Abstract:
Continuously variable transmission consists of two rolling friction planetaries with a transversely mounted disk interposed between wheels of the planetaries. Varying the position of the disk varies the speed ratio. Transmitted forces urge an idler wheel into a converging space between the internal ring and the wheel in contact with the disk so as to establish contact forces as a function of transmitted torque. Ratio change is made easy by temporarily moving the disk laterally and utilizing the resultant change in contact position to establish a velocity vector which urges the disk toward a new position using only the power being transmitted. Well-known gear systems are used to extend the ratio range. Well-known tractants, or friction enhancing lubricants are used as lubricants to prevent wear yet maximize capacity.

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     Not Applicable. 
     BACKGROUND 
     1. Field of the Invention 
     This invention relates to friction gearing continuously variable transmissions, specifically to an improved mechanism for transmitting power through tractional or frictional engagement of rings, wheels and a disk or disks. 
     Unique features relate to efficiency, control of loads in response to transmitted torque, control of speed ratio, maximum power capacity, reliability and manufacturing costs. 
     2. Description of Prior Art 
     Many continuously variable transmission concepts have been proposed in the past for vehicle and industrial applications. 
     Electrical, hydraulic, and mechanical methods have been proposed with many sub-categories and many combinations of sub-categories. 
     No proposed method has yet been accepted in the manner of either manual or automatic transmissions. This is because the prior art has failed in one or more requirements. Poor efficiency has been a major deterrent to most proposed systems. Damage during use or lack of reliability has likewise been a major deterrent. Complexity of control has been a major difficulty. The inability to transmit the power developed by large engines has been a limitation. High precision and high costs of precision have been substantial problems. The need for high capacity bearings to support high contact forces has been a limitation both because of bearing capacity and because of bearing power losses. Bearing power losses are higher with friction enhancing lubricants. Many other miscellaneous problems were also encountered. 
     Still, it is recognized that a continuously variable transmission which could overcome these problems would have operating fuel economies of real significance because engines, or prime movers, would be able to operate at more economical conditions. Thus saving valuable energy. Simultaneously, a proper continuously variable transmission would produce better acceleration, speed and deceleration performances. 
     Much of the mechanical prior-art has utilized the principle of transmitting power through rolling contact between two bodies. This principle can be used in a dry atmosphere like air and like halocarbon vapor; or, it can be used in the presence of various liquids. Some liquids have been developed specifically for this purpose and are known as tractants. These tractants lubricate surfaces, as do common oils, but they excel at supporting high shear stresses under contact conditions of high local pressures. 
     In order to avoid high power losses in traction mechanisms, it is necessary to reduce the contact force when the transmission is operating at less than maximum torque. 
     On the other hand, a time delay between a sudden increase in torque and the corresponding increase in contact force has been the cause of catastrophic damage to the rolling surfaces when slippage has occurred. Prior-art systems have been too slow to prevent such damage in the worst conditions. 
     The limited speed range of most of the prior-art has been partially overcome by using various combinations of fixed ratio gearing, clutches, brakes and the like. Compatibility with these systems is not shared by all prior-art but it is a major factor in some systems. 
     Currently there are three systems which appear to be favored by the automotive industry. 
     Firstly, the double toric system which has been under development for nearly a century. This system eliminates the need for high capacity bearings to support contact forces, but it suffers from a number of other factors: a. the need to control six rollers all in different planes, simultaneously, in order to change ratio; b. high inertia and flexibility of parts needed to respond to sudden torque changes for the prevention of catastrophic slippage; c. high manufacturing costs for the high precision rollers, concave faces and control mechanisms; d. power losses in the rolling contacts due to what is referred to as “spin”. 
     Secondly, the system known as the double half-toroid. This system minimizes the power losses due to spin but it suffers from: a. the need to support high contact forces with bearings, and their attendant power losses; b. high manufacturing costs for rollers, concave discs, and the control mechanisms; c. the need to control four rollers, in different planes, simultaneously, to change the ratio; d. high inertia of parts needed to respond to a sudden change in torque for the prevention of catastrophic slippage. 
     Thirdly, the system known as the VanDoorne metal belt. This system has had some success in vehicles with small engines but it suffers from a number of factors: a. it can&#39;t handle the power from big engines; b. it has poor efficiency when operarted at part load; c. the ratio change hydraulics have to be coordinated with the pressure needed to prevent slippage; d. the system is noisy. 
     In short, the prior-art has to be improved substantially to meet the requirements of a successful system. Such improvements are described in the following explanation of the invention. 
     OBJECTS AND ADVANTAGES 
     It is an object of the present invention to provide a continuously variable transmission system of high efficiency. 
     It is another object of the invention to provide a continuously variable transmission with improved resistance to slipping damage encountered by sudden changes in torque. 
     It is yet another object of the invention to provide a continuously variable transmission capable of handling the power from large engines as well as from small engines. 
     Another object is to improve the ease of controlling speed ratio by reducing the complexity of elements needed to effect ratio changes. 
     It is a further advantage to achieve the above objects in an economical manner using easily manufactured parts. 
     It is an additional advantage to achieve compatibility with other mechanical devices for extending the speed ratio range. 
     It is a significant object to provide a continuously variable transmission which is compatible with known oils or tractants. 
     It is an advantage to eliminate the need for bearings to support high contact forces because of their cost, because of their power losses and because of their size limitations. 
     These and other objects and advantages of the present invention will become apparent from the following description of the accompanying drawings, which disclose several embodiments of the invention. It is to be understood that the drawings are to be used for purposes of illustration only, and not as a definition of the invention. 
     SUMMARY 
     In accordance with the present invention, a disk is interposed between members of two friction gearing planetaries so as to permit transmission input and output speed ratios to be changed by changing the position of the disk with respect to the planetaries, simultaneously the contact forces are adjusted to accomodate changes in torque. 
    
