Patent Publication Number: US-7722490-B2

Title: Cones, configurations, and adjusters for friction and non-friction dependent continuous variable transmissions

Description:
CROSS REFERENCE TO RELATED APPLICATIONS 
   This invention is a Continuation-in-part (CIP) of U.S. patent application Ser. No. 11/039,297, which was filed on Jan. 20, 2005 now abandoned. In addition, this invention is entitled to the benefit of Provisional Patent Application (PPA) Ser. No. 60/696,588 filed on Jul. 5, 2005, PPA Ser. No. 60/700,847 filed on Jul. 19, 2005, PPA Ser. No. 60/724,098 filed on Oct. 6, 2005, PPA Ser. No. 60/729,822 filed on Oct. 25, 2005, PPA Ser. No. 60/773,916 filed on Feb. 16, 2006, PPA Ser. No. 60/795,528 filed on Apr. 27, 2006, PPA Ser. No. 60/845,617 filed on Nov. 28, 2006, and PPA Ser. No. 60/901,686 filed on Feb. 14, 2007. 

   BACKGROUND 
   1. Field of Invention 
   This invention relates to variable torque/speed transmission, specifically to a variable transmission where the transmission ratio can be varied continuously between any two predetermined values. 
   2. Description of Prior Art 
   In most applications the transmission ratio, which is the torque vs. speed ratio transmitted by a driving source, needs to be adjustable in order for the driving source to operate efficiently and effectively. For example, for a vehicle, during start-up, assuming that it is on a level road, the driving source needs to provide torque to accelerate the vehicle and torque to overcome the resisting forces mainly due to friction and wind resistance. Once the vehicle has reached its desired speed, again assuming that it is on level road, the engine only needs to provide torque to overcome the resisting forces, which in this case is likely to be greater than during start-up, but less than the total torque needed during start-up. Hence in this case the torque that the driving source needs to provide is less than the torque that it needs to provide during start-up. However, here the driving source needs to rotate the output shaft at a higher speed since the desired speed of the vehicle is assumed to be greater than the speed of the vehicle during start-up. From the example above, it can be seen that during start-up, the driving source needs to provide a relatively large torque and operate at a relatively low speed. And once the desired speed is reached, the driving source needs to provide a relatively small torque and operate at a relatively high speed. Here a relatively large torque would be wasteful. Hence in order to increase the efficiency of the driving source most vehicles have a transmission, which can vary the torque vs. speed ratio of the driving source. 
   Most vehicles, such as cars, bikes, or motorcycles use a discrete variable transmission. Here the operator can select between several discrete transmission ratios usually by selecting an input gear or sprocket that is coupled to an output gear or sprocket, which is selected from a set of output gears or sprockets of various pitch diameters. The main advantage of a Continuous Variable Transmission (CVT) over a discrete variable transmission is that a CVT can provide the driving source with a more efficient transmission ratio under most conditions. 
   One well know CVT, which principal of operation is similar with many CVT&#39;s of prior art, consists of two cones, each keyed to a separate shaft, that are coupled by a belt. Because the cones have a tapered surface, the pitch diameters of the cones, which depend on the diameters of the surface of the cones where the belt is axially positioned, changes as the axial position of the belt is changed. Since the apex of the cones point in the opposite direction, changing the axial position of the belt increases the pitch diameter of one cone while decreases the pitch diameter of the other cone. This fact is used to change the transmission ratio between the shafts. One problem with this CVT is that changing the transmission ratio causes wear and frictional energy loses, since the belt has to slide and/or stretch relative to the surfaces of the cones as the pitch diameters are changed. 
   Another problem with the CVT mentioned in the previous paragraph is that torque can only be transmitted by friction. The need of friction limits the torque that can be transmitted, without causing unpractical high stresses in the belt and in the CVT&#39;s supporting members. 
   SUMMARY 
   It is an object of this invention to present cones or cone assemblies with one or two oppositely positioned torque transmitting devices, such as torque transmitting arcs of constant pitch (formed by torque transmitting members) or teeth. The torque transmitting devices will be used for torque transmission between at least one means for coupling, such as transmission belt or chain, and a cone or cone assembly. The cones or cone assemblies can be used to construct CVT&#39;s for which significant circumferential sliding between the torque transmitting surfaces of the torque transmitting devices and the torque transmitting surfaces of the means for coupling engaged to them due to change in pitch diameter can be eliminated, as to reduce wear and frictional energy loses typical in similar devices of prior art and allow the usage of positive engagement devices, such as teeth, in coupling the torque transmitting devices with their means for coupling. 
   It is another object of this invention to present CVT&#39;s that consist of at least one cone or one cone assembly of this invention that is coupled by a means for coupling to at least one means for conveying rotational energy, such as a pulley, a sprocket, a cone assembly of this invention, or a cone of this invention. 
   It is another object of this invention to provide adjuster systems that can increase the performance of the CVT&#39;s of this invention and other CVT&#39;s that suffer from either or both transition flexing and a limited duration at which the transmission ratio can be changed, so that efficient non-friction dependent CVT&#39;s and efficient friction dependent and CVT&#39;s do not suffer from transition flexing and/or a limited duration at which the transmission ratio can be changed can be constructed. Several CVT&#39;s utilizing an adjuster system are described in this patent. 
   OBJECTS AND ADVANTAGES 
   Accordingly the objects and advantages of the present invention are:
     (g) To provide cones or cone assemblies that can be used to construct various CVT&#39;s.   (h) To provide several CVT&#39;s for which frictional energy loses and wear due to change in transmission ratio can be significantly reduced over many CVT&#39;s of prior art.   (i) To provide several non-friction dependent CVT&#39;s that have better efficiency than many CVT&#39;s of prior art.   (j) To provide adjuster systems that can eliminate or significantly reduce transition flexing in some of the CVT&#39;s described in this patent as well as other CVT&#39;s that suffer from the same problem, as to increase the performance and live of those CVT&#39;s.   (k) To provide adjuster systems that can substantially increase the duration at which the transmission ratio can be changed for some of the CVT&#39;s described in this patent as well as other CVT&#39;s that suffer from the same problem, as to improve the transmission ratio changing responsiveness of those CVT&#39;s   (l) To increase the efficiency of machines by introducing CVT&#39;s that have sufficient torque transmission efficiency to replace discrete variable transmissions.
 
Still further objects and advantages will become apparent from a consideration of the ensuing description and drawings.
   

   
     DRAWING FIGURES 
     In the drawings, closely relayed figures have the same number but different alphabetic suffixes. Also because of time constraint some items are not drawn to scale, however with the accompanying description their intent should be clear. 
       FIGS. 1A and 1B  show the general configuration for the cone with torque transmitting member(s), where a torque transmitting member is positioned at the larger end of its cone. This cone assembly is labeled as cone assembly  1026 . 
       FIGS. 1C and 1D  show the general configuration for the cone with torque transmitting member(s), where a torque transmitting member is positioned at the smaller end of its cone. This is another drawing of cone assembly  1026 . 
       FIGS. 2A and 2B  show a cone  1024  on which a friction torque transmitting member  1046 F, which uses friction to transmit torque, is attached. 
       FIGS. 3A ,  3 B,  3 C, and  3 D are drawings of a cone with two torque transmitting members, which are placed opposite from each other. This cone assembly is labeled as cone assembly A  1026 A. 
       FIGS. 4A ,  4 B,  4 C, and  4 D are drawings of a cone with one torque transmitting member and one maintaining member, which is placed opposite from the torque transmitting member. The arc length of its torque transmitting member is limited as will be discussed in the description for cone assembly B  1026 B. This cone assembly will be referred to as cone assembly B  1026 B. In addition,  FIGS. 4A ,  4 B,  4 C, and  4 D also show a mover mechanism that will be used to move the torque transmitting members and the maintaining members relative to the surface of the cone to which they are attached in the axial direction. 
       FIGS. 5A ,  5 B,  5 C, and  5 D are drawings of a cone with one torque transmitting member, which arc length is limited. The arc length limitation will be discussed in the description for cone assembly C  1026 C. This cone assembly will be referred to as cone assembly C  1026 C. 
       FIGS. 6A to 6D  shows a cone assembly AF  1026 AF that uses friction torque transmitting members  1046 F. 
       FIG. 7A  shows a front-view of an attachment plate that is connected to its telescope. 
       FIG. 7B  shows a top-view of an attachment plate that is connected to its telescope. 
       FIGS. 8A and 8B  shows a CVT that uses two cone assemblies A  1026 A. This CVT will be labeled as CVT  1 . 
       FIG. 9A  is a top-view of a CVT that uses two cone assemblies B  1026 B, which are coupled to two transmission pulleys. This CVT will be labeled as CVT  2 . 
       FIG. 9B  is a top-view of a CVT that uses two cone assemblies C  1026 C, which are coupled to two transmission pulleys. This CVT will also be labeled as CVT  2 . 
       FIG. 9C  is a cross-sectional front view of CVT  2  taken at the axial midpoint of a torque transmitting member, which is positioned at the larger end of cone assembly B  1026 B. 
       FIG. 9D  is a cross-sectional front view of CVT  2  taken at the axial midpoint of a torque transmitting member, which is positioned at the smaller end of cone assembly B  1026 B. 
       FIG. 9E  shows a joiner mechanism that can be used to connect the slider bushings of cone assemblies B  1026 B and cone assemblies C  1026 C. 
       FIG. 10  shows a top-view of a CVT  3 , which is a CVT where one cone assembly is coupled by a belt to a pulley. 
       FIG. 11A  is a sectional front-view of CVT  1 . 
       FIG. 11B  is a top-view of CVT  1 . 
       FIG. 12A  is a sectional front-view of CVT  1 . 1 . 
       FIG. 12B  is a top-view of CVT  1 . 1 . 
       FIG. 13  is a top-view of transition flexing adjuster AD 1 A  101 A. 
       FIG. 14  is a top-view of mover adjuster AD 2 A  102 A. 
       FIG. 15  is a partial top-view of transition flexing adjuster AD  101 A. 
       FIG. 16  is a partial top-view of transition flexing adjuster AD  101 , on which a relative rotational position sensor SN 3 A  133 A is mounted. 
       FIG. 17  is a top-view of rotatable coupling  190 . 
       FIG. 18  is a top-view of a ring and brush electrical connection. 
       FIG. 19  is a sectional front-view of constrainer mechanism CN 1 A  111 A. 
       FIGS. 20A-20D  shows how the relative rotational position between the torque transmitting members need to be adjusted in order to reduce transition flexing. 
       FIGS. 21A-21C  show graphs that show the required rotational rotation, l θ , vs. arc length of the critical non-torque transmitting arc, l c . 
       FIG. 22  is a top-view of CVT  2 . 
       FIG. 23  is a top-view of CVT  2 . 1 . 
       FIGS. 24A-24D  show sectional front-views of CVT  2 . 1 , which show the angle θ, which is the angle between the neutral point, N, and the midpoint, M, of the upper positioned torque transmitting member, and the direction of transmission ratio change rotation, Δθ. 
       FIG. 25  shows an equation that can be used in order to calculate transmission ratio change rotation. 
       FIGS. 26A-26C ,  27 A,  27 B,  28 A,  28 B,  29 A,  29 B show sectional front-views of CVT  2 . 1 , which are used in order to illustrate the required direction of the adjusting rotation, ω A , of transmission pulley  41 C in order to compensate for transmission ratio change rotation. 
       FIG. 30A  shows a top-view of electrical adjuster  160 . 
       FIG. 30B  shows a front-view of electrical adjuster  160 . 
       FIG. 31  shows a top-view of CVT  1 . 2 . 
       FIG. 32  shows a top-view of CVT  2 . 2 . 
       FIG. 33  shows a top-view of CVT  2 . 3 . 
       FIG. 34  shows a top-view of CVT  2 . 4 . 
       FIG. 35  shows a top-view of CVT  2 . 5 . 
       FIG. 36  show a top-view of differential adjuster shaft  1 . 
       FIG. 37  show a top-view of differential adjuster shaft  2 . 
       FIG. 38  show a top-view of differential adjuster shaft  3 . 
       FIG. 39  show a partial phantom-view of the differential of differential adjuster shaft  3 . 
       FIG. 40  show a top-view of differential adjuster shaft  4 . 
       FIG. 41  show a partial phantom-view of the differential of differential adjuster shaft  4 . 
       FIG. 42  shows a partial side-view of differential D  212 D, which utilizes the index wheel mechanism. 
       FIG. 43A  shows partial top-view of the index wheel mechanism in its locking position. 
       FIG. 43B  shows partial top-view of the index wheel mechanism in its stepwise releasing mode. 
       FIG. 43C  shows partial top-view of the index wheel mechanism in its completely releasing mode. 
       FIG. 43D  shows partial top-view of an alternate index wheel  221 B. 
       FIG. 44  shows a top-view of a configuration for a CVT that uses a differential adjuster shaft  5 . 
       FIGS. 45 and 46  show partial front views of a CVT utilizing differential adjuster shaft  5   
       FIG. 47  shows a top-view of a configuration where a differential adjuster shaft is connected to a mover frame. 
       FIG. 48  shows a top-view of a configuration of a differential adjuster shaft where its differential shafts are replaced by splines. On those splines, spline sleeves on which the transmission pulleys are keyed-on are slideably mounted. 
       FIG. 49A  shows a top-view of spring-loaded adjuster AS 1   171 . 
       FIG. 49B  shows a partial front-view of spring-loaded adjuster AS 1   171 . 
       FIG. 49C  shows a partial side-view of spring-loaded adjuster AS 1   171 , showing the hidden inner profile of the adjuster. 
       FIG. 49D  shows a sectional top-view of spring-loaded adjuster AS 1   171 . 
       FIG. 50A  shows a front-view of spring-loaded adjuster AS 2   172 . 
       FIG. 50B  shows a top-view of spring-loaded adjuster AS 2   172 . 
       FIG. 51A  shows a front-view of mechanical adjuster AM 1   181 . 
       FIG. 51B  shows a top-view of mechanical adjuster AM 1   181 . 
       FIG. 52  shows a top-view of CVT  2 . 6 . 
       FIG. 53  shows a top-view of CVT  2 . 7 . 
       FIG. 54  shows a top-view of CVT  1 . 3 . 
       FIGS. 55A and 55B  show sectional front-views of a CVT  2  showing the guiding wheels  200 . 
       FIG. 56  shows a partial sectional view of a torque transmitting member mated with a transmission belt, where between their teeth, gaps exist. 
       FIG. 57  shows a load cell wheel that is used to measure the tension of a transmission belt via a load cell. 
       FIG. 58  shows a the mounting of a cone assembly in the sliding cone mounting configuration. 
       FIG. 59  shows a side-view of the transmission belt tensioning mechanism used in the sliding cone mounting configuration. 
       FIG. 60  shows a front-view of a tensioning slider A used in the transmission belt tensioning mechanism shown in  FIG. 59 . 
       FIG. 61A  shows as a front-view of a chain link for a chain, which can be used in a CVT, for which the depth of its left side plate is deeper than that of its right side plate. 
       FIG. 61B  shows as a front-view of a chain link for a chain, which can be used for a CVT, for which rubber legs are attached to the chain link plates. 
       FIG. 62A  shows a side-view of a link A as seen from the right side of the link which is used to form a torque transmitting member chain, which is a torque transmitting member formed by chain links. 
       FIG. 62B  shows a front-view of a link A, which is used to form a torque transmitting member chain. 
       FIG. 63A  shows a side-view of a torque transmitting member chain, as seen from the right side of the chain, formed by alternating links A  270  and links B  272 . 
       FIG. 63B  shows a front-view of a torque transmitting member chain formed by alternating links A  270  and links B  272 . 
       FIG. 64A  shows a side-view of an end link configuration for a link A as seen from the right side of the link. 
       FIG. 64B  shows a front-view of an end link configuration for a link A. 
       FIG. 65A  shows a side-view of a single tooth link. 
       FIG. 65B  shows a front-view of a single tooth link. 
       FIG. 66  shows a reshaped left link plate of a link that can be used to form a torque transmitting member chain. 
       FIG. 67A  shows how to adjust the location of the reinforcements in a torque transmitting member in order to increases or decrease the height of its neutral-axis. 
       FIG. 67B  shows how to adjust the dimensions of a torque transmitting member in order to increases or decrease the height of its neutral-axis. 
       FIG. 68  shows a front-view of the chain torque transmitting member. 
       FIG. 69  shows a torque transmitting member that is formed by a left torque transmitting side member and by a right torque transmitting side member. 
       FIG. 70A  shows a partial top-view of a torque transmitting side member. 
       FIG. 70B  shows a partial side-view of a torque transmitting side member. 
       FIG. 70C  shows an end-view of a torque transmitting side member. 
       FIG. 71  show as a top-view of a single tooth cone. 
       FIG. 72  show as a top-view of a single tooth cone that has a supporting surface. 
       FIG. 73A  shows a side-view of an inverted belt that can be used with a single tooth cone. 
       FIG. 73B  shows as sectional-view of an inverted belt that can be used with a single tooth cone. 
       FIG. 74A  shows a top-view of an specialized inverted belt that can be used with a single tooth cone that has a supporting surface. 
       FIG. 74B  shows a side-view of an specialized inverted belt that can be used with a single tooth cone that has a supporting surface. 
       FIG. 75 , shows a side-view of a chain link of an inverted chain that can be used with a single tooth cone. 
       FIG. 76 , shows a sectional-view of a single tooth cone CVT  2  cut near the smaller end of one of its cones which utilizes a supporting wheel. 
       FIG. 77  shows a top-view reinforced transmission belt  300 . 
       FIG. 78A  shows a side-view of a pin belt 
       FIG. 78B  shows an end-view of a pin belt end-view 
       FIG. 79  shows a front-view of a cone  440  and its larger end cover  45  for which the front half surfaces have been removed. 
       FIG. 80  shows a partial sectional right-end-view of a cone  440 . 
       FIG. 81  shows an right-end-view of a cone  440 . 
       FIG. 82  shows a left-end-view of cover  445 . 
       FIG. 83  shows an end-view of a spline collar  470  mounted on a machined down portion of spline  430 . 
       FIG. 84  shows a front-view of a back sliding tooth cone assembly  420 B. 
       FIG. 85A  shows a front-view of a spline shaft extension  432 . 
       FIG. 85B  shows a top-view of a spline shaft extension  432 . 
       FIG. 86  shows a side-view of an assembled CVT  2  input/output shaft utilizing a front sliding tooth cone assembly  420 A and a back sliding tooth cone assembly  420 B. 
       FIG. 87  shows another side-view of an assembled CVT  2  input/output shaft utilizing a front sliding tooth cone assembly  420 A and a back sliding tooth cone assembly  420 B. 
       FIG. 88  shows top-view of an assembled CVT  2  input/output shaft utilizing a front sliding tooth cone assembly  420 A and a back sliding tooth cone assembly  420 B. 
       FIG. 89  shows a front-view of a CVT utilizing a CVT  2  input/output shaft. 
       FIG. 90  shows a partial top-view of a CVT utilizing a CVT  2  input/output shaft. 
       FIG. 91A  shows a front-view of a front pin belt cone assembly  520 A where portions of its front surface has been cut and removed. 
       FIG. 91B  shows an end-view of a front pin belt cone assembly  520 A where the pin belt torque transmitting member  590  and pin belt non-torque transmitting member  690  are positioned near the smaller end of the cone. 
       FIG. 92A  shows a front-view of a front pin belt cone assembly  520 A where its entire front surface has been cut and removed. 
       FIG. 92B  shows an end-view of a front pin belt cone assembly  520 A where the pin belt torque transmitting member  590  and pin belt non-torque transmitting member  690  are positioned near the larger end of the cone. 
       FIG. 93  shows a partial sectional-view of front pin belt cone assembly  520 A where some items are not shown. 
       FIG. 94  shows another partial sectional-view of front pin belt cone assembly  520 A. 
       FIG. 95  shows a top-view of pin belt torque transmitting member  590 . 
       FIG. 96  shows a sectional-view of pin belt torque transmitting member  590 . 
       FIG. 97  shows another sectional-view of pin belt torque transmitting member  590 . 
       FIG. 98  shows another sectional-view of pin belt torque transmitting member  590 . 
       FIG. 99  shows an end-view of a trailing plate  593 . 
       FIG. 100  shows an end-view of a trailing plate  593  that is secured to pin belt cone  540  using a ball clamp  620 . 
       FIG. 101  shows an end-view of a trailing plate  593  that is secured to pin belt cone  540  using a dome shaped nut  621 . 
       FIG. 102A  shows a side-view of a pin transmission belt  630 . 
       FIG. 102B  shows an end-view of a pin transmission belt  630 . 
       FIG. 103  shows a top-view of pin belt non-torque transmitting member  690 . 
       FIG. 104  shows a sectional-view of pin belt non-torque transmitting member  690 . 
       FIG. 105  shows another sectional-view of pin belt non-torque transmitting member  690 . 
       FIG. 106  shows an end view of non-torque trailing plate  693 . 
       FIG. 107  shows as a top-view of alternate friction torque transmitting member  1590 . 
       FIG. 108  shows a sectional-view of alternate friction torque transmitting member  1590   
       FIG. 109  shows a front-view of friction trailing plate  1593 . 
       FIG. 110  shows a cross-sectional-view of alternate friction torque transmitting member  1590  that is engaged with its V-belt, which is labeled as V-belt  1600 . 
       FIG. 111  shows a cross-sectional-view of alternate friction non-torque transmitting member  1690  that is engaged with its V-belt, which is labeled as V-belt  1600   
       FIG. 112A  shows a front-view of pin belt cone  540 . 
       FIG. 112B  shows an end-view of pin belt cone  540 . 
       FIG. 113  shows a front-view of back pin belt cone  540 B. 
       FIG. 114  shows a left-end-view of back pin belt cone larger end cover  545 B 
       FIG. 115  shows a top-view for the mounting of a single cone assembly on a shaft/spline. 
       FIG. 116A  shows a front-view of twin sprocket pulley  700 . 
       FIG. 116B  shows a sectional-view of twin sprocket pulley  700 . 
       FIG. 117A  shows a front-view of two sprockets  702  mounted in parallel. 
