5, 6 and 15.

Each of the three pump unit cylinders has its piston provided with a piston rod which is operatively connected to the pair of crankshafts by means of a rocker and a slide and guide assembly. Since the rocker, guide and slide assemblies for the two pump working pistons and the pump counterbalance piston are substantially identical as to features of structure, it will be understood that the description and drawings directed to the former also describe and will suffice for an understanding of the latter. The piston rods for the two pump working cylinders 100 of the pump unit are designated by the numeral 260, while the rod for the piston of the counterbalance cylinder is indicated at 262 (see FIG. 5). Mounted upon the platform 58 as shown in FIGS. 5 and 22 are a plurality of crossheads or guides or guide brackets 264 comprising bearings or supports for the slides which carry the rocker arms. Each bracket 264 is positioned between each of the vertically disposed pair of throws of the two crankshafts and an associated pump unit cylinder 100 or 102 as shown in FIG. 15.

The construction of each guide bracket 264 of the cross-head is clearly shown in FIG. 23, the same including a base 266 adapted to be secured by bolts to the surface 58 and having a longitudinally extending keyway 268 therebeneath which is engaged with a positioning key 270 disposed in the surface 58 as shown in FIG. 22 and FIG. 24. The member 264 is further provided with an overhanging arm 272 which overlies and is parallel to the base 266 to provide a horizontally and longitudinally extending guide slot therebetween. The adjacent surfaces of the base and arm are provided with curved guide surfaces 274 and 276 respectively between which is secured a slide to be hereinafter described. A closure plate or end plate 278 is secured as by fastening bolts 280 engaged in threaded recesses 282 formed in the member 264, whereby to close the outer end of the slot between the arm and the base. There is provided a bore 284 disposed through the member 264 and opening centrally and longitudinally of the slot between the arm and base for the reception of the piston rods 260 and 262.

Slidably and guidably received in the slot of the member 264 between arm 272 and base 266 thereof is a slide indicated generally by the numeral 290 as shown in FIG. 25. This slide comprises an elongated body 292 having upper and lower rounded guiding surfaces 294 and 296 which are complementary to and cooperate with previously mentioned guide surfaces 276 and 274 of the guide 264. The body is provided with a plurality of longitudinally extending guide bores 298 which are slidably received upon the fastening bolts 280 previously mentioned, as will be apparent from a comparison of the FIGS. 22 and 24. A pair of cylindrical projections or trunnions 300 extend from opposite sides of the body 292 and project laterally from the sides of the slot formed in the member 264 between the arm 272 and the base 266 thereof. Retainer disks 302 are secured by bolts 304 to the ends of the projections 300 as best shown in FIG. 22. Oil grooves such as that shown at 295 extending longitudinally of the top surface 294 serve to facilitate lubrication of the slide.

Referring now to FIGS. 24 and 25, it will be seen that the elongated body 292 of the slide is provided with a bore 306 extending centrally therethrough and opening upon that end of the slide body which is adjacent to the slot closure plate 278, and an axially aligned internally threaded bore 308 of a different diameter and which merges with the bore 306 being separated therefrom by an annular rib or ring 310.

Use is made of this bore construction to detachably secure a piston rod 260 or 262 to the slide body. Thus there is provided a connector having an externally threaded cylindrical stem 312 which is seated in the bore 308 and abuts the rib 310, and which has its other end diametrically reduced and externally threaded as at 314 for engagement in the internally threaded extremity of the rods 260 or 262. Between the portions 312 and 314, the connector is provided with an enlarged collar or rib 318 which abuts against the end of the rod 260 or 262 and against the end of the slide body 292. A cap screw 319 and washer 321 cooperating respectively with an internally threaded bore in the connector body portion 312 and the rib 310 serve to secure the piston rods 260 and 262 to the slide bodies 292.

As so far described it will be apparent from FIG. 24 that the collar 318 of the connector and the attached end of the rod 260 are slidable through the previously mentioned bore 284 of the guide body 264.

