Field of the Invention

The invention relates generally to fluid driving and driven apparatus for conversion of flow of fluids under pressure to mechanical rotation and flow of fluids under pressure to drive other fluids and remotely to apparatus for metering other fluids and more specifically to a fluid apparatus which provides a pair of gerotor units in radially adjacent position.

Short Summary of the Invention

A radially oriented, double gerotor fluid device having capabilities to operate as a fluid driven motor or a motor- pump combination with selective output characteristics and further to operate as a metering device dependent upon various component selectivity. The unit includes a drivable or mounting shaft having a first gear rotor and first valving plate thereon, a second rotor ring having both internal and external lobes and a third, stationary ring gear and also including an external, stationary valve plate ♦ and a valve plate- movable with the rotor ring for rotation or a combination of rotation and orbital movement with a rotor ring. All of these units are contained within a pressure housing and communication and flow control means are provided for proper direction of flow, dependent upon the selected operation for initial fluid direction to the valve plates and receipt of exhausted and driven fluid. The first and third gear and ring are similarly provided with lobes to provide, in combination with the rotor ring, a series of contracting and expanding chambers to drive and be driven by the fluid.

The unit also is provided with counterbalance to offset the orbital movement of the rotor ring and thereby provide a smoothly operating unit.

The coordination of the valving plates, particularly the orbiting or selectively rotating plate in combination

with the stationary plates provides for smooth fluid flow and the design of the unit, being radial in arrangement rather than the ordinary axial or longitudinal arrangement for jointed gerotors is unique.

Background and Objects of the Invention

The applicant, inventor is well aware of, what is known in the industry, as gerotors art. In all of his exposure and searches, the art has failed to reveal and radially arranged double gerotor units. It is acknowledged that gerotors have been arranged in axial or longitudinal align¬ ment but no items of this nature have been found incorporat¬ ing the applicant's concepts. Pertinent, although substan¬ tially different in operation and concepts, are devices described and claimed in United States Patents, No. Re. 26,383 to Huber and 3,574,489 to Pierrat and in publications by the .H. Nichols Co. in Design News, 8-18-80 and a non-published bulletin both of which relate to internally generated rotor sets (IGRs). The devices illustrated and discussed in such articles and patents are clearly distinct from the subject matter disclosed herein.

It is therefore an object of the applicants' invention to provide a double gerotor device which is relatively simple in its construction and which provides for dual gerotor operation with alignment of the rotors being radial.

It is a further object of the applicants' invention to provide a double gerotor device which provides for efficient, straight through valving which includes the benefits of larger valving ports, larger sealing lands and which prevents cross porting.

It is still a further object of the applicants' inven¬ tion to provide a double gerotor device which, through its design permits utilization thereof as a motor, motor-pump or metering unit.

It is still a further object of the applicants' inven¬ tion to provide a double gerotor device which will hold

loads without hydraulic pressure and will give precise positioning as well as precise stop-start characteristics.

It is still a further object of the applicants' inven¬ tion to provide a double gerotor device which, due to its inherent design, eliminates "dogbone" linkages between the orbiting rotor and the rotating motor shaft.

These and other objects and advantages of the appli¬ cants' device will more clearly appear from a consideration of the accompanying description made in conjunction with the accompanying drawings.

Brief Description of the Drawings

Figure 1 is a simple perspective drawing of a double gerotor device embodying the concepts of the applicants' invention;

Figure 2 is a transverse cross section taken substan¬ tially along Line 2-2 of Figure 1;

Figure 3 is a radially transverse section taken sub¬ stantially along Line 3-3 of Figure 2;

Figure 4 is a cross section taken substantially along Line 4-4 of Figure 3;

Figure 5 is a cross section taken substantially along Line 5-5 of Figure 4;

Figure 6 is a cross section taken substantially along Line 6-6 of Figure 4;

Figure 7 is a cross section taken substantially along Line 7-7 of Figure 4;

Figure 7a illustrates a portion of Figure 7 illustrating a modification of the interacting lobes of the various gearing sections of the unit;. _. .

