US3901630A

US3901630A - Fluid motor, pump or the like having inner and outer fluid displacement means

Info

Publication number: US3901630A
Application number: US449000A
Authority: US
Inventors: John B Kilmer
Original assignee: Individual
Current assignee: Individual
Priority date: 1971-07-28
Filing date: 1974-03-07
Publication date: 1975-08-26
Anticipated expiration: 1992-08-26

Abstract

Improved fluid-mechanical and mechanical-fluid energy translation devices, such as fluid motors, pumps and certain actuators, meters, couplers and the like of the type having an orbital member disposed between a rotor element and a stator element and coupled with one of the elements by fluid displacement means and with the other element by gear means, are provided by employing therein a plurality of eccentric means for positively but shiftably mounting the member upon the element to which it is coupled by fluid displacement means in manner restricting relative motion between the member and the lastmentioned element to relative orbital motion. The element upon which the member is thus mounted may be either a rotor or a stator element and may be either the inner or the outer of the elements in various embodiments of devices incorporating the invention. The eccentric means, which are essentially cranks or shafts with offset axes, significantly are alone sufficient to accomplish the positive, shiftable mounting of the member and the restriction of same to relative orbital motion and to do so quite independently of any other fluid and mechanical couplings that may exist between the member and the elements in various particular forms of devices. The preferred embodiment also provides a further improvement in devices of this type employing vanes to define fluid displacement chambers by arranging the parts to maintain the pair of vanes bounding each chamber parallel to each other throughout the operating cycle, thereby maintaining the chordal transverse cross-sectional area of each chamber substantially constant throughout such cycle. The devices embodying the invention are characterized by increased efficiency and reliability, reduced wear on certain primary parts, and greater economy of manufacture by virtue of reduced strength and looser tolerance requirements in connection with certain primary parts.

Description

United States Patent [1 1 Kilmer 1 FLUID MOTOR, PUMP OR THE LIKE HAVING INNER AND OUTER FLUID DISPLACEMENT MEANS John B. Kilmer, 900 S. 8th St., Lamar, Colo. 81052 [22] Filed: Mar. 7, 1974 [21] Appl. No.: 449,000

Related US. Application Data [62] Division of Ser. No. 166,672, July 28, 1971, Pat. No.

[76] Inventor:

[52] US. Cl. 418/59; 418/61 R; 418/61 B;

418/67; 418/186 [51] Int. Cl. F01C l/02; F03C 3/00; F04C 1/02 [58] Field of Search 418/61 R, 61 A, 61 B, 59,

Primary Examiner-John J. Vrablik Attorney, Agent, or FirmSchmidt, Johnson, Hovey &

Williams [5 7] ABSTRACT Improved fluid-mechanical and mechanical-fluid energy translation devices, such as fluid motors, pumps and certain actuators, meters, couplers and the like of the type having an orbital member disposed between a rotor element and a stator element and coupled with 1 Aug. 26, 1975 one of the elements by fluid displacement means and with the other element by gear means, are provided by employing therein a plurality of eccentric means for positively but shiftably mounting the member upon the element to which it is coupled by fluid displacement means in manner restricting relative motion between the member and the last-mentioned element to relative orbital motion. The element upon which the member is thus mounted may be either a rotor or a stator element'and may be either the inner or the outer of the elements in various embodiments of devices incorporating the invention. The eccentric means, which are essentially cranks or shafts with offset axes, significantly are alone sufficient to accomplish the positive, shiftable mounting of the member and the restriction of same to relative orbital motion and to do so quite independently of any other fluid and mechanical couplings that may exist between the member and the elements in various particular forms of devices. The preferred embodiment also provides a further improvement in devices of this type employing vanes to define fluid displacement chambers by arranging the parts to maintain the pair of vanes bounding each chamber parallel to each other throughout the operating cycle, thereby maintaining the chordal transverse cross-sectional area of each chamber substantially constant throughout such cycle. The devices embodying the invention are characterized by increased efficiency and reliability, reduced wear on certain primary parts, and greater economy of manufacture by virtue of reduced strength and looser tolerance requirements in connection with certain primary parts.

13 Claims, 18 Drawing Figures AW-HEP im g sum :1 OF 6 PATENTED 901 30 sum 2 OF 6 PATENTED AUGZ 6 I975 SHEET u F PATENTEB AUG 2 6 I975 sum 5 pg g FLUID MOTOR, PUMP OR THE LIKE HAVING INNER AND OUTER FLUID DISPLACEMENT MEANS This is a division of application Ser. No. 166,672,

which the aforesaid and other limitations and disadvantages of conventional constructions are overcome.

it is another important object of this invention to provide such improved devices in which operating effifiled y 1971, HOW 5 ciency and reliability are increased, and in which wear This invention relates to energy translation devices u on the epicyclic gear structure is decreased. more particularly, to that Class Of devices It is another important object of the invention to proployed for translating energy in the form Of presvide uch an improved device can be man ifac. Sure into energy in the term of mechanical rotation tured more economically than conventional devices for vice versa, which commonly include devices employl0 Comparable purposes b virtue f th l we t ength able as fluid Pressure dl'lven motors Conversely as factors and looser tolerances that may be employed P p as well as eettam devlces empleyable as f particularly in connection with the epicyclic gear structors, meters, couplers and the like. Still more specifi ture the invention is eoncer'ned h Improvements It is another important object of the invention to pi'O- such devices of the type having a P of Spaced-apart, vide Such improved devices in which the orbital maconcentric, relatively rotatable machine elements and chine member is positively but shiftably mounted upon an orbital machine member disposed therebetween and one of the machine elements by means of a plurality of operably couPlediwlth at least one of the l freely rotatable eccentric crank or shaft mechanisms ments by fluld glsplacement g s at F which are operable, independently of any other fluid or one of e me elements y amca coup mg mechanical coupling that may exist between the orbitmeans typically in the form of what is commonly called g member and the machine elements, to Support ahd g i l l t h th inv mien confine the motion of the orbital member relative to Y' 0 genera c ass e e the machine element upon which it is thus mounted to pertains and which employ a pair of relatively rotatable free Orbital movement t d' i elerilents m combination with an m erme t It is another important ob ect of the invention to proorbital machine member therebetween assume a varivide such improved devices in which any requirement ety of forms, suitable examples of which may be found f or a 1:1 gear mesh between the orbiting member and in the following patents:

U.S. Pat, No, Title Patcntee Granted 3,215,043 Hydraulic Torque M. J. Huber Nov. 2, 1965 Motors 3,391,608 Hydraulic Torque M. J, Huber July 9, 1968 Motor 3,490,383 Hydraulic Pump Or .I. T. Parrett Jan. 20, 1970 Motor 3,516,765 Fluid Actuated Boyadjieff et June 23, 1970 Actuator ul Although prior devices of the general class perfo afrarne element, as required in many conventional desatisfactorily in many applications, they are typically vices in which the Orbital member floats, is eliminated,- subject to various limitations and disadvantages pecuand in which the epicyclic gear surface associated with liar to the particular construction thereof, many of the orbital member may be provided on the outer cirwhteh pp to be attributable to the faet that the cumference of the latter with resultant reduction of biting member is normally floated between the inner l d d stresses n h teeth th f" and outer machine elements so that the device must de- Another important object of the invention is to pr p "P the interfacing of epicyclic gear faces on vide such improved devices in which the orbital moveone element and the orbital member to confine the latment f h i l member may be employed to er to an Orbital P of motion as well as to Produce 5O complish directly the valving employed to control the the desired relative rotation between such element and exhausting of from an annular ethe member. The mentioned conventional relationship ties of i l t ha ber on a progressively cybetween the orbiting member and the machine ele- Cled basis ments between Which it is interposed, result In a heees' Another important object of this invention is to proy for eonstl'uetmg the p y e gear faces with vide such improved devices in which operating effistantially greater strengths and tighter tolerances than ciency is improved by the employment of pairs of Shim Ou e feqllll'ed It the eh gear mechanfsm a able, displacement chamber bounding vanes extending not required to confine the orbiting member to its orbibetween the orbital member and one of the machine tal path, as well as to produce relative rotation. Moreelements and which remain parallel to each other Over, h n the epicyclic gearing itself is empl y 0 throughout the operating cycle to maintain the chordal confine the Orbiting member to tts ol'bltal P the transverse cross-sectional area of each chamber subcreased friction and strains, which can be very substanmi l Constant throughout such cycle, so h the tial in this class of device, result in undue wear and rate f fl id fl i and out f individual displace- Sometimes breakage t0 the epicyclic geatlng e ment chambers may be kept in phase with the areas of The same factors have also been found to seriously Opening f input and exhaust valves which are i limit the efficiency of operation that may be achieved with a device of given construction.

Accordingly, it is the primary object of this invention to provide improved devices of the mentioned class in trolled in sinusoidal fashion by the movement of the orbital member, as contrasted, with conventional constructions in which the effective cross-sectional area of the chamber or piston is a function of the stroke posi- 3 tion so that fluid flow is not precisely phasedwith valve operation I Another important object of this invention is to proplings' in device constructions as diverse as vane definedfluid chamber devices, radial ball piston devices, hollow'cylinder virtual piston devices, and gerotor devicesm I Another important object of this invention is to provide device's employing the mentioned improvements which'are further characterized bythe use of fluid couplings between the orbital member and both of the machine elements.

Still other objects of the invention, including certain significantdetailsofconstruction, will be made clear or become apparent to those skilled in the art from the accompanying drawings and the description of illustrative embodiments of the invention that follows.

Inithe accompanying drawings:

FIG. 1 is a perspective view of a currently'preferred energy translation device embodying the invention;

FIG. 2 is a central cross-sectional view of FIG. 1 taken th'roughthe axis thereof;

FIG. 3 is a cross-sectional view taken on line 33 of FIG. 2;

FIG. 4 is a cross-sectional view taken on line 4-4 of FIG. 2;

FIG. 5 is a fragmentary, enlarged, cross-sectional view taken on line 55 of FIG. 3;

FIG. 6 is a fragmentary, enlarged, cross-sectional view taken on line 6-6 of FIG. 3;

FIG. 7 is a perspective view of one preferred embodiment of eccentric shaft employed in the device of FIG.

FIG. 8 is a perspective view of one of the vanes employed in the device of FIG. 1-,

, FIG. 9 is a central cross-sectional view of another embodiment of energy translation device incorporating the invention taken on the axis of such device;

FIG. 10 is a cross-sectional view taken on line 1010 of FIG. 9; i 7

'FIG. 11 is a fragmentary, cross-sectional view taken on'line 11-11 of FIG. 10;

FIG. 12 is a transverse cross-sectional view of another'emb'odiment of energy translation device incorporating the invention;

FIG. 13 is a central cross-sectional view of still another embodiment of energy translation device incorporating the invention taken through the axis thereof;

FIG. 14 is a cross-sectional view taken on line l4l4 of FIG. 13;

FIG. 15 is a fragmentary,cross-sectional view taken on line l5-15 of FIG. 13; I

FIG. 16 is a central cross-sectional view of still another embodiment of energy translation device incorporating the invention; I FIG 17 is a cross-sectional viewtaken online 17-17 of FIG. 16; and d I v FIG. 18 is a fragmentary, cross-sectional view taken on line 18-l8 of FIG. 16.

Referring first to FIGS. 1-8 inclusive, the preferred embodiment of the invention will be illustrated and d escribed in connection with the devicegenerally desi'g 4 nated 20. The device 20 broadly includes a manifold -22, a valve and bearing block 24, an outer hub element 26, an inner element 28, an orbiting ring member 30, an end plate 32 and a main shaft 34. The manifold 22, the block 24, the inner element 28, and the end plate 32 are all secured together as a unit by the main shaft 34 and by bolt means as at 36, with a spacer 38 being provided between the block 24 and the plate 32 around each bolt 36. The group of parts just mentioned are all also keyed to the main shaft 34 by a key as at 40. The axial dimension of spacers 38 and inner element 28 is F slightly greater than the axial dimension of orbiting member 30 to provide running clearance for the member 30 in fluid sealed relationship between block 24 and plate 32. For illustrative purposes, in a typical application of the device 20, the manifold 22, block 24, inner element 28, plate 32 and main shaft 34 may all be stationary and can be mounted on a base frame 42 of other equipment by means of bolts as at 44. The outer hub element 26 is rotatably mounted upon an end portion 46 of main shaft 34 by suitable ball bearing means as at 48, and a sleeve bearing support surface 50 is also provided between the hub element 26 and the block 24, a seal being effected between the hub 26 and block 24 by an O-ring as at 52. The extremity of hub 26 adjacent end portion 46 of the shaft 34 is preferably sealed by a removable cap 54 held in place by bolts as at 56, with an O-ring seal as at 58.

In the embodiment of device 20 chosen for illustra tion, it will be perceived that the outer hub element 26 is rotatable relative to the inner element 28, as well as the manifold 22, the block 24 and the plate 32, about the axis of the main, shaft 34. Accordingly, the hub element 26 is provided with a plurality of threaded studs extending therefrom to facilitate mechanical coupling of the hub element 26 with an external rotatable assembly. When the device 20 is powered from a source of fluid under pressure, as hereinafter more fully described, the device 20 functions as a fluid-driven motor which is particularly adapted to low-speed, hightorque application, and it will be understood that the outer, rotatable hub element 26 is then rotationally driven by the action of device 20 so that the studs 60 would be employed to couple the hub to an external asstruction and operation of the device 20 in the context of its application as a fluid driven motor.