It will also be noted by a study of FIGS. 23, 24 and 30 that the closure plate 278 has arcuate raised surfaces 320 which are adapted to engage the ends of the plates 276 and 274 to retain the latter tightly in position in the slotted portion of the member 264. In addition, the plate 278 is provided with further raised surfaces 322 which engage the recessed end surfaces 324 of the arm and base of the member 264 to secure a firm seating engagement therewith.

Disposed upon each side of the slide body 292 and freely journaled upon the projections 300, being retained thereon by the retainer disks 302, are a pair of rockers 326 and 328. As best shown in FIG. 20, the two ends of the arms of the rockers 326 and 328 have transversely aligned apertured bosses 330 and 332, respectively, the bores or apertures in the bosses 332 being smoothly cylindrical as indicated at 334 while both of the bosses 330 are cylindrical and splined at their outer end portions only as at 336. A pair of connecting rods 338 and 340 are adapted for respective journaling upon the upper and lower crankshafts 170 and 172 previously mentioned. The connecting rods 338 and 340 are provided for the rocker assemblies which are operatively connected to the pump unit working piston connecting rod 260. A modified construction of connecting rod 342 is employed for the throws 210 and 216 of the upper and lower crankshafts which are connected to the rocker assembly that, in turn, is connected with the counterbalance cylinder piston rod 262 of the pump unit.

Each of the connecting rods 338, 340 and 342 has a cylindrical bearing 344 thereon and extending transversely at one end thereof and constituting a wristpin bearing which is received between the adjacent apertured bosses 330 and 332 of each of the rocker arm assemblies. For use with the connecting rods 338 and 340 of the pump working piston assemblies there are provided wristpins 346 having centrally disposed eccentric bearings 348 thereon for reception in the wristpin bearing 344. The opposite ends of the wristpins 346 are provided with a pair of cylindrical slide bearing or retaining surfaces 350 for engagement in the cylindrical bearing bores 334 of the rockers 328, and with a cylindrical splined extremity 352 for sliding, non-rotating engagement in the splined bores 336 in the rockers 326.

It will thus be apparent that the connecting rods of the upper and lower crankshafts are connected to the upper and lower ends of the rocker arm assemblies, each assembly comprising a pair of rocker arms 326 and 328, in such a manner that by rotationally adjusting the extension 348 of the wristpin 346 in the connecting rod wristpin 344, an independent eccentric adjustment of the wristpins of the two connecting rods attached to each rocker assembly can be obtained. When so obtained the splined engagement of the members 352 and 336 will serve to retain the wristpins in their adjusted position.

By means of this arrangement the length of the connecting rods of the upper crankshaft with respect to the length of the connecting rod of the lower crankshaft and also the effective operating length of lever arms of the rocker can be varied readily thereby varying the velocity, accelerations and ranges or the reciprocation of the slides 292 and of the piston rods and pistons rigidly connected therewith.

Further, in the connecting rod 342 by means of which the middle throws of the upper and lower connecting rods are attached to the rocker arm assembly which actuates the pump unit counterbalance piston 262, the wristpin bearing 344 receives therein a wristpin of a similar construction and operation to wristpin previously described in connection with the pump working piston assemblies.

As previously mentioned, the connecting rods 342 of the counterbalance cylinder unit are of the same general construction as those (338 and 340) of the pump working cylinders but are approximately 1.41 times the weight of the latter. This particular weight relation arises from the particular angular relation of the crank throws 210, 216 to the throws 208, 214 and 212, 218. Obviously other angular relations between these throws would result in different weight relations. Further, the same weight ratios are provided between the corresponding rockers, pistons, piston rods and slides of the single counterbalance unit and the pair of pump working cylinder units.

It is an especially important and advantageous feature of this construction that it enables a precise and controlled variation of the length of each connecting rod, of each end of a rocker arm and of the effective lever arm of each end of each rocker arm. This further enables the counterbalance assembly to have an eccentric adjustment which will compensate for any given eccentric adjustment of the two working cylinder rocker eccentrics.

