US2553859A - Variable oscillating gear - Google Patents

Description

May 22, 1951 J. D. KREIS VARIABLE OSCILLATING GEAR IIII' 4 Sheets-Sheet 1 5 m m V mm 7. A

Filed Oct. 9, 1946 May 22, .1951 J. 0. KREIS 2,553,359

' VARIABLE oscmmmcmx Filed Oct. 9, 1946 v 4 Sheets-Sheet 2 INVEN TOR. JOSEPH 0. [(3518 ATTOBNE Y8 y 1951 J. D. KREIS 2,553,859

VARIABLEDSCILLATING GEAR Filed Oct. 9, 1945 4 Sheets-Sheet s 5 i I INVENTOR.

JOSEPH D. KEE/S f/?TM TTOBNEYS May 22, 1951 J. D. KREIS VARIABLE oscmnmc GEAR '4 Sheets-Sheet 4 Filed Oqt. 9, 1946 INVENTOR. JOSE PH D. KeE/S ATTOBA/[YS Patented May 22, 1951 UNITED STATES PATENT 7 OFFICE VARIABLE' OSGILLAT IN G GEAR Joseph D. Kreis, Gleveland, Ohio Application Oc'tbber'l), 1946, Serial No. 702,154

17 Claims.

This invention relates to variable oscillating gear mechanisms, that: is, devices for converting continuous rotary motion into'oscillating rotary motion, having a provisioncfor varying the amplitude of the oscillating motion. In its preferred embodiment, as described herein, the invention is applied to a drive for the agitator of a washing machine, but, as will be seen, the mechanism may be employed in various environments.

An object of the invention is to provide a mechanism for converting continuous rotary motion into oscillating rotary motion.

Another object of the invention is to provide such a mechanism in which the amplitude of the oscillating movement may be varied while the mechanism is'in ope-ration.

Another object of the invention is to provide means for rotational coupling between two bodies having offset axes of rotation.

Another object of the invention is to provide a mechanism for converting continuous rotary motion into oscillating-rotary motion which will be compact, reliable and durable, and will be economical of manufacture.

Another object isto provide a mechanism which is adapted for enclosure in a driven rotat able housing which may be sealed and contain a bath of lubricant.

A further object of the invention is to provide an improved driving mechanism for a washing machine agitator.

Other objects and advantages more or less ancillary to the foregoing and the manner in which all the vvarious objects are realized will appear in the following description, which, considered in connection with the accompanying drawings, sets forth the preferred embodiment of the invention.

Referring to the drawings:

Fig. l is an elevational view, partly in section, illustrating the application of the invention to a washing machine;

Fig. 2 is a sectional view of a fragmentary por tion taken on a plane indicated on a line 2-'2' of Fig. 1;

Fig, 3 is a plan view o f'a portion of the'mechahis-m showing the eccentric planet gear;

Fig. 4 is a view of the concentric planet gear as seen from below;

Fig. 5 is a vertical section through the planet gears taken on a plane indicated by the lines 5--'5 in Fig. 3; and

Fig. 6 is a vertical section through the planet gears taken on a plane indicated by the line 6 -6 in- Fig. 3.

Referring. to-Fi'g. -1=, the-invention is illustrated as incorporated in a: conventional washing ma chine having a tub H n-iounted on a framei2 and including. a drive pulley I3 associated-l with a motor (not shown) and a: power tahe-offipulleyl t for the operation: of a wringer (not shown-L The gearing which for-ms the subject of thislin-e. vention is'principally enclosediina housing- 45in the iorm of a hollow pulley. The agitator shaft ripheral grooves therein mime retention. of the 52 extendsupward from the housing through a gland in the bottom. of the tub. The housing [5 comprises two flanged sheet metal stampings l6 and I? lFigs. 1. and 6) which are annular inform and struck with. the marginal portions thereof:

directed inwardly tof'orm the sides 3 015 a vebelt pulley. when the two stampings are assembled:

opposed relation to .eachtother. The two-stampe ings it and. [1. are. retained in, clamped; relation by conical-headetlscrews l9-1 seated inopenings 21 in. the stampih'gs and threaded intospacinga,

sleeves 22. A gasket 23-, preferably composed of synthetic rubber, is clamped between the opposed edges of the flanges 3., providing a seal against leakage of. oil from the housing. The lower hub. 260i the housing l5.is.iormedaby a frustoeco'nical malleable casting. havinga peripheral groove 21-.

