US2827857A

US2827857A - Rotary pump

Info

Publication number: US2827857A
Application number: US166628A
Authority: US
Inventors: Theodore F Eserkaln
Original assignee: Individual
Current assignee: Individual
Priority date: 1950-06-07
Filing date: 1950-06-07
Publication date: 1958-03-25
Anticipated expiration: 1975-03-25

Description

March 25, 1958 T. F, ESERKALN ROTARY PUMP e Sheets-sheaf. 1

Filed June 7, 1950 March 25, 1958 T. F. ESERKALN 2,827,857

ROTARY PUMP Filed June '7, 1950 6 Sheets-Sheet 3 INVENTOR. 7Ze0aore ffS /id/lr ,4 ffar/r ey March 25, 1958 T. F. EsERKALN ROTARY PUMP 6 Sheets-Sheet 4 Filed June 7. 1950 March 25, 1958 'r. F. ESERKALN 2,827,857

- ROTARY PUMP Filed June 7, 1950 6 Sheets-Sheet 5 IN V EN TOR.

7Z0dore Ffseria/n March 25 1958 T. F. EsERKALN 2,827,857v

ROTARY PUMP Filed June 7. 1950 6 Sheets-Sheet e INVENTORL Y K Tbadfllf [Berta/n BY United States Patent RO RY UMP Theodore F. Eserkaln, Wauwatosa, Wis.

pp cat on une 1950, Seria N 166,628

C a m l- 193-129) This in ent n e ates to pum and motors .and more particularly to a vane type device including a working C am e th apacity of wh h may be a t at w to a y t olumet ic displacement of the device when used as a pump or to vary the torque when used as a motor.

Throughout the remainder of the specification; the device will be described primarily as a pump but it is to be understood that the term pump also defines a motor, since the only difference between its operation as a pump or motor lies in the fact that as a pump it is driven mechanically while as a motor it is driven by the application of fluid :under pressure. The term vane" as used in this specificationis to be construed as any element which serves to divide the working chamber of the pump into separate cylinders.

The primary object of the present invention resides in the provision of a new and improved pump which has increased flexibility in performance and application coupled with compact sine and increased mechanical eflicicncy.

Another object of the invention resides in the provision in a pump of new and improved means for effecting the reversal of the direction of flow of the fluid output of the pump without reversing the direction of rotation of the pump.

Another object of the invention resides in the provision of a new and improved pump, of the vane type, in which the reversal of the direction of pump operation may easily be effected either while the pump is idle or in operation.

Another object of the present invention residues in the provision in a rotary pump of a new and improved combination of elements which include a rotor, adapted to be selec ively driven in either direction, having a hollow cylindrical flange portion including a series of circumferentially spaced radial slots, and a plurality of cooperating parts including a non-deformable enveloping element surrounding the hollow cylindrical flange portion of the rotor, a non-deformable member housed within the hollow cylindrical flange portion of the rotor, and'a plurality of vanes, disposed'for constant contact with the adjacent surfaces of the non-deformable enveloping element surrounding the hollow cylindrical flange portion of the u and e ce-de rm b e member ho sed ithin he hollow cyli drica fla ge p t on f. he otor, uided for al sl d n mo ment n the slots te med in the flan P r i n f he r o h n n rmable element, nondeformable member and vanes being movable as a unit with respect to the rotor for varying the volumetric displacement of the pump. I

Another object of the invention lies in the provision ina vane type rotary pump of new and improved means for varying the displacement of the pump selectively on either side of a neutral or zero displacement position bythe arcuate movement of the rotor enveloping element 2,827,857 Patented Mar. 25, 1958 p ,2 and its associated parts as a'unit with respect to the axis of rotation .of the rotor.

Another object of the invention lies in the provision in a rotary pump of a new and improved construction and arrangement of theparts of the pump which permits the several cooperating parts of the pump to be rotated simultaneously at the same speed to thereby materially reduce wear on the parts of the pump and also materiall increase the operating etficiency of the unit.

Another object of the invention, relating more partieularly to the form illustrated in Figs. 16-19 of the drawings, lies in the provision of cylindrical vane elements.

Another object of the invention, relating to the form of "the invention disclosed in'Figs. 16-19, lies in the construction and arrangement of the several parts of the ice 1 pump in a manner which permits the anchoring of either the rotor enveloping element or the member housed within the rotor against rotary movement, without imparing the efliciency of the pump operation or increasing wear on the cooperating parts, due to rolling action of the cylindrical vane on the part which may be fixed against rotating movement.

Another object of the invention resides in the provision in a pump of a new and improved means for facilitating its connection into a working circuit by providing a plurality of inlet and outlet ports arranged for selective positioning with respect to the pump mounting bracket and for use in making the desired pipe connections.

Another object of the invention resides in the improved construction of the device which permits it to function efficiently through a wider range of speeds of rotation efficient and simultaneous operation of a single vane in both chambers.

Another object of the invention resides in the positive positioning of the vanes in a manner which enables the unit to be operated selectively in either direction of rotation as either a pump or a motor.

Another object of the invention resides in the provision in a vane type pump of a new and improved combination of elements which cooperate in a manner to provide for the constant contact between the vanes and a cooperating surface without requiring the use of either hydraulic pressure or yieldable mechanical means.

Another object of the invention resides in the formation of a curved surface on the vane adapted for constant line contact with a cooperating surface in a manner such that eccentric displacement of the vane carrying rotor with respect to the cooperating surface will effect a rocking movement of the line of contact between the vane and the cooperating surface from one position to vane carrier is altered with respect to, the cooperating surfaces with which the vane contacts during rotation of the vane carrier with the cooperating surfaces.

A further object of the invention resides in the provision in a vane type pump of. a rotatably mounted vane carrier having an outer cylindrical surface, a non-deformable element surrounding said vane carrier having a cylindrical inner surface of a gerater diameter than that of the carrier and a non-deformable member disposed withinthe carrier having a cylindrical outer surface with the diameter smaller than that of the cylindrical surface of the carrier; the radius of the non-deformable member plus the diameter of the cylinder forming the curved surface on thevvanesbeing equal to the radius of the cylindricalinner surface of the non-deformable element surrounding the vane carrier.

Another object of the invention, with reference to the modified form of valve disc shown in Fig. '12of the drawings, resides in the provision of a new and improved arrangement whereby the substitution of the present valve disc renders the device capable of functioning as a compound pump by directing the discharge of the outer pump into the intake of the inner pump.

Another object of the invention, with reference to the modified form of valve disc shown in Fig. 13 of the drawings, resides in the provision of a new and improved arrangement whereby the substitution of the present valve disc makes it possible to utilize the discharge of each pump independently. I

Another .object of the invention, with reference to the single working chamber pump shown in Fig. 14 of the drawings, resides in the provision of a new and improved vane type pump particularly adaptable for use as a motor.

