text: the basic configuration of the geroter device shown in fig1 to which this invention relates is well known in the fluid transmission art and may be appreciated in greater detail than will be described herein by reference to u . s . pat . no . 3 , 572 , 983 to mcdermott . referring now to the drawings wherein the showings are for the purpose of illustrating a preferred embodiment of the invention only and not for the purpose of limiting same , there is generally shown in fig1 a housing 2 having inlet and outlet ports 4 , 6 communicating through ports 7a and 7b in a rotatable valve member 7 with flow ports 8a and 8b , respectively in a port plate 8 to define a known commutator - type valving arrangement . the valve member is connected by a splined shaft member 9 for driving rotation with an externally - toothed star member 10 . housing 2 also includes a ring member 12 eccentrically receiving the star member 10 to define a plurality of increasing and decreasing volume chambers 14 in communication at one axial end with port plate 8 . ring member 12 has a plurality of pockets 16 axially - extending therethrough , each of which receive a cylindrical roller 18 rotatably disposed therein . each pocket is semi - cylindrical and configured to define axially - extending recesses 20 spaced from one another by a roller support surface 22 and communicating with one another by grooves or depressed areas 24 extending around support surface 22 . referring now to fig2 there is shown a ring member 12 having a plurality of n roller teeth 18 and a star member 10 having a plurality of n - 1 teeth 26 . in the embodiment illustrated the designation &# 34 ; n &# 34 ; refers to the number 7 and correspondingly &# 34 ; n - 1 &# 34 ; refers to the number 6 . ring member 12 eccentrically receives the star member 10 and the eccentricity of the arrangement is shown as the distance between the ring axis 32 and the star axis 28 . circumferentially - spaced and opening to the internal periphery of the ring member 12 , are n semi - cylindrical , axially - extending pockets 16 . each pocket 16 is adapted to rotatably receive a cylindrical roller 18 , each different roller individually lettered &# 34 ; a &# 34 ; through &# 34 ; g &# 34 ;. rollers 18 interact with the star teeth 26 to form variable volume chambers 14 which are individually identified by letters a through g . as thus described , the star and ring members 10 , 12 will interact with one another in the usual manner . more particularly with the ring member 12 fixed from rotating , the star member 10 will orbit hypocycloidally within the ring member 12 whereby the star center defines a circle 34 about the ring center , of radius equal to the eccentricity of the device . this movement of the star member opens and closes volume chambers a through g while the star member rotates a peripheral distance equal to one tooth spacing . more particularly the commutator valving will supply high pressure to three chambers and low pressure to three chambers with the seventh or odd chamber operating as a changeover chamber and being at any pressure between high and low . thus in the chamber position illustrated in fig2 the axis of eccentricity defined as a line extending between the ring and star member &# 39 ; s axes 32 , 28 , and shown as the y -- y axis separates high pressure chambers b , c and d from the low pressure chambers e , f and g with pressure chamber a being a changeover chamber at that instant . furthermore , it will be appreciated that the y -- y axis of eccentricity will rotate at an angular speed equal to the orbiting speed of the star member 10 . thus when the star member has orbited one tooth position in the direction of orbiting arrow 36 , which represents a motor application of the geroter , the y -- y axis will also have rotated and now will bisect roller c and pressure chamber g ; chambers c , b and a being at high pressure and chambers d , e and f at low pressure . thus , all volume chambers 14 lying on one side of the y -- y axis are either expanding or contracting and all expanding and contracting volume chambers are connected by the valving to either inlet or outlet ports 4 , 6 in the housing respectively . now referring to fig3 and 4 , it will be seen that the circular pockets 16 in ring member 12 are defined by a radius r nominally larger than the radius r &# 39 ; of the rollers 18 . each pocket &# 39 ; s configured surfaces includes a pair of axially - extending recesses 20 symmetrically spaced from the pocket centerline 34 and shown as having a rectangular configuration defined by inner , outer and rearward edge surfaces 31 , 33 , 35 . recesses 20 are separated from one another between their inner edge surfaces 31 by an arcuate roller support surface or land 22 and communicate with one another by means of grooves or depressed areas 24 shown extending around the roller support surface 22 . extending from the outer edge surface 31 of each recess 20 and opening to the internal periphery of ring member 12 is a pocket leading edge support surface 38 which is in radial alignment with roller support surface 22 . in the embodiment shown , tests have indicated that an included angle x of at least 120 ° between centers of recesses 20 having effective peripheral widths intercepting arcs y of at least 30 ° results in an efficient balancing arrangement . it will be appreciated that the position and configuration of lands 22 and depressed areas 24 can be varied to provide geometric configurations other than that shown , whereby recesses 20 can communicate with one another . the position of roller d within its pocket 16 is believed to result partly from the direction of the contact force exerted on roller d by its mating star tooth 26 as will now be described in detail with reference to roller - pocket configurations of the present invention shown in fig4 and that of the prior art shown in fig5 wherein like numbers designated by a prime (&# 39 ;) indicate like parts where applicable . in both figures the geometric arrangements are similar in that a cylindrical roller d , d &# 39 ; is disposed within an oversized cylindrical pocket 16 , 16 &# 39 ;. importantly the position of the roller within its pocket determines the placement of the line of tangency between the roller and pocket surface which by definition establishes line - to - line contact between roller and pocket . thus in the prior art shown in fig5 fluid under high pressure from volume chamber d &# 39 ; enters into the clearance z &# 39 ; at one end between pocket