therein. for the reception of the circumsference of the stamping. The walls of: the caste ing 2e. defining the groove 21 are rolled or pressedinto intimate toil tight engagement with the The,

stamping l? to client the support thereof. upper hub 28 is sealed into the upper stamping It in the same manner. Thehub 28 is provided with a counterbored central opening 29 into which is ressed a flanged bushing 30 which forms a radial and thrust bearing surface rcr rotational supporter the housing l5. The bush m 30 is jourhall'ed on a flanged sleeve 3-!- threaded ontoa depending cylindricalportion 32 or; a spider 33. The pider is formed with a cylindrical flange 3'4 cireur'njacent the hub 21? which defines a pocket between the flange and hub for the retention of packing 36. The-spider 33 is further formed with aplurality of equallyspaced ears '3! having cups 313- in theextreinities- Cap screws;

marginal edges of openings 4! in the frame member I2. The agitator shaft 42 is sealed against leakage by packing 48 retained by a sleeve 49 threaded into a cup 58 formed in the central portion of the bearing member 4|. The bottom of the tub is retained between a flange 5Ia of the casting and a nut 52 threaded onto the sleeve 49. The agitator shaft passes through an opening 53 in the bottom of the cup 59, through the casting 33 and into the housing I5.

The agitator shaft is driven by a sun pinion 56 (Fig. 6) formed integral with a sleeve 5'! splined to the lower end of the shaft (Fig. 1) and retained by a spring collar 58. The lower end of the shaft 42 is journaled in a flanged bushing 59 pressed into a bore in a central cylindrical portion 6! of the hub casting 26/ A thrust washer 62, keyed to the sun pinion, by a tab which is bent for engagement between teeth in the face of the'pinion, is interposed between the pinion and the thrust bearing face of the bushing 59.

Oil may be drained from the housing through a passage 64 in the hub 26 by removing a plug 66 at the bottom of the hub. A plug 61 threaded into the upper stamping I6 of the housing is provided to facilitate replenishment of the oil. The mechanism preferably runs in a bath of oil.

.'The oscillating gear contained in the housing I5 is based upon the principles disclosed in my copending application Serial No. 667,965, filed May 7, 1946, for Oscillating gear. In accordance with the principles therein set forth, the present apparatus includes a fixed sun pinion 93 mounted inthe spider 33 and in coaxial relation with the agitator shaft 42 and the agitator sun pinion 56. Aplanet gear 81 is concentrically mounted with respect to and engages the fixed sun pinion 93, the housing I5 serving as a carrier. A second planet gear 68 engages the agitator sun pinion 56. and is mounted for eccentric rotation with respect to a support boss I3, while the axis of the gear is constrained to move along a path concentric with the agitator pinion 56 by a yoke 81. The planet gears 68 and 81 are rotatively coupled by a rack and pinion arrangement which enforces equal rotation of the two gears While accommodating relative displacements of their axes. Rotation of the carrier is then translated into oscillatory displacement of the agitator shaft 42 by reason of the eccentricity of the axis of the. planet gear 68 with respect to its center of rotational support, 1. e. the boss 13.