Other objects and advantages will become apparent.

from the following description of the illustrative embodiments of the present invention shown in the accompanying drawings;

In the drawings:

Figure l is .a vertical longitudinal sectional view through a pump constructed in accordance with the teachings of the present invention, as indicated by line 1-1 of Fig. 2.

Fig. 2 is a front elevational view of the pump showing means for selectively adjusting'the displacement of the pump and the direction of rotor rotation and also showing the adjustable bracket, in dotted lines, for the purpose of facilitating the installation of the necessary piping for the hydraulic circuit in which the pump is connected;

Fig. 3 is a rear elevational view of the pump showing.

fragmentary portions of the hydraulic circuit and indi-. cating the general arrangement of the ports in a manner to provide for any of a multiplicity of piping arrangements which are available by opening or blocking either of the inlet or outlet ports and making the piping connections conform with the most desirable arrangement for the particular application at hand;

Fig. 4 is a vertical sectional view taken on the line 4-4 of Fig. 1 showing the eccentric mounting of the positioning of the pump mounting.

3 invention be desired;

collector plate showing the inlet and Fig. ,8 is a front elevational view of the distributor and outlet passages an associated porting, together with means for retaining the plate in a fixed relationship with the pump casing;

Fig. 9 is a rear elevational view of the plate shown in Fig. 8 showing vthe porting which leads the fluid to and from the rotor chamber of the pump;

Fig. 10 is a vertical sectional view taken on the line iii-16 of Fig. 1 showing the ports in the pump casing which are aligned with the cooperating ports in the distributor plate;

Fig. 11 is a vertical sectional view taken on the line 11-11 of Fig. 1" showing the inlet and outlet passages formed in the pump casing; the dotted lines indicating a modified form of the casing permitting independent use of the two pumps;

Fig. 12 is a front elevational view of a modified form of distributor and collector plate showing fluid inlet and outlet passages and porting arranged in a manner to placethe two pumps in series connection wherein the discharge of the outer pump is directed into the intake of the inner P p; r

Fig. 13 is a view similar to that shown in Fig. 12 showing a further modification of the distributor and col lector plate wherein the passages and porting are arranged to permit the independent use of the discharge of both of the pumps;

'Fig. 14 is a view, similar to that shown in Fig. 5A, showing a modified form of the present invention in which the pump is provided with a-single working chamber which makes-the device more readily adaptable for use as a motor, should this form of application of the Fig. 15 is a diagrammatic view showing the movement of the line of contact between the cylindrical surface on the vane-and the inner and outer non-deformable ring elements-of the pump; the full line showings indicating the mean position wherein the respective radii of the driver passed through the axial center of the vane and of the inner andouter rings at the line of contact between the vane and their respective surfaces are coincident, and the extreme position wherein the radii are separated by the amount of eccentricity between the driver and the displacement adjusting means with respect to the center of rotation of the pump rotor;

Fig. 5 is an elevational view of the pump assembly with the cover removed and showing the neutral or zero displacement position; v

Fig. 5A is a view similar to Fig. 5 showing the pump parts in a position of maximum pump displacement in one direction of rotor rotation;

pump parts in a Fig. 5-8 is a view similarrto Fig. 5 showing the pump 1 parts in a position of maximum pump displacement in the other direction of rotor rotation; v

Fig. 6 is a perspective view of oneof the vanes of the pump showing the arcuate configuration of the opposite surfaces of the vane which contact the respective surfaces of both inner and outer ring elements;

Fig. 7 is a front elevational view of the pump rotor showing the guide means for the vanes and also the inlet and outlet porting for the fluid;

inner and outer rings; arbitrary intermediate positions being indicated by the dotted line showing, for the purpose of more clearly illustrating the'movementofthe line of-contact on: the curved surfaces of'the vanes.

Fig. 16'is a view similar to Fig; 5 with the pump parts inneutral position but showinga modified form ,of the invention .in which the vanes are formed of cylindrical members adapted for rolling contactlwith the surfaces with which they are in contact.

Fig. 17 is a view similar to that shown. in Fig. S-A incorporating the modified form of vanes and showing the parts in a position of maximum pump displacement in one direction of rotor'rotation;

Fig. l8'is a'frontelevationall' view of the pump rotor showing, the guide means .for the modified form of vanes together with the required inlet and outlet porting for the flow of-fluid to and from theworking chambers of thepumpg and Q f .Fig. 19 'is a perspective view of one of the vanes used in the modified form of the invention;

Referring more. particularly to the drawings, it will he noted that the pump of the' present invention comprises a casing or housing 20, preferably in the form of a casting and including a pumpgrecess 21 and suitable inlet and outlet eharnbers 22' and 23 respectively. A plurality of concentrically arranged contiguous bores of different diameters serve to form an opening extending through the housing. Each of these bores serve a particular purpose and include a gasket recess 24, a rotor recess 25,.a bear-- ing receivingybore 26,-: a shaft receiving bore 27 and a collar receiving bore 28. a v a I he ee f t e o n so b t e st rilis ti n e s est rs housing through the medium of a washer 31 and a deformable O-ring 32 positioned within the gasket recess 24. The pump housing 20 is adapted to be attached to a mounting bracket 33 secured to the end of the housing 20 opposite the cover 29 by means of cap screws 34. The mounting bracket 33 includes an upstanding flange 35 through which the cap screws 34 are passed and a flat base portion 36 adapted to be attached to a supporting surface (not shown) in any approved manner. Referring more particularly to Fig. 3 of the drawings, it will be noted that the arrangement of the cap screws 34 is such that the housing 20 may be attached thereto selectively in either the position shown in full lines, wherein the inlet nd outlet piping extends horizontally from the housing,

or in the dotted line position, wherein the inlet and outlet pipes extend vertically from the housing. The selective I positioning of the housing on the mounting bracket 33 is important as it provides a means by which the connection of the pump into a hydraulic system is greatly facilitated due to the fact that the piping may be attached through the casing in any one of a large member of cornbinations made available through the selected positioning of the housing on the mounting bracket. Suitable holes 37 are formed in the base 36" to permit the passageof pipes through the base should the desired piping require this arrangement.