    
     DRAWINGS 
     Figures 
     Further advantages and details can be gleaned from the drawings wherein similar reference numerals denote similar elements throughout the several views: 
     FIG. 1 is a side elevation view, partially in cross-section, of the present invention depicting a disk in rolling friction contact with wheels of two planetaries; 
     FIG. 2 is an elevation view, along the line A—A of FIG. 1, depicting the planetary wheels in rolling friction contact with the disk and, additionally, the idler wheels used to establish torque responsive contact loading; 
     FIG. 3 is an elevation view, along the line C—C of FIG. 1, depicting the planetary wheels in rolling friction contact with the disk and, additionally, the idler wheels used to establish torque responsive contact loading; 
     FIG. 4 is a sectional view along the line B—B of FIG. 1, depicting a method of control with an eccentric and a roller track; 
     FIG. 5 is a top view along the line D—D in FIG. 4, in partial section, of a disk in rolling friction contact with the wheels of two output planetaries; 
     FIG. 6 is similar to FIG. 5 except that a control change of position calls for another ratio; 
     FIG. 7 is similar to FIG. 6 except that the disk position corresponds to attainment of the ratio called for in FIG. 6; 
     FIG. 8 is a velocity vector diagram showing velocity components when the eccentric has called for a new ratio in FIG. 6; 
     FIG. 9 is a side elevation similar to FIG. 1 of a system whose input and output members turn in the same direction; 
     FIG. 10 is an elevation view of a planetary using different ring surfaces and wheel surfaces for rolling contacts; 
     FIG. 11 is a section view of FIG. 10; 
     FIG. 12 is a schematic drawing of a disk used with a single planetary for variable speed; 
     FIG. 13 is same as FIG. 12 except at a different speed ratio. 
    