The planet gear 68 (Figs. 3, 5, and 6) which meshes with the pinion 56 on the agitator shaft, is supported by a hub 69 which is slidable radially of the gear, the hub being rotatably supported on an arm 'II pivoted in the housing. The arm II is formed with a boss I2 at one end thereof which is bored for pivotal movement around one ofthe sleeves 22 in the housing. The opposite end of the arm is formed with a cylindrical boss I3 which provides a radial support for the hub 69 within which it is mounted. The hub has a lower flange I4 thereon which is borne by the surface of the arm circumjacent the boss I3, and has an upper flange I6 thereon which supports the gear 68.

The central portion 68a (Figs. 3 and 5) of the web of gear 68 is elevated, and is formed with a slot 1'! therein directed radially of the gear. The upper portion of the hub 69 is formed with a diametral wall I8 having a rack I9 machined in the upper surface thereof, the rack being disposed in a plane slightly above the flange I6, and being slidably received in the slot 11. Engagement of the rack I9 within the slot constrains the hub 69 from rotation relative to the gear 68. The rack teeth form a part of the mechanism for shifting the hub 69 radially of the gear 68 to vary the eccentricity of the hub with respect to the axis of the gear and the consequent amplitude of the oscillatory motion. The flange I6 is cut away at one end of the rack bar I8 to permit maximum movement of the hub 69 to the right as will be seen in Fig. 6.

The gear 68 is maintained in mesh with the pinion 56 by a yoke 8I having a collar 82 at its inner end pivoted on a sleeve 83 on the agitator shaft 42, and formed with a bore 84 in its outer end which provides a bearing for the machined concentric surface 86 at the periphery of the elevated central portion 68a of the planet gear 68.

Under the combined action of the arms 'II and 8|, the planet gear 68 is constrained with respect to the housing I5 and the agitator shaft 42 since its center moves in an are about the shaft, whereas its eccentric hub swings in an are about a sleeve 22 of the housing, that is, substantially radiall of the housing.

The planet gear 81 (Figs. 4, 5, and 6) embodies a bored and faced hub 88 journalled on a flanged bearing sleeve 89 fixed in the housing. The sleeve 89 is formed with a conical bore 99 constituting the seat for a conical fiange 9I struck from the marginal edge of an opening in the upper face I6 of the housing. The parts are retained in assembled relation by a plug 92 engaged with the flange 9I and threaded into the sleeve. The planet gear 81 meshes with the fixed pinion 93 (Figs. 1 and 6) which is retained in the portion 32 of the spider 33, preferably by being bonded therein during the die-casting of the member 33.

A stroke-adjusting pinion 94, mounted on the shaft 42, and rotatable independently of the shaft, is formed integral with the sleeve 83 and with a sleeve 96 which extends upwardly into the spider 33 through the fixed pinion 93.

The adjusting pinion 94 remains stationary except when the amplitude of the oscillation is adjusted. The pinion 94 has the same number of teeth as the pinion 93.,

A ring gear 9'1, having the same diameter and number of teeth as the planet gear 81, is mounted on the lower face of the gear 87 in mesh with the adjusting pinion 94.

The bore of the ring gear is rotatably received on a turned outer face 98 of the web of the planet gear, and is retained thereon by buttons 99 threaded into the planet gear, the heads of which overlie the inner edge of the ring gear.

The means for coupling the two planet gears for concurrent rotation must accommodate lateral displacement of the two gears resulting from the eccentricity of the axes of the planet gears. The coupling comprises two parallel racks IIlI and I02 formed on the upper face of the gear 68, and two parallel racks I93 and I94 on the lower face of the gear 81 within the ring gear 97. The racks NH and I62 are parallel to, and equally spaced from, the sliding rack I9 on the hub 69. When the gearing is assembled the racks [Ill and I93 and the racks I92 and I04 are parallel and disposed in face-to-face relation. The intermediate coupling member comprises a floating shaft I96 having wide-faced pinions I07 and I08 splined on each end of the shaft. The pinion I9! meshes with the racks IIlI and I93, and the pinion I98 meshes with the racks I02 and I04.