' The rotor 33 which forms one element of the pump is housed within the recess 21 of the pump casing 20. The rotor 38 includes a shaft 39, a disc or plate portion 40 anda forwardly extending hollow cylindrical'fiange 41. With the rotor '38 properly positionedin the casing 20, the end of the shaft 39 projects beyond the casing20 and the mounting bracket 33 to provide a means on which any suitable driving element such as a pulley or gear (not shown) may be secured. The source of power for effect ing the rotation of the pulley or gearmay be of any appropriate form such as an independent electric motor or any suitable driven shaft adapted for transmitting power to rotate the shaft 39.- The inner end of the shaft 39 is journaled for rotation in a roller bearing (t2, the outer race of which is pressed into the bore 26 formed in the housing 20, While a ball bearing 43 retained in spaced relationship with the roller bearing 42 by a spacer collar 44 serves as a second support for the shaft 39. The outer in turn is retained within the bore 28 formed in the housing 20. In addition to serving as the impeller for the pump, the rotor 38 is proyided with the hollow cylindrical portion 41' which is divided into a plurality of sectors 46 by plurality of radially disposed slots 47 each adapted to receive and guide individual vanes 48.

race of the bearing 43 is pressed into a collar 45, which Each of the vanes 43 comprise a quadrilateral prism having a pair of parallel fiat sides 49 and a pair of convex sides 50. The convex sides 50 of the vanes'48 are formed by portions of the surface of a cylinder having a diameter substantially equal to the difference in the radii of the outer cylindrical surface of a non-deformable member 51 and the inner cylindrical surface of a non-deformable element 53 generated from a longitudinal axis positioned by the centers of the ends of the prism. Each vane has alength which is coextensive with the depth of the hollow cylindrical flange portion 41 of the rotor 38.

The inner convex surface 50 of each of the vanes 43 is arranged for line contact with the outer cylindrical surface of a non-deformable ring member 51; while the outer convex surface 50 on each vane 48 is arranged for line contact with an inner cylindrical surface 52 formed on a non-deformable element 53, preferably in the shape of a ring, and disposed to surround the hollow cylindrical portion 41 of the rotor 38. The depth of the ring member 51 and the element 53 being identical with the length at the va es eee e nee t e d a ng i in e lea l that w e the es 48 e e p s io ed w thin the l s A he Pe e 3% Wi h heir inn r surfeer n seatact with the outer surface of the ring member 51 that the outer surfaces 50 of the vane provide a series of contacts along which the element 53 may be slid into posi: tion during the process of assembling the pump. It will also be noted at this point that the non-deformable else.- ment 53 is supported in concentric relationship with the non-deformable member 51 by reason of the fact that each of the vanes 48 have the identical diametric dimension so that any displacement of the member 51 with respect to the axis of rotation of the rotor 38 will effect an equal displacement of the element 53.

The cooperating relationship of the several pump elements including the rotor 38, the vanes 48, the non deformable member 51 and the non deformable element 53 should now be considered for the purpose of deter..- mining the form of the present pump. From the showing in Figs. 5, S-A and 5-B it will be noted that an outi pump or working chamber is formed between the inner cylindrical surface 52 on the element 53 and the onter cylindrical surface of the hollow portion 41 of the rotor 38 and in like manner an inner pump or working chamber is formed between the outside diameter of themember 51 and the inside diameter of the hollow cylindrical portion 41 of the rotor 38.

The pumping operation of the device is effected by the displacement of the non-deformable element 53 and its associated parts from concentric relationship with the axis of rotation of the rotor 38 and the amount of eccentricity to one side of the concentric relationship will vary the displacement of the pump in one direction of discharge flow, while the amount of eccentricity of the other side of the concentric relationship will vary the pump displacement with the discharge of the pump flowing in the oppositedirection.

While any suitable adjusting means may be employed for varying the displacement of the pump and the direction of the pump discharge, in the present disclosure I have chosen to illustrate a means for effecting the alienate movement of the non-deformable member 51 and its associated parts. This adjusting means comprises a stub shaft 54 mounted ecceutrically with respect to the axis of rotation of a shaft 55 to which it is secured. The shaft 55 is rotatably mounted in a bore 56 formed in the ,Q Yer 29 and disposed eccentrically with respect to the cover portion 29. It should be noted that at this point that the axis of rotation of the shaft 55 is slightly below the axis of rotation of the rotor 38. The amount of offset of the stub shaft 54 with respect to the shaft 55 being substantially equal to the distance between the respective axes of the rotor shaft 39 and the shaft 55 so that the norpdeformable ring member 51 and the non-deformable element 53 may be positioned in concentric relationship with the rotor 38, in which the pump is in neutral or zero displacement position and from which it may be movedin an arc to one side or the other to increase the displace: ment of the pump from zero to a maximum displacement regardless of the direction of rotation of the rotor 38. The outer end of the shaft 55 is provided with flat faces 57 adapted to receive a crank or adjusting handle (not shown) by which the shaft 55 may be adjusted by partial rotation to move the stub shaft 54 into and out of .concentric relationship with the axis of rotation of the rotor 38. A jamb nut 58 is threaded on the shaft 55 and cooperates with a shoulder 59 formed on the shaft 55 to draw the shaft 55 outwardly so that the shoulder 59 bears tightly against a portion of the cover 29 to lock the stub shaft 54 in desired position with respect to the axis of the rotor 38. A pointer 60 is secured to the shaft 55, in anyv appropriate manner, to provide a visual means for indicat ing the position of the stub shaft 54 with respect to the axis of the rotor 38. Referring more specifically to Fig. 2, the full line showing of the pointer 60 indicates the concentric relationship of the stub shaft 54 with the of rotation of the rotor 38, wherein the cooperating 61;?

I 7 inents of the pump are in the position shown in Fig. 5. The dotted line showing of the pointer 60, shown to the left of the full line showing, indicates the maximum eccentricity of the ring member 51 with respect to the rotor 38 wherein the several elements of the pump are in the position shown in Fig. A of the drawings. In like manner, the dotted line showing of the pointer 60 to the right in Fig. 2 indicates the maximum eccentricity of the ring member 51 in the direction opposite to that previously mentioned. The several elements of the pump then assuming the position shown in Fig. 5B of the drawings.

A brief discussion of the arrangements of fluid passages and porting of the pump will now be described. As previously mentioned, the housing includes a pair of

chambers

22 and 23. The chamber 22 is provided with a pair of threaded

passages

61 and 62 either of which is adapted to receive a pipe 63 or a pipe plug 64. The interchangeability of the positioning of the pipe 63 and the plug 64 serves to simplify a piping arrangement for connecting the pumpv into a working circuit. In like manner, the chamber 23 is similarly provided with a pair of threaded

ports

65 and 66 which are adapted to selec tively receive either a pipe 67 or a pipe plug 68 in a manner similar to that previously described and for a like purpose. A passage or port 6? connects the chamber 22 with the rotor recess and in like manner a port 70 serves to efiect communication between the chamber 23 and the rotor recess 25. Ports 71 and 72 formed in a disc valve or distributor and collector disc 73 connect respectively with ports 69 and 70 to direct fluid to or from

passages

74, 74' and 75, 75' respectively. Each of the

passages

74, 74', 75, and 75 (see Fig. 8) are arcuate in form and are disposed in concentric relationship with a bore 76 formed in the plate 73. The bore 76 being receivable on a hub portion 77 of the rotor shaft 39. The plate 73 is secured in fixed position against the base of the rotor recess 25 by means of a pair of dowel pins 78 which are secured in diametrically spaced relationship in the base of the rotor recess 25 and are adapted to receive bore 79 formed in the plate 73. The plate 4 3 of the rotor 38 is provided with a plurality of circumferentially spaced

