US3093079A

US3093079A - Variable volume fuel injection distributor pump

Info

Publication number: US3093079A
Authority: US
Inventors: George C Graham
Original assignee: Individual
Current assignee: Individual
Priority date: 1957-02-20
Filing date: 1957-02-20
Publication date: 1963-06-11
Anticipated expiration: 1980-06-11

Description

June 11, 1963 G. c. GRAHAM 3,093,079

VARIABLE VOLUME FUEL INJECTION DISTRIBUTOR PUMP Filed Feb. 20, 1957 7 Sheets-Sheet 1 INVENTOR 62-0 55 6. 524mm! June 11, 1963 G. c. GRAHAM 3,093,079

VARIABLE VOLUME FUEL INJECTION DISTRIBUTOR PUMP Filed Feb. 20, 1957 7 Sheets-Sheet 2 Tia-2A 95 96 4h 97 95 INVENTOR i-ueq: (66464401 IQZMMW ATTORNEY June 11, 1963 e. c. GRAHAM 3,093,079

VARIABLE VOLUME FUEL INJECTION DISTRIBUTOR PUMP Filed Feb. 20, 1957 7 Sheets-Sheet 3 June 11, 1963 G. c. GRAHAM 3,093,079

VARIABLE VOLUME FUEL INJECTION DISTRIBUTOR PUMP Filed Feb. 20, 1957 '7 Sheets-Sheet 4 RNEY June 11, 1963 e. c. GRAHAM 3,093,079

VARIABLE VOLUME FUEL INJECTION DISTRIBUTOR PUMP Filed Feb. 20, 1957 7 Sheets-Sheet 5 lNVENTOR 620?;5 dIP/MMM ATTORNEY G. C. GRAHAM June 11, 1963 VARIABLE VOLUME FUEL INJECTION DISTRIBUTOR PUMP 7 Sheets-Sheet 6 Filed Feb. 20, 1957 N M x W 5 l W R M. N\\ fl Q INVENTOR sam a C few/ M BY I . ATTO NEY June 11, 1963 G. c. GRAHAM 3,093,079

VARIABLE VOLUME FUEL INJECTION DISTRIBUTOR PUMP Filed Feb. 20, 1957 7 Sheets-Sheet 7 INVENTOR f (7 6164/44/14 United States Patent 3,093,079 VARIABLE VGLUME FUEL INJECTION DKSTRIBUTGR P George C. Graham, 76 Crest Road, Ridgewood, NJ. Filed Feb. 20, 1957, Ser. No. 641,314 13 Claims. (Cl. 103-2) This invention relates to liquid pumps and particularly to improved variable volume pumps adapted to distribute separate, independent injections of fuel to respective cylinders of internal combustion engines or the like.

The apparatus of the present invention is adapted to receive a flow of fuel from a supply tank or the like and to produce an output therefrom in the form of a plurality of successive, discrete portions of fuel, each portion being distributed to a corresponding cylinder of an internal combustion engine. This is accomplished by providing a plurality of pumping cylinders in a rotor which cooperates with one or more end plates having special porting arrangements that divide the output from each rotor cylinder into a plurality of discrete portions, each of which is distributed for injection into a cor-responding cylinder of the engine at controlled time intervals. The apparatus also includes a variable control mechanism which may be operated by suitable means to vary the amount of fuel distributed to each engine cylinder in order to provide for acceleration or deceleration of the engine at will.

The special cylinder and end plate porting arrangements herein also constitute the means for eliminating or at least substantially diminishing the effects of cavitation, and this is accomplished by discharging from each pump cylinder a portion of the fuel prior to the distribution of the remaining fuel to the respective engine cylinders. This preliminary discharge may also be returned to the fuel supply tank under pressure in conjunction with an injector in the tank to enhance the pumping action of the apparatus herein.

Still other objects and advantages of my invention will be apparent from the specification.

The features of novelty which I believe to be characteristic of my invention are set forth herein and will best be understood, both as to their fundamental principles and as to their particular embodiments, by reference to the specification and accompanying drawings, in which:

FIGURE 1 is a schematic diagram of a fuel system including one embodiment of the distributor fuel injection pump invention herein;

FIG. 2 is a schematic diagram of a fuel system including another embodiment of the present pump invention;

FIGS. 2A and 2B are schematic diagrams of fuel systems including further embodiments of the invention herein;

FIG. 3 is an end view of one embodiment of the pump, some parts being shown in section;

FIG. 4 is a greatly enlarged fragmentary cross section view, partly broken away and partly in elevation, taken on line 4-4 of FIG. 3;

FIG. 5 is a View of one of the end plates of the pump, taken on line 5-5 of FIG. 4;

FIG. 6 is a side view of the pump shown in FIGS. 3, 4 and 5, partly broken away and partly in section, some parts being omitted;

FIG. 7 is a side view of the rotor element of the pump shown in FIGS. 3 through 6, some parts being shown in phantom outline;

FIG. 8 is a partial section view of the rotor element of FIG. 7, taken on line 8-8 of FIG. 4;

FIG. 9 is an exploded view, in perspective, of the structural elements that operate the variable volume controls of the pump;

FIG. IO-is a perspective view of a modified form of piston that may be utilized in the pump;

FIG. 11 is a section view taken on line 1l'll of FIG. 10;

FIGS. 12 and 13 are greatly enlarged fragmentary diagrammatic views of the interior walls of the end plates of the pump indicating the cooperative action between the rotor cylinder ports and the end plate discharge ports for the engine cylinders only;

FIG. 14 is a schematic graph illustrating the action of each pump cylinder in relation to respective cylinders of the internal combustion engine which are supplied with fuel as exemplified by the embodiment shown in FIGS. 12 and 13;

FIG. 15 is a fragmentary side View of the end plate of another embodiment of the pump and showing a modified porting arrangement;

FIG. 16 is a section view taken on line 16-16 of FIG. 15;

FIG. 17 is a side view partly broken away of a modified embodiment of a pump rotor employing rectangular rather than round pistons;

FIG. 18 is. a section view, partly broken away, taken on line 18-4-8 of FIG. 17, and including additional elements of the pump assembly;

FIG. 19 is a fragmentary section view taken on line lit-19 of FIG. 17;

FIG. 20 is a partial section view, some parts omitted, of another view of a pump whose rotor is shown in FIG. 8 above, incorporating an oil lubricating system;

FIG. 21 is a view similar to FIG. 7 showing a further embodiment of the cylinder rotor of the present pump invention, some parts being omitted; and

FIGS. 22 through 24 show modified end plate porting arrangements for cooperation with the embodiment of FIG. 21, some parts being omitted.