'I66 and engaged with the faces of the planet gears are provided to maintain the pinions in ass-asse proper'ilneai relation and prevent the-teeth from bottoming in the racks;

Relative motion between the two planet gears may be considered with respect to a component parallel to the racks and a component in quadrature to the racks. The parallel component is accommodated by rotation of the pinions: and shaft, the quadrature component by sliding move ment of the pinions and shaft along; the shaft axis. In this connection, the rollers I'99, by engagement with the sides of the racks, prevent the intermediate member from sliding out of engage ment'- with the racks. pl-anet-ge'ars is possible, since the pinions I9 'I'and1 IIlIi are mounted for simultaneous rotation: with the shaft I96.

The-means for varying the eccentricity of the: hub 69 with respect to the axes of the gear 68- includes, as has been stated, therach 19 on the hub I6. The rack is shifted by a pinion II-I- rotatably mounted on the shaft I66 between the rollers I99. This pinion also meshes with a rack H2 cut in a bar H3 slidably mounted in a diainet'ral path in the lower face of the gear 81..

The'ends' of the bar I I3 are formed for abutment against the spiral cam surfaces H4 and H5 formed inthe inner edge of the ring gear 81. Thus, by rotating the ring gear with respect to the planet gear, the rack H2 is shifted radially oft he g'ear, rotating thepinion III and shifting the rack I9 and hub 69* radially of the lower planet gear.

Normally, the gears 81 and 91 do not rotate relative-to each othenand the amplitude of cscil.- lation of the shaft 42 remains constant. To ad- 'just the amplitudethe pinion 94 isturned, which incidentally may be accomplished duringthe operation of the machine. The'pinion 94 is integral with the sleeve 96, the upper end thereof being machined to form a worm wheel II 6 thereon (Figs. 1 and 2) disposed withinthe spider 33. A worm I I1, cut into a shaft H8, meshes with and rotates the worm wheel H6. The shaft H8 is enclosed in a cylindrical housingv H9 formed. integral with the spider 33. A pin I2 I: in the hous ing, engaged in a groove [22in the-shaft, retains the shaft against axial displacement.

The outer end of the shaft H8 is coupled, by a shaft'I23 (Fig. 1) and universal. joints I24 and I25, to the spindle I26 of an adjusting knob. I21. The spindle I26 is journalled in aboss I28 formed in the flange of the frame member I2, and is retained by a star washer I29 secured by a nut I3'I. A detent I32 having the inner end thereof seatedupon the boss I28, and its intermediate portion bent to project through an opening I 33 in the frame is engaged with the star washer I29. The detent is held within the opening I33 by a compression spring I34 engaged between the hubof the detent and the knob I21. of the knob is machined with a groove therein which is disposed in telescopic engagement withv acylindrical portion I36 of the frame. By pressing the knob inward, the star washer I29=may be released from the detent, and the shaft.;l23 rotated. The joints I24 and I are designedifor suflicient telescopic movement to facilitate such action.

Alternately, by exerting an outward force against the protruding end I 31 of the detent, the: Such operation.

star washer may be released. may be effected by any well known'form'of linkage which if desired may be associated with a. In this,-

Norelative rotation of-fhe The periphery.

tater shaft will cause the hub 69 to return to the center of the gear 68-, terminating the oscillating For this action to take place, the' gears H6 and H1 must be so designed as toibemovement.

reversible.

If desired, the gears I I6 and H1 may be made. irreversible and the detent mechanism be omitted.v

Preferably, the ratio of gear 8'! to pinion 93 is slightly different from the ratio of gear 68 to pinion 56, with the result that the agitator shaft The amount of creeping. movement may be determined by well-known will creep slightly.

formulas for the action of compound planetary gears, as set out inthe abovementioned copending application.

One or more of sleeves 22- (Fig. 1) opposite the planet gears may be enlarged to balance theweightof the planet gears, or two sets of planet gears in opposite sides of the housing may be provided to secure a balancedmechanism.

