BACKGROUND OF THE INVENTION TECHNICAL FIELD: This invention relates to mechanical apparatus for changing the speed and torque of the output shaft of a prime mover. More specifically, this invention is directed to an apparatus for providing an infinitely variable, ripple free change of speed or torque from a prime mover.

BACKGROUND ART: Historically, significant efforts have been directed to the provision of transmission assemblies adapted for changing the speed and torque of the power output of a prime mover. Many of these assemblies have involved the use of rachet drives, eccentrically oriented cam assemblies, and variable length lever arms.

Representative of the past efforts in this regard are the structures disclosed in the following issued patents: U. S. Pat. 3,803,931; U. S. Pat. 3,517,913; U. S. Pat. 3,229,549; U. S. Pat. 3,229,3,073,173; U. S. Pat. 2,199,052; U. S. Pat. 2,159,739; U. S. Pat.

3,915,129; Italian Pat. 460047 and French Pat. 590, 087.

DISCLOSURE OF THE INVENTION The instant invention includes an input shaft journaled in a restraining support or housing, a cam, and one or more cam followers. The invention further includes structure for changing the spatial interrelationship of the cam and the can followers. In one embodiment the cam followers may be axially fixed while the cam is mounted for slidable displacement relative to the cam followers, e. g. the cam may be slidably splined on the input shaft. In another embodiment, the cam may be axially fixed and cam followers may be adapted for slidable displacement relative to the cam. Various cam follower configurations are contemplated relating, but not limited to a slidable arrangement on one or more independently controllable output shafts or balls splined on the output shaft or one or more cam follower pivot shafts wherein the cam followers are adapted for linear displacement along a length of those shafts. In yet a further embodiment two or more cam followers may be pivotedly mounted to the retaining

housing and held in a spaced relationship with the cam. In other embodiments the cam followers are positioned linearly in tandem along the length of the cam. In yet further embodiments two or more cam followers may be placed or arranged in a circular arrangement about a centrally positioned cam. In another arrangement, linear tandemly mounted sets of cam followers are placed in a generally, spaced circular arrangement about a common centrally positioned cam. The output of the linear tandem assemblies may be integrated to produce a single output from a plurality of intermediate output paths. The cam followers may be separated one from the other on the cam thereby greatly reducing contract stresses between cams and cam followers.

The cam may be designed so that the position of wheels associated with the cam follower (s) always lie on a circle of unchanging diameter irrespective of what the transmission ratio might be. A hoop of given size is utilized in some embodiments to keep the cam followers in constant contact with the cam at all times. In addition, in some embodiments barrel shaped cam follower wheels may be used to further increase cam contact area with cam follower wheels and thus further decrease contact stresses.

The cam and cam follower wheels may be designed such that they are never stressed beyond the endurance limit of the material they are made of.

The instant invention may be adapted to include structures for applying longitudinal force directly on the cam or the cam follower thereby displacing the cam or cam follower along the length of a shaft on which it is mechanically associated. In some embodiments this structure may include a steerable, rotating wheel biased against and rolling on a cylindrical hub extending from the cam. The wheel may be journaled in a fork, which in turn, is journaled in the housing. This structure is adapted such that upon the wheel being steered in a first direction the cam or cam follower moves in the opposite direction. Steering the wheel in a second direction results in the cam or cam follower moving in a direction opposite to the second direction. A feedback system associated with the structure operates to retain the wheel in a straight direction thereby assuring the maintenance of selected ratios.

In the embodiments adapted for use with bicycles, each cam follower may be fitted with a cam contact member which may be a wheel journaled in the follower. The shifting in this embodiment is facilitated in that the input force is diminished at the top

and the bottom of pedal motion. For other applications the wheel in the cam follower is a castor.

Proper operation of the instant invention is generally dependent on adequate friction being maintained at the cam and cam follower engagement or interface.

To this end the invention provides structure to isolate that engagement surface from being contaminated by lubricants. To ensure a lubricant-free contact between cam and cam followers, some embodiments of the invention provide one or more housings disposed to isolate the engagement of the cam followers and the cam from lubricants in the environment of the engagement. These housings may assume many different forms, including housings around bearings and journaled elements, e. g. the bearings utilized in the invention may be sealed bearings. The invention may also include a housing around the engagement interface of the cam and cam followers itself.