Referring now to the drawings in detail, FIG. 1 shows a fuel distributing system including a fuel tank 21 containing a supply of fuel 22 suitable for consumption by an internal, combustion engine or the like. Connected at one end with the interior of fuel tank 21 is a fuel supply line 23 whose other end is connected to an arcuate suc-' 'tion or intake port of an end plate of one embodiment of the distributor pump to be described in greater detail hereinbelow. Said end plate is shown greatly enlarged relative to the other elements in the figure, and the arrow indicates the direction of rotation of a cylinder rotor relative thereto. Positioned at suitable points in fuel supply line 23 are a fuel supply pump 24 and a fuel filter 25 which perform their well known functions.

Connected to the other end of the intake Port of the distributor pump end plate is one end of a return line 26, the other end of which communicates with the interior of fuel tank 21. Positioned in return line 26 is a relief or pressure control valve 27 which serves to maintain the desired fuel pressure within the intake port of the end plate.

FIG. 2, which is similar to FIG. 1, shows another embodiment of the distributor pump end plate having a modified porting array which will be described in greater detail hereinbelow. A 'supplemnetal return or overflow line 28 is provided for causing a portion of discharged fuel to bypass relief valve 27 on its return to tank 21.

One embodiment of the distributing fuel injection pump of the present invention is shown in FIGS. 3 through 9. The pump, generally designated 31, comprises a pair of generally

circular end plates

32 and 33 which are spaced apart by a spacer ring 34.

End plates

32 and 33 and spacer ring 34 are secured together by a circular array of bolts 35, or the like, near the perimeter of said plates.

Plates

32 and 33 and spacer ring 34 form a'chamber 36 atented June 1-1, 1963 within which a circular disk-like rotor 37 rotates on its axis. The flat outer walls of rotor 37 are in sliding substantially liquid tight engagement with the respective interior walls of

end plates

32 and 33.

Threadably attached to the axial center of end plate 33 is a journal 41 containing a ball bearing 42, or the like, which supports rotatable drive shaft 43 which may be connected by suitable gearing, not shown, to an automotive internal combustion engine, not shown. The inner end of shaft 43 terminates in a square shaped stud 44 which engages a central square shaped aperture 45 (FIG. 7) in one side of rotor 37 whereby the latter is rotated on a stationary axis.

Rotor 37 has four radial cylinders A, B, C and D, of substantially circular cross-section, that are symmetrically arrayed in cruciform fashion (FIGS. 7 and 8). The outer ends of cylinders A, B, C and D are closed by liquid

tight screws

46, 47, 48 and 49, respectively (FIGS. 4, 8), or by other suitable means. The inner ends of cylinders A, B, C and D communicate with central aperture 51 in rotor 37, the diameter of said aperture being somewhat greater than that of coaxial aperture 45.

Positioned within each of cylinders A, B, C and D, and movable longitudinally therein, are piston rods 52, of circular cross-section and providing a substantially liquid tight sliding fit with the walls of the respective cylinders. The side of each piston rod 52, as shown, for example, in FIGS. 4, 8 and 9, has a longitudinal flat 53 extending some distance from its outer end, whereby a transfer chamber is formed between said fiat and the wall of the cylinder, through which fluid may pass to and from the interior of the cylinder. Flats 53 on one longitudinal pair of pistons 52 are arrayed toward one side of rotor 37 while the flats on the other longitudinal pair of pistons 52 are arrayed toward the opposite side of the rotor (FIGS. 4, 8).

The inner end of each piston 52 is provided with a spaced transverse tongue 54 which is adapted to be engaged by a corresponding lip 55 on axial control nut 56, positioned within and movable laterally in all directions within aperture 51 of rotor 37. (FIGS. 4, 8 and 9.) Lips 55 of nut 56 are always in slidable engagement with tongues 54 of each respective piston 52, regardless of the position of said nut within aperture 51 of rotor 37. Nut 56 has an axial aperture 57 which accommodates shaft 58 around which said nut rotates freely when rotor 37 is rotated by drive shaft 43.

Connected to the outer end of shaft 58 is a cross bar 59 having in its outer face 61 a lateral recesse 62 within which cross head 63 is slidably movable. Cross-head 63 has an axial aperture 64 which is engaged by pin 65 which projects longitudinally and off center from the inner end face of control shaft 66.

Control shaft 66 is rotatably mounted within central aperture 67 of stationary block 68 which is mounted securely within an axial aperture in end plate 32. Control shaft 66 is provided with annular recess 69 which accommodates resilient O ring 71, made of rubber or other suitable material, to serve as a sealing means for control shaft 66. The inner face of block 68 has a transverse recess 72 which slidably accommodates cross bar 59.

The outer face of block 68 has a transverse recess 73 which accommodates cross bar 74 having a central aperture 75 through which control shaft 66 extend-s. Cross bar 74 has a pair of apertures 76 through which bolts 77 extend to secure said bar and block 63 to end plate 32. The outer end of control shaft 66 has a transverse aperture 78 which accommodates control lever 79 by means of which said shaft is rotated.

The rotation of control shaft 66, either by manual operation of lever 79 or by other suitable mechanical or automatic means connected thereto, causes the arcuate movement of pin 65 which, through the linkages shown and described hereinabove, results in a corresponding movement of control nut 56 in respect of the stationary axis of rotor 37. Although control shaft 66 is axially aligned with the axis of rotation of rotor 37, a rotation of said shaft enables control pin 65, by virtue of the compound linkage shown in FIG. 9, to move the axis of shaft 58 from a zero or neutral position to full displacement from the rotor axis.

When lever 79 is in the vertical position, FIG. 4, the axis of shaft 58 is at its farther-most displocement from the axis of rotation of rotor 37; and when the latter rotates, pistons 52 will produce a full pumping stroke within their respective cylinders. When lever 79 is in the horizontal position as shown in FIG. 6, shaft 58 is coaxial with the axis of rotation of rotor 37 and, upon the rotation of the latter, pistons 52 do not move within their respective cylinders and hence no pumping action will take place. Thus, between the limits of these 90 radial positions, shaft 66 may be adjusted at will to control the extent of longitudinal pumping motion of pistons 52 within their respective cylinders to produce the desired volume of fluid to be .delivered from the pump in respect of each revolution of rotor 37 One longitudinal pair of cylinders A and C is provided with

arcuate ports

81 and 82, respectively, both extending through one side wall of rotor 37, while the other longitudinal pair of cylinders B and D is provided with

arcuate ports

83 and 84, respectively, extending through the opposite wall of rotor 37. It will be noted that

arcuate cylinder ports

81 and 83 are equidistant from the axial center of rotor 37, while

arcuate ports

82 and 84 are also equidistant from said axial center, except that the latter pair of ports is spaced a shorter distance from said center than the former pair. The flats 53 of each piston 52 are located to face their respective cylinder ports of the respective cylinders A, B, C and D. The longitudinal dimensions of flats 53 on pistons 52 are sufficient to provide free flow of fluid from and into the various cylinders through the cylinder ports, even at the outer extreme position of the respective pistons, as shown, for example, by the position of the lower piston in FIG. 4.