    
     DETAILED DESCRIPTION 
     Referring to FIG. 1, FIG.  2  and to FIG. 3,  20  is a continuously variable transmission (CVT) having a shaft  22  on the left and a shaft  24  on the right; either shaft may be used as the power input while the other is the power output. A casing  26  and end bells  28  and  30 , constitute the CVT housing. Retaining rings  32  and  34  secure the end bells to the casing. 
     Bearing  36  rotatably supports shaft  22 . Seal  38  seals shaft  22 . Ring  40  is driveably connected to shaft  22  through members  42  and  44 . Wheel  46  contacts the inner diameter of ring  40  and is rotatably supported by a bearing  48  on pin  50 . Pin  50  is supported by retainer plates  43   a  and  43   b.  Retainer plates  43   a  and  43   b  are separated by spacers and are fastened to two bosses one of the bosses is shown in FIG.  1  and is numbered  27   b  on casing  26  with screws  29   a  and  29   b.  Retaining rings  52  secure the pin  50  against axial movement. 
     Disk  56  contacts wheel  46  at a point opposite the contact of wheel  46  and ring  40 . Disk  56  is rotatably supported by a bearing  58  which is eccentrically mounted to a track roller assembly  60  through needle bearing  62  and eccentric  64 . Track roller assembly  60  consists of two rollers pressed onto a shaft. The track roller assembly is guided by ways  66   a  and  66   b  in casing  26 . Control arms  69   a  and  69   b  are mounted to eccentric  64 . 
     Another wheel,  68 , contacts disk  56  on the opposite side of the disk center from wheel  46 . Wheel  68  contacts the inner diameter of ring  76  and is rotatably supported by a bearing  70  on pin  72 . Pin  72  is supported by retainer plates  71   a  and  71   b . Retainer plates  71   a  and  71   b  are separated by spacers and are fastened to bosses one of the bosses is shown in FIG.  1  and is numbered  75   b  on casing  26  with screws  29   c  and  29   d.  Retaining rings  74  secure the pin  72  against axial movement. 
     Ring  76  is attached to stiffening ring  78  and web  80  which driveably connect to shaft  24 . Bearing  82  rotatably supports shaft  24  to end bell  30 . Seal  84  provides sealing for shaft  24 . 
     Sun wheel  86  contacts disk  56  on the face opposite the contact with wheel  46 . Bearing  85  supports sun wheel  86  on pin  87 . Pin  87  is mounted in slots  89   a  and  89   b  which are elongated in a radial direction perpendicular to the surface of disk  56 , as shown in FIG.  2 . Slots  89   a  and  89   b  are part of roller retainers  81   a  and  81   b , respectively, which are separated by three spacers one of which is shown in FIG.  1  and is numbered  83   b . Screws  29   e ,  29   f  and  29   g  fasten the retainers and spacers to bosses of housing  26 . 
     The centerline of sun wheel  86  is positioned away from the centerline of ring  40  so that the gap between the inside diameter of ring  40  and the outside diameter of sun wheel  86 , shown in FIG. 2, changes in width. Load wheels  88  and  90  are respectively in contact with sun wheel  86  and ring  40 , and positioned in the aforesaid gap. Load wheel  88  is rotatably mounted on a bearing  92 , which is only partially constrained. The inner race of bearing  92  has protrusions with abutment surfaces  94 . Abutment surfaces  94 , and  96  on the roller retainers  81   a  and  81   b,  limit the position of the inner race and hence, the wheel  88 . 
     Wheel  90  is rotatably mounted on bearing  98  and limited in position by abutment surfaces  100  and  102 . Springs  104   a  and  104   b  are in tension and force bearings  92  and  98  closer together, resulting in pre-load forces of contact between members of the planetary contained within ring  40 . 
     Seal  84  provides sealing for shaft  24 . 
     Sun wheel  106  contacts disk  56  on the face opposite the contact with wheel  68 . Bearing  101  supports sun wheel  106  on pin  103 . Pin  103  is mounted in slots  105   a  and  105   b  which are elongated in a radial direction perpendicular to the surface of disk  56 , as shown in FIG.  3 . Slots  105   a  and  105   b  are part of roller retainers  107   a  and  107   b,  respectively, which are separated by spacers  109   a ,  109   b  and  109   c.  Screws  29   h ,  29   i  and  29   j  fasten the retainers and spacers to bosses  27   h ,  27   i  and  27   j  of housing  26 . 
     The centerline of sun wheel  106  is positioned away from the centerline of ring  76  so that the gap between the inside diameter of ring  76  and the outside diameter of sun wheel  106 , shown in FIG. 3, changes in width. Load wheels  108  and  110  are respectively in contact with sun wheel  106  and ring  76 , and positioned in the aforesaid gap. Load wheel  108  is rotatably mounted on a bearing  118 , which is only partially constrained . The inner race of bearing  118  has protrusions with abutment surfaces  100 . Abutment surfaces  100 , and  102  on the roller retainers  107   a  and  107   b,  limit the position of the inner race and hence, the wheel  106 . 
     Wheel  110  is rotatably mounted on bearing  120  and limited in position by abutment surfaces  114  and  112 . Springs  116   a  and  116   b  are in tension and force bearings  118  and  120  closer together, resulting in pre-load forces of contact between members of the planetary contained within ring  76 . 
