Abstract:
The present invention comprises a fluid pump motor unit and a controller unit which controls the output of the pump/motor irrespective of the speed of the power source driving the pump/motor unit. 
     The pump/motor unit comprises a cylindrical housing within which there is arranged at least one rectangular expansible cylinder assembly mounted on a crankshaft in a radial pattern, the cylindrical assembly being pivotally mounted within the housing for movement about trunnions, the rectangularly adapted piston assembly within said housing being journaled on a crankshaft which crankshaft with respect to the centerline of the cylindrical housing has a rotation parallel to, but spaced from, the centerline of the housing. The pivotal oscillation of each cylinder assembly alternately opens a port for the inflow of a fluid and subsequently closes that port while simultaneously opening another port for the outward flow of the fluid under compression as the piston moves toward the top of the chambers. Novel means are provided to seal the side walls of the cylinder with the end plates of the housing and additional novel means are provided to seal the piston and cylinder during the movement of the piston therein. The invention also provides for intake and outward flow of the fluid within the housing through the end plates by means of conduits contained therein. 
     The controller unit encompassed within the present invention comprises a shaft keyed to the crankshaft of the pump/motor unit, a pair of rotatable sleeves, one within the other, the latter keyed to the shaft keyed to the crankshaft, the sleeves being counter rotatable with reference to each other, each having a helical groove therein substantially disposed 180 degrees along the circumference of each sleeve relative to each other and intersecting each other, the two grooves thus providing a camming surface in which a pin inserted within the two grooves can be moved by another pin operating in an arcuately inclined groove in another sleeve on a control rod which is rotatable between positions which place the crankshaft rotatable between positions which place the crankshaft of the pump/motor unit in aspects ranging from full forward position to neutral.

Description:
FIELD OF INVENTION 
     The present invention lies in the field of mechanisms which through compressive forces provide for the movement of fluids to create motive power for the propulsion of fluids and the employment of such fluids to create propulsive factors. More specifically, the present invention relates to fluid pumps which can be equally employed as fluid driven motors and more particularly, to such pumps/motors in which the compression chambers oscillate within a housing. 
     Background of the Invention and Prior Art 
     Devices which utilize compression chambers to move fluids therethrough have long been known and employed. These conventionally known devices can be generally grouped into these two categories. The first is having true and predetermined compression chambers with articulated pistons moving within the chambers in a staggered sequence to draw in fluids and exhaust these fluids through a complex arrangement of valve assemblies, compressing ports, valves, valve actuating mechanisms, valve actuating mechanism control devices and equally complex arrangements relating to the operation of the compressive chambers themselves. The other category utilizes a series of conventional compression chambers and very complex system of valving cooperating with these compression chambers to move fluid through the mechanisms to accomplish the same mechanical result. 
     Not unsurprisingly, these known devices have followed the structure of conventional compression mechanisms unchanged from the time of the first practical utilization of the steam engine. These devices utilize a housing having fixed cylinderical chambers within which articulated pistons mounted on angular crankshafts are moved up and down. The intake and exhaust systems for fluids to be propelled by the compressive forces developed by the interaction of such chambers and piston are complex mechanisms within themselves, relying upon cams, springs and similar acting means to be opened for the introduction and exhausting of fluids to which compressive forces developed by the interaction of the pistons within the chambers. 
     There have been limited known developments to simplify not only the compression chambers but also to simplify the mechanisms for the intake and exhaust of fluids through such compression chambers. There have been a few innovators who chose to reverse the conventional compression devices by employing oscillating compression chambers within which conventional articulating pistons moved up and down. 
     Summary of the Present Invention 
     The present invention markedly differs from the known art in several aspects. First of all, the invention comprises a fluid pump/motor unit and a controller unit which controls the output of the pump/motor irrespective of the speed of the power source driving the pump/motor unit. For example, the pump/motor unit can be put into a neutral position by the controller unit and the power source turned on in the instance of electric motor drive or started up in the instance of an internal combustion engine. The speed of the power source can be set as desired, then the controller unit may be actuated between neutral and full forward output of the pump/motor unit. The speed of the power source may be increased or decreased and the volume of output can be maintained by moving the controller toward neutral or toward the full forward position respectively. The output from the pump/motor unit may be stopped simply by putting the controller in neutral and without changing the speed of the controller. 
     Secondly, the present invention includes a unit which, when separated from the controller unit, can be used as a fluid pump or as a motor actuated by a fluid pressurized source. The latter can be the pump unit itself. There is no requirement that the pump unit be directly connected to the motor aspect unit, yet such an arrangement is encompassed within the present invention. In such a combination, the controller unit is interposed between the pump aspect unit and the motor aspect unit. In such a combination, it is the control of the flow of fluid between the two identical units which establishes the driving unit. It is also within the scope of the present invention to separate the pump aspect unit from the motor aspect unit, employ the controller unit with the pump aspect unit and interconnect the pump aspect unit with the motor aspect unit by means of conduits so that the motor unit can be positioned in direct connection with the elements to be driven by the motor aspect unit. As an example, in a boat, the pump and controller assembly disclosed herein can be connected to the boat&#39;s engine. Conduits may be laid to the motor aspect which is directly connected to the shaft of a propellor assembly. 