       FIG. 117B  shows a sectional-view of two sprockets  702  mounted in parallel. 
       FIG. 118  shows partial back-view of CVT constructed from a front sliding tooth cone assembly  420 A and a back sliding tooth cone assembly  420 B where the tooth carriages  450  are positioned near the smaller end of the cone. 
       FIG. 119A  shows a front-view of a spring-loaded slider pulley assembly  720 . 
       FIG. 119B  shows an end-view of a spring-loaded slider pulley assembly  720 . 
       FIG. 120  shows an end-view of a front pin belt cone assembly  520 A where the torque transmitting orientation is counter-clockwise. 
       FIG. 121  shows a partial back-view of CVT constructed from a pin belt cone assembly  520 A and a back pin belt cone assembly  520 B where pin belt torque transmitting member  590  and pin belt non-torque transmitting member  690  are positioned near the larger end of the cone. 
       FIG. 122  shows partial back-view of CVT constructed from a pin belt cone assembly  520 A and a back pin belt cone assembly  520 B where the pin belt torque transmitting member  590  and pin belt non-torque transmitting member  690  are positioned near the smaller end of the cone. 
       FIG. 123  shows a partial end-view of a pin belt spring-loaded slider pulley  720 -M 4 A. 
       FIGS. 124 ,  125 , and  126  show sectional-views of alternate pin transmission belts. 
       FIGS. 127 ,  128 , and  129  show sectional-views of alternate pin transmission belts with their spring-loaded slider pulleys. 
       FIG. 130A  shows a side-view of a alignment wheels pulley assembly  730 . 
       FIG. 130B  shows an end-view of a alignment wheels pulley assembly  730 . 
       FIG. 131A  shows a side-view of an alignment wheels pulley shaft  731 . 
       FIG. 131B  shows an end-view of an alignment wheels pulley shaft  731 . 
       FIG. 132  shows a front-view of front pin belt cone assembly  520 A utilizing a gaps method pin belt torque transmitting member  590 A. 
       FIG. 133  shows a top-view of a gaps method pin belt torque transmitting member  590 A. 
       FIG. 134  shows a front-view of a pin belt tooth B  591 -S 2 B. 
       FIG. 135  shows a front-view of a pin belt tooth C  591 -S 2 C. 
       FIG. 136A  shows a front-view of single tooth cone link A  800 A. 
       FIG. 136B  shows a side-view of single tooth cone link A  800 A. 
       FIG. 136C  shows a sectional-view of single tooth cone link A  800 A. 
       FIG. 136D  shows a partial back-view of single tooth cone link A  800 A. 
       FIG. 137A  shows a front-view of a partial chain section that is constructed from a single tooth cone link B  800 B which right end is sandwiched by single tooth cone link C  800 C and a single tooth cone link A  800 A. 
       FIG. 137B  shows an end-view of a partial chain section that is constructed from a single tooth cone link B  800 B which right end is sandwiched by single tooth cone link C  800 C and a single tooth cone link A  800 A. 
       FIG. 137C  shows a front-view of alternate single tooth cone link A  810 A. 
       FIG. 138A  shows a front-view of chain single tooth cone  820 . 
       FIG. 138B  shows an end-view of chain single tooth cone  820 . 
       FIG. 139A  shows a front-view of chain transmission pulley  850 . 
       FIG. 139B  shows an end-view of chain transmission pulley  850 . 
       FIG. 140A  shows a front-view of a blocks transmission belt  842 . 
       FIG. 140B  shows an end-view of a blocks transmission belt  842 . 
       FIG. 141A  shows a front-view of a blocks belt single tooth cone  860 . 
       FIG. 141B  shows an end-view of a blocks belt single tooth cone  860 . 
       FIG. 142A  shows a front-view of an opposite teeth cone  861 . 
       FIG. 142B  shows an end-view of an opposite teeth cone  861 . 
       FIG. 143A  shows a front-view of a transmission pulley that can be used with blocks transmission belt  842 . 
       FIG. 143B  shows an end-view of a transmission pulley that can be used with blocks transmission belt  842 . 
       FIG. 144  shows a partial end-view of a pin belt spring-loaded slider pulleys  721 B used with a chain that is partially shown in  FIGS. 137A and 137B . 
       FIG. 145A  shows a front-view of a modified blocks transmission belt. 
       FIG. 145B  shows an end-view of a modified blocks transmission belt. 
       FIG. 146A  shows a front-view of a guides for moving cones  900 . 
       FIG. 146B  shows an end-view of a guides for moving cones  900 . 
       FIG. 147  shows an end-view of a guides for stationary cones  920 . 
       FIG. 148  shows a partial front-view were 3 moving cones guiding plates  904  are used to maintain the axial position of a guides transmission belt  930 . 
   

   REFERENCE NUMERALS IN DRAWINGS 
   For the reference numerals in this patent, the label M(number) after a reference numeral, where (number) is a number, such as M 2  for example, is used to label different members of a part that is given one reference numeral but consist of more than one member. And the label S(number) after a reference numeral, where (number) is a number, such as S 2  for example, is used to label the different shapes of a part that is given one reference numeral. Furthermore, same parts that are used in different location might have a different labeling letter after their reference numeral, or a different reference numeral altogether if this is helpful in describing the invention. If two parts have the same reference numeral then they are identical unless otherwise described. 
   DESCRIPTION OF INVENTION 
   First the basic idea of the invention will be presented in the General Cone Assembly section. Then some alternate configuration of the invention, labeled as cone assembly A  1026 A, cone assembly B  1026 B, and cone assembly C  1026 C will be presented. Next, a mover mechanism will be described. Finally, several preferred configurations for a Continuous Variable Transmission (CVT) utilizing the invention will be described. 
   Also in case no specific method of fixing one part to another is described, then the method of gluing one part to another can be used. Although more sophisticated methods might be preferable, having to explain these methods would complicate the description of the invention without helping in describing the essence of the invention. Also in case no specific method for keying a part is provided than set-screws that screw completely or partially through the part to be keyed and the shaft on which it is keyed on can be used. 
   General Cone Assembly (Cone Assembly  1026 )— FIGS. 1A ,  1 B,  1 C,  1 D,  2 A, &amp;  2 B) 
   The corner stone of the invention is shown in  FIGS. 1A ,  1 B,  1 C, and  1 D. It consists of a cone  1024  that is keyed to a shaft  1016  using an attachment sleeve  1036 , located at the smaller end of the cone. At the larger end of the cone, an end cover  1037  that has a support sleeve  1038  through which shaft  1016  is slid through is mounted. On cone  1024  one torque transmitting member  1046  is attached so that a torque transmitting arc, which partially wraps around the surface of cone  1024  at an axial section of cone  1024 , is formed. Having the torque transmitting arc formed by a group of torque transmitting members would also work. The torque transmitting arc formed by the torque transmitting member  1046  only covers a circumferential portion of cone  1024 , so that the circumferential portion adjacent to the torque transmitting arc is not covered by the torque transmitting arc. A circumferential portion adjacent to a torque transmitting arc, which is not covered by a torque transmitting arc, is referred to as a non-torque transmitting arc and labeled as non-torque transmitting arc  1028 . The torque transmitting arc is formed by the torque transmitting surfaces of torque transmitting member  1046 , and will be used for torque transmission between cone  1024  and a rotational energy conveying device, such as belt, chain, gear, pulley, or wheel for example. 
   A torque transmitting member  1046  is channel shaped, with two sides and a base. Here the bottom surface of the base of the torque transmitting member  1046  rests on the surface of cone  1024 , and a leveling loop  1066  rests on the top surface of the base of torque transmitting member  1046 . The leveling loop  1066  is used to provide a level-resting place for a rotational energy conveying device. The inner side surfaces of torque transmitting member  1046  have at least one tooth, which will be used for torque transmission between a rotational energy conveying device and cone  1024 . In this application, the torque transmitting members  1046  have a plurality of teeth, which are labeled as teeth  1047 . For smooth operation teeth  1047  should have an involute tooth shape. It is also possible to have torque transmitting members  1046  which side surfaces are not toothed, since friction between the side surfaces of torque transmitting member  1046  and the torque transmitting surface(s) of a rotational energy conveying device can also be used to transmit torque,  FIGS. 2A and 2B  show a cone  1024  on which a friction torque transmitting member  1046 F, which uses friction to transmit torque, is attached. Torque transmitting member  1046  is preferably made out of steel reinforced rubber. In order prolong the live of torque transmitting member  1046 , and reduce the required force to move torque transmitting member  1046  to a different axial position relative to the surface of cone  1024 , the bottom surface of the base of torque transmitting member  1046  is PTFE coated. Furthermore, an attachment plate  1048  is attached to both ends of torque transmitting member  1046 . The heads of the attachment plates  1048  are preferably molded into the base of torque transmitting member  1046 . The length of torque transmitting member  1046  can be varied according to the need of the CVT where it is utilized. 
   In order to attach the torque transmitting member  1046  to cone  1024 , cone  1024  has two slots  1027 . Here each attachment plate  1048  of torque transmitting member  1046  is placed in a slot  1027 , and secured to cone  1024  using an attachment wheel  1049 . The attachment wheels  1049  are aligned so that they roll with minimum amount of drag when torque transmitting member  1046  is moved from one axial position of cone  1024  to another. It is recommended that an attachment wheel  1049  has some flexibility as to allow some slight play as to account for the change in curvature of the inner surface of cone  1024  where an attachment wheel  1049  is positioned, as the torque transmitting member  1046  is moved from one axial position of cone  1024  to another. It is also recommended that an attachment wheel  1049  has a low friction outer surface so as to minimize frictional losses in instances where an attachment wheel  1049  has to be dragged relative to the inner surface of cone  1024 . Furthermore, the attachment plates  1048  can also be used to attach a mover mechanism, which is used to move the torque transmitting member  1046  to a new axial position. 
   The torque transmitting member  1046  is attached on cone  1024  so that it can only slide in the axial direction of cone  1024 , which is the direction along the length of shaft  1016 . Sliding the torque transmitting member  1046  in the axial direction changes the pitch diameter of the torque transmitting arc, which depends on the diameter of the surface of cone  1024  where torque transmitting member  1046  is positioned. The arc length, and hence the pitch, of the torque transmitting arc remains constant regardless of its pitch diameter. The arc length of the non-torque transmitting arc increases as torque transmitting member  1046  is being slid from the smaller end of cone  1024  to the larger end of cone  1024 . 
   Furthermore, in order to prevent a rotational energy conveying device, such as a transmission belt, to deform as it comes in and out of contact with torque transmitting member  1046 , the surface of cone  1024  that will not be covered by torque transmitting member  1046 , should be made flush with the top surface of the base of torque transmitting member  1046 . Another method would be to eliminate the base of torque transmitting member  1046 . This can be achieved by constructing torque transmitting member  1046  out of two side members that sit directly on the surface of cone  1024 , which will be joined beneath the surface of cone  1024 . Also, in order to reduce vibrations due to the centrifugal force of torque transmitting member  1046 , cone assembly  1026  should be properly balanced 
   The cones can be made out of die-cast stainless steel. And in order to obtain better dimensional tolerances and a smoother surface finish, it is recommended that the cones obtained from the die-cast process be machined. 
   The surface of cone  1024  should be PTFE coated. This will reduce the friction between torque transmitting member  1046  and the surface of cone  1024 , which will extend the live of torque transmitting member  1046  and reduce the force required to move torque transmitting member  1046  to a new axial position. PTFE coating the surface of cone  1024  also reduces friction between the surface of cone  1024  and the rotational energy conveying device, so that wear due to sliding between the surface of cone  1024  and the rotational energy conveying device due to change in pitch diameter is minimized. 
   Hence a cone assembly  1026 , which mainly consists of a cone  1024  and its torque transmitting member(s)  46 , has been introduced. 
   Cone Assembly A  1026 A— FIGS. 3A ,  3 B,  3 C, &amp;  3 D 
   Cone assembly A  1026 A is a cone assembly  1026  with the restriction described in this section. Cone assembly A  1026 A has two torque transmitting arcs, each consisting of the torque transmitting surfaces formed by a torque transmitting member  1046  or a group of torque transmitting members  1046 . The torque transmitting arcs are positioned opposite from each other on the surface of a cone A  1024 A. Furthermore, at the smallest end of cone A  1024 A, each torque transmitting arc provides coverage to less than half of the circumference of cone A  1024 A. As described before, the circumferential portions adjacent to the torque transmitting arcs, which are not covered by the torque transmitting arcs, will be referred to as non-torque transmitting arcs. 
   Cone Assembly B  1026 B— FIGS. 4A ,  4 B,  4 C, &amp;  4 D 
   The only difference between cone assembly A  1026 A and cone assembly B  1026 B is that for cone assembly B  1026 B, one torque transmitting arc is replaced with a maintaining arc, formed by one or a group of maintaining member(s)  46 N, hence it also uses a cone A  1024 A. A maintaining member  1046 N is identical to a torque transmitting member  1046  except that it is not used for torque transmission between a rotational energy conveying device and a cone. The primary function of the maintaining member(s)  46 N is to maintain the axial position of a rotational energy conveying device, such as a transmission belt, when it is not in contact with a torque transmitting member  1046 . Hence the inner side surfaces of maintaining member(s)  46 N should not be toothed, and friction between the rotational energy conveying device and maintaining member(s)  46 N should be minimized by selecting a proper surface finish and shape for maintaining member(s)  46 N. 
   Furthermore, the arc length of the torque transmitting arc is limited such that the torque transmitting surface(s) of the rotational energy conveying device(s) of the CVT where cone assemblies B  1026 B are used, will never cover the entire non-torque transmitting arc of a cone assembly B  1026 B. However, the arc length of the torque transmitting arc is long enough so that for the CVT where cone assemblies B  1026 B are used, at least a torque transmitting arc of at least one cone assembly B  1026 B is always engaged with its rotational energy conveying device. 
   Cone Assembly C  1026 C— FIGS. 5A ,  5 B,  5 C, &amp;  5 D 
   Cone assembly C  1026 C, is a cone assembly  1026  with the restriction described in this section. As in cone assembly B  1026 B, the arc length of the torque transmitting arc, formed by the torque transmitting surfaces of torque transmitting member(s)  1046 , is limited such that the torque transmitting surface(s) of the rotational energy conveying device(s) of the CVT where cone assemblies C  1026 C are used, will never cover the entire non-torque transmitting arc of a cone assembly C  1026 C. However, the arc length of the torque transmitting arc is long enough so that for the CVT where cone assemblies C  1026 C are used, at least a torque transmitting arc of at least one cone assembly C  1026 C is always engaged with its rotational energy conveying device. Like before, in order to reduce vibration due to the centrifugal force of the torque transmitting member(s)  1046 , cone assembly C  1026 C should be properly balanced. 
   In the description for cone assembly A  1026 A, cone assembly B  1026 B, and cone assembly C  1026 C, the drawings for these cone assemblies show torque transmitting members  1046  that are toothed. Instead of torque transmitting members  1046  that are toothed, friction torque transmitting members  1046 F, which use friction to transmit torque, can also be used for these cone assemblies or any other cone assembly  1026 . For example, shown in  FIGS. 6A to 6D  is cone assembly AF  1026 AF, which is identical to cone assembly A  1026 A except that it uses friction torque transmitting members  1046 F instead of torque transmitting members  1046 . 
   Mover Mechanism— FIGS. 4A ,  4 B,  4 C,  4 D,  7 A, &amp;  7 B 
   The torque transmitting members  1046  and the maintaining members  1046 N will be moved relative to the surface of the cone on which they are attached using a mover mechanism. The maintaining members  1046 N are attached to the mover mechanism in the same manner as the torque transmitting members  1046 , and hence moved in the same manner. For clarity purposes, the maintaining members  1046 N will not be referred to in this section. 
   The mover mechanism consists of a slider bushing  1055 , which is attached to a shaft in a manner such that it tightly fits onto the shaft but is free to slide along the length of the shaft and in and out of the cone on which it is used through the support sleeve  1038  of the end cover  1037  of that cone. A rotor  1056  is fitted onto slider bushing  1055 . Locking collars will be used to fix the axial position of rotor  1056  relative to slider bushing  1055 , however rotor  1056  is free to rotate on slider bushing  1055 . In order to attach telescopes  1057  to rotor  1056 , pin-holed plates are attached to the outer surface of rotor  1056 . The telescopes  1057  will be used to connect the torque transmitting member(s)  46  to rotor  1056 , so that the axial position of the torque transmitting member(s)  46  depend on the axial position of rotor  1056 . The length of telescopes  1057  can vary so that they can connect the torque transmitting member(s)  46  to rotor  1056  when the torque transmitting member(s)  46  are positioned at the smallest end and at the largest end of the cone on which they are attached. In instances were only one torque transmitting member  1046  is attached to rotor  1056 , it is recommended that rotor  1056  is shaped as to reduce the centrifugal force due to that torque transmitting member  1046 . The bottom end of each telescope  1057  has two parallel pin-holed plates, which will be used to join the bottom end of a telescope  1057  to a pin-holed plate on rotor  1056  using a locking pin, on which the pin-holed plates of the attached telescope  1057  are able to rotate. The top end of each telescope  1057  has an attachment plate, which is joined to an attachment plate  1048  of a torque transmitting member  1046  using a telescope connector. Here, in order to allow the attachment plates of a telescope  1057  to rotate relative to attachment plates  1048 , locking pins are used. 
   Below is a detailed description of attachment plate  1048 , which is shown in its assembled state as a front-view in  FIG. 7A  and as a top-view in  FIG. 7B . The top end of attachment plate  1048  consists of a disk shape, which will be molded into a torque transmitting member or non-torque transmitting member. For assembly purposes it is recommended that the disk shape is molded into its torque transmitting member or its non-torque transmitting member such that it can rotate relative to its torque transmitting member or its non-torque transmitting member, otherwise, its torque transmitting member or its non-torque transmitting member has to be twisted during assembly. The slots of the cone into which the attachment plate  1048  will be inserted should have sufficient play to allow proper assembly. Below the disk shape, a pin shape exists. In the assembled state, this pin shape is positioned between the side surfaces of a slot of its cone. Below the pin shape, a plate with a hole exist. The hole of this plate is aligned as to allow an attachment wheel  1049  mounted on it to roll when its torque transmitting member is moved from one axial position on its cone to another. Since there might be instances where attachment wheel  1049  will not roll smoothly, it should have a low friction surface so that it can be dragged. Also in the assembled state, sufficient play between attachment wheel  1049  and the surface of its cone should exist to account for the change of curvature of its cone. 
   The top attachment plate of a telescope  1057 , which is labeled as telescope attachment plate  1058 , will be connected to attachment plate  1048  using a telescope connector  1059 . Telescope attachment plate  1058  is shaped on the top end of a telescope  1057  and is shaped like a plate with a hole, which has a rounded top side. Telescope connector  1059  has a L-shape, where the horizontal and vertical members are formed by plates. At the bottom surface of the horizontal member of telescope connector  1059  a clevis exist. This clevis will be used to join telescope attachment plate  1058  to telescope connector  1059  using a pin and locking rings. At the vertical member of telescope connector  1059 , a hole that has the same alignment as the hole of the plate with a hole of attachment plate  1048  exists. In the assembled state, the hole of the plate with a hole of attachment plate  1048  is aligned with the hole of the vertical member of telescope connector  1059 , and a bolt, on which attachment wheel  1049  is mounted and which is secured with a nut, goes through those holes. Also, in the assembled state the bottom surface of the plate with a hole of attachment plate  1048  is engaged with top surface of the horizontal member of telescope connector  1059  so as to prevent the plate with a hole of attachment plate  1048  to pivot about the axis of its hole. 
   All parts discussed above are preferably made out of stainless steel, except the slider bushing  1055 , which is preferably made out of oil-impregnated bronze. The mover mechanism described above can be used to change the axial position of the torque transmitting member(s)  46  and the maintaining member(s)  46 N, if any, relative to the surface of cone  1024 , or cone A  1024 A to which they are attached, by changing the axial position of slider bushing  1055  relative to their cone  1024 , or cone A 1024 A. 
   Continuous Variable Transmission Variation  1  (CVT  1 )— FIGS. 8A &amp; 8B   
   CVT  1  consists of a pair of cone assemblies A  1026 A, each equipped with a mover mechanism described previously. Here one cone assembly A  1026 A will be keyed to a driver shaft  1012  and the other cone assembly A  1026 A will be keyed to a driven shaft  1014 . Torque between the cone assemblies A  1026 A is transmitted by a toothed transmission belt  1067 , which couples the torque transmitting members  1046  of cone assembly A  1026 A on the driver shaft  1012  with the torque transmitting members  1046  of cone assembly A  1026 A on the driven shaft  1014 . The configuration of CVT  1  and the arc length of the torque transmitting arcs of cone assemblies A  1026 A should be designed such that for each cone assembly A  1026 A, at least one torque transmitting arc is always engaged with transmission belt  1067 . As described earlier, the arc lengths of the non-torque transmitting arcs increase as the torque transmitting members  1046  are slid from the smaller end of their cone A  1024 A to the larger end of their cone A  1024 A and vice-versa. Since there are instances were the arc lengths of the non-torque transmitting arcs do not correspond to a multiple of the width of teeth  1047  some stretching of transmission belt  1067  to account for this is to be expected. The transmission ratio depends on the axial position of the torque transmitting members  1046  on the surfaces of cones  1024 A. The torque transmitting members  1046  of the cone assemblies A  1026 A should always be properly aligned. In order to achieve this, the slider bushing  1055  on the driver shaft  1012  and the slider bushing  1055  on the driven shaft  1014  are connected by a connector  1075 , in a manner such that they can rotate relative to connector  1075 . In order to change the transmission ratio the pitch diameters of the torque transmitting arcs, formed by the torque transmitting surfaces of torque transmitting members  1046 , of the cone assemblies A  1026 A have to be changed. This is achieved by changing the axial position of transmission belt  1067  and the torque transmitting members  1046  relative to the surfaces of cones  1024 A using an actuator, which is attached to connector  1075 . 