Referring now particularly to FIG. 3, in conjunction with FIG. 2, it will be seen that the outer hub element 26 is provided on its inner circumference with a set of inwardly facing gear teeth 62 aligned with a set of outwardly facing gear teeth 64 on the outer surface of the generally ring-shaped orbiting member 30. The

teeth

62 and 64 together present what is normally referred to as an epicyclic gear transmission or coupling between the orbiting member 30 and the outer rotatable hub element 26, it being understood that there will be a lesser number of teeth 64 on the member 30 than there are teeth 62 on the elementi26; but that'the sets of

teeth

62 and 64 are appropriately shaped for proper meshing as the member 30, which is of lesser outer diameter than the corresponding inner diameter of hub element 26, orbits within the latter. Thus, it will be perceived that, assuming the provision of some means for orbiting the member 30 while constraining the same against rotation, the teeth 64 will walk with respect to the teeth 62 on hub element 26, thereby driving and im parting rotational movement to the latter.

The inner diameter of the orbiting member 30 is somewhat larger than the outer diameter of the inner element 28, presenting a space 66 therebetween. A plurality of fluid displacement chambers 68 are formed within the space 66 by pairs of

vanes

70 and 72. As best shown in FIG. 8, each of the

vanes

70 or 72 includes a pair of

cylindrical end portions

74 and 76 interconnected by a web portion 78. The cylindrical portion 74 of each

vane

70 or 72 is pivotally but captively received within a cylindrical slot 80 in the inner circumferential face of the orbiting member 30 while the opposite cylindrical end portion 76 is pivotally and slidably received within a corresponding elongated slot 82 formed in the outer circumferential surface of the inner member 28. Any number of three or more of the fluid displacement chambers 68 may be used, depending upon the size and intended application of the device 20, the illustrated embodiment utilizing five of such chambers 68. It will be understood that, when fluid under pressure is introduced into a particular chamber 68 as hereinafter more fully described and as occurs during utilization of the device as a motor, the

vanes

70 and 72 defining the lateral extent of such chamber will be urged apart to effect a sealing contact between the

vane portions

74 and 76 and the corresponding surfaces of

slots

80 and 82. With the chamber 68 thus sealed, as further fluid is introduced therein, the fluid pressure within such chamber 68 will force the adjacent portion of the orbiting member away from the opposing surface of stationary inner element 28. While one chamber 68 is being supplied with fluid under pressure, the chamber or chambers 68 on the opposite side of the orbiting member 30 will be having fluid exhausted therefrom, and such relationship is caused to progress circularly from each chamber 68 to an adjacent chamber 68 by the valving and control means hereinafter described. Accordingly, the fluid being continuously introduced into certain chambers 68 while being exhausted from other chambers 68 and the rotary progression of such relationships during the operating cycle exert forces upon the member 30 tending to make the latter move in an orbital path with respect to the axis of shaft 34 and the outer and

inner elements

26 and 28 respectively.

As will be noted from FIG. 3, the

vanes

70 and 72 bounding the sides of each displacement chamber 68 are adapted to pivot within the slots 80 and to pivot and slide within the slots 82 as required to accommodate the orbital movement of the member 30. As will be further significantly noted, however, the

slots

80 and 82 are so juxtaposed that each pair of

vanes

70 and 72 will be and always remain substantially parallel to each other regardless of the direction or degree in which both are pivoted to accommodate the orbital movement of the member 30. Since the other lateral faces of each member 68 are closed by the parallel surfaces 84 and 86 of block 24 and plate 32, the parallelism of each vane 70 with its associated vane 72 assures that the chordal transverse cross-sectional area of the chamber 68 therebetween will remain substantially constant. This is in sharp contrast with the conventional practice of disposing all of the chamber defining vanes in this class of device essentially radially of the central axis of the device, which results in a nonlinear rate of change in the volume of the enclosed chamber with respect to the stroke or instantaneous positioning of the orbiting member at different times during the operating cycle. It has been found that maintaining the chordal transverse cross-sectional area of the chambers 68 constant throughout the operating cycle substantially increases efficiency by maintaining fluid flow rates to and from the chambers 68 precisely in phase with the sinusoidal variance in valve opening areas conveniently provided by using the orbiting motion of the member 30 to open and close valve apertures, in the manner now to be described.

Referring now also to FIG. 4, the device 20 is provided with a pair of

fluid ports

88 and 90 which may be an inlet port and an outlet port respectively.

Ports

88 and 90 are adapted to be coupled with the pressure and return sides of an external source of hydraulic system oil or other suitable fluid pressure, when the device 20 is being used as a motor. In passing, it should be noted that the device 20 is reversible and that the directions of orbiting of the member 30 and rotation of the element 26 may be reversed merely by reversing the flow of fluid to and from the

ports

88 and 90. The port 88 communicates with an irregular passage 92 within the manifold 22, which in turn communicates with a plurality of openings 93 each terminating in an elongated slot-like opening 94 in the face of block 24 adjacent the member 30, there being such an opening 94 for each of the chambers 68. Similarly, the port 90 communicates with an irregular passage 96 fonned in the manifold 22, which in turn communicates with a plurality of openings 97, each terminating in an elongated slot-like opening 98 in the face of block 24 adjacent the member 30, it bein'g noted that there is an opening 98 for each opening 94 and that they are arranged in parallel pairs corresponding to each of the chambers 68.

Referring now back to FIGS. 2 and 3, in conjunction with FIG. 4, it will be seen that adjacent each chamber 68 the opposing faces of the orbiting member 30 are relieved or cutaway as at 100 and 102 to provide a fluid flow passage 100-102 communicating with the corresponding chamber 68 and to provide hydraulic balancing of member 30 between block 24 and plate 32. The pair of passage portions 100 for each chamber 68 communicate with each other through a relatively large circular opening 104 through the orbiting member 30, which is also adapted to provide clearance for the bolts 36 and spacers 38 without engagement between the spacers 38 and the orbiting member 30. Thus, it will be seen that fluid may flow freely to or from each chamber 68 through the opposed neck passages 102 and the generally rectangular passages 100 that are intercommunicated by the corresponding opening 104. Since the fluid forces acting between member 30 and block 24 and between member 30 and plate 32 are balanced, member 30 axially floats between block 24 and plate 32, although it is otherwise positively mounted for guidance in an orbital path as hereinafter described.

The

openings

94 and 98 are indicated by dotted lines in FIG. 3 and will be seen, with reference to the topmost chamber 68 of FIG. 3, to be spaced apart just sufficiently that the relieved passages 100 may be positioned therebetween and in communication with n'ei-' ther when the orbiting member 30 is in a position at which the fluid connection to such chamber 68 is just being changed from a pressure to an exhaustion phase of the fluid cycling of such chamber 68. Referring to the chamber 68 located at approximately 2-oclock in FIG. 3, however, it will be seen that the fluid inlet opening 94 is fully aligned and communicating with the corresponding relieved passages 100, while the associated exhaust opening 98 is completely out of communication with the passage 100. The relieved passages 100 associated with the other chambers 68 are in differing progressive relationships with their associated inlet opening 94 and exhaust opening 98, so that as the member 30 moves orbitally with respect to the axis of shaft 34 the chambers 68 will each be successively subjected to first an input of fluid under pressure of flow rate increasing to maximum then waning to minimum, then reversing direction for exhausting fluid at a rate also increasing to maximum then waning to minimum before the commencement of the next input or pressure phase. The

opeings

94 and 98 are so disposed within the block 24, with respect to the location of the passages 100 in the member 30, that the mentioned progressive cycling of each chamber 68 through its fluid input and fluid exhaust phase will be controlled automatically by the orbiting of the member 30 with the areas of valve opening communication between the

openings

94 and 98 and the passages 100, as well as the rates of flow of fluid therethrough, varying sinusoidally. It will also be noted that while the chambers 68 on one side of the member 30 are being subjected to pressure, those on the other side will be in their exhaust phase enhance and maintain the orbital movement of the member 30.