     In the present invention, the pump/motor unit comprises cylindrical housing within which there is arranged at least one rectangular expansible cylinder assembly mounted on a crankshaft in a radial pattern, the cylindrical assembly being pivotally mounted within the housing for movement about trunnions, the rectangularly adapted piston assembly within said housing being journaled on a crankshaft which crankshaft with respect to the center line of the cylindrical housing has a rotation parallel to but spaced from the center line of the housing. The pivotal oscillation of each cylinder assembly alternately opens a port for the inflow of a fluid and subsequently closes that port while simultaneously opening another port for the outward flow of the fluid under compression as the piston moves toward the top of the chambers. Novel means are provided to seal the side walls of the cylinder with the end plates of the housing and additional novel means are provided to seal the piston and cylinder during the movement of the piston therein. The invention also provides for intake and outward flow of the fluid within the housing through the end plates by means of conduits contained therein. Lubrication of the moving parts is provided by non-fluid means as well as by the flowing of a liquid lubrication under pressure in conduits within the end portions of the moving parts of the invention. In certain applications or usages of the pump/motor aspect, frictionally engaging surfaces may be coated with any of the presently, or to be developed in the future, well known lubricating compositions, such as TEFLON. 
     The controller unit encompassed within the present invention comprises a shaft keyed to the crankshaft of the pump/motor unit, a pair of rotatable sleeves, one within the other, the latter keyed to the shaft keyed to the crankshaft, the sleeves being counter rotatable with reference to each other, each having a helical groove therein substantially disposed 180° relative to each other, the two grooves thus providing an intersecting camming surface in which a pin inserted within the two grooves can be moved by another pin operating in an arcuately inclined groove in another sleeve on a control rod which is rotatable between positions which place the crankshaft rotatable between positions which place the crankshaft of the pump/motor unit in aspects ranging from full forward position to neutral. 
     The present invention also encompasses novel sealing means for the pivotal cylinders and novel sealing means for the rectangular piston assembly within each cylinder. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     The present invention in its various embodiments and uses is graphically presented in the drawings which are illustrative and do not limit the invention is size or components. The drawings present the invention in varying scales which are dependent upon the presentation of the embodiments and uses of the invention according to the detail deemed necessary for clarity in understanding the structure and the operation of the invention. 
     For different embodiments of the invention, identical views are not presented in all instances. Since most of the components are identical and vary only by the number required, it is believed that those of skill in the art will understand how they would be arranged in operational relationships if they are not shown in the drawing figures. 
     Similarly, since many components are identical, the same reference numerals are employed for the different embodiments. 
     FIG. I is a perspective view of the fluid pump/motor and controller assembled, a portion of the housing for the controller being broken away to show the fluid ports and relationship of the controller to the other unit. 
     FIG. Ii is an elevation view of the interior surface of the output side end plate of the pump/motor unit. 
     FIG. III is an elevation view of the underside of the adaptor plate which is fitted into each end plate of the pump/motor unit. 
     FIG. IV is an elevation view of the interior surface of either end plate of the pump/motor unit ready for assembly of the unit when employed with the 4-cylinder embodiment of the present invention. 
     FIG. V is an end view of the pump/motor unit with the output side end plate removed showing the arrangement of the 4-cylinder embodiment. 
     FIG. VI is an end view of the pump/motor unit with the output side end plate removed showing the 3-cylinder embodiment of the invention. 
     FIG. VII is an end view of the pump/motor unit with the output side end plate removed showing the 2-cylinder embodiment of the invention. 
     FIG. VIII is a cross-section of FIG. VI along the plane VIII--VIII in that figure and includes an elevation of the controller unit in partial section. 
     FIG. IX is an elevation end view in partial section of the number 1 piston of the present invention. 
     FIG. X is an elevation side view in partial section of the number 1 piston of the present invention. 
     FIG. XI is a side view and an end view, both in elevation, of the number 2 piston of the present invention. 
     FIG. XII is a side view and an end view, both in elevation and both in partial section, of the number 3 piston of the present invention. 
     FIG. XIII is a side view and an end view, both in elevation, of the number 4 piston of the present invention. 
     FIGS. XIV a, b, c and d are a top view in perspective of any of the 4 piston types along the plane XIV--XIV of FIG. IX. 
     FIG. XIBb is an enlarged perspective of the corner assembly of the piston seal shown in FIG. XIVa. 
     FIG. XIVc is a top plan view of the piston seal spring shown in FIG. XIVa. 
     FIG. XIVd is an elevation view of the open side of the spring shown in FIG. XIVc. 
     FIG. XV is a partial side elevation view of one of the piston seal assemblies shown in FIG. XIVa. 
     FIG. XVI is a sectional view of the crankshaft of the pump/motor unit and the control shaft of the controller unit taken along the axial center line of the two shafts. 
     FIGS. XVII, XVIII and XIX are cross-sectional views of the shafts in FIG. XVI along the planes XVII, XVIII and XIX in the Figure. 
     FIG. XX is a perspective view of the controller cam sleeves shown in FIG. XVI. 
     FIGS. XXIa, XXIb, XXIc and XXIcr schematic showings of the relative axial position of the cylinder, piston and crankshaft and the relative axial positions of the cam shaft and controller cam at the two maximum operating positions and the intermediate operating position of the controller unit. 
     FIG. XXII is a perspective of the cylinder of the present invention. 