Instead of having a flat 53, each piston 52a may alternatively be provided at its outer end, as shown in FIGS. 10 and 11, with a longitudinal bore 88 communicating with a somewhat elongated transverse slot 89, the mouth of which cooperates with its respective cylinder port. Slot 89 is elongated in order that fluid may be transmitted therethrough to and from its corresponding cylinder port regardless of the position of piston 52 in its respective cylinder.

FIG. 5 shows the interior face of either end plate 32 or end plate 33, which are substantially mirror images of each other, and which are positioned with their respec' tive similar porting elements substantially opposite each other. The interior face of each end plate is provided with a wide recessed arcuate suction or intake port 91, occupying a sector approximately 270 long. Each intake port 91 is provided at one end with an inlet aperture 92, and at the other end with an outlet aperture 93 bored through their

respective end plates

32 and 33. Connected to inlet aperture 92 is fuel supply line 23 and connected to outlet aperture 93 is fuel return line 26 (FIG. l).

Each

end plate

32 and 33 is also provided with four narrow arcuate

recess outlet ports

95, 96, 97 and 98, each being approximately 45 in length or occupying end plate sectors of substantially that length.

Each

outlet port

95, 96, 97 and 98 is provided with its

own exit port

101, 102, 103 and 104, respectively, communicating with the exterior of

end plates

32 and 33. Each of these exit ports is tapped to accommodate the threaded end of a tube, preferably of flexible copper, or the like, which leads to a separate corresponding cylinder in the internal combustion engine into which fuel is to be injected. There being four outlet ports in each

end plate

32 and 33, it is apparent that an eight cylinder internal combustion engine is served by this embodiment;

Cylinders A and C are supplied with liquid from intake port 91 in end plate 33, while cylinders B and D are supplied with liquid'from intake port 91 in end plate 32. Since

cylinder ports

81 and 83 are displaced a greater distance from' the axial center of rotor 37 than

cylinder ports

82 and 84; respectively, intake ports 91 are sufficiently wide to supply all of said cylinder ports.

It is necessary, however, to discharge liquid from each rotor cylinder selectively and successively into specific outlet ports in end plates .32 and 33, for distribution and injection into specific corresponding cylinders of the internal combustion engine. Consequently, the axial displacement between cylinder ports 81, 82' and

ports

83, 84, is matched by a substantially equivalent axial displacement between

outlet ports

95, 96, and

ports

97, 98, in each

end plate

32 and 33. Thus,

cylinder ports

81 and 83 Will transmit fluid only to

outlet ports

95 and 96, while

cylinder ports

32 and 84 will transmit fluid only to

outlet ports

97 and 98, in their

respective endplates

32 and 33. In order to ensure substantially equal distribution of fuel to each of the engine cylinders,.

arcuate ports

95, 96, 97 and 98 are of substantially equal angular length.

The distributing operation of the injection pump herein is schematically illustrated in FIGS. 12, 13 and 14. FIG. 12. is a view of the interior wall of end plate 33, and FIG. 13 is an interior view of end plate 32. FIG. 14 is a diagrammatic graph showing the relationship between the rotor cylinders A, B, C and D, and cylinders 1 through 8 of the internal combustion engine which is to be supplied with fuel. The outward pumping strokes of rotor pistons 52 take place during substantially 180 of rotation of rotor 37 and during substantially the other 180 of rotation, the pistons move inwardly to produce the requisite suction action to fill their respective cylinders for intake ports 91.

Drive shaft 43 of the distributing pump of the present invention is connected by suitable means to the distributor shaft or other operating shaft of an eight cylinder engine whereby rotor 37 rotates 360 during two revolutions of the engine. The action of the distributor in discharging the engine spark plugs is coordinated in timed relationship with the pumping action of the respective pistons so that fuel discharged through arcuate ports 95 through 98 in end plates 32 and 33'will be injected into the intake manifold adjacent the intake port of each respective en gine cylinder prior to ignition time, and prior to or during the time that the intake valve for each respective engine cylinder is open.

Upon rotation of rotor 37, each cylinder of said rotor is supplied with fuel when its respective port traverses intake ports 91 in

end plates

32 and 33 and during the. inward suction motion of its respective piston. Rotor cylinders B and D' receive fuel from intake port 91 in end plate 32, while rotor cylinders A and C receive fuel from intake port 91 in end plate 33.

As rotor 37 continues its movement, cylinder port 81 of rotor cylinder A traverses arcuate port 95 in end. plate 33, said port being connected by a suitable pipe line to cylinder 3 of the internal combustion engine. This traverse takes place during approximately 45 of the rotation of rotor 37, after which the next 45 of its rotation causes. cylinder port 81 to traverse port 96 in end plate 33, said port being connected by suitable pipeline to cylinder 4 of the internal combustion engine. During the substantially 90 rotaton of rotor 37 when ports 95 and 96in end plate 33 are traversed, piston 52 in rotor cylinder A moves outward to produce the requisite pressure to cause the transmission of the liquid into said ports and, consequently, into the corresponding engine cylinders.

The next 90 of rotation of rotor 37 causes portd-iv of rotor cylinder B to traverse

ports

97 and 98 in end plate 32, said ports being connected respectively to cyls inders 5 and 6 of the internal combustion engine. the third of rotation of rotor 37, port 32 of rotor cylinder C traverses

ports

97 and 98 in end plates 33 through which fuel is transmitted to

engine cylinders

7 and 8, respectively. During the fourth 90 rotation of rotor 37, port 83 of rotor cylinder D traverses ports and 96 in end plate 32 for transmitting fuel to

engine cylinders

1 and 2, respectively.

In some embodiments,

ports

95, 96, 97 and 93 may be somewhat shorter in angular length than 45, since

cylinder ports

81, 82, 83 and 34 actually traverse the respective end plate ports for a longer angular time than the actual angular lengthof the end plate ports because of the additive length of said cylinder ports themselves. Also, the lengths of cylinder ports 81 through 84 may be arranged to be slightly longer than the angular lengths of the lands between the ends of ports 91 and the ad jacent ends of

ports

95, 96, 97 and 98, as well as longer than the angular length of the lands between adjacent ends of

ports

95 and 96, and of

ports

97 and 93. Hence, there may be a slight overlapping of traverse time of the cylinder ports across the end plate ports which is not deleterious to the operation and timing of the pump; in fact, by providing for the slightly overlapping length of cylinder ports 81 through 84, continuous flow of liquid through the cylinders of the rotor and through the respective ports is achieved, whereby possible knocking of the pump is obviated.

Although, as indicated above,

cylinder ports

81 and 83 are-substantially equidistant from the axial center of rotor 37 as are

ports

82 and 84, at a different distance therefrom, it isunderstood that other suitable operative arrays of said ports may be arranged provided the porting of end plates is modified to accommodate the cooperating traverse of said cylinder ports to permit the desired flow of fluid to and from the cylinders. Also-the lengths of arcuate ports 95 through 98 may be varied somewhat within operative limits to transmit different volumes of liquid to the engine cylinders or to establish different timing for the fuel injection into the engine cylinders.

