US2159941A - Hydraulic machine - Google Patents

Description

y 23, 1939- E. E. GUINNESS 2,159,941

HYDRAULIC MACHINE Filed Nov. 14, 1954 5 Sheets-Sheet 1 Edwa'rd Ewur! Gun nnass lNvEMT-opZ May 23, 1939. E. E GUINNESS HYDRAULIC MACHINE Filed Nov.

14, 1934 5 Sheets-Sheet 2 fdv vm Pd Ewar'i' Guinness \NVENTOE,

May 23, 1939. E. E. GUINNESS HYDRAULIC MACHINE Filed Nov. 14, 1934 5 Sheets-Sheet 4 Edward Ewqv-i- Gui in mass \NVENTOL mun/L. LE AT y 1939- E. E. GUINNESS 2,159,941

HYDRAULIC MACHINE Filed Nov. 14, 1934 5 Sheets-Sheet 5 Edward. EuJoH- Guunnes$ 1NvaN'r UNITED STATES PATENT OFFICE HYDRAULIC MACHINE Edward Ewart Guinness, Wolverhampton, England, assignor, by direct and mesne assignments, to Fluvario, Limited, West Bromwich, England, a company of Great Britain Application November 14, 1934, Serial No. 752,966

In Great Britain September 11, 1933,

3 Claims.

This invention relates to hydraulic machines, and concerns machines such as rotary engines, pumps, vane motors, blowers, exhausters or the like, hereinafter referred to and included in the term rotary engine of the kind including stator and rotor members, the latter being adapted for" rotary movement and provided with vanes adapted to co-operate with the adjacent surface of the stator member in creatingthe head of the delivered fluid, or in applying the fluid energy to the rotor member.

Other objects will become apparent from the '20 2-2 of Figure 1.

Figure 3 is a detail view of the same construction.

Figure 4 is a sectional side elevation of a modified form of pump. Figure 5 is a sectional side elevation on the line 5-5 of Figure 4.

Figure 6 is a sectional end elevation on the line 66 of Figure 9 showing one form of apparatus for the hydraulic transmission of power embodying a pair of rotary engines constructed in accordance with this invention.

Figure 'I is a plan view of the construction shown in Figure 6.

Figure 8 is a sectional view on the line 88 of Figure 6 with certain portions of 'the apparatus a removed for the sake of clarity.

Figure 9 is a fragmentary side elevation of the same construction with one of the transfer mem bers removed and taken on the line 9-9 of Figure 8.

Figure 10 is an inverted plan view of a transfer member of the same construction.

Figure 11 is a perspective view of a portion of a modified form of vane employed in this construction.

Figure 12 is a part sectional view corresponding to the right hand side of Figure 6 showing a modification of the construction illustrated in Figures 6-10.

Figure 13 is a part sectional view on the line l3--l3 of Figure 12.

Figure 14 is a side elevation of the reversing valve shown in Figures 12 and 13. s

In the construction illustrated in Figures 1 55 to 3 of the drawings, the pump comprises a stationary casing III, a stator ll mounted slidably therein, and a rotor I! mounted rotatably upon the casing and disposed within the stator.

The casing comprises a hollow cast metal frame l3 of somewhat square form closed at each side by end plates M of similar shape, one of these plates having an attachment bracket [5 formed integrally therewith for securing the pump in position.

The rotor is' of cylindrical or disc shape and. is formed integrally at each end with a supporting spindle [6, one of these spindles forming also a shaft I! for driving the pump.

Each spindle is supported by a bearing [8 of the roller type, housed each within an annular flange formed as an axial extension of the adjacent end plate of..the casing, and for closing the bearing adjacent the driving shaft there is provided an annular cover disc l9 secured-to one of the aforesaid annular flanges, this cover disc being formed centrally with an annular recess containing a suitable oil seal 20 such as a felt. washer.

The other bearing is closed by a circular cover member 2| secured to the casing end plate.

For preventing the fluid from entering the bearings, each casing end plate is formed adjacent the rotor with an annular recess in each of which recesses is mounted a sealing ring 22 comprising an annular cage 23 of channel section,- shown more clearly in Figure 3, and having mounted within the channel and adjacent each side thereof a pair of metal rings 24, one of said rings having in abutment therewith an annular leatherwasher 25 of L section, including an inwardly extending flange which is adapted to be maintained by the fluid pressure in contact with the periphery of the spindle I6.

To ensure that the fluid shall urge the leather washer into abutment with the spindle, the sealing ring is provided with a fluid diverting strip 26 of annular form having an inclined edge 21 extending inwardly into abutment with the spindle, such edge serving to cut the adjacent fluid vfilm and to divert the fluid into the interior of the sealing ring so that it forces the washer 25 into contact with the spindle.