ports

80 and 80. The parts 80 being positioned to lie immediately adjacent the outer surface of each of the sectors 46 of the rotor 38; while the ports 8%) are disposed to lie immediately adjacent the inner surface of the several sectors 46 of the rotor 38. From the foregoing, it will be noted that the passages and porting of the pump is simple in form and serve to provide cooperating means through which fluid may be directed to and from the pump. Referring more particularly to Figs. 1, 5, 5A and 5 -B when taken into conjunction with Figs. "i1 inclusive the following description of the operation of the device will be clearly understood. At the outset of this description it should be understood that the rotor 38 may be impelled selectively in either direction and in like manner, the position of the several cooperating pump elements ma be chan ed from maximum eccentricit in one direc-' tion to maximum eccentricity in the other direction'or in any desired adjusted position between the two extreme positions and including a central position wherein all of the parts of the pump are concentrically arranged with the resulting effect being a neutral or zero displacement position wherein the pump may be said to be idling. Since the pump parts are free to rotate in either direction and since the piping to and from the pump may be arranged in any suitable manner, the

chambers

22 and 23 may be selectively chosen with either as the inlet chamber with the remaining chamber servingas the outlet chamber. For the purpose of the present description the chamber 22 will arbitrarily be taken as the inlet chamber and hence fluid from any suitable reservoir (not shown) maybe drawn into the chamber 22 through the intake .pipe 63., Under the rotary action of the pump fluid will be drawn from the chamber 22 through ports 69,71, and

passages

74 and 74 and thence through ports and 80' which are, at the moment, in communication with the respective passages 74 and 74'. Referring more particularly to Fig. 5-A, it will be noted that the rotor 38 is turning in a clockwise direction and the degree of eccentricity of thering member 51 is at an extreme position to the left of the neutral position so that the volumetric capacity of the cylinders formed by the adjacent vanes 43 in the outer working chamber in cooperation with the inner cylindrical surface 52 of the ring 53 and the outer cylindrical surface of the rotor sectors 46 are increasing in capacity during one-half of the revolution of the associated pump parts and are decreasing in capacity during the other half of the rotation of the rotor 38; in like manner the similar cylinders formed by adjacent vanes 48 in the inner working chamber in cooperation with the inner cylindrical surface of the sectors 46 and the outer cylindrical surface of the element 53 function in the identical manner, just previously described, save for the fact that their action is oifset degrees with respect to those in the outer pump. It will thus be seen that during the portion of rotation of the pump wherein the ports 3% and 80' formed in the rotor 33 are in communication respectively with the

passages

74 and 74, fluid will be drawn into the expanding chambers and in like manner, during the remaining portion of a single rotation of the pump parts, fluid will be expelled from the decreasing capacity of the cylinders through the ports 8i? and 80' which are in communication with the passages '75 and 75 and the fluid thus discharged from the decreasing capacities of the cylinders will be directed through ports 72, 7%, outlet chamber 23, and into the pipe 67 which leads to the working side of a circuit in which the pump is connected. With the above arrangement of ports and passages the combined capacities of both inner and outer pumps are utilized in the working circuit.

At this point it is deemed advisable to emphasize the fact that in actual pump operation the element 53, the several vanes 48 and the member 51 travel in the same direction and at the same speed of rotation as the rotor 38 with the result that sliding friction between the element 53, vanes 4-8 and member 51 is reduced to a minimum and the efficiency of the pump is materially increased. The unitary rotation of the assembly comprising the element 53, the vanes =88 and the member 51 is etfec'ted by the fact that the curved surfaces 54? of the vanes 42:

are respectively in line contact with the inner surface 52 cf the element 53 and the outer cylindrical surface of the member 51. The arrows on Figs. 5-A and 5-B indicating the direction of unitary rotation of the assembly comprising the element 53, the vanes 43 and the member 51 under the influence of rotative movement of the rotor 38 which includes the hollow cylindrical flange portion 41 provided with slots 47 to receive the several vanes 43 which retain the member 51 and element 53 in concentric spaced. relationship.

As the form of the vanes 43 provide one of the principal reasons for the successful and efficient operation of the present pump by reason of the fact that, in all positions of the adjustment between the rotor and the remaining operating parts of the pump, the curved or convex portion of each vane is retained in line contact with a cooperating element or member of the unitary assembly independently of either hydraulic or yieldabie mechanical means. in addition to this important feature, the vanes are so constructed that the line of contact between them and the element with which they cooperate is free to move on the convex surface of the vane as the amount of eccentricity between'the radial center line of the vane and a radial line from the point of contact between the convex surface of the vane and the cooperating element of the pump drawn to the axis of-the element form a common line at two positions in the circumference of the element to positions substantially perpendicular to, the commonradial lines wherein the two radii form the greatest angle with each other.