     FIG. 4 is a view through B—B of FIG.  1 . Shaft  122  is the ratio control input shaft which may be positioned by any suitable means normally used to either manually or automatically select the CVT speed ratio. Ratio change arm  124 , with pin  126 , is fastened to turn with control shaft  122 . Pin  126  engages both control arms  69   a  and  69   b  through slots in the control arms. The control arms  69   a  and  69   b  are attached to eccentric  64  so as to control the angular position of eccentric  64  with respect to roller assembly  60 . Needle bearing  62  permits ease of rotation between eccentric  64  and the shaft of roller assembly  60 . 
     FIG. 5 is a sectional view along D—D of FIG.  4 . Contact spots  128  and  130  are the elastic deflection areas of contact between disk  56  and planetary sun rollers  86  and  106 , respectively. In FIG. 5, spots  128  and  130 , the center of disk  56  and the center of roller assembly  60  are in a straight line. 
     FIG. 6 is the same as FIG. 5 except that control members  122 ,  124 ,  126  and  69   b  have been moved so as to move the center of disk  56  off the line joining  128  and  130 , by rotating eccentric  64 . 
     FIG. 7 shows that spots  128  and  130  are again co-linear with the center of disk  56  which has moved to a new position in response to the new position of ratio change arm  124 . 
     FIG. 8 is a velocity vector diagram of conditions which exist with contact spots  128  and  130  when the center of disk  56 , at  132 , is off the line, joining  128  and  130 , by an amount  134 . Vectors  136  and  142  are rotational velocity vectors resulting from the spinning of disk  56 . Vectors  140  and  146  are the velocity vectors of the planetary rollers  86  and  106 , respectively. Vectors  138  and  144  are the translational vectors urging the disk  56  to its new position of equilibrium. 
     FIG. 9 is the same as FIG. 1 except that one planetary assembly is flipped  180  degrees, about the disc, so that the planetary idler rollers are on the bottom in one planetary and on the top in the other planetary. This results in the same direction of rotation for input and output shafts  22  and  24 , rather than the reversal of direction as in FIG. 1. A new casing  148  is the only part that is different from those of FIG.  1 . 
     Operation 
     Operation of the CVT is based on the principle of transmitting power through rolling contact of one member forced against another with sufficient force to prevent gross slippage. This principle may be used in gaseous environments, including air and halocarbon vapors. Or, it may be used in the presence of oil or grease. Numerous oils and greases are available for this purpose. Some have higher tractive and lubricative properties than others and are the preferred materials. They are known as friction enhancing lubricants. 
     Referring to FIG.  1  and to FIG. 2, initial conditions of operation include pre-load forces between rolling members of the two planetaries and the disk  56 . Thus the CVT is ready for power input at either shaft  22  or shaft  24 . 
     Assume power input to shaft  22 , turning in a clockwise direction as viewed from the input end. This would be the same as if the CVT were being driven by a conventional vehicle engine. Shaft  22 , web  42 , ring  40  and ring  44  would all rotate in unison because they are rigidly connected to each other. Bearing  36 , in end bell  28 , supports shaft  22  and permits its rotation. Rotation of ring  40  causes planetary roller  46  to rotate about pin  50  through bearing  48  because ring  40  and roller  46  are in contact with sufficient force to cause traction. 
     Similarly, rotation of ring  40  causes rollers  90  and  88  to rotate because of tractive contact caused by springs  104   a  and  104   b  acting on the inner race protrusions  92  and  98 . The springs tend to force the planet rollers into the converging gap between the ring  40  and sun roller  86 . Movement into the converging gap is resisted by the forces on sun roller  86 . These forces also cause forces between disk  56  and sun roller  86  because the bearing  85  and pin  87  are free to move radially in slots  89   a  and  89   b.  Thus, rotation of rollers  90  and  88  also cause the sun roller  86  to rotate and in turn drive disk  56 . Disk  56  is also being driven on the opposite face by roller  46 . The contact of sun roller  86  and disk  56  may be directly opposite the contact between planetary roller  46  and disk  56 , or, they may be slightly offset to compensate for a slight loss in velocity resulting from an extra contact in the path driving sun roller  86 . Exact 50%-50% driving through the two different paths is not necessary and has only a small effect on the capacity or efficiency of the CVT. 
