US2166114A - Variable displacement pump or motor - Google Patents

Description

v July 13, 1939- E.` K. BENEDl-:K 2,166,114

VARIABLE DISPLACEMENT PUMP 0R MOTOR Filed DSC. 24, i934 7 Sheets-Sheet 2 @WML 46) 49 ELEKKEJENEDEK.. ,l p m/ July 18, 1939. E. K. BENEDEK 2,166,114

VARIABLE DISPLACEMENT PUMP OR MOTOR Filed Dec. 24, 1934 7 Sheets-Shea?l 3 July 18, 1939. E. K. BENEDEK VARIABLE DISPLACEMENT PUMP OR MOTOR 7 Sheets-Sheet 4 Filed Dc. 24, 1934 v ELEKKBQIEDEK TE E f- 1' .JJ .55, I

July '18, 19.39. E. K. BENEDEK "IT-115-15- ELEKKEENEDE- A @a4 i Ta-E1- '512D Patented July 1 8, 1939 UNITED' STATES PATENT OFFICE VARIABLE DISPLACEMENT PUDIP OR MOTOR 18 Claims.

This invention relates to variable displacement pumps and motors of the radial piston or plunger type having a. primary and secondary rotor and the principal object is to improve the eiciency andV pressure capacity of 'such mechanisms.

An object is to provide a new and improved arrangement for connecting the pistons with the necessary reactance means for reciprocating the pistons.

Another object is to arrange the cooperative relationship between the reactance means and the pistons in a manner such that al1 moments of the resultant forces are resisted by reactionary u forces vset up in the reactance means without reactionary forces between the pistons and their supporting walls.

A correlative object is to arrange these elements relative to their respective rotors in a manner such that the reactionary forces on the respective rotors which might tend to cause moments of one rotor with respect to the other are directed parallel to each other and through` the axes of the respective rotors whereby the forces acting on either rotor are balanced therein and do not create relative moments of one rotor with respect to the other.

Another object is to provide a piston crosshead thrust plate arrangement capable of being ad- Justed so that the pump or motor operates without any binding whatsoever and which is adapted to be simply and denitely locked in proper position to secure such freedom of operation.

A further object is to provide a hydrostatically balanced'variable stroke mechanism operable as a pump or motor and having a new and improved piston operating reactance arrangement.

A further object is to provide for the reduction of bending stresses on the necessary thrust connections between the reactance means and pistons.

Other objects and features, including thelgeneral simplicationof pump or motor design of `the class referred to, will become apparent from the following description of the invention with reference to the accompanying drawings.

Referring briefly to the drawings:

Fig. 1 is a plan view of an entire pump or motor mechanism showing the fluid feed connections and impeller shaft;

Iig. 2 is a central longitudinal fragmentary sectional view showing the main working parts (pintle, primary rotor or barrel and secondary rotor comprising two-face plates and support Il therefor) of one form of pump or motor according to Fig. 1, the section being indicated by the line 2 2 on Fig. 1;

Fig. 3 is a transverse sectional view corresponding to Fig, 2 and as indicated by the line 3 3 on Fig. 1 and line 3a--3a on Fig. 2;

Fig. 4 is a sectional view taken substantiallyalong the line 3b 3b of Fig. 2 but with all the pistons and crossheads removed so as to show'one face plate in elevation and the entire set of thrust plates in section;

Fig. 5 is an enlarged view showing a piston and its crossheads in the manner of Fig. 3, but with the piston inclined (exaggerated) with respect to the crosshead proper to' show the, preferred iiexible connection between the pistons and crossheads;

Fig. 6 is a view of one piston and its crosshead shown in the manner of Fig, 3, but with the thrust plate at one side of the crosshead as when the reactance assembly is adjusted eccentrically of 20 the primary rotor;

plates and radially opposite sides of slots in the :l0l

crossheads, the views being respectively indicated by the lines 8 8 on Fig. 9 and 9 9 on Fig. 8;

Fig. 10 is a plan view of the needle bearing assembly including the cage arrangement of Figs. 8 and 9;

Figs. 11 and 12 are side and end elevations respectively of the thrust plate arrangement of Figs. 2 to 4;

Fig. 13 is a fragmentary side elevation of the -outer end of one of the pistons in the arrange- 40 ment according to Figs. 5 and 6;

Fig. 14 is a fragmentary sectional view of a modified crosshead and reactance connection means, the view corresponding to the showing at the upper portion of Fig. 2; 45

Fig. 15 is a view of said modified form of ma- L chine taken along the line |5 -I5 on Fig. 14, this view corresponding in general to Fig. 3;

Fig. 16 is a diagram showing the forces operat-j r piston and crosshead according to Figs. i4 and l5, the view being taken along the line I8-I8 on Fig. 14;

Fig. 19 is a fragmentary sectional view taken along the line I9-I9 on Fig. 14;

Figs. 20 and 21- are side and end elevations respectively of the needle roller bearings employed, for example, in the arrangement of Figs. 14 and 15 to support the ends of the crosspins;

Fig. 22 is a longitudinal fragmentary sectional view taken on the line 22-22 on Fig. 23 of still another modified machine, the view corresponding in general to Fig. 2;

Fig. 23 'is a transverse sectional view taken along the line 23--23 on Fig. 22; and

Fig. 24: is a' fragmentary sectional view of a portion of one of the rotary reactance plates, the section being taken at 24-24 on Fig. 22; and

Figs. 25 and 26 are diagrams showing the forces imposed by the piston operating connections between the primary and secondary rotors in an exemplary form of my improved mechanism acting as a pump.

In all forms of the invention shown-the piston crossheads are connected with the reactance means in such manner that the combined piston operating forces are distributed to the pistons and crossheads purely radially of the piston carrier 0r rotor. In all forms antifriction needle bearings of the capillary vtype are used to eliminate all sliding friction in the necessary generally tangential relative movement between the piston and reactance means connections.V

The actual crosshead connection is shown in three types. In the first to be described, thrust plates are provided in slots in the crossheads and antifrictional bearings are interposed between bothsides of each thrust plate and the adjacent 'walls of the slot in each crosshead. a sufficient number of the bearings to carry the load being always in line with the pistons. In the second solution of the problem the thrust plates are replaced by two or more crosspins, each antifrictionally journalled infixed sockets in the face plates. Here again the operating forces on the pistons are truly radially of the piston' carrier. In the third solution two or more crosspins are antifrictionally journalled directly in the crossheads and the ends of the pins ride in suitable slots which may be very easily formed in the face plates of the reactance rotor as will be shown below.

' I as by bolts 5, two of each set of bolts being shown. 'I'he main fluid feed 'connections Aare associated with the casing part 2 having an ,enlarged hub 6 carrying the pintle I0, the hub having ports at each side receiving the mains Iand 8, the latter being interchangeably used as pressure and discharge uid lines. Y

y Referring to Fig. 2, valve pintle I0 has a relatively enlarged portion I I, press tted. e. g., into a central axial bore of the hub 5 andis prevented from outward movement (to the left)V with respect to the hub by a shouldered flange I2 on the pintle adapted to abut the adjacent end wall ysurface of the hub. The working surface of dle rollerA assemblies I'I and.- I1' for normally mechanically preserving uniform clearance all around the pintle working surfaces while allowing free passage of the Working fluid past the bearings. The rotor 25 has a central bore 20 receiving the pintle, the bore terminating at 20' forming a closed chamber 2I adjacent the inner end of the pintle. The central portion 20 of the bore is hydraulically fitted to the pintle surface I5 and respective portions of the bore form suitable raceways for the bearing assemblies I1 and I'I. The pintle ports are shown at I8 in the working section of the pintle. The impeller shaft of the rotor, indicated at 3|, extends outwardly through a suitable central opening in the end plate 3 of the casing.

The mounting for the primary rotor or piston barrel 25 comprises antifrietion bearings 26, these having inner and outer races 28 and 29 respectively Iaxially abutting accurately formed surfaces on or in the casing section 2 and 3 respectively and shouldered end portions of the barrel. The bearings may be adjustable and are vdesigned for both radial and axial thrust. Suitable means (not shown) for taking up the axial thrust and thereby all play in the bearings, may be provided-for instance in accordance with my prior application Serial No. 754,753, led November 26, 1934.

My said prior application discloses an arrangement for truly balancing the hydraulic forces between the working sections of the pintle I0 and rotor bore 20 and this comprises a working uid feed duct 30 centrally of the pintle which discharges into the space 2I between the end of the rotor bore and the pintle. lThe duct 30 is communicated, as shown in my said application, with the pressure line side of the machine s that, during the entire running operation of the machine, the working fluid is forced into and along the perimetral space between the pintle androtor bore, which space is initially maintained mechanically by the pilot bearings I1 and I 'I'.

The pistons 35, Figs. 2 and 3, operate in radial cylinder bores 35. having reduced port outlets at 36' leading to the bore 20 of the barrel and adapted to register with the pintle ports I8 which latter communicate with respective axial feed ,and/or discharge ducts I9 (Fig. 3) in the pin` tle. The pistons preferably have two or three part crossheads so as to allow axial deflection of the crossheads proper .with respect to the working portions of the pistons. As shown, see also Figs. 5- and 6, the piston crossheads comprise blocks 40 relatively wide in the plane of the pistons and relatively narrow transversely, the blocks being slidable in radial ways 4I in a central drivingflange 42 of the rotor, see particularly Fig. 2, the flange being centrally disposed with respect to the transverse plane of the pistons" and extending to theouter ends of the crosshead elements when -the barrel is in concentric relation The crossheads, on their inner sides, toward the pistons, have transverse channels 43 each provided with two underlianging lips 44. The channels 43 are formed to receive thrust blocks 45 which accurately t Ithe channels on three sides,

the fourth side being arcuately surfaced as at 46 complementary to the arcuate surface 41 on the. enlarged head portions 48 of the pistons. Preferably the heads 48 and the mating surfaces of the blocks 45 are arcuate transversely as Well as in planes parallel to the general plane of the Ito the reactance assembly as shown in Fig. 3.

pistons, this being shown in Fig. 10, so that, in -75 the event of disalignment between the pistons and crossheads in either intersecting central normal plane of the piston axes, there will be no binding between the pistons .and the crossheads. Preferably there is sufficient clearance (several thousandths of an inch) between the under sides of the piston head formations 48 and the lips Il as diagrammatically indicated at 49, Fig. 5, so that the maximum expected deflection under maximum torque force T will not cause the pistons and crossheads to bind in their respective guideways inwardly from the head portions-toward the axis of the barrel:

The reactance means operating on the crossheads comprise. as shown, face plates 50, one at each side of the radial flange I2 and close thereto. These face plates have annulan disc-like flange formations at 5I lying adjacent the driving flange 42 and tubular flanges 52 for engagement with a suitable rotary support. As shown, the support comprises ball bearing assemblies, one for each face plate and the assemblies include balls 55 and inner and outer rings 56 and 51. The outer bearing ring members 51 are suitably secured in a. common adjustment ring 56,-

part only of which is shown but which, as shown in my said prior application, is mounted to slide in general casing transversely of the pintle and cylinder barrel axes. The adjustment means may comprise suitable bars arranged on opposite sides of the adjustment ring and projecting into the casing through suitable aligned bores therein, one of such bores being indicated at 59, Fig. 1.

Each of the face plates, as shown in Figs. 2 and 4, is arcuatelyv grooved as at 60 adjacent the crossheads 4U and the crossheads are transversely slotted as at 62 for receiving thrust plates 63, the opposite ends 65 of the thrust plates extending into the respective grooves 60 of the face plates. As shown, each thrust plate has a central portion which has planar parallel surfaces on the opposite sides radially of the'machine. These planar surfaces extend only to the lateral limits of the crossheads and beyond these limits, in both directions axially of the machine, the thrust plates are arcuately formed as at 65a and 65h to fit the slots 60 for circumferential adjustment therein. The detailed construction is best illustrated in Figs, l1 and 12. 'Ihus the thrust plates are fully supported over wide areas in the grooves Y 60 of the face plates and are nevertheless adjustable circumferentiallyl for initial setting in proper position.

' If the thrust plates are to be secured rigidly in the face plates as contemplated in this embodiment it is necessary that the slots 62 in the crossheads be wide enough to permit tangential movement of the thrust plates in both directions from a central position, the distance being determined by the maximum eccentric adjustment of the main adjustment ring carrying the thrust plates. It is, moreover, necessary to provide some means vfor guidingthe crossheads on .the thrust plates. Heretofore in arrangements of this type, the thrust plates were merely made to fit the slots and slide directly thereon with great frictional` waste. I provide instead a series of antifriction needle bearings of the capillary type between both the inner and outer surfaces of the thrust plates and the outer and inner slot surfaces of the crossheads. These needle bearings are indicated at 61 and 68 and are mounted in the bearing space so that they may freely rotate with respect to each other in rolling contact with the Iuntil the barrel turns entirely freely.

thrust plate and crosshead surfaces. With this in view I provide a general cage for each series of needle bearings as shown in Fig. 13, see also Figs. 8 and 9. Fig. 13 shows side rail members 1l! connected by end rail members 1| forming a complete cage. The disposition of the rollers in the reactangular cage is such that the rollers are, at no time, tight in the cage, that is, pressed against each other. This may be accomplished by rst illling the cage and then removing one or two rollers. l

Preferably the side rail members 10 overhang and underhang the ends of the'needle bearings and this will, of course, necessitate clearance spaces for the overhanging and underhanging parts of the cage. For the sake of clearness of illustration no cages or clearance spaces are shown in Figs. 2 and 3.

For greater rigidity and accuracy of operation the face plates 50, particularly the disc-like flange formations 5l thereof, are secured to each other through the medium of suitable transverse bolts 13 which may have suitable spacing sleeves 14, see Fig. 7, the spacing sleeves preventing sliding contact between the inner faces of the face plates and the adjacent faces of the driving flange and the crossheads. 'I'he securing bolts pass through enlarged openings 15 in the radial driving flange, the openings being large enough to admit free circular movement of the securing bolts and spaces therein incident to the relative eccentricity of the face plates and cylinder barrel.

It will be noted that the thrust plates, notwithstanding the arcuate ends, are insertable through the crosshead slots, the bearings being put in afterward.

- When the rossheads, pistons, thrust plates and bearings are assembled and the face plates brought into position with-respeetto+the ends of the thrust plates, the thrust plates may then be nicely adjusted circumferentially of the machine the ends of the thrust plates may be' locked as by appropriate set screws 16, see particularly Figs. 2 and 4, the set screws engaging the arcuate end portions of the thrust plates at any suitable position, preferably centrally thereof as indicated in Fig. 4. Additional separate locking screws (not shown) may be provided to held the set screw in place,

It will be seen that when the thrustplates are fastened firmly in this manner the forces acting on the piston are such that the piston is subjected only to a direct axial thrust and the rotors themselves do not tend-to build up moments with respect to each other which,A did such exist, would have to be withstood bythe pistons and crossheads which constitute the only driving connection between the rotors.

Referring rst to Fig. 25, these'forces and reactions, insofar as they affect the rotors them- Thereafter ,-g

selves are diagrammaticallyv illustrated. The" force Fes is directed radially of the secondary rotor, that is, directly through the .eccentric C2. This force is balanced by an equal and opposite reactionary force F'sa through the eccentric axis Cz and along the centerline of the thrust -piate Yor reactance means 63. Thus the force F63 produces no moment of the. eccentric rotor but the entire thrust is taken directly in the bearings 55 (see Fig. 2) which are concentric with the secondary rotor about the axis Cz. The reactionary force Rss of the -pist'on is necessarily along the axis of the piston which passes through the center Ci of the primary rotox and is resisted by the v their respective rotational axes and are passed directly to the bearings and 26 (Fig. 2) respectively. These forces, insofar as they tend to create moments of one rotor with respect to the other.

are thus rendered ineffective and disposed of once and for all.

Referring next to Fig. 26, the effect of the forces, insofar as they concern the pistons, the I thrust plates 63, and crossheads, are illustrated. In this instance, the force Fes is balanced by a reactionary force R63, both of which, due to the f-act that any rocking or twisting of the plate 63 is resisted in the eccentric rotor itself, are parallel to the center line P of the piston. Both forces, however, are offset from each other an amount equal to the instantaneous eccentricity e. Therefore, were the plate 63 free to rock about a transverse axis, such as indicated at Y, the piston 36 or crosshead I0 would have to resist a moment equal to F63 times e, e being the instantaneous eccentrieity, which moment would tend to cause reactionary forces X between the pistons and crosshead and their respective guiding guide walls with resultant wear on all of these' members and the walls. In other words, if the plate 63 were free so to rock, the reactionary forces C and D, which in the present structure are provided in the secondary rotor, would be transferred and applied as the reactions X. It will be seen, therefore, that xing the plate 63 so that it cannot rock provides the reactances C and D between the secondary rotor and plate 63 so that the reactarices X are unnecessary. for completing equilibrium of the forces. The pistons and crossheads, therefore, are entirely free from reactionary forces, such as indicated at X, tending to cause wear of. either or locking.

In this particular embodiment of the invention, therefore, the forces acting on either rotor are balanced therein and do not create relative moments of one rotor with respect to the other, and the forces applied to the pistons are so directed that they do not impose any side thrusts on the pistons and crossheads.. The sameI results are accomplished in the other embodiments herein illustrated, as will be readily apparent from the foregoing detailed analysis.

In the second solution of the problem, see Figs. 14 to 20 inclusive, the thrust plates are replaced by individual cross-pins 80, a plurality of which are provided for each crosshead. These are balanced in the slots 82 in the crossheads on opposite sides of the piston axes and in the case of using three crosspins, one is centrally disposed with respect to the piston'and the other two are disposed equal distances from the central pin but spaced from the ends of the slots for the required relative travel of the crossheads and pins. The intermediate portions of the crosspins roll freely in the slots 82 and the ends of the pins are xedly secured in the face plates in needle bearing assemblies 84, so that, though the pins 80 may rotate freely about their respective axes, the resultant assemblages of pins, taken as a single thrust means, cannot rotate bodily. As shown, these needle bearing assemblies have separate bushings 85 in appropriate bores in the face plates 50 and, if desired, the needles may be closed in by suitable annular plates (not shown) ing the bearings of lubricant. Here again the races are not entirely filled with the needles (packed in) but adequate space is provided so that the needles always roll freely. It will be l noted that the pins are 'relatively short and that the face plates are made to ride almost directly on the crosshead surfaces, only a few thousandths clearance being provided between the inner face plate surfaces and the axially facing crosshead surfaces. Thereby bending strains on the crosspins 80 are minimized. As indicated in Fig. 16, the outward pressure forces of the pistons, shown by arrows at A, oppose the inward forces of the reactance means, indicated at B; the two sets of forces subjecting the pins to shearing stresses .only at the almost negligible unsupported portions.

With reference to Fig. 18, it will be seen that on relative tangential movement between the cross pins and face plates the pins simultaneously roll on either the inner or outer faces of the slots 82 depending on whether the pistons ar'e effecting their pressure or suction strokes (see arrows 802) indicating the rotation. o'f the pins-say on the inner slot surfaces when the crosshead moves according to the arrow 80a oneasier to locate the bores for the bushings 85 as on an indexing machine head, where such arcuate arrangement of crosspins is used.

Referring now to the third solution, Figs. 22 to 24, this comprises the same general arrangement of crosspins 80 but the needle bearings 84' are supported directly in the crossheads 40 instead of in the face plates. Again annular plates (not shown) may be provided to close the bores adjacent the needle ends and the needles are provided with sufficient total clearance that free rolling of the needles is assured. The device is somewhat simpler than that previously described partly in that it reduces the number of needle bearing assemblies necessary for a complete installation and, moreover, it simplifies machining of the face plates 50. It is easier to form the slots 85 in the face pl-ates for receiving the ends of the crosspins 88" as on an indexing fixture for an end milling machine, rather th-an having to breach the crossheads to form such slots. It is also contemplated that instead of chordal slots 85, such as shown inr Fig. 24, single circumferential slots comparable to the slot in Fig. 4 may be used to support -the ends of the crosspins 80'. If the slot is continuous the reactance assembly E50- 55, ctc., has to be started in rotation whenever the machine begins operating. Such initiation of rotation may be accomplished by the spacers 14 on the .securing bolts 13, these engaging the enlarged openings 15 of the driving flange to start the reactance assembly rotating in any eccentric `adjustment of the said assembly relative to the cylinder barrel.

I claim:

1. In a Variable displacement pump or motor of the radial piston type, a easing, primary and secondary rotors in the casing, one carrying a set of pistons and crossheads and radial guides for the crossheads and the other paired reactance means for the crossheads and having radial walls, the crossheads being disposed between barrel in the zone of the cylinder, a radial guide- Y the radial walls of the reactance means in slid'- on lall 4sides to maintain the4 rollers grouped in' ing relation thereto, slots in the radial walls of the reactance means extending past the crossheads in both directions circumferentially thereof, thrust plates having tangential portions guided in the crossheads respectively for oscillation therein tangentially of. the machine, said thrust plates having end portions received in said slots of the reactance means,`and means for securing the plates in said slots in fixed circumferential -position Arelative to the reactance means, said slots and last named means constraining the ranged generally tangentiallyof the machine, and

having planar surfaces generally normal to the piston axis, thrust plates extending through said slots and having their ends anchored in respective face plates and constrained thereby from .bodily rotation relative thereto, said thrust plates having planar surfaces opposite the planar `surfaces of the crosshead slots, a series of free capillary needle rollers disposed between said planar surfaces of the thrust plates and of the slots, and means loosely embracing the rollers position in line with the pistons.

ment radial piston type, a primary rotor and valve plntle therefor, cylinders and pistons carried by said rotor, crossheads for the pistons, a secondary rotor comprising face plates embrac-i ing the crossheads on opposite sides thereof, means to support said rotors for relatively eccentric adjustment, slots in said crossheads having radially opposite planar tangential surfaces, thrust plates having .opposite planar tangential surfaces disposed in said slots, said plates having their opposite ends` anchored in said face plates and constrained from movement relative to the face plates, and capillary needle rollers interposed between the planar surfaces of the crosshead slots and thrust plates in alignment with the pistons.

4. In a pump or motor of the radial piston variable displacement type, a primary rotor, pistons carried by the primary rotor, a valve plntle cooperatively arranged with respect to the rotor, a secondary rotor comprising face plates on opposite sides of the pistons and means to adjust the same e'ccentrically of the primary rotor, crossheads for the pistons and radial guides for the crossheads in the primary rotor, parallel grooves in the face plates on opposite sides of the crossheads, slots in the crossheads generally parallelI 5. .In a rotary, radial piston pump or motor, a

rotatable barrel having a radial cylinder, valve means for the cylinders, a radial flange on the Way in the flange having guide surfaces parallel to the cylinder axis and positioned in advance of and to the rear of the cylinder respectively, a piston reciprocable in the cylinder, a rotary reactance eccentric to the barrel and having Walls disposed closely alongside the end faces of the flange, a headfon the piston reciprocable radially Within and guided by the radial guideway and having a way extending tangentially fore and aft from the piston axis, means connected to the reactance and accommodated in said tangential way for oscillation therealong; said means dening a tangentiallyelongated thrust surface fixed against all movements relative to the reactance rotor and engaging the tangential Way both fore and aft of the piston axis at all times.

6. In a rotary, radial piston pump or motor, a rotatable barrel having a radial cylinder, valve means for the cylinder, a radial guideway in the flan'ge having guide surfaces parallel to the Cylinder axis, a piston reciprocable in the cylinder, a radial head member on theA piston reciprocable radially in the flange guideway and guided thereby, a rotary reactance member eccentric to the barrel and extending alongside the flange and radial head member, thrust means carried byA the reactance member and extending transversely of the head memberA and defining parallel inner and outer reactance surfaces extending forwardly and rearwardly from the piston axis, said head member having complementary Ways parallel to and operatively associated with said inner and'outer reactance surfaces respectively for reciprocating thepiston and for transmitting torque through the medium lof the radial head member between the barrel flange and reactance member, and` accommodating the said thrust means for oscillation therealong forwardly and rearwardly along the path of rotation, and means securing the thrust means to said reactance memberl with said reactance surfaces in fixed position tangentially thereof and constrained against bodily rotation relative to both members.

7. In a rotary, radial piston pump or motor, a rotatable barrel having a radial cylinder, valve means for the cylinder, a radial flange on the barrel in the zone of the cylinder, a radial guide- Way in the flange having guide surfaces parallel to the cylinder axis and positioned in advance of and to the rear of the cylinder respectively, a piston reciprocable in the cylinder, a rotary reactance member eccentric to the barrel and having walls disposed closely alongside the end faces ofthe ange respectively, a radial head member von the piston reciprocable radially in and guided by the radial guideway, one of said members having tangential inner and outer parallel ways extending fore and aft beyond the piston axis, a plurality of thrust pins mounted in one of said members for individual rotation about their own axes respectively and with their axes fixed in position with respect to the member in which they are mounted and positioned todene' an inner and an outer tangential surface extending fore and aft beyond the piston axis, and said pins being accommodated between the ways of the other member for rolling oscillation therealong.

8. In a rotary, radial piston pump or motor, a rotatablebarrel having a radial cylinder, valve means for the cylinder, a radial ange on the barrel in the zone of the cylinder, a radial guideway in the flange having guide surfaces parallel to the cylinder axis, and positioned in advance of `and to the rear of the cylinder respectively, a

piston reciprocable in the cylinder, a radial head on the piston reciprocable radially between and guided by the flange guide surfaces, andhaving a tangentially extending operating way, a rigid thrust plate accommodated in the tangential operating way and connected at its ends to the reactance in fixed position and non-rotative relation with respect to the reactance and having a tangential portion in the tangential operating way in cooperation therewith both fore-and aft of the piston axis concurrently at all times.

9. In a rotary, radial piston pump or motor, a rotatable barrel having a radial cylinder, valve means for the cylinder, a radial flange on the barrel in the zone of the cylinder, a radial guideway in the flange having guide surfaces parallel to the cylinder axis and positioned in advance of and to the rear of the cylinder respectively, a piston reciprocable in the cylinder, a rotary reactance eccentric to the barrel and having Walls disposed closely alongside the end faces of the flange respectively, a radial head on vthe piston reciprocable radially in and guided by the radial guideway,and having a tangential way extending fore and aft from the piston axis,a plurality of thrust pins mounted at their ends in the reactance for rotation about their individual axes, and with their axes in a common tangential plane, and defining a tangential thrust means' which is non-rotative bodily with respect to the reactance, said pins being accommodated in said tangential way of the head for oscillation therealong.

10. In a rotary, radial piston pump or motor, a rotatable barrel having a radial cylinder, valve means for the cylinder, a radial flange on the barrel in the zone of the cylinder, a radial guideway in the flange having guide surfaces parallel to the cylinder axis and positioned in advance of and to the rear of the cylinder respectively, a piston reciprocable in the cylinder, a rotary reactance eccentric to the barrel and having walls radial head on the piston reciprocable radiallyv in and' guided by the radial guideway, a plurality of thrust pins in the head, each pin extending laterally beyond the flange and being accommodated at its ends in said-tangential ways for oscillation therealong, said pins being positioned to engage said Ways concurrently both fore and aft of the piston axis at all times.

11. In a rotary, radial piston pump or motor, a rotatable barrel having a radial cylinder, valve means for the cylinder, a radial flange on the barrel in the zone of the cylinder, a radial guide- Way inthe flange having guide surfaces parallel to the cylinder axis, a piston reciprocable in the cylinder, a radial head on the piston reciprocable radially in the flange guideway and guided thereby, and means carried by the head and extending transversely therefrom and defining inner and outer tangential reactance surfaces at both faces of the head, said surfaces extending forwardly and rearwardly from the piston axis, and rotary reactance means eccentric to the barrel and extending alongside the flange and radial head, and having. complementary` tangential ways operatively engaging said inner and outer reactance engaging surfaces respectively i for reciprocating the piston and for transmitting torque through the medium of the radial head portion between the barrel flange and reactance means, and accommodating the said means for relative oscillation thereof forwardly and rearwardly along the path of rotation.

12. In a rotary, radial piston pumpor motor, a rotatable barrel having a radial cylinder, valve means for the cylinder, a radial flange on the barrel in the zone of the cylinder, a radial guideway in the flange having guide surfaces parallel to the cylinder axis, a piston reciprocable in the cylinder, a radial head member on the piston and accommodated between said surfaces and bridglng the space therebetween and being reciprocable radially in the flange guideway and guided thereby, a rotary reactance member eccentric to the barrel and extending alongside the flange and radial head member, thrust means carried by one of said members in the radial zone of the flangeand extending transversely of the head member and defining parallel inner and outer tangential reactance surfaces extending forwardly and rearwardly fromfthe piston axis, one of said members having complementary ways parallel to and operatively associated with said inner wardly along the path of rotation, means securing the thrust means to one of said members in xed position tangentially thereof with said reactance surfaces constrained against bodily rotation relative to both members, said thrust means being in rolling engagement with the tangential surfaces both fore and aft of the piston and adjacent the piston at all times.

13. In a rotary, radial piston pump or motor, a rotatable barrel having a radial cylinder, valve means for the cylinder, a radial flange on the barrel in the zone of the cylinder, a radial 'guideway in the fiange having guide surfaces parallel to the cylinder axis, and positioned in advance of and to the rear of the cylinder respectively, a piston reciprocable in the cylinder, a` radial head on the piston reciprocable radially in and guided by the flange guideway, andhaving a tangentially extending operating Way therethrough, a rigid thrust plate accommodated in the tangential operatingway and having its ends engaged with the reactance in non-rotative relation with respect to the reactance and having a tangential portion in the tangential operating wayfor cooperation therewith both fore and aft of the piston axis concurrently at all times.

- 14. In a rotary radial piston pump. or motor, a-

rotatable barrel havingl a rigid cylindrical portion and radial cylinders therein, valve means for the cylinders, a radialvtorque flange on the rigid cylindrical portion in the zone of the cylinders and extending radially outwardly from the cylindrical portion, guideways in the flange and aligned with the cylinders respectively, each guideway having guide surfaces parallel to each other and to the axis of the associated cylinder, pistons reciprocable in the cylinders respectively, rigid heads for the pistons respectively and reciprocable in the associated guideways, thrust means carried by and extending laterally from each head and defining rigid tangentially elongated operating surfaces at each side of the associated head, which-surfaces are constrained from bodily rotation with respect to the associated head, a rotary reactance eccentric to the barrel reactance plate elements adjustably and turnand having tangential operating ways accommodating the thrust means with said rigid tangentially extending surfaces in cooperation with the ways for oscillation therealong to effect load and torquetransmission between the barrel and reactance.

15. In a rotary radial piston pump or motor, a rotatable barrel having a rigid cylindrical portion and radial cylinders therein, valve means for the cylinders, a radial torque flange on the rigid cylindrical portion in the zone of the cylinders and extending radially outwardly from the cylindrical portion, guideways in the flange and aligned with the cylinders respectively, each guideway having guide surfaes parallel to each other and to the axis of, the associated cylinder, pistons reciprocable in the cylinders respectively, a rigid head member for each piston reciprocable in the associated guideway, a rotary reactance member eccentric to the barrel and having portions alongside the head member, one of said last named members having tangential ways, rigid thrust means extending transversely of the members and connected to the other one of said members and defining tangential surfaces which are non-rotative bodily with respect to the member by Whichthe thrust means Vis carried and which are accommodated in said tangential ways of the other member.

16. In a pump or motor of the variable displacement radial piston type, aV casing, a valve pintle supported therein, a piston cylinder barrelI in telesc'oping relation to the pintle, radial ways in the barrel aligned with the pistons, crosshead elements for the pistons in said ways, transverse openings in the crosshead elements anda plurality of crosspins carried in said openings in balanced arrangement relative to the piston axes,

ably mounted in the casing and having openings to receive the pins, lthe openings in one o! said elements comprising slots for allowing free travel of the crosspins relative to said slotted element while guiding the pins for definite travel, and antii'rictional needle bearings in the openings oi the coacting element for securing the pins for free rotation only in said coacting element. l

17. Mechanism according toclaim 16, wherein each of the crosshead elements has a plurality of transverse bores supporting the needle bearings and pins and the face plates are slotted to receive the ends of the pins.

18. In a pump or motor of the radial piston type, a casing, a valve pintle mounted in the casing, a cylinder barrel in telescoping relation to I the pintle, a circular radial driving iiange carried by the barrel and having circumferentially spaced openings therein, radial cylinders and crosshead ways aligned therewith in the plane of the flange, crosshead elements lexiblygco'nnected with the pistons and slidable in said ways, face plate elements journalled in the casf ing on opposite sides of said ange and arranged to be adjusted transversely of the axis of the barrel for governing the stroke ofthe pistons, means passing through the ange and rigidly securing the face plate elements together in xed relationship to each other close to the ange, a plurality of crosspins in each ot saidcrosshead elements in balanced relation with respect to the piston axes, the face plate elements having openings receiving the ends of the pins to.actu ate the pistons, and individual antifriction journal mountings for each ofthe pins in one of Ithe aforesaid elements.

- ELEK K. BENEDEK.

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