With the structure thus far described, those skilled in the artwill appreciate that, without the provision of further means for guiding and confining the member 30 to an orbital path, the

teeth

62 and 64 would have to be formed to close tolerances to properly guide the member 30 and would also have to be of particularly sturdy construction in order to bear the substantial forces that would be imposed thereon, and that, even with such a construction, the friction and wear upon the

teeth

62 and 64 would inevitably be substantial as is common in conventional devices; actually, since the bolts 36 and spacers 38 do not and are not intended to engage the inner surfaces of clearance openings 104, it will also be clear that the member 30 would tend to rotate as well as orbit with respect to the inner element 28 to an extent further complicating the problem of perhaps even rendering the apparatus inoperable. The objects of the invention are, therefore, attained in the device by the provision of a plurality of three or more eccentric crank or shaft assemblies generally designated 106 (see particularly FIGS. 2, 3 and 7). Each eccentric assembly 106 may include a central cylindrical portion 108 journaled by needle bearings 110 within the orbiting member 30, and a pair of oppositely extending

cylindrical portions

112 and 114 of smaller diameter than the portion 108 and having a central axis offset from the central axis of the portion 108. The

eccentric end portions

112 and 114 are respectively journaled in the valving block 24 and the end plate 32 by needle bearings 116 and 118. in the preferred illustrative device 20, tive of the assemblies 106 are utilized for convenience in spacing the same between the valving means associated with each of the five chambers 68 employed in such device. It should be noted, however, that any number greater than two of such assemblies 106 may be employed, although it is preferable to use a number of assemblies 106 that may be equally spaced around the member 30 without interference with the valving means associated with the particular number of equally spaced chambers 68 that are to be employed. The offset between the axis of the portions 1 l2 and 114 with respect to the axis of the portion 108 is so chosen as to permit exactly the range of orbital movement of the member 30 needed to bring the teeth 64 into proper walking mesh with the teeth 62 as the member 30 is orbited.

The assemblies 106 are found to add very little friction to the device and considerably less than that encountered where meshing gears must be relied upon to provide orbital guidance for the member 30. The assemblies 106 are operably sufficient, independently of any other structures or relationships in the device 20, the positively but freely and shiftably mount the member 30 upon the stationary portions of the device 20 including the inner element 28 and to guide and confine the movement of the member 30 to a perfect orbital path with respect to the axis of the shaft 34. In so doing, it will be apparent that the assemblies 106 increase efficiency, decrease wear and lower manufacturing costs by decreasing the material strengths and tolerances necessary in constructing various parts including particularly the

epicyclic gear teeth

62 and 64.

The other construction details of the device 20 are substantially conventional and may vary to considerable extent as those skilled in the art will appreciate. For the sake of completeness, however, it is noted that the embodiment of device 20 chosen for illustration is provided with a cavity 39 (see FIG. 6) for collecting fluid that may normally be expected to leak around the vanes and through the running clearances between the parts, which fluid may be drained through a passage 120 in the valving block for removal through a communicating drain port 122 provided in the manifold. It will also be noted that redundant fluid displacement chambers are formed as at 124 between the functional fluid displacement chambers 68, and provision for venting such redundant chambers 124 is made by passages 126 extending therefrom through the end plate into communication with the collection cavity 39, which avoids trapping or cavitation of fluid in the redundant chambers 124.

Although it is believed that the operation of the device 20 will be largely self-evident to those skilled in the art from the preceding description of the construction and relationship of the parts, it may be briefly summarized that, in operating the device as a fluid motor, fluid under prcssureis supplied to the inlet port 88 for flow through the passage 92 and the

openings

93 and 94 in the valving block 24 into whichever of the relieved passages in the member 30 are then in communication therewith, and thence through the corresponding neck passage 102 into the corresponding fluid displacement chamber 68, the pressure within such chamber 68 exerting a force to move the member 30 radially outwardly from such chamber. Simultaneously fluid is being exhausted from the chambers 68 remote from those receiving a pressure input, with such fluid exhausting through the corresponding neck passages 102 and relieved passages 100 through corresponding openings 98 and 97 in the valving block 24, thence into the passage 96 within the manifold 22 and to the external fluid return line coupled with exhaust port 90. As the chambers 68 are progressively filled and exhausted una. r the control of the valving communication alignment of the passages 100 with the

openings

94 and 98 that occurs automatically upon orbital movement of the member 30, the latter is urged to orbit continually while being supported and confined to an orbital path by the eccentric assemblies 106. As the member 30 orbits, the teeth 64 upon the outer circumference of the member 30 walk around the teeth 62 on the inner circumferentia] surface of the hub 26 causing the latter to rotate with respect to the orbital member 30, the inner member 28 and the shaft 34. Rotational power is then derived from the device 20, operating as a motor, by suitable mechanical coupling with the rotating hub element 26. As previously noted, the device lends itself well to applications requiring a reversible motor, in that, all that is required for reversing the direction of rotation of the hub 26 is to reverse the flow of fluid with respect to the

fluid ports

88 and 90.

If it is desired to utilize the device 20 as a pump, the operation is essentially the same, except that mechanical rotative power is applied to the hub element 26 to turn the latter, which causes the member 30 to orbit under constraint of the eccentric assemblies 106, by virtue of the walking relationship between the

epicyclic gear teeth

62 and 64. As the member 30 is thus moved inan orbital path, the individual chambers 68 are progressively placed in a fluid suction or fluid exhausting condition such that fluid may be pumped from an external line through the inlet port 88, thence through the fluid paths already traced but in the opposite direction, for delivery to an output line coupled with the port 90, the pumping action of the device 20 again being reversible, if desired, merely by reversing the direction of rotation in which the hub 26 is driven. Although the de' vice 20 illustrated in FIGS. l-8 and described in connection therewith is the currently preferred embodiment of the invention, it should be appreciated that the improvements incorporated by the invention into the illustrated device 20 would be equally applicable and effective with devices employing various modifications of construction or operation as, for example, utilization of the device 20 in a manner in which the hub element 26 is held stationary and motor power derived from or pumping power applied to the shaft 34 having

parts

22, 24, 28 and 32 keyed thereto for rotation therewith, or a modified construction of the device 20 in which the chambers 68 are provided between the hub element 26 and the orbital member 30 with the epicyclic gear coupling being between the inner circumference of the member 30 and the outer circumference of element 28 and/or especially modifications of the device 20 employing differing numbers of chambers 68 and/or eccentric assemblies 106 than illustrated in the preferred embodiment, (it being noted also that the number of chambers 68 and the number of eccentric assemblies 106 need not be equal, although the illustrated construction is found to be convenient).