Other embodiments of the invention include structure to effect a springless biasing of the cam followers against the cam. In yet other embodiments multiple power paths are utilized to eliminate large contact stresses.

One end of the cam provides lowest, it may be zero, output speed. The other end of the cam provides maximum output speed. These are an indefinite number of output speeds between these extremes. The cam followers may be coupled to the output shaft by one-way clutches. Multiple cam followers and output shaft assemblies, may be arranged in a planetary array around a common variable throw cam with follower outputs integrated into a single output speed. These means provide multiple times as much power as one might get from a single power path transmission of nearly the same size.

BRIEF DESCRIPTION OF DRAWINGS FIG. 1 is a an end view of a linear, tandem configured transmission of the invention; FIG. 2 is a top view of the transmission of FIG. 1 shown in cross sectional view; FIG. 3 is the transmission of FIG. 1 shown with a shift screw mechanism; FIG. 3A is an exploded view of a control apparatus of the invention; FIG. 4 is a first alternative embodiment of the transmission of the invention ; FIG. 5 is a selective side view of a radial array of the invention adapted for use with a bicycle;

FIG. 6 is an end view of the input end of the radial array of FIG. 5; FIG. 7 is an end view of the other end of the radial array of Fig. 5 adapted for use with a bicycle; FIG. 8 is a section through the cam array view of the transmission of FIG. 5; FIG. 9 is an end view of an in-line fixed ratio speed changer; FIG. 10 is a cross sectional view of the in-line fixed speed changer of FIG. 9; FIG. 11 is an input end view of a fixed ratio speed changer adapted for right angle power output; FIG. 12 is a top view of the fixed ratio speed changer of FIG. 11 ; FIG. 13 is perspective view of a linear actuator of the invention; FIG. 14 is a top view of the linear actuator of FIG. 13; FIG. 14A is a perspective view of an alternative embodiment of the linear actuator of FIG. 13; FIG. 15A is an end view of a first embodiment of the linear actuator of the invention; FIG. 15B is an end view of a second embodiment of the linear actuator of the invention; FIG. 15C is an end view of a third embodiment of the linear actuator of the invention; FIG. 16 is an end view of a multiple power path embodiment of the invention; FIG. 17 is a cross sectional top view of the multiple power path embodiment of the invention as illustrated in FIG. 16; FIG. 18 is an end view of an independently controlled multiple power path embodiment of the invention; FIG. 19 is a cross sectional view of the multiple power path embodiment of FIG. 18; FIG. 20 is an example of an alternative follower embodiment; FIG. 21 is a cross sectional view of Forward, Reverse, Park, and Neutral control of the transmission of the invention.

FIG. 22 is a cross sectional view of a two power path embodiment of the transmission of the invention; FIG. 23 is an end view of the transmission of FIG. 22;

FIG. 24 is a cross sectional view of another embodiment of the invention; FIG. 25 is an end view of the transmission of FIG. 24; FIG. 26 is a graphical representation of speed, torque and ratio of a transmission of the invention; and FIG. 27 is a graphical representation of performance characteristics of the instant invention.

BEST MODE (S) FOR CARRYING OUT THE INVENTION FIGS. 1 and 2 illustrate the transmission of the invention configured in a linear arrangement. An elongate, cylindrical power input shaft 31 is journaled in a support on housing 33 for rotation about its longitudinal axis 32. A cam 35 with two or more lobes is slidably mounted or roller splined to the input shaft 31. Cam 35 is fitted with a cylindrical integral hub 37. The integral hub 37 is splined for slidable displacement along the input shaft 31. Two or more pivotedly mounted and axially constrained followers 39 are coupled, by over running clutches 41, to an output shaft 43. The output shaft 43 is journaled in the housing 33. The output shaft 43 is preferably oriented parallel to the input shaft 31. Each cam follower 39 is fitted with a cam contact member 45 which is shown as a rotatable wheel. In those instances where the wheel is mounted on a bearing, the bearing is preferably sealed, i. e. the bearing is surrounded by a housing which contains the lubricant within the bearing and precludes the lubricant from escaping from the bearing housing. The wheel is therefore mounted in a housing or structure which precludes the lubricant within the mounting bearing from migrating from that bearing to the engagement interface of the cam and the cam follower thereby contributing to a lubricant-free contact between cam and cam follower. Cam contact member 45 is a castor wheel the castor wheel may run along or be journaled in a lubricated-for-life sealed castor bearing 47. The cam follower 39 is biased against cam 35 by compression spring 44.