Conveniently, one or more springs 28 of plate form are provided for urging the strip 26 into engagement with the washer 25.

The stator l l is of generally annular form having an interior of circular configuration of a diameter somewhat greater than the diameter of the rotor, and opposite sides of the stator are formed with a suction port and a delivery port 29 and 30 respectively, for supplying and discharging the fluid to and from the rotor, and these ports are of rectangular section and arranged diametrically opposite one on each side of the rotor.

The upper and lower sides 3| of these ports diverge inwardly of the pump so that these sides are more or less tangential to the periphery of the rotor to facilitate the passage of the fluid through the ports.

Formed in the casing frame l3 on opposite sides thereof and adjacent the suction and delivery ports are suction and delivery passages 32 and 33 communicating respectively with these ports. Conveniently the frame I3 is provided adjacent each of these passages with a machined face for connection to suitable suction and delivery pipes not shown on the drawings.

The exterior of the stator adjacent the aforesaid suction and delivery ports is machined to provide on opposite sides thereof two plane parallel vertical faces 34 which engage slidably corresponding surfaces formed on the interior of the pump casing adjacent the passages thereof to permit of the necessary relative movement between the pump stator and rotor.

Thus a limited sliding movement of the stator is permitted in a vertical direction and perpendicular to the axis of the driving shaft, and the dimensions of the stator are such that when this is slidden its maximum distance in one direction relative to the rotor, the interior of one side thereof abuts the periphery of the rotor, while the exterior of the opposite side abuts the adjacent horizontal surface of the casing frame as is evident from Figure 1.

Although the construction illustrated in Figures 1 to 3 comprises a rotary pump, it should be understood that such an arrangement can be employed equally well as a vane motor, the discharge and suction ports 30 and 29 then becoming inlet and exhaust ports respectively for supplying fluid under pressure to the motor and for discharging it therefrom.

In order to maintain a fluid-tight connection between the engaging surfaces of the stator and casing adjacent the port 30 which serves to admit or discharge fluid under pressure to or from the rotor according to whether the apparatus is used as a motor or pump, while permitting the aforesaid sliding movement; the surface 34 of the stator adjacent the port 30 is formed with a recess 35 extending annularly around the port and having slidably mounted therein an annular sealing member or ring 36 which extends continuously and completely around the port. Convenientlv. the ring is formed from metal such as cast iron. phosphor-bronze. or from-leather, and is adapted for engagement with the adjacent surface of the casing.

In order to ensure such engagement. the recess 35 is provided with a plurality of passages 31 extending inwardly of the sta or and communicating with the port adjacent the periphery of the rotor, so that during the operation of the apparatus as a pump or motor fluid is forced under pressure through these passages to urge the sealing member into engagement with the housing. and there is provided around the port a fluid tight-joint which permits the relative movement between the stator and housing to take place.

Similar sealing means is provided adjacent the port 29 to permit of the direction of movement of the rotor being reversed for short periods if required when the apparatus is employed as a pump, the port 29 serving under such circumstances to deliver fluid under pressure from the pump.

Similarly, each end face of the stator may be provided with a recess extending annularly therearound and provided with similar sealing rings arranged in the same manner to provide a fluid-tight connection between the stator and the casing end plates.

Further, the sealing rings may be carried by the casing itself, although it is preferred to mount them in the movable member.

The pump rotor I2 is provided with a plurality of peripheral recesses 38 extending longitudinally for the full length thereof, and conveniently an even number; namely, four such recesses are provided arranged symmetrically around the periphery of the rotor.

The recesses are of U section, and have each slidably and rotatably mounted therein a vane 39 of cylindrical form extending for the full length of the rotor, the arrangement being such that the vanes are capable of movement in a radial direction and can thus maintain contact with the interior of the stator during the complete rotation of the rotor for various positions of the stator in relation thereto.

To maintain the vanes in contact with the interior of the stator, opposite recesses are connected each by a passage 40 extending diametrically through the rotor and each adapted to contain the fluid so that when the stator is eccentric in relation to the rotor, during the inward movement of one vane consequent on the rotation of the rotor, the vane opposite thereto is forced outwardly of the rotor by the resultant fluid pressure within the opposite recesses and their connecting passage and into contact with the adjacent surface of the stator.

To maintain the fluid pressure within the recesses 38 and connecting passages 40 during the continued movement of the rotor, the forward longitudinal edge 4| of each recess is provided with an inwardly extending groove 42 adapted to provide communication between the interiorof the pump and the base of each recess when the vane is in its outermost position and during its passage from the suction to the delivery port.

Conveniently the depth of each groove is such that on further movement of the vane past the delivery port towards the suction port, the inward movement thereof closes the communication between the recess and the interior of the pump and prevents the egress of the fluid.