Turning attention now to the remaining embodiments illustrated in the drawings, it should first be observed that such additional embodiments are shown and described for two reasons. Firstly, such additional embodiments indicate the wide applicability of the improvements contemplated by the invention, and particularly the employment of eccentric crank or shaft mechanisms for mounting the orbiting member upon one .of the other machine elements with respect to which it is to be supported and guided in an orbitalpath of travel, in conneetionwiththe great variety of basic constructions that are common to devices in this field. Actually, such additional embodiments are intended to illustrate the fact that the invention is applicable to devices in which either of the inner and outer relatively rotatable machine elements may be the stator while the other serves as a rotor, to devices in which the intermediate orbiting member is mechanically coupled by epicyclic gearing to either the inner or outer machine elements and to either the stator or the rotor machine element, to devices in which the orbiting intermediate machine member is supported for orbital movement upon either the inner or outer machine elements and upon either the stator or the rotor machine elements, andto devices in which the intermediate orbiting member is coupled by fluid displacement means to either the inner or the outer machine elements or to both. Secondly, the remaining embodiments are intended to illustrate constructions in which the principles of the invention may be applied to present what essentially constitute new types of devices in the sense that combining the principles, structures and relationships of the invention into the overall combinations of elements produces devices of a new order of improved efficiency, economy and reliability. However, since the principlesandconstructions of the remaining embodiments are essentially similar to those of the preferred embodiment of FIGS. l-8 with respect to the constructions involved in introducing the positive eccentric mounting means for confining the intermediate member to an orbital path and with respect to such features as the automatic control of valving, the provision of suitable fluid passages within the device structure, etc., andsince the implementation of such principles and features should be now largely self evident to those skilled in the art from the preceding description of the preferred embodiment, the remaining embodiments have been shown and will be described only in such detail as would appear necessary to indicate to those skilled in the art the differences between such additional embodiments and the preferred embodiment already described in detail.

Thus, referring next to the embodiment of FIGS. 9-1l, the device is generally designated 220 and will be recognized as involving the application of the invention to what is essentially a radial ball piston type energy translation device. The device 220 is also chosen, in contrast with the preferred embodiment of FIGS. 1-8, to illustrate employment of the invention in an energy translation machine in which the outer machine element comprises the stator, while the inner machine element serves as the rotor, an in which the intermediate orbiting member is supported and mounted upon the rotatable inner element.

In the device 220, an outer, stationary, cylindrical housing is presented by a pair of

cylindrical frame members

222 and 224, spacer rings 226 and 228 and an outer ring gear element 230 all secured together as by bolt means 232. A rotatable shaft 234 is supported within the

frame members

222 and 224 by

roller bearings

236 and 238, along with a thrust washer 240 and a snap ring axial retainer 242. An inner machine element, rotatable with the shaft 234 is presented by and includes a pair of

cylindrical side plates

244 and 246 respectively keyed to the shaft 234 as at 248 and 250. The intermediate orbiting member 252 is generally annular and is disposed in the space between the shaft 234 and the outer, stationary gear element 230. The intermediate orbiting member 252 is mounted upon the inner rotatable machine element and confined to an orbital path of travel with respect to the-latter by a plurality of eccentric crank or shaft assemblies 254 each having a central portion 256 journaled in the member by roller bearings 258 and a pair of offset cylindrical end portions 260 and 262 of greater diameter and eccentricly journaled respectively in

plates

244 and 246 by roller bearings 264 and 266. Although, again, the employment of five eccentric assemblies 254 is shown for convenience ofillustration, the number of eccentric assemblies 254 to be employed may be any number larger than two. Also, and as is equally applicable to the eccentric assembly 106 illustrated in connection with the embodiment of FIGS. 1-8, the eccentric assemblies 254 may assume various configurations with respect to constructional detail as long as the necessary crank action and positive mounting relationship required to achieve the purposes of the invention are maintained; thus, the assembly 254 might employ separate eccentric crank shafts interfacing between the member 252 and the

plates

244 and 246 respectively, or a set of single-ended crank shafts mounting the member 252 upon only one of the

plates

244 and 246 could be used, etc. The orbiting member 252 is provided with a plurality equal to three or more of radially extending cylinder bores 268, each of which is open at its inner end and is closed at its outer end by a circumferential portion of the member 252 preferably constructed as an initial separate annular band 270 which may conveniently be fitted and secured upon the remainder of the member 252 after machining of the bores 268. The outer band portion 270 of member 252 also carries thereon an inner set of outwardly facing gear teeth 272 adapted to mesh with an outer, interfacing set of gear teeth 274 on the inner surface of the outer element 230, and which together present an epicyclic gear transmission coupling between the outer element 230 and the orbiting member 252. Thus, the band 270 serves both as a cylinder head for the cylinder bores 268 and as the inner portion of the epicyclic gear transmission 272-274.

A free floating ball piston 267 is provided within each I of the cylinder bores 268 and adapted to roll axially of the latter as the member 252 orbits in a manner hereinafter described. A ball race 278 having an annular groove 280 therein is secured to the shaft 234 for rotation therewith, which provides a support for the balls 276. A fluid displacement chamber 282 is thus presented within each cylinder bore 268 between the cylin der head band 270 and the ball piston 276.

Fluid flow ports

284 and 286 are provided in the

end plates

222 and 224 respectively. Port 284 is communicated with an annular ring passage 288 formed in the plate 222, which in turn communicates with a set of slots 290 formed through the plate 226. Similarly port are made to the

fluid ports

284 and 286. Each chamber 282 is provided with a pair of opposed valving openings 296 and 298 extending from the cylinder bore 268 in opposite directions through the orbiting member 252 and disposed for valving communication with the

fluid apertures

290 and 294 as the member 252 is orbited. The orientation of both the

apertures

290 and 294 are indicated in dotted lines in FIG. 10, merely to show positional relationships to the valving openings 296 or 298, as the case may be, during orbiting of the member 252, it being understood that the automatic valving action is substantially the same as described in detail in connection with the embodiment of FIGS. 1-8. From this, it will be understood that the chambers 282 are progressively subjected to fluid pressure and exhaust cycling in successive progression, so that the forces in the various individual chambers 282 will cause the member 282 to orbit upon the eccentric assemblies 254 with respect to the inner machine element 244-246 and the axis of shaft 234 upon which the element 244-246 is mounted and keyed. As the member 252 thus orbits, the teeth 272 will walk around" the teeth 274 of outer machine element 230, which is stationary, so that the member 252 will rotate as well as orbit with respect to the outer machine element 230 and, in turn, will impart rotational movement and energy to the inner machine element 244-246 and the shaft 234, when the device 220 is being employed as a motor, as is for the moment assumed. The direction of rotation of the orbiting member 252, the inner machine element 244-246 and the shaft 234 may be reversed merelyby reversing the pressure and exhaust couplings to

ports

284 and 286. Those skilled in the art will further appreciate that device 220 may also be employed as a pump by applying rotative power to the shaft 234, which will rotate the inner element 244-246 and the member 252, whereupon the member 252 will be orbited as well as rotated by virtue of the eccentric assemblies 254 as the teeth 272 walk around the teeth 274. Since the ball pistons 276 are effectively sealing the inner extremities of the bores 268, and since the volumes of chambers 282 are progressively changing as the member 252 orbits, and since the

apertures

290 and 294 are automatically being progressively and alternately aligned with the valving openings 296 and 298, the device 220 will efficiently perform a fluid pumping operation drawing fluid into the port 284 and discharging the same from port 286, or vice versa depending upon the direction in which the shaft 234 is driven.