A control structure having a crowned wheel 48, disposed in structure adapted to ensure lubricant-free contact between wheel 48 and cylinder hub 37 is journaled in a steerable fork 49. This structure may be a sealed bearing. The fork 49 is journaled in housing 33 and is biased by a compression spring 50 against cylindrical hub 37. Fork 49

is steered by a tiller 53 to move the rotating cam 35 one way or the other to change ratios or to maintain a selected ratio. As the orientation of the fork 49 is changed by the tiller 53, the orientation of the wheel 48 on hub 37 is also changed. A change in the latter orientation causes a force to be applied to the hub 37 by the wheel 48 which produces an axial displacement of the hub, and hence the cam, along the length of the input shaft 31.

Due to the configuration of the cam, this axial displacement changes the ratios of the transmission.

The cam 35 is contoured to selectively create an infinite number of ripple-free speeds on the cam follower 39 from zero up to a selected top speed and to smoothly rewind while another follower provides selected speed. All of this is associated with structure adapted to ensure lubricant-free contact between cam surface and follower wheels. Notably, the principal housing 33 surrounds the engagement area of the cam and the cam followers and isolates that area from the environment. The housing 33 thereby isolates that engagement area from lubricants which may be in the environment. For those instances wherein lubricants may be found within the body of the principal housing 33, secondary housings, namely sealing structures are provided around lubricant containing elements of the transmission, for example bearings. It follows that the invention utilizes sealed bearings which retain the lubricant within the bearing structure housing and preclude the escape of that lubricant from the bearing housing., Such secondary housings or sealing structure are found positioned about the mounting structure of the cam follower wheels and the wheel 48 and in other locations wherein lubricant containing elements are found within the body of the transmission. As noted above these housings, both principal and secondary are utilized to ensure that lubricants within such bearings do not migrate to the engagement area of the cam (s) and cam followers.

Cam design is adapted to provide totally ripple free rotation of the output shaft in all ratios.

In operation the input shaft 31 rotates the cam 35 causing the spring biased followers 39 to oscillate. First one follower 39 is driven by the cam 35 to provide an unrippled speed to the output shaft 43 and then the other follower 39 is driven by the cam 35 to provide an unrippled speed to the output shaft 43. The magnitude of the output speed depends on cam location relative to the follower 39. The smaller the cam

throw the lower the output speed. The larger the cam throw the higher the output torque.

The location of the cam relative to the cam followers is controlled by the control apparatus. By changing the orientation of the wheel 48 on hub 37, an axially directed force is applied by the wheel 48 to the hub 37 thereby resulting in an axial displacement of the cam along the input shaft. The axial displacement results in a change of the relative positioning of the cam and the cam followers and a resultant change in the ratio of the transmission.

FIG. 3 illustrates the transmission of FIG. 1 and FIG. 2 with cam hub 37, compression spring 50, tiller 53, crowned wheel 48 and fork 49 being replaced by a shift screw 54 threaded into housing 33. The inner end of the shift screw 54 is configured in a ball shape to fit into a socket 55 defined within the outer race of ball bearing 56. The inner race of sealed ball bearing 56 is integral with or fixed to cam 35. Lock nut 57 or the like locks the shift screw 54 into selected ratio settings. FIG. 3A illustrates the control apparatus in more detail with the inner race of the bearing 56 being shown as retained on the screw 54 by a first retaining ring 57A and a second retaining ring 57B being used to retain the outer race of the bearing in the cam 35. Further a bearing pillow is also shown.