     Tractive forces acting on planetary roller  88 , shown in FIG. 10, tend to wedge the roller into the converging gap between the ring  40  and the sun  86 . Normal contact forces from ring  40  and from sun roller  86  must vectorially balance said tractive forces. This allows an increase in contact forces in response to an increase in tractive forces and thereby prevents slippage between the tractive elements. This is the same notion used by Dietrich in U.S. Pat. No. 1,093,922 for a fixed ratio friction planetary, except that a disk  56  has been interposed between rolling elements. Tractive forces on planetary roller  90  tend to drive it out of the gap into the diverging direction. This action is prevented by having the bearing inner race abutment surfaces  100  contact abutment surfaces  102  on the roller retaining members  81  a and  81   b.  Normal contact forces are maintained on planetary roller  90  because ring  40  and its structure are permitted to deflect slightly so that the roller forces hold it in equilibrium. The fact that rollers  88  and  90  have very low inertia and that they must move only slightly to greatly increase the contact loads are a major advantage over prior art which must move parts having large inertias and must move them considerably further because of greater elastic deflections. This feature allows the subject invention to respond to sudden changes in transmitted torque which would cause other drives to slip and cause surface damage. 
     The ratio of speed between the input  22  and the disk  56  is dependent upon the position of the disk  56  with respect to the contact spots on rollers  46  and  86 . The closer the center of disk  56  is to the contact spot, the faster disk  56  will turn. Conversely, as the center of disk  56  moves away from the contact spot, the slower disk  56  will turn. This is the method by which the invention achieves continuously variable speed ratios. Disk  56  is allowed to rotate freely by being supported by bearing  58 . Bearing  58  is in turn mounted on eccentric  64  which is supported on needle bearing  62  on track roller assembly  60 . Control arms  69   a  and  69   b  control the position of eccentric  64  with respect to roller assembly  60  and disk  56 . Roller assembly  60  is constrained to travel in tracks  66   a  and  66   b.    
     Power transmitted to disk  56  by rollers  46  and  86  is similarly transmitted by disk  56  to rollers  68  and  106  of the second planetary shown in FIG.  3 . Referring to FIG. 3, which is looking at the planetary from the output side as depicted by view D—D of FIG. 1, the surface of disk  56  would be moving from left to right; rollers  68 ,  108 , and  110  would be turning clockwise; roller  106  would be turning counterclockwise. Roller  108  would be pushing on ring  76  with a clockwise force while the reaction force would be pushing roller  108  into the converging portion of the gap between the sun roller  106  and the ring  76 . Similarly since sun roller  106  is pushing on roller  108  in a direction to turn  108  clockwise, its force will tend to push  108  into the converging gap. 
     The normal forces must combine to resist the transmitted forces, and thus establish contact forces in proportion to transmitted torque. Low inertia and slight movement again achieve fast response to torque changes compared to prior art. 
     Operation of the ratio changing mechanism is explained referring to FIGS. 4,  5 ,  6 ,  7 , and  8 . The control shaft  122  may be rotated about its axis as constrained by housing  26 . The position of control shaft  122  determines the position of control arm  124  which contains pin  126 . When the arm  69   b  is aligned as shown in FIG. 5, a line between contact spots  128  and  130  passes through the center of disk  56 . 
     When the position of the control shaft  122  is changed as in FIG. 6, the position of pin  126  is changed and drags the control arm  69  to a new position. The center of disk  56  is moved because of eccentric  64  attached to control arm  69 . The line between contact spots  128  and  130  is no longer aligned with disk center  132 , but is moved a distance  134  as shown in FIG.  8 . Velocity vectors from the planetary wheels are shown as  140  and  146 . Velocity vectors of the disk contact spots must be perpendicular to a line joining the spot and the disk center  132 , and are shown as  136  and  142  in FIG.  8 . 
     The difference in velocity vectors  136  and  140  give rise to a vector  138  which urges disk  56  to move so that the resultant velocity of contact spot  128  is the same as wheel vector  140 . Similarly the resultant velocity vectors at contact spot  130  give rise to vector  144  which is similar in magnitude and direction as vector  138 . Thus both contact spots produce forces and vectors urging the disc to a new position. 
     When the disk has moved so that conditions of alignment are as shown in FIG. 7, contact spots and the disk center again align and the vector urging movement of the disk again goes to zero. 
     Description—Alternative Embodiment 
     Referring to FIG.  10  and FIG. 11, an alternative compound planetary is shown which achieves a reduction in the number of contact stress cycles and which permits independent selection of the magnitude of contact stress in the various frictional contacts. Independent selection of contact stress is a means to prevent loss of traction due to hydroplaning which can occur at low contact stress values with some tractants. 