The embodiment of FIG. 12 is similar in all essential respects to the embodiment of FIGS. 9-11, and particularly so with respect to the eccentric mounting of the intermediate orbital member, the automatic valving arrangement, the provision of fluid passages and other miscellaneous details of construction, except that the embodiment of FIG. 12 will illustrate for those skilled in the art the application of the invention to a device 320 in which the radial ball pistons 276 of the embodiment of FIGS. 9-11 are replaced by hollow cylindrical virtual pistons 376, and the inner ball race 278 is replaced by a polygonal support block 378. Thus, it will be understood that in the device 320, the rotatable shaft 334 carries thereon the polygonal block 378, which is provided with a flat surface 302 for each of the hollow cylindrical pistons 376. The pistons 376 are slidably mounted. within cylindrical cylinder bores 368 formed in the orbiting member 352. The orbiting member 352 is again mounted for rotational movement with and orbital movement with respect to an inner machine element 344 by eccentric assembly 354 similar to those previously described. Each piston 376 is normally urged toward the corresponding surface 302 of the block 378 by a spring 304. It will be understood that an epicyclic gear coupling is provided in the manner previously described between the outer circumference of the orbiting member 352'and an outer machine element 330.

In operation, the device 320 functions in all respects similarly to the operation described for the embodi ment of FIGS. 9-11, except that, as the member 352 orbits relative to the inner machine element 344 and the block 378, which are both secured to the shaft 334, the hollow pistons 376 merely provide a seal between the cylinder bores 368 and the surfaces 302 of block 378, so that the chambers 382 presented by the bores 368 and hollow pistons 376 progressively change in volume due to the virtual piston effect as the member 352 is orbited. Those skilled in the art will understand that various modifications could be made in the device 320, such as providing cylinder chambers 368 and pistons 376 of other than cylindrical cross section and that the devie 320 may be operated in either direction or in either a motor or a pumping application, without departing from the principles of the invention, the vital improvement of the device 320 as compared with prior art concepts stemming from the provision of the eccentric assemblies 354 for positively mounting and confining the orbital member 352 to orbital motion with respect to the machine element 344, along with the precise valving thus permitted and the advantages thereby attained in accordance with the objects of the invention.

The embodiment of device 430 illustrated in FIGS. 13-15 is intended to illustrate the application of the invention to an energy transmission device of the type generally known to those skilled in the art as a gerotor. The device 430 employes as its outer machine element, which for illustration may be assumed to be the stationary element thereof, a pair of side plates for 432 and 434 separated by an annular spacer 436, together with a manifold plate 438 facing the end plate 434, and all suitably secured together by bolts 4.40. A rotatable main shaft 442 is carried by

bearings

444 and 446 in the

end plates

432 and 434 respectively. The inner machine element, which is rotatable with the shaft 442 and keyed thereto as at 448 is provided with an inner gerotor gear element 450 having external teeth 453 thereon.

An orbiting stator member 452 is mounted upon and confined to orbital movement with respect to the

end plates

432 and 434 by a plurality of eccentric crank or shaft assemblies 454, each of which includes a central cylindrical portion 456 journaled in the member 452 by bearings 458 and a pair of cylindrical end portions 460 and 462 respectively journaled in

end plates

432 and 434 by bearings 464 and 466.

As best seen in FIG, 14, the orbital member 452 is provided with alternate teeth portions 468 and concavities 470 configured to slidingly mate with the teeth 453 of the inner gerotor element 450. As those skilled in the art will recognize there are one more outer teeth 468 and concavities 470 than there are inner teeth 453, presenting the conventional gerotor relationship in which the teeth 453 walk around the teeth 468 and concavities 470 to provide not only an epicyclic transmission arrangement but also a relationship presenting a successive series of fluid displacement chambers 472 between the element 450 and the member 452 at each successive stage of the walking movement between the

teeth

453 and 468. It will also be understood that the relationship between the teeth 453 and the teeth 468 and concavities 470 also is capable of imparting orbital movement to the member 452 when the latter is freely floating, but only with considerable wear upon the teeth 453 and..468 and stringent constructional strength requirements when the member 452 is guided in its orbital movement only by the relationships mentioned.

In the device 430 contemplated by this invention however, the provision of the eccentric assemblies 454 positively and orbitally mounting the member 452 on the outer element 432-434 greatly relieves the forces and strains upon the

teeth

453 and 468 and permits the latter to be constructed and employed with only those strengths and tolerances required for the epicyclic gear relationship and the progressive displacement chamber creating function characterizing the gerotor design.

The manifold plate 438 is provided with fluid pressure and

exhaust ports

474 and 476 which communicate respectively with

annular ring passages

478 and 480 formed in the end plate 434. The passage 480 communciates with a plurality of radial passages 482 in the end plate 434, each of which then communicates with an axial passage 484 through the plate 434 terminated in a fluid aperture 486 in the face of end plate 434 adjacent the member 452. The annular passage 478 is similarly communicated through the plate 434 with a plurality of fluid apertures 488 in the face of the plate 434 adjacent the member 452, there being a pair of

fluid apertures

486 and 488 provided for each of the concavities 470 in the member 452.

A valving groove 490 is relieved or cut away in the member 472 for each of the concavities 470 to provide fluid communication with the displacement chambers 472 successively presented within the concavities 470 as the member 452 is orbited. As will be clear from FIG. 14, the valving grooves 490 automatically and progressively alternate being in communication with the

fluid apertures

486 and 488 as the member 452 is orbited, thereby. providing for sinusoidal variance between maximum pressure and maximum exhaust aperture phases of the valving cycle for each of the displacement chambers 472 successively and in synchronization with the orbiting of the member 452.