In operation, the cam 35 of the embodiment of FIG. 3 is moved by a rotation of the shift screw 54. As the cam is slidably displaced along the length of the input shaft 31. The sealed contact member 45 of the cam follower 39, being mounted as a caster, automatically follows the path to the new ratio selection, just like the tail wheel of an airplane automatically follows the airplane's front wheels. As a result of the biasing of the contact member 45 against the cam 35 through the sealed-in structure to ensure lubricant-free contact between the contact member and cam bearing 47 no sliding of the contact member over the cam 35 occurs.

It is within contemplation that the shift screw 54 could be replaced by a hydraulically actuated structure, an electrically operated device or by a simple lever and still form part of the instant invention.

FIG. 4 illustrates a schematic view of a springless embodiment of the transmission of FIG. 3. In this embodiment a three lobed cam 35A, instead of a two lobed cam 35A, is illustrated. Furthermore, FIG. 4 illustrates the use of three instead of two cam followers 39. This particular embodiment includes an elongate cylindrical input

shaft 31 A journaled in housing 33A, a pivot shaft 60 and differential shafts 64 and 65 are journaled within housing 33A and extend outwardly from differential 66. Cam followers 39A', 39A", and 39A'"are pivotedly mounted on shaft 60. Each cam follower 39A', 39AI'and 39A"I engages a respective identical cam lobes 36A', 36Atl and 36AIll on one end and is mechanically associated with one of two differential shafts 64,65 or carrier 76 on its other end. Cam follower 39A'is associated with differential shaft 64 through linkage 70. Cam follower 39Ail is associated with differential carrier 76 journaled on shaft 64 via linkage 72. Cam follower 39A"l is mechanically interconnected with differential shaft 65 via segment gears 73 and 74. Differential carrier 76 journals jack shaft 75 which is fixed to segment pinion 76 and link 77 is linked to link 79 which is fixed to shaft 64 which is journaled in differential 76. Pinion 76 meshes with gear 81 which is fixed to shaft 75 which is journaled in differentials 76 and housing 35A.

In operation a rotation of input shaft 31A is transmitted through cam 35A, followers 39A, links 70 and 72 and segment gears 73 and 74 to segment gear 81 in mesh with segment pinion 78 which is fixed to jack shaft 75 which is journaled in differential carrier 76. Link 77 is fixed to jack shaft 75 which is journaled or pinned to segment 78 which, on its other end is pin journaled to link 79 which is fixed to shaft 64 which is journaled in carrier 76 and housing 35A. Torques on 39 are equal resulting in constant contact between cam follower wheels 39 and the cam 36.

The alternative embodiment of the infinitely variable transmission of the invention, as shown in FIGS. 5, 6,7, and 8 includes an elongate cylindrical input shaft 31A which is hollow. The input shaft 31A is journaled in a rotatable housing 33A and on stator shaft 80. The shafts 31A and 80 and housing 33A are mounted so that they can be rotatated differently from one another. The input shaft 31 A may be rotated about the transmission's longitudinal axis at a speed and torque different than the speed and torque of housing 33A and/or the stator shaft 80 which is always zero.

The input shaft 31 A includes a slidable spline, or ball spline, connection to the cam, such as ball grooves 86. Cam 35A has matching ball grooves 84. Balls 82 ride in grooves 86 and 84. Cam 35A is thereby held on, and displaceable axially on, input shaft 31 A and is configured to have one lobe which intercooperates with a plurality of cam follower wheels 45A journaled on axles 88 fixed to follower arms 90 which are fixed to

and pivot with planet shafts 92 journaled in housing 33A. The cam 35A is designed to have a first end 94 and an opposite end 96.

Each cam follower 39A', 39AIl, and 39A... includes two arms 90 fixed to planet shafts 92, and an axle 88 extending there between. A wheel or roller 45A with a crowed rim associated with a lubricated-for-life sealed ball bearing, or the like, is mounted on axle 88 structure. The seals ensure lubricant-free contact between the cam surface and the follower wheel surface. Roller 98 is also journaled on axle 88 outside follower arm 90. A hoop 100, which may be comprised of a short torsion spring, rides on rollers 98. The cam 35A is shaped so that the diameter of hoop 100 remains constant while it all the while biases all follower wheels against the cam in all throws and/or during any part of any given throw. In this particular embodiment no springs are required.