By the expression forward is meant that side of the recess which is in advance of the vane in the normal direction of rotation, i. e., that side thereof which is subject to fluid pressure.

By constructing the vanes of cylindrical form and mounting them rotatably upon the rotor, the contact between the vanes and the adjacent surface of the stator is purely a rolling one, so that sliding friction is substantially eliminated and a considerable saving in wear on the vanes and stator results.

Further, by utilising the pressure of the fluid within the pump for forcing the vanes into engagement with the stator surface, the pressure of the vanes on to the surface is substantially constant for all positions of the stator in relation to the rotor.

In order that the position of the stator in relation to the rotor can be controlled, the stator is provided at its upper and lower sides with cam pieces 43 extending outwardly of the adjacent casing through apertures 44 provided in the frame thereof.

Adjacent the outer end of each cam piece, the casing is provided with a cam 45 adapted for engagement with the cam piece, and each mounted upon a suitable spindle 46 extending longitudinally of the pump, and the ends of these spindles may carry levers 41, the free ends of which are connected by a link 48 of somewhat curved form to provide clearance between it and the driving shaft, while the free end of one of the levers 41 may be connected to a suitable control lever or other operating means. 7

The cams are arranged with their apices at 90 in relation to one another, so that each cam serves to move the stator in one direction only.

With a pump constructed as described above, the fluid is sucked in through the suction port and discharged through the delivery port, the volume of fluid delivered being variable by sliding the pump stator relative to the casing and rotor.

As is evident from the description, the stator can be slidden into a position of maximum eccentricity in relation to the rotor in which the effective length of the vanes is at a maximum during their passage from the suction to the delivery port, so that for this position of the stator the maximum volume of fluid is delivered during a given rotation of the rotor.

Further, in this position, the periphery of the rotor and vanes engages the interior of the stator during movement from a delivery to a suction port, and the circulation of any fluid around the interior of the stator is prevented. Thus the maximum amount of useful work is done by the rotor with the stator in its position of greatest eccentricity.

The volume of fluid delivered by the pump may be decreased by operating the control gear to slide the stator from its maximum eccentricity until its interior is concentric with the periphery of the rotor, in which position the pump does not deliver any fluid, the latter being simply circulated around the interior of the stator.

On further operation of the control gear to slide the stator beyond its concentric position, the direction of flow of fluid within the pump is reversed, and fluid may be sucked in through the delivery port and expelled through the suction ,fport.

Thus, the quantity of fluid delivered from the pump may be varied infinitely from a maximum to a zero value and vice versa, while in addition its direction of flow may be reversed if desired.

Such a form of pump may be employed under all circumstances where itis desired to varythe quantity of the delivered fluid, and may be employed equally well for pumping water, oil or other liquids.

When employed as a vane motor, the mechanical power output of the apparatus is varied by operating the control gear to slide the stator II transversely of the rotor l2.

In the modified construction illustrated in Figures'4 and 5, the pump is of a form generally similar to the preceding arrangement, but in this construction, the stator II is of built up type comprising a portion 48 arranged annularly around the rotor and having an internal diameter somewhat greater than the diameter of the latter member, and this annular portion is provided at opposite ends with circular end discs 49 and 50 disposed adjacent each end of the rotor,

the former disc being formed integrally with the annular portion, and the latter constructed separately therefrom.

In this construction, instead of making the vane recesses or housings of U form in cross section they are of rectangular section, an even number convenientlyfour such recesses being again provided, and arranged symmetrically around the periphery of the rotor; while each vane comprises a blade 5| of rectangular section extending for the full length of the rotor and slidably mounted in each of the recesses or housings so that the blades can move radially with respect thereto.

The peripheral face of each blade is formed with a longitudinal recess 52 of circular form in which is mounted rotatabiy a roller 53 of a length equal to that of the recess and again adapted for rolling engagement with the adjacent surface of the stator, each blade and roller forming together a complete vane.

Conveniently, the depth of each recess 52 is made somewhat lessthan the diameter of each roller, and the longitudinal edges of each recess extend towards one another so that. the rollers are retained in the recesses, although in order to reduce friction, they are maintained out of contact with the base of the recesses.

As in the preceding construction, the bases of opposite recesses 38 are connected by circular passages 40 extending diametrically of the rotor and disposed at opposite ends thereof.

The diameter of these passages is slightly less than the width of the blades 5|, and the latter are each provided on their inner faces with a plunger 54 of circular form extending inwardly into the passages, the length of each of these plungers being such that the opposed ends of opposite plungers are spaced slightly apart for all positions of the pump stator within the housing.