As so far described, it will now be apparent that by adjusting the differential assembly 196, the crank throws of the two crankshafts may be given any desired lead or angular variation with respect to each other and thus one may vary the position of travel, as well as the rate of travel and rate of acceleration of the rocker arm slides and consequently of the pump piston rods associated therewith. By this means a wide range of adjustments of the stroke of the pistons of the pump unit are possible. Still further individual adjustments may be made as to individual pistons of the eccentric piston pin construction and the splined means for retaining the same in adjusted position.

PUMP ASSEMBLY

(FIGS. 31-38)

A pump unit or pump assembly constituting the wave generator and forming a sub-assembly of this apparatus has been previously identified by the numeral 20 and appears in the assembly views of the apparatus in FIGS. 1, 3-6. Reference is now made more specifically to FIGS. 31-38 for a description and showing of the construction of the components of the pump assembly.

As previously described, the pump assembly illustrated consists of three cylinders disposed in side-by-side arrangement and including a pair of outer cylinders 100 comprising the power cylinders or the working cylinders of the pump unit, together with a cylinder 102 between the two outer cylinders and which comprises a counterbalance or compensating cylinder for the unit.

Since the two outer working cylinders 100 are of identical construction, the same numerals employed to designate the corresponding parts of each, reference will now be made specifically to FIG. 32.

As shown, and as described hereinabove, the cylinders 100 have the coupling flanges 108 which are detachably secured to the coupling flanges 106 of the pipes or conduits 104. The cylinders are provided with a recessed or enlarged bore 360 which comprises a water jacket for the pump and a sleeve or cylinder liner 362 is received within cylinder 100, suitable O-rings 364 being provided therebetween to establish a fluid-tight seal between the cylinder liner and the cylinder 100 to form the water jacket therebetween. Suitable annular cannels or grooves 366 and 368 are formed in the adjacent end surfaces of the coupling flanges 108 and 106 respectively to receive therein a correspondingly shaped packing metal O-ring 370 and aligned bores 372 and 374 are formed in the cylinder 100 and in the coupling flange 106.

A removable insert sleeve 371, having an O-ring 373, is removably seated in a counterbore 375 in the outer end of the bore 372 and is retained in place by the engagement of the metal O-ring 370. Removal of this sleeve gives access for applying a wrench to the valve assembly of the pump piston, to be later described.

At its end which is remote from the coupling flange 106 the bore 372 of the cylinder liner 362 is diametrically enlarged to provide a bore 376 and a bushing or sleeve 378 (see also FIG. 35) is received in the enlarged bore 376 intermediate the ends of the latter. A plurality of packing rings 380 are disposed in the enlarged bore 376 on opposite sides of the bushing 378, those at the right side of the bushing abutting against the retainer plate 382 seating on one end of the bore while those at the left are engaged by a packing gland or bushing 384 which is slidable in the open end of the enlarged bore 376 and in the registering bore 386 of the cylinder 100, a packing retainer ring 388 being disposed in a recess or enlargement 390 in the packing gland 384. The latter is provided with a coupling flange 392 whereby the packing gland may be clamped to the open end of the cylinder 100 as by means of fastening bolts 394. It will be observed that the packing gland and the coupling flange thereof are provided with an axial bore 396 extending therethrough and which is of the same diameter as the bores 372 and 374.

Slidable in the bores 396 and 372 and in the bushing or sleeve 378 is a pump piston 400 of a construction to be subsequently described, the packing members 390 serving to provide a fluid tight packed joint therewith.

A water inlet conduit 402 communicates with the water jacket 360 through an inlet passage or bore 404 in the wall of the cylinder for supplying water or other suitable coolant to the cooling jacket of the cylinder from any suitable source. At the lower side of the water jacket there is provided a water outlet passage 406 together with a drain plug 408 whereby the water jacket of the cylinders may be drained as desired.

