Cylindrical cam clutch
PRIOR ART 
     Prior art includes the following inventions; 
     Engine Drive, U.S. Pat. No. 2,440,674, May 1948, by J. D. Bell. This invention features three parallel cylindrical cams driven by the piston of an internal combustion engine. The reciprocating connecting rod imparts revolving motion to the cylinders by engaging two endless helical grooves in the cylinders. 
     Apparatus For Transforming A Rotary Motion Into An Alternating Linear Movement, U.S. Pat. No. 3,465,602, Sept. 1969, by J. P. Garaud. This invention features two parallel cylindrical cams which are driven by gears. The cylinders have continuous spiral grooves which impart alternating linear movement to a sliding element. 
     There are two other inventions featuring parallel cylindrical cams with helical grooves which operate sliding elements, these being; Mechanical Movement, U.S. Pat. No. 2,472,919, June 1949, by R. E. Paris, and Double Cam Drive, U.S. Pat. No. 3,682,005, August 1972, by Paul A. Fantz. 
     Concurrent art includes Cylindrical Cams which is disclosed in a copending application by this inventor. The drive cam of this invention is mounted on a smooth shaft and is similar to the driven cam of the cylindrical cam clutch. 
     SUMMARY 
     The invention is distinct and distinguishable over prior art in two respects; first, it uses drive cams to operate a driven cam, and second, the drive cams can be allowed to reciprocate on the shaft so as not to transmit motion to the pins. 
     The invention is distinct from the Cylindrical Cams of the copending application in its use of drive cams which reciprocate. 
    
    
     DRAWINGS 
     FIG. 1 is an elevation of the cylindrical cam clutch. 
     FIG. 2 is a cross section of the cylindrical cam clutch. 
     FIG. 3 is an enlarged view of a reciprocating pin. 
    
    
     DESCRIPTION 
     FIG. 2 shows the cylindrical cam clutch in the standard position of reference with the tops of the cylinders at 0°, the fronts of the cylinders at 90°, the bottoms of the cylinders at 180°, and the rears of the cylinders at 270°. 
     FIG. 1 is an elevation of the cylindrical cam clutch showing right drive cam 1 and left drive cam 2 mounted on splined drive shaft 3, showing driven cam 4 mounted on driven shaft 5 which is parallel to drive shaft 3, and showing right reciprocating pin 6 and left reciprocating pin 7 mounted in intermediate housing 8 between drive cams 1 and 2 and driven cam 4. 
     Each right drive cam 1 and left drive cam 2 has a continuous spiral groove defined by a cylindrical base 9 and two opposed inclined side walls 10 in the face 11 of cylinder 12. Right drive cam 1 and left drive cam 2 are identical but are revolved 180° from each other when installed on splined shaft 3. 
     The continuous spiral groove of right drive cam 1 is designated right groove 13, and the continuous spiral groove of left drive cam 2 is designated left groove 14. 
     Each groove 13 and 14 is evenly disposed on opposite sides of central vertical reference planes of revolution which are perpendicular to cylinders 12. The grooves curve outward to right and left from the reference plane, reach a point of maximum distance from the reference plane, and then reverse their direction of curvature and curve back toward the reference plane. The points of maximum distance of the grooves from the reference plane are designated right dead center 15 and left dead center 16. Dead centers 15 and 16 mark the point in the grooves at which the direction of reciprocation of the pins is reversed. 
     Right groove 13 has its right dead center 15 at 0° and its left dead center 16 at 180°. 
     Left groove 14 has its right dead center 15 at 182° and its left dead center 16 at 2°. (The 2° difference will be explained below.) 
     Driven cam 4 has two continuous spiral grooves designated right groove 17 and left groove 18, each groove defined by a cylindrical base 19 and two opposed inclined side walls 20 in face 21 of cylinder 22. 
     Grooves 17 and 18 also have central vertical reference planes of revolution. Right groove 17 has its right dead center 15 at 0° and its left dead center 16 at 180°. Left groove 18 has its right dead center 15 at 182° and its left dead center 16 at 2°. 
     The reason for revolving the left groove 14 of left drive cam 2 and the left groove 18 of driven cam 4 2° beyond the right grooves is to avoid having both reciprocating pins positioned at dead center when the machine is shut down and the cylinders stop revolving. During operation the momentum of the cylinders carries the pins past dead center, but when the machine is stopped, started, and the pins begin their movement from a stationary position, those pins which are positioned at dead center could move into the wrong arms of the grooves and reverse the direction of revolution of the cylinders. One pin must be either approaching or passing beyond dead center to prevent reverse revolution when the cylinders start to revolve. 
     Driven cam 4 can be made to revolve in the same direction as drive cams 1 and 2 by placing the right dead centers 15 at 178° and the left dead centers 16 at 358° in the left grooves 14 and 18. 
     Reciprocating pins 6 and 7 are mounted in sliding rectangular metal blocks 23 which are adapted to slide laterally in housing 8. The upper end of right pin 6 engages right groove 13 of drive cam 1, and the lower end engages right groove 17 of driven cam 4. The upper end of left pin 7 engages left groove 14 of left cam 2, and the lower end engages the left groove 18 of driven cam 4. 
     The reciprocating pins roll against the side walls of the grooves. In certain instances the direction of roll at opposite ends of the pins is in opposite directions. The pins are divided into two separate parts in order to accommodate rolls in opposite directions, as shown in FIG. 3. The upper end of the pin consists of a tapered roller 24 integrally adjoined to a shaft 25. The lower end of the pin consists of a tapered roller 26 integrally adjoined to a hollow cylinder 27 in which shaft 25 of the upper end revolves. Cylinder 27 revolves inside sliding block 23. 
     Operation 
     FIG. 1 shows the clutch in the disengaged position. Drive cams 1 and 2 are reciprocating and revolving in a clockwise direction on drive shaft 3. Pins 6 and 7 are stationary, and driven cam 4 is stationary. 
     The clutch is engaged by locking drive cams 1 and 2 together when they revolve 180° from the position shown in FIGS. 1 and 2. In the engaged position the right dead center 15 of drive cam 1 has revolved 180° to the bottom of the shaft and has engaged the upper end of right pin 6. The left dead center 16 of drive cam 2 has revolved 180° to the bottom of the shaft and has engaged the upper end of left pin 7. 
     During the first revolution of 180° in the engaged position, the right side wall 10 of drive cam 1 will exert pressure (lateral thrust) against right pin 6 and force the pin to the left (toward the center of the housing 8), and the left side wall 10 of drive cam 2 will exert pressure against left pin 7 and force the pin to the right (toward the center of the housing 8). 
     The lower end of right pin 6 will exert pressure (lateral thrust) against the left side wall 20 of right groove 17 and the lower end of left pin 7 will exert pressure against the right side wall 20 of left groove 18, and driven cam 4 will revolve 180° counterclockwise. 
     Drive cams 1 and 2 will be locked together by pins located inside drive shaft 3 as disclosed in a copending application. 
     The cylindrical cam clutch can be modified to operate as a forward-reverse transmission. The outer portion of the left drive cam 2 can be separated from the inner portion and adapted to be revolved 2° on both sides of 0°. The outer portion of the left side of driven cam 4 would be modified in a similar manner. When the outer portions of the cams were revolved to the 2° position, forward drive would result. When the outer portions were revolved to the 358° position, reverse drive would result.