he. th s e h 1eeti9a. r feren e sheshi h ai t9 t estemmatie s ow ng i .5 in wh h the n A in cates the .0 0J1 e ei-the tien 1% n ates. he g ea es diver ence hetwee the two radii- Qhneu ly. th "m nt e eeh ae hetwe n the v ne 11 he ee peranng' el m nt w l 1 ve fern he e 2 rem posi ion nd ee 9 PQSifiQI B 1e'side of the rete ra ius to. a similar extr me. 1:0... .11. 01 th he side of t e 01 diu sinus hel ef a eve at on 0f the mint nd en e urn t the pesitie 1 de i e t remain n half o the ret re slh eh- .1 this he ns it is c ea tha he l n o swtaee een ee between the vas a d t ee retias e em nt meve 'ever t eur eee 0 the' eh the ote; 38 hree e nn th. it th asseeia ee atient the m1. P wh ch nelude th v nes 48. he memb r 5,1 an the element 5 The am u 1t 0f eeeht i h iress 9 member 5, en elemen 53 wi h eP'eet t6 th at ie ihe ee ed, 0n his. by the. le ter E- w th eteh t th e an 31 he eh i t fi e i 'ee ee 'he s tha the tsetse! me surements 0m he in h e ee between he ot er F west su f ce 50 9 ehe 43.; or as e We e' ihslj e veee s use e3 he h ve shrt ee 5. e the element a when eeeh es t1 f e Peh er the 911 1 e hte lihe'e th e seem e edi-he efi theeYlihQ iee eh teee 52 i he v a heated b the dimehei a s Ilse tee h... 99? 9t th he e that slieeie r th s a eet is hee e 1 .1 911 lessee? ehe s the; ma he 9 t ehsh e s e and nee he ee eeheiehle'r shew. f10111 e a 01 0011- teet between e serves shatese 'eithei e el01 te' 1 with the inner cylindrical surface 52 of the ellement 53 e efieet 10111 t e eeht e t e se eee .52 th s perpend l ime f which te ht d w1 Pert 011 01 a chord 1, 0f 1 ee e he e rt t n the ra us o the s reee ;fl e er h e t e d am t r o t e c nv x e fe 9f the n is ual 1 h hitt r ne be ween the radius m of the member 51 and the radius a of the element 5;; it will be jclear that a radial :drawn from the common center of the member 51 and element 53 passing through the axis of the cylinder forming the convex surface of the vane will indicate that the vane surfaces 5.0 will lie in eorita ct with the inner cylindrical surface 52 of the element 53 and also in contact .with the outer cylindrical surface of the member .51. Hence it will be apparent that if this condition exists :in the extreme position of eccentricity between the rotor 38 and the unit formed -by member 51, vanes 48, and element 53 it must also exist in all positions having a lesser eccentricity. From the foregoing discussionfit will be apparent that I have provided .a pump construction in which the operating efiiciency of the device is maintained by the automatic compensation for varying chordal positions of the vanes with respect to the surfaces with which the convex portions .of the vane contact during their eccentric rotation with respect to the rotation of the parts with which they are maintained in constant surface contact. It should also be noted at this point that vanes of the present design'are adapted toma'intain their desired surface contact with the cooperating'parts of the pump without requiring the inclusion of either hydraulic'pressure or yieldable mechanical means to elfect the desired result. A further advantage of the cooperative relationship between the several parts of the pump lies in the fact that the nicety of fit between the convex surfaces50 of the vanes and the cooperating surfaces of the element 53 and the member 51 is such that all of the cooperating parts of the pump rotate as-a unit with each part having the same angular velocity. By reason of this fact, it will be apparent that the emq ncy of the pump is greatly increased due to the practical elimination of s i in eh e wee the eeehiere i s eef 9f t 1 11, 1

element 53 which efi ect s the increase of the capacity of the several cylinders during one-half of a cycle of revolution and the decrease of the capacity of the sevcle of revolueral cylinders during the other half of a cy tion to thereby elfect the intake of fluid by suction into the increasing capacity of the cylinders while they are in communication with the intake passages 74 and 74 d ikew ie t the xh us ng 0f fluid nd P essure frornthe decreasing capacityof the cylinders when they are in communication with the passages and 75.

Referring more particularly to Fig. 12 of the accompanying drawings it will be noted I have illustrated a modified form of the valve or distributor and collector plate 73 shown in Fig. 8. The modified form discloses a valve or distributor and collector plate 73 which is generally similar to the valve 73 except for the fact that the discharge of the outer pump is directed into the intake sideof the inner pump with the result that the pressure obtainable is substantially doubled since the unit new functions at a two stage compound pump. In order to insure the obtaining of the maximumpressure in this pump arrangement, it should he noted that the discharge of the pump having the greater volumetric capacitl lis connected to theintake side of the pump having the'smaller volumetric capacity. It fshouldalso be understood that when the valve 73' is substituted for the v 73 in the main pump showing that the pump to" be effective only be rotated one direction, that is with the rotor 32; turning in a clockwise direction wherein fluid is drawn into the pump through the ports 71 and intake passage 74 is discharged from the outer pump through the passage and intothe passage 7 4 through a connecting passage 81. The discharge of the inner pump is directed through the passage 75 t0 the i se Pe t72 Ieferri ng more particularly to Fig. 13 of the drawings it will be noted that another modified form of the valve .or dietributor plate 73 is shown, In the present modified 1 elv 9. p t 73"1 s empleyed i h g nerall m a o m an rran ement w th the a ve e e 1 in his e e t 01 the e ha th 1 0 s e ee e e e a e a ran d n airne he t0 Pe mi th in e e d n o h dis arge t'th inne nd 00te1 Pumpe- R fi r i 1 e p 1- 1leh t e 0 the 99 1 pah ins d aw n s i wi l h he d .1 1 he e i t d 11 modifie 0 1 of pump .e ne heted in a r e ee w th the t a hihss .0 he a es ht i i 1 utilizing e n l ne ihs h mber- Thi e ifie 01111 0f P11 119 is identical in operation and construction with the pumps previously described exceptfor the fact that only a single e ie 0f in ake and ou le ne te $9 er eq r h modified form of pump e bdying a single working hamber l n s i s en eevel t e e pl d as a meter in which instance fluid under pressure delivered to the intake side of theunit provides the motive power for fi ine t i .0. th H 1" d he ha 0f the ro o may b pnovid d th e pu le se 9. e he h (not shown) as a power take off medium. to be used in any desired ma n Another, modified form of the pump construction is 48', which may be formed by appropriate lengths of drill rod having the correct diameter. These cylindrical'vanes 48' serve to replace the flat sided vanes 48 (previously described). The inclusion in this disclosure of four vanes in place of the six shown in the previous form of the invention is purely arbitrary and of no real significance. Here again, the present modified form of pump can function in the identical manner as previously described wherein the cooperating parts of the pump rotate as a unit with the rotor 38 with each of the parts having the same angular velocity. However, the inclusion of the cylindrical vanes 48 in the present modification makes it possible to restrain either the member 51 or the element 53 against rotation without impairing the efficient operation of the pump. This condition is made possible by the fact that the cylindrical vanes 43 are free to revolve about their axes and maintain a constant rolling contact with the fixed surface 52 of the element 53 if this element is fixed against rotation, or maintain a constant rolling contact with the outer surface of the member 51 if this member be fixed against rotation. In either instance, it will be clear that the frictional resistance between the cooperating parts of the pump will be reduced to a minimum by reason of the rolling contact between the engaging surfaces of the relatively moving parts.

While the invention has been described in considerable detail in the foregoing specification, it is to be understood that various changes may be made in its embodiments without departing from or sacrificing any of the advantages hereinafter claimed.