   When for both cone assemblies A  1026 A, transmission belt  1067  is not in contact with a complete non-torque transmitting arc then the transmission ratio can be changed without causing significant circumferential sliding between the torque transmitting surfaces of the torque transmitting members  1046  and the transmission belt  1067 . This is because only the arc length of the non-torque transmitting arc changes as the transmission ratio is changed. The configuration where the transmission ratio can be changed without any significant circumferential sliding between the torque transmitting surfaces of the torque transmitting members  1046  and transmission belt  1067  is referred to as a moveable configuration. And the configuration where changing the transmission ratio will tend to cause significant circumferential sliding between the torque transmitting surfaces of the torque transmitting members  1046  and transmission belt  1067  is referred to as an unmovable configuration. Here changing the transmission ratio when transmission belt  1067  is in an unmovable configuration should simply cause the actuator to stall. 
   One method to eliminate or reduce stalling of the actuator is to equip the actuator with a spring-loaded piston. Here when the transmission belt  1067  is in a moveable configuration, than the torque transmitting members  1046  will move with the actuator. However, when the transmission belt  1067  is not in a moveable configuration then moving the actuator will not move the torque transmitting members  1046  but will stretch or compress the spring of the spring-loaded piston of the actuator. And once both cone assemblies A  1026 A have rotated so that transmission belt  1067  is in a moveable configuration, the tension or compression in the spring-loaded piston will move transmission belt  1067  and the torque transmitting members  1046  in the direction the actuator was moved until the tension or compression of the spring-loaded piston is relieved. 
   When transmission belt  1067  is in the axial position where the transmission ratio is unity, where the cone assembly A  1026 A on the driver shaft  1012  rotates at the same speed as the cone assembly A  1026 A on the driven shaft  1014 , then transmission belt  1067  can get stuck in an unmovable configuration. One method to avoid this problem is to make the smaller end of one cone assembly A  1026 A slightly larger than the larger end of the other cone assembly A  1026 A. Under this configuration the cone assemblies A  1026 A will never rotate at the same speed, so that the rotational position of one cone assembly A  1026 A relative to the other cone assembly A  1026 A continuously changes as the cone assemblies A  1026 A are rotating. Hence eventually the cone assemblies A  1026 A will rotate to a movable configuration. 
   Another method to avoid having transmission belt  1067  stuck in an unmovable configuration is to have a mover control system control the movement of the actuator. Here, every time the actuator is about to move transmission belt  1067  to the position where the transmission ratio between the cone assemblies A  1026 A is unity, the mover control system will stop the actuator. Then the mover control system will wait until the cone assemblies A  1026 A have rotated to a rotational position such that once the actuator moves transmission belt  1067  to the axial position where the transmission ratio between the cone assemblies A  1026 A is unity, during the rotation of the cone assemblies A  1026 A an instance were transmission belt  1067  is in a movable configuration exists. In order for the mover control system to work, it needs to know the rotational position of each cone assembly A  1026 A, the rotational speed of each cone assembly A  1026 A, the axial position of transmission belt  1067 , and the speed of the actuator. 
   In order for the mover control system to determine the rotational position and rotational speed of the cone assemblies A  1026 A, a marked wheel  1085  is keyed to the driver shaft  1012  and to the driven shaft  1014 , and each marked wheel  1085  has a marked wheel decoder  1086 , which is attached to the frame of the CVT. In order to accurately determine the axial position of transmission belt  1067 , a gear rack  1076  is attached to the actuator, and a gear  1077 , which engages the gear rack  1076 , is attached to the frame of the CVT. A marked wheel  1085  is attached to the gear, and a marked wheel decoder  1086  decodes the information from this marked wheel  1085  to determine the axial position of transmission belt  1067 . 
   The information from the wheel decoders  86  mentioned previously, will be transmitted to a computer. The computer will then process the information to properly move the actuator, such that when the transmission belt  1067  is moved to the axial position where the transmission ratio is unity, an instance where the CVT is in a moveable configuration exists. 
   The mover control system can also be designed so that it only moves transmission belt  1067  when it is in a moveable configuration, as to prevent the actuator from stalling when it tries to move transmission belt  1067  when it is in an unmovable configuration. However, despite the use of a mover control system, stalling of the actuator is still possible. Furthermore, when gear  1077  is coupled to a rotary actuator it can be used as the actuator, which controls the axial position of the transmission belt  1067 , see  FIG. 8A . 
   Continuous Variable Transmission Variation  2  (CVT  2 )— FIGS. 9A ,  9 B,  9 C,  9 D, &amp;  9 E 
   CVT  2  consists of either two cone assemblies B  1026 B, which are keyed to a driver shaft  1012  such that the torque transmitting arc of one cone assembly B  1026 B is positioned opposite from the torque transmitting arc of the other cone assembly B  1026 B, or two cones assemblies  1026 C, which are attached in the same manner. Each cone assembly  1026 (B/C) is coupled to a transmission pulley  1098 , attached on driven shaft  1014 , by a transmission belt  1067 . 
   The surfaces of the transmission pulleys  1098  are tapered as to match the taper of the outer surfaces of cone assemblies  1026 (B/C). This allows the transmission belts  1067  for this CVT to be shaped such that they can rest on the surface of their respective cone assembly  26 (B/C) and on the surface of their respective transmission pulley  1098  without being twisted. Hence, there is no need for leveling loop  1066  for CVT  2 . Also, as described earlier, the arc lengths of the non-torque transmitting arcs increase as the torque transmitting members  1046  are slid from the smaller end of their cone to the larger end of their cone and vice-versa. Since there are instances were the arc lengths of the non-torque transmitting arcs do not correspond to a multiple of the width of the teeth  1047  some stretching of the transmission belts  1067  to account for this is to be expected. 
   Like in CVT  1 , the transmission ratio is controlled by controlling the axial position of the torque transmitting members  1046  relative to the surface of their respective cone using the mover mechanism described earlier. In order to ensure that the axial position of the torque transmitting members  1046  relative to their respective cones is identical as to ensure that they rotate at the same speed, the slider bushings  1055  of the cones assemblies  1026 (B/C) are rigidly connected by a slider joiner base  1096  and slider joiner rods  1097  ( FIG. 9E ). The smaller end of the cone  1024 A which smaller end is facing the larger end of the other cone  1024 A has holes through which the slider joiner rods  1097  can slide through. The change in axial position of the torque transmitting members  1046  has to be accompanied by the change in axial position of the transmission pulleys  1098 . In order to achieve this, the transmission pulleys  1098  are keyed to a spline sleeve  1099  ( FIGS. 9A &amp; 9B ), which is free to slide along the length of the driven shaft  14 , which here is shaped like a spline, but is not free to rotate relative to driven shaft  1014 . 
   Furthermore, the slider bushing  1055  of the cone assembly  1026 (B/C) located closes to the actuator, which is used to change the transmission ratio, and the spline sleeve  1099  of the transmission pulleys  1098  are connected by a connector B  1075 B, in a manner such that they can rotate relative to connector B  1075 B, in a configuration such that the torque transmitting members  1046  are always properly aligned with their transmission pulleys  1098 . Also, as described for CVT  1 , here in instance when the transmission ratio is changed when the transmission belts  1067  are in an unmovable configuration, the actuator, used to change the transmission ratio, should simply stall. Here an unmovable configuration is a configuration were both torque transmitting members  1046  are in contact with their transmission belts  1067 . 
   Furthermore, in order to maintain proper tension in the transmission belts  1067  for every transmission ratio of CVT  2 , each transmission belt  1067  is equipped with a tensioning mechanism. The tensioning mechanism consists of two tensioning wheels  1105 , two tensioning sliders  1106 , two tensioning constrainers  1107 , two tensioning movers  1108 , and a tensioning actuator  1109 . The tensioning wheels  1105  will be attached so that they touch the base of the transmission belts  1067 . Each tensioning wheel  1105  is attached to a tensioning slider  1106 . Each tensioning slider  1106  slides on a tensioning constrainer  1107 . The tensioning constrainers  1107  are angled so that the tensioning wheels  1105  will maintain the proper tension in the transmission belts  1067  for every axial position of the transmission belts  1067 . In order to change the axial position of the tensioning sliders  1106 , each tensioning slider  1106  has two vertical sleeves, which will slide on two vertical guides of a tensioning mover  1108  so that the tensioning sliders  1106  can freely slide vertically as the axial positions of tensioning movers  1108  are changed. The tensioning actuator  1109  connects the tensioning mover  1108  closest to connector B  1075 B to connector B  1075 B, and the tensioning mover  1108  closest to connector B  1075 B to the other tensioning mover  1108  in a manner such that each tensioning wheel  1105  is properly aligned with its torque transmitting member  1046  and its transmission pulley  1098  for every transmission ratio. Furthermore, tensioning wheels  1105  have smooth non-toothed side surfaces so that they can be used to maintain the alignment of the transmission belts  1067 . 
   The configuration for CVT  1  and CVT  2 , and other CVT&#39;s using the cones assemblies or cones of this patent, can also be used for cone assemblies that use friction torque transmitting members  1046 F instead of torque transmitting members  1046 . In this case, torque is transmitted through friction; however, in this case there is no stretching of the transmission belts that occur in CVT&#39;s where toothed torque transmitting members  1046  are used due to instances were the arc lengths of the non-torque transmitting arcs do not correspond to a multiple of the width of the teeth of their torque transmitting members. 
   In addition to the CVT&#39;s described earlier another recommended configuration for a CVT is a CVT that is identical to CVT  1  except that one cone assembly is replaced with a transmission pulley. This CVT will be referred to as CVT  3 . Here as in CVT  2 , it needs to be ensured that the transmission pulley is always properly aligned with the torque transmitting members of its cone assembly for all transmission ratios. The basic method to maintain alignment and to maintain tension in the transmission belts used in CVT  2  can also be used here. Under this configuration only one cone assembly A  1026 A or one cone assembly AF  1026 AF is needed, and here the transmission belt used will never get stuck in an unmovable configuration, hence the mover control system of CVT  1  is not needed in this design. A configuration for this CVT, where a cone assembly AF  1026 AF, which uses two friction torque transmitting members  1046 F, is coupled by a friction belt  1067 F to a friction pulley  1098 F is shown as a top-view in  FIG. 10 . For optimum performance, when a friction torque transmitting member  1046 F is engaged with its friction belt  1067 F, the neutral-axis of the friction torque transmitting members  1046 F and the friction belt  1067 F should coincide. 
   Performance Improving Adjuster Systems 
   Furthermore for CVT  1  and CVT  2 , in order to reduce or eliminate stretching of the transmission belts in instances were the arc lengths of the non-torque transmitting arcs do not correspond to a multiple of the width of the teeth of their torque transmitting members, which will be referred to as transition flexing, and in order to increase the duration at which the transmission ratio can be changed by reducing or eliminating stalling of the actuator that is used to change the transmission ratio in instance when the transmission ratio is changed when the transmission belts are in an unmovable configuration, adjuster systems for CVT  1  and CVT  2 , and the CVT&#39;s utilizing them will be described below. If friction torque transmitting members  1046 F instead of torque transmitting members  1046  are used, then the adjuster systems are only needed to increase the duration at which the transmission ratio can be changed. 
   The adjuster systems described in this patent can also be used increase the performance of other CVT&#39;s, besides CVT  1  and CVT  2 , that suffer from either or both transition flexing and a limited duration at which the transmission ratio can be changed by eliminating or reducing transition flexing and/or by increasing the duration at which the transmission ratio can be changed. Most likely, the adjuster systems of this patent, can benefit any machine that utilizes torque transmitting devices that alternately come in and out of contact with a common torque transmitting device, for which instances exist or can exist where rotational adjustment to an alternating torque transmitting device or a common torque transmitting device can improve the engagement of an alternating torque transmitting device with its common torque transmitting device; or for which instances exist where rotational adjustment(s) to alternating torque transmitting device(s) or common torque transmitting device(s) can compensate for the rotation of the torque transmitting device(s) that occur during transmission ratio change which may prevent transmission ratio change; or for which instances exist where rotational adjustment to a torque transmitting device which alternates between being in a moveable configuration, where the transmission ratio can be changed, and being in an un-moveable configuration, where the transmission ratio cannot be changed, can maintain that torque transmitting device in a moveable configuration. 
   Adjuster System for CVT  1  ( FIGS. 11A ,  11 B,  12 A,  12 B,  13  to  19 ,  20 A to  20 D,  21 A to  21 C) 
   Here the CVT  1  to which an adjuster system is added is labeled as CVT  1 . 1 . CVT  1 . 1  is almost identical to CVT  1 , shown again in  FIGS. 11A &amp; 11B , described earlier. CVT  1  mainly consist of a cone assembly CS 1 A  21 A and a cone assembly CS 1 B  21 B, which are identical and each have two opposite positioned torque transmitting members which are rotatably constrained but are allowed to slide axially relative to the surface of their cone assembly. The torque transmitting members of cone assembly CS 1 A  21 A are labeled as torque transmitting member CS 1 A-M 1   21 A-M 1  and torque transmitting member CS 1 A-M 2   21 A-M 2 , while the cone of cone assembly  21 A is labeled as cone CS 1 A-M 3   21 A-M 3 . And the torque transmitting members of cone assembly CS 1 B  21 B are labeled as torque transmitting member CS 1 B-M 1   21 B-M 1  and torque transmitting member CS 1 B-M 2   21 B-M 2 , while the cone of cone assembly  21 B is labeled as cone CS 1 B-M 3   21 B-M 3 . The cone assembly CS 21 A  21 A is keyed to the input shaft SH 1   11 , and the cone assembly CS 1 B  21 B is keyed to the output shaft SH 2   12 . In order to transmit torque from the input shaft SH 1   11  to the output shaft SH 2   12 , the torque transmitting members of cone assembly CS 1 A  21 A are coupled with the torque transmitting members of cone assembly CS 1 B  21 B by transmission belt BL 1 A  31 A. The transmission ratio is changed, by changing the axial position of the torque transmitting members. And in order to change the axial position of the torque transmitting members, each cone assembly has a mover sleeve, which can slide axially relative to its shaft. And each torque transmitting member is connected to a mover sleeve by two telescopes, so that the axial position of the torque transmitting members depend on the axial position of the mover sleeves. 
   The transmission ratio can only be changed when for both cone assemblies only one torque transmitting member is in contact with transmission belt BL 1 A  31 A. Otherwise stalling of the transmission ratio changing actuator occurs. The configuration where the transmission ratio can be changed is referred to as a moveable configuration. Also as described earlier, here transition flexing is not eliminated. 
   CVT  1 . 1 , which is shown in  FIG. 12A  and  FIG. 12B , is slightly different than CVT  1 . For CVT  1 . 1 , like for CVT  1 , a cone assembly with two transmitting members is coupled by a transmission belt, which here is labeled as transmission belt BL 1 B  31 B to another cone assembly with two torque transmitting members. However, for CVT  1 . 1 , in order to eliminate or significantly reduce transition flexing, a transition flexing adjuster AD 1 A  101 A is added to a slightly modified version of cone assembly CS 1 A  21 A, which is labeled as cone assembly CS 2 A  22 A, and a transition flexing adjuster AD 1 B  101 B is added to a slightly modified version of cone assembly CS 1 B, which is labeled as cone assembly CS 2 B  22 B. Also here the input shaft is labeled as input shaft SH 3   13  and the output shaft is labeled as output shaft SH 4   14 . As can be seen from the labeling, here cone assembly CS 2 A  22 A is identical to cone assembly CS 2 B  22 B. Transition flexing adjuster AD 1 A  101 A, which is shown in detail in  FIGS. 13 ,  15 , and  16 , has an adjuster body AD 1 A-M 1   101 A-M 1  and an adjuster output member AD 1 A-M 2   101 A-M 2 . Transition flexing adjuster AD 1 B  101 B is identical to transition flexing adjuster AD 1 A  101 A. The adjuster body AD 1 A-M 1   101 A-M 1  of transition flexing adjuster AD 1 A  101 A is fixed to the end of a mover sleeve CS 2 A-M 6   22 A-M 6 , where the two telescopes CS 2 A-M 4   22 A-M 4  of torque transmitting member CS 2 A-M 1   22 A-M 1  are attached. And the adjuster output member AD 1 A-M 2  of transition flexing adjuster AD 1 A is used to mount the two telescopes CS 2 A-M 5   22 A-M 5  of torque transmitting member CS 2 A-M 2   22 A-M 2 . A constraining mechanism CN 1 A  111 A, which will be described in detail later, is used such that the adjuster output member AD 1 A-M 2   101 A-M 2  of transition flexing adjuster AD 1 A  101 A can be used to adjust the rotational position of torque transmitting member CS 2 A-M 2   22 A-M 2 . And the adjuster body AD 1 B-M 1   101 B-M 1  of transition flexing adjuster AD 1 B  101 B is fixed to the end of the mover sleeve CS 2 B-M 6   22 B-M 6 , where the telescopes CS 2 B-M 4   22 B-M 4  of torque transmitting member CS 2 B-M 1   22 B-M 1  are attached. And the adjuster output member AD 1 B-M 2   101 B-M 2  of transition flexing adjuster AD 1 B  101 B is used to mount the telescopes CS 22 B-M 5   22 B-M 5  of torque transmitting member CS 2 B-M 2   22 B-M 2 . And a constraining mechanism CN 1 B  111 B, is used such that the adjuster output member AD 1 B-M 2   101 B-M 2  of transition flexing adjuster AD 1 B  101 B can be used to adjust the rotational position of torque transmitting member CS 2 B-M 2   22 B-M 2 . Since cone assembly CS 2 B  22 B is identical to cone assembly CS 2 A  22 A, except that is mounted on the output shaft SH 4   14  instead on the input shaft SH 3   13 , the only difference between constraining mechanism CN 1 B  111 B and constraining mechanism CN 1 A  111 A is that is mounted on cone assembly CS 2 B  22 B instead of cone assembly CS 2 A  22 A. 
   And in order to substantially increase the duration at which the transmission ratio can be changed, a mover adjuster AD 2 A  102 A and a mover adjuster AD 2 B  102 B, which are basically identical to the transition flexing adjuster  101 A are used. Mover adjuster AD 2 A  102 A, which is shown in  FIG. 14 , has an adjuster body AD 2 A-M 1   102 A-M 1  and an adjuster output member AD 2 A-M 2   102 A-M 2 . And mover adjuster AD 2 B  102 B, which is identical to mover adjuster AD 2 A  102 A, has an adjuster body AD 2 B-M 1   102 B-M 1  and an adjuster output member AD 2 B-M 2   102 B-M 2 . 
   The adjuster body AD 2 A-M 1   102 A-M 1  of mover adjuster AD 2 A  102 A is keyed to the input shaft SH 3   13 , and cone assembly CS 2 A  22 A is fixed to the adjuster output member AD 2 A-M 2   102 A-M 2  of mover adjuster AD 2 A  102 A, see  FIG. 12 . And the body of mover adjuster AD 2 B  102 B is keyed to the output shaft SH 4   14 , and cone assembly CS 2 B  22 B is fixed to the output member AD 2 B-M 2  of mover adjuster AD 2 B  102 B. 
   In order to properly control the transition flexing adjusters AD 1 A and AD 1 B and the mover adjusters AD 2 A and AD 2 B, a computer CP 1   121 , which controls these adjusters based on the input of a transmission ratio sensor SN 1 A  131 A, a rotational position sensors SN 2 A  132 A, a rotational position sensor SN 2 B  132 B, a relative rotational position sensor SN 3 A  133 A, which shown in detail in  FIG. 16 , and a relative rotational position sensor SN 3 B  133 B, is used. If more practical, the relative rotational position sensors can be replaced with rotational position sensors that monitor the rotational positions of the adjuster output members of the transition flexing adjusters. The transmission ratio sensor SN 1 A  131 A is mounted on a frame so that it can be used to monitor the rotation of the transmission ratio gear rack gear via a sensor strip that is wrapped around the transmission ratio gear rack gear, so that computer CP 1   121  can determine the transmission ratio, and hence the axial position of the torque transmitting members relative to the cones on which they are attached. And from that information computer CP 1   121  can determine the pitch diameters, which depend on the diameter of the surfaces of the cones where the torque transmitting members are positioned. The rotational position sensor SN 2 A  132 A, is mounted on a frame so that it can monitor the rotational position of cone assembly CS 2 A  22 A via a sensor strip wrapped around cone assembly CS 2 A  22 A. The rotational position sensor SN 2 B  132 B, is mounted on a frame so that it can monitor the rotational position of cone assembly CS 2 B  22 B via a sensor strip wrapped around cone assembly CS 2 B  22 B. The relative rotational position sensor SN 3 A  133 A, consist of a sensor inner sleeve SN 3 A-M 1   133 A-M 1  and a sensor outer sleeve SN 3 A-M 2   133 A-M 2 , were the sensor inner sleeve SN 3 A-M 1   133 A-M 1  is located inside the sensor outer sleeve SN 3 A-M 2   133 A-M 2 . The sensor inner sleeve SN 3 A-M 1   133 A-M 1  and the sensor outer sleeve SN 3 A-M 2   133 A-M 2  can rotate relative to each other. The amount of rotation between the sensor inner sleeve SN 3 A-M 1   133 A-M 1  and the sensor outer sleeve SN 3 A-M 2   133 A-M 2  can be monitored by computer CP 1   121 . The sensor inner sleeve SN 3 A-M 1   133 A-M 1  is keyed to the adjuster output member AD 1 A-M 2   101 A-M 2  of transition flexing adjuster AD 1 A  101 A, and the sensor outer sleeve SN 3 A-M 2  is mounted on the adjuster body AD 1 A-M 2  of transition flexing adjuster AD 1 A  101 A. Hence using the relative rotational position sensor SN 3 A, the computer CP 1   121  can determine the rotational position of the adjuster output member AD 1 A-M 2  relative to the rotational position of the adjuster body AD 1 A-M 1 . And hence the rotational position of torque transmitting member CS 2 A-M 2   22 A-M 2  relative to torque transmitting member CS 2 A-M 1   22 A-M 1 . And in order to monitor the rotational position of torque transmitting member CS 2 B-M 2   22 B-M 2  relative torque transmitting member CS 2 B-M 1   22 B-M 1 , a sensor SN 3 B  133 B is mounted on the transition flexing adjuster AD 1 B  101 B in the same manner as sensor SN 3 A  133 A is mounted on transition flexing adjuster AD 1 A  101 A. Hence by using the sensors above computer CP 1   121 , can determine the axial position of the torque transmitting members relative to the cones on which they are attached, and hence the pitch diameter; and the rotational positions of the torque transmitting members. 
