US1947050A

US1947050A - Multistage reversible variable discharge pump

Info

Publication number: US1947050A
Application number: US545298A
Authority: US
Inventors: Albert R Kuzelewski
Original assignee: American Engineering Co Ltd
Current assignee: American Engineering Co Ltd
Priority date: 1931-06-18
Filing date: 1931-06-18
Publication date: 1934-02-13
Anticipated expiration: 1951-02-13

Description

Feb 13, 1934. A, R. KUZELEWSKI MULTISTAGE REVERSIBLE VARIABLE DISCHARGE PUMP Filed June 18, 1931 '7 Sheets-Sheet l Feb, 13, 1934-. R, KUZELEWgK] LQ JKY QSQ MULTISTAGE REVERSIBLE VARIABLE DISCHARGE PUMP Filed June 18, 1931 7 Sheets-Sheet 2 Feb. 13 1934. R KUZELEWSK! 1,947,5@

MULTISTAGE REVERSIBLE VARIABLE DISCHARGE PUMP Filed June 18, 1931 7 Sheets-Sheet 3 Feb, 13, 1934. A. R. KuzELEwsKn MULTISTAGE REVERSIBLE VARIABLE DISCHARGE PUMP Filed June 18, 1931 7 Sheets-Sheet 4 Ffieh 19340 A. R. KUZELEWSKH L 4 fi MULTISTAGE REVERSIBLE VARIABLE DISCHARGE PUMP Filed June 18, 1951 7 Sheets-Sheet 5 Feb, 113, 1934. v A. R. KUZELEWSKE L94Z5 MULTISTAGE REVERSIBLE VARIABLE DISCHARGE PUMP Filed June 18, 1951 7 Sheets-Sheet 6 WNW Feb. 113, 119354. A. R. KUZELEWSKH 3)479@5@ MULTISTAGE REVERSIBLE VARIABLE DISCHARGE PUMP Filed June 18, 1931 7 Sheets-Sheet 7 L/Az v E I W W Patented Feb. 13, 1934 MUL'I'ISTAGE REVERSIBLE VARIABLE DISCHARGE PUMP Albert R. Kuzelewski, Philadelphia, Pa., assignor to American Engineering Company, Philadel- V phia, Pa., a corporation of Pennsylvania Application June 18, 1931. Serial No. 545,298

21'Claiml.

This invention relates to improvements in reversible and variable discharge pumps of the type disclosed in U. S. Patent No. 1,077,979, and known in the 'trade as Hele-Shaw.

One object of my invention is to provide a generally improved multi-stage pump of this general type.

Another object of the invention is to provide a pump of the stated character in which the fluid pressures are balanced with respect to the bearings of the rotary parts.

Still another object of the invention is to provide a pump of the stated character in which the fluid pressures are substantially balanced with respect to the central or master valve element.

Still another object of the invention is to provide a pump of the stated type in which the diameters of the rotary parts may be relatively small in relation to the power capacity.

The invention further contemplates the provision of a pump of the stated type having relatively low peripheral velocities. v

A still further object of the invention is to provide a pump of the stated character having a relatively uniform discharge substantially free from fluctuations.

A still further object of the invention is to provide a pump of the stated type having antifriction'bearing means interposed between the guide block and the housing.

A further and more general object of the invention is to provide a pump of the character set forth having generally improved operating characteristics.

Another object of the invention is to provide a pump of the stated type in which provision is made for reducing the power output while maintaining constant delivery.

The invention further resides in certain novel and improving structural details and features hereinafter set forth and illustrated in the attached drawings, in which:

Figure 1 is a plan view of a pump made in accordance with my invention;

Fig. 2 is a side elevational view of the pump;

Figs. 3 and 4 are end elevational and partial sectional views of the pump;

Fig. 5 is a transverse sectional view on the line 55, Fig. 6 2

Fig. 6 is a longitudinal sectional view as though taken on the line 6-6, Fig. 8; I

Fig. '1 is a fragmentary sectional view taken on the line 7-7, Fig. 5;

Fig. 8 is a development of the two intermediate cylinder bodies and the connecting gears:

Fig. 9 is a fragmentary horizontal sectional view on the line 9-9, Fig. 3;

Fig. 10 is a fragmentary sectional view on the line 10-10. Fig. 4;

Fig. 11 is a transverse sectional view illustrating a modification of my invention, and

Fig. 12 is a fragmentary sectional view on the line 12-12, Fig. 11.