From the foregoing it is apparent that the discharge from each cylinder into its respective cooperating group of spaced apart and successive outlet ports will be completed before a next succeeding cylinder discharges its contents into its respective cooperating group of spaced apart and successive outlet ports. Thus, a succession of separate, successive discharges takes place from the several discharge ports in a controlled and timed sequence, which is particularly advantageous when fuel is to be injected successively into separate cylinders of an internal combustion engine, for example.

The operating parts of the pump are arranged to cause the outward motion of pistons 52 during the 90 of rotor motion when the cylinder ports are traversing their

respective outlet ports

95, 96, 97 and 98 in

end plates

32 and 33. Since cylinders A, B, C and D are symmetrically arrayed in rotor 37 and pistons 52 are of equal length, the pumping action-in each of said cylinders will be equal to each other and will provide an equal amount of fuel to be delivered to each of the respective engine cylinders. The amount of fuel delivered to the engine cylinders may be varied by manipulating lever 79 to rotate control shaft 66, whereby the stroke of pistons 52 may be shortened or lengthened, as desired, for controlling the operating power. of the engine.

In the foregoing description, it is assumed that the pumping action of pistons 52 in rotor 37 takes place in the sector above the horizontal diameter of the illustration of FIG. 5. Consequently, it is apparent that a part of that pumping action will take place while the-cylinder ports of the respective cylinders are traversing the end portions of intake port'91 from which fuel is transmitted into the cylinders within. the 180 sector below said horizontal diameter. In most circumstances, the

discharge of fluid from a particular cylinder into an end.

Uponportion of intake port 91 is compensated by the taking up of fluid from the same intake port by the cylinder that is positioned 180 apart from said discharging cylinder, whereby the pressure conditions in port 91 are effectively stabilized.

In some cases, however, it may be desirable to isolate the discharge action of the cylinders from intake port 91, and consequently,

end plates

32 and 33 may be ported as shown in FIGS. 2, 15 and 16. In this embodiment, intake port 111 is substantially 180 in length or slightly less, and is provided with inlet port 112 connected to supply line 23 and with an outlet port 113 connected to return line 26. In order to take care of the initial discharge from the rotor cylinders, an arcuate discharge port 114 having an operational discharge length of approximately 45 is slightly spaced apart from the end of intake port 111. This first discharge port 114 has an outlet aperture 115 (FIG. 2), which is connected by means of pipe line 116 to return line 26. A last discharge port 117, similar to port 114, is provided for returning the remainder of the rotor cylinder discharge liquid through outlet port 118 by Way of pipe line 119 to overflow line 28 connected to return line 26.

Discharge ports

114 and 117 are substantially as wide as port 111 in order to accommodate the cylinder ports which are radially displaced from each other. In this embodiment,

outlet ports

95, 96, 97 and 98 are similar in size, array and function to the identically numbered ports shown in FIG. 5.

FIGS. 15 and 16 also show an alternative means for providing outlet apertures for outlet ports 95 through 98. Said

respective outlet apertures

123, 124, 125 and 126 are bored radially through

end plates

32 and 33, and are connected to outlet apertures 95 through 98 by means of lateral recesses 127. The outer ends of apertures 123 through 126 may be tapped to accommodate the threaded ends of flexible copper tubing, or the like, which transmit the liquid to the respective engine cylinders.

An additional advantage of providing for first and

last discharge ports

114 and 117, respectively, lies in the fact that when cavitation occurs in the volatile fuel, a large portion of the vapor may be discharged from the rotor cylinders before transmitting fuel to outlet ports 95 through 98, and before returning to take up a further supply of fuel from intake port 111. In either porting arrangement in the respective embodiments of FIGS. and 15, the positions of cylinder ports 81 through 84 assist in the elimination or at least reduction of the effects of cavitation from the fuel to be transmitted to the engine cylinders by virtue of the fact that they are each arrayed laterally some distance from the outer ends of their respective cylinders. Thus, upon rotation of rotor 37, centrifugal action causes the liquid fuel to fill up the end portions of said cylinders, and the lighter weight vapor being displaced from said end portions, will pass first through the cylinder ports at the beginning of the pumping strokes of the respective pistons during the initial approximate 45 movement of each cylinder above the horizontal diameter of the pump prior to the approximate 90 rotation during which outlet ports 95 through 98 are being supplied with fuel.

In some embodiments of the present invention, it is possible to dispense with fuel pump 24 and relief valve 27 previously shown in FIGS. 1 and 2, by taking advantage of the work action of rotor pistons 52 to draw fuel from tank 21 through line 23 into intake port 91a of FIG. 2A, by way of inlet port 92a. In this embodiment, intake port 91a does not have an outlet port. Port 91a is approximately 225 in length, approximately 45 being in a position Where the pistons are still performing their discharge functions. The pressure condition in intake port 91a is stabilized by virtue of the fact that one rotor cylinder is receiving fluid from said port and at substantially the same rate as its paired cylinder is diccharging fluid into said port. Intake port 91a is completely filled with liquid by the suction action of pistons 52 as their respective cylinder ports traverse said intake port. The initial discharge from the cylinders takes place through discharge port 11411 and through outlet port 115a to return line 26, for eliminating or at least reducing the effects of cavitation, after which the rotor cylinders perform their distributing function in conjunction with ports through 98 in the respective end plates as described hereinabove.

The end plate porting arrangement may be further modified as in FIG. 2B, which shows intake port 91b receiving fluid through inlet port 92b from supply line 23. In this embodiment, the rotor cylinders are performing their suction action during the full traverse of port 91b. In beginning their pumping strokes, however, the rotor pistons now discharge the first portion of liquid into discharge port 11% from which liquid flows through outlet port b to return line 26. Discharge port 11411 is substantially 90 in length or slightly less, and consequently, end plate distributing ports 95 through 98 are traversed during substantially the last half of the 180 discharge action of the respective cylinders. One advantage that may be realized in the embodiment of FIG. 2B is that a greater amount of vapor bubbles produced by cavitation may be disposed of through port 114!) before the cylinder ports traverse distributing ports 95 through 98 to insure the delivery of vapor-free fuel to the cylinders of the engine.

FIG. 2B also includes an injector connected directly between return line 26 and fuel supply line 23, said injector comprising a tube 128 which is a continuation of return line 26 lying submerged in the fuel supply 22 at or near the bottom of tank 21. The end of tube 128 is surrounded by a coaxial open ended tube 129 which tapers around the end of tube 128 and joins fuel supply line 23.

Tubes

128 and 129 together act as a fluid injector that takes advantage of the work energy of the rotor pistons in discharging liquid under pressure through port 114k. Thus, the liquid flowing under pressure from tube 128 assists in the pumping of fuel from the tank into supply line 23. In some embodiments, tip 130 of tube 128 may be made in the form of a nozzle of a suitable elastic material which compensates for different volumes of fuel passing therethrough due to variations in the speed of the pump and to the different settings of the variable volume control described hereinabove. It is understood that injectors as described herein, are particutarly well adapted to operate in conjunction with fuel pumps as described herein which are capable of dividing each cylinder discharge under pressure into sever-al separate output quantities, at least one of which is passed through the injector to enhance the pumping action of the device.