I claim:

1. In a pump the combination of a rotor including a hollow cylindrical flange portion, a non-deformable enveloping element surrounding the flange portion of said rotor, a cylindrical inner surface on said non-deformable element cooperating with the outer cylindrical surface on the flange portion of said rotor to form an outer working chamber, a non-deformable member housed within the hollow portion of said rotor, a cylindrical outer surface on said non-deformable member cooperating with the inner surface on the hollow portion of said rotor to form an inner working chamber, a plurality of one-piece vanes guided for radial sliding movement in the flange portion of said rotor, each of said vanes having oppositely disposed longitudinally extending cylindrical surfaces comprising parts of the surface of a cylinder having a diameter equal to the difference between the radii of said cylindrical inner surface of said element and said cylindrical outer surface of said member, said oppositely disposed longitudinally extending cylindrical surfaces serving respectively to contact said inner cylindrical surface on said non-deformable element and said outer cylindrical surface on said non-deformable member to retain said element and member in unalterable spaced relationship; said vanes serving to divide each of said working chambers into a plurality of cylinders, adjusting means for altering the position of the common axis of said non deformable element and non-deformable member with respect to the axis of said rotor to thereby vary the capacity of said working chambers and hence the displacement of the pump, means for effecting the rotation of said rotor, and fluid inlet and outlet means communicating with said working chambers whereby rotation of said rotor effects the intake of fluid into the cylinders cornmunicating with said fluid inlet means and the discharge of fluid-under pressure from the cylinders communicating with said outletmeans. V

2. In a pump the combination of a rotor including a hollow cylindrical flange portion, a freely rotatable nondeformable enveloping element surrounding the flange portion of said rotor, a cylindrical inner surface on said non-deformable element cooperating with the outer cylindrical surfacelon the flange portion of, said rotor tojform an outer [working chamber, a-freely rotatable non deformable member housed within the hollow flange portion of said rotor, aqcylindrical outer surface on said nondeformable member cooperating with the inner surface ofthe hollowlflange portion of said rotor to form an innerworking chamber, a pluralityof one-piece vanes guided for radial sliding movement in the flange portion of said rotor, each of said vanes having oppositely disposed longitudinally extending cylindrical surfaces comprising parts of the surface of a cylinder having a diameter equal to the difference between the radii'of said cylindrical inner surface of said element and said cylindrical outer surface of said member, said oppositely disposed longitudinally extending cylindrical surfaces serving respectively to contact said inner cylindrical surface on said non-deformable'element and said outer cylindrical surface on said non-deformable member to retain said elementand said member in unalterable spaced relation ship, said vanes serving to divide both of said working chambers into a plurality of cylinders, adjusting means for altering the position of the common axis of said nondeformable element and said non-deformable member with respect to the axis of said rotor to thereby vary the capacity'of said working chambers and hence the dis placement of the pump, driving means for elfecting rotation of said rotor, vanes, non-deformable member and non-deformable element as a unit with each part having the identical angular velocity whereby wear between the cooperating parts is materially reduced, and fluid inlet and outlet means communicating with said working chambers whereby the rotation of said rotor and associated parts eflects the intake of fluid into the cylinders communicating with said fluid inlet means and the discharge of fluid under pressure from the cylinders communicating with said fluid outlet means.

3. in a pump the combination of a rotor including a hollow cylindrical flange portion, a non-deformable enveioping element surrounding the flange portion of said rotor, a cylindrical inner surface on said non-deformable element cooperating with the outer cylindrical surface on the flange portion of said rotor to form an outer working chamber, a non-deformable member housed within the hollow cylindrical flange portion of said rotor, a cyrndrical outer surface on said non-deformable memcooperating with the inner surface on the flange portion of said rotor to form an inner working chamber, a

'pluraiity of one piece vanes guided for radial sliding movement in the flange portion of said rotor, each of said Manes having oppositely disposed longitudinaily exrding cylindrical surfaces comprising parts of the sure of a cylinder having a diameter equal the differbetween the radii of said cylindrical inner surface of aid element and said Cf/llldlijli outer surface of said member, said oppositely r. o ed longitudinally e nding'cylindrical surfaces serving re ely to consaid inner cylindrical surface on said no deformable rat and said outer c ndrical surface on said nondcv rinable member to retain said element and said memher in unalterable spaced relationship, said serving to divide both of said Working chambers into a plurality of cylinders, adjusting means for altering the position of the common of said element and said member selectively in opposite directions from concentric relationship with. the axis of rotation of said rotor to thereby effect re'rsai'of'the direction of flow of the pump output, ivit for effecting the rotat of said rotor, and d inlet and outlet c'ommrnicating with both of said working chambers whereby rotation of said rotor effects the of fluid into'the cylinders communicatwith saidfluid inlet means the discharge of fluid der pressure from the cylinders communicating with Quid fluid outlet means. I

4. A pump constructed as set forth in claim 3, in which the adjusting means for the position of the common of said non-deformable element and said non deformable member selectively in opposite directions from concentric relationship with the axis of said rotor is an asaas'e r 13 eccentric arranged to impart acuate movement-of the common axis of said element and member through the axis of; said rotor. v p

5.- In a pump" the combination of a; rotor including a hollow cylindrical flange portion, a'freely rotatable nondeformable enveloping, element surrounding the flange portionof said rotor, acyli-ndrical-inner surface on said non-deformable element'cooperatingrwith the outer cylindrical surface on the flange portion of said rotor to'form an outer working chamber, a freely rotatable non-deformable member housed within the hollow cylindrical flange portion of said rotor, a cylindrical; outer surface on said non-deformable member cooperating with the inner surface of the hollow cylindrical portion of said rotor to form an inner working chambeigla plurality of one-piece vanes guided for. radial slidingv movement in the flange portion of said rotor,=each ofsaid vaneshaving oppositely disposed longitudinally extending cylindrical surfaces comprising partsof the surface of a cylinder having a diameter equal to the difference betweenthe radii of said cylindrical inner surface ofsaid element and said cylindrical outer surface of said member, said oppositely disposed longitudinally extending cylindrical surfaces having serving respectivelyto contact said inner cylindrical surface of said non-deformable element and said outer cylindrical surface of said non-deformable member to retain said element and member in unalterable' spaced relationship; said vanes serving to divide both of said working chambersinto a plurality of cylinders, adjustingmeans for altering the position ofthe common axis of said nondeformable elementand; said non-deformable member selectively in opposite directions from concentric relationship with the ,ax-is of rotation of said rotor to thereby effect the reversal of the direction of flow of the pump output, driving meansfor effecting the rotation of said rotor, vanes, member and element as a unit with, each part having the identical angular velocity whereby wear on the cooperating parts of the pump is materially reduced, and fluid inlet. and outlet means communicating With both of said working chamberswhereby the rotation of said rotor and its associated parts effects the intake of fluid into the cylinders communicating with' said fluid inlet means and the discharge of fluid under pressure from the cylinders communicating with said fluid outletmeans.

6. A pump constructed as set forth in claim 5, in which the adjusting means fora-ltering the position of the common axis of said non-deformable element and said nondeformable member selectively in opposite directions from concentric relationship withlthe axis of said rotor is an eccentric arranged to impartarcuate movement" of the common axis of said non-deformable element and said non-deformable member through the axis of said rotor.