The bore 374 constitutes the fluid outlet or the pump discharge means of the pump cylinder 100. In order to admit fluid to the cylinder to be compressed and pumped thereby, there is provided an inlet conduit 410 which extends through a suitable packing gland 412 in the wall of the cylinder 100 and has its extremity threadedly engaged in the bore 414 in the cylinder liner 362. In addition, the sleeve 378 (again see FIGS. 35 and 32) is provided with a circumferentially extending channel 416 upon its outer surface and 418 upon its inner surface with inwardly extending bores 420 communicating therebetween. As will be now apparent, the grooves 416 and 418 and the bores 420 establish continuous communication between the inlet conduit 410 and the interior of the sleeve 378, and thus into the interior of the piston 400 as will be apparent hereinafter.

Fluid is supplied to each of the pump unit working cylinders 100 by means of a supply pipe 422 which in turn is connected as by the valve fittings 424 with the previously mentioned pump inlet conduits 410, as will be readily apparent from FIGS. 1 and 4-6. The previously mentioned feed pump unit 26 constitutes the means for supplying the fluid under pressure to the supply conduit 422 and thus to the interior of the working cylinders 100 of the pump unit 20.

It is also contemplated and is an important concept of this invention to provide a heating means of any suitable type (not shown) for heating the fluid supplied by the conduit 422 and the feed pump unit 28 to the pump unit 20. Since the details of the pump feed conduit heater are not material to the invention claimed herein an illustration of the same is omitted as being unnecessary. However, this heater may be applied anywhere along the conduit 422 and especially thereon adjacent the communication of this conduit with the cylinders 100 of the pump unit 20.

Referring especially to FIGS. 4, 6 and 31A, it will be seen that an accumulator 425 is utilized in connection with each pump working cylinder 100 and an accumulator 474 is associated with the pump counterbalance cylinder 102. Since the construction and operation of these accumulators is identical a description of the accumulator 425 as disclosed in FIG. 31A will suffice for all.

The accumulator 425 comprises a cylindrical housing having a tubular neck 427 at one end by which it is secured to and communicates with the pump cylinders 100 or 102. At its other end, the housing has a connection 429 by which it is connected through a conduit 431 to a suitable source of inert gas under pressure, by means of suitable control valves such as a nitrogen bottle or the like.

Secured to the connector 429 in the interior of the housing 425 is an expansible bag 433 which is inflatable to predetermined volume by controlling the quantity of inert gas introduced thereinto from the conduit 431 and thus apply a predetermined, variably adjusted pressure upon the contents of the housing 425.

The neck 427 has a valve seat 435 at its junction with the interior of the housing 425 which is controlled by a spring opened inwardly, opening poppet valve 437. The latter has its stem 439 slidably guided in radially extending ribs 441 in the stem 427, a compression spring 443 engaging the ribs and valve head to yieldingly open the latter. A retainer 445 of any suitable character is carried by the stem 439 and abuts the ribs 441 to prevent withdrawal of the poppet valve 437 from the tubular neck. A drain or bleed plug 451 is provided in the stem 427.

The operation of this portion of the apparatus is as follows. The inflatable bag 433 is supplied with an inert gas and is maintained at a pressure about one-half of the working pressure. This pre-loading of the accumulator maintains an even pressure on the fluid intake of the working cylinder 100, supplied by the intake conduit 410. When employed with the counterbalance cylinder 102, as shown at 474 in FIG. 31, it serves to dampen pulsations and to return energy to the counterbalance piston and from there to the pump pistons.

The purpose of the valve 437 is one of safety. It prevents or limits expansion of the inflatable bag 433 in the event of loss of fluid in the housing 425 for any reason and permits pre-loading of the accumulator in preparation for operation of the apparatus.

At this point attention is directed to FIGS. 31 and 36 for a description of the counterbalance cylinder 102 of the pump unit which is provided with an axial bore 430 diametrically enlarged or recessed intermediate its ends as at 432 to provide a cooling jacket. Received in the axial bore is the cylinder sleeve or cylinder liner 434 which at one end is provided with an enlarged flange 436 adapted to be secured to the end of the cylinder 102 as by fastening bolts 438. Suitable O-rings or packing or sealing members 440 and 442 are provided between the cylinder liner 434 and the bore 430 of the cylinder and between the enlarged flange 436 and the end of the cylinder.