     This compound planetary may be used in place of the simple planetaries of FIGS.  1 ,  2  and  3 . 
     Ring  148  replaces ring  44  of FIG. 1, and includes inner surfaces  162  and  166 . Annular groove  156  is made to provide clearance between ring  148  and contact surface  176  of planet wheel  150 . 
     Surfaces  164  and  158  on idler wheels  154  are in contact with ring  148  inner surfaces,  162  and  166 , and with sun wheel  152  external surfaces  170  and  172 . 
     Sun wheel  152  is in contact with disk  56  on surface  174 . 
     Planet wheel  150  is in contact with ring  148  surfaces  162  and  166  on its surfaces  178  and  180 . Planet wheel  150  is in contact with disk  56  on surface  176 . 
     Bearing journals  160  are for mounting to bearings to permit rotation of the wheels. 
     The position of disk  56  is variable as in FIG. 1 
     Operation—Alternative Embodiment 
     Assume ring  148  is driven. Power from ring  148  to planet wheel  150  is transmitted through contacts of surfaces  178  and  180  of wheel  150  and inner diameter surfaces  162  and  166  of ring  148 . Surface  176  of wheel  150  then drives the disk  56 . 
     Ring  148  also drives planet idler wheels  154  through contacts with ring  148  inner surfaces  162  and  166 , on surfaces  164  and  168  of wheels  154 . Wheels  154  drive sun wheel  152  on surfaces  170  and  172 . Sun wheel  152  then drives disk  56  through contact with surface  174  of sun wheel  152 . 
     Thus, ring  148  drives disk  56  at a speed ratio dependent upon the position of disk  56  with respect to the driving contacts of surfaces  174  and  176 . Contact stress cycles are reduced on surfaces  174  and  176  compared to FIG. 1, FIG.  2  and FIG.  3 . 
     Contact surfaces  162 ,  166 ,  164 ,  158 ,  172 ,  170 ,  178 , and  180 , may be sized to prevent low traction due to hydroplaning on the tractant fluid. 
     Description—Additional Embodiment 
     Referring to FIG.  12  and FIG. 13, an additional embodiment is shown in schematic form. A single planetary is used with a movable disk, driven by a power source. Housing  184  contains driving disk  192  which is connected to power source  186  through shaft  190 . Disk  192  is in contact with the periphery of planet wheel  196 , on one surface, and with the periphery of sun wheel  194  on the opposing surface. 
     Planet wheel  196  is rotationally supported by housing member  198 . Sun wheel  194  is rotationally supported by housing member  200 . Idler wheels as shown in FIG. 2 are included. Output assembly  188  is rotationally supported in housing  184  and is in tractional contact with planet wheel  196  and idler wheels. 
     Power source  186  is movable with respect to housing  184 . Actuator  202  connects housing  184  to power source  186  through linkage  204 . 
     Operation—Additional Embodiment 
     Referring to FIG. 12, rotational power from power source  186  rotates shaft  190  and disc  192 . Disk  192  rotates wheels  194   1 nd  196  through rolling traction. Planet wheel  196  rotates the ring of assembly  188  through rolling traction. Power from sun wheel  194  is transmitted to idler wheels which also drive the ring of assembly  188  through rolling traction. Idler wheels as shown in FIG. 1 control normal loads in response to the magnitude of torque. The speed ratio between power source  186  and output assembly  188  is determined by the position of disk  192 . 
     Referring to FIG. 13, the speed ratio between power source  186  and output assembly  188  is increased, compared to FIG.  12 . Position of disk  192  has been changed as a result of actuator  202  changing the length of linkage  204  and repositioning the power source. 
     CONCLUSIONS, RAMIFICATIONS AND SCOPE 
     Thus the reader will see that the continuously variable transmission of the invention provides a means that solves all of the problems of prior traction drives, and may be used to save fuel usage when used with engines of all sizes. The invention uses simple shapes that are economical to manufacture. The invention provides means to protect it from damage due to sudden overloads, is easy to control ratio changes, and capable of many different arrangements. The ability to achieve high efficiency by elimination of thrust bearings and low loss contacts are advantages over other continuously variable transmissions. 
     While my above descriptions contain many specificities, these should not be construed as limitations on the scope of the invention, but rather exemplifications of preferred embodiments. Many other variations are possible. For example, two, three, or more disks may be interposed between the two planetaries. Some of the planetary members may be gear driven. Other loading means described in prior art may be used. Such as split tapered rings, or shrink fits. Input and output shafts may be coaxial and on the same side of the planetaries. The invention may be used with other gear trains to achieve geared neutral, split power paths, synchronous shifts and non-synchronous shifts. All to extend the speed range. 
     Accordingly, the scope of the invention should be determined not by the embodiments illustrated, but by the appended claims and their legal equivalents. 
     