     FIG. XXIII is a cross-sectional view of the controller unit taken along plane XXIII--XXIII in FIG. VIII. 
     FIG. XXIV is a side elevation of the controller unit in partial section. 
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     The following description of the structure of the invention in its various embodiments with reference to the drawings will aid in understanding the subsequently-to-be-described functioning of the various components of the invention. 
     In FIG. I, A designates the assembled unit of the invention whether the unit is to be employed as a pump or a motor. B designates the pump/motor unit, and C designates the controller unit. The housing for the pump/motor unit comprises a cylindrical sleeve 1 which is fitted between end plates 3 and 3a (FIG. XVIII), being the power side and plate and the output side end plate respectively. A plurality of housing bolts 3b pass through end plate 3a and are secured in end plate 3. At least one inlet port 3c and at least one outlet port 3d are formed in at least one end plate. Depending upon the use to which the pump/motor unit may be put, one or more inlet and outlet ports may be formed in each end plate. Crankshaft 14 (FIG. XVIII) extends through the power side end plate 3. When the unit is to be used as a pump, the crankshaft 14 is connected to a power source by any of the various well known means. In similar manner, when the unit is to be employed as a motor, the crank shaft 14 is coupled to the device to be driven. 
     The housing for the controller unit is similar to that of the pump/motor unit. The cylindrical sleeve 1 continues from the pump/motor unit to enshroud the controller unit. This unit also has two end plates, 30 being the end plate abutting the output side end plate 3a of the pump/motor unit and 30a being the outside end plate of the controller unit. The controller unit is connected to the pump unit by housing bolts 31b which are secured in the outer surface of end plate 3a of the pump/motor unit. Control rod assembly 54 of the controller unit has journals 54a in controller end plates 30 and 30a FIG. XXIV. Control rod cam assembly 55 actuates the controller cams, of which only outer controller cam sleeve 51 is visible in FIG. I as will be explained subsequently. 
     FIG. II, the output end plate 3a has on its interior surface a recess 2a for the adaptor plate 2 seen in FIG. III. The power side end plate 3 has an identical recess on its interior surface. Aperture 14d receives the pump/motor crankshaft assembly seen in FIGS. V-VII and XVI. The apertures 10 for the housing bolts 3b have a seal 11 in end plate 3a. In end plate 3 the housing bolts are received in tapped holes 10b and require no seals. The inlet and outlet ports 3c and 3d respectively in end plate 3a match up with circular conduits on the underside of adaptor plate 2 as will be subsequently seen. A plurality of L-shaped grooves 21 are formed in the inner surface of end plates 3a to provide for the influx of fluid to be pressurized in the instance of use of the pump/motor unit as a pump or of pressurized fluid when the unit is being employed as a motor. Similarly, an equal plurality of opposing L-shaped grooves 22 is formed in the surface of end plate 3a to provide an outlet for the fluid pressurized when the unit is employed as a pump and an outlet for the de-pressurized or reduced pressurized fluid received when the unit is employed as a motor. The structural and operational relationships of grooves 21 and 22 with the cylinders and pistons and the adaptor plate will be explained subsequently. Port 12a receives lubricating fluid for the crankshaft, cylinder and piston assemblies as will be explained. 
     As seen in FIG. III, the underside of the adaptor plate 2 contains a plurality of concentric channels formed in the surface of the underside about the aperture 14d for the crankshaft. Channel 12e receives the lubricating fluid from port 12 (FIG. II). The lubricating fluid from this channel is conducted to the various bearings through port 24 as will be explained. The lubricating fluid is returned through port 25a into channel 25. The incoming fluid which is to be pressurized within the pump or is under pressure when the unit is a motor is received from inlet port 3c in the end plate 3a into channel 28. The outgoing fluid from the pump/motor unit flows around channel 27 to outlet port 3d in end plate 3a. The adaptor plate for end plate 3 may contain the same number of concentric channels and lubricating ports or the channels 27 and 28 may be omitted since the fluid inlet and outlet ports are not normally provided on end plate 3. In some usages, fluid inlet and outlet ports may be necessary on both end plates. In the instance when hydraulic fluid is employed, a separate lubricating oil will not be required. Instead, a small quantity of the pressurized hydraulic fluid will be passed into the channel 25 for circulation for lubrication of the various bearings and seals and returned into channel 12 to be passed through the lubricating route provided and explained subsequently. This will require making a small cut in the wall between channels 28 and 25. A peripheral channel 30 is formed in the edge of adaptor plate 2 to receive any lubricating fluid which may pass by the cylinder and piston seal assemblies. It is drained from channel 30 by port 26 (FIGS. IV and V) and will collect in the bottom of the housing from whence it may be drained by plug 1a FIG. VIII. 
     In FIG. IV, the novel elements shown in FIGS. II and III have been placed in operational relationships and other novel elements of the invention have been added. The upper side of the adapter plate 2 has not been shown separately but since it contains but a few openings, it can be seen with sufficient clarity in FIG. IV. 