   In order to connect the transmission ratio sensor SN 1 A  131 A, the rotational position sensor SN 2 A  132 A, and the rotational position sensor SN 2 B  132 B to computer CP 1   121 , simple wire connections are used. Also since transition flexing adjusters AD 1 A  101 A, transition flexing adjuster AD 1 B  101 B, mover adjuster AD 2 A  102 A, mover adjuster AD 2 B  102 B, relative rotational position sensor SN 3 A  133 A, and relative rotational position sensor SN 3 B  133 B are rotating relative to computer CP 1   121 , in order to connect these transition flexing adjusters, mover adjusters and, relative rotational position sensors to the computer CP 1   121 , a ring and brush connection, is used. An example of a ring and brush connection is shown in  FIG. 18 . Here two output connections of computer CP 1   121 , one positive and one negative, are directed to two pair of brushes, labeled as brush BR 1 A  141 A and brush BR 1 B  141 B, by cables. Brush BR 1 A  141 A is in contact with the positive electrical ring RN 1 A  151 A. And brush BR 1 B  141 B is in contact with the negative electrical ring RN 1 B  151 B. The electrical rings are attached to the body of the adjuster by insulated fins RN 1 A-S 1   151 A-S 1  and insulated fins RN 1 B-S 1   151 B-S 1 . And cables are used to direct the current or signal from the electrical rings to the electrical poles of the adjuster. 
   A configuration for the transition flexing adjuster AD 1 A  101 A, which has an adjuster body AD 1 A-M 1   101 A-M 1  and an adjuster output member AD 1 A-M 2   101 A-M 2 , is shown in  FIG. 13 . Here the adjuster output member AD 1 A-M 2   101 A-M 2  can rotate relative to the adjuster body AD 1 A-M 1   101 A-M 1 , which is mounted at the end of the mover sleeve CS 2 A-M 6   22 A-M 6 , see  FIG. 12 . The mover sleeve CS 2 A-M 6   22 A-M 6  is almost identical to the mover sleeve used in CVT  1 , hence it can also slide axially relative to its cone and is used to change the axial position of its torque transmitting members. The only difference between mover sleeve CS 2 A-M 6   22 A-M 6  and the mover sleeve used in CVT  1  is that for mover sleeve CS 2 A-M 6   22 A-M 6  no rotor  1056  is used. The adjuster body AD 1 A-M 1   101 A-M 1  is fixed to the mover sleeve CS 2 A-M 6   22 A-M 6 , but the adjuster output member AD 1 A-M 1   101 A-M 1  can rotate relative to the mover sleeve CS 2 A-M 6 . Telescopes CS 2 A-M 4   22 A-M 4  are basically identical to telescopes  1057  described previously. The top end of telescopes CS 2 A-M 4   22 A-M 4  are connected to torque transmitting member CS 2 A-M 1   22 A-M 1 , and the bottom end of telescopes CS 2 A-M 4   22 A-M 4  are attached to mover sleeve CS 2 A-M 6 ; and the top end of telescopes CS 2 A-M 5   22 A-M 5  are connected to torque transmitting member CS 2 A-M 1   22 A-M 2 , and the bottom end of telescopes CS 2 A-M 5   22 A-M 5  are attached to the adjuster output member AD 1 A-M 2   101 A-M 2 . The telescopes CS 2 A-M 4   22 A-M 4  and telescopes CS 2 A-M 5   22 A-M 5  are attached in the same manner as the telescopes  1057  are attached to their torque transmitting members and to their rotor  1056 . Hence mover sleeve CS 2 A-M 6  and adjuster output member AD 1 A-M 2   101 A-M 2  also have pin-holed plates, which are basically identical to the pin-holed plates attached on the outer surface of rotor  1056  as described in the Mover Mechanism section of this patent. Here the adjuster output member AD 1 A-M 2   101 A-M 2 , see  FIG. 13 , has the following shapes, it has an adjuster output shaft AD 1 A-M 2 -S 1   101 A-M 2 -S 1 , on which an adjuster extension arm AD 1 A-M 2 -S 2   101 A-M 2 -S 2  is attached. The adjuster extension arm AD 1 A-M 2 -S 2   101 A-M 2 -S 2  has an L-shape. The short leg of the L-shaped adjuster extension arm AD 1 A-M 2 -S 2   101 A-M 2 -S 2  is extending radially outwards from the center of the front surface of the adjuster output shaft AD 1 A-M 2 -S 1   101 A-M 2 -S 1 . The long leg of the L-shaped adjuster extension arm AD 1 A-M 2 -S 2   101 A-M 2 -S 2  is parallel to the adjuster output shaft AD 1 A-M 2 -S 1   101 A-M 2 -S 1  and is extending axially backwards so that the telescopes CS 2 A-M 5   22 A-M 5  of torque transmitting member CS 2 A-M 2   22 A-M 2  can be attached at the same axial position as the telescopes CS 2 A-M 4   22 A-M 4  of torque transmitting member CS 2 A-M 1   22 A-M 1 . This leg has two telescopes attachment plates AD 1 A-M 2 -S 4   101 A-M 2 -S 4 , which are used to attach the telescopes CS 2 A-M 5   22 A-M 5  to this leg. The telescopes attachment plates AD 1 A-M 2 -S 4   101 A-M 2 -S 4  are basically identical to the pin-holed plates attached on the outer surface of rotor  1056  as described in the Mover Mechanism section of this patent. In addition, a constrainer slide  111 A-M 1  is also attached to this leg. Furthermore, in order to balance the centrifugal forces of the adjuster extension arm AD 1 A-M 2 -S 2   101 A-M 2 -S 2  and its attachments, an adjuster balancing arm AD 1 A-M 2 -S 3   101 A-M 2 -S 3 , which also has an L-shape, is positioned opposite from the adjuster extension arm AD 1 A-M 2 -S 2   101 A-M 2 -S 2  on the front surface of the adjuster output shaft adjuster AD 1 A-M 2 -S 1   101 A-M 2 -S 1 . 
   Furthermore in order to ensure that the adjuster output member AD 1 A-M 2   101 A-M 2  can be used to control the rotational position of torque transmitting member CS 2 A-M 2 , a constrainer mechanism CN 1 A  111 A, shown in  FIG. 19 , is attached to the long leg of the L-shaped adjuster extension arm AD 1 A-M 2 -S 2   101 A-M 2 -S 2 . The constrainer mechanism consist of a constrainer slide  111 A-M 1 , that is placed between the telescopes attachment plates of the long leg of the L-shaped adjuster extension arm AD 1 A-M 2 -S 2   101 A-M 2 -S 2 ; a constrainer slider  111 A-M 2 , that is slideably inserted into the constrainer slide  111 A-M 1 ; and two constrainer links  111 A-M 3 , each connecting the bottom member of telescope CS 2 A-M 5   22 A-M 5  to the constrainer slider  111 A-M 2 . The constrainer slide  111 A-M 1  is shaped like slender round rod, on which the constrainer slider  111 A-M 2  is slideably inserted. The constrainer slider  111 A-M 2  is shaped like a sleeve, which has two identical slider clevises  111 A-M 2 -S 1  which are positioned opposite of each other. Each slider clevis of the constrainer slider consist of two parallel slider clevis plates, which are flat plates, which flat surfaces are perpendicular to the side surface of the constrainer slider. Each slider clevis plate has a hole and the outer edge of each slider clevis plate is rounded-off. Each constrainer link  111 A-M 3  is shaped like slender flat bar that has a constrainer link hole, which is a hole that is slightly larger than the holes of the slider clevis plates, at each end. The end of each constrainer link is rounded-off so that a half disk shape, which diameter is identical to the width of the constrainer link and which center is located at the center of the constrainer link hole, exist at each end of the constrainer link. Furthermore, the bottom member of each telescopes CS 2 A-M 5   22 A-M 5  also has a telescope constrainer clevis CS 2 A-M 5 -S 1   22 A-M 5 -S 1 . The position of the telescope constrainer clevis on the bottom member of one telescope CS 2 A-M 5   22 A-M 5  is identical to that of the other telescope CS 2 A-M 5   22 A-M 5 . Each telescope constrainer clevis consists of two parallel telescope constrainer clevis plates. The telescope constrainer clevis plates are flat plates, which flat surfaces are perpendicular to the side surfaces of their telescopes. Each telescope constrainer clevis plate has a hole, which is slightly smaller than the constrainer link holes, and the outer edge of each telescope constrainer clevis plate is rounded-off. In order to connect the bottom members of the telescopes CS 2 A-M 5   22 A-M 5  to the constrainer slider  111 A-M 2 , constrainer pins  111 A-M 4  are used. The constrainer pins  111 A-M 4  are shaped like slender round rods. Here one constrainer link hole of each constrainer link  111 A-M 3  is placed between the slider clevis plates of a slider clevis  111 A-M 2 -S 1 , such that a constrainer pin CN 1 A-M 4   111 A-M 4  can be inserted through the constrainer link holes and those slider clevis holes. The body of a constrainer pin  111 A-M 4  has a diameter small enough such that a constrainer link  111 A-M 3  can freely rotate on it, but large enough such that a constrainer pin CN 1 A-M 4   111 A-M 4  can be securely held in place relative to its slider clevis  111 A-M 2 -S 1  by friction between the slider clevis hole surfaces and the body of the constrainer pin  111 A-M 4 . Also, the constrainer pins  111 A-M 4  are long enough such that sufficient engagement between the constrainer pins  111 A-M 4  an a set of slider clevis plates of a slider clevis  111 A-M 2 -S 1  can exist. 
   And the other constrainer link hole of each constrainer link  111 A-M 2 -S 1  is placed between a set of telescope constrainer clevis plates of a telescope constrainer clevis CS 2 A-M 5 -S 1   22 A-M 5 -S 1 , such that a constrainer pin  111 A-M 4  can be inserted through the constrainer link holes and the telescope constrainer clevis plate holes. Here the diameters of the constrainer pins are small enough such that the constrainer links can freely rotate on them, but large enough such that they can be securely held in place relative to their telescope constrainer clevis plates by friction between their side surfaces and the telescope constrainer clevis hole surfaces. In addition, the constrainer pins are long enough such that sufficient engagement between the constrainer pins and a set of telescope constrainer clevis plates can exist. 
   In addition, while the slots of the cone of cone assembly CS 2 A where the attachment pins CS 2 A-M 1 -S 1   22 A-M 1 -S 1 , used to attach torque transmitting member CS 2 A-M 1   22 A-M 1  to a cone assembly CS 2 A  22 A, are inserted, should allow minimal rotational movements between torque transmitting member CS 2 A-M 1   22 A-M 1  and its cone, the slots where the attachment pins CS 2 A-M 2 -S 1   22 A-M 2 -S 1  of torque transmitting members CS 2 A-M 2   22 A-M 2  are inserted should allow sufficient rotational movement between the torque transmitting member CS 2 A-M 2   22 A-M 2  and its cone such that transition flexing can be eliminated. Hence here, the attachment pins of torque transmitting member CS 2 A-M 2   22 A-M 2  are placed in a gap. In this application, a torque transmitting member which attachment pins are placed in a gap will be referred to as a gap mounted torque transmitting member. 
   From the description above it can be observed that the torque transmitting member CS 2 A-M 1   22 A-M 1  is rotatably constrained relative to mover sleeve CS 2 A-M 6   22 A-M 6 , and torque transmitting member CS 2 A-M 2   22 A-M 2  is rotatably constrained relative to the adjuster output member AD 1 A-M 2   101 A-M 2 , and since the adjuster output member AD 1 A-M 2   101 A-M 2  can rotate relative to the mover sleeve CS 2 A-M 6   22 A-M 6 , the transition flexing adjuster AD 1 A  101 A can be used by computer CP 1   121  to adjust the rotational position of the torque transmitting member CS 2 A-M 2   22 A-M 2  relative to torque transmitting member CS 2 A-M 1   22 A-M 1 . As described earlier, like CVT  1 , CVT  1 . 1  has two identical cone assemblies, one on the input shaft SH 3   13 , which is labeled as cone assembly CS 2 A  22 A, and another one on the output shaft SH 4   14 , which is labeled as cone assembly CS 2 B  22 B. Hence here, the transition flexing adjuster AD 1 B is identical to transition flexing adjuster AD 1 A, and is mounted on cone assembly CS 2 B  22 B in the same manner as transition flexing adjuster AD 1 A is mounted on cone assembly CS 2 A  22 A. 
   Next the mover adjusters AD 2 A and AD 2 B, which will be used to substantially increase the duration at which the transmission ratio can be changed, are described. In order to substantially increase the duration at which the transmission ratio can be changed, the mover adjusters will be used to try maintain CVT  1 . 1  in a moveable configuration, as shown in  FIG. 11  and described in detail in the Continuous Variable Transmission Variation  1  (CVT  1 ) section of this patent, regardless of the rotational position of the input shaft SH 3   13  and the output shaft SH 4   14 . This is achieved by allowing the cone assemblies to slip relative to their shaft so that they are maintained in a moveable configuration. Here movable adjuster AD 2 A is used to allow cone assembly CS 2 A  22 A, positioned on the input shaft SH 3   13 , to slip relative to the input shaft SH 3   13 . And movable adjuster AD 2 B is used to allow cone assembly CS 2 B  22 B, positioned on the output shaft SH 4   14 , to slip relative to the output shaft SH 4   14 . In order to achieve this, the adjuster body AD 2 A-M 1   102 A-M 1  of movable adjuster AD 2 A is keyed to the input shaft SH 3   13  so that it is constrained from rotating and moving axially relative to input shaft SH 3   13 . And the cone assembly CS 2 A  22 A is fixed to the adjuster output member AD 2 A-M 2   102 A-M 2  of movable adjuster AD 2 A  102 A so that it is constrained from rotating and moving axially relative the adjuster output member AD 2 A-M 2   102 A-M 2 . In order to mount mover adjuster AD 2 A  102 A to input shaft SH 3   13 , mover adjuster AD 2 A  102 A has an sliding hole, which center is located at the center-axis of mover adjuster AD 2 A  102 A and goes through the entire axial length of mover adjuster AD 2 A  102 A, except through the adjuster attachment ring AD 2 A-M 1 -S 1   102 A-M 1 -S 1 , which has a mounting hole, which is of a smaller diameter. The diameter of the sliding hole of mover adjuster AD 2 A  102 A is considerably larger than the diameter of output shaft SH 13   13  so that adjuster output member AD 2 A-M 2   102 A-M 2  can freely rotate relative to output shaft SH 13   13 . And in order to mount the adjuster body AD 2 A-M 1   102 A-M  1  of mover adjuster AD 2 A  102 A to the output shaft SH 13   13 , the adjuster body AD 2 A-M 1   102 A-M 1  has an adjuster attachment ring AD 2 A-M 1 -S 1   102 A-M 1 -S 1  that extends axially backwards from the adjuster body AD 2 A-M 1 . The diameter of the mounting hole of the adjuster attachment ring AD 2 A-M 1 -S 1  is only slightly larger than the diameter of input shaft SH 3   13 , so that the adjuster body AD 2 A-M 1   102 A-M 1  can be securely mounted on input shaft SH 3   13 . In addition, the adjuster attachment ring AD 2 A-M 1 -S 1  has a set-screw that is used to prevent the adjuster body AD 2 A-M 1   102 A-M 1  from moving axially and from rotating relative to input SH 3   13 . The mover adjuster AD 2 B  102 B is used to mount cone assembly CS 2 B  22 B on output shaft SH 4   14  in the same manner as the mover adjuster AD 2 A  102 A is used to mount cone assembly CS 2 A  22 A on input shaft SH 3   13 . And as described earlier, the rotational position of cone assembly CS 2 A  22 A, which is mounted on the input shaft SH 3   13 , is monitored by computer CP 1   121  via rotational position sensor SN 2 A  132 A. And the rotational position of cone assembly CS 2 B  22 B, which is mounted on the output shaft SH 4   14 , is monitored by computer CP 1   121  via rotational position sensor SN 2 A  132 A. 
   Now that the physical configuration of CVT  1 . 1 , including its adjuster system, has been described. The operation of transition flexing adjuster AD 1 A  101 A, transition flexing adjuster AD 1 B  101 B, mover adjuster AD 2 A  102 A, and mover adjuster AD 2 B  102 B will described. 
   In order to explain the operation of the transition flexing adjusters, first the required relative rotational movements between the torque transmitting members of a cone assembly CS 2   22 , such as cone assembly CS 2 A  22 A or cone assembly CS 2 B  22 B, in order to eliminate transition flexing will be described. The relative rotational movements that can be used to eliminate transition flexing are shown in  FIGS. 20A ,  20 B,  20 C, and  20 D, which show the different rotational positions of a cone assembly CS 2   22  as it is rotated clockwise. For illustrative purposes, one torque transmitting member is referred to as torque transmitting member  11  and the other torque transmitting member is referred to as torque transmitting member  22 . We start with  FIG. 20A , here torque transmitting member  11  is in contact with the transmission belt  3  while torque transmitting member  22  is not. Here in order to eliminate transition flexing that will occur when torque transmitting member  22  comes in contact with the transmission belt  3 , the lower positioned space between the torque transmitting members, which in this case is non-torque transmitting arc A 4 , needs to be a multiple of the width of the teeth of the torque transmitting members. If this is the case then no adjustment for the rotational position of torque transmitting member  22  relative to torque transmitting member  11  is needed. Otherwise a transition flexing adjuster needs to rotate one torque transmitting member clockwise or counter-clockwise relative to the other torque transmitting member such that the non-torque transmitting arc A 4  is a multiple of the width of the teeth of the torque transmitting members. In  FIG. 20A , the rotation provided by the transition flexing adjuster is shown as ωa, which is arbitrarily selected as clock-wise. After some rotation of the cone assembly, both torque transmitting member  11  and torque transmitting member  22 , as shown in  FIG. 20B , are in contact with the transmission belt  3 . During this configuration, the transition flexing adjuster maintains the relative rotational position between the torque transmitting members, such that the non-torque transmitting arc A 4 , which in this instance is covered by the transmission belt  3 , remains a multiple of the width of the teeth of the torque transmitting members. After some further rotations of the cone assembly, torque transmitting member  11  comes out of contact with the transmission belt  3 , as shown in  FIG. 20C . Here in order to eliminate transition flexing that will occur when the torque transmitting member  11  comes in contact with transmission belt  3  again, the lower positioned space between the torque transmitting members, which in this case is non-torque transmitting arc B 5 , needs to be a multiple of the width of the teeth of the torque transmitting members. If this is the case then no adjustment for the rotational position of torque transmitting member  11  relative to torque transmitting member  22  is needed. Otherwise a transition flexing adjuster needs to rotate one torque transmitting member clockwise or counter-clockwise relative to the other torque transmitting member such that the non-torque transmitting arc B 5  is a multiple of the width of the teeth of the torque transmitting members. In  FIG. 20C , the rotation provided by the transition flexing adjuster is also shown as ωa, which in this instance is again arbitrarily selected as clock-wise. After some rotation, both the torque transmitting member  11  and the torque transmitting member  22 , as shown in  FIG. 20D , are in contact with transmission belt  3 . During this configuration, the transition flexing adjuster maintains the relative rotational position between the torque transmitting members, such that the non-torque transmitting arc B 5 , which is covered by the transmission belt  3  remains a multiple of the width of the teeth of the torque transmitting members. For clockwise rotation of a cone assembly, as shown in  FIGS. 20A-20D , the lower positioned non-torque transmitting arc is the critical non-torque transmitting arc, since it is the non-torque transmitting arc that is about to be completely covered by the transmission belt so that it has to be adjusted immediately. However, for counter-clockwise rotation of a cone assembly CS 2   22 , the upper positioned non-torque transmitting arc is the critical torque transmitting arc, since in this case it is the non-torque transmitting arc that is about to be completely covered by the transmission belt so that it has to be adjusted immediately. 
   Graphs showing the required relative rotation between the torque transmitting members (l θ ) vs. the arc length of the critical non-torque transmitting arc (l c ) are shown in  FIGS. 21A ,  21 B,  21 C. For these graphs, the y-axis represents the required arc length, l θ , that the torque transmitting member that is about to engage with its belt has to be rotated relative to the torque transmitting member currently engaged. For cases where the cone assemblies are rotated counter-clockwise, a positive value for l θ  represents counter-clockwise rotation, and a negative value for theta represents clockwise rotation. And for cases where the cone assemblies are rotated clockwise, a positive value for l θ  represents clockwise rotation, and a negative value for theta represents counter-clockwise rotation. So basically, a positive value for l θ  means that the tooth/torque transmitting member has to be rotated in the direction of rotation of the cone assembly relative to its transmission belt, and a negative value for l θ  means that the tooth/torque transmitting member has to be rotated in the opposite direction of rotation of the cone assembly relative to its transmission belt. Furthermore, the x-axis represents the arc length of the critical non-torque transmitting arc, l c . Here the width w t  corresponds to the width of the teeth of the torque transmitting members. In order to determine the value for the arc length of the critical non-torque transmitting arc, l c , computer CP 1   121  uses the data for the pitch diameter and the data for the rotational positions of the torque transmitting members. Also, the vertical lines, excluding the y-axis, of the graphs shown in FIGS.  21 A/B/C mean that no adjustment is required. 
   Now the operation of the mover adjusters in order to substantially increase the duration at which the transmission ratio can be changed will be described. When the transmission ratio is about to be changed, the computer CP 1   121  monitors the rotational position of the cone assemblies CS 2 A  22 A and CS 2 B  22 B using the rotational position sensors SN 2 A  132 A and SN 2 B  132 B, and once the cone assemblies are in a moveable configuration, such as shown in  FIG. 11 , the moveable adjusters AD 2 A  102 A and AD 2 B  102 B allow the cone assemblies to slip relative to their shaft such that they are maintained in a movable configuration. Then the transmission ratio is changed. In cases where the adjusters cannot be continuously maintained in a moveable configuration, due to practical or economical reasons for example, then the moveable adjusters can be used to at least substantially increase the duration that the cone assemblies are in a moveable configuration. 