An axial bore 444 extends through the cylinder liner and constitutes the chamber of the counterbalance pump, this bore having a reduced internally threaded end 446 for a purpose to be subsequently apparent. At its other end, the bore is diametrically enlarged as at 448 to receive therein a plurality of packing members 450 which abut against a retainer ring 452 seated on the annular surface at the bottom of the bore 448 and its junction with the bore 446. A packing gland 454 in the form of a sleeve is slidably received in the bore 448 to compress the packing 450 therein and is provided with an enlarged centrally aperturned flange 456 by which it is secured to the open end of the cylinder 102 as by means of fastening bolts or studs 458. Slidable in the chamber 444 is a preferably solid piston plunger 460 comprising the counterbalance piston of the pump unit as set forth hereinafter. This piston has a fluid tight engagement in the bore 444 by means of the packing member 450 previously mentioned.

Coolant is supplied to the cooling jacket of the counterbalance cylinder and is discharged therefrom by any suitable cooling circulating system, which may include the coolant supply conduit 462 (see FIG. 31) and the coolant discharge conduit 464.

Each of the previously described working cylinders 100 and the counterbalance cylinder 102 are mounted upon the previously described surface 58, being retained in selected position thereon as by means of keys 466 secured to each of the cylinders as by bolts 468 and projecting therebeneath for engagement in recessed grooves or channels 470 in the surface of the platform 58 as will be apparent from FIGS. 31, 32, 36 and 38.

Referring now to FIG. 31, it will be seen that the internally threaded bore 446 of the working chamber 444 has a nipple 472 engaged therein and by which an accumulator 474 is secured to and placed into operative communication with the chamber 444. This accumulator is of the same construction described in detail in connection with FIG. 31A. Opposite to the nipple 472, the accumulator 474 is provided with a coupling 476 and a conduit 478 corresponding to the conduit 431 previously mentioned by means of which any desired fluid pressure may be applied and maintained in the accumulator chamber and within the inflatable rubber bag therein. A suitable volume of liquid 480 may be retained in the accumulator chamber 474 to thus apply any desired back pressure to the counterbalance piston 460.

In the compensator cylinder and accumulator of FIG. 31 a working pressure compensating conduit 449 applies the main working pressure in the Y-tube assembly 30 to the pump counterbalance cylinder 102 by a conduit 449 and a bore in the cylinder head 436. Thus the pressure operating in the Y-tube assembly is equalized with that in the compensator cylinder and its accumulator.

Referring again to FIGS. 36 and 37, it will be seen that the counterbalance piston 460 is provided with a stem extending therefrom and comprising the previously mentioned piston rod 262 which rod may be provided with a diametrically reduced polygonal shaped portion 484 for engagement by a wrench and terminates in a diametrically reduced externally threaded extremity 486 by which it is detachably secured to the body of slide 292 (see FIGS. 24 and 25) as by means of the previously described cap screw 319. Since the slide is of substantially the same construction for both the working cylinders and the counterbalance cylinder of the pump unit, the illustration of this slide in FIGS. 24 and 25 and the description of same as set forth hereinbefore will suffice for an understanding of the slide and its association with the counterbalance cylinder.

Referring now specifically to FIGS. 33 and 34 for an understanding of the construction of the pump working piston 400. The latter comprises a cylindrical member which is open at both ends, being provided intermediate its ends with a partition 500. Immediately adjacent this partition and extending towards the forward end of the piston therefrom is a longitudinally extending slot 502 constituting the inlet port opening into the hollow interior of the piston and which at all times registers with the openings 420 in the sleeve 378 and thus with top inlet conduit 410 as previously described.