Figures 8 through 15 are overlay cross sections taken substantially along Line 5-5 of Figure 3 to illustrate the various elements of the unit and similarly taken from the end of the unit directly opposite Line 5, the overlays being Intake positions in Figures 8, 10, 12 and 14 and exchaust positions in Figures 9, 11, 13 and 15 and illustrating the members in advancing 90° positions; and,

Figure 16 is a cross section similar to Figure 4 but showing the same in a modified form for use of a motor-pump combination.

Description of the Device

In accordance with the accompanying drawings, the rotary motion fluid apparatus or device embodying the concepts of the applicants' invention is generally designated 20 and is, in the primary form illustrated in Figures 1 through 15, described as a fluid driven motor. It should be understood that the applicant has provided a rotary motion fluid device and inherent therein are certain characteristics which allow for modifications of the unit to allow the same to function as a motor-pump combination and further, alter¬ natively, as a metering device. In each instance, although the basic unit remains the same, minimal structural and fluid control changes allow such variation without departing from the scope of the invention.

An important consideration that must be kept in mind is that the term fluids includes other than liquids.

Another important aspect of the description of the invention is that -minimal concern has been directed to the effective sealing procedures and structures utilized and required for true operation of such units. The applicant is well aware of the requirements of sealing the various portions of the unit for proper power delivery and fluid transfer but in various instances within this application, to simplify the description while maintaining clarity, sealing techniques and structures are not totally described except where to eliminate such. description would prevent one skilled in the art from utilizing the teachings herein.

As illustrated, the unit 20 is designed and constructed for a double gerotor unit. A double gerotor is defined as a pair of gerotor members arranged in radially adjacent position as compared to singular units which may be arranged in tandem or axially aligned fashion.

The unit 20 consists of and includes a housing having a generally cylindrical shaped outer casing 21a, a pair of end members 21b, 21c to close the end of the casing 21a with sealing members 21d, 21e arranged therebetween with attach¬ ment members such as the threaded fasteners 21f securing such ends 21b, 21c to the casing 21a. Fluid under pressure is introduced to the closed housing through inlet 21g and is exhausted therefrom from outlet 21h. As further illustrated, mounting bosses 21i, 21j are provided centrally of end plates 21b, 21c for the rotational mounting of a shaft 22 therein. Bearings 23a, 23b and seals 23c, 23d are similarly provided within the bosses 21i, 21j for rotation of the shaft 22 for, if the unit is being operated as a double, fluid driven motor, powered output of the shaft 22.

As particularly illustrated in Figure 2 and further in Figure 7, a typical driving or driven, central portion of shaft 22 would include a first abutting and locating shoulder 22a, a gear ring mounting section 22b, a threaded longitudi¬ nal portion 22c for sliding movement of a locator ring 24 and a tightening nut 24a acting against the ring 24 for positioning of the various components of the unit along shaft 22. ^" A bearing surface member 24b may also be provided in spaced relation to the adjustment nut 24a, as shown.

As illustrated in Figure 7, the gear ring mounting section 22b . is multisided in configuration for proper mounting of the ring gear 25 thereon. Obviously such a shape in combination with the passage through gear 25 provides for positive mounting of the gear 25 to the shaft 22. The first or primary gear ring 25 includes a relatively thin, radially lobed member arranged to rotate with and to be driven by or drive the shaft 22. The gear 25 provides a plurality of arcuately spaced lobes 25a separated by inwardly directed lobe lands 25b to evolve a continuous, rounded gear tooth surface which, in combination with the radially adjacent rotor ring 27 will provide a series of expanding and contracting cylinders which act upon or are acted upon by the operative fluid. A modified version of the lobe

construction is illustrated in Figure 7a in which the radially outwardly extending lobes are provided of cylindri- cally shaped rollers 25f which are captured for rotation on the extending most portion of each of the teeth 25. Such roller construction and the means for mounting the same are not unique to the art. It should be noted that the appli¬ cants have selected a series of seven lobes 25a and lands 25b to provide a seven toothed ring or primary gear 25 but this selection is purely illustrative.