With such an arrangement, as in the preceding construction, when during the rotation of the rotor a vane is forced inwardly of the rotor by the adjacent surface of the stator, the vane opposite thereto is forced outwardly by the fluid pressure between the opposed plungers and the rollers are maintained continuously in contact with the stator during the rotation of the rotor.

In order to maintain the fluid pressure within the passages 40 during the continued rotation of the rotor, the forward side face of each blade is provided with a semi-circular groove 55 disposed longitudinally thereof and communicating with a channel or passage 56 extending centrally of the plunger to the inner end thereof, each of these grooves being so disposed that they are in communication with the fluid within the stator during movement of the vanes from a suction to a delivery port only, the inward movement of the blades 5| during the remainder of such movement preventing the egress of the fluid during the passage of the vanes from the delivery to the suction port.

In this construction, the position of the stator within the housing, and hence the output of the pump is controlled by control gear comprising a control sleeve 51 mounted rotatabiy around the driving shaft II, the sleeve being provided at its rear end with a peripheral flange 58 carrying a rearwardly extending pin 59 which engages a radially extending recess 60 formed in the adjacent face of the stator end disc 49.

The forward end of the sleeve is provided with an operating lever GI, the arrangement being such that on moving the lever to pivot the sleeve, the stator is slidden transversely of the rotor to vary the quantity of fluid delivered by the pump.

Alternatively, suitable cams may be provided for sliding the pump stator as in t e preceding construction.

Although I have described the pump rotors in both constructions as being provided with four vanes, it should be understood that in both forms of the apparatus any suitable even number of vanes may be employed according to the diameter of the pump rotor.

Referring now to Figures 6 to 11 of the drawings, the hydraulic transmission apparatus there illustrated comprises a rotary pump shown generally at II 3, and a vane motor shown generally at II i disposed adjacent the end of the pump, the latter and the motor being contained in a common casing II comprising two pairs of horizontal side members IIB of somewhat curved form, one pair being disposed above and the other beneath the pump and motor, and the individual members of each pair being connected by a central vertical partition plate II! which serves to separate the pump from the motor.

For closing the end of the casing, the latter is provided with end plates H8 and H9 of circular form and disposed respectively adjacent the pump and adjacent the motor.

The opposite sides of the casing are open as at I20, and the side edges of the side members II6 are formed with vertical machined faces I2I arranged for the detachable reception of transfer members I22 adapted to transfer the fluid from the pump to the motor and vice versa in a manher to be hereinafter described.

Extending longitudinally through the casing and supported from roller bearings carried by the pump end plate H8 and by an annular bearing member II Ia supported from the partition plate, is a main driving shaft I 23 for imparting the drive to the pump.

Adjacent the end plate IIO the driving shaft is provided with a peripheral flange I24 formed integrally therewith, while disposed around the exterior of the shaft and extending from the end plate II8 to the partition plate II! is a pump rotor I25 of annular form provided adjacent one end with an internal recess I26 of annular shape within which is housed the periphery of the flange I2 3.

Conveniently, this flange is provided with a plurality of holes through which extend longitudinally and into the rotor securing pins I21, to secure the latter to the driving shaft.

The pump rotor I25 is provided with a plurality of longitudinally extending peripheral recesses I28 of part circular form arranged symmetrically around the rotor, the base portions of such recesses adjacent the pump end plate being constituted also by arcuate slots I29 formed in the periphery of the flange I24. Conveniently six such recesses are provided in the rotor.

Slidably and rotatably mounted in each of these recesses is a vane I 30 of hollow cylindrical form which extends for the full length of the rotor, and for preventing the oil or other fluid filling the interior of the vanes, the latter contain cork packing I30a.

Disposed within the pump portion of the easing and arranged above and beneath the rotor are a pair of stator members I3I each of somewhat arcuate form which extend for the full width of the side members IIG, and-these members are of a thickness substantially less than the distance between the periphery of the rotor and the adjacent inner surface of the side members, and are provided at their sides with vertical plane faces I32 which engage slidably corresponding faces formed on the adjacent surfaces of the two transfer members I22, so that each stator member can slide in a vertical direction towards or away from the surface of the rotor.

Conveniently, the inner face I33 of each stator member has a curvature similar to that of the periphery of the rotor, so that each member can be slidden in an inward direction until it is concentric with and in abutment with the rotor.

Extending longitudinally of the casing and between the front end plate I I8 and the partition plate H1, is a pair of baflles I34 disposed one at each side of the casing and centrally of the aforesaid opening I20.

The transverse section of each bafiie is of somewhat Wedge form, and these are so arranged that their inner sides just make contact with the periphery of the rotor and with the vanes during the rotation thereof, as will be apparent from Figure 6.