In the operation of the devie 430 as a motor, the progressive, phased .valving of fluid pressure and exhaust to the displacement chambers 472 causes the teeth 453 of inner rotary element 450 to walk around the teeth and

rotational movement

468 and 470 of the member 452, simultaneously imparting rotationalmovement to the inner element 450 and shaft 442 and orbital movement to the member 452. Since such orbital movement of member 452 is essential to the operation of a gerotor device, as well as to the precision control of valving, the eccentric assemblies 454 improve the efficiencies of the basic gerotor design by relieving a substantial amount of the stresses and friction that would otherwise exist between the element 450 and the member 452 in order for the former to guide the latter in an orbital path. It will be understood, of course, that the direction of rotation of the shaft 442 may be reversed by reversing the pressure and exhaust couplings to the

ports

474 and 476; that the device 430 may be employed as a pump by applying rotational power to the shaft 442 rather than fluid pressure differentials to the

ports

474 and 476; and that various other constructional and" operational modifications could be employed without sacrificing the advantages accruing from incorporation of the invention, including the eccentric assemblies 454, into a device of a gerotor type.

The illustrative embodiment shown as device 530 in FIGS. 16-18 is, in many respects, similar and even identical to gerotor device 430 shown and described in connectwion with FIGS. 13l5. Accordingly, portions of the device 530 essentially identical to similar portions of the device 430 will be similarly numbered and will not be again described in detail, except to note such material changes or variances as there may be. The device 530 illustrates the incorporation of the principles of the invention into an energy translation device embodying certain physical features of the gerotor design in combination with the provision of additional vane defined fluid displacement chambers between the outer machine element and the intermediate orbital member.

Parts of the device 530 similar in construction and function to parts described in connection with the device 430 include the

end plates

432 and 434, the spacer 436 (with the exceptions hereinafter noted), the manifold plate 438, the bolt means 440, the shaft 442, the inner gerotor element 450, the intermediate orbiting member 452 (with the exceptions hereinafter noted), the eccentric mounting assemblies 454, the

fluid ports

474 and 476, the

passages

478, 480, 482 and 484, the grooves 490 and the

valving apertures

486 and 488.

The orbiting member 452 of device 530 differs from that described in connection with device 430 in two material respects. First, the member 452 of the present embodiment additionally includes, in association with each groove 490, communicating with a concavity 470, a pair of further grooves 502 and 504 which are spaced on opposite sides of the groove 490 and communicate with the space 506 between the outer circumference of the member 452 and the inner circumference of the ring 436. The disposition of the grooves 502 and 504 associated with each of the grooves 490 is such that when the groove 490 is in valving communication with the fluid aperture 486, the groove 504 will be communicating with the fluid aperture 488, and when the groove 490 is communicating with the fluid aperture 488, the groove 502 will be communicating with the fluid aperture 486. Thus, it will be apparent that for each sector of the device 530 including a concavity 470, the space 506 will be coupled with the fluid exhaust while the concavity 470 is coupled with fluid pressure and vice versa.

The space 506 circumscribing the member 452 is divided into a plurality of fluid displacement chambers 508, their placement being one chamber 508 for each concavity 470 and radially aligned with the latter. The space 506 is thus divided by a plurality of shiftable vanes generally designated 510, which may be essentially similar in construction with the vanes 70 shown in FIG. 8. Each vane 510 has an inner cylindrical portion 512 pivotally received within a corresponding cylindrical slot 514 provided in the outer circumferential surface of member 452, which constitutes the second material difference between the member 452 in

devices

530 and 430. v

At the opposite and outer end of each vane 510 is a cylindrical end portion 516 which is pivotally and slidably received within a corresponding slot 518 provided in the inner circumferential surface of the ring 436 of device 530.

Thus, it will be understood that, in the device 530, the automatic valving provided by the

grooves

490 and 502 and 504 in conjunction with the

fluid apertures

486 and 488, and which is controlled by the orbiting of the member 452 in essentially the manner previously described, is effected to progressively subject not only the fluid displacement chambers 472 within the concavities 470, but also the outer fluid displacement chambers 508 to fluid conditions varying sinusoidally between maximum pressure and full exhaust, with each corresponding pair of

chambers

472 and 508 being out of phase with regard to such fluid cycling. It will be appreciated, therefore, that the simultaneous occurrence of a pressure phase within a given inner chamber 472 while its corresponding outer chamber 508 is in an exhaust phase produces an additive effect from the fluid energy available to even more positively move the member 452 into the orbital path in which it is guided and to which it is confined by the eccentric crank or shaft assemblies 454. Also, the employment of the outer chambers 508 to aid in 'imparting orbital movement to the member 452 still further relieves the stresses and friction between the

teeth

453 and 468 and increases the efficiency of the chambers 472 for performing their gerotor fluid displacement function. As the member 452 is orbited by the fluid energy forces, in the application of the device 530 as a motor, the walking action between the

teeth

453 and 468 provides an epicyclic gear coupling between the rotor element 450 and the orbiting member 452 and imparts rotational movement to the rotor element 450 and the shaft 442 as previously described in connection with the device 430. As with the device 430, the device 530 may operate in either direction upon a reversal in fluid connections and may alternately be used in a pumping application by applying, rather than deriving, rotative mechanical energy to the shaft 442.

From the illustrative embodiments of energy translation devices embodying the principles of the inventions that have been hereinbefore shown and described, it should be apparent, first, that the invention is well suited to accomplishing the objects and advantages mentioned above, secondly, that the invention is advantageously applicable in a wide variety of fluid motors, pumps, and the like, and, thirdly, that various minor modifications and changes could be made from the embodiments chosen for illustrative purposes with out departing from the true spirit or substance of the invention. Accordingly, it should be understood that the invention is intended to be limited only by the fair scope of the claims that follow.

I claim:

1. In a device of the class including fluid motors, pumps and certain activators, meters, couplers and the like, in which energy is translated from fluid to mechanical or from mechanical to fluid manifestations thereof, the combination of:

a pair of elements,

said elements being relatively movable with respect to each other;

means for supporting said elements for relative rotational movement therebetween;

said member being relatively movable with respect-to each of said elements respectively;

first fluid displacement means for effecting a fluid' coupling between said member and one of said'elements at a plurality greater than two of zones ,between said member and said one element, the ef fective volumes of said zones being individually variable and at any time dependent upon the relative position of said member and said one element;

said first fluid displacement means including means for effecting fluid ingress and egress connections with said zones in a predermined order for the selective introduction or removal of fluid;

means for effecting both fluid and mechanical couplings between said member and the other of said elements,

said coupling means including interengaging epicyclic gear means having cooperating tooth means on said member and said other element respectively, said tooth means on said member having a different number of teeth than said tooth means on said other element to provide a mechanical gear ratio different from unity between said member and said other element,

said gear means forming a part of structure presenting second fluid displacement means including a plurality greater than two of fluid displacement chambers between said member and said other element, the effective volumes of said chambers being individually variable and at any given time dependent upon the relative positions of said member and said other element,

said second fluid displacement means additionally including means for selectively effecting fluid ingress and egress connections with said chambers in a predetermined order for the selective introduction or removal of fluid; and

further means, separate from and operably sufficient independently of both of said fluid displacement means and said gear means, for supporting said member and for limiting said predetermined movements to relative orbital movement between said member and said one element and to relative orbital and rotational movements between said member and said other element,

said further means providing said support for the member and said limitation of relative movement between the member and the respective elements without reliance upon mechanical forces transmitted through said tooth means and comprising a plurality greater than two of spaced eccentric crank means intercoupling said member and said one element.