     When the adapter plate is inserted in operational relationship to the end plate 3a, it will be seen that the L-shaped slots 21 and 22 in the interior surface of end plate 3a having matching extensions 21a and 22a respectively, in the surface of adaptor plate 2. The extensions 21a extend just beyond the inner edge of channel 28 on the underside of plate 2a to provide incoming flow of the fluid from channel 28 into slot 21 and into the chamber as will be explained. Similarly, extension 22a extends just beyond the inner edge of channel 27 on the underside of plate 2 to provide for outgoing flow of fluid from the chamber via slot 22. Since channel 27 is farther from the outer edge of plate 2, extension 22a is longer than extension 21a. The number of extensions 21a and 22a will be determined by the number of cylinders in the unit which can range from 1 to 4, although the 3 and 4 cylinder arrangements will normally be used. 
     Since a four cylinder arrangement is the most complex, FIG. IV is employed to show the novel sealing ring assemblies 7, each of which assemblies comprises on resilient expansible sealing ring 7a which is inserted in a matching recess 7b in both the surface of adaptor plate 2 and the surface of end plate 3a. The sealing ring 7a is an inverted U-shape with one leg angled slightly. The interior of the ring forms a channel which is closed by another ring 7c (FIG. VIII). When end plate 3a is laying with the shown surface upward, the ring protrudes slightly above the surface so that when the end plate is assembled, the cylinder of the invention will press the sealing ring back into the recess sufficiently to forming a sealing fit between the end wall of the cylinder and the surface of the end plate/adaptor plate. The outer two-thirds of the sealing ring is provided with a plurality of spaced apertures 23 for the flow of lubrication fluid into and out of the sealing ring recess for lubricating the end walls of the cylinders as well as the matching surface of the end plate/adaptor plate. In a similar manner the inner third of each sealing ring 7a is provided with a plurality of spaced apertures 23a which not only insure lubrication of this portion of the sealing ring 7a but also provide lubricating oil for the novel piston assemblies of the present invention as will be explained subsequently. FIG. IV for the end plate of the 4-cylinder embodiment shows that the sealing rings, and therefore the cylinders are radially positioned about the crankshaft at a 90° spacing. For the 3-cylinder embodiment the sealing rings would be positioned at 120° spacings. In the instance of a 2-cylinder embodiment, the spacing of the sealing ring assemblies would be 180° about the center line of the crankshaft. The use of only 1 cylinder is within the scope of the present invention and hence the sealing ring assembly for such an embodiment would be positioned on a radial of the end plate. 
     Two of the most novel aspects of the present invention are the cylinder assemblies and the piston assemblies associated therewith to provide the pivotable expansible compression chambers. The individual components, cylinder assembly and piston assembly, are shown in FIGS. IX-XIV and XXII. Their working relationship can be seen in FIGS. V-VIII. 
     FIGS. V, VI and VII show three embodiments of the invention and differ primarily in number of cylinder and piston assemblies. 
     Since only the number of components is the variant, the same reference numerals are employed in FIGS. V-VII. Again, since the 4-cylinder embodiment is the most complex, it will be the embodiment, as shown in FIG. V, upon which the detailed description is based. Generally, only one cylinder assembly and one piston assembly will be described. However, it is to be understood that such description applies to each cylinder assembly and piston assembly unless indicated otherwise. 
     Within the housing of the embodiment shown in FIG. V there is to be seen a compression chamber assembly D, one of four, but may be one of one, two or three. This assembly comprises a cylinder assembly 4, a piston assembly 6 and a crankshaft 14 upon which the piston assembly 6 is rotatably journaled. 
     The cylinder assembly 4 comprises an inverted, U-shaped cross section cylinder 4a with a trunnion 5 on each end. As is seen in FIG. XXII, the cylinder 4a is of rectangular form with a rectangular chamber 4b formed by the cylinder side walls 4c interiorly thereof. The trunnion 5 is integrally formed on each end wall 4d of the cylinder. As can be seen in FIG. VIII, each trunnion 5 is mounted in a trunnion recess 5a in each end plate. Between each trunnion 5 and its recess 5a are means 5b to provide friction-free movement of the trunnion within the recess. This means may be in the form of a bushing, a bearing or a self-lubricating material such as tetraflorochloroethylene or equivalent compositions. The friction elimination means, if a bushing or bearing, may be in the form of an insert which is fitted into the recess 5 or it may be fitted onto the trunnion 5. If a self lubricating material is used, the material may be an insert fitted into the recess 5 or fitted on the trunnion 5 or both. The choice of the friction-eliminating means 5b will be determined by the use of the unit and/or the composition of the fluid which will be passed through the unit. Each trunnion 5 has an axial slot 15 on the upper and lower surfaces and an annular ring 15a interconnecting these slots for lubricating oil received from apertures 23 in sealing ring 7a. 
     As seen in FIGS. V, VI, VII, IX-XIV, the piston assembly 6 shown has a block-like rectangular form comprising a piston head 6a and a piston rod 6b formed integrally with the piston head. The block-like form simplifies manufacture since it may be made from a rolled or drawn rod of proper cross-section. The piston head has vertical side walls 6c and end walls 6d. In the piston head shown in the foregoing Figures just mentioned, the vertical side and end walls 6c and 6d have a peripheral recess 6e parallel to and spaced vertically downwardly from the piston head surface 6f. This recess 6e holds the novel pressure and lubricating sealing ring assembly 8 of the present invention. As seen in FIG. XIV and XV with reference to the FIG. VI, this novel ring assembly comprises two sets of two pairs of identical, rectangularly formed, notched plates 8a and 8b. Each pair is pivotally joined at their respective intersection by a connecting pin 8c. Each pair also has on its inner face 8d a vertical slot 8e which receives an end of the piston sealing assembly spring 8f which, as can be seen in FIGS. XIV and XV is flat with curved ends to be fitted into slots 8e, the spring resting against the inner wall 6g of recess 6e. In this manner, the spring maintains a free spacing between the sealing plates and the inner wall 6g of recess 6c for flow of lubricating oil in the recess and out through apertures 19 in the piston sealing plates into the groove 18 on the outer side of the plate. 