With reference to the drawings, a preferred embodiment of my invention comprises a substantially rectangular housing 1, the open ends of which are normally closed by means of

coverplates

2 and 3 respectively. Rigidly supported in the

end plates

2 and 3 and in an inwardly projecting partition 4 of the housing is a cylindrical valve member 5, the ends of this member projecting through the said end plates, as shown in Fig. 6. Journaled on the housing in antifriction bearings 6, '7, 8 and 9 and closely embracing the valve 5 is a pair of rotary cylinder bodies 11 and 12, each of these bodies having two circumferential series of radial cylinders designated respectively 13, 14, 15 and 16. The inner ends of the cylinders of the series 13 are adapted to register with a pair of oppositely arranged ports 17 and 18 in the surface of the valve 5, the port 17 communicating with a pair of channels 19, 19 extending longitudinally through the body of the valve 5 to the adjacent end thereof, and the port 18 communicating with a corresponding pair of channels 21 which extend parallel to the channels 19 and also terminate in the adjacent end of the valve body. A pair of ports 22 and 23 corresponding to the ports 17 and 18 is provided for the cylinders of the series 14, and these ports 22 and 23 also respectively communicate with the inner ends of the channels 19 and 21, it being noted that the channels 19 and 21 terminate in the present instance just inwardly of the said ports 22 and 23. Ports corresponding to the ports 17, 18, 22 and 23 and correspondingly placed are provided for the cylinders of the series 15 and 16, these ports being respectively designated by the reference numerals 24, 25, 26 and 27, the ports 24 and 26 communicating with a pair of channels 28 extending longitudinally through the body of the valve 5 to the adjacent end thereof, and the ports 25 and 27 communicating with a pair of channels 29 which also extend longitudinally through the valve body and terminate in the adjacent end thereof. As in the case of the channels 19 and 21, the channels 28 and 29 terminate at their inner ends just inwardly of the ports 24 and 25. The arrangement of cylinders and ports described above is such that as the cylinder bodies 11 and 12 rotate, each cylinder of the respective series is alternately brought into communication with the associated oppositely arranged ports, and through said ports with longitudinal valve channels with which said ports communicate.

Suitably attached to the outer end of the cylinder body 12 within the end plate 3 is a gear 31, this gear being provided with an anti-friction bearing 32. Journaled in the end plate 3 on anti-friction bearings 33 and 34 is a shaft 35 which carries a pinion 36 meshing with the gear 31, the shaft 35 projecting through the end plate 3 and through a suitable stufling box 37 formed therein. The shaft 35 with the pinion 36 and gear 31 thus provide for rotation about the valve 5 and by an external power source (not shown) of the cylinder body 12. The valve body 12 at its inner end is also provided with a gear 38 which meshes with an annular series of pinions 39 carried by a) corresponding series of shafts 41 journaled in anti-friction bearings 42 in the partition 4 of the housing 1, the opposite end of each of the shafts carrying a pinion 43 which meshes with a gear 44 on the cylinder body 11, this gear connection between the cylinder bodies providing for rotation about the valve 5 and from the same external power source of the cylinder body 11, this body rotating in the same direction and at the same speed as the cylinder body 12. While the aforedescribed means for operatively connecting the cylinder bodies is a highly desirable one, it will be understood that other means may be employed without departing from the invention; and in fact there are to be no implied limitations as to the character of the driving mechanism as a whole.