Another embodiment of the pump herein is shown in FIGS. 17, 18 and 19 wherein previous rotor 37 is replaced by rotor 131 between

end plates

32 and 33. Rotor 131 is provided with cylinders W, X, Y and Z, which are similar in array to cylinders A, B, C and D of rotor 37. Cylinders W, X, Y and Z are cut completely through the thickness of rotor 131 and accommodate pistons 132 movable longitudinally therein. Pistons 132 have a substantially rectangular cross section, and it will be noted from FIG. 18 that the lateral dimensions of said pistons are equal to that of rotor 131. The outer surfaces of pistons 132 are in slidable engagement with the interior surfaces of

end plates

32 and 33, as are the outer walls of rotor 131, whereby cylinders W, X, Y and Z are provided with a substantially liquid tight seal. The inner ends of pistons 132 have the same structure as that provided for pistons 52 and are operatively engaged by nut 56 to produce the requisite pumping and suction strokes for such pistons.

One side wall of each cylinderW, X, Y and Z has a longitudinal recess 133 positioned intermediate between the outer faces of rotor 131 and extending for some distance from the outer ends of said respective cylinders (FIGS. 17 and 18). Each of said recesses 133 communicates with an

arcuate cylinder port

134, 135, 136 and 137, corresponding to cylinders W, X, Y and Z, respectively. It will be noted that arcuate cylinder ports 134 and 136 are cut through one side of rotor 131, while arcua-

te cylinder ports

135 and 137 are cut through the opposite wall of said rotor in a manner comparable to cylinder ports 81 through 84 in rotor 37 Cylinder ports 134 and. 135 are positioned somewhat closer :to the radial center of rotor 13-1 than

ports

136 and 137 in order to produce the same selectivity of porting action as described hereinabove in connection with the cylinder ports of rotor 37.

In the embodiment of FIG. 17, however, cylinder ports 134 through 137 are generally closer to the axial center of. rotor 131 than are ports 81 through 84, in order to insure that, liquid from a particular cylinder will flow only through the corresponding a-rcuate outlet ports in either

end plate

32 or 33. In order to accommodate the functions of cylinder ports 134 through 137, arc-uate intake ports 91 and :arcuate outlet ports 95 through 98'will be positioned in a suitable corresponding array closer to the axial center of the pump. Also, the positions or arcuate outlet ports 95 through 98 in the end plates may be slightly staggered in order to preserve the selectivity of cooperative function for distributing the fuel to the respective engine cylinders. This may also require a slight slanting modification of the ends of intake ports 91 and 111, and of the ends of discharge ports 114 and'1127, to insure the proper timing of the pumping and suction functions of the cylinders. These. modifications will be determined by experimental and design requirements, but will not alter .the ultimate distributing and injecting functions of the pump as described hereinabove.

Central aperture 51 of rotor 131 is provided with a plurality of recesses 138 cut through the body thereof, said recesses eachaccomrnodating a projecting finger 139 of suitable length on spider 141 mounted on the inner end of drive shaft 43' (FIG. 19) which rotates said rotor.

In some embodiments, it may be. desirable to provide lubrication for the. interior Working parts of the pump, as shown schematically in FIG. 20. Aperture 140 is bored radially through rotor 37 connecting axial aperture 51 witht-he chamber'36 between

end plates

32 and 33. See also FIGS. 4, 7 and 8. Spacer ring 34 is pro vided with a radial aperture. 142 which threadably accommodates a tube 143. Block 6 8 is provided with a transverse aperture 144; one endof which communicates with the interior of axial aperture 51 of rotor 37, the other end of'which meets a corresponding aperture 145 out through cross bar'74. Aperture 145 threadably accommodates tube 146 which is connected to a source of lubricating oil' (not shown), or the like. Pipe 143 is connected by way' of a return line to the source of lu 'bricating oil; Oil 147 withinaxial aperture 51 lubricates the action of nut 56 in conjunction with pistons 52. Also, a film of the oil Will spread over the surface of pistons 52' to provide lubrication between said pistons and their respective cylinders. The radial position of aperture 141 in rotating rotor 37 will produce a centrifugal pumping action for oil 147 whereby said rotor will act as a circulatingrpump for the lubricating oil, thereby dispensing with the necessity of utilizing exterior lubricating pumps. In such embodiments, tube 143 can be connected directly to inlet aperture 144, either externally of the pump or through end plate 32.

Although the foregoing description is concerned with a fuel injection pumphaving two ported end plates and:

a rotor having two pairs of cylinders, each pair coop-- crating with a respective end plate, the principles of the invention may also be: realized by the utilization of a:-

single ported end plate and: a rotor having a single pair.

10 of cylinders cooperating therewith, as illustrated diagrammatically in FIGS. 21 through 24. The construction of such a pump would be similar to that shown in FIGS. 3 through 9 except that inlet and outlet porting 1 would be provided only on the interior wall of end plate 32a, end plate 33 serving as a blank end plate for enclosing the chamber within which rotor 3 7a operates.

Rotor 37a in FIG. 21 is now provided with only two longitudinally arrayed cylinders B and D which contain pistons 52 as shown in "FIG. 8 and which are 0p erated by the same mechanisms for adjustably controlling the pumping action of said pistons as shown in FIG. 9. Cylinders B and D are provided with ports 84a and 83a, respectively, which are cut through the same side of rotor 37a for cooperation with ports on the interior wall of end plate 32a.

In order to provide fuel injection for a four cylinder internal combustion engine, the interior wall of end plate 32a (FIG. 22) is provided with an intake port 151 which occupies the 180 sector during which pistons 52 draw liquid into their respective cylinders. Four

arcuate discharge ports

152, 153, 154 and 155 are positioned on the interior wall of end plate 32a and, in pairs, occupy sectors of said end plate. Discharge ports 152 through are connected by suitable outlets (not shown) bored in end plate 32a to respective cylinders of the engine. Cylinder port 83a traverses

discharge ports

152 and 153 and expels fuel from cylinder D successively into

discharge ports

152 and 153 during 180 rotation of rotor 37a, while at the same time cylinder port 84:: admits fuel from intake port 151 into cylinder B. During the next 180 rotation of rotor 37a, fuel from cylinder B is expelled through cylinder port 84:: successively into discharge ports 154 and 155, during which time cylinder D is being replenished with fuel from intake port 151.

FIG. 23 shows a discharge porting arrangement on end plate 32b which serves a six cylinder internal cornbustion engine. Here, ports 83a and 84a of rotor 37a cooperate with six

arcuate discharge ports

156, 157, 158 and 159, and 161, each of which, in pairs, occupies a 60 sector of end plate 32/). Each discharge port 156 through 161 is connected *by suitable means to a corresponding engine cylinder. Fuel from cylinder D is expelled through port 83a as the latter traverses

ports

156, 157' and 158 during of the rotation of rotor 37a, after which fuel from cylinder B is expelled through port 842: as the latter traverses discharge ports 159, 160 and 161.