Each cam follower 39A', 39A", and 39A... may be fixedly mounted to its planet shaft 92 which in turn is oriented parallel to input shaft 31 A. Each shaft 92 includes one way clutch members 41 A, coupling shafts 92 to planet gears 102 which are in meshing engagement with idler gears 105 journaled on stub shafts107 extending from housing 33A. Idler 105 is also in mesh with sun gear 110 fixed to stator shaft 80.

Bearing 112 with one race fixed to cam 35A and the other race fixed to shift lubricated-for-life sealed rods 81 which are slidable in sun gear 110 to engage shift members not shown outside of housing 33A.

Support 116 is integral with or fixed to stator shaft 80 and extends to tube 118 which journals primary input shaft 31A fixed to pedals 120 and sprocket 122.

Chain 123 couples sprocket 132 to sprocket 124 fixed to input shaft 31A.

In operation pedal power, or start-stop power of any kind, is transmitted by the input shaft 31A to rotate the cam 35A, which drives the followers 39A which take turns, through respective one way clutches 41 A, driving planet gears 102 engaged with the sun gear 110 to walk around the sun gear 110 which, if held stationary, causes the housing 33A to rotate. Speed ratios may be changed by moving the control rods 126 which move the cam 35A to a different location under the axially fixed follower 39A. The transmission is unloaded essentially twice during each rotation of the pedals making it easy to move the cam. As pedal power increases the resulting forces push the follower wheels 45A against the cam 35A. Friction in lubricant-free contact area keeps the

followers 39A from sliding down the cam 35A. No other force is needed to maintain selected ratios.

Alternatively, as shown in FIG. 6, a sprocket 132, may be journaled on shaft 131 fixed to the bicycle fork. Sprocket 132 is fixed to gear 133 which is in mesh with pinion 134 which in turn is fixed to input shaft 31A.

FIGS. 9 and 10 show input shaft 31 B, in a preferred embodiment of a fixed ratio in-line speed reducer of the invention. The shaft 31 B is journaled in housing 33B, and is fixed to identical cams 35B positioned 180 degrees apart which are contoured to produce ripple free out put speed. Cam follower wheels 45B journaled on axles 88B which are fixed to followers 39B which are journaled on pivot shaft 130 which is fixed in housing 33B. Followers 39B are rotatably pinned to links 138 which are, in turn, rotatably pinned to over running clutches 41B journaled on concentric output shaft 43B. The output shaft is journaled on input shaft 31B and in housing 33B. Compression springs 134 bias wheels 45B against cams 35B. The aforesaid elements are structured to ensure lubricant- free contact between cam surface and follower wheels.

A large family of fixed ratio, very low cost, in-line speed changers can be made from these few identical, except for the cams, parts. The speed changer can be made with three cams and be spring free, as in the transmission of FIG. 4.

In operation, rotation of the input shaft 31B rotates cams 35B that oscillate over running clutches 41B to provide ripple free rotation of the output shaft 43B.

FIGS. 11 and 12 illustrate a right angle, fixed ratio speed reducer much like the in-line speed reducers of FIG. 9 and FIG. 10 except that the output shaft 43 C is at right angles to the input shaft 31C and links 148 have ball-shaped ends that fit into sockets 150 on bell cranks 152 and 154 and into sockets 156 on clutch 41C. Cams 35C may be contoured to provide perfect ripple free outputs.

A linear actuator embodiment of the invention is illustrated in FIGS. 13-15. In this embodiment the apparatus includes an elongate cylindrical output shaft 43D journaled in housing 33D for easy rotational and axial movement, wheel forks 90D journaled in housing 33D, a motor mounting plate 170 fixed to one wheel fork 90D and pierced for wheel 45D spring biased against output shaft 43D journaled in housing 33D in structure (e. g. a sealed bearing) to ensure lubricant-free contact between shaft 43D and

wheel (s) 45D. The axle of one wheel 45D is driven by motor 168 fixed to motor mounting plate 170.

A plurality of spring biased wheel forks 90D may be journaled in their respective independent housing lobes 172. A pin 173 extends from each wheel fork 90D through slots 174 in housing 33D into holes in shift plate 176 journaled on the centerline of output shaft 43D and held in place by retaining ring 178. Rotation of output shaft 43D, caused by motor driven wheel 45D, causes all of the other wheels 45D to rotate. A control screw 180 threaded through housing 33D is coupled to motor mounting plate 170.