Each baflle is of such a depth that its upper andlower sides are spaced somewhat from the adjacent sides of the stator members to provide above or beneath each bafile suction ports I35 and discharge ports I36, two pairs of ports each comprising a suction and a discharge port being provided one on each side of the rotor, the suction port of one pair being arranged diametrically opposite the suction port of the other pair, and the delivery port of one pair being arranged similarly with respect to its corresponding port in the other pair.

As in the case of the construction illustrated in Figures 1 to 3, the interior of each stator member adjacent the ports is recessed somewhat as at I31, so that the fluid on admission to, or discharge from, the pump has a path which is substantially tangential to the periphery of the rotor.

In order to permit of relative movement between the stator members and the baflies, while providing a continuous surface for the abutment of the vanes during their passage past the suction and delivery ports, the upper and lower sides of each ba'fiie are recessed at I38 and I39 adjacent each end thereof as shown in Figure 9, and the sides of the stator members are provided adjacent the plates II! and II 8 with portions I40 which extend inwardly into these recesses as again shown in Figure 9.

The space between the said inwardly extending portions of each stator member provides the main opening of the suction and discharge ports, but to increase the area of these ports the sides of the baflle recesses I39 adjacent the partition plate are inclined as shown at I 4|, such inclination assisting also the movement of the fluid into and from the pump.

For maintaining the rotor vanes I30 in contact with the interior of the stator members and with the battles, for various positions of these stator members in relation to the pump rotor, the main driving shaft I23 is provided with a pair of spaced peripheral grooves I42 of semicircular section disposed within the interior of the rotor, and the recesses I28 containing nonadjacent vanes are connected to these grooves by openings I43 extending radially through the annular rotor I25, and the grooves and the recesses are arranged to contain fluid so that when during rotation one vane is forced inwardly of the rotor owing to the eccentricity of the stator member in relation thereto, the resultant fluid pressure produced forces the non-adjacent vanes outwardly thereof and maintains them incontact with the stator members and with the baffles.

To maintain the grooves and recesses filled with fluid during the continued rotation of the rotor, the forward edge of each recess is provided with grooves I44 corresponding to and arranged to function in a manner similar to the grooves 42 in the construction shown in Figures 1 and 2.

The driving shaft I23 is provided with an extension I45 which projects beyond the motor end plate vI I9, and rotatably mounted upon this extension is a sleeve I46 supportedfrom the extension I45 and from the end plate II9 by roller bearings I41 and I48 respectively.

Conveniently, the bearing I48 is carried by an annular bearing member I49 supported from the plate II9.

Adjacent the end plate II9, the sleeve I46 is provided with a peripheral flange I50, and is I formed adjacent this flange with an annular extension I5I upon which is mounted a rotor I52 again of annular form, generally similar in. configuration to the pump rotor i25 and mounted in the same manner. I

As in the case of the pump, the motor is provided with motor stator members I53 of a form generally similar to the pump stator members and again arranged above and beneath the rotor; but unlike the case of the pump, these members are stationary.

The motor rotor I52 is provided with'vanes I54 of a form similar to and housed in the same manner as in the case of the pump vanes, but it is preferred to guide the motor vanes and to maintain them in abutment with the interior of the stator member by providing the adjacent surfaces of the bearing members III and I49 with recesses of somewhat oval form to provide on each of these members cam faces I55 of a form corresponding to the configuration of the interior of the stator members and adapted to engage each end of the vanes adjacent the inner side thereof to maintain them in engagement with these members.

Since during rotation of the motor rotor a certain sliding movement must occur between the motor vanes and either the inner face of the stator members or the cam faces if the vanes are simultaneously in contact with both of these faces, it is preferred to provide means for maintaining the vanes out of actual abutment with the cam faces during the normal working of the apparatus.

For this purpose, the annular extension I5I of the sleeve I46 is provided with a peripheral groove I56, while the rotor is grooved internally at I56, and as in the case of the pump, the vane recesses are connected to these grooves by openings I51, and the recesses and openings are kept filled with fluid in a manner similar to the pump to maintain the vanes in abutment with the inner face of the stator members and out of contact with the cam faces I55.

In order to reduce the resistance to rotary movement of the motor vanes, these may be provided with a plurality of spaced peripheral grooves I5'I disposed longitudinally of the vanes as shown in Figure 11.

Suitable oil seals I58 are provided for preventing the leakage of oil from the roller bearings of both the pump and the motor.

The motor is provided with bafiles I59 disposed in a manner similar to the pump baflies; while the sides of the stator members I53 are provided similarly at their ends with inwardly extending portions I60 which since the motor stator members are stationary, abut the baffles and thus provide a continuous surface for the engagement of the motor vanes.

In a manner similar to the pump, the baffles co-operate with the adjacent sides of the stator members to provide at opposite sides of the motor a pair of inlet and exhaust ports I6I and I62 respectively, corresponding to the suction and discharge ports of the pump.