     The piston head top surface 6f of the piston head is joined to the vertical end and side surfaces 6c and 6d by a chamfered surface 6h. The purpose of the chamfered edge is to allow the piston head to rise within the cylinder chamber to the fullest extent possible, including substantially full contact between the cylinder chamber upper surface and the piston head top surface. 
     As seen in FIGS. IX and X the piston rod 6b is substantially a rectangular block depending from the underside of the piston head and is made integral therewith with a rounded lower end 6j. The rod 6b has an aperture 6k to receive the crankshaft 14. The aperture 6e retains the piston rod crankshaft bushing 6m. The piston rod crankshaft bushing 6m may be of a roller bearing type well known in the art. To those skilled in the art, it will be apparent that a recess (not shown) may be formed on each side of the piston rod crankshaft aperture 61 for the insertion of well known ball bearing races. Alternatively, depending upon the use of the invention, bushings in the form of bearings, per se, may be omitted and an insert of a self-lubricating, friction free material such as tetraflurochloreythylchloride or other similar well known material having the same properties may be placed within the aperture 61 and a complimentary coating of the same material may be placed on the crankshaft. Within the scope of the invention, piston rod 6b has a lesser width along the axis of the crankshaft as shown in FIG. X, i.e., forming a T-shape. 
     The piston rod of the present invention is unique and novel in comparison with the present state of the art of piston rods in that there is no need to provide the portion of the piston rod which encircles the crankshaft with an upper and lower segment which must be bolted together. Additionally, there is no articulation between the cylinder and piston. 
     The pistons employed in the present invention differ from each other only in the structure of the piston rod in the various embodiments shown in FIGS. IX-XIII. The piston rods, however, have a common feature and that is, equal cross-sectional area. Thus, the number 2-4 pistons shown in FIGS. XI-XIII have two depending spaced piston rods 6b in order to be accommodated on the crankshaft 14 in a straddling fashion as can be seen in FIG. VIII. 
     In addition to the lubrication for the piston head previously provided, means are provided on the piston rods to lubricate the piston rod crankshaft bushing as well as conduct oil from the piston sealing recess 6c to the bearing; an aperture 16 is formed on each side of each piston rod 6b intersecting piston lubrication channel 20 and being connected by channel 17 passing along the face of the piston rod and becoming a bore 17&#39; as it passes through the piston head to piston seal recess 6e. 
     Another aspect of the novel piston of the present invention which is common to all forms of the piston is the arcuate under surface 6i of each piston head. This arcuate surface accommodates the arcuate end 6j of each other piston rod. This arcuate surface is formed on each side of each piston rod with the exception of the piston rod on the number 4 piston. On this latter piston, the arcuate surface is formed only between the inner surfaces of each piston rod, the outer surface of each piston rod of a number 4 piston being flush with the piston head. 
     Referring now to FIG. VIII, and reading generally from left to right, a fitting plate E, indicated in phantom, may be provided to provide support between the pump/motor unit A and the power source (not shown) so that the weight of the unit A is not borne by the crankshaft 14a as end portion 14f is connected to the power shaft (not shown) by known devices such as keying (not shown). In lieu of fitting plate E, a footed plate (not shown) may be used when the unit A is to be supported on the mounting for the power source. In either instance, it is contemplated that such supporting plate would be bolted to the external face of end plate 3 in a conventional manner. Other forms of support for unit A will occur to those of skill in the art. 
     In assembly of unit A, end plate 3 is placed horizontal with its interior surface upward. The trunnion seals 5a are then inserted into the trunnion seal recesses 5b in end plate 3. The adaptor plate 2 is then inserted into the adaptor plate recess 2a in end plate 3. The cylinder sealing ring assemblies 7a and 7c are then inserted into the cylinder sealing recesses 7b, one for each cylinder in the embodiment employed in the adaptor plate 2 inserted in end plate 3. Cylindrical sleeve seal 9 is inserted in sleeve seal recess 9a in end plate 3. 
     Each piston assembly is put together by placing a piston sealing spring 8f in the recesses 8e in each of a pair of piston sealing rings 8a and 8b pivotally pinned together by pin 8c (FIG. XIVa, b, c) and the placing of each of the pairs in the piston sealing ring recess 6e in each piston. The crankshaft bearings 13 are inserted into the crankshaft bearing recesses 61 in each piston rod 6b. 
     Each compression chamber assembly is then assembled by inserting each piston assembly into the inner chamber 4b of the cylinder 4a so that the piston sealing ring pairs 8b which are biased by piston sealing ring spring 8f and are in contact with the inner walls 4c of the chamber 4b, thus leaving the piston sealing ring pairs 8a on each open end of each cylinder. 