' Operation While it is believed the operation of the mechanism disclosed herein. will be clear to those skilled in the art from the foregoing. des cription, a concise consecutive description of the op eration follows.

Assuming that the knob I21 is set for no oscilv lation of the agitator shaft 42, the hub 69 will .be concentric with the gear 68. If now the motor is energized to rotate the housing I5, the planet gears 81 and 68 are revolved around the sunv gears 93 and 56 respectively by the housing I5. The two planet gears are constrained to rotate equal- 1y about their axes (that is, with respect to the- By constructing the gearing so that these two. pairs of gears are of slightly different ratio, as

stated above, the sun gear 56 and the agitator shaft 42 on which it is mounted will be caused to rotate slowly at a constant rate or creep.

The ring gear 91 is in mesh with the pinion 94.

which remains fixed. Since the pinions 93 and 94 areof the same number of teeth and the planet gear 81 and ring gear 9'5 are of the same number of teeth, the gears 81 and 97 rotate together and remain in the same relative position.

In order to cause oscillation of the agitator shaft 42, the hand wheel I2! is rotated, rotating the pinion 94 through the following chain of mechanism: shafts I26, I23, and H6, gears H7 and H6, and sleeve 96, with which the pinion 94' is integral. This rotation of the pinion 94 relative to the fixed pinion 93 causes rotation of the ring gear 91 with respect to the planet gear 81; and, by this rotation, the bar H3 on which the rack I I2 is formed is reciprocated across the face of the gear 81 by the internal cam surfaces H4 and H5 of the ring gear. We may assume that the movement is sufiicient to shift the rack H2 to'the position illustrated in Fig. 6. As the rack is moving inwardly, it is in mesh with the pinion II I which thus rotates about the shaft I06. The pinion I I I meshes with the rack I9 on the hub- 69, shifting the hub away from the center of the planet gear 68 to an eccentric position such asillustratedin Fig. 6. This motion of the hub- 69" with respect to the gear 68 is accommodated byrotation of the arm 'H on which the hub 69 is rotatably mounted about its pivot 22 (Fig. 3),;

and by circumferential movement of the gear 68 with respect to the housing I5. The link I! maintains the hub at a fixed distance from its pivot 22 and the yoke 8i maintains the planet gear 68 at its set distance from the central axis of the shaft 42. Depending upon the actual angular relation of the planet gears with respect to the housing I5, this shifting movement of the hub will cause more or less rotation of the planet gear 68 with respect to the housing and thus of the sun gear 56. This temporary rotation of the sun gear 56 is, of course, communicated to the agitator shaft 42 on which it is mounted. This displacement just mentioned ceases upon the termination of change in the position of the hub 69 with respect to the gear 68; but when the hub has been displaced to an off-set position, a continuous oscillating movement of the agitator shaft 42 is produced.

The underlying reason or principle of this action may be more easily understood by reference to the relatively simple mechanism of my abovementioned copending application than by reference to the more complex mechanism disclosed here; and it is believed that it will be apparent to anyone who understands the said application.

However, in terms of the structure here presented, the action is as follows: Rotation of the housing I5 rolls the planet gear 87 and ring gear 9'! as a unit around the fixed pinions 93 and 94, these planet gears rotating on the hub 89 fixed in the housing. The planet gear 68 is caused to rotate about the eccentric axis defined by the hub 69 at exactly the same rate as the planet gear 81 by the coupling between these two gears comprising the shaft Hi5 and the pinions Ill! and H38 fixed thereon. This coupling accommodates relative displacement of the axes of the gears, however, both by rotation of the pinions I01 and. W8 on the racks lfil, I92, I03, and 104, and by sliding movement of the pinions longitudinally of and with the shaft [66, which is permitted by the fact that the pinions are of greater width than the racks. The planet gear 68, therefore, rotates uniformly with the planet gear 8"! whatever the relative positions of the axes of those gears. However, since the axis of rotation of the planet gear 68 defined by the hub 69 is eccentric with respect to the axis of the gear 68 and since the axis of the gear 68 is constrained tomove in a circle concentric with the agitator shaft 42, the uniform rotation of the planet gear 68 must cause a displacement of the hub 69 about the axis of the gear. By reason of the double constraint between the agitator pinion 56 and the planet gear 68 imposed by their teeth and the yoke 8|, this displacement of the hub 69 is imparted to the agitator pinion as a variable motion, oscillatory in character. The average rate of rotation of the pinion 56 is either zero or a small rate, as previously set out in the description of operation of the gearing with the planet gear 68 centered.