An inlet valve cage 504 has a diametrically reduced externally threaded rear extremity 506 screw threadedly engaged in the internally threaded bore 508 at the open right end of the piston 400. At its outer end the hollow cage 504 is provided with a valve chamber 510 which terminates in a conical valve seat 512. One or more fluid passages 514 extends from the chamber 510 into the interior of the piston 400 and a spider 516 is provided with an axial valve stem passage 518 in which is slidably received and guided the stem 520 of the valve 522.

At its other end the valve stem is reduced in diameter and is externally threaded as at 532 and by means of a pair of lock nuts 534 and a flanged guide sleeve and retainer 536, a compression spring 538 is compressively engaged and abutted against the spider 516 and its projecting guide bushing 517 to thus yieldingly retain the valve upon its seat.

It will thus be seen that fluid entering the interior of the piston through the port 502 may enter by the passage 514 into the chamber 510 and thus may pass the valve when the latter is opened as set forth hereinafter.

The open other end 260 of the piston 400, comprising the abovementioned piston rod, is internally threaded as at 540 to receive a connector 312 as previously mentioned and as shown in FIGS. 24 and 25 by which the pump working piston is secured to guide member 292. Pin 542 may be employed to retain the connector in pump piston 400 against accidental displacement therefrom.

As so far described, it will now be apparent that by appropriately choosing the mass of the counterbalance piston and in view of the angular disposition of the crank throws of the two crankshafts which are connected to the counterbalance piston and to the two working or pump pistons, the inertia and force of the working pistons may be effectively balanced to thereby eliminate vibrations to the mechanism arising from the reciprocation of the three pistons. In addition, by adjusting the back pressure or load applied to the counterbalance piston through the fluid pressure maintained in the accumulator chamber 474 of the counterbalance cylinder the load imposed upon the mechanism by the pump pistons may be effectively also counterbalanced. Thus there results a smooth working and vibrationless mechanism in the three cylindered unit of the pump unit.

It is evident that during their reciprocation, as fluid is required in the bores 374 and 372, the pump working piston 400 will intake fluid from the supply conductor 410 and passage 502 into piston 400 behind the valve 522 on the piston outstroke and on the piston instroke will discharge this fluid past the valve and into the bores 372 and 374 in front of the pistons.

It is also to be understood that the valved pistons 400 and their inlet means 422, 424, 410, and 420 may also be employed to introduce other liquids and gases into the conduits of the Y-tube assembly for other purposes as desired.

OPERATION OF APPARATUS

1-43

The operation of the apparatus of FIGS. 1-43 is as follows. As shown in the diagrammatic view of FIG. 39, fluid pressure is supplied from the nitrogen tank 1420 to the discharge valve assemblies 82 for preloading their valves, and to the accumulative cylinders 474 and 425 of the counterbalance cylinder 102 and the work cylinders 100 of the pump unit 20. Water, oil or other fluid upon which the pump unit 20 is to operate is supplied from the tank 28 or other suitable source to the feed pump 26 and from the latter, by the feed conduit 422, to the working cylinders 100 of the pump unit, from which cylinders the fluid is discharged by the piston valves in the pump cylinders into the pipes or conduit 104 of the Y-tube assembly 30. By means of the Y-tube assembly and the conduits 152 the fluid is supplied to the interior of a well bore or to any other object to which the fluid pressure and the wave generated therein is to be applied.

The reciprocation of the pump pistons in the working cylinders 100 operates to produce a high frequency pulsating wave in the fluid medium as hereinbefore set forth. Further, the pump pistons serve to drive or propel the fluid medium through the conduits 104 previously mentioned. In conjunction with the propulsive action of thp working cylinders of the pump unit, the discharge valve assemblies through the tubes 110 serve to discharge fluid from the Y-tube assembly and from the pipes and conduits connected therewith. By appropriately timed operation of the discharge valves, under specific variable timing control means hereinbefore set forth, further high frequency energy carrying waves may be set up in the fluid.

The stroke of the working pistons of the pump unit are capable of a wide range of variation as to the time of the stroke, the duration of the stroke, the velocity, acceleration and range of movement of the pistons during their stroke, while additionally the phase relation between the pistons can also be adjusted.