An eight cylinder internal combustion engine may also be provided with fuel injection by the utilization of a two cylihder rotor 37a with a porting arrangement on a simple end plate 320, as shown in FIG. 24. End plate 32c is now provided with

arcuate discharge ports

162, 163, 164,

165, 166, 167, 168 and 169, each occupying, in pairs,.

a 45 sector of said end plate and each being connected by suitable means with a corresponding cylinder of the engine. In this embodiment, cylinder port 83a successive.- ly traverses discharge

ports

162, 163, 164 and 16-5, while cylinder port 84a successively traverses discharge ports 1'66, 167, 168 and 169 to provide successive fuel injection into the corresponding engine cylinders in the same manner described in connection with FIGS. 22 and 23.

In the embodiments of FIGS. 21 through 24, it is understood that the rotation of rotor 37a will be coordinated with the operation of the internal combustion. engine so that discharge of fuel through the end plate ports of the pump will be in requisite timed relationship for injection thereof into the respective engine cylinders.

In some embodiments, it may be desirable to provide a.pump embodying the principles of the present invention, and employing a two cylinder rotor as shown in FIG. 21, except that cylinder ports 83a and 84a will be.

cut through opposite walls of rotor 37a bounded by two end plates similar to those shown in FIGS. 22 through 24, with the difference that only one arcuate row of discharge ports would appear in the upper 180 sector of each end plate. For example, in an embodiment comparable to that of FIG. 22 for serving a four cylinder engine, discharge ports 1'52 and 153 would be positioned on the interior wall of one end plate while discharge ports 154 and 155 would appear on the interior wall of the other end plate, each end plate having its own inlet port 151.

Similarly for six cylinder engine injection in an array comparable to that shown in FIG. 23, one end plate would be provided with

arcuate discharge ports

156, 157 and 158, while the opposite end plate on the other side of rotor 37a would be provided with arcuate discharge ports 159, 160 and 161. For the eight cylinder engine,

ports

162, 163, 164 and 165 (FIG. 24) would appear on one end plate while

discharge ports

166, 167, 163 and 169 would appear on the other end plate.

Furthermore, when two end plates are provided for the foregoing modifications of FIGS. 22 through 24, it is understood that cylinder ports 8 3a and 84a (FIG. 21) may be spaced equidistantly from the axial center of rotor 37a; consequently, discharge

ports

152, 153 on one end plate, and discharge ports 154, 155 on the other end plate, would be displaced an equal distance from the axial center of the respective end plates. The same equivalent displacement will obtain for

discharge ports

156, 157 and 158 on one end plate, and discharge ports 159, 160 and 161 on the opposite end plate, comparable to FIG. 23; equivalent axial displacement will obtain also for

ports

162, 163, 164 and 165 on one end plate, and discharge

ports

166, 167, 168 and 169 on the opposite end plate, comparable to FIG. 24.

It will be understood, of course, that in all the foregoing modifications of FIGS. 21 through 24, intake port 151 on each end plate need only be sufficiently wide to cooperate with its corresponding cylinder port 83a and 84a.

In characterizing the end plate ports as having arcuate lengths of 45, 60, 90, 180", or other angular lengths, in the various embodiments herein, it is to be understood that said designations actually indicate the approximate angular sectors of the respective end plates that are occupied by said ports. Also, in the case of the end plates 32b (FIG. 23) and 320 (FIG. 24) the lengths of the discharge ports will vary one from the other to account for variance in the output of rotor cylinders B and D during different portions of the piston strokes therein. In actuality the ports are sufiiciently shorter than the angular sector dimensions in order to permit the placement of lands between the ends of adjacent ports which are thereby rendered capable of performing their separate selective functions.

If it is desirable in some embodiments of the present invention to shorten the duration of injection of fuel to each individual engine cylinder and still maintain accurate injection timing, this can be accomplished by V shortening the end plate discharge ports to the engine cylinders and providing auxiliary return discharge ports to the fuel supply to accommodate the complete output from the respective rotor cylinders.

FIGS. 1, 2, 2A, 2B, 12, 13, 22, 23 and 24 illustrate diagrammatically various types of end plate porting arrangements, and therefore the full diameters of said end plates are not indicated in said figures, as was done in FIGS. 5 and 15. It is understood that these end plate diameters as well as the dimensions of all of the other parts of the various embodiments of the apparatus described and claimed herein will be determined by the usual manufacturing and functional requirements thereof.

In addition to fuel injection of internal combustion engines, it is contemplated that the pump of the present invention can be utilized for the selective distribution of discrete quantities of liquid to other apparatus which operates under predetermined timing conditions; as for ex- 12 ample, in lubricating systems, chemical processes, and sequential operation of various types of apparatus.

In the specification, I have explained the principles of my invention, and the best mode in which I have contemplated applying those principles, so as to distinguish my invention from other inventions; and I have particularly pointed out and distinctly claimed the part, mode or combination which I claim as my invention or discovery.

While I have shown and described certain preferred embodiments of my invention, it will be understood that modifications and changes may be made without departing from the function and scope thereof, as will be clear to those skilled in the art.

I claim:

1. A variable volume pump comprising a housing, a pair of end plates in said housing defining a chamber between their opposing interior walls, a member rotatable upon a stationary axis within said chamber, the walls of said member being in intimate sliding contact with respective opposing interior walls of said end plates, two longitudinal pairs of cylinders in said member, each pair arrayed substantially relative to the other, said cylinders being closed at their outer ends, each pair of cylinders being operative in conjunction with a respective one of said pair of end plates, a port for each of said cylinders, the ports of one longitudinal pair of cylinders being cut through one sliding wall of said member and the ports of the other pair of cylinders being cut through the opposite wall of said member, the port in one cylinder of each pair of cylinders b ing displaced radially a greater distance from the axis of said member than the port of the other cylinder of said pair, a piston in each of said cylinders, means connected to each of the pistons and movable into various positions eccentric to said axis for producing longitudinal motion of said pistons in said cylinders whereby during the suction stroke of a piston in one cylinder of a pair of cylinders the piston in the other cylinder of said pair is producing a pressure stroke, each of said alternate pressure and suction stroked occurring during substantially of the rotation of said member, said movable means serving as an axis for said pistons independent of the axis of rotation of said member, an arcuate inlet port on the interior wall of each end plate and being traversed by a cylinder port during the time that its respective piston is performing its suction stroke, and a first group of separate circumferentially spaced, arcuate discharge ports on the interior wall of each end late traversable successively by the port of one of its respective pair of cylinders, and a second group of separate, circumferentially spaced, arcuate discharge ports on the interior wall of each end plate traversable successively by the port of the other of said respective pair of cylinders, each group of discharge ports being posi tioned in a corresponding sector of its respective end plate where each piston is performing its pumping stroke in the cylinder whose port is traversing its corresponding group of discharge ports.