Each of the cylinders of the four

series

13, 14, 15 and 16 is provided with a plunger, the pistons of the respective series being designated respec- 'tively 45, 46, 47 and 48. The pistons 45 are respectively pivotally connected by pins 49 with a series of slipper elements 51 slidably secured against the inner face of a ring 52, which ring forms the inner race for an annular series of roller bearings 53. As shown in Fig. 6, the slippers 51 are secured against the ring 38 by means of a pair of flanged retaining rings 54, 54 which are suitably secured to the ring 52 and which embrace the edges of said ring and the projecting edge portions or flanges 55 of the said slippers, the'latter being free to adjust themselves circumferentially in the inside of the ring 52.

The outer race for the bearings 53 is constituted by a ring 56 which is confined within an internal annular groove in a guide block 57 slidably supported in the housing. This block as shown in Fig. 5 has an outer substantially rectangular form corresponding to the rectangular form of the housing 1, and the block finds sliding bearings in the housing at 58, 58 and 59, 59 respectively, detachable wear plates or shoes 61 being interposed between the housing and the said block, and in the present instance being fixed to and movable with the latter. Guide pins 62 in the form of studs threaded into one side of the guide block extend slidably into

guide cylinders

63, 63 on the housing, and at the opposite side a rod 64 extending through a suitably packed opening in the side of the housing provides means for adjusting the guide block from the outside of the housing. It will be noted that the adjustability of said block affords an adjustment of the ring 52 and of the series of pistons connected thereto from a position concentric with the rotary axis of the cylinder body 11 to eccentric positions at opposite sides of said axis. In the concentric position of the ring, rotation of the cylinder body 11 results in no reciprocatory movement of the plungers in their cylinders. Movement into either of the eccentric positions, however, results in a reciprocation of the plungers. The ports 17 and 18 of the valve 5 are so arranged relative to this eccentric adjustment that the plungers act successively and progressively to evacuate oneof said ports and to apply fluid pressure to the other of said ports, depending on the adjustment with respect to the rotational axis of the cylinder body. In the adjusted position of the guide block shown in Fig. 5, the flow is as indicated by the arrows, the plungers functioning to withdraw fluid from the port 17 and the channels 19 and to subsequently discharge this fluid through the port 18 into the channels 21. An adjustment of the block 57 into the opposite position of eccentricity with respect to the rotational axis of the cylinder body will result in a reversal of the flow and a circulation of fluid from the port 18 to the port 17. The mode of operation of thistype of pump is well known in the art and requires no further description in defining the present invention.

The pistons 46 of the cylinders 14 are similarly operatively connected through slippers 51', ring 52' and bearings 53' with the block 57, so that any movement of this block affecting the pistons 45 similarly affects the pistons 46, the latter functioning as described above and depending on the position of eccentricity of the guide block to withdraw fluid from one or other of the ports 22-23 and to subsequently discharge the said fluid into the other of the ports.

The pistons 47 and 48 are similarly operatively ,from the exterior of the casing to eccentric posi tions at opposite sides of the rotational axis of the cylinder body 12 through the medium of a rod 66 extending through the side of the housing whereby fluid is withdrawn from the ports 24-26 and discharged into the ports 25-27, or vice versa, depending upon the adjusted position of the 'said block, all as previously described in connection with the cylinder body 11.

In the present instance, reference being had to Figs. 1 and 2 of the drawings, the adjusting

rods

64 and 66 are interconnected in such manner that their movements are synchronized. The rod 64 carries at its outer end a double rack 67, one side of which is engaged by asegmental gear 68 carried by a rock shaft 69 suitably supported in a bracket 71 on the housing. The opposite side of the rack 67 engages a gear 72 iournaled in the said bracket, and this gear also engages at its opopsite side a rack 73 at the outer end of the rod 66. With this interconnection, any actuation of the rod 66 through the shaft 69 and segmental gear 68 results in a corresponding and opposite adjustment of the rod 66. The arrangement is such that the two guide blocks 57 and 65 respectively connected as previously described to the

rods

64 and 66 may be simultaneously adjusted from a neutral position in which they are both concentric with the axis of rotation of the cylinder bodies 11 and 12 into corersponding positions of eccentricity at opposite sides of said axis. Synchronized adjustment of the guide blocks 57 and 65 and of the action of the two pump units respectively by the cylinder bodies 11 and 12 is thus provided for. In Fig. 9, I have illustrated the relative positions of the guide blocks in one eccentric adjustment. It will be understood, however, that the invention is not limited to such synchronized movement between the different stages of the pump, and for some purposes it may be of advantage to provide for independent adjustments of the said stages, as hereinafter more fully set forth.