The angular or phase relation between the two crankshafts 170 and 172 rotating at a uniform velocity can be adjusted by the differential assembly 196 operatively interposed therebetween as shown in FIG. 14, thereby resulting in considerable variation in the type of motion, see FIGS. 40-41, imparted to the reciprocating crosshead or slide 290, see FIG. 25, through the pair of rockers 328, see FIG. 15, which rockers are connected to the pair of crankshafts.

In addition to the variation of motion imparted to the slides and pistons by adjusting the phase relation between the two crankshafts, it is also obvious that further considerable variation can be obtained by appropriate individual adjustments of the eccentric bearings 344 of the wristpins by which each end of the rocker assemblies is secured to one of the two crankshafts.

For a more complete understanding of the type of variation of movement obtainable by the eccentric adjustments of the connections between the crankshaft connecting rods and the crosshead rocker arms, attention is now directed more specifically to FIGS. 40-43. In these diagrammatic views, the pair of crankshafts are indicated by the numerals A and B, and there are crankshafts C and D connected to the rocker E whose pair of oppositely extending arms F and G are engaged by adjustable eccentric connections H and I. The central portion of the rocker is shown pivoted as at J to the slide or crosshead K to which the pistons of the working and counterbalance cylinders are connected. The position of the crank throws or the crankshafts A and B to which the connecting rods C and D are pivoted is shown at L and M in FIG. 40, and the full line position of the rocker arm E, with the eccentric connections H and I being in a neutral position may be regarded as a normal position to which the other positions of adjustment may be compared. Shown in dotted lines in the position E' of the rocker arm when the two crank throws L and M are disposed at 180.degree. positions, or at L' and M'. The position N therefore represents the normal distance of travel given to the slide K and therefore to the pump and counterbalance pistons during the rotation of the crankshafts in the above described neutral position of the associated parts of this mechanism.

In FIG. 41 is shown the position of the parts in which the differential gear assembly 196 has been manipulated to effect a different phase relation between the crankshafts A and B, from that shown in FIG. 40, as by advancing the crankshaft A 90.degree. with respect to that of B. The full and dotted line positions again show respectively the rearward and forward extremities of the slide during its operation for the setting of the parts with the eccentrics being again in their neutral position.

FIG. 42 shows the effect upon the motion of the slide and therefore upon the pistons of the pump unit which may be obtained by adjusting the eccentric connections H and I each to their maximum away from the central line or axis of travel of the reciprocating slide K.

FIG. 43, in turn, shows the effect upon the motion imparted to the slide and pistons when the eccentric adjustments H and I are both adjusted in the same direction, with the crankshafts remaining in the neutral position shown in FIG. 99.

It will be noted that the adjustment of eccentrics H, I or both, serves to vary the effective length of the rocker arms F or G as well as the effective length of the connecting C and D.

It will thus be understood that by means of the individual adjustments of each of the eccentrics H or I for each piston, as well as by the adjustment of the phase relation of the two crankshafts A and B, a very wide variety of motions, accelerations, and amplitude or travel may be given to the pistons, thereby varying their stroke from zero to a maximum, and also providing an infinite number of variations in their accelerations.

Claims

What is claimed:

1. A generator of energy transmitting waves in a liquid medium comprising a reciprocating pulsator having direct contact with said medium during generation of compression and rarefaction phases of said energy waves, a pair of drive shafts, a guide, a slide mounted upon said guide for rectilinear reciprocation and connected to said pulsator, a rocker pivoted at its midportion upon said slide for reciprocation therewity, a pair of connecting rods each connected to one of said drive shafts, means adjustably pivoting each connecting rod to one end of said rocker and thereby varying the axis of the pivotal connection from the rocker axis of pivotal connection to said slide, means for driving one of said drive shafts and a driving connection between said shafts for varying the angular relation therebetween and thereby varying the movement imparted by the rocker to said pulsator.