Conveniently, the motor inlet ports I6I are arranged diagonally opposite to the pump discharge ports I36, the motor exhaust ports I62 being disposed similarly with respect to the pump suction ports as shown in Figure 9, for a reason which will be hereinafter apparent.

In order to'provide a continuous circulation of the fluid through the apparatus, it is necessary that the pump discharge ports I36 should be connected to the motor inlet ports IIII, and that the motor exhaust ports I62 should be connected to the pump suction ports I35.

For this purpose the transfer members I22 are formed as castings ofhollow form provided on one side with a machined face I63 adapted for abutment with the adjacent face I2I and I64 of the side members H6 and bafiies I34 and I59 respectively, and each transfer member is formed with a pair of internal passages I65 and I66, the passage I65 being disposed adjacent said machined face and the passage I66 remote therefrom.

Each of these passages is of somewhat U form, the passage I65 being of substantially circular section while the passage I66 is of elongated section. Each of the former passages is arranged to provide a communication between the pump delivery ports I36 and the motor inlet ports I6I and thus serve as pressure chambers for connecting these ports, while each of the latter passages is arranged to provide a communication between the motor exhaust ports I62 and pump suction ports I35, and thus provide a suction chamber for connecting these latter ports.

Thus, fluid is admitted from each suction chamber I66 through the suction ports I35 to opposite sides of the pump rotor, is swept by the pump rotor vanes co-operating with the adjacent stator member to the following discharge port, and is deflected therethrough by the adjacent bafile and by the engagement of the latter with the periphery of the pump rotor or vanes thereof, and in a direction which is somewhat tangential to the exterior of the rotor.

The fluid now under a considerable pressure is forced through the pump discharge ports I36 into each pressure chamber I65, and passes therefrom through the motor inlet ports I6I into the motor, and is forced against the vanes on opposite sides of the motor rotor, being again similarly deflected by the motor bafiles I59 through the motor exhaust ports I62 back into the suction chambers I66.

Thus a continuous circulation of the fluid from the pump to the motor and back again is set up, while by arranging the pump discharge ports diagonally opposite to the motor inlet ports, and the motor exhaust ports diagonally opposite to the pump suction ports, any sudden change in the-direction of the fluid during its passage from the pump to the motor and back is avoided so that hydraulic losses are reduced to a minimum, while the motor rotor is driven inthe same direction as the direction of rotation of the pump rotor.

Further, by admitting the fluid to opposite sides of the pump and motor rotors, the work done on opposite sides of each rotor is substantially equal and no unbalanced transverse pressure is applied to the rotors, so that the whole apparatus is mechanically and hydraulically balane :d,

Again, by admitting the fluid to opposite sides of the rotors useful work is performed on both sides of the pump and motor, and in fact the amount of work done with an apparatus constructed as shown in Figures 6 to 11 of the drawings is approximately twice that performed with construction of substantially the same size wherein the pump and motor are each provided with a single fluid supply and discharge port in which useful work is done by or on one half only of the respective rotors.

Again, by disposing the bafiles so that the whole of the fluid is expelled through the discharge or exhaust ports as the case may be, no wasteful work is done by circulating the liquid around the interior of the pump or motor, and the efliciency of the apparatus as a whole is enhanced.

Suitable control means are provided for varying the position of each stator member in relation to the pump rotor and thus to vary the volume swept out by a vane during a given revolution of the rotor and hence the volume of the fluid delivered from the pump to the motor during such revolution.

Conveniently such control means comprise the provision on the medial part of each stator member of a bracket I61 extending outwardly therefrom, and which is slidable in a suitable opening provided in the adjacent side member I I6, and the free end of each bracket is connected pivotally to one end of a lever I68, the opposite end of the lever being supported from a spindle I69 supported pivotally upon a pair of lugs I10 carried by the adjacent side member, the spindle being provided with a further lever I1I extending oppositely to the lever I68, and each of these levers I1I are connected pivotally at their free ends to one of a pair of screws I12 and I13 which extend towards one another, the former screw having a, right hand thread and the latter a left hand thread, each thread being of the same pitch and being connected by a common turn-buckle I14 which is adapted to be rotated from suitable operating means not shown in the drawings.

As will be apparent on rotating the turn-buckle, the screws are moved in opposite directions to slide the two stator members I3I towards or away from the rotor by an equal amount, so that the work done on each side of the rotor is equal for all positions of the stator members in relation to the rotor and consequently for all variations in the amount of power transmitted from the pump to the motor.