The amplitude and frequency of the oscillatory movements and the rate of the creeping movement may be determined by the application of known principles of mechanism which have been set out for convenience in my above-mentioned copending application and need not be repeated here.

It will be apparent to those skilled in the art that for certain applications where no variation of the amplitude of oscillation is desired, many of the principles of construction disclosedhereinbe understood that the specific terminology is. not intended to be restrictive or confining, and

that various rearrangements of parts and modifications of detail may be resorted to without departing from the scope or spirit of the invention as herein claimed.

I claim:

1. A variable oscillating gear mechanism comprising two sun gears, a planet gear meshing with each sun gear, a carrier on which the planet gears are mounted for revolution about the sun gears, means defining an axis of rotation for one planet gear adjustable radially of the said one gear, and

means coupling the planet gears for concurrent rotation.

2. A variable oscillating gear mechanism comprising two sun gears, one of the sun gears being fixed, a planet gear meshing with each sun gear, a carrier on which the planet gears are mounted for revolution about the sun gears, means defining an axis of rotation for one planet gear adjustable radially of the said one gear, and

means coupling the planet gears for concurrent rotation.

3. A variable oscillating gear mechanism comprising two coaxial shafts, a sun gear fixed on each shaft, a carrier rotatable about the axis of the shafts, a planetgear meshing with each sungear, means constrained to rotation about the shaft axis with the carrier defining an axis of rotation for each planet gear, means coupling the planet gears for equal rotation about their respective axes, and means for adjusting the axis of rotation of one planet gear radially of the said one gear, whereby the said one gear may be given varying amounts of eccentricity with respect to that axis.

4. A variable oscillating gear mechanism comprising two coaxial shafts, one of the shafts being fixed, a sun gear fixed on each shaft, a carrierrotatable about the axis of the shafts, a planet gear meshing with each sun gear, means con-' strained to rotation about the shaft axis with the carrier defining an axis of rotation for each planet gear, means coupling the planet gears for equal rotation about their respective axes, and means for adjusting the axis of rotation of one planet gear radially of the said one gear, whereby the said one gear may be given varying amounts of eccentricity with respect to that axis.

5. A variable oscillating gear mechanism comprising two sun gears, a first planet gear meshing with one of said sun gears, a second planet gear meshing with the remaining sun gear, said second planet gear having an eccentric axis of rotation, a carrier in which the said planet gears are mounted for revolution about the sun gears, means coupling the planet gears for concurrent rotation about their axes, and means for varying the axis of eccentricity of the said second planet gear comprising a member movable radially of the gear,-

a member movable radially of the said first "planet gear, and-means coupling the .twomemwith one of said sun gears, a second planet gear ,1

meshing with the remainingsun gear, said second planet gear havingan eccentric axis of rotation, a carrier in which the said planet gears are mounted for revolution .about the :sun gears,

means coupling the planet gears for concurrent rotation about their axes, and means for varying the axis of eccentricity of the vsaid second planet gear comprising a first member movable radially of the gear, a second member movable radially of the said first planet gear, means coupling the two members, and a part rotatable about the axis of the said first planet gear for moving the second member.