Immediately adjacent the ring or primary gear 25 are a pair of valve plates 26a, 26b. These plates 26a, 26b are generally circular in shape and are provided with an inner passage 26c therethrough for engagement for the multisided shaft portion 22b. These valving plates then rotate with the ring gear 25. The valve plates 26a, 26b are each provided with a plurality of valving apertures 26d there¬ through and the location of such apertures is selected with and provided with the design of the ring or gear 25 to partially underlie one of the extending lobes but to provide fluid communication to a next adjacent cavity. It should be noted that the particular shape of each valving passage is defined by- -inner and outer arcs and by angular lines and in practice this may vary although minimally. Obviously from the stated and shown geometry, seven such passages are provided in the plates.

Arranged immediately radially outwardly from the ring rotor or gear 25 is an annular, double lobed member 27 which has an inner diameter providing rounded gear teeth with the inner peripheral teeth designated 28a and the outer or land portions designated 28b. Obviously, these teeth are provided to intermesh with the teeth of the gear rotor to provide a plurality of expanding and contracting chambers and to provide such chambers, as in other gerotor structures, the number of such teeth on the double lobed ring member 27 is one greater than the number of teeth on the ring rotor or gear 25. The diameter and number of relative lobes per each

ember is well known to the gerotor art and is inherent and specific to the intent of the device.

As illustrated, the ring rotor 27 is also provided with external teeth consisting of the extending lobe portions 29a and internal land portions 29b to again form rounded tooth portions completely around the periphery of the ring rotor 27. The number of the teeth is again, preselected for application and pressure utilized.

A stationary ring gear 30 surrounds the rotor ring member 27 and such ring gear 30 is provided with internally extending teeth consisting of the inwardly extending tooth portions 30a and the radially outward land portions 30b. Again, the teeth on the stationary ring 30 is one greater than the teeth on the rotor ring member 27.

As previously described for the rotor ring member, the applicant has considered utilization of roller members on at least the stationary ring member 30 and this concept is illustrated in Figure 7a. As shown therein, a plurality of roller members 30d are held by capturing portions 30c of the extending teeth elements 30a to thus provide an actual rolling surface between the various elements. These roller members may selectively be provided on the ring rotor 27 or at the designer's option, all members.

It should be obvious that the rotor ring 27 is of such a size and with the selected variations of teeth between itself and the. ring gear 25 and the stationary ring member 30, that it is free to both rotate and orbit within the spacing between the ring gear 25 and the stationary ring 30. As is well known, a single gerotor unit consisting of a rotating and orbiting ring gear or star gear and a stationary ring requires a "dog-bone" connection of the ring gear to the shaft of the unit. Applicant, using the rotor ring 27 as the orbiting member eliminates such a connection as this member may be termed "free-floating" as controlled by the various fluid pressures.

A first valving ring pair 26a, 26b mounted for rotation with shaft 22 and ring gear 25 has been described. A second

valving ring pair, fixed to the housing 20 and fixed relative to the stationary ring gear 30 is provided and is designated ^" respectively 32a, 32b. Each of these valves 32a, 32b consists of a flat plate member and each is provided with valving passages 32c equal to the number of lobes in station¬ ary ring 30 directly therethrough and each passage 32c is provided with a ramped or canted area 32d communicating therewith to insure flow to the resultant area between the rotor ring 27 and the stationary ring member 30. The particular ramping portion appears best in Figure 4.

A third valving plate is provided for each side of the gerotor assembly and such pair of plates is designated 35a, 35b. Each plate is provided with an oversized central aperture 35c which is of a size to permit both rotation and orbital movement of the same in conjunction with the rotor ring 27. The plates 35a, 35b are pinned or otherwise connected to ring 27 as by the aperture 35f and pin 35g combinations. The pins 35g are positioned with respect to the first valve plates 26a, 26b and stationary valve plates 32a, 32b that they are in the radial gap provided there¬ between. Also provided on the plates 35a, 35b are two sets of radially- and arcuately spaced valving apertures 35d, 35e. These valving passages each include one more passage than that provided on the first valve plate 26a, 26b at such radial location and one less passage 35e than that provided on the valve plates 32a, 32b at such radial location. These rotational and orbital valving plates 35a, 35b then may be considered to be master valving plates which move in con¬ junction with the rotating and orbiting rotor ring 27 and, as such, control the flow to ^" the individual chambers formed by the intermeshing teeth as further controlled by the stationary ring valve 32a, 32b and the rotating ring valve 26a, 26b.