With the arrangement and connection of parts described above wherein the said guide blocks are eccentrically adjusted to opposite sides of the rotational axis of the respective cylinder bodies, it will be apparent that the pump unit represented by the cylinder body 11 must necessarily affect those of the associated valve ports on the opposite side of the valve from the ports similarly affected by theunit represented by the cylinder body 12. The fluid pressure applied by the said units therefore operates on opposite sides of the valve 5, which in effect tends to substantially balance said pressures with respect to the valve and tends to maintain the latter in a position truly concentric with the rotational axis of the rotary parts. The pressure strains upon the entire mechanism are thus effectively neutralized.

In the adjusted positions of the guide blocks 5'7 and 65 corresponding to that illustrated in Fig. 5, the passage of fluid to and from the sides of ports 19, 21 and 28, 29 is as indicated by the arrows in Figs. 3 and 4. Through the medium of fittings 74 and '75 respectively connected to the opposite ends of the valve body 5 and pipes '76, '7'7, '78 and '79, the channels 19 and 29 are mutually connected with a main 81, while the channels 21 and 28 are mutually connected to a second main 82, the flow of fluid in these mains in the illustrated adjustment of the parts being indicated by the arrows in Figs. 2, 3 and 4. The units of the multi-stage pump described, therefore, operate jointly to circulate fluid in one direction or another, depending on adjustment of the parts as previously described through an external fluid system, of which the

mains

81 and 82 form a part.

A valuable feature of my invention is illustrated in Fig. 8, which shows a development of the cylinder bodies 11 and 12. As therein illustrated, it will be noted that the

cylinders

13 and 14 are circumferentially offset to a predetermined extent with respect to each other, as also are the cylinders 15 and 16. It will also be noted that the cylinders 14 are similarly offset circumferentially from the cylinders 15. The amount of offset between each pair of adjacent cylinders 1314, 14-15 and 15-16 is the same, and the arrangement is such that a like offset relation exists between the cylinders 13 and cylinders 16. Thisoffset relation of the cylinders provides for a substantially uniform distribution of the impulses of the cylinders around the axis of rotation, and effects a material reduction in vibration in the pump due to the action of the plungers in the pressure and evacuating strokes. A pump made in accordance with my invention is substantially free from vibration.

In conjunction with the pump mechanism described above, I provide a novel and highly advantageous system of force feed lubrication, this pump 83 operates through suitable piping 88 to withdraw oil from the make-up tank of the pump and to pass it to an elevated reservoir, from which the oil is withdrawn through a pipe 89 by the pump 84, all as indicated by the arrows in Fig. 3. Through a pipe 91, the pump 84 forces the oil to a channel 92 extending longitudinally in the upper part of the housing 1, and from this channel 92 the oil is distributed to the various operating parts of the pump.