       
         
               
             
               
               
             
           
               
                   
               
               
                 Reference Numerals In Drawings 
               
               
                   
               
             
             
               
                   
               
             
          
           
               
                  20 
                 continuously variable transmission 
               
               
                  22 
                 power shaft-left 
               
               
                  24 
                 power shaft-right 
               
               
                  26 
                 casing 
               
               
                  27 
                 boss of casing 26 
               
               
                  28 
                 end bell-left 
               
               
                  29 
                 screw fasteners 
               
               
                  30 
                 end bell-right 
               
               
                  32 
                 retaining ring-end bell-left 
               
               
                  34 
                 retaining ring-end bell-right 
               
               
                  36 
                 bearing-power shaft-left 
               
               
                  38 
                 seal-power shaft-left 
               
               
                  40 
                 ring-traction-left 
               
               
                  42 
                 web-left 
               
               
                  43 
                 retainer plate 
               
               
                  44 
                 stiffening ring-left 
               
               
                  45 
                 retainer spacer 
               
               
                  46 
                 wheel-planetary-left 
               
               
                  48 
                 bearing-in wheel-left 
               
               
                  50 
                 pin-in wheel-left 
               
               
                  52 
                 retaining rings 
               
               
                  56 
                 disk 
               
               
                  58 
                 bearing-in disk 
               
               
                  60 
                 track roller assembly 
               
               
                  62 
                 needle bearing-eccentric 
               
               
                  64 
                 eccentric 
               
               
                  66 
                 guide ways 
               
               
                  68 
                 wheel-planetary-right 
               
               
                  69 
                 control arm 
               
               
                  70 
                 bearing-in wheel-right 
               
               
                  71 
                 retainer plate 
               
               
                  72 
                 pin-in wheel-right 
               
               
                  73 
                 retainer spacer 
               
               
                  74 
                 retaining rings 
               
               
                  76 
                 ring-traction-right 
               
               
                  78 
                 stiffening ring-right 
               
               
                  80 
                 web-right 
               
               
                  81 
                 wheel retainer 
               
               
                  82 
                 bearing-power shaft-right 
               
               
                  83 
                 retainer spacer 
               
               
                  84 
                 seal-power shaft-right 
               
               
                  86 
                 wheel-sun-left 
               
               
                  87 
                 pin 
               
               
                  88 
                 load wheel-left-driving (left) 
               