7. In a pump the combination of a rotor including a hollow cylindrical flange portion, a non-deformable enveloping element surrounding the flange portion of said rotor; a cylindrical inner surface on said non-deformable element cooperating with the outer cylindrical surface on the flange portion of said rotor to form an outer working chamber, a non-deformable member housed within the hollow portionof said rotor, a cylindrical outer surface onrsaid non-deformable member cooperating with the inner surface on the flange portion of said rotor to form an inner working' chamber, a plurality of one-piece vanes guiddfor radial sliding movement in the flange portion of said rotor, each of said vanes having oppositely longitudinally extending cylindrical surfaces comprising parts of th'e surface of a cylin der having a diameter equal to the difference between the radii of said cylindrical inn i surface of said element and said cylindrical outer surface of said member, said oppositely disposed longitudinally extending cylindrical surfaces serving respectively 'to contact said inner cylindrical surface on said non-deformable "element and said outer cylindrical surface on saidnon-deformabIe member to "retain said element and member in unalterable spaced relationship; said vanes.v serving, to divide both of said workingchambers into' a plurality of cylinders, adjusting means for altering thepo'sition of the common axis. of said element and. said. member selectively in opposite directions from concentric relationship with the, axis of rotationof said rotor to thereby effect reversal of the direction offlow of thepumpoutput andvary the capacity of the working chambers to. vary the displacement of the pump, driving'means for effecting therotation of said rotor, and fluid inlet and outlet. means, communicating with both of. said workingchamberswhereby rotation of said, rotor effects the. intake of fluid into the cylinders communicatingwith. saidfluid inlet means and the discharge of fluid under pressure! from't-hecylinders com.- municating/with said fluid outlet means.

8. A pump constructedas set forth in claim 7, in which the cooperating. pump parts including said rotor, vanes, non-deformable element and non-deformable member rotate as a unitwitheach parthaving the identical angular. velocity Wherebywear on the cooperating parts, of the pump are materially reduced.

9. A. pump constructed. as set forth in claim 7, in which the adjusting; means for altering the position of the common a-xis ofsaid nonsd'eformable element and said nondeformablemember selectively in opposite directions from concentric relationship with the axis of said rotor is an eccentric arranged, to impart arcuate movement to the common axis. of said element and said. member through the axis of said rotor.-

10. In a rotary pump the combination with a rotor including a hollow cylindrical flange portion, a plurality of radially disposed vane" receiving slots in the flange portion. of saidrotor, non-deformable enveloping element surrounding the flange portion of said. rotor having a cylindrical inner surface. cooperating with the outer cylindrical surface. of said rotor to form an outer Working chamber, a nonrdeforma'ble member housed within said hollow cylindrical portion of said rotor having a cylindrical outer surface cooperating with the inner surface of the flange portion of said rotor to form an inner working chamber, a plurality of one-piece vanes each comprising a quadrilateral prism including a pair of parallel flat sides and. a pair of convex longitudinally extending parallel faces formed by portions of the surface of a cylinder having a diameter equal to the difference between the radii of said, cylindrical inner surface of said element and said cylindrical outer surface of said member, each of said vane receiving slots in said rotor adapted to cooperate with the flat sides on one of said vanes to position and guide the same for radial sliding movement in the flange portion of said rotor, said convex faces of said vanes serving to retain said element and member in unalterable spaced relationship with one convex face of each of said vanes having constant line contact with the inner cylindrical surface of said non-deformable element and the opposite convex face of each of said vanes having constantline contact with the outer cylindrical surface of said non-deformable member, said vanes serving to divide both of said working chambers into a plurality of cylinders, means for adjusting the eccentricity of said unit-deformable element and said nondeformable member as a unit with respect to the axis of rotationof said rotor to thereby simultaneously vary the capacity of both of said working chambers and the- 15 V angular velocity whereby wear on the cooperatingparts of the pump is materially reduced.

12. A pump constructed as set forth in claim 16, in which the adjusting means for altering the position of the common axis of said non-deformable element and said non-deformable member selectively in opposite directions from concentric relationship with the axis of said rotor is an eccentric arranged to impart arcuate movement to the common axis of said element and said member through the axis of said rotor.

13. In a pump the combination of a rotor including a hollow cylindrical portion, a non-deformable envelop ingelement surrounding the hollow cylindrical portion of said rotor, a cylindrical inner surface on said non-deformable element cooperating with the outer cylindrical surface on hollow cylindrical portion of said rotor to form a working chamber, anon-deformable member housed within the hollow portion of said rotor, a plurality of one-piece vanes arranged for radial sliding movement in the hollow cylindrical portion of said rotor, said vanes each including a pair of longitudinally extending parallel cylindrical surfaces formed by portions of the surface of a cylinder having a diameter equal to the ditference' be tween the radii of said cylindrical surface of said element and said cylindrical outer surface of said member, said longitudinally extending parallel cylindrical surfaces of said vanes serving to provide a means by which said element member are retained in fixed spaced relationship by being disposed between said non-deformable enveloping element and said non-deformable member and having constant surface contact with said inner cylindrical surface of said non-deformable element and the outer cylindrical surface of said non-deformable member, said vanes serving to divide said working chamber into a pinrality of cylinders, said non-deformable element and said non-deformablemet'nber having a common axis offset from the axis of said rotor to control the volumetric displacement of said pump, adjusting means for altering the position of the common axis of said non-deformable element and said non-deformable member with respect to the axis of said rotor, driving means for effecting the rotatlon of said rotor, and fluid inlet and outlet means communicating with said working chamber whereby rotation of said rotor elfects the intake of fluid into the cylinders communicating with said fluid inlet means and the discharge of fluid under pressure from the cylinders communicating with said outlet means.

14. A pump constructed as set forth in claim 13, in which the cooperating pump parts including said rotor,

vanes, non-deformable element and non-deformable member rotate as a unit with each part having the identical angular velocity whereby Wear on the cooperating parts of the pump is materially reduced.

15. A pump constructed as set forth in claim 13, in which the adjusting means for altering the position of the common axis of said non-deformable element and said non-deformable member with respect to the axis of rotation of said rotor is an eccentric arranged to impart arcuate movement of the common axis of said element and member through the axis of said rotor.

16. In a pump the combination of a rotor including a hollow cylindrical portion, a non-deformable enveloping element surrounding the hollow cylindrical portion of said rotor, a cylindrical inner surface on said non-deformable element cooperating with the outer cylindrical surface on the hollow cylindrical portion of said rotor to form a working chamber, a non-deformable member housed within the hollow cylindrical portion of said rotor, a plurality of one-piece vanes arranged for radial sliding movement in the Wall of the cylindrical portion of said rotor, said vanes each including a pair of longi tudinally extending parallel cylindrical surfaces formed by portions of the surface of a cylinder having a diameter equal to the diflerence between the radii of said inner; cylindrical surface of said element and said outer cylindrical surface of said member, said longitudinally extending parallel cylindrical surfaces of said vanes serving to provide a means by which said element and member are retained in fixed spaced relationship by being disposed between said non-deformable enveloping element and said non-deformable member and having constant surface contact with said inner cylindrical surface of said noneformable element and the outer cylindrical surface of said non-deformable member, said vanes serving to divide said working chamber into a plurality of cylinders, said non-deformable element and said non-deformable member being retained in coaxial position by said vanes, adjusting means for altering the position of the common axis of said element and said member with respect to the axis of said rotor, driving means for effecting the rotation of said rotor, and fluid inlet and outlet means communicating' with said working chamber whereby rotation of said rotor effects the intake of fluid into the cylinders communicating with said fluid inlet means and the discharge of fluid under pressure from the cylinders communicating with said outlet means.