2. The invention of claim 1, wherein the rotational axes of said crank means are parallel to and spaced away from the axis of relative rotation of said elements.

3. The invention of claim 1, wherein said one element is a non-rotating stator, and said other element is a rotating rotor.

4. The invention of claim 1, wherein said elements are concentric about their axis of relative rotation, and said member is generally annular and disposed between said elements.

5. The invention of claim 1, wherein said one element is part of an housing structure, said other element is an inner gerotor gear provided with external tooth means,

and said member is an outer gerator gear provided with internal tooth means engageable with said external tooth means of said other element.

ing said second fluid displacement means with pressurized fluid, and means for synchronizing the activation of said first and second fluid displacement means for cooperative application of their respective and opposing forces to shift said member in an orbital path relative to said elements and thereby relatively rotate said elements.

7. In a device as set forth in claim 1, wherein there are an equal number of said zones and said chambers.

8. In a device as set forth in claim 7, wherein the volumes of the individual zones vary oppositely to the volumes of corresponding individual chambers.

9. In a device as set forth in claim 8, wherein is provided means responsive to relative orbital movement between said member and said elements for controlling the flow of fluid to and from individual zones and chambers.

10. A combined radial chamber and gerotor, double and opposed displacement type, low speed, high torque, internal transmission, fluid motor comprising: an inner machine element having a central axis and a radially outwardly facing surface;

and outer machine element having a generally annular, radially inwardly facing surface of substantially greater diameter than said outwardly facing surface of said inner element;

means for supporting said elements for relative rotation about said axis with said inwardly facing surface of said outer element concentric to said axis of said inner element and in spaced apart, circumscribing relationship to said outwardly facing surface of said inner element to present a generally annular space between said elements;

an intermediate ring member having radially inner and outer surfaces and shiftably disposed in said space between said surfaces of said inner and outer elements; epicyclic gear means, including a number of teeth on said outwardly facing surface of said inner element and a greater number of cooperating teeth on the inner surface of said intermediate member, operably coupling said member with said inner element;

said gear means forming a part of structure presenting first fluid displacement means operably coupling said member with said outwardly facing surface of said inner element at a plurality greater than two of zones spaced about the inner surface of said member;

second fluid displacement means operably coupling said member with said inwardly facing surface of said outer element at a plurality greater than two of zones spaced about the outer surface of said member;

means for activating said first and second fluid displacement means in opposed synchronization to shift said member relative to said elements; and

a plurality of eccentric crank means intercoupling said member with said outer element to prevent relative rotation therebetween and to limit shifting said teeth on the ouwardly facing surface of the inner element and the inner surface of the intermediate member are of the gerotor type 13. The invention of claim 12, wherein said second fluid displacement means are of the vane-separated, ra-

dial chamber type.

Claims

1. In a device of the class including fluid motors, pumps and certain activators, meters, couplers and the like, in which energy is translated from fluid to mechanical or from mechanical to fluid manifestations thereof, the combination of: a pair of elements, said elements being relatively movable with respect to each other; means for supporting said elements for relative rotational movement therebetween; a member, said member being relatively movable with respect to each of said elements respectively; first fluid displacement means for effecting a fluid coupling between said member and one of said elements at a plurality greater than two of zones between said member and said one element, the effective volumes of said zones being individually variable and at any time dependent upon the relative position of said member and said one element; said first fluid displacement means including means for effecting fluid ingress and egress connections with said zones in a predermined order for the selective introduction or removal of fluid; means for effecting both fluid and mechanical couplings between said member and the other of said elements, said coupling means including interengaging epicyclic gear means having cooperating tooth means on said member and said other element respectively, said tooth means on said member having a different number of teeth than said tooth means on said other element to provide a mechanical gear ratio different from unity between said member and said other element, said gear means forming a part of structure presenting second fluid displacement means including a plurality greater than two of fluid displacement chambers between said member and said other element, the effective volumes of said chambers being individually variable and at any given time dependent upon the relative positions of said member and said other element, said second fluid displacement means additionally including means for selectively effecting fluid ingress and egress connections with said chambers in a predetermined order for the selective introduction or removal of fluid; and further means, separate from and operably sufficient independently of both of said fluid displacement means and said gear means, for supporting said member and for limiting said predetermined movements to relative orbital movement between said member and said one element and to relative orbital and rotational movements between said member and said other element, said further means providing said support for the member and said limitation of relative movement between the member and the respective elements without reliance upon mechanical forces transmitted through said tooth means and comprising a plurality greater than two of spaced eccentric crank means intercoupling said member and said one element.

5. The invention of claim 1, wherein said one element is part of an housing structure, said other element is an inner gerotor gear provided with external tooth means, and said member is an outer gerator gear provided with internal tooth means engageable with said external tooth means of said other element.

6. The invention of claim 1, wherein said zones and said chambers are disposed on radially opposite faces of said member and there is provided means for successively activating said first fluid displacement means with pressurized fluid, means for successively activating said second fluid displacement means with pressurized fluid, and means for synchronizing the activation of said first and second fluid displacement means for cooperative application of their respective and opposing forces to shift said member in an orbital path relative to said elements and thereby relatively rotate said elements.

10. A combined radial chamber and gerotor, double and opposed displacement type, low speed, high torque, internal transmission, fluid motor comprising: an inner machine element having a central axis and a radially outwardly facing surface; and outer machine element having a generally annular, radially inwardly facing surface of substantially greater diameter than said outwardly facing surface of said inner element; means for supporting said elements for relative rotation about said axis with said inwardly facing surface of said outer element concentric to said axis of said inner element and in spaced apart, circumscribing relationship to said outwardly facing surface of said inner element to present a generally annular space between said elements; an intermediate ring member having radially inner and outer surfaces and shiftably disposed in said space between said surfaces of said inner and outer elements; epicyclic gear means, including a number of teeth on said outwardly facing surface of said inner element and a greater number of cooperating teeth on the inner surface of said intermediate member, operably coupling said member with said inner element; said gear means forming a part of structure presenting first fluid displacement means operably coupling said member with said outwardly facing surface of said inner element at a plurality greater than two of zones spaced about the inner surface of said member; second fluid displacement means operably coupling said member with said inwardly facing surface of said outer element at a plurality greater than two of zones spaced about the outer surface of said member; means for activating said first and second fluid displacement means in opposed synchronization to shift said member relative to said elements; and a plurality of eccentric crank means intercoupling said member with said outer element to prevent relative rotation therebetween and to limit shifting movement of said member relative to said outer element to orbital motion.

11. The invention of claim 10, wherein said outer element is part of an outer housing strUcture, and said inner element is a rotatable rotor carried by a shaft journalled in said housing structure.

12. The invention of claim 10, wherein said first fluid displacement means, said epicyclic gear means, and said teeth on the ouwardly facing surface of the inner element and the inner surface of the intermediate member are of the gerotor type.

13. The invention of claim 12, wherein said second fluid displacement means are of the vane-separated, radial chamber type.