7. A variable oscillating gear mechanism comprising two sun gears,a first planet gear meshing with one of said sun gears, a second planet gear meshing with the remaining sun gear, said :second planet gear having an eccentric axis of rotation, a carrier in which the said planet gears are mounted for revolution about the sun gears,

means coupling the planet gears for concurrent rotation about their axes, and means for varying the axis of eccentricity of the said-second planet gear comprising a first member movable radially of the gear, a second member movable radially of the said first planet gear, means coupling the two members, a gear rotatable about the axis of the said first planet gear for moving the second member, and a pinion rotatable about the axis of the sun gears for rotating the r last named gear with respect to the planet gear.

l8. An oscillating gear I mechanism comprising a fixed shaft, a rotatable shaft coaxial with the fixed shaft, a housing rotatable on the shafts, a sun gear fixed on each shaft within the housing, a first planet gear meshing with one sun gear and rotatable about a shaft fixed in the housing,

a second planet gear meshing with the other sun the shafts, a sun gear fixed on each shaft, a first planet gear meshing with one sun gear and rotatable about a shaft fixed in the carrier, a second planet gear meshing with the other sun gear, a hub for the said second planet gear mounted in the gear for radial movement thereof, said hub being constrained with respect to said carrier, a yoke for the second planet gear rotatable about the axis of said coaxial shafts and defining an axis of rotation for said second planet gear through the axis of that gear, means coupling the planet gears for concurrent rotation comprising a rack on each planet gear, each rack being parallel to and opposing the rack on the other gear, and a pinion meshing with the racks of both planet gears, the pinion being of greater width than the racks; and means for varying the eccentricity of the hub of the second planet gear with respect to the axis of that gear.

10. A variable oscillating gear mechanism comprising two coaxial shafts, a carrier rotatable on 1110 the shafts, a. sun gear fixed on-each shaft, a first planet gear meshing with the fixed sun gear and rotatable about a 'shaft fixed in the carrier, .a second planet gear meshing with the other sun gear, a hub for the said second planet gear mounted in the gear for radial movement thereof, said hub being constrained with respect to said carrier, a yoke for the second planet gear rotatable about the axis of said coaxial shafts and defining an axis of rotation for said second planet gear through the axis of that gear, means coupling the planet gears for concurrent rotation comprising a rack on each planet gear, each rack being parallel to and opposing the rack :on the other gear, and a pinion meshing with-the racks of both planet gears, the pinion being of greater width than the racks; and means for varying the eccentricity of the hub of the second planet gear with respect .to the axis-of that gear comprising a member slidable radially of the first planet gear, a member slidable radially of the second planet gear and means coupling the two members. a I

11. An oscillating gear mechanism comprising two coaxial shafts, a housing rotatable on the shafts, a sun gear fixed on each shaft within the housing, a first planet gear meshing with one sun gear and rotatable about a shaft fixed in the housing, a second planet gear meshing with the other sun gear, a shaft for the said second planet gear mounted for movement radially of the housing and constrained to rotate therewith;

and means coupling the planet gears for concurrent rotation comprising a pair of parallel racks on each planet gear, each rack'being parallel to and in opposition to a rack on the other gear, a floating shaft perpendicular to the racks, and a pinion fixed on each-end of the shaft meshing with a rack of each planet gear, the'p'inion's being of greater width than the racks.

12. An oscillating gear mechanism comprising a fixed shaft, arotatable shaft coaxial with the fixed shaft, a housing rotatable on the shafts, a sun gear fixed oneach shaft within the housing, a first planet gear meshing with the fixed sun gear and rotatable about a shaft fixed in the housing, a second planet gear meshing with the rotatable sun gear, a shaft for the said second planet gear mounted for movement radially of the housing and constrained to rotate therewith; and means coupling the planet gears for concurrent rotation comprising a pair of parallel racks a floating shaft perpendicular to the racks, and

a pinion fixed on each end of the shaft meshing with a rack of each planet gear, the pinions being of greater width than the racks.