A tubular housing extension 184 may serve as a clevis. A similar clevis is journaled in and travels with output translator shaft 43D. Switch 182 is fixed to housing 33D and turns the motor on and off or alternatively into reverse. FIG. 14A illustrates an alternative embodiment wherein the orientation of the motor 168 is controlled by a tiller 175 as opposed to a screw 180.

In operation with motor switch 182 on, causing the output translator shaft 43D to rotate, allowing the operator to turn the control dial to move shaft 43D at a selected speed in a selected direction. Movement of the control dial to zero stops the linear motion of the output translator shaft. The faster one moves the dial the faster the output shaft moves. A movement of the dial to the other side of zero reverses the direction of that motion. With a reversible motor one can also reverse the motion by reversing the motor. Limit switches turn the power off at the extremes of motion or where ever the operator chooses between those extremes. Addition of further wheels 45D increases the available output force as shown in FIGS. 15A, 15B, and 15C.

FIGS. 16 and 17 show a transmission of the invention with the cam followers arranged around the cam to create multiple power paths each with its own contact areas on the cam and means of reintegrating the power into a single output shaft 43E.

Input shaft 31E is journaled in housing 33E. One two lobed cam 35E is slideably splined on the input shaft 31E. An apparatus 188 is positioned to move the cam 35E under load. Axially fixed followers 39E are pivotedly coupled through one way clutches 41 E to two or more intermediate output shafts 190 oriented parallel to input shaft 3 E and journaled in housing 33E. This embodiment includes means to integrate the multiple outputs generated from multiple contact positions of cam followers on the cam structure to ensure lubricant-free contact between cam surface and follower wheels surface into

one final output shaft 43E such as via a bevel gear differential where output shaft 43E is journaled on one shaft 190 is integral with idler shaft 196. Idlers 194 are journaled on shaft 196 to mesh with a bevel gear 193 keyed to one shaft 190 and to a bevel gear 192 fixed to a sprocket journaled on output shaft 43E and chain coupled to the other shaft 190. Cam follower casters 45E have a traction radius which may be substantially larger than the rolling radius of the caster wheel.

In operation the multiple power paths multiply the amount of output torque provided to the output shaft 43E without increasing the amount of contact stress between follower wheels 45E and cam 35E and without increasing capacity of the one way clutches 41E. Two power paths multiply available output torque by two. Four power paths multiply the amount of torque available by four, etc. All of this without exceeding the endurance limit of the material used to provide desired output torques.

FIGS. 18 and 19 disclose a transmission of the invention with multiple independently controlled output shafts. It is like the transmission of FIGS. 16 and 17 except that cam 35F is turned by input shaft 3 IF which is journaled in housing 33F and is axially constrained, and the tandemly arranged clutch assembly of the transmission of FIGS. 16 and 17 is slideably or ball splined to output shaft 43F along with means to shift the cam assembly's axial position on shaft 43F. FIGS. 18 and 19 show two independent output shafts but there may be more.

FIGS. 18 and 19 show a transmission of the invention with multiple individually controlled output shafts, driven from a common input cam. FIG. 19 shows the transmission of FIG. 15 and 16 with multiple power paths but without the differentials used to integrated the power from the multiple power paths into a single output shaft.

Input shaft 31F is journaled in and extends from housing 33F. The shaft 31F is fixed to cam 35F. Cam followers 39F, each with a respective castor 45F, is held against cam 35F by springs 44F. Each set of followers is individually biased by compression springs although they may be biased by hoop technology previously described. Cylinders 37F are slidably splined to output shafts 43F. Rotating controls wheels 188 are positioned within steerable forks, which are spring loaded against the cylinders 37F.

Output shafts 43F are journaled in and extending from housing 33F. The output shafts 43F, are slidably coupled to inner races of one-way clutches 4 IF and thus to followers 39F.

One cam 35F drives two or more independently controlled output shafts 43F.

Other control positioning structures disclosed above may be used instead.