Also illustrated in the various figures is a counter¬ balance member 38. This member consists of a carrier cage 39 and a plurality of roller balls 40 and, as best illus¬ trated in Figure 3, is crescent shaped. The concept of this

member is to offset the unbalancing forces caused by the orbital motion of the rotor ring 27 and the attached valving ^" plates 35a, 35b. This bearing or counterbalance member 38 likewise moves with this combination and will provide an opposite and equally directed force to the orbital motion of the ring 27 and plate combination. Although this member is shown as a roller-cage combination, it should be obvious that it is simply a moveable counterbalance and may take other forms.

To this point, all of the elements to provide a radially arranged, double gerotor device, to operate as a fluid-driven rotational-output motor are provided. A typical flow pattern through the unit is illustrated in Figure 4 and in viewing Figure 4 it must be taken into consideration that the section shown is not a purely diametric section but is taken along Line 4-4 of Figure 3 which permits alignment of passages and teeth of the unit. Flow through the unit is shown- as two parallel paths one of which is directed to the radially outward set of chambers formed by the stationary teethed ring 30 and the outer teethed periphery of the orbital and rotational rotor ring 27 while ^" the other path is to the radially inward set of chambers formed by the inner periphery of the rotor ring 27 and the teeth of the ring gear 25 of shaft 22. Obviously this motor is reversible simply by reversal of flow therethrough and the sequential operation of the valving is controlled by the valve plate combinations to fill a chamber with fluid thus forcing it circularly which simultaneously causes orbiting motion of the rotor ring and it is this combined motion between the two sets of chambers which provides for proper rotational power to the output shaft. This parallel arrangement has many beneficial considerations which include the number of power pulses per revolution which lowers torque ripple output and such a unit will hold a load without requiring continued hydraulic pressure. This latter attribute also includes a self-braking factor as well as a precise stop- start factor.

The particular locations of the various valving ports and therefore the control of flow from and to the contracting and expanding chambers is illustrated in the sequential views of Figures 8 through 15. Figures 8, 10, 12, and 14 illustrate the unit as though it were being from the right hand side of Figure 4 at the view Line designated 8, 10, 12 & 14 and Figures 9, 11, 13 & 15 are as though the unit was being viewed from the view Line of 9, 11, 13 & 15 of Figure 4. This set of views also illustrates shaft 22, ring gear 25, rotor ring 27 and stationary ring gear 30 and, through dotted lines, the inner and outer diameters of the first valve plates 26a, 26b and the outer stationary valve plates 32a, 32b. Further shown on the various views in dotted lines are the valving passages 26d of the first valve plate and passages and ramped surfaces 32c, 32d of the stationary plate and in solid lines, the valving apertures 35d, 35e of the rotating, orbiting valving plates 35a, 35b.

The views are arranged with ring positions of 0°, 90° 180° and 270° with rotation being clockwise to produce a clockwise output shaft rotation. With the specific selection of seven tooth construction for the gear or ring gear 25, obviously σne more- for the inner teeth of the rotor ring 27, and 17 for the outer teeth -of the rotor ring 27 and thus 18 for the inner teeth of the stationary ring 30, there will be a total of 17 shaft rotations and 119 orbital shifts for the rotor ring 27 before the valving arrangement returns to the position of that shown in Figure 8 or Figure 9. As these views show the particular elements and their relative posi¬ tions through one shaft rotation, 0 and 360 shaft positions being identical at least for...the ring gear and carried plate, it is not thought that it is necessary to detail the opening and closing of the various flow passages in response to rotation and orbital movement.

The utilization of the applicant's various concepts such as the radial tandem positioning, the plate valving which not only reduces total size but provides for straight through valving, dissimilar valving surfaces for the intake

and exhaust valves accompanied with larger sealing lands to prevent leakage and cross porting all provide for high volumetric efficiency. The simplicity of three valve plates to control inlet and outlet respectively and simple three piece duplex gerotor construction all must be considered in comparing the uniqueness of the applicant's design. The simplicity also results in a wide selection for independent displacements of the gerotor elemen s, particularly of the inner and outer rings and simple length modifications. All of these factors are of considerable merit when comparing the applicant's unit to the prior art.