and roller and exerts a gradient hydrostatic pressure between pocket and roller , with the clearance approaching zero at the line of tangency . the position of the line of tangency in turn is determined by the direction and magnitude of the resultant force of the hydrostatic pressure , and the resultant contact force between star tooth and roller . importantly the direction of the contact force changes as the star member moves relative to the ring member and the line of tangency moves proportionately ( i . e ., compare tooth contact of roller d with that of roller c in fig2 to determine limits of roller - star tooth contact for roller d , d &# 39 ;). thus the peripheral portion of roller d &# 39 ; over which a constant hydrostatic force is exerted , increases and decreases as the star member moves relative to the ring member . the peripheral force distribution thus shown vectorially in fig5 for an instantaneous position of star tooth contact represents a summation of the gradient and constant hydraulic pressure over the roller surface which resolves itself into a changing resultant balancing force 42 &# 39 ; of higher magnitude having a larger , lateral force component and a much smaller balancing component in the y -- y direction than that which is obtained in the present invention . in the prior art the risk exists of the resultant force 42 &# 39 ; taking a direction which results in an outward directed &# 34 ; balancing &# 34 ; force in the y -- y direction . in such case , contact or sealing is lost between the star and roller members . in accordance with the present invention , the tangency line of contact is constantly maintained at the leading edge support surface 38 adjacent low pressure volume chamber e because fully hydrostatic pressure is communicated through clearance z ( normally between . 0005 inches (. 0127mm ) to . 0010 inches (. 0254mm ) as shown ) to each recess 20 by lands 24 . more particularly , if the tangency line tends to be positioned between recesses 20 because of star tooth loading , the hydrostatic pressure in that recess 20 and that portion of land 24 adjacent the peripheral portion of roller d which would otherwise be sealed is sufficient to bias roller d inwardly to establish hydrostatic pressure between the roller and pocket surfaces . this is more clearly shown by the vectorial peripheral force distribution shown in fig4 which represents a summation of the pressures acting axially along the depth of roller d . the force distribution shown is essentially a uniform radial load extending around the periphery of roller d from the recess 20 closest low pressure volume chamber e and a gradient radial load in the support surface 38 and resolves itself into a constant resultant force 42 of lesser magnitude but much better orientation than the resultant force 42 &# 39 ; of the prior art . to complete the force analysis , it should be noted that in both fig4 and 5 , a bearing lubricating film exists between the leading edge support surface 38 , 38 &# 39 ; adjacent low pressure chamber e , e &# 39 ; and the pocket . this film may develop a hydrodynamic force upon rotation of roller d , d &# 39 ; although such force , if developed , is considered insignificant when compared to the hydrostatic forces . the resultant force 42 in the present invention thus sufficiently biases the star member 10 downwardly forcing tooth contact to occur at points 44 , 46 on rollers g and a respectively . high pressure chambers b , c and d are thus sealed from low pressure chambers e , f and g and the geroter is balanced at this instant . in this connection , it will be noted that some pressure differential may occur between volume chambers a and b and a and g which will tend to displace rollers a , g within their pockets 16 in a position opposite to that shown as the pressure in changeover chamber a rapidly changes . however it is believed that the magnitude of the resultant force 42 is sufficient to bias rollers a , g toward the position shown . in any event if either or both of the rollers a , g were to receive any significant pressure buildup in their recesses 20 , the forces developed would tend to increase the sealing effect . it should also be noted that a pressure gradient does not exist behind rollers b , c , e , and f because the respective volume chambers on each side of these rollers are both at either high or low pressure . however , it will be noted that high pressure rollers b and c are biased into the position of roller d by the teeth of star member 10 and fluid is entrapped behind the rollers during this time . thus when roller c is exposed to volume chambers which are at high and low pressure on each of its sides during the orbiting of the star member as explained above , the fluid behind roller c is rapidly pressurized to form the above - defined pressure pattern . while the preferred embodiment has been explained as operating as a motor with the star member orbiting in the direction of arrow 36 , it should be apparent from the symmetry of the pocket construction that the radial balancing means disclosed herein will operate satisfactorily if the orbiting motion of the star member 10 is reversed resulting in reversed motor shaft rotation . similarly , the radial pressure balancing means , while described above in a motor application , will likewise function in a pump application . it is also appreciated that the magnitude and direction of resultant force 42 is achieved by the particular pressure pattern established behind the roller 18 which is characterized by being symmetrically distributed about the pocket periphery between recesses 20 . thus , the symmetrical pressure distribution will not be adversely effected if a third recess is placed in line with the pocket center , although satisfactory balancing has been achieved with only two recesses . the invention has been described with reference to a preferred embodiment . obviously , modifications and alterations will occur to others upon reading and understanding of the specification . it is my intention to include all such modifications and alterations insofar as they come within the scope of the present invention . it is thus the essence of my invention to provide a radial , pressure - balancing arrangement in a fluid - operated device of the geroter type which utilizes a predetermined rollerpocket recess configuration to produce a predetermined pressure gradient which effectively biases a ring - roller tooth to produce sealing engagement between the star and ring roller assembly .