2. A pump according to claim 1 wherein said discharge ports were separated by lands and wherein each cylinder port is in the form of a transverse, elongated slot whose length is slightly greater than the length of the lands between adjacent ends of all of the discharge ports in the respective end plate that it traverses.

. 3. A pump according to claim 1 wherein the successive, arcuate discharge ports traversed by the port of one of a pair of cylinders are displaced radially from the successive arcuate discharge ports traversed by the port of the other cylinder of said pair by a radial distance substantially equivalent to the respective radial displacement of said cylinder ports.

4. A pump according to claim 1 wherein said inlet port on each end plate has an arcuate length greater than 180 and is adapted to be traversed by the port of each co- 13 operating cylinder during the pressure stroke of its respectivepiston for a portion of the rotation of said member prior to said cylinder port traversing its corresponding arcuate discharge ports.

5. A pump comprising a housing, an end plate in said housing, a member slidably rotatable against said end plate within said housing, a pair of cylinders arrayed longitudinally in respect of each other in said member, a port for each cylinder facing said end plate, one of said cylinder ports being displaced radially from the axis of said member a greater distance than the other cylinder port, an arcuate int-akeport in said end plate with which both cylinder ports cooperate, a first group of separate, circumferentially spaced arcuate discharge ports in said end plate and located in a position to cooperate with one of said cylinder ports, a second. group of separate, circumferentially spacediarcuate discharge ports in said end plate and locatedina position to cooperate with the other of said cylinder ports, each of. said groups of discharge ports being positioned and arranged to receive a single discharge output from a corresponding cylinder and to divide said dischargeoutput into a group of separate successive discharges, a pistonin each of said cylinders, means tor producing longitudinal motion for said pistons Within the respective cylinders, and means for controlling said first means to adjust the length of the stroke of said pistons.

6. A pump comprising a housing, a pair of end plates in said housing, a member slidably rotatable between said end plates, a pair of radially disposed cylinders in said member, a port for one cylinder facing one end plate, a port for the other cylinder facing the other end plate, an arcuateintake port in each end plate cooperating with a corresponding cylinder port, a plurality of circumferentially spaced arcuate discharge ports in each end plate adapted to cooperate with a corresponding cylinder port, said discharge ports in each of said end plates being positioned and arranged to receive a single discharge output from a corresponding cylinder and to divide said discharge output into a group of separate successive discharges, a piston in each of said cylinders, first means connected to each of said pistons and movable into positions eccentric to the axis of rotation of said member for producing longitudinal motion for said pistons within the respective cylinders, and second means connected to said first means for controlling said first means to adjust the length of the stroke of said pistons.

7. A variable volume pump comprising a housing, a pair of spaced apart end plates in said housing forming a chamber therebetween, :a member rotatable on a stationary axis within said chamber, a pair of walls on said member in intimate sliding contact with respective interior walls of said end plates, a plurality of cylinders in said member, a piston in each of said cylinders, said piston being adapted to produce a suction stroke and a discharge stroke within its respective cylinder, said pistons being connected to a common axis of rotation movable independently of the axis of rotation of said member, a port for each of said cylinders cut through a Wall of said member, and a plurality of sets of circumferentially spaced separate outlets on the interior walls of each of said end plates, the port of each cylinder slidingly cooperating with successive separate outlets of only a respective selected set of outlets on said end plates whereby at least a portion of each discharge from each cylinder during a single discharge stroke of its respective piston is transmitted in separate successive portions to the outlets of said respective set.

8. A variable volume pump comprising a housing. an end plate in said housing, a member rotatable on a stationary axis in said housing, a wall on said member in intimate sliding contact with the Wall of said end plate, a plurality of radially disposed cylinders in said member, a piston in each of said cylinders, said piston being adapted to produce a suction stroke and a discharge stroke within its respective cylinder, said pistons being connected to a common axis of rotation movableindependently-of the axis of rotation of saidmember, a port for each of said cylinders cut through :a wall of said member, and'a plurality of sets of circumferentially' spaced separate outlets on said Wall of said end-plate, the port of each cylinder slidingly' cooperating with circumferentially spaced separate outlets of only a respective selected set of outlets on said end plate whereby at least a portion of each discharge from each cylinder during a single discharge stroke of its respective piston is transmitted in separate successive portions to the outlets of said cylinders respective set'of out lets.

9. A variable volume pump comprising a housing, a chamber within said housing, a member rotatable within said chamber, a drive shaft connected to said member and extending through a wall of said housing, said shaft causing said member to rotate upon a stationary axis, at least one pair of cylinders arrayed longitudinally in respect of each other in said member, a piston in each cylinder, a movable hub to which the-inner end of each piston is connected, said hub being movable at Will and serving as an axis of rotation for said pistons independent of the axis of rotation of said member, a port for each of said cylinders, the port of one cylinder being displaced a greater distance from the axis of rotation of said member than the port of the other cylinder, inlet means in said housing cooperating with both cylinder ports, two groups of circumferentially spaced, separate arcuate outlets in a wall of said housing, said groups of outlets being'radially spaced apart from each other, each of said groups of outlets being located to cooperate with the port or a corresponding cylinder only, each of said groups of outlets receiving successive, separate portions of fluid from a single discharge of a cooperating cylinder.

10. A variable volume pump comprising a housing, a chamber within said housing, a member rotatable within said chamber, a drive shaft connected to said member and extending through a first wall of said housing, said shaft causing said member to rotate upon a stationary axis, at least one pair of cylinders arrayed longitudinally in respect of each other in said member, a piston in each cylinder, first means to which the inner end of each piston is connected, said first means being movable relative to said member and serving as an axis of rotation for said two pistons independent of the axis of rotation of said member, second means extending through a second wall of said housing and operative on said first means for moving the axis of rotation of said pistons at will relative to the axis of rotation of said member whereby variable volume pumping action of said pistons is achieved when said member rotates, a port for each of said cylinders, the port of one cylinder being displaced a greater distance from the :axis of rotation in said member than the port of the other cylinder, inlet means in said housing cooperating with both cylinder ports, two groups of circumferentially spaced, separate arcuate outlets in a wall of said housing, said groups of outlets being radially spaced apart from each other, each of said groups of outlets being located to cooperate with the port of a corresponding cylinder only, each of said groups of outlets receiving successive, separate portions of fluid from a single discharge of a cooperating cylinder.