     The assembly of the crankshaft is then begun. The crankshaft sleeve 14a (FIGS. XVI-XIX) is placed on the end of the crankshaft which is to be inserted in end plate 3. The crankshaft/sleeve bearing 13 is inserted in crankshaft bearing recess 14b in end plate 3. It is to be noted (FIGS. XVI-XIX) that the centerline of the crankshaft is parallel but spaced from the centerline of the sleeve. 
     Each compression chamber assembly in the embodiment to be employed is then placed in proper relationship with the other compression assemblies so that the piston rod 6b of each assembly is in proper relationship to the other piston rods whereby a cylindrical form of the length of the cylinder is formed. As seen in FIG. VIII, piston rod 6b No. 1 is straddled by piston rod 6b No. 2, which in turn is straddled by piston rod 6b No. 3. 
     With the compression chamber assemblies thus properly aligned, the end of the crankshaft 14 opposite the end bearing the crankshaft sleeve 14a is then inserted through the crankshaft bearings 13 which are mounted in the crankshaft bearing recesses 6e in each piston rod until the piston rods are flush with surface 14d of the crankshaft 14. 
     With end plate 3 lying horizontally with the cylinder sealing ring assemblies upward, the crankshaft carrying the compression chamber assemblies is then slid into the crankshaft bearing 13 in end plate 3. The assemblies are pivotally moved around the crankshaft until the one trunnion 5 of each assembly can be fitted into its proper recess and the crankshaft on compression chamber assemblies are moved into seating engagement with the surface of end plate 3 and adaptor plate 2 inserted therein. Cylindrical sleeve 1 is then placed into position over end plate 3 with end plate recess 1a abutting end plate 3. 
     Crankshaft sleeve 14a  is placed over stub shaft 14f&#39; and crankshaft bearing 13a is inserted into end plate 3a. End plate 3a is then assembled in the same manner as described above with reference to end plate 3 and the portion of the pump/motor unit A previously assembled is inserted into end plate 3a in the manner described for end plate 3. At this juncture, the pump/motor unit is assembled by insertion of the pump/motor unit A housing bolts 3b. 
     If the thus assembled unit A is to be employed as a pump or motor without the controller unit, it will be apparent that end plate 3a will have a recess 14b&#39; to receive the crankshaft bearing 13 and the end portion 14f&#39; of the crankshaft which will not be accessible from the outside of unit A. This is indicated in FIG. VIII by dotted line. 
     Controller B is assembled in the following general manner, (FIGS. XVI-XIX, XX, XXIII and XXIV) . Controller cam shaft keys 14c are inserted into controller cam shaft key recesses 50a in the end of controller cam shaft 50 which is to be joined to crankshaft 14. Inner controller cam key 50a is inserted into inner cam key recess 50b in controller cam shaft 50. Inner controller cam 52 is then fitted onto cam shaft 50 by sliding key 50a into key recess 52a milled into inner cam 52. As best seen in FIG. XVI, note that the center line 63 of shaft 50 is coaxial with center line 61 of the power source shaft 14f and that center line 64 of cam 52 is coaxial with center line 61 of crankshaft sleeve 14a. Outer controller cam 51 is then slid over inner control cam 52 so that the outer cam control slot 51a is perfectly matched in crossing pattern with inner cam control groove 52b , and slot 51a&#39; is matched in cross pattern with groove 52b&#39;. 
     Controller cam shaft 50 is then assembled by sliding controller cam shaft keys along recesses 14e in crankshaft 14; controller end plate 30 is then fitted over the controller cam shaft as assembled by sliding the cam shaft aperture 30a over the assembled shaft until the end plate 30 is in contact with end plate 3a. Control rod assembly journal 45a is inserted into journal recess 30b in end plate 30. 
     Control rod assembly 54 comprises a control shaft 54b, one end of which is to be fitted into journals 54a in end plate 30, the opposite end having a perpendicularly extending lever 54c which is employed to turn the control shaft as will be explained subsequently. 
     The lever 54c is secured on control shaft 54b and is mounted on upper control cam assembly 55. The assembly comprises a camming unit 55a having a camming groove 55b, The camming unit 55a can be secured to the shaft 54b by a key 55c, a set screw or similar devices, or the camming unit may be formed by milling a piece of stock to produce the shaft 54b and the camming unit 55a as an integral part thereof. The camming unit 55a further includes an upper cam roller 55d positioned within camming groove 55b. The roller 55d is rotatably mounted on shaft 55c which is fixedly positioned in cam assembly housing 55e. Cam assembly housing 55e has a cylindrical form as can be seen in FIG. XXIV with due reference to FIG. VIII. Camming unit 55a also includes a stabilizer plate 55f which extends parallel to control shaft 54b, is securable to the interior surfaces of controller end plates 30 and 30a and carries a slot 55g which is fitted around and precludes the rotational movement of cam assembly housing 55e during operation of the pump/motor unit. 
     The cam assembly housing 55e surrounds a controller cam housing 55h which has an aperture 55s to accept outer and inner controller cams 51 and 52 and carries the lower roller cams 55i and 55j which are fitted into the cam slot 51a and 51a&#39; and cam groove 52b and 52b&#39; respectively in outer controller cam 51 and inner controller cam 52 respectively. The roller cams 55i and 55j are rotatably mounted on lower roller cam shafts 55k which are mounted in bores 55l in the housing 55h. Each upper surface of roller cam shaft 55k has a keyway 55m which matches a keyway 55n in the upper surface of each bore 55l. A key 55p is fitted into keyways 55m and 55n to secure the roller cam shaft 55k within housing 55h and also to prevent rotation of the roller cam shaft. 