Ports

93 and 94 conduct oil from the channel to recesses 95 and 96 in the tops of the guide blocks 57 and 65 respectively, from which recesses oil is passed through suitable ports to the bearings 53, 53' and to the corresponding bearings of the guide block 65, see Fig. 6. Oil is also passed from the recesses 95 and 96 down both sides of the guide blocks to the gears 8'7, 43 and 39 and to the bearings 6, '7, 8 and 9. Through a series of pipes 9'7 and 98 at the top of the housing, oil is also carried from the channel 92 to the upper bearings 58 of the guide blocks 5'7 and 65, the lower guide block bearings being lubricated by accumulations of oil in the bottom of the housing. Also from thebottom of the housing suitable pipes 99 conduct excess oil back to the make-up tank. From the end of the channel 92, see Fig. 6, a pipe 101 carries oil to a port immediately above the gear 36, this oil being distributed also to the bearings 82, 33 and 34, and eventually accumulating in the bottom of the unitary chamber 102 of the casing end plate or head 3. From this chamber, the oil is forced through a pipe 103 to a central channel 104 in the valve body 5, this channel extending the full length of the valve and. being closed at the opposite end by a suitable plug 105. From this channel, passages 106extend to recesses 107 in the peripheral surface of the valve body 5, thereby providing adequate lubrication to the contacting surfaces of the said valve and the rotary cylinder bodies 11 and 12. A feature of this system of lubrication resides in the fact that lubrication of the contacting surfaces of the valve 5 and the cylinder bodies 11 and 12 continues during such periods as the guide blocks 5'7 and 65 are in the concentric or neutral position.

A desirable modification of my invention is illustrated in Figs. 11 and 12, in which the guide block designated 57 is mounted in the housing upon rollers 108 which replace the sliding bearings 58 and 59 illustrated in the preceding embodiments. As illustrated in Fig. 12, the rollers 108 are mounted in adjacent pairs upon shafts 109 supported at the corners of the guide block, and

each roller is provided with an anti-friction bear-' ing 111, which bearings are confined between the rollers proper and the shaft 109. The faces of the rollers arerecessed for reception of themeversely formed tracks 112 upon which the said rollers operate, thus resisting side thrust and maintaining with the guide studs 62 and the operating rods 64' a true alignment of the parts.

It will be noted in this ins ance also that the;

single operating rod 64 of the prior described embodiment is replaced by two vertically spaced guide rods 64', 64'. The aforedescribed method of mounting materially facilitates adjustment of the guide blocks.

A pump made in accordance with my invention has many advantages over prior pumps operating on the same general principle. By providing the multi-stage effect, it is possible for a given'pump capacity to materially reduce the circumferential dimensions of the rotary parts. The peripheral velocities of the rotary parts are thus correspondingly reduced, permitting relatively light construction and greater durability under heavy load conditions. A pump constructed in accordance with my invention also possesses a superior and highly desirable flexibility of control, in that where the guide blocks of the units or stages are independently adjustable, the volumetric output of the pump may be maintained simultaneously with a predetermined increase or decrease in power output. This flexibility of control finds a valuable application where the pump is used as the prime mover of a fluid motor, in that with a constant pump delivery, the speed of the motor may be accurately regulated over a wide range. A further advantage previously mentioned also resides in the ability to adjust the units of the multi-stage pump in opposite phases applying pressure to opposite sides of the valve 5, which balances the pressures on the cylinder bearings and other rotary parts and tends to maintain true alignment of the valve.

While I have herein illustrated for the purpose of broadly describing my invention a pump having four sets of cylinders or pump units, it will be apparent that there is no limitation in this respect, and that following the general principles set forth, a pump may be constructed having fewer or a greater number of units as required; and that these units further may be assembled in sets, as illustrated, or individually withoutdeparture from the invention. The invention in principle is capable of many embodiments other than that herein illustrated, and there are to be no limitations except as imposed by the terms of the following claims.

I claim:

1. In a pump of the stated character, the combination with a housing, of cylindrical valve means supported within said housing, a pair of cylinder bodies concentric with said valve and each having a series of radial cylinders, said valve means having ports respectively cooperative with the cylinders of the respective bodies, and means for rotating the cylinder bodies in the housing including a geared transmission operatively connecting said bodies, said geared transmission being mounted independently of and in spaced relation with said valve.

2. In a pump of the stated character, the combination with a housing, of cylindrical valve means supported in said housing, a pair of cylinder bodies mounted in said housing concentric with the valve means, each of said cylinder bodies having a series of radial cylinders and the valve means having ports in operative association with said cylinders, a gear associated with each of said bodies, a shaft journaled in the housing and having secured thereto pinions respectively meshing with the said gears, and means for rotating one of said bodies in the housing.