11. A fuel distributing system for an automotive engine or the like, comprising a fuel supply, a pump housing, an end plate in said housing, a member slidably rotatable against said end plate within said housing, a pair of cylinders arrayed longitudinally in respect of each other in said member, a port for each cylinder facing said end plate, one of said cylinder ports being displaced radially from the axis of said member a greater distance than the other cylinder port, an arcuate intake port in said end plate with which both cylinder ports cooperate, a connection between said intake port and said fuel supply, a first group of separate circumferentially spaced arcuate discharge ports in said end plate and located in a position to cooperate with one of said cylinder ports, and a second group of separate, circumferentially spaced arcuate discharge ports in said end plate and located in a position to cooperate with the other of said cylinder ports, each of said groups of discharge ports being positioned and arranged to receive a single discharge output from a corresponding cylinder and to divide said discharge output into a group of separate, successive discharges, both of said cylinder ports traversing said intake port in said end plate, said intake port in said end plate being disposed on said end plate in the path of said cylinder ports in advance of and subsequent to both groupsof discharge ports whereby a portion of the initial discharge from each cylinder is returned into said intake port prior to discharge into its corresponding discharge ports, and a portion of the terminal discharge from each cylinder is also returned into said intake port after discharge into its corresponding discharge ports.

12. A fuel injection system for an internal combustion engine having a plurality of engine cylinders, comprising a fuel supply, a pump housing, a rotatable member in said housing, a plurality of pump cylinders radially disposed in said member, a plurality of sets of separate successive outlets circnmferentially spaced in said pump housing, a port for each cylinder, said port being located in said member in a position to cooperate with a corresponding set of outlets, each of said sets of outlets cooperating with the port of a corresponding pump cylinder moving past said outlets to receive separate successive portions of a single discharge from said pump cylinder, means connecting the first outlet of each set to said fuel supply, means connecting the remaining outlets of each set to corresponding cylinders of the engine, a piston in each of said cylinders, and means for producing longitudinal motion for said pistons within their respective cylinders.

16 13. A fuel injection system according to claim 12 wherein the outer end of each of said pump cylinders is closed, and each port is spaced from the outer end of its respective pump cylinder at the requisite distance to cooperate with its corresponding set of outlets in said housing.

References Cited in the file of this patent UNITED STATES PATENTS 1,904,653 Davis Apr. 18, 1933 1,974,961 Johnson Sept. 25, 1934 2,016,812 Benedek Oct. 15, 1935 2,248,452 Erickson July 8, 1941 2,332,665 Parsons Oct. 26, 1943 2,452,470 Johnson Oct. 26, 1948 2,506,974 Sorensen May 9, 1950 2,557,508 Leibing June 19, 1951 2,581,764 Leibing Jan. 8, 1952 2,633,187 Smith Mar. 31, 1953 2,651,999 Harrington Sept. 15, 1953 2,716,944 Ferris Sept. 6, 1955 2,720,344 Isreeli et a1. Oct. 11, 1955 2,764,964 Meyer Oct. 2, 1956 2,827,852 Links Mar. 25, 1958 2,969,738 Ulbing Jan. 31, 1961 FOREIGN PATENTS 128,020 Great Britain June 19, 1919 137,482 Great Britain Jan. 15, 1920 163,354 Austria June 25, 1949 215,745 Switzerland Oct. 16, 1941 463,854 Great Britain Apr. 7, 1937 529,664 Great Britain Nov. 26, 1940 1,044,469 France Nov. 17, 1953

Claims

1. A VARIABLE VOLUME PUMP COMPRISING A HOUSING, A PAIR OF END PLATES IN SAID HOUSING DEFINING A CHAMBER BETWEEN THEIR OPPOSING INTERIOR WALLS, A MEMBER ROTAABLE UPON A STATIONARY AXIS WITHIN SAID CHAMBER, THE WALLS OF SAID MEMBER BEING IN INTIMATE SLIDING CONTACT WITH RESPECTIVE OPPOSING INTERIOR WALLS OF SAID END PLATES, TWO LONGITUDINAL PAIRS OF CYLINDERS IN SAID MEMBER, EACH PAIR ARRAYED SUBSTANTALLY 90* RELATIVE TO THE OTHER, SAID CYLINDERS BEING CLOSED AT THEIR OUTER ENDS, EACH PAIR OF CYLINDERS BEING OPERATIVE IN CONJUCTION WITH A RESPECTIVE ONE OF SAID PAIR OF END PLATES, A PORT FOR EACH OF SAID CYLINDERS, THE PORTS OF ONE LONGITUDINAL PAIR OF CYLINDERS BEING CUT THROUGH ONE SLIDING WALL OF SAID MEMBER AND THE PORTS OF THE OTHER PAIR OF CYLINDERS BEING CUT THROUGH THE OPPOSITE WALL OF SAID MEMBER, THE PORT IN ONE CYLINDER OF EACH PAIR OF CYLINDERS BEING DISPLACED RADIALLY A GREATER DISTANCE FROM THE AXIS OF SAID MEMBER THAN THE PORT OF THE OTHER CYLINDER OF SAID PAIR, A PISTON IN EACH OF SAID CYLINDERS, MEANS CONNECTED TO EACH OF THE PISTONS AND MOVABLE INTO VARIOUS POSITIONS ECCENTRIC TO SAID AXIS FOR PRODUCING LONGITUDINAL MOTION OF SAID PISTONS IN SAID CYLINDERS WHEREBY DURING THE SUCTION STROKE OF A PISTON IN ONE CYLINDER OF SAID PAIR OF CYLINDERS THE PISTON IN THE OTHER CYLINDER OF SAID PAIR IS PRODUCING A PRESSURE STROKE, EACH OF SAID ALTERNATE PRESSURE AND SUCTION STROKES OCCURRING DURING SUBSTANTIALLY 180* OF THE ROTATION OF SAID MEMBER, SAID MOVABLE MEANS SERVING AS AN AXIS FOR SAID PISTONS INDEPENDENT OF THE AXIS OF ROTATION OF SAID MEMBER, AN ARCUTATE INLET PORT ON THE INTERIOR WALL OF EACH END PLATE AND BEING TRAVERSED BY A CYLINDER PORT DURING THE TIME THAT ITS RESPECTIVE PISTON IS PERFORMING ITS SUCTION STROKE, AND A FIRST GROUP OF SEPARATE CIRCUMFERENTIALLY SPACED, ARCUATE DISCHSARGE PORTS ON THE INTERIOR WALL OF EACH END PLATE TRAVERSABLE SUCCESSIVELY BY THE PORT OF ONE OF ITS RESPECTIVE PAIR OF CYLINDERS, AND A SECOND GROUP OF SEPARATE, CIRCUMFERENTIALLY SPACED, ARCUATE DISCHARGE PORTS ON THE INTERIOR WALL OF EACH END PLATE TRAVERSABLE SUCCESSIVELY BY THE PORT OF THE OTHER OF SAID RESPECTIVE PAIR OF CYLINDERS, EACH GROUP OF DISCHARGE PORTS BEING POSITIONED IN A CORRESPONDING SECTOR OF ITS RESPECTIVE END PLATE WHERE EACH PISTON IS PERFORMING ITS PUMPING STROKE IN THE CYLINDER WHOSE PORT IS TRAVERSING ITS CORRESPONDING GROUP OF DISCHARGE PORTS.