Further, by admitting the fluid to opposite sides of the rotor, the work done by the co-operation of the vanes and stator member is equal for each stator member, so that the fluid pressure on the interior of the stator members which tends to move these in an outward direction, is equal for each member, and by connecting the latter by control gear in the manner described the fluid pressure on the two stator members is counterbalanced and there is no resultant tendency for the stator members to move transversely of the rotor as in the case with constructions such as those shown in Figures 1 to 5 wherein more work is done on one side of the rotor to produce a nection to suitable resultant fluid pressure tending to move the stator member into a position in which it is concentric with the rotor.

Further, in the arrangement illustrated in Figures 6 to 11 of the drawings, the two stator members can be slidden from a position in which they are displaced by a maximum distance from the periphery of the pump rotor, and the quantity of fluid delivered by the pump to the motor for a given rotation of the rotor is at a maximum and the greatest amount of power under maximum load conditions is transmitted by the apparatus, to a position in which they are adjacent the periphery of the rotor, wherein no fluid is delivered to the motor and no power is transmitted by the apparatus, the latter being thus in neutral gear.

Thus, a considerable variation may be obtained in the amount of power transmitted.

If desired a still further variation may be obtained by constructing the motor stator members in a manner exactly similar to the pump stator'members and arranging them for movement towards or away from the motor rotor, similar control means being provided as in the case of the pump. With such an arrangement the cam faces I55 are omitted, and the means for maintaining the vanes in engagement with the interior of the stator members may be exactly similar to that employed in the case of the pump.

As will be apparent, when the pump stator members I3I are adjacent the periphery of the pump rotor, the fluid is expelled almost completely from the pump, and in order to enable the fluid readily to fill the pump when it is desired to again reach normal output, quickly, the transfer members are each apertured as at I15 and provided with nipples I16 adapted for conpipes which serve to supply fluid from a reservoir not shown in the drawings to the suction chambers I66 and hence to the interior of the pump.

In order that the direction of rotation of the motor rotor canbe reversed with respect to the pump rotor, as for instance when the apparatus is employed as an infinitely variable gear for mechanically propelled vehicles, means may be provided for reversing the direction of flow of the fluid through the motor.

For this purpose, each of the transfer members I22 is, as shown in Figures 12 to 14, made of hollow cylindrical form with the central axis thereof disposed longitudinally of the apparatus and parallel to the axis of rotation. of the pump and motor rotors, the transfer members being again provided with peripheral flanges which are bolted to the adjacent side members II6 of the casing.

Mounted within each of the transfer members is a reversing valve I11 of cylindrical form adapted for rotation about an axis parallel to the axis of rotation of the rotors and provided at one end with an operating spindle I18 which projects through a cover plate I19 which serves to secure the valve within thetransfer member.

Each of these reversing valves is formed internally at one side thereof with pressure and suction chambers I65 and I66 respectively and of a form similar to the pressure and suction chambers of the preceding construction and again adapted to provide respectively a communication between the pump delivery and motor inlet ports and between the motor exhaust and pump suction ports with the valve in the position shown in Figure 12.

Formed in the opposite side of each reversing valve is a pair of spaced reverse ports I80 of substantially U form and arranged with their planes parallel to the axis of rotation of the valve and each of these ports is adapted on movement of the valve through 180 to provide communication between a pump delivery port I36 and motor exhaust port I62 or between a motor inlet port I6! and a pump suction port I35.

In this latter position of the valve, the fluid is admitted to and discharged from the motor through the motor exhaust and inlet ports respectively, so that the direction of flow of the fluid through the motor is reversedwith consequent reversal of the direction of rotation of the motor rotor I52.

In order that the fluid may be again supplied readily to the pump after the apparatus has been in the neutral position with the stator members I3I in abutment with the periphery of the pump rotor, each valve is provided with a fluid supply passage I8I extending diametrically therethrough and adapted with the valves in the position shown to provide a communication between each of the suction chambers I66 and a suitable nipple I16 provided on the exterior of each transfer member and adapted as in the-previous construction,

for connection to a suitable fluid supply reservoir not shown in the drawings.

With the valve in the reverse position, the end of the supply passage I8I is closed by the seating thereof on the medial part I82 of the transfer member adjacent the baffles.

Any suitable control gear may be provided for rotating the two reversing valves simultaneously and by an equal movement to reverse at one operation the direction of flow of the fluid at both sides of the motor rotor.

The fluid employed for transmitting the power from the pump to the motor is preferably oil, although other suitable fluids may be used.

The apparatus is adapted to transmit the POW- er to a driven shaft at I83 and in order that this shaft may be driven at the same speed as the driving shaft I23, while at the same time unnecessary wear of the transmission apparatus may be avoided under such conditions, clutch means, shown generally at I84 are provided for alternatively placing the driven member in direct engagement with an extension I85 of the driving shaft or with an annular extension I86 of the rotor member I46 which is provided with clutch dogs I81 for this purpose. Thus, the shaft I83 may be driven at the same speed as the driving shaft I23 and in the direction of rotation of the latter, or an infinitely variable drive may be imparted to the driven shaft which may be rotated in either direction relative to the driving shaft.