Applicant's unit has utilization and may function as a combination motor-pump wherein fluid power is utilized and converted to rotary power for the pumping of a second liquid. This particular use is illustrated in Figure 16. In this form of the invention, fluid under pressure is being delivered to the outer set of chambers and the inner set of chambers is being utilized for pumping another fluid. In such a choice, there would be a low mass flow and high pressure rise on the inner chamber set while, if the unit were operated in a reverse or fluid supplied to the inner set of chambers condition with the outer doing the pumping, the resultant would be a high mass flow and low pressure rise on the pumped fluid of the outer chamber set.

In this, form, a housing 51, end plates 52, 53 with inlets and outlets 54, 55, 56 and 57 is provided and a shaft 58 is mounted for rotation within the housing 51 and shaft 58 would serve no other purpose than as a mounting for rotation of the gerotor assembly and alignment thereof.

Inlet 54 may be termed ati inner member inlet as it provides inlet flow to the inner set of lobes or teeth as exist between ring gear 60 and rotor ring 62 with the outlet 57, termed an inner member outlet for the exhaust of fluid from such area. Inlet 55 may similarly be termed an outer member inlet as it provides inlet flow to the outer set of lobes or teeth as exist between rotor ring 62 and stationary

ring 63 with the outlet 56 termed an outer member outlet for the exhaust of fluid from such area.

The basic gerotor assembly would again include the ring gear 60 having a pair of valving plates 61a, 61b carried therewith, a rotor ring 62 capable of and placed and sized for rotational and orbital movement and the stationary assembly consisting of stationary ring 63 and stationary valve plates 64a, 64b. The only required variation to operate the applicant's unit as a motor-pump is the elimina¬ tion of the orbiting movement of the plate valves 62a, 65b carried by the rotor ring 62. Each of the valving plates 65a, 65b are provided with valving apertures, the inner designated 65c and outer 65d, as illustrated and positioned on Figure 5. Obviously as this set of plates does not orbit with the rotor ring 62, it may serve as a commutator for flow distribution from and to the two inlets and two outlets while preventing flow therebetween.

It it is necessary to eliminate the orbital motion of the rotor ring 62 from the plates 65a, 65b, this may be simply achieved. As illustrated, a connective pin 66 is provided to connect the plates 65a, 65b and rotor ring 62 is ^' this pin is received into openings of the plates 65a, 65b which openings are of a diameter twice the eccentricity of the rotor ring in its orbital path or, to eliminate wear, a pair of bearings 67a, 67b having offset pin receiving passages may be provided to receive the pins and complete the connections between units. The offset would be twice the orbiting eccentricity and thus the only driving effect resultant to the two valve plates 65a, 65b would be circular. For this reason, it is possible to make the plates circular in shape to eliminate the counterbalance of Figure 4.

As stated, shaft 58 serves only a centering and rotation function in this form and therefore a complete shaft struc¬ ture is not required. It should also be obvious that shafts, as stated, may be of any form to allow attachment of other units, mounting and other functions or services.

One simple and obvious use is available from the applicant's basic concept is its modification thereof to form a motor-pump combination. With the form shown in Figure 16, a metering function may be performed wherein the supplied fluid is the controlling factor in the addition of other fluids to the final output. For example, a fluid supplied, which requires an additive is utilized as the power source to the set of chambers which will act as the motor and is admitted to the proper inlet 54 or 55. Fluid is then made available to the set of chambers that will act as the pump through the other 54 or 55 inlet. The output is then joined in the correct mixture through connection of outlets 56, 57. It should be obvious that such metering may be selective by varying chamber sizes of the gerotor arrange¬ ment and all resultant flow will be properly metered as additive flow is controlled by supplied flow of fluid.

It should be obvious that the applicant has provided a new and unique, what may be termed a double, duplex or similar terminology, gerotor device which incorporates all of the aspects of normal gerotors but which provides an improved and fluidically and economically feasible structure.