2. A generator of energy transmitting waves in a liquid medium comprising a reciprocating pulsator having direct contact with said medium during generation of compression and rarefaction phases of said energy waves, a pair of crankshafts, a guide, a slide mounted upon said guide for rectilinear reciprocation and connected to said pulsator, a rocker pivoted at its midportion upon said slide and reciprocable therewith, a pair of connecting rods each pivoted to a crankshaft and to one end of said rocker, means for causing rotation of one crankshaft, means interconnecting said crankshafts, means for varying the phase relation of said crankshafts whereby to independently vary the motion imparted by each crankshaft to said rocker and slide, an eccentric pivot connecting each connecting rod to said rocker and operable to vary the effective length of its rocker arm.

3. A generator of energy transmitting waves in a liquid medium comprising a reciprocating pulsator in direct contact with said medium, a pair of drive shafts, a reciprocatory counterbalance weight, a pair of guides, a slide mounted on each of said guides and connected one to said pulsator and the other to said counterbalance weight, a pair of rockers each pivoted at its mid-portion to one of said slides for reciprocation therewith, each rocker having a pair of connecting rods connecting it to both of said crankshafts, means for driving one of said crankshafts, means interconnecting said crankshafts, means for varying the phase relation of said crankshafts, adjustable means pivoting said connecting rods to said rockers whereby to vary the effective length of the rocker arms, said adjusting means for said counterbalance weight rocker being operable to proportion the counterbalance stroke to compensate for variations in the pulsator stroke.

4. An assembly for generating an energy wave having compression and rarefaction phases within an energy wave transmitting medium, comprising a working cylinder and a counterbalance cylinder each having a piston reciprocable therein, a source of power, means connecting each piston to said source of power for reciprocation thereby, said counterbalance piston being of such mass and disposed at such phase relation to said working piston as to balance the momentum of the latter and its associated connecting means, including pressure equalizing means for applying the pressure at the working piston output to the counterbalance piston.

5. An assembly for generating an energy wave having compression and rarefaction phases within an energy wave transmitting medium, comprising a working cylinder and a counterbalance cylinder each having a piston reciprocable therein, a source of power, means connecting each piston to said source of power for reciprocation thereby, said counterbalance piston being of such mass and disposed at such phase relation to said working piston as to balance the momentum of the latter and its associated connecting means, including means for storing energy into the counterbalance piston by fluid pressure from the working piston on its working stroke whereby to obtain a flywheel effect from the counterbalance piston.

6. An assembly for generating an energy wave having compression and rarefaction phases within an energy wave transmitting medium, comprising a working cylinder and a counterbalance cylinder each having a piston reciprocable therein, a source of power, means connecting each piston to said source of power for reciprocation thereby, said counterbalance piston being of such mass and disposed at such phase relation to said working piston as to balance the momentum of the latter and its associated connecting means, including adjusting means in the means connecting each piston to said source of power for varying the resultant thrust of one piston upon the other whereby to maintain the pistons balanced despite variations in their strokes.

7. A generator of energy transmitting waves in a liquid medium comprising a pump cylinder having communication with a liquid medium and a reciprocating pump piston having direct contact with said medium during generation of compression and rarefaction phases of said energy waves, means for reciprocating said pump whereby to generate an energy transmitting wave in said medium, pressure means for loading said pump cylinder to augment the waves including a pressure chamber communicating with the latter rearwardly of the piston, and means for maintaining pressure in said pressure chamber.

8. The combination of claim 7 wherein said piston has a one-way valve in its head, means for introducing fluid into said piston rearwardly of said valve and for discharging fluid through said valve when a relative rarefaction exists in the fluid medium adjacent the valve.

9. The combination of claim 7 wherein said piston has a one-way valve in its head, means for introducing fluid into said piston rearwardly of said valve and for discharging fluid through said valve when a relative rarefaction exists in the fluid medium adjacent the valve, said pressure chamber communicating with said means for introducing fluid.

10. The combination of claim 7 wherein said pressure chamber has an expansible bag therein for imposing pressure upon the liquid medium within said pressure chamber, said pressure maintaining means including a source of fluid under pressure having communication with the interior of said expansible bag.