     The cam assembly housing 55e has closed back surface 55t with a bore to fit over the controller cams. The housing 55h is fitted over the controller cams into contact with a first roller bearing assembly 55r mounted on the inner surface of housing back 55t. A second roller bearing assembly 55u in an assembly mounting plate 55u&#39; is inserted into a recess 55v in housing 55e and provides rotational support against uncontrolled lateral movement of housing 55h. Roller bearing assembly 55u is held in recess 55v by a split ring 55w insertable into a groove 55x in housing 55e. 
     FUNCTIONING OF CONTROLLER UNIT 
     When the elements of the controller unit are in the positions shown in FIGS. VIII and XXIII and XXIV, the unit permits the pump/motor unit to function with full output of pressurized fluid as will be described subsequently. 
     In the position of elements shown in FIGS. VIII and XXIII, the lever 54c is in an upright position. The upper control cam assembly 55 is stationary. Within the cam assembly housing 55e, the housing 55h will rotate since the inner and outer controller cams 51 and 52 are rotating with controller cam shaft 50 which is locked to crankshaft 14, and the roller cams 55i and 55j are held in their positions in cam slot 51a and cam groove 52b by the fact that cam shaft 55k is secured in housing 55h which is rotating about shaft 50 because key 55p locks housing 55h and cam shaft 55k against independent movement. 
     The rotation of control lever 54c on shaft 54 in a counter clockwise direction produces a rotational movement of camming unit 55a. As camming unit 55a is rotated by shaft 54, camming groove 55b, by its rotation, causes upper camming roller 55d to move in camming groove 55b towards the pump/motor unit. As camming roller 55d moves, its connection to cam assembly housing 55e causes this housing to move equally toward the pump/motor unit. The movement of housing 55e, even though this housing is rotating about shaft 50, moves lower camming rollers 55i along camming slots 51a and 51a&#39; in outer controller cam 51 thereby rotating outer controller cam 51 in a clockwise direction while simultaneously moving lower camming rollers 55j along camming slots 52b and 52b&#39; in inner controller cam 52 thereby causing inner controller cam 52 to rotate in a counter clockwise direction. As inner controller cam 52 rotates in the counter clockwise direction, such rotation causes controller cam shaft 50 to similarly rotate in a clockwise direction. The counterclockwise rotation of cam shaft 50, which is keyed to the crankshaft 14 of the pump/motor unit, rotates the crankshaft sleeves 14a and 14a&#39; which are secured to crankshaft 14. This rotation of crankshaft sleeve 14a and 14a&#39; progressively moves the path circumscribed by the axis of rotation of crankshaft 14 above the power source shaft stub 14f from a position of parallel to, but spaced from, the centerline of the axis of rotation of the shaft of the power source to a position coaxial with the axis of rotation of the shaft of the power source as seen in FIGS. XXIa-XXIc. In this position of coaxiality, the pistons in all chamber assemblies are placed in a neutral position; i.e., the pistons will not move upwardly or downwardly as the shaft upon which they are mounted continues to rotate. In such a position the pistons cease to provide compression and decompression within the cylinders and the output from the pump/motor unit is substantially zero, thus placing the pump/motor unit in a neutral position or non-power producing status even though the power source continues to operate at the same speed or, in fact, at any speed. 
     To reverse the power output from the pump/motor unit, the control lever 54c is rotated clockwise to the position shown in FIG. VIII and the related elements are consequentially moved in patterns reverse to those just described and in summary, the path circumscribed by the crankshaft 14 axis of rotation is moved from coaxiality with the axis of rotation of the shaft of the power source to a position wherein the axis of rotation of the crankshaft 14 is again parallel to, but spaced from, the axis of rotation of the shaft of the power source. 
     Within the controller unit, the only truly continuously moving part is the controller cam housing 55h. Since this housing is not in frictional engagement with cam assembly housing 55e there is no problem of lubrication to prevent wear between the two housings. Nonetheless, all surfaces of the controller unit have a coating of any friction-free material, such as tetrachlorofluorethylene (TEFLON) or any similar material having the same friction-free properties. 
     In the present invention, one of the most important aspects to be understood is the crankshaft. As can be seen in FIG. VIII and FIGS. XVI-XIX from the power source shafts 14f and 14f&#39;, The crankshaft has a single offset portion 14 to which the piston rods are journaled. Referring to FIGS. XVI-XIX and XXIa-XXIc, the centerline of this offset portion is indicated by numeral 60. This centerline 60 is offset from the centerline 61 of the power source shaft stub 14f and center line 63 of shaft 50 is one-half the distance, or throw, the pistons are moved relative to the cylinders in the course of their movement as the crankshaft rotates, as will be readily recognized by those of skill in this art. 