   Adjuster System for CVT  2  ( FIGS. 22 ,  23 ,  24 A to  24 D,  25 ,  26 A to  26 C,  27 A,  27 B,  28 A,  28 B,  29 A, &amp;  29 B) 
   Here a slightly modified version if CVT  2  to which an adjuster system is added is labeled as CVT  2 . 1 . CVT  2 . 1  is almost identical to CVT  2  described earlier. CVT  2 , which is shown in  FIG. 22 , consist mainly of two transmission pulleys, transmission pulley PU 1 A  41 A and transmission pulley PU 1 B  41 B, and two cone assemblies which each have a torque transmitting member and a non-torque transmitting member, labeled as cone assembly CS 3 A  23 A and cone assembly CS 3 B  23 B. The torque transmitting member of cone assembly CS 3 A  23 A is labeled as torque transmitting member CS 3 A-M 1   23 A-M 1 ; and the torque transmitting member of cone assembly CS 3 B  23 B is labeled as torque transmitting member CS 3 B-M 1   23 B-M 1 . And the non-torque transmitting member of cone assembly CS 3 A  23 A is labeled as non-torque transmitting member CS 3 A-M 2   23 A-M 2 ; and the non-torque transmitting member of cone assembly CS 3 B  23 B is labeled as non-torque transmitting member CS 3 B-M 2   23 B-M 2 . Also the cone of cone assembly CS 3 A is labeled as cone CS 3 A-M 3   23 A-M 3  and the cone of cone assembly CS 3 B is labeled as cone CS 3 B-M 3   23 B-M 3 . Each torque transmitting member and each non-torque transmitting member is attached to its cone such that it can slide axially relative to its cone, but is restrained from rotating relative to the its cone. The torque transmitting members are used for torque transmission, and the non-torque transmitting members are mainly used to maintain the axial position of their transmission belt and guide their transmission belt during transmission ratio change. The transmission pulleys PU 1 A  41 A and PU 1 B  41 B are keyed to a spline sleeve SP 1 A  51 A, which is slideably mounted on the input spline shaft SH 5   15 , and the cone assemblies CS 3 A  23 A and CS 3 B  23 B are keyed to the output shaft SH 6   16  in a manner such that the torque transmitting member of one cone assembly is positioned opposite from the torque transmitting member of the other cone assembly. In order to transmit torque from the input spline shaft SH 5   15  to the output shaft SH 6   16 , a transmission belt BL 2 A  32 A is used to couple transmission pulley PU 1 A  41 A with cone assembly CS 3 A  23 A, in a manner such that torque transmitting member CS 3 A-M 1   23 A-M 1  can properly engage with transmission belt BL 2 A  32 A. And a transmission belt BL 2 B  32 B is used to couple transmission pulley PU 1 B  41 B with cone assembly CS 3 B  23 B, in a manner such that torque transmitting member CS 3 B-M 1   23 B-M 1  can properly engage with transmission belt BL 2 B  32 B. The transmission ratio is changed by changing the axial position of the torque transmitting members and the transmission pulleys relative to of their cone, in a manner such that for all transmission ratios, the torque transmitting members can properly engage with their transmission pulley. The transmission ratio can only be changed when only one torque transmitting member is in contact with its transmission belt, otherwise stalling of the transmission changing actuator occurs. And in order to maintain the proper tension in the transmission belts and help maintain the axial position of the transmission belts, each transmission belt has two tensioning wheels. The tensioning wheels for transmission belt BL 2 A  32 A are labeled as tensioning wheel TW 1 A  61 A and tensioning wheel TW 1 B  61 B. And the tensioning wheels for transmission belt BL 2 B  32 B are labeled as tensioning wheel TW 1 C  61 C and tensioning wheel TW 1 D  61 D. Each tensioning wheel is always in contact with the inner surface of its transmission belt, and is positioned between its cone assembly and its transmission pulley. For each transmission belt, one tensioning wheel is in contact with the slack side of the transmission belt, and the other tensioning wheel is in contact with the tight side of the transmission belt. From the description above, it becomes obvious that CVT  2  allows its transmission belts to flex more in order to compensate for transition flexing than CVT  1 , since here the lengths of the transmission belts that can flex always extend from the torque transmitting members to the transmission pulleys, while for CVT  1  in some instances the length that its transmission belt can flex only extend from one torque transmitting member to the other. 
   CVT  2 . 1 , see  FIGS. 23 ,  24 A,  24 B,  24 C, and  24 D, is slightly different than CVT  2 . Like CVT  2 , for CVT  2 . 1  the two transmission pulleys are mounted on the input spline shaft, which here is labeled as input spline shaft SH 7   17 , by the use of an spline sleeve SP 1 B  51 B. And like CVT  2 , each transmission pulley is coupled to a cone assembly with a torque transmitting member and a non-torque transmitting member that are directly mounted on an output shaft, which here is labeled as output shaft SH 8   18 , by a transmission belt. Here the cone assemblies are labeled as cone assembly CS 3 C  23 C and cone assembly CS 3 D  23 D, and the transmission belts are labeled as transmission belt BL 2 C  32 C and transmission belt BL 2 D  32 D. And the torque transmitting member of cone assembly CS 3 C  23 C is labeled as torque transmitting member CS 3 C-M 1   23 C-M 1 , and the torque transmitting member of cone assembly CS 3 D  23 D is labeled as torque transmitting member CS 3 D-M 1   23 D-M 1 . And the non-torque transmitting member of cone assembly CS 3 C  23 C is labeled as non-torque transmitting member CS 3 C-M 2   23 C-M 2 , and the non-torque transmitting member of cone assembly CS 3 D  23 D is labeled as non-torque transmitting member CS 3 D-M  123 D-M 2 . While the cone of cone assembly CS 3 C is labeled as cone CS 3 C-M 2   23 C-M 3 , and the cone of cone assembly CS 3 D is labeled as cone CS 3 D-M 3   23 D-M 3 . However unlike CVT  2 , for CVT  2 . 1  for each transmission belt, only one tensioning wheel is used. These tensioning wheels operate and are mounted in the same manner as the tensioning wheels mounted on the slack side of the transmission belts of CVT  2 . Here the tensioning wheel for transmission belt BL 2 C  32 C is labeled as tensioning wheel TW 1 E  61 E and the tensioning wheel for transmission belt BL 2 D  32 D is labeled as tensioning wheel TW 1 E  61 F. 
   Like CVT  2 , in order to change the transmission ratio, a transmission ratio changing actuator is used. The strength of the transmission ratio changing actuator should be limited such that under no condition should it be able to cause excessive high stresses in the transmission belts. So that it will stall or slip in instances when it is about to cause excessive high stresses in the transmission belts. But in order to avoid unnecessary stalling or slipping of the transmission ratio changing actuator, it should be strong enough to be able to stretch the transmission belts within an acceptable limit. 
   Furthermore, for CVT  2 . 1 , in order to eliminate or significantly reduce transition flexing, and substantially increase the duration at which the transmission ratio can be changed, an adjuster AD 3   103  is used. Like the adjusters described earlier, adjuster AD 3   103  has an adjuster body AD 3 -M 1   103 -M 1  and an adjuster output member AD 3 -M 2   103 -M 2 , that can rotate relative to the adjuster body AD 3 -M 1   103 -M 1 . The adjuster body AD 3 -M 1  is mounted on spline sleeve  51 B using a set-screw so that it is axially and rotatably constrained relative to spline sleeve  51 B. And on the adjuster output member AD 3 -M 2   103 -M 2 , the transmission pulley PU 1 C  41 C is fixed via a torque sensor SN 4 C  134 C, so that adjuster output member AD 3 -M 2   103 -M 2  is virtually axially and rotatably constrained relative to transmission pulley PU 1 C  41 C. And since the adjuster output member AD 3 -M 2   103 -M 2  can rotate relative to the adjuster body AD 3 -M 1 , transmission pulley PU 1 C  41 C can rotate relative to spline sleeve  51 B. However, no adjuster is used to mount transmission pulley PU 1 D  41 D to spline sleeve  51 B. Here transmission pulley PU 1 D  41 D is mounted to spline sleeve  51 B via a torque sensor SN 4 D  134 D, so that transmission pulley PU 1 D  41 D is virtually axially and rotatably constrained relative to spline sleeve  51 B. 
   In order to control adjuster AD 3   103 , a computer CP 2   122 , which controls adjuster AD 3   103  based on the input from a transmission ratio sensor SN 1 B  131 B, a rotational position sensor SN 2 C  132 C, a rotational position sensor SN 2 D  132 D, a rotational position sensor SN 2 E  132 E, a torque sensor SN 4 C  134 C, and a torque sensor SN 4 D  134 D is used. 
   The transmission ratio sensor SN 1 B  131 B is mounted on a frame so that it can be used to monitor the rotation of the transmission ratio gear rack gear via a sensor strip wrapped around the transmission ratio gear rack gear, so that computer CP 2   122  can determine the transmission ratio, and hence the axial position of the torque transmitting members relative to the cones on which they are attached. And from that information computer CP 2   122  can determine the pitch diameter, which as described earlier is the diameter of the surfaces of the cones where the torque transmitting members are positioned. 
   The rotational position sensors SN 2 E  132 E, is mounted on a frame so that it can be used to monitor the rotational position of output shaft SH 8   18  via a sensor strip wrapped around output shaft SH 8   18 . And from that information computer CP 2   122  can determine the rotational position of the torque transmitting members. The rotational position sensor SN 2 C  132 C, is mounted on a frame so that it can be used to monitor the rotational position of transmission pulley PU 1 C  41 C via a sensor strip wrapped around a portion of transmission pulley PU 1 C  41 C, or the adjuster output member on which transmission pulley PU 1 C  41 C is mounted. And the rotational position sensor SN 2 D  132 D, is mounted on a frame so that it can be used to monitor the rotational position of transmission pulley PU 1 D  41 D via a sensor strip wrapped around transmission pulley PU 1 D  41 D, or the adjuster output member on which transmission pulley PU 1 C  41 C is mounted. Using the rotational position sensor SN 2 C  132 C and SN 2 D  132 D, computer CP 2   122  can determine the absolute rotational position of the transmission pulleys and the rotational position of one transmission pulley relative to the other. Also if more advantageous, here a rotational position sensors that monitor the rotational position of the transmission pulleys can be replaced with a relative rotational position sensor that monitors the rotation between the adjuster body and the adjuster output member of adjuster AD 3   103 , and hence the relative rotational position between the transmission pulleys. 
   The torque sensors SN 4 C  134 C and SN 4 B  134 D, which each have a body and an output shaft, can measure the torque applied between their body and their output shaft. However unlike an adjuster, no significant rotation between the body and the output shaft of a torque sensor is allowed. Torque sensor SN 4 A  134 C is used to measure the pulling load on transmission pulley PU 1 C  41 C due to the torque at input spline shaft SH 7   17  and the rotational resistance provided by cone assembly CS 3 C  23 C. And torque sensor SN 4 D  134 D is used to measure the pulling load on transmission pulley PU 1 D  41 D due to the torque at input spline shaft SH 7   17  and the rotational resistance provided by cone assembly CS 3 D  23 D. Here the body of torque sensor SN 4 C  134 C, is fixed to the adjuster output member AD 3 -M 2   103 -M 2  and the output shaft of torque sensor SN 4 C  134 C is fixed to transmission pulley PU 1 C  41 C; and the body of torque sensor SN 4 D  134 D is keyed to the spline sleeve SP 1 B  51 B, and transmission pulley PU 1 D  41 D is keyed to the output shaft of torque sensor SN 4 D  134 D. 
   In order to connect the transmission ratio sensor SN 1 B  131 B and the rotational position sensor SN 2 C  102 C to computer CP 2   122 , simple wire connections are used. And since adjuster AD 3   103 , torque sensor SN 4 C  134 C, and torque sensor SN 4 D  134 D are rotating relative to computer CP 2   122 , in order to connect them to computer CP 2   122 , the ring and brush connection, is used. An example of a ring and brush connection is shown in  FIG. 18  and is described earlier. 
   The rotational position sensors SN 2 E  132 E, which monitors the rotational position of the shaft on which the cone assemblies are mounted, can consist of sensor wheel, which has a circular surface that has an alternating reflective and un-reflective pattern, and a counter, which counts the occurrence each time a reflecting pattern is positioned in front of it, as the sensor wheel is rotating. The counter resets each time the respective shaft rotates one full rotation from a predetermined reference point. Based on the amount of reflective patterns counted, the controlling computer, computer CP 2   122 , to which the sensor is connected can determine the angular position of the respective shaft. In the controlling computer, the angles between the reference points of the torque transmitting members which angular positions relative to the predetermined reference point of the sensor wheel do not change as the transmission ratio is changed should be programmed. For the cone assemblies described in the description for CVT  1  and CVT  2 , the reference points of the torque transmitting members are located at the midpoint of the torque transmitting members. Here if the predetermined reference point is placed to coincide with the reference point of one torque transmitting member, than the angle between the reference point of that torque transmitting member and the predetermined reference point is 0 degrees. And the angle between the reference point of the other torque transmitting member and the predetermined reference point is 180 degrees. 
   For the front pin belt cone assembly  520 A and back pin belt cone assembly  520 B described in the Alternate CVT&#39;s section of this application, the angular position of a reference point of a torque transmitting member is located on the line that starts at the center of one torque transmitting member slide  560 -S 2  and ends at the center of the other torque transmitting member slide  560 -S 2 , see  FIGS. 77A ,  77 B,  78 A, and  78 B. And for front sliding tooth cone assembly  420 A and back sliding tooth cone assembly  420 B and single tooth cone assemblies, which will be described later in this application and which all have only one tooth each, the reference point of a torque transmitting member is located at the same angular position as the angular position where the mirror line of their tooth is located. Like for the cone assemblies described in the description for CVT  1  and CVT  2 , the predetermined reference point can be located at a reference point of a torque transmitting member. And like for the cone assemblies described in the description for CVT  1  and CVT  2  if the predetermined reference point located at a reference point of a torque transmitting member, than the angle between the reference point of that torque transmitting member and the predetermined reference point is 0 degrees. And the angle between the reference point of the other torque transmitting member and the predetermined reference point is 180 degrees. 
   Furthermore, from the transmission ratio sensor SN 1 B  131 B, the controlling computer, computer CP 2   122 , can determine the axial position of the torque transmitting members on the surface of their respective cones and from there the engagement coverage of the torque transmitting members; since the engagement coverage as a function of the axial position of the torque transmitting members relative the surface of their respective cones can be easily obtained experimentally and/or mathematically and then be programmed into the controlling computer. By using this information and the information from the rotational position sensors SN 2 E  132 E, the controlling computer can be programmed so that it can determine the engagement status of the cone assemblies, which here were labeled as a cone assembly CS 3 C  23 C and cone assembly CS 3 D  23 D, as they are rotating. The engagement status of the cone assemblies are: 1) only the torque transmitting member of cone assembly CS 3 C  23 C is engaged, 2) the torque transmitting member of cone assembly CS 3 C  23 C is engaged and the torque transmitting member of cone assembly CS 3 D  23 D is about to come into engagement, 3) the torque transmitting member of cone assembly CS 3 C  23 C and the torque transmitting member of cone assembly CS 3 D  23 D are engaged, 4) the torque transmitting member of cone assembly CS 3 C  23 C is about to come out of engagement and the torque transmitting member of cone assembly CS 3 D  23 D is engaged, 5) only the torque transmitting member of cone assembly CS 3 D  23 D is engaged, 6) the torque transmitting member of cone assembly CS 3 D  23 D is engaged and the torque transmitting member of cone assembly CS 3 C  23 C is about to come into engagement, 7) the torque transmitting member of cone assembly CS 3 D  23 D and the torque transmitting member of cone assembly CS 3 C  23 C are engaged, 8) the torque transmitting member of cone assembly CS 3 D  23 D is about to come out of engagement and the torque transmitting member of cone assembly CS 3 C  23 C is engaged. 
   Besides depending on the rotational position of the cone assemblies, the engagement statuses above also depend on the input setting of the designer or user. For example, for engagement status  2 ) the torque transmitting member of cone assembly CS 3 C  23 C is engaged and the torque transmitting member of cone assembly CS 3 D  23 D is about to come into engagement, the designer needs to set a value in degrees when status  2  starts and status  1  ends. For example, here the designer can program the controlling computer so that status  2  starts 5 degrees before actual engagement of the torque transmitting member of cone assembly CS 3 D  23 D. Obviously, a different value than 5 degrees can also be used. The value selected should ensure that for the equipment selected the CVT operates properly. The value for proper operation depends mainly on the responsiveness of the actuators, such as the adjusters and the transmission ratio changing actuator, the responsiveness of the controlling computer, the inertia of the components of the CVT, and the operating speed and acceleration of the motor coupled to the CVT. The proper value for engagement status  2 ) can be obtained experimentally by first running the machine at a low value or zero and then increasing the value if improper operations occur until improper operation cease to occur. The same method can be used to program the values for engagement statuses  4 ,  6 , and  8 . 
   The engagement statuses described in the previous paragraph can be used to have the controlling computer, computer CP 2   122 , properly control adjuster AD 3   103  to reduce transition flexing. For example, as in CVT  1 , in order to reduce transition flexing, the adjuster should provide adjustments when only one torque transmitting member is engaged with its transmission belt. Hence preferably the controlling computer should only use the adjuster to reduce transition flexing when the engagement status is either 1) only the torque transmitting member of cone assembly CS 3 C  23 C is engaged or 5) only the torque transmitting member of cone assembly CS 3 D  23 D is engaged. Although the entire durations at which the adjuster can provide adjustments is the duration of engagement statuses  1 ) only the torque transmitting member of cone assembly CS 3 C  23 C is engaged and 2) the torque transmitting member of cone assembly CS 3 C  23 C is engaged and the torque transmitting member of cone assembly CS 3 D  23 D is about to come into engagement, and the duration of engagement statuses  5 ) only the torque transmitting member of cone assembly CS 3 D  23 D is engaged and 6) the torque transmitting member of cone assembly CS 3 D  23 D is engaged and the torque transmitting member of cone assembly CS 3 C  23 C is about to come into engagement. 
   For proper operation the adjuster need to be fast enough such that it can provide proper adjustments during the engagement status or engagement status duration described in the previous paragraph. The required speed for the adjuster can be estimated by first determining the sum of the maximum rpm of the shaft on which the cone assemblies are mounted and the maximum speed of transmission ratio change rotation, which will be discussed latter, and from there calculating the duration of one complete revolution based on that sum, and then multiplying the duration of one complete revolution by the minimum angle the shaft on which the cone assemblies are mounted can be rotated so that only one torque transmitting member is engaged minus the maximum amount of adjustments needed, and then dividing that value by 360 degrees. It is however recommended that the speed of the adjuster is considerably faster than the estimation above. 
   Also, from the transmission ratio sensor, the controlling computer, computer CP 2   122 , can determine the axial position of the torque transmitting members on the surface of their respective cones and from there the arc length of the critical non-torque transmitting arc, which is the surface of the cone assembly about to be engaged, which is not covered by the torque transmitting member and is about to be covered by its transmission belt. This of course assumes that the entire torque transmitting member is toothed. If the torque transmitting member has a portion or portions that are not toothed, such as an extension, than those portions are part of the critical non-torque transmitting arc. Also here it is obviously assumed that the end portions of the torque transmitting member consists of complete tooth shape. A complete tooth shape, which width is the width of a tooth, w t , is a tooth shape that corresponds to a tooth shape that starts at the midpoint of the space between two teeth and ends at the midpoint of the space between two teeth. If the end portions of the torque transmitting member do not consists of a complete tooth, then appropriate adjustments have to be made to the critical non-torque transmitting arc. For example, if one end portion of the torque transmitting member which is forming one end of the critical non-torque transmitting arc consists of a ⅔ complete tooth shape, than the other ⅓ of that tooth shape should be considered as part of the torque transmitting member instead of part of the critical non-torque transmitting arc so that the arc length of that ⅓ of a complete tooth shape should be subtracted from the arc length of critical non-torque transmitting arc. 
   A cone assembly can be viewed as a partial gear, which pitch-line is located at the neutral-axis or bending-axis, if it is a chain, of the torque transmitting member which in most cases is also where the height center-line of the teeth of its torque transmitting member is located, for the transmission belt described in the Alternate CVT&#39;s section of this patent, its pitch-line is located at the at the center of the pins, which when engaged with its torque transmitting member coincides with the pitch-line of its torque transmitting member. For a series of gears with different diameters of the same pitch, the width of a tooth, w t , remains constant at the pitch-line. Since for a cone assembly, the pitch of its torque transmitting member should also remain constant as it is positioned at different diameters, here the width of a tooth, w t , should also remains constant at the pitch-line for different diameters of its torque transmitting member. Also, when a torque transmitting member is fully engaged with its transmission belt, the pitch-line of the torque transmitting member and the pitch-line of the transmission belt should coincide. 
   In order to have a width of a tooth, w t , value that remains constant for different diameters of the torque transmitting members, the length of the critical non-torque transmitting arc should be measured at the pitch-line of the torque transmitting member of its cone assembly; so that the width of a tooth, w t , as shown on the vertical-axis and horizontal-axis of the graphs in FIGS.  21 A/B/C corresponds to the width of a tooth as measured at the pitch-line. As described earlier, a complete tooth shape, which width is the width of a tooth, w t , is a tooth shape that correspond to a tooth shape that starts at the midpoint of the space between two teeth and ends at the midpoint of the space between two teeth; this is true regardless circumferential-line used to measure the arc length of the critical non-torque transmitting arc. 
   Obviously, the arc length of the critical non-torque transmitting arc can be measured at a different circumferential-line, but then the width of a tooth, w t , as shown on the vertical-axis of the graphs in FIGS.  21 A/B/C should also be measured at the circumferential-line at which the length of the critical non-torque transmitting arc is measured. And if the circumferential-line does not coincide with the pitch-line, the width of a tooth changes as the transmission ratio is changed. For optimum performance, the controlling computer, computer CP 2   122 , should be programmed so that it can determine or estimate the width of a tooth at each transmission ratio. A competent engineer should be able do determine the equation that determines or estimates the width of a tooth at a desired circumferential-line as a function of the diameter of its torque transmitting member, which can be derived by the fact that the width of a tooth at a desired circumferential-line is “the width of a tooth at the neutral-axis of the torque transmitting member” multiplied by “the radius of the desired circumferential-line” divided by “the radius of the neutral-axis of the torque transmitting member”. Once the equation is obtained, it can be programmed into the controlling computer so that it can determine the width of a tooth, w t , at each transmission ratio. However, unless otherwise stated for this application the length of the critical non-torque transmitting arc is always measured at the pitch-line of the torque transmitting member of its cone assembly. 
   The controlling computer, computer CP 2   122 , will then use this information and the data from FIGS.  21 A/B/C to control adjuster AD 3   103  to reduce transition flexing. The equation for the engagement coverage of the torque transmitting members as a function of the transmission ratio, and the equation for the arc length of the critical non-torque transmitting arc as a function of the transmission ratio can easily be obtained or estimated experimentally and/or mathematically based on the length of the torque transmitting members and then programmed into the controlling computer. 
   The engagement statuses can also be used when adjuster AD 3   103  is used to increase the duration at which the transmission ratio can be changed. Here engagement statuses  2 ,  4 ,  6 , and  8 , act as transition engagement statuses where the adjuster(s) and the transmission ratio changing actuator, if required, perform no operation so that they can come to a halt so that they are ready to perform their next task. 
   As described earlier, in order to reduce transition flexing, the rotational position of transmission pulley PU 1 C  41 C relative to transmission pulley PU 1 D  41 D needs to be monitored by the controlling computer, computer CP 2   122 . In order to achieve this rotational position sensor SN 2 C  132 C and rotational position sensor SN 2 D  132 D, or a relative rotational position sensor that monitors the rotation between the adjuster body and the adjuster output member of adjuster AD 3   103  can be used. The relative rotational position sensor can also utilize the sensor wheel and counter described previously. In addition, adjuster AD 3   103  should be connected to the controlling computer so that the controlling computer knows the direction the adjuster is rotating one transmission pulley relative to the other, such as rotating transmission pulley PU 1 D  41 D clockwise relative to transmission pulley PU 1 C  41 C or rotating transmission pulley PU 1 D  41 D counter-clockwise relative to transmission pulley PU 1 C  41 C for example. Two values from the data from the rotational position sensors or the relative rotational position sensor should be determined and monitored by the controlling computer. The first value is the “phase for cone assembly CS 3 C  23 C” value. This value represents the phase between cone assembly CS 3 C  23 C and its transmission belt. The second value is the “phase for cone assembly CS 3 D  23 D” value. This value represents the phase between cone assembly CS 3 D  23 D and its transmission belt. In order to determine the “phase for cone assembly CS 3 C  23 C” and the “phase for cone assembly CS 3 D  23 D” values, first the value for the amount of adjustment needed in order to rotate one transmission pulley from a position where its teeth are aligned with the teeth of the other transmission pulley, to the next position where its teeth are aligned with the teeth of the other transmission pulley needs to be determined. Once this value is obtained, it should be used to program the controlling computer so that the values for the “phase for cone assembly CS 3 C  23 C” and the “phase for cone assembly CS 3 D  23 D” values are zero when the teeth of one transmission pulley are aligned with the teeth of the other transmission pulley, and reset to zero each time the adjuster has rotated one transmission pulley relative to the other transmission pulley such that the teeth of the transmission pulleys are aligned again. And for all other relative rotational positions between the transmission pulleys, the controlling computer via the data from the rotational position sensor should determine the angle a transmission pulley has been rotated relative to the other transmission pulley. For the value for the “phase for cone assembly CS 3 C  23 C”, if the rotational position of transmission pulley PU 1 C  41 C is adjusted relative to the rotational position of transmission pulley PU 1 D  41 D so that its transmission belt is moved away from its torque transmitting member, torque transmitting member CS 3 C-M 1   23 C-M 1 , which is about to be engaged, which for a configuration of CVT where the transmission pulleys are rotating clockwise corresponds to adjustments where transmission pulley PU 1 C  41 C is rotated counter-clockwise relative to transmission pulley PU 1 D  41 D, a positive value is assigned for the angle measurement that transmission pulley PU 1 C  41 C has been rotated relative to transmission pulley PU 1 D  41 D from an initial position where the teeth of the transmission pulleys are aligned. As described above, this angle measurement resets to zero each time the teeth of the transmission pulleys are aligned again. This angle measurement is the value for the “phase for cone assembly CS 3 C  23 C”. So basically, the “phase for cone assembly CS 3 C  23 C” represents the angle between the teeth of transmission pulley PU 1 C  41 C and the teeth of transmission pulley PU 1 D  41 D where the teeth of transmission pulley PU 1 C  41 C are positioned behind the teeth of transmission pulley PU 1 D  41 D according to the direction the transmission pulleys are rotating. Also, for the “phase for cone assembly CS 3 C  23 C”, if the rotational position of transmission pulley PU 1 C  41 C is adjusted relative to the rotational position of transmission pulley PU  41 D so that its transmission belt is moved towards its torque transmitting member, torque transmitting member CS 3 C-M 1   23 C-M 1 , which is about to be engaged, which for a configuration of CVT where the transmission pulleys are rotating clockwise corresponds to adjustments where transmission pulley PU 1 C  41 C is rotated clockwise relative to transmission pulley PU  41 D, the “phase for cone assembly CS 3 C  23 C” is obtained by subtracting “the angle measurement transmission pulley PU 1 C  41 C has been rotated relative to transmission pulley PU 1 D  41 D from an initial position where the teeth of the transmission pulleys are aligned” from “the value for the amount of adjustment needed in order to rotate one transmission pulley from a position where its teeth are aligned with the teeth of the other transmission pulley, to the next position where its teeth are aligned with the teeth of the other transmission pulley”. Also in case the transmission pulleys are rotating counter-clockwise, then in order to move the transmission belt for cone assembly CS 3 C  23 C away from its torque transmitting member which is about to be engaged, transmission pulley PU 1 C  41 C has to be rotated clockwise relative to transmission pulley PU 1 D  41 D; and in case the transmission pulleys are rotating counter-clockwise, then in order to move the transmission belt for cone assembly CS 3 C  23 C towards its torque transmitting member which is about to be engaged, transmission pulley PU 1 C  41 C has to be rotated counter-clockwise relative to transmission pulley PU 1 D  41 D. Here and in the previous description using the terms moved away and moved towards, moved away means that the transmission belt about to be engaged is rotated in the opposite direction the cone assemblies are rotating; and moved towards means that the transmission belt about to be engaged is rotated in the direction the cone assemblies are rotating. The “phase for cone assembly CS 3 D  23 D” represents the angle between the teeth of transmission pulley PU 1 D  41 D and the teeth of transmission pulley PU 1 C  41 C where the teeth of transmission pulley PU  41 D are positioned behind the teeth of transmission pulley PU 1 C  41 C according to the direction the transmission pulleys are rotating. The method to obtain the “phase for cone assembly CS 3 D  23 D” is identical to the method to obtain the “phase for cone assembly CS 3 C  23 C”. So here if transmission pulley PU 1 D  41 D is rotated in the opposite direction the cone assemblies are rotating relative to transmission pulley PU 1 C  41 C, the “phase for cone assembly CS 3 D  23 D” is the angle measurement transmission pulley PU 1 D  41 D has been rotated relative to transmission pulley PU 1 C  41 C from an initial position where the teeth of the transmission pulleys are aligned. Like the “phase for cone assembly CS 3 C  23 C”, the “phase for cone assembly CS 3 D  23 D” resets to zero each time the adjuster has rotated one transmission pulley relative to the other transmission pulley such that the teeth of the transmission pulleys are aligned again. And if transmission pulley PU 1 D  41 D is rotated in the direction the cone assemblies are rotating relative to transmission pulley PU 1 C  41 C, the “phase for cone assembly CS 3 D  23 D” is obtained by subtracting “the angle measurement transmission pulley PU 1 D  41 D has been rotated relative to transmission pulley PU 1 C  41 C from an initial position where the teeth of the transmission pulleys are aligned” from “the value for the amount of adjustment needed in order to rotate one transmission pulley from a position where its teeth are aligned with the teeth of the other transmission pulley, to the next position where its teeth are aligned with the teeth of the other transmission pulley”. 
   From the angular values for the “phase for cone assembly CS 3 C  23 C” and “phase for cone assembly CS 3 D  23 D” and the pitch diameter of the transmission pulleys, the controlling computer should determine and monitor the correspond arc lengths, which should be measured at the pitch-lines of the portions of the transmission belts fully engaged with their transmission pulleys, of those angular values. The arc length for the “phase for cone assembly CS 3 C  23 C” will be referred to as the “phase arc length for cone assembly CS 3 C  23 C” and the arc length for the “phase for cone assembly CS 3 D  23 D” will be referred to as the “phase arc length for cone assembly CS 3 D  23 D”. 
   In FIGS.  21 A/B/C the vertical-axis shows the arc length of adjustment required in order to reduce transition flexing, and the horizontal-axis shows the arc length of the critical non-torque transmitting arc. As described earlier the same adjustment method used for a CVT  1 , such as CVT  1 . 1 , can also be for a CVT  2 , such as CVT  2 . 1 . Obviously since CVT  2 . 1  has two transmission belts, while CVT  1 . 1  only has one, for CVT  2 . 1  before any adjustment is made, the teeth of its transmission belts need to be aligned so that they resemble one transmission belt. Also for CVT  1 . 1 , the arc length of the critical non-torque transmitting arc is the space between the torque transmitting members that is about to be covered by its transmission belt, if the same adjustment method used for CVT  1 . 1  is used for CVT  2 . 1 , then the corresponding arc length of the critical non-torque transmitting arc needs to be used for CVT  2 . 1 ; so that for CVT  2 . 1  the arc length of the critical non-torque transmitting arc is also the space between the torque transmitting members, which should be measured at the pitch-line of the torque transmitting members, that is about to be covered by its transmission belt. Since for CVT  2 . 1  the rotational position of one torque transmitting member relative to the other torque transmitting member is fixed, the arc length of the critical non-torque transmitting arc is simply (“the circumference of the entire surface of either the cone for cone assembly CS 3 C  23 C or the cone for cone assembly CS 3 D  23 D as measured at the pitch-line of their torque transmitting members” minus “the arc length of the torque transmitting member of cone assembly CS 3 C  23 C as measured at the pitch-line of the torque transmitting member” minus “the arc length of the torque transmitting member of cone assembly CS 3 D  23 D as measured at the pitch-line of the other torque transmitting members”) divided by two. 
   Since for CVT  2 . 1  the phase or rotational position of one transmission pulley relative to the other instead of the rotational position of one torque transmitting member relative to the other needs to be known, a slightly different approach referred to as the “adjustment phase” method might be more practical. For the “adjustment phase” method, if the graph show in  FIG. 21A  is used for cone assembly CS 3 C  23 C then the vertical-axis value shows the required “phase arc length for cone assembly CS 3 C  23 C”, and the horizontal-axis value shows the arc length of the critical non-torque transmitting arc. And if the graph show in  FIG. 21A  is used for cone assembly CS 3 D  23 D then the vertical-axis value shows the required “phase arc length for cone assembly CS 3 D  23 D”, and the horizontal-axis value shows the arc length of the critical non-torque transmitting arc. Hence by using the graph show in  FIG. 21A , the arc length of the critical non-torque transmitting arc as determined by the controlling computer from the data from the transmission ratio sensor, the “phase arc length for cone assembly CS 3 C  23 C”, the “phase arc length for cone assembly CS 3 D  23 D”, and the engagement statuses, the controlling computer can control adjuster AD 3   103  to reduce transition flexing; in order to reduce transition flexing, the arc length of the critical non-torque transmitting arc, the “phase arc length for cone assembly CS 3 C  23 C”, the “phase arc length for cone assembly CS 3 D  23 D”, and the engagement statuses should be monitored continuously by the controlling computer, computer CP 2   122 . Regarding the engagement statuses, for engagement status  1  (only the torque transmitting member of cone assembly CS 3 C  23 C is engaged) and engagement status  2  (the torque transmitting member of cone assembly CS 3 C  23 C is engaged and the torque transmitting member of cone assembly CS 3 D  23 D is about to come into engagement), if used, the “phase arc length for cone assembly CS 3 D  23 D” should match the vertical-axis value of the graph show in  FIG. 21A , while the horizontal-axis value of that graph should correspond to the arc length of the critical non-torque transmitting arc. And for engagement status  5  (only the torque transmitting member of cone assembly CS 3 D  23 D is engaged) and engagement status  6  (the torque transmitting member of cone assembly CS 3 D  23 D is engaged and the torque transmitting member of cone assembly CS 3 C  23 C is about to come into engagement), if used, the “phase arc length for cone assembly CS 3 C  23 C” should match the vertical-axis value of the graph show in  FIG. 21A , while the horizontal-axis value of that graph should correspond to the arc length of the critical non-torque transmitting arc. Also, the method to reduce transition flexing described in this paragraph applies to operations where the transmission ratio is not changed. A detailed control scheme to reduce transition flexing during transmission ratio change will be described latter. 
   It is recommended that CVT  2 . 1  is designed so that at the lowest (start-up) transmission ratio, no adjustment is required, so that the controlling computer does not need to know the “phase arc length for cone assembly CS 3 C  23 C” and the “phase arc length for cone assembly CS 3 D  23 D” during start-up. It is recommended that CVT  1 . 1  is designed in the same manner. 
   It does not matter in what direction the adjuster rotates one transmission pulley relative to the other as long as the proper phase is obtained. The controlling computer can be programmed so that it only rotates one transmission pulley relative to the other in one direction, preferably in the opposite direction the cone assemblies are rotating so that the adjuster only needs to slip; or the controlling computer can be programmed so that it rotates one transmission pulley relative to the other in the direction that requires the least amount of adjustment for example. For least amount of adjustment, if the “phase arc length for cone assembly CS 3 C  23 C” and the “phase arc length for cone assembly CS 3 D  23 D” is less or equal to “the value for the amount of adjustment needed in order to rotate one transmission pulley from a position where its teeth are aligned with the teeth of the other transmission pulley, to the next position where its teeth are aligned with the teeth of the other transmission pulley” divided by two, the controlling computer should be programmed so that the transmission belt about to be engaged is moved away from its torque transmitting member; and if the “phase arc length for cone assembly CS 3 C  23 C” and the “phase arc length for cone assembly CS 3 D  23 D” is greater than “the value for the amount of adjustment needed in order to rotate one transmission pulley from a position where its teeth are aligned with the teeth of the other transmission pulley, to the next position where its teeth are aligned with the teeth of the other transmission pulley” divided by two, the controlling computer should be programmed so that the transmission belt about to be engaged is moved towards its torque transmitting member. 
   And although the following adjustment is not critical and can be omitted, the performance of the CVT can be increased when in instances when both torque transmitting members are in contact with their transmission belt, adjuster AD 3 A  103 A is used to adjust the rotational position between the transmission pulleys so as to properly adjust the torque applied to each transmission pulley so that the torque rating and/or the durability of the CVT is maximized. One method is to have adjuster AD 3   103  try to evenly distribute the load on each tooth. In order to achieve this, the rotational position sensor is used to estimate the amount of teeth of each transmission pulley that is transmitting torque at that instance, and the torque sensors can be used to determine the load on each transmission pulley. And by dividing the measured load on a transmission pulley by its estimated amount of teeth, the load on each of its teeth can be estimated. Another method is to have adjuster AD 3   103  try to maintain an even tension in the transmission belts. 
   Furthermore, although the following is also not critical and can be omitted, the torque sensors SN 4 C  134 C and SN 4 D  134 D can also be used as a diagnostic device that ensures the proper operation of adjuster AD 3   103  in trying to eliminate transition flexing. For instance, when under non-transmission ratio changing operation the reading of torque sensor SN 4 C  134 C when only transmission pulley PU 1 C  41 C is transmitting torque is significantly different than the reading of torque sensor SN 4 D  134 D when only transmission pulley PU 1 D  41 D is transmitting torque, or when the reading of a torque sensor is excessively high, the controlling computer of the CVT can take corrective actions and safety steps that prevents or minimizes damages to the CVT, such as adjusting the adjustment provided in order to reduce transition flexing, or signaling warnings, or initiating shutdowns. 
   The reason why adjuster AD 3   103  is needed in order to substantially increase the duration at which the transmission ratio can be changed is because of transmission ratio change rotation. Transmission ratio change rotation is rotation of a cone assembly that occurs when the axial position of its torque transmitting member is changed while it is in contact with its transmission belt. In order to help explain transition ratio change rotation, the points where the transmission belts first touch the upper surface of their cone assemblies will be referred to as points N. Here points N are neutral points, which are points where almost no sliding between the transmission belts and the surface of their cone assembly occur when the pitch diameter of the cone assemblies are changed, regardless of the rotational position of the torque transmitting members. This is because the lengths of the transmission belts from their point N to the points where the horizontal mirror lines of the transmission pulleys intersect the surfaces of the transmission pulleys remain almost constant as the transmission ratio is changed, since the center distance between the cone assemblies and the transmission pulleys do not change; however this is only true for reasonably small changes in pitch diameter of the cone assemblies. And point N is also the neutral point because changes in the pitch diameter of the cone assemblies do not affect the portions of the transmission belts that are not in contact with a cone assembly. 
   Note, for other configurations of a CVT, point N might be positioned elsewhere. For CVT&#39;s that utilizes transmission pulleys, a point N is most likely located at a point that corresponds to the end point of a portion of a transmission belt which length from the point where the horizontal mirror line of a transmission pulley intersect the surface of that transmission pulley to point N remains almost constant as the pitch diameter of its cone assembly is changed. For different configurations of CVT&#39;s, the location of point N can easily be determined experimentally, by simply determining the point where almost no sliding between the transmission belt and the surface of its cone assembly occur as the pitch diameter of the cone assembly is changed. 
   When the midpoint of the torque transmitting member is not positioned at point N, then significant transmission ratio change rotation occurs. The amount of transmission ratio change rotation depends on the angle θ, which is the angle between the midpoint of the torque transmitting member, referred to as point M, and point N. And the direction of transmission ratio change rotation depends on whether the midpoint of the torque transmitting member is positioned to the left or to the right of point N, and on whether the pitch diameter of the torque transmitting member is increased or decreased. The reason that transmission ratio change rotation has to occur is because if no slippage between the torque transmitting member and the transmission belt is allowed, then the arc length between point N and the midpoint of the torque transmitting member, point M, has to remain constant regardless of the pitch diameter. For a given initial angle θ 1 , initial radius R 1 , and final radius R 2 , the transmission ratio change rotation, Δθ, can be determined from the equation shown in  FIG. 25 . From the equation shown in  FIG. 25 , it can be seen that the transmission ratio change rotation, Δθ, increases with an increase in initial angle θ 1 . Also from  FIGS. 24A-24D , where the initial angle θ 1  is simply labeled as θ, it can be observed that clockwise transmission ratio change rotation occurs when the pitch diameter is increased and the center of the torque transmitting member is positioned to the left of point N, see  FIG. 24D , and when the pitch diameter is decreased and the center of the torque transmitting member is positioned to the right of point N, see  FIG. 24A . And counter-clockwise transmission ratio change rotation occur when the pitch diameter is increased and the center of the torque transmitting member is positioned to the right of point N, see  FIG. 24B , and when the pitch diameter is decreased and the center of the torque transmitting member is positioned to the left of point N, see  FIG. 24C . 
   Furthermore, because of the configuration of CVT  2 . 1 , in instances where both torque transmitting member CS 3 C-M 1   23 C-M 1  and torque transmitting member CS 3 D-M 1   23 D-M 1  are in contact with their transmission belt, the transmission ratio change rotation for cone assembly CS 3 C  23 C is different from that of cone assembly CS 3 D  23 D. Hence in order to allow the transmission ratio to be changeable when both torque transmitting members are in contact with their transmission belts, compensating relative rotation between either the cone assemblies or the transmission pulleys has to occur. As described earlier, the relative rotational position between the cone assemblies will not be changed, since it is desired to keep the rotational position of torque transmitting member CS 3 D-M 1   23 D-M 1  opposite or close to opposite from the rotational position of torque transmitting member CS 3 C-M 1   23 C-M 1 . Therefore, in order to compensate for the transmission ratio change rotation, adjuster AD 3   103  is used to adjust the rotational position of transmission pulley PU 1 C  41 C relative to transmission pulley PU 1 D  41 D. In order to compensate for the transmission ratio change rotation, adjuster AD 3   103  is used to rotate transmission pulley PU 1 C  41 C relative to transmission pulley PU 1 D  41 D such that the pulling loads on the transmission pulleys, as measured by torque sensor SN 4 C  134 C and torque sensor SN 4 D  134 D, are about equal. 
   Besides eliminating transition flexing and compensating for transmission ratio change rotation, the adjuster system for CVT  2 . 1  can also be used to compensate for wear that causes unequal pulling loads in the alternating transmission pulleys. 
   The rotational movements between transmission pulley PU 1 C  41 C and transmission pulley PU 1 D  41 D for different rotational positions and transmission ratio changes (increasing/decreasing) as to compensate for transmission ratio change rotation, and the rotational movements between transmission pulley PU 1 C  41 C and transmission pulley PU 1 D  41 D as to eliminate or reduce transition flexing, when the input shaft is rotated clock-wise are described below: 
   —Decreasing Pitch Diameter and Torque Transmitting Member CS 3 C-M 1   23 -M 1  on Upper Half ( FIGS. 26A-26C ) 
   Here while Torque Transmitting Member Cs 3 C-M 1   23 C-M 1  is Engaged and Torque transmitting member CS 3 D-M 1   23 D-M 1  is not engaged with its transmission belt, adjuster AD 3   103  is used to reduce transition flexing. This situation corresponds to engagement status  1  (only the torque transmitting member of cone assembly CS 3 C  23 C is engaged) and engagement status  2  (the torque transmitting member of cone assembly CS 3 C  23 C is engaged and the torque transmitting member of cone assembly CS 3 D  23 D is about to come into engagement). In order to have a pause between the different operations of adjuster AD 3 A  103 A, which are reducing transition flexing and compensating for transmission ratio change rotation, only engagement status  1  should be used to reduce transition flexing and to change the transmission ratio. Hence adjuster AD 3 A  103 A and the transmission ratio changing actuator are not in operation during engagement status  2 . If no pause is desired than engagement status  1  and engagement status  2  should be used to reduce transition flexing and to change the transmission ratio. In this instance adjuster AD 3   103  is not used to compensate for transmission ratio change rotation, despite the fact that due to transition ratio change rotation the cone assemblies are rotated counter-clockwise. Since here only one torque transmitting member is in contact with its transmission belt, transmission ratio change rotation does not cause excessive stretching of the transmission belts. And some counter-clockwise rotation of the cone assemblies, which causes slippage at the output shaft, slightly reduces the performance of the CVT, but is not damaging the CVT. A detailed control scheme to reduce transition flexing during transmission ratio change is described after the rotational movements between the transmission pulleys for different rotational positions and transmission ratio changes description. 
   And once both torque transmitting member CS 3 C-M 1   23 C-M 1 , which is positioned on the upper half, and torque transmitting member CS 3 D-M 1   23 D-M 1  are in contact with their transmission belts, see  FIGS. 26A-26C , it can be observed that here when point M of torque transmitting member CS 3 C-M 1   23 C-M 1  is positioned to the right of point N, see  FIG. 26A , the transmission ratio change rotation of cone assembly CS 3 C-M 1   23 C-M 1  is clockwise; and when torque transmitting member CS 3 C-M 1   23 C-M 1  is positioned to the left of point N, see  FIG. 26B , the transmission ratio change rotation of cone assembly CS 3 C  23 C is counter-clockwise. And in this case, the transmission ratio change rotation of cone assembly CS 3 D  23 D is always counter-clockwise, see  FIG. 26D . From  FIGS. 26B and 26C  it can be seen that here if torque transmitting member CS 3 C-M 1   23 C-M 1  is positioned to the left of point N, θ of cone assembly CS 3 D  23 D is always greater than θ of cone assembly CS 3 C  23 C. Hence, regardless of whether the transmission ratio change rotation of cone assembly CS 3 C  23 C is clockwise or counter-clockwise, here changing the transmission ratio causes cone assembly CS 3 D  23 D to rotate counter-clockwise relative to cone assembly CS 3 C  23 C. In order to compensate for the transmission ratio change rotation, adjuster AD 3   103  needs to rotate transmission pulley PU 1 C  41 C counter-clockwise relative to transmission pulley PU 1 D  41 D. As discussed previously, here the pulling load in the transmission pulleys PU 1 C  41 C and PU 1 D  41 D will be used to control the rotation of adjuster AD 3   103 . Here once the pulling load in transmission pulley PU 1 D  41 D falls below a preset low limit value relative to the pulling load in transmission pulley PU 1 C  41 C, the adjuster AD 3   103  rotates transmission pulley PU 1 C  41 C counter-clockwise relative to transmission pulley PU 1 D  41 D. And once the difference in pulling load between transmission pulley PU 1 D  41 D and transmission pulley PU 1 C  41 C has reached an acceptable preset value, the adjuster AD 3   103  stops rotating. In  FIGS. 26A and 26B , the rotation provided by adjuster AD 3   103  is labeled as ω A . Also, here the pulling load is the load that tends to rotate a transmission pulley counter-clock-wise. In instances where the adjuster AD 3   103  is not providing sufficient adjustment, in order to prevent excessive flexing of the transmission belts, the transmission ratio changing actuator should stall. Also if desired, in instances where the pulling load in transmission pulley PU 1 D  41 D falls below a lower preset low limit value relative to the pulling load in transmission pulley PU 1 C  41 C, the transmission ratio changing actuator can be temporarily stopped until adjuster AD 3   103  has reduced the difference in pulling load between transmission pulley PU 1 D  41 D and transmission pulley PU 1 C  41 C to a corresponding acceptable preset value. This situation corresponds to engagement status  3  (the torque transmitting member of cone assembly CS 3 C  23 C and the torque transmitting member of cone assembly CS 3 D  23 D are engaged), and engagement status  4  (the torque transmitting member of cone assembly CS 3 C  23 C is about to come out of engagement and the torque transmitting member of cone assembly CS 3 D  23 D is engaged). In order to have a pause between the different operations of adjuster AD 3 A  103 A, which are reducing transition flexing and compensating for transmission ratio change rotation, only engagement status  3  should be used to compensate for transmission ratio change rotation and to change the transmission ratio. Hence adjuster AD 3 A  103 A and the transmission ratio changing actuator are not in operation during engagement status  4 . If no pause is desired than engagement status  3  and engagement status  4  should be used to reduce transition flexing and to change the transmission ratio. 
   And once torque transmitting member CS 3 C-M 1   23 C-M 1  comes out of contact with its transmission belt, during transmission ratio change as during non-transmission ratio change operation, adjuster AD 3   103  is used to reduce transition flexing. This situation corresponds to engagement status  5  (only the torque transmitting member of cone assembly CS 3 D  23 D is engaged), and engagement status  6  (the torque transmitting member of cone assembly CS 3 D  23 D is engaged and the torque transmitting member of cone assembly CS 3 C  23 C is about to come into engagement). In order to have a pause between the different operations of adjuster AD 3 A  103 A, which are reducing transition flexing and compensating for transmission ratio change rotation, only engagement status  5  should be used to compensate for transmission ratio change rotation and to change the transmission ratio. Hence adjuster AD 3 A  103 A and the transmission ratio changing actuator are not in operation during engagement status  6 . If no pause is desired than engagement status  5  and engagement status  6  should be used to reduce transition flexing and to change the transmission ratio. Since in this instance only one torque transmitting member is contact with its transmission belt, it is not necessary for adjuster AD 3   103  to compensate for transmission ratio change rotation, despite the fact that due to transmission ratio change rotation, cone assembly CS 3 D  23 D, and hence output shaft SH 8   18  are rotated counter-clockwise. Since some counter-clockwise rotation applied to cone assembly CS 3 D  23 D, which causes slippage at the output shaft SH 8   18 , slightly reduces the performance of the CVT but is not damaging the CVT. A detailed control scheme to reduce transition flexing during transmission ratio change is described after the rotational movements between the transmission pulleys for different rotational positions and transmission ratio changes description. 
   —Decreasing Pitch Diameter and Torque Transmitting Member CSC 3 C-M 1   23 C-M 1  on Lower Half ( FIGS. 27A &amp; 27B ) 
   Here while torque transmitting member CS 3 C-M 1   23 C-M 1  is not engaged with its transmission belt, adjuster AD 3   103  is used to reduce transition flexing. This situation corresponds to engagement status  5  (only the torque transmitting member of cone assembly CS 3 D  23 D is engaged) and engagement status  6  (the torque transmitting member of cone assembly CS 3 D  23 D is engaged and the torque transmitting member of cone assembly CS 3 C  23 C is about to come into engagement). In order to have a pause between the different operations of adjuster AD 3 A  103 A, which are reducing transition flexing and compensating for transmission ratio change rotation, only engagement status  5  should be used to reduce transition flexing and to change the transmission ratio. Hence adjuster AD 3 A  103 A and the transmission ratio changing actuator are not in operation during engagement status  6 . If no pause is desired than engagement status  5  and engagement status  6  should be used to reduce transition flexing and to change the transmission ratio. Since in this instance only one torque transmitting member is in contact with its transmission belt, it is not necessary for adjuster AD 3   103  to compensate for transmission ratio change rotation, despite the fact that due to transition ratio change rotation the cone assemblies are rotated counter-clockwise. Since some counter-clockwise rotation of the cone assemblies, which causes slippage at the output shaft, slightly reduces the performance of the CVT but is not damaging the CVT. A detailed control scheme to reduce transition flexing during transmission ratio change is described after the rotational movements between the transmission pulleys for different rotational positions and transmission ratio changes description. 
   And once both torque transmitting member CS 3 C-M 1   23 C-M 1 , which is positioned on the lower half, and torque transmitting member CS 3 D-M 1   23 D-M 1  are in contact with their transmission belt, see  FIGS. 27A &amp; 27B , adjuster AD 3   103  is used to compensate for transmission ratio change rotation. By using the same method described in the previous section, where torque transmitting member CS 3 C-M 1   23 C-M 1  is positioned on the upper half and both torque transmitting members are in contact with their transmission belt, it becomes clear that here in order to compensate for the transmission ratio change rotation, the adjuster AD 3   103  needs to rotate transmission pulley PU  41 C clockwise relative to transmission pulley PU 1 D  41 D. As discussed previously, here the pulling load in the transmission pulleys PU  41 C and PU 1 D  41 D will be used to control the rotation of adjuster AD 3   103 . Here once the pulling load in transmission pulley PU 1 D  41 D increases above a preset high limit value relative to the pulling load in transmission pulley PU 1 C  41 C, the adjuster AD 3   103  rotates transmission pulley PU 1 C  41 C clockwise relative to transmission pulley PU 1 D  41 C. And once the difference in pulling load between the transmission pulleys has reached an acceptable preset value, adjuster AD 3   103  stops rotating. In instances where the adjuster AD 3   103  is not providing sufficient adjustment, in order to prevent excessive flexing of the transmission belts, the transmission ratio changing actuator should stall. Also if desired, in instances where the pulling load in transmission pulley PU 1 D  41 D increases above a higher preset high limit value relative to the pulling load in transmission pulley PU 1 C  41 C, the transmission ratio changing actuator can be temporarily stopped until adjuster AD 3   103  has reduced the difference in pulling load between transmission pulley PU 1 D  41 D and transmission pulley PU  41 C to a corresponding acceptable preset value. This situation corresponds to engagement status  7  (the torque transmitting member of cone assembly CS 3 D  23 D and the torque transmitting member of cone assembly CS 3 C  23 C are engaged), and engagement status  8  (the torque transmitting member of cone assembly CS 3 D  23 D is about to come out of engagement and the torque transmitting member of cone assembly CS 3 C  23 C is engaged). In order to have a pause between the different operations of adjuster AD 3 A  103 A, which are reducing transition flexing and compensating for transmission ratio change rotation, only engagement status  7  should be used to compensate for transmission ratio change rotation and to change the transmission ratio. Hence adjuster AD 3 A  103 A and the transmission ratio changing actuator are not in operation during engagement status  8 . If no pause is desired than engagement status  7  and engagement status  8  should be used to reduce transition flexing and to change the transmission ratio. 
   And once torque transmitting member CS 3 D-M 1   23 D-M 1  comes out of contact with its transmission belt, adjuster AD 3   103  is used to reduce transition flexing. This situation corresponds to engagement status  1  (only the torque transmitting member of cone assembly CS 3 C  23 C is engaged), and engagement status  2  (the torque transmitting member of cone assembly CS 3 C  23 C is engaged and the torque transmitting member of cone assembly CS 3 D  23 D is about to come into engagement). In order to have a pause between the different operations of adjuster AD 3 A  103 A, which are reducing transition flexing and compensating for transmission ratio change rotation, only engagement status  1  should be used to compensate for transmission ratio change rotation and to change the transmission ratio. Hence adjuster AD 3 A  103 A and the transmission ratio changing actuator are not in operation during engagement status  2 . If no pause is desired than engagement status  1  and engagement status  2  should be used to reduce transition flexing and to change the transmission ratio. Since in this instance only one torque transmitting member is in contact with its transmission belt, adjuster AD 3   103  is not used to compensate for transmission ratio change rotation, despite the fact that transmission ratio change rotation rotates cone assembly CS 3 C-M 1   23 C-M 1 , and hence output shaft SH 8   18 , counter-clockwise. Since some counter-clockwise rotation applied to cone assembly CS 3 C  23 C, which causes slippage at the output shaft SH 8   18 , slightly reduces the performance of the CVT but is not damaging the CVT. A detailed control scheme to reduce transition flexing during transmission ratio change is described after the rotational movements between the transmission pulleys for different rotational positions and transmission ratio changes description. 
   —Increasing Pitch Diameter and Torque Transmitting Member CS 3 C-M 1   23 C-M 1  on Upper Half ( FIGS. 28A &amp; 28B ) 
   Here while torque transmitting member CS 3 C-M 1   23 C-M 1  is engaged and torque transmitting member CS 3 D-M 1   23 D-M 1  is not engaged with its transmission belt, adjuster AD 3   103  is used to reduce transition flexing. This situation corresponds to engagement status  1  (only the torque transmitting member of cone assembly CS 3 C  23 C is engaged) and engagement status  2  (the torque transmitting member of cone assembly CS 3 C  23 C is engaged and the torque transmitting member of cone assembly CS 3 D  23 D is about to come into engagement). In order to have a pause between the different operations of adjuster AD 3 A  103 A, which are reducing transition flexing and compensating for transmission ratio change rotation, only engagement status  1  should be used to reduce transition flexing and to change the transmission ratio. Hence adjuster AD 3 A  103 A and the transmission ratio changing actuator are not in operation during engagement status  2 . If no pause is desired than engagement status  1  and engagement status  2  should be used to reduce transition flexing and to change the transmission ratio. Since in this instance only one torque transmitting member is in contact with its transmission belt, the adjuster AD 3   103  is not used to compensate for transmission ratio change rotation, despite the fact that due to transition ratio change rotation the cone assemblies are rotated clockwise, for the same reason discussed earlier. A detailed control scheme to reduce transition flexing during transmission ratio change is described after the rotational movements between the transmission pulleys for different rotational positions and transmission ratio changes description. 
   And once both, torque transmitting member CS 3 C-M 1   23 C-M 1 , which is positioned on the upper half, and torque transmitting member CS 3 D-M  123 D-M 1  are in contact with their transmission belts, see  FIGS. 28A &amp; 28B , adjuster AD 3   103  is used to compensate for transmission ratio change rotation. As discussed earlier, here the direction of the transmission ratio change rotation is simply opposite from that were the transmission ratio is decreased. And as described before here a larger angle between the midpoint of a torque transmitting member and point N, results in a larger transmission ratio change rotation. Previously it was described that when the transmission ratio is decreased and torque transmitting member CS 3 C-M 1   23 C-M 1  is positioned on the upper half and both torque transmitting members are in contact with their transmission belt, the adjuster AD 3   103  needs to rotate transmission pulley PU 1 C  41 C counter-clockwise relative to transmission pulley PU 1 D  41 D. Hence in this case, the adjuster AD 3   103  needs to rotate transmission pulley PU 1 C  41 C clockwise relative to transmission pulley PU 1 D  41 D. As discussed previously, here the pulling load in the transmission pulleys will be used to control the compensating rotation of the adjuster AD 3   103 . Here once the pulling load in transmission pulley PU 1 D  41 D increases above a preset high limit value relative to the pulling load in transmission pulley PU 1 C  41 C, the adjuster AD 3   103  rotates transmission pulley PU 1 C  41 C clockwise relative to transmission pulley PU 1 D  41 D. And once the difference in the pulling load between transmission pulleys has reached an acceptable preset value, the adjuster AD 3   103  stops rotating. In instances where the adjuster AD 3   103  is not providing sufficient adjustment, in order to prevent excessive flexing of the transmission belts, the transmission ratio changing actuator should stall. Also if desired, in instances where the pulling load in transmission pulley PU 1 D  41 D increases above a higher preset high limit value relative to the pulling load in transmission pulley PU 1 C  41 C, the transmission ratio changing actuator can be temporarily stopped until adjuster AD 3   103  has reduced the difference in pulling load between transmission pulley PU 1 D  41 D and transmission pulley PU 1 C  41 C to a corresponding acceptable preset value. This situation corresponds to engagement status  3  (the torque transmitting member of cone assembly CS 3 C  23 C and the torque transmitting member of cone assembly CS 3 D  23 D are engaged), and engagement status  4  (the torque transmitting member of cone assembly CS 3 C  23 C is about to come out of engagement and the torque transmitting member of cone assembly CS 3 D  23 D is engaged). In order to have a pause between the different operations of adjuster AD 3 A  103 A, which are reducing transition flexing and compensating for transmission ratio change rotation, only engagement status  3  should be used to compensate for transmission ratio change rotation and to change the transmission ratio. Hence adjuster AD 3 A  103 A and the transmission ratio changing actuator are not in operation during engagement status  4 . If no pause is desired than engagement status  3  and engagement status  4  should be used to reduce transition flexing and to change the transmission ratio. 
   And once torque transmitting member CS 3 C-M 1   23 C-M 1  comes out of contact with its transmission belt, during transmission ratio change as during non-transmission ratio change operation, adjuster AD 3   103  is used to reduce transition flexing. This situation corresponds to engagement status  5  (only the torque transmitting member of cone assembly CS 3 D  23 D is engaged), and engagement status  6  (the torque transmitting member of cone assembly CS 3 D  23 D is engaged and the torque transmitting member of cone assembly CS 3 C  23 C is about to come into engagement). In order to have a pause between the different operations of adjuster AD 3 A  103 A, which are reducing transition flexing and compensating for transmission ratio change rotation, only engagement status  5  should be used to compensate for transmission ratio change rotation and to change the transmission ratio. Hence adjuster AD 3 A  103 A and the transmission ratio changing actuator are not in operation during engagement status  6 . If no pause is desired than engagement status  5  and engagement status  6  should be used to reduce transition flexing and to change the transmission ratio. Since in this instance only one torque transmitting member is in contact with its transmission belt, adjuster AD 3   103  is not used to compensate for transmission ratio change rotation, despite the fact that transmission ratio change rotation rotates cone assembly CS 3 D-M 123 D-M 1 , and hence output shaft SH 8   18 , clockwise. Since some clockwise rotation applied to the output shaft SH 8   18  is not damaging the CVT, and actually increases the total amount of rotation at the output shaft SH 8   18  at the expense of the work provided by the transmission ratio changing actuator. A detailed control scheme to reduce transition flexing during transmission ratio change is described after the rotational movements between the transmission pulleys for different rotational positions and transmission ratio changes description. 
   —Increasing Pitch Diameter and Torque Transmitting Member CS 3 C-M 1   23 C-M 1  on Lower Half ( FIGS. 29A &amp; 29B ) 
   Here while torque transmitting member CS 3 C-M 1   23 C-M 1  is not engaged with its transmission belt, adjuster AD 3   103  is used to reduce transition flexing. This situation corresponds to engagement status  5  (only the torque transmitting member of cone assembly CS 3 D  23 D is engaged) and engagement status  6  (the torque transmitting member of cone assembly CS 3 D  23 D is engaged and the torque transmitting member of cone assembly CS 3 C  23 C is about to come into engagement). In order to have a pause between the different operations of adjuster AD 3 A  103 A, which are reducing transition flexing and compensating for transmission ratio change rotation, only engagement status  5  should be used to reduce transition flexing and to change the transmission ratio. Hence adjuster AD 3 A  103 A and the transmission ratio changing actuator are not in operation during engagement status  6 . If no pause is desired than engagement status  5  and engagement status  6  should be used to reduce transition flexing and to change the transmission ratio. In this instance the adjuster AD 3   103  is not used to compensate for transmission ratio change rotation, despite the fact that due to transition ratio change rotation the cone assemblies are rotated clockwise, for the same reasons discussed earlier. A detailed control scheme to reduce transition flexing during transmission ratio change is described after the rotational movements between the transmission pulleys for different rotational positions and transmission ratio changes description. 
   And once both torque transmitting member CS 3 C-M 1   23 C-M 1 , which is positioned on the lower half, and torque transmitting member CS 3 D-M 1   23 D-M 1  are in contact with their transmission belts, see  FIGS. 29A &amp; 29B , the adjuster AD 3   103  is used to compensate for transmission ratio change rotation. As discussed earlier, here the direction of the transmission ratio change rotation is simply opposite from that were the transmission ratio is decreased. And as described before here a larger angle between the midpoint of a torque transmitting member and point N, results in a larger transmission ratio change rotation. Previously it was described that when the transmission ratio is decreased and torque transmitting member CS 3 C-M 1   23 C-M 1  is positioned on the lower half and both torque transmitting members are in contact with their transmission belt, the adjuster AD 3   103  needs to rotate transmission pulley PU 1 C  41 C clockwise relative to transmission pulley PU 1 D  41 D. Hence here, the adjuster AD 3   103  needs to rotate transmission pulley PU 1 C  41 C counter-clockwise relative to transmission pulley PU 1 D  41 D. As discussed previously, here the pulling load in the transmission pulleys will be used to control the rotation of adjuster AD 3   103 . Once the pulling load in transmission pulley PU 1 D  41 D decreases below a preset low limit value relative to the pulling load in transmission pulley PU 1 C  41 C, the adjuster AD 3   103  rotates transmission pulley PU 1 C  41 C counter-clockwise relative to transmission pulley PU 1 D  41 D. And once the difference in pulling load between transmission pulleys has reached an acceptable preset value, the adjuster AD 3   103  stops rotating. In instances where the adjuster AD 3   103  is not providing sufficient adjustment, in order to prevent excessive flexing of the transmission belts, the transmission ratio changing actuator should stall. Also if desired, in instances where the pulling load in transmission pulley PU 1 D  41 D falls below a lower preset low limit value relative to the pulling load in transmission pulley PU 1 C  41 C, the transmission ratio changing actuator can be temporarily stopped until adjuster AD 3   103  has reduced the difference in pulling load between transmission pulley PU 1 D  41 D and transmission pulley PU 1 C  41 C to a corresponding acceptable preset value. This situation corresponds to engagement status  7  (the torque transmitting member of cone assembly CS 3 D  23 D and the torque transmitting member of cone assembly CS 3 C  23 C are engaged), and engagement status  8  (the torque transmitting member of cone assembly CS 3 D  23 D is about to come out of engagement and the torque transmitting member of cone assembly CS 3 C  23 C is engaged). In order to have a pause between the different operations of adjuster AD 3 A  103 A, which are reducing transition flexing and compensating for transmission ratio change rotation, only engagement status  7  should be used to compensate for transmission ratio change rotation and to change the transmission ratio. Hence adjuster AD 3 A  103 A and the transmission ratio changing actuator are not in operation during engagement status  8 . If no pause is desired than engagement status  7  and engagement status  8  should be used to reduce transition flexing and to change the transmission ratio. 
   And once torque transmitting member CS 3 D-M 1   23 D-M 1  comes out of contact with its transmission belt, adjuster AD 3   103  is used to reduce transition flexing. This situation corresponds to engagement status  1  (only the torque transmitting member of cone assembly CS 3 C  23 C is engaged), and engagement status  2  (the torque transmitting member of cone assembly CS 3 C  23 C is engaged and the torque transmitting member of cone assembly CS 3 D  23 D is about to come into engagement). In order to have a pause between the different operations of adjuster AD 3 A  103 A, which are reducing transition flexing and compensating for transmission ratio change rotation, only engagement status  1  should be used to compensate for transmission ratio change rotation and to change the transmission ratio. Hence adjuster AD 3 A  103 A and the transmission ratio changing actuator are not in operation during engagement status  2 . If no pause is desired than engagement status  1  and engagement status  2  should be used to reduce transition flexing and to change the transmission ratio. However in this instance the adjuster AD 3   103  is not used to compensate for transmission ratio change rotation, despite the fact that transmission ratio change rotation rotates cone assembly CS 3 C-M 123 C-M 1 , and hence output shaft SH 8   18 , clockwise. Since some clockwise rotation applied to the output shaft SH 8   18  is not damaging the CVT, and actually increases the total amount of rotation at the output shaft SH 8   18  at the expense of the work provided by the transmission ratio changing actuator. 
   A detailed control scheme to reduce transition flexing during transmission ratio change is as follows, when both torque transmitting members are engaged, then adjuster AD 3   103  simply performs as described in the rotational movements between the transmission pulleys for different rotational positions and transmission ratio changes description above. When one torque transmitting member has just disengaged with its transmission belt, adjuster AD 3   103  rotates the just disengaged transmission belt relative to its torque transmitting member such that that torque transmitting member is positioned so that it can properly engage with its transmission belt. If required transmission ratio change can be temporarily stopped or slowed down during this period. When there is still time left, then as the transmission ratio is changed, the rotational position of the transmission belt about to be engaged is proportionally adjusted relative to the rotational position of its torque transmitting member. For example, as the pitch diameter is increased, the transmission belt is proportionally moved away from its torque transmitting member about to be engaged such that the proper phase is obtained; and when the pitch diameter is decreased, the transmission belt is proportionally moved towards its torque transmitting member about to be engaged such that the proper phase is obtained. In instances where the adjuster is not able to provide sufficient adjustments (leaves a predetermined tolerance range) the transmission ratio actuator should stop. 
   Also it is recommended that when only one torque transmitting member is engaged with its transmission belt and the direction of rotation of transmission ratio change rotation is opposite from the direction of rotation of the shaft on which the cone are assemblies are mounted, then the speed of the transmission ratio changing actuator should be limited, based on the feedback of the rotational position sensors SN 2 E  132 E, so that the just disengaged torque transmitting member will not reengage with its transmission belt due to transmission ratio change rotation. 
   It is recommended that a pause between the different operations of adjuster AD 3 A  103 A, which are reducing transition flexing and compensating for transmission ratio change rotation, is used, in order to have CVT that is reliable and consistent. The pauses should be long enough to account for the inaccuracy of the CVT in determining the proper engagement status. For example, the CVT might assume that it is engagement status  2  while it is still engagement status  1 . Also in instances where the direction of rotation of adjuster AD 3 A  103 A from the current operation to the next operation changes, the pauses should be long enough so that adjuster AD 3 A  103 A can come to a complete halt before the next operation starts. If a pause is not used than some improper engagement between a torque transmitting member and its transmission belt might occur due to the reduced duration for reducing transition flexing; and some or an increased amount of stalling of the transmission ratio changing actuator might occur. 
   The strength of the adjuster AD 3 A  103 A and the transmission ratio changing actuator should be limited such that they cannot cause excessive flexing in the transmission belts. They should stall or slip before they cause excessive flexing in the transmission belts. If slippage limiting torque devices such as friction clutches are used, they should be mounted such that they will not affect the accuracy of the transmission ratio sensor SN 1 B  131 B and if used, the accuracy of the relative rotational position sensor that monitors the rotation between the adjuster body and the adjuster output member of adjuster AD 3   103 . Also, the preset low limit values, the preset high limit values, the acceptable preset values, and if used, the lower preset low limit values and the higher preset high limit values, should be selected so that they occur before stalling of the transmission ratio changing actuator occurs. 
   Despite the utilization of adjuster AD 3   103 , occasional stalling of the transmission ratio changing actuator can still be allowed, as long as the stalling is sufficiently reduced as to justify the cost of the adjuster. Since although it might be theoretically possible to completely eliminate stalling of the transmission ratio changing actuator, by also taking into account the flexibility of the transmission belts, this might not be economically practical. The cost to implement this might not compensate for the additional duration at which the transmission ratio can be changed. 
   Furthermore, in the instances where adjuster AD 3   103  needs to rotate transmission pulley PU 1 C  41 C in the direction the cone assemblies are rotating, adjuster AD 3   103  needs to provide a pulling torque, which might be quite large, since it has to overcome the rotational resistance of cone assembly CS 3 C  23 C. This situation is similar to a situation where a load is pulled up a cliff. And in the instances where adjuster AD 3   103  needs to rotate transmission pulley PU 1 C  41 C in the opposite direction the cone assemblies are rotating, adjuster AD 3   103  needs to provide a releasing torque, which allows transmission pulley PU 1 C  41 C to slip relative to the input shaft. Unlike the pulling torque, the releasing torque does not have to provide torque that overcomes the rotational resistance of cone assembly CS 3 C  23 C. Here when a holding mechanism, which prevents transmission pulley PU 1 C  41 C from freely rotating in the opposite direction the cone assemblies are rotating is used, the only load adjuster AD 3   103  needs to exert is due to friction. This situation is similar to a situation where a load is lowered down a cliff using a winch that has a locking mechanism that prevents the load from going down the cliff without any input at the winch. By providing both transmission pulleys with an adjuster, the need of the adjusters to provide a pulling torque can be eliminated. Since here, in order to compensate for transmission ratio change rotation, one adjuster needs to provide a pulling torque, and the other adjuster needs to provide a releasing torque. Hence here the adjusters can be operated such that only the adjuster that needs to provide a releasing torque is active. Also, by providing both transmission pulleys with an adjuster, the adjusters can also be operated as to eliminate any rotation at the output shaft due the changing of the transmission ratio. 
   Electrical Adjuster ( FIGS. 30A AND 30B ) 
   In this section a design for an electrical adjuster  160  that can be used as a transition flexing adjuster, mover adjuster, or adjuster AD 3   103  is described. 
   All the adjusters described in this invention consist of an adjuster body and an adjuster output member, that can rotate relative to the adjuster body. In order for the adjuster to transmit torque from a transmission pulley or a cone assembly that is fixed to the adjuster output member to the shaft to which the adjuster body is fixed, the adjuster output member has to be able to hold the adjuster output member fixed relative to the adjuster body despite the fact that torque is applied at the adjuster output member. This can be can be achieved by using an electrical brake or a holding mechanism. 
   For the electrical adjuster  160 , shown as top-view in  FIG. 30A  and as a front-view in  FIG. 30B , a holding mechanism is used. Here the adjuster motor  160 -M 1  drives a worm gear  160 -M 2 , which engages with an adjuster gear  160 -M 3 . The helix angle of the worm gear  160 -M 2 , α, is designed such that the worm gear  160 -M 2  can drive the adjuster gear  160 -M 3  but the adjuster gear  160 -M 3  can&#39;t drive the worm gear  160 -M 2 . Hence here, the worm gear  160 -M 2  and the adjuster gear  160 -M 3  form the holding mechanism that allows the torque applied at the adjuster output member to be transmitted to the adjuster body. 
   The body of the adjuster consists mainly of an attachment sleeve  160 -M 4 , which has an attachment sleeve arm  1   160 -M 4 -S 1 , an attachment sleeve arm  2   160 -M 4 -S 2 , an adjuster motor holder  160 -M 7 , and a counter-weight  160 -M 8 . The attachment sleeve  160 -M 4  can be fixed to an input shaft, an output shaft, or a spline sleeve, so that it is rotatably and axially constrained relative to the shaft or sleeve on which it is attached using a electrical adjuster set screw  160 -M 5 . Extending radially outwards from the side surfaces of the attachment sleeve  160 -M 4  are the two attachment sleeve arms  160 -M 4 -S 1  and  160 -M 4 -S 2 . Attached to attachment sleeve arm  1   160 -M 4 -S 1  is the adjuster motor holder  160 -M 7 , on which the adjuster motor  160 -M 1  is pressed in such that due to friction, the adjuster motor  160 -M 1  can not move axially or rotate relative to the adjuster motor holder  160 -M 7 . And attached to the attachment sleeve arm  2   160 -M 4 -S 2  is counter-weight  160 -M 8 , which is used to counter-balance the centrifugal force of the adjuster motor holder  160 -M 7 , the adjuster motor  160 -M 1 , and the worm gear  160 -M 2 . Using another adjuster motor with a worm gear to counter-balance the centrifugal force of the existing adjuster motor  160 -M 1  and worm gear  160 -M 2  should also work. The additional adjuster motor can be used to increase the torque capacity of the electrical adjuster  160 , or it can be used as a back-up in case the main adjuster motor  160 -M 1  fails. 
   And extending axially backwards from the attachment sleeve  160 -M 4  are four attachment sleeve fins  160 -M 4 -S 3 , spaced at 90 deg. from each other, on which two electrical rings  160 -M 6  are securely pressed in, as to prevent them from rotating or from moving axially relative to the attachment sleeve fins  160 -M 4 -S 3 . Each electrical ring  160 -M 6  is connected to a pole/connection of the adjuster motor  160 -M 1 . The surfaces of the attachment sleeve fins  160 -M 4 -S 3  in contact with the electrical rings  160 -M 6  are insulated such that the electricity directed to the electrical rings  160 -M 6  by some electrical brushes are directed to the electrical poles of the adjuster motor  160 -M 1  by electrical cables  160 -M 9 . If an electric motor that requires more than two input signals is used, than additional electrical rings  160 -M 6  and electrical cables  160 -M 9  are needed. 
   Positioned axially in front of the attachment sleeve  160 -M 4  is an attachment sleeve flange  160 -M 4 -S 4 , which is larger in diameter than the main body of attachment sleeve  160 -M 4 . And positioned axially in front of the attachment sleeve flange  160 -M 4 -S 4  is an attachment sleeve extension  160 -M 4 -S 5 , which is shaped like a hollow cylinder which has a smooth side surface, except at its front end, were it is threaded. 
   The adjuster gear  160 -M 3 , with which the worm gear  160 -M 2  engages, is shaped like a spur gear, that has a centrically positioned cylindrical extension at its front surface. The spur gear shaped portion of adjuster gear  160 -M 3  is labeled as spur gear  160 -M 3 -S 1 . And shaped axially in front of the spur gear  160 -M 3 -S 1  is an adjuster gear extension  160 -M 3 -S 2 , which is shaped like a hollow cylinder, which center is positioned at the center of the spur gear  160 -M 3 -S 1 . And positioned axially in front of the adjuster gear extension  160 -M 3 -S 2  is an adjuster gear flange  160 -M 3 -S 3 , which is shaped like a disk that has a thick rim. The rim portion of adjuster gear flange  160 -M 3 -S 3  extends forwards beyond the surface of its disk shape. On the rim portion of the adjuster gear flange  160 -M 3 -S 3 , two bolt holes that can be used to attach the electrical adjuster  160  to a torque transmitting device such as a cone assembly, a transmission pulley, an attachment extension on which the telescopes of a torque transmitting member can be attached, etc. The adjuster gear  160 -M 3  also has a centrically positioned hole that goes through all shapes of the adjuster gear  160 -M 3 , so that it can be slid onto the attachment sleeve extension  160 -M 4 -S 5 . When adjuster gear  160 -M 3  is slid onto attachment sleeve extension  160 -M 4 -S 5  until the back surface of adjuster gear  160 -M 3  is in contact with the attachment sleeve flange  160 -M 4 -S 4 , the threaded portion of attachment sleeve extension  160 -M 4 -S 5  is not covered by the disk shaped portion of adjuster gear flange  160 -M 3 -S 3  but is only covered by its flange shaped portion. The engagement between the back surface of adjuster gear  160 -M 3  and the attachment sleeve flange  160 -M 4 -S 4  prevents the adjuster gear  160 -M 3  from moving axially backwards relative to the attachment sleeve  160 -M 4 , and in order to prevent the adjuster gear  160 -M 3  from moving axially forwards relative to the attachment sleeve  160 -M 4 , an electrical adjuster nut  160 -M 10  is threaded onto the threaded portion of the attachment sleeve extension  160 -M 4 -S 5 . The width of the electrical adjuster nut  160 -M 10  should be less than the thickness of the rim shape of adjuster gear flange  160 -M 3 -S 3 . Since the adjuster gear  160 -M 3  has to rotate relative to the attachment sleeve  160 -M 4 , friction between the engaging surfaces of the attachment sleeve  160 -M 4 , the adjuster gear  160 -M 3 , and the electrical adjuster nut  160 -M 10  should be minimized. This can be done by coating the engaging surfaces of the adjuster gear with bronze. 
   It might also be useful to have a limiting clutch attached between the shaft of the adjuster motor and the worm gear, as a safety measure in case the controlling computer fails to control the electrical actuator properly. It is also recommended that a housing that protects the components of the electrical adjuster from dirt is used. 
   CVT  1 . 2  ( FIG. 31 ) 
   This CVT, which is shown in  FIG. 31 , is almost identical to CVT  1 . 1 , which is shown in  FIG. 12 , except that here cone assembly  22 B is replaced with a transmission pulley  41 ; and a transmission belt and transmission belt tensioning mechanism, used in CVT  2 . 1 , is used here. In this case only one moveable adjuster, one transition flexing adjuster, one rotational position sensor, and one relative rotational position sensor is needed. 
   CVT  2 . 2  ( FIG. 32 ) 
   CVT  2 . 2 , shown in  FIG. 32 , is identical to CVT  2 . 1 , which is shown in  FIG. 23 , except that here no torque sensors are used to control the relative rotational position of the transmission pulleys. Here only the rotational position sensors are used to control the rotational position of the adjuster mounted transmission pulley in order to reduce transition flexing and compensate for transmission ratio change rotation. Here in order to compensate for transmission ratio change rotation, the rotational position of the adjuster mounted transmission pulley is controlled based on the results obtained from the equation shown in  FIG. 25 , where Δθ from the adjuster mounted cone assembly is subtracted from Δθ of the non-adjuster mounted cone assembly. It is preferred that counter-clockwise rotations are considered positive and clockwise rotations are considered negative. Here the values for θ should be continuously recalculated at short enough intervals as to minimize stalling of the transmission ratio changing actuator, since the values for θ continuously change as the cone assemblies are rotating. Also here, only θ for one cone assembly needs to be monitored, since the controlling computer can determined θ for the other cone assembly mathematically. Also for configurations were the change in pitch diameter is large, the equation shown in  FIG. 25  is not very accurate. This is because as described earlier, as the pitch diameter is changed, the lengths of the transmission belts from their point N to the points where the horizontal mirror line of the transmission pulleys intersect the surfaces of the transmission pulleys remain almost constant only for small changes in pitch diameter. However, this should not be a problem, since here the values for θ are calculated at short intervals so that the changes in pitch diameter between one calculated value and its subsequent calculated value should be small. And some discrepancy between the actual values and the calculated values for Δθ can be compensated by some flexing of the transmissions belts. However, if desired a more accurate equation for calculating Δθ, which takes into account the changes in pitch diameter and which will be referred to as the adjusted equation, is presented in the following paragraphs. 
   The adjusted equation, takes into account the changes in θ due to the change in the radius of the cone assembly where its torque transmitting member is positioned as its pitch diameter is changed, labeled as dθ/dR; and takes into account the rotation of the cone assembly also due to the change in the radius, labeled as dθ rot /dR. For the adjusted equation, first the equation shown in  FIG. 25  is modified by replacing θ 1  with (θ 1 +dθ/dR); and then dθ rot /dR is added to the modified equation. Here in instances were θ, θ 1  in  FIG. 25 , increases with the change in radius, dθ/dR is positive, and in instances were θ decreases with the change in radius, dθ/dR is negative. Also, in instances were dθ rot /dR increases the value for Δθ with the change in radius, dθ rot /dR is positive, and in instances were dθ rot /dR decreases the value for Δθ with the change in radius, dθ rot /dR is negative. Note, here the positive and negative signs for dθ/dR and dθ rot /dR do not have anything to do with the direction of rotation of the cone assembly, since at this stage the values for θ and Δθ are considered positive regardless of the direction of rotation of the cone assembly. However, once the magnitudes for A 0  has been calculated using the adjusted equation, then the signs for the Δθs based on the direction of their rotation are assigned. As before, it is preferred that counter-clockwise rotations are considered positive and clockwise rotations are considered negative 
   A rough estimation for the values for dθ/dR and dθ rot /dR, which here are assumed to be identical, can be obtained experimentally. This can be done by using a configuration for a CVT  2  where only one cone assembly is coupled to its transmission pulley by a transmission belt. Also in order to monitor dθ/dR and dθ rot /dR as the pitch diameter, and hence radius, of the coupled cone assembly is changed, a computer that can monitor the rotational position of the coupled cone assembly and the transmission ratio via appropriate sensors is needed. The experiment is conducted by first positioning the transmission belt at the smallest pitch diameter, and positioning the midpoint of the torque transmitting member at the location where the transmission belt first touches the upper surface of the cone assembly. Then, the transmission belt is moved towards the largest pitch diameter, while the transmission ratio and the rotation of the cone assembly is continuously monitored by the computer. The computer can then use this information to compute the values for dθ/dR and dθ rot /dR, which can then be used in the adjusted equation. 
   The method for determining dθ/dR and dθ rot /dR described in the previous paragraph might not be accurate enough for some applications. If this is the case, then the values for dθ/dR can be determined by again using a configuration for a CVT  2  where only one cone assembly is coupled to its transmission pulley by a transmission belt. However here, it might be easier to use a cone assembly that does not have a torque transmitting member. The experiment is conducted by first positioning the transmission belt at the smallest pitch diameter and then moving it towards the largest pitch diameter while continuously monitoring the location of point N, which is the point where the transmission belt first touches the upper surface of the cone assembly. Here the movement of point N as the pitch diameter, and hence radius, is changed is dθ/dR. And the values for dθ rot /dR can be determined by the same method used in the previous paragraph. However here instead of moving the transmission belt in one step, the transmission belt should be moved in a stepwise manner. So that by making adjustments as necessary, it can be assured that the midpoint of the torque transmitting member is positioned at or close enough to point N each time the pitch diameter is changed. 
   Also in cases where acceptable flexing in the transmission belts can not compensate for the inaccuracy of the equation shown in  FIG. 25  or its adjusted equation, stalling of the transmission ratio changing actuator occurs. 
   CVT  2 . 3  ( FIG. 33 ) 
   CVT  2 . 3 , shown in  FIG. 33 , is identical to CVT  2 . 1 , except that here two adjusters are used, one for each transmission pulley. In order to reduce transition flexing any or both adjusters can be used. The simplest method is to designate an adjuster that will be used to reduce transition flexing so that only that adjuster is used to reduce transition flexing unless there is a problem with the designated adjuster so that the other adjuster, which functions as a back-up, is used to reduce transition flexing. Another method is to first arbitrarily designate an adjuster that will be used to reduce transition flexing until during transmission ratio change an instance occurs where the direction of rotation for compensating for transmission ratio change rotation is different from the direction of rotation for reducing transition flexing, at which the adjuster that was not used for compensating for transmission ratio change rotation is used to reduce transition flexing. That adjuster will then be used to reduce transition flexing, unless there is a problem, until the next occurrence at which the direction of rotation for compensating for transmission ratio change rotation is different from the direction of rotation for reducing transition flexing, at which again the adjuster that was not used for compensating for transmission ratio change rotation is used to reduce transition flexing, which might or might not be the same adjuster that is currently used to reduce transition flexing. If desired both adjusters can be used to reduce transition flexing simultaneously. 
   If both adjusters are used to reduce transition flexing simultaneously or in instances where both adjusters are rotating while only one torque transmitting member of a cone assembly is engaged, the “phase for cone assembly CS 3 C  23 C” is obtained by adding the “phase for cone assembly CS 3 C  23 C” based on the action of the first adjuster to the “phase for cone assembly CS 3 C  23 C” based on the action of the second adjuster; the same method described earlier in the Adjuster System for CVT  2  section should be used to determine each. And in the same manner the “phase for cone assembly CS 3 D  23 D” is obtained by adding the “phase for cone assembly CS 3 D  23 D” based on the action of the first adjuster to the “phase for cone assembly CS 3 D  23 D” based on the action of the second adjuster. If the “phase for cone assembly CS 3 C  23 C” value obtained from the first adjuster and the second adjuster, is greater than “the value for the amount of adjustment needed in order to rotate one transmission pulley from a position where its teeth are aligned with the teeth of the other transmission pulley, to the next position where its teeth are aligned with the teeth of the other transmission pulley” than “the value for the amount of adjustment needed in order to rotate one transmission pulley from a position where its teeth are aligned with the teeth of the other transmission pulley, to the next position where its teeth are aligned with the teeth of the other transmission pulley” should be subtract from that “phase for cone assembly CS 3 C  23 C” value. And if the “phase for cone assembly CS 3 D  23 D” value obtained from the first adjuster and the second adjuster, is greater than “the value for the amount of adjustment needed in order to rotate one transmission pulley from a position where its teeth are aligned with the teeth of the other transmission pulley