It should, however, be understood that such clutch means forms no part of the invention forming the subject of the present application.

If desired in order to maintain a fluid-tight connection between the pump stator members, and in addition the motor stator members if the latter are movable, and the adjacent surfaces of the transfer members or of the plates H1, H8, H9, these surfaces or the surfaces of the stator members may be provided with sealing means similar to that shown at 36 in the construction illustrated in Figure 1; such arrangement with this construction obviating the necessity to machine accurately the co-operating surfaces.

As will be apparent from Figure 8, the motor end plate H9 is spaced from the partition plate III by a distance less than the spacing off the latter from the pump end plate II8, while the length of the motor stator members and motor vanes is less than the length of the corresponding pump members, although the radial dimensions of these members and of the two rotors are similar.

With such an arrangement, the motor rotor is driven at a speed substantially greater than that of the pump rotor, and is particularly suitable in cases where the apparatus is employed for transmitting power from a slow running oil engine, but it should of course be understood that the length of the said motor members may be made equal to or greater than that of the corresponding pump .members according to the speed of the driving shaft and to the speed at which it is desired to transmit the power. For instance, the length of the motor members may be considerably greater than that of the corresponding pump members where the power is obtained from a high speed petrol engine.

Such changes in gear ratio may of course be obtained also by altering the respective radial dimensions of the pump and rotor members to vary the ratio of the swept volumes of the pump and motor as required.

Although I have described the invention as being applied to a rotary pump and a vane motor combined to provide apparatus for the hydraulic transmission of power it is understood that the invention is equally applicable to a pump which is unprovided with a motor and employed for any purpose where it is desired to vary the hydraulic head of the delivered fluid, or, alternatively, it may be applied to a vane motor, blower or exhauster wherein no pump is provided, and it is desired to vary the mechanical output of such an engine, the fluid being supplied from any suitable external source.

Further, the vanes of the form shown in Figures 4 and 5, may be employed in the construc tion shown in Figures 6 to 14, while instead of providing the pump and motor rotors with six vanes it should-be understood that any suitable even number of vanes may be employed according to the diameter of the rotors.

I claim: I

1. In a rotary engine, stator and rotor members, said rotor having a plurality of recesses extending substantially in the direction of its axis of rotation, vanes of cylindrical form rotatable in said recesses and adapted for rolling engage- -ment with the adjacent surface of the stator member, said vanes being movable inwardly and outwardly of said recesses, said stator surface being eccentric in relationto said rotor, said engine having a cam face concentric in relation to said stator surface but spaced therefrom, said cylindrical vanes extending between said cam face and stator surface and having a diameter slightly less than the distance between said cam face and stator surface, and means for maintaining said vanes out of actual contact with the cam face and in rolling engagement with said,

rotor, said engine having a cam face concentric in relation to said stator surface but spaced therefrom, said cylindrical vanes extending between said cam face and stator surface and having a diameter slightly less than the distance between said cam face and'stator surface, said rotor having passages adapted to supply fiuid under pressure from said engine to the bases of said recesses and maintain said vanes out of actual contact with the cam face and in rolling engagement with said stator surface during the rotation of the rotor.

I aim a rotary engine, stator and rotor members, said rotor having a plurality of recesses extending substantially in the direction of its axis of rotation, vanes of cylindrical form rotatable in said recesses and adapted for rolling engagement with the adjacent surface of the stator member, means for supplying fluid to said vanes and for discharging said fluid from the engine, said stator surface being eccentric in relation to the adjacent surface of the rotor member, said stator and rotor being relatively displaceable to vary said eccentricity, said eccentric stator surface being adapted during the rotation of the rotor to permit of some vanes moving outwardly in relation to their recesses and others simultaneously moving inwardly in relation to their recesses to an extent dependent on said eccentricity, each of said vane recesses having in one side wall thereof a groove extending from the edge of the recess towards the base thereof, each of said grooves being capable of feeding fluid under pressure from the interior of said engine to the base of the vane recess, said rotor having passages of substantial cross section connecting recesses of outwardly moving vanes to recesses of simultaneously inwardly moving vanes, said grooves having a length substantially less than the diameter of the adjacent cylindrical vane, said vanes for various relative displacements of the stator and rotor members being adapted in their innermost positions in relation to their recesses to close the communication provided by said grooves between the interior of the engine and the vane recesses, and in their outermost positions in relation to their housings to open such communications and permit of fluid under pressure being fed to the recesses.

EDWARD EWART GUINNESS.

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