13. A variable oscillating gear mechanism comprising two coaxial shafts, a housing rotatable on the shafts, a sun gear fixed on each shaft, a first planet gear meshing with one sun gear and rotatable about a shaft fixed in the housing, a second planet gear meshing with the other sun gear, a hub for the said second planet gear mounted for movement radially of the housing and constrained to rotate therewith, a yoke for the said second planet gear for the rotational constraint thereof with respect to said coaxial shafts, means coupling the planet gears for concurrent rotation, and means for varying the cocentricity of the hub of the second planet gear with respect to the axis of that gear.

14. A variable oscillating gear mechanism comprising a fixed shaft, a rotatable shaft coaxial with the fixed shaft, a housing rotatable on the shafts, a sun gear fixed on each shaft within the housing, a first planet gear meshing with the fixed sun gear and rotatable about a shaft fixed in the housing, a second planet gear meshing with the rotatable sun gear, a yoke rotatably mounted about the said coaxial shafts and rotatably supporting said second planet gear, a hub for the second planet gear mounted in the gear for movement radially thereof and mounted for movement radially of the housing and constrained to rotate therewith, means coupling the planet gears for concurrent rotation, and means for varying the eccentricity of the hub of the second planet gear with respect to the axis of that gear.

15. A variable oscillating gear mechanism comprising a fixed shaft, a rotatable shaft coaxial with the fixed shaft, a housing rotatable on the shafts, a sun gear fixed on each shaft within the housing, a first planet gear meshing with the fixed sun gear and rotatable about a shaft fixed in the housing, a second planet gear meshing with the rotatable sun gear, a yoke rotatably mounted about the said coaxial shafts and rotatably supporting said second planet gear, a hub for the second planet gear mounted in the gear for movement radially thereof and mounted for movement radially of the housing and constrained to rotate therewith; means coupling the planet gears for concurrent rotation comprising a pair of parallel racks on each planet gear, each rack being parallel to and opposing a rack on the other gear, a floating shaft perpendicular to the racks, a pinion fixed on each end of the shaft meshing with a rack of each planet gear, the pinions being of greater width than the racks; means for varying the eccentricity of the hub of the second planet gear comprising a rack slidable radially of the first planet gear intermediate the aforementioned racks, a cam and cam follower for shifting the rack, a gear for operating the cam journalled in the housing, a pinion coaxial with the sun gears meshed with the cam operating gear, an actuator for the pinion, a rack on the hub parallel to and opposing the rack slidable on the first planet gear, and a pinion free on the floating shaft intermediate the pinions fixed thereon and meshing with the slidable rack and hub rack.

16. A variable oscillating gear mechanism comprising a fixed shaft, a rotatable shaft coaxial with the fixed shaft, a housing rotatable on the shafts, the housing being conformed as a pulley, a sun gear fixed on each shaft Within the housing, a planet gear meshing with each sun gear mounted within the housing and revolvable about the sun gears therewith, means providing one of the planet gears with an axis adjustable radially of the gear, and means coupling the planet gears for concurrent rotation.

17. A variable oscillating gear mechanism comprising a fixed shaft, a rotatable shaft coaxial with the fixed shaft, a housing rotatable on the shafts, the housing being conformed as a pulley, a sun gear fixed on each shaft within the housing, a planet gear meshing with each sun gear mounted within the housing and revolvable about the sun gears therewith, means providing one of the planet gear with an axis adjustable radially of the gear, and means coupling the planet gears for concurrent rotation, the housing being adapted to retain an oil bath.

JOSEPH D. KREIS.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,660,356 Postel Feb. 28, 1928 1,804,983 Higgins May 12, 1931 2,004,572 Furness June 11, 1935 2,149,668 Crosthwaite Mar. 7, 1939 2,232,091 Battin Feb. 18, 1941 2.374,718 Andrew May 1, 1945 2,378,967 Andrew June 26, 1945

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