               
                  89 
                 slot 
               
               
                  90 
                 load-wheel-left-driven (right) 
               
               
                  92 
                 bearing-load wheel 
               
               
                  94 
                 abutment surfaces on inner race 
               
               
                  96 
                 abutment surfaces on casing 
               
               
                  98 
                 bearing-load wheel 
               
               
                 100 
                 abutment surfaces on 98 
               
               
                 101 
                 bearing 
               
               
                 102 
                 abutment surfaces on casing 
               
               
                 103 
                 pin 
               
               
                 104 
                 springs-pre load 
               
               
                 105 
                 slot 
               
               
                 106 
                 wheel-sun-right 
               
               
                 107 
                 wheel retainer 
               
               
                 108 
                 load wheel-right driving (right) 
               
               
                 109 
                 spacer 
               
               
                 110 
                 load wheel-right driven (left) 
               
               
                 112 
                 abutment surfaces connected to casing 
               
               
                 114 
                 abutment surfaces on inner race 
               
               
                 116 
                 springs-pre load 
               
               
                 118 
                 bearing 
               
               
                 120 
                 bearing 
               
               
                 122 
                 control shaft 
               
               
                 124 
                 ratio change arm 
               
               
                 126 
                 pin 
               
               
                 128 
                 contact spot-sun 86 
               
               
                 130 
                 contact spot-sun 106 
               
               
                 132 
                 center of disk 56 
               
               
                 134 
                 amount eccentric displaced 132 from line joining 128 and 130 
               
               
                 136 
                 velocity of rotation of disk 56 at spot 128 
               
               
                 138 
                 velocity of translation of disk 56 
               
               
                 140 
                 velocity of planetary wheel 46 or sun wheel 86 
               
               
                 142 
                 velocity of rotation of disk 56 at spot 130 
               
               
                 144 
                 velocity of translation of disk 56 
               
               
                 146 
                 velocity of planetary wheel 68 or sun wheel 101 
               
               
                 148 
                 planetary ring 
               
               
                 150 
                 planet wheel 
               
               
                 152 
                 sun wheel 
               
               
                 154 
                 idler planet wheels 
               
               
                 156 
                 annular clearance groove in ring 148 
               
               
                 158 
                 idler wheel traction surface 
               
               
                 160 
                 bearing journals 
               
               
                 162 
                 traction surface of ring 148 
               
               
                 164 
                 idler wheel traction surface 
               
               
                 166 
                 traction surface of ring 148 
               
               
                 168 
                 annular clearance groove in idler wheels 154 
               
               
                 170 
                 traction surface for sun wheel 152 to idler wheel 154 
               
               
                 172 
                 traction surface for sun wheel 152 to idler wheel 154 
               
               
                 174 
                 traction surface of sun wheel 152 to disk 56 
               
               
                 176 
                 traction surface of planet wheel 150 to disk 56 
               
               
                 178 
                 traction surface of planet wheel 150 to disk 56 
               
               
                 180 
                 traction surface of planet wheel 150 to disk 56 
               
               
                 184 
                 housing 
               
               
                 186 
                 power source 
               
               
                 188 
                 output assembly 
               
               
                 190 
                 input shaft 
               
               
                 192 
                 driving disk 
               
               
                 194 
                 sun wheel 
               
               
                 196 
                 planet wheel 
               
               
                 198 
                 housing support for planet wheel 196 
               
               
                 200 
                 housing support for sun wheel 194 and idler wheels 
               
               
                 202 
                 actuator 
               
               
                 204 
                 linkage