     It has been previously described that the crankshaft 14 is mounted in sleeves 14a and 14a&#39; which are eccentrically positioned with reference to the crankshaft 14 and as can be seen in FIG. VIII and FIGS. XIV-XIX. In FIG. XVI and FIGS. XXIa-XXIc it will be seen that the centerlines 62 of the sleeves and centerline 64 of cam 52r spaced from the centerline of the power shaft stub portion 14f and 14f&#39; of the crankshaft and shaft 50 the same distance as the centerline 60 of the crankshaft portion on which the pistons are journaled but diametrally positioned relative thereto. Thus, the crankshaft sleeve centerline 62 and the piston bearing crankshaft portion centerline 60 rotate about centerline 61 in the same path but spaced 180° from each other. Similarly, cam center line 64 rotates about center line 63 which is coaxial with center line 61 but at the same distance therefrom as center line 62. This relationship is constant and fixed when the unit A is employed as a pump or a motor to produce optimum output of pressurized fluid as a pump or optimum output of rotational force as a motor. However, when the cam 52 is rotated by the lateral movement of the upper control cam housing assembly 55, this rotation is imparted to shaft 50 which in turn causes the crankshaft 14 to rotate the sleeves 14a and 14a&#39; as described above in the functioning of the controller unit to change the output of the pump. 
     Functioning of the Pump/Water Unit 
     During the rotation of the crankshaft in its normal pressurizing or driving centerline position, the varying positions of the pistons within the cylinders and the pivotal attitudes of the various cylinders about their trunnions as a result of the rotation of the crankshaft is seen in FIGS. V-VII. Each piston on its downward stroke uncovers the inlet port 22 to draw fluid into its respective chamber by the negative pressure created by the downward movement of the piston. The piston end walls in conjunction with the cylinder end walls act as inlet valves. As each piston completes its downward movement, the inlet port is covered by the cylinder end wall as the cylinder is rotated about its trunnion. The outlet port for each chamber assembly is automatically closed by the opposite cylinder end wall due to the position of the cylinder during the downward movement of its respective piston. 
     As the rotation of the crankshaft continues, each piston having completed its downward or negative-pressure producing movement, begins to move upwardly within its respective cylinder. At the beginning of this movement upwardly, both inlet and outlet ports 21 and 22 are covered by the end walls of the cylinder and the fluid within the chamber is placed under increasing pressurization. Just as the optimum pressure is being attained, in the vicinity of 10,000 psi, the relative movement of the piston and its cylinder pivots the cylinder to begin to move the opposite side of the end wall sufficiently to uncover the upper portion of the outlet port 22. As the piston continues to rise in its respective cylinder, the pivotal movement of the cylinder continues to uncover the remainder of the associated outlet port and when the piston has reached the upper limit of is movement and its upper surface is substantially in contact with the upper surface of the cylinder chamber, all fluid has been exhausted from the chamber and the cycle is repeated. 
     The end walls of each cylinder are in constant contact with the cylinder sealing assemblies in the end walls of the pump/motor unit during the pivotal to-and-fro movement of the respective cylinder. The pistons also contact the cylinder sealing assemblies at the apex of their travel. Since the piston sealing ring assemblies have almost a vertical knife edge at each corner of the piston sealing ring assemblies, the upper and lower ends of such knife edges is slightly chamfered as shown in FIG. XIV. This chamfer acts as a cam when the piston sealing assembly contacts the cylinder sealing assembly and depresses the leading edge of the cylinder sealing assembly as the piston sealing assembly continues to ride over the cylinder sealing assembly, thereby preventing cutting of the surface of the cylinder sealing assembly by the piston sealing assembly knife edges. 
     The piston sealing ring assemblies are novel in concept of providing sealing for rectangular or non-circular pistons and also in their structure. As seen in FIGS. XIVa-XIVd, each assembly comprises a plurality of pairs of flat plates which overlap each other at each corner of the piston and also overlap each other along the sides and ends of the pistons. Each pair is pivotally pinned to each other at the corner intersections. Each plate of each pair which is positioned in the side wall of the sealing assembly recess in each piston has a vertical groove into which one end of a sealing assembly spring is fitted, the intermediate portion of the spring between the ends resting against the back wall of the sealing assembly recess. When the sealing ring assembly is fitted into the recess prior to the insertion of the piston into its respective cylinder, the resilience of the spring causes those elements with which it has contact to protrude slightly beyond the side walls of the piston. Since the pairs are joined at the corners by the pins, those sealing rings on the ends of the piston, in contrast to the plates in the side walls, will be drawn inwardly with reference to the recess. When the thus assembled piston is inserted into the chamber of the cylinder, the plates on the side walls which were slightly extended beyond the side surfaces of the piston head will be forced back into a position which is paralled with the side walls. Because of the pivotal connection at the corners, the plates which are positioned on the end walls of the recess will be brought out into a sealing position with the end plates of the housing. The spring thus positions the plates with which it is directly in contact into sealing engagement with the side walls of the cylinder. In this instance, the spring exercises a radial movement of the plates to insure that the piston is in a sealed, or anti-pressure release, relationship with the cylinder. At the same time, the spring exerts a longitudinal force, which is translated through the pinning of the plates at the corners to cause the plates on the end walls of the piston to establish sealing contact with the end plates of the unit through the cylinder sealing ring assemblies. 
     The inventive aspects of the present invention have been set forth in the specification and illustrative drawings encompassed herein. Those modifications which may take form in the minds of those of skill in this particular art are encompassed in the claims of and for the invention which follow.