FIG. 20 discloses one of several possible cam followers that can be used in this invention. Input shaft 31 G drives cam 35G which drives castor wheel 45G, in structure to ensure lubricant-free contact between cam surface and follower wheel. Castor wheel 45G journaled in follower 39G axially journaled in housing 33G and configured as a rack gear in mesh with gear 197 coupled by one-way clutch 41G to pivot or output shaft 43 G journaled in housing 33G. Spring 44G biases castor wheel 45G against cam 35G.

FIG. 21 discloses means to provide forward, reverse, neutral and park as part of the transmission of the invention. Variable speed output shaft 210 is journaled in housing 33H and journaled concentrically in final output shaft 43H journaled in and extending from said housing. Gear 212 is fixed to shaft 210 and meshes with gear 214 which is fixed to jack shaft 216. This jack shaft 216 is journaled in carrier 218 and is fixed to output shaft 43H. Pinion 217 is also fixed to jack shaft 216 meshes with gear 219 which is fixed to concentric shaft 229. Brake drum 220 is fixed to shaft 229 and engages with brake band 221 which is actuated by the transmission operator. Pinion 224 is fixed to jack shaft 216 and is in mesh with idler gear 225 which is journaled on stub shaft 225 which extends from and is integral with carrier 218. Idler 225 is in mesh with gear 230 which is keyed to shaft 232 which is fixed to brake drum 237. Brake drum 237 is engage able with brake band 238.

In operation brake bands 221 and 238 are free from drums 237 and 220 and the transmission is in neutral. Tightening band 221 holds gear 219 still. Input gear 212, on shaft 31H is in mesh with gear 214 which is fixed to jack shaft 216 and which rotates gear 217 which then rolls around held gear 219 causing carrier 218 to rotate shaft 43G in a reverse direction.

Releasing brake band 221 and tightening brake band 238 and stopping brake drum 237 causes jack shaft 216 to rotate carrier 218 which is fixed to output shaft 43G in a forward direction. When both brake bands 221 and 238 are tightened the transmission is in park.

FIGS. 22 and 23 show a bike transmission with two power paths. It puts out twice the torque per cam/cam follower contact stress as the single power path bike transmission of FIG. 16 and FIG. 17. The two power paths of the transmission of

FIG. 22 are in radial array with springless hoop 100K biasing follower 39K against cam 35K in structure to ensure lubricant-free contact between the cam surface and follower wheels. The follower wheel which rotates on a shaft 250 is cantilevered from clutch housing 33K. Outputs from planet shafts 252 journaled in housing 33K are gear coupled together through stator gear 254.

One cam 35J drives two pivot/output shafts.

FIG. 23 shows a bicycle or, perhaps, an industrial speed changer of the invention, with multiple power paths directly driving the output housing. No differentials required.

FIGS. 24 and 25 illustrate a vehicular transmission. Input shaft 31L is journaled in and extending from housing 33L, double lobed cam 35L is integrated with hub 37L slidably, or ball splined to input shaft 31L. Cam follower castor wheels 45L with axles 88L journaled in rollers that run in hoop 100L biasing those wheels against the cam 35L in structure to ensure lubricant-free contact between cam surface and follower wheels. Planarity gearing 260 couple to output gear 262. The planet shafts 264 are journaled in housing 33L and are coupled by over running clutches 41L to cam followers 39L. Planetary gears 260 provide selection of forward, or reverse, drive, as well as park and a free neutral, a bypass gearset automatically clutched, 102, on a jack shaft 101 couple output shaft 43L to input shaft 31L to provide engine braking.

FIG. 26 shows speed torque ratios of the instant transmission. It is infinitely variable in speed with output torques inversely proportional to output speeds. It is a constant power transmission.

FIG. 27 shows the speeds of the followers where the dot-dash line is speed of first follower, the solid line is the speed of the second follower, the dotted line is the speed of the third follower and the dashed line is the speed of the fourth follower riding on one lobe of the cam. The second lobe provides a like set of speeds. The top line is the integrated output speed.

Characteristics of the described and illustrated embodiments are intended for illustrative purposes and are not considered limiting or restrictive. It is to be understood that various adaptations and modifications may be made by those skilled in the art to the embodiments illustrated herein, without departing from the spirit and sign of the inventions, as defined by the following claims thereof.