3. In a pump of the stated character, the combination with cylindrical valve means supported within the housing, of a pair of cylinder bodies concentric with said valve means and each having a series of radial cylinders, said valve meanshaving ports adapted respectively to register with the inner ends of the cylinders of the respective bodies, a gear carried by one of said bodies, and means for connecting said gear with a source of power, a second gear carried by said body, a corresponding gear carried by the other of said bodies, and a shaft journaled in the housing and having secured thereto a pair of pinions meshing with the two last-named gears whereby rotation of the first of said bodies from the source of power results in a rotation of the other body.

4. A pump of the stated character comprising a housing, a cylindrical valve mounted in said housing, a pair of cylinder bodies embracing and concentric with the valve and each having a series of radial cylinders, ports in said valve adapted respectively to register with the inner ends of the cylinders of the respective bodies, a gear carried/by each of said bodies, an annular series of shafts journaled in said housing and each having secured thereto a pair of pinions meshing respectively with the gears of said bodies, and means for rotating said bodies in the housing.

5. In a pump of the stated character, the combination with a housing, of cylindrical valve means supported within said housing, a pair of cylinder bodies concentric with said valve means and each having a series of radial cylinders, said valve means having independent sets of ports respectively operatively associated with the cylinders of the respective bodies, and each of said sets of ports comprising a pair of ports arranged at opposite sides of said valve means, pistons in thecylinder bodies, means for relatively rotating the valve, means and said cylinder bodies, and means for actuating said pistons in the bodies whereby fluid is withdrawn from a port of one of said sets and from the oppositely arranged port of the other of said sets andis subsequently discharged into the remaining ports of the respective sets.

6. In a pump of the stated character, the combination with a housing, of cylindrical valve means supported in the housing, said valve means comprising independent and corresponding sets of oppositely arranged ports, a cylinder body operatively associated with each of said sets of ports, means for relatively rotating said bodies and the valve means, and means for simultaneously withdrawing fluid from a port of one set and from the opposite port of another set and for subsequently discharging said fluid into the opposite ports of both of said sets whereby fluid pressure is applied simultaneously to opposite sides of the valve means. i

7. In a pump of the stated character, the combination with a housing, of cylindrical valve means supported within the housing, a pair of cylinder bodies concentric with said valve means and each having a series of radial cylinders, said valve means having for each cylinder body a pair of oppositely arranged ports, pistons in said cylinders, means for relatively rotating the valve means and said cylinder bodies, and means for actuating said pistons to circulate fluid through the associated ports, one port of each set and the oppositely arranged port of the other set constituting discharge ports, and the other port of each set constituting suction ports whereby fluid pressure is applied simultaneously to opposite sides oi the valve.

8. In a pump of the stated character, the combination with a housing, of cylindrical valve means mounted in said housing, said valve means having in its periphery two sets of oppositely arranged ports, a pair of cylinder bodies embracing and concentric with said valve means and each having a series of radial cylinders for operative association respectively with said sets of ports, means for relatively rotating the valve means and the said bodies, and means including said cylinder bodies for simultaneously withdrawing a fluid from those of the ports of the respective sets at opposite sides of the valve means and for subsequently discharging said fluid into the remaining ports or the respective sets.

' 9. In a pump of the stated character, the combination with a housing, of cylindrical valve means mounted in said housing,said valve means having independent sets 01' oppositely arranged ports, cylinder bodies mounted insaid housing concentric with the valve means and each having a series of radial cylinders in operative association with said sets of ports respectively, means operatively associated with one of said cylinder bodies for withdrawing fluid from one of the ports of the associated set, means operatively associated with the other of said cylinder bodies for withdrawing fluid from the opposite port of the other of said sets, and means operatively associated with each of said cylinder bodies for subsequently discharging the withdrawn fluid into the other part of the associated set.

10. In a pump of the stated character, the combination with a housing, of cylindrical valve means mounted in said housing, said valve having independent sets of oppositely arranged ports, cylinder bodies mounted in said housing concentric with the valve means and each having a series of radial cylinders in operativeassociation with said sets of ports respectively, means operatively associated with one of said cylinder bodies for withdrawing fluid from one of the ports of the associated set, means operatively associated with the other of said cylinder bodies for withdrawing fluid from the opposite port of the other of said sets, means operatively associated with each of said cylinder bodies for subsequently discharging the withdrawn fluid into the other port of the associated set, and means for connecting the suction and discharge ports of one of said sets respectively to the suction and discharge ports of the other of said sets.

11. In a pump of the stated character, the combination with a housing, of cylindrical valve means mounted in said housing and having a plurality of sets of oppositely arranged ports, cylinder bodies within said housing rotatable about the valve means and each having a series of radial cylinders in operative association respectively with said sets of ports, means for relatively rotating the cylinder bodies and the valve means whereby the ports of the sets are brought successively into communication with each cylinder of the associated series, mechanism operatively associated with the cylinder bodies for withdrawing a fluid from one of the ports of the associated set and for discharging the fluid into the other of said ports, and means for adjusting said mechanism whereby the discharge ports of two of said cylinder bodies lies on opposite sides of the said valve means.

12. In a pump of the stated character, thecombination with a housing, of cylindrical valve means supported in said housing, a plurality of independent cylinder bodies embracing said valve means and concentric therewith, each of said bodies having a series of radial cylinders and said valve means having a plurality of sets of ports adapted respectively for communication I with the cylinders of the respective series, transmission gearing in said housing operatively con necting said cylinder bodies whereby the motion of one of said bodies is transmitted to another, pistons in said cylinders, a supporting annulus forthe pistons of the respective series and adjustable to positions concentric and eccentric to the axis of rotation of the associated cylinder body, and means for simultaneously adjustin said annular supports inopposlte directions with respect to the concentric position.

13. In a pump or the stated character, the combination with a housing, 01! a cylindrical valve element mounted in said housing, said element having a plurality of sets of ports, a plurality of cylinder bodies mounted for rotation in the housing about the valve, each of said bodies having a series of radial cylinders, which series are respectively adapted for communication with the said sets 01' valve ports, transmission gearing in said housing operatively connecting said cylinder bodies whereby the motion of one of said bodies is transmitted to another, pistons in said cylinders, means for controlling the operation of said pistons including an annular member operatively associated with the pistons of each series and adjustable to positions concentric and eccentric with the axis of rotation of the associated cylinder body, means for simultaneously adjusting said annular members in opposite directions with respect to the concentric position, and means for rotating said bodies in the housing.

14. In a pump of the stated character, the combination with a housing, of cylindrical valve means mounted in said housing, a plurality of cylinder bodies mounted in said housing concentric with and embracing said valve means, each 105 of said bodies having a series of radial cylinders, ports in said valve cooperative with the cylinders of the respective series, pistons in said cylinders, means for relatively rotating the valve means and the cylinder bodies, an annular member operatively associated with the pistons of each series and adjustable to positions concentric and eccentric with the axis of rotation of the associated cylinder body, and means for simultaneously adjusting two of said annular members in opposite directions with respect tothe concentric position.

15. In a pump of the stated character, the combination with a housing, of cylindrical valve means mounted in said housing, a plurality of 120 cylinder bodies mounted in said housing concentric with and embracing said valve means, each of said bodies having a series of radial cylinders, ports in said valve cooperative with the cylinders of the respective series, pistons in said cylinders, means for relatively rotating the valve means and the cylinder bodies, means for actuating the pistons including an annular member operatively associated with the pistons of each series and adjustable to positions concentric and eccentric with the axis of rotation of the associated cylinder body, operating rods for said annular mem-' bers projecting through the wall of the housing, mechanism associated with the projecting end of one of said rods for adjusting the associated 135 annular member in the housing, and means interconnecting the last-named rod with another of said rods whereby adjustment of the rod first named results in a corresponding and opposite adjustment of the rod interconnected therewith. 140

16. In a pump of the character described, the combination with a housing, of cylindrical valve means supported within said housing, a cylinder body embracing and concentric with said valve means and having a series of radial cylinders, 145 said valve means having a pair of ports in opposite sides thereof adapted for communication with the cylinders, of said series, pistons in said cylinders, means for relatively rotating the valve means and the cylinder body, and means for ac- 150 tuating said pistons in the cylinders including an annular member operatively associated therewith and adjustable from a position concentric with said cylinder body to eccentric positions at opposite sides of the concentric position, adjustment of said annular member into one of said eccentric positions effecting a flow of fluid from one of said valve ports to the other, and the other of said eccentric adjustments reversing the direction of flow in said ports, a second cylinder body in said housing concentric with the valve and having a series of radial cylinders, said valve having a second set of ports at opposite sides thereof for communication with the last-named series of cylinders, mechanism for relatively rotating the cylinder body and the valve member, pistons in said cylinders, and means for actuating said pistons including a second annular member operatively associated therewith and adjustable from a position concentric with the cylinder body to opposite positions of eccentricity, and means for operatively associating the firstnamed annular member with the second-named annular member whereby an adjustment of one of said members effects a corresponding and opposite adjustment of the other of said members. W. In a pump of the stated character, the combination of a pair of pump units each comprising a cylindrical valve element, a cylinder body embracing and concentric with said valve element and having a series of radial cylinders, said valve element having a pair of ports in opposite sides thereof for communication with said cylinders, pistons in said cylinders, means for relatively rotating the cylinder body and the valve, and means for actuating the pistons to withdraw a fluid from one of said ports and to discharge said fluid into the other of said ports, said actuating means comprising an annular member associated with said pistons and adjustable from a neutral position concentric with the cylinder body to an eccentric position, and means for interconnecting the annular members of the two units whereby an adjustment of one effects a corresponding and opposite adjustment of the other.

18. In a pump of the stated character, the combination with a pair of pump units comprising a common cylindrical valve element, each of said units in addition including a cylinder body embracing and concentric with said valve element and having a series of radial cylinders, said valve element having a pair of ports in opposite sides thereof for communication with said cylinders, pistons in said cylinders, means for relatively rotating the cylinder body and the valve, and means for actuating the pistons to withdraw a, fluid from one of said ports and to discharge said fluid into the other of said ports, said acelement, a support for said element in the housing adjacent each end thereof, a support in said housing for the valve intermediate the supports first named, cylinder bodies embracing the valve element at opposite sides of the last mentioned support, pistons in said cylinders, means associated with the pistons of each cylinder body for causing the operation of said pistons in the cylinders, and means for simultaneously adjusting the first mentioned means in opposite directions to effect corresponding and simultaneous operations of the pistons of both cylinder bodies.

20. In a pump of the stated character, the combination with the housing, of cylindrical valve means supported within said housing, a pair of cylinder bodies concentric with said valve means and each having one or more series of radial cylinders, said valve means having ports adapted respectively to register with the cylinders of the respective bodies, means in said housing intermediate the cylinder bodies lfOI supporting said valve means, means for relatively rotating one of said cylinder bodies and said central valve, and transmission means mounted in said housing independently of said cylindrical valve, and operatively connecting one of said cylinder bodies with the other whereby any movement imparted to one of said cylinder bodies will be simultaneously imparted to the other.

21. In a pump of the stated character, the combination with a housing, of a cylindrical valve means supported within said housing, a plurality of cylinder bodies concentric with said valve, and each having one or more series of radial cylinders, said valve means having a plurality of ports adapted respectively to register with the inner ends of the respective cylinder bodies, a partition in the housing intermediate adjacent cylinder bodies for supporting the intermediate portion of said valve, means for relatively rotating one of said cylinder bodies and said valve means, and transmission means mounted in said partition independently of and in spaced relation with said valve means, said transmission ALBERT R. KUZELEWSKI.

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