17. A pump constructed as set forth in claim 16, in which the cooperating pump parts including said rotor, vanes, non-deformable element and non-deformable member rotate as a unit with each part having the identical angular'velocity whereby wear on the cooperating parts of the pump is materially reduced.

18. A pump constructed as set forth in claim 16, in which the adjusting means for'altering the position of the common axis'of said non-deformable element and said non deformable member selectively'in opposite directions from concentric relationship with the axis of said rotor is an eccentric arranged to impart arcuate movement of the common axis of said non-deformable element and non-deformable member through the axis of said rotor.

19. In a pump the combination of a rotor including a hollow cylindrical portion, a non-deformable envelop.- lng element surrounding the hollow cylindrical portion of said rotor, a cylindrical inner surface on said nondeformable element cooperating with the outer cylindrical surface on the hollow cylindrical portion of said rotor to form a working chamber, a non-deformable member housed within said rotor, a plurality of one-piece vanes arranged for radial sliding movement in the wall of the hollow cylindrical portion of said rotor, said vanes each including a pair of longitudinally extending parallel cylindrical surfaces formed by portions of the surface of a cylinder having a diameter equal to the difference between the radii of said inner cylindrical surface of said element and said cylindrical surface of said member, said longitudinally extending parallel cylindrical surfaces of said vanes serving to provide a means by which said element and member are retained in fixed spaced relationship by being disposed between said non-deformable enveloping element and said non-deformable member and having constant surface contact with said inner cylindrical surface of said non-deformable element and the outer cylindrical surface of said non-deformable member, said vanes serving to divide said working chamber into a plurality of cylinders, said non-deformable element and said non-deformable member being retained in coaxial position by said vanes, adjusting means for altering the position of the common axis of said non-deformable element and said non-deformable member selectively in opposite directions from concentric relationship with the axis of rotation of said rotor to thereby etfectreversal of the direction offlow of the pump output and vary the capacity of the working chambers to'vary the displacement of the pump, driving means for effecting the'rota: tion of said rotor, and fluid inlet and outlet means communicating with said Working chamber whereby rotation of said rotor effects the intake of fluid into the cylinders communicating with said fluid inlet, means and the dis charge of fluid under pressure from the cylinders communicating with said fluid outlet means.

20. A pump constructed as set forth in claim 19, in which the cooperating pump parts including said rotor, vanes, non-deformable element and non-deformable member rotate as a unit with each part having the identical angular velocity whereby wear on the cooperating parts of the pump are materially reduced.

21. A pump constructed as set forth in claim 19, in which the adjusting means for altering the position of the common axis of said non-deformable element and said non-deformable member selectively in opposite directions from concentric relationship with the axis of said rotor is an eccentric arranged to impart arcuate movement to the common axis of said non-deformable element and said non-deformable member through the axis of said rotor.

22. In a rotary pump the combination of a rotor including a hollow cylindrical portion, a plurality of radially disposed vane receiving and guiding slots in the wall of the cylindrical portion of said rotor, a non-deformable enveloping element surrounding the hollow cylindrical portion of said rotor, an inner cylindrical surface on said non-deformable element cooperating with the outer surface on the hollow cylindrical portion of said rotor to form a working chamber, a non-deformable member having a cylindrical outer surface housed within said rotor, a plurality of one-piece vanes each comprising a quadrilateral prism including a pair of parallel flat sides and a pair of longitudinally extending parallel convex faces formed at portions of a cylinder having a diameter equal to the difference between the radii of said cylindrical inner surface of said element and said cylindrical outer surface of said member, each of said vane receiving slots in wall of the hollow cylindrical portion of said rotor adapted to cooperate with the flat sides on one of said vanes to position and guide the same for radial sliding movement in the wall of the hollow cylindrical portion of said rotor, said longitudinally extending parallel convexed faces of each of said vanes forming a means for retaining said element and said member in fixed spaced relationship by having one convex face of each of said vanes having constant line contact with the inner cylindrical surface of said non-deformable element and the opposite convex face of each of said vanes having constant line contact with the outer surface of the said non-deformable member, said vanes serving to divide said working chamber into a plurality of cylinders, adjusting means for altering the position of the common axis of said non-deformable element and said non-deformable member as a unit with respect to the axis of rotation of said rotor to thereby simultaneously vary the capacity of said chamber and the displacement of the pump, driving means for effecting the rotation of said rotor, and fluid inlet and outlet means communicating with said working chamber whereby rotation of said rotor effects the intake of fluid into the cylinders cornmunicating with said fluid inlet means and the discharge of fluid under pressure from the cylinders communicating with said outlet means.

23. A pump constructed as set forth in claim 22, in which the cooperating pump parts including said rotor, vanes, non-deformable element and non-deformable member rotate as a unit with each part having the identical angular velocity whereby wear on the cooperating parts of the pump is materially reduced.

24. A pump constructed as set forth in claim 22, in which the adjusting means for altering the position of the common axis of said non-deformable element and said non-deformable member with respect to the axis of rotation of said rotor is an eccentric arranged to impart arcuate movement of the common axis of said non-deformable element and non-deformable member through the axis of said rotor.

References Cited in the file of this patent UNITED STATES PATENTS 1,468,889 Trotter Sept. 25, 1923 1,607,383 Aurand Nov. 16, 1926 2,256,099 Mayer Sept. 16, 1941 2,266,191 Granberg Dec. 16, 1941 2,280,626 Carpenter Apr. 21, 1942 2,354,076 Tucker et a1. July 18, 1944 2,368,572 Say Jan. 30, 1945 2,458,023 Pike Jan. 4, 1949 2,469,097 Wrenn May 3, 1949 2,494,884 Lassmann Jan. 17, 1950 2,531,861 Schmitt Nov. 28, 1950 2,543,603 Schatzel Feb. 27, 1951 2,552,860 Oliver May 15, 1951 2,592,247 Coe Apr. 8, 1952 2,635,551 DeLancey Apr. 21, 1953 2,646,004 Bergen July 21, 1953 2,649,739 Hufferd et al. Aug. 25, 1953 2,678,607 I-Iutferd et a1. May 18, 1954 FOREIGN PATENTS 596,902 Great Britain Jan. 13, 1948 OTHER REFERENCES Ser. No. 239,352, Sturm (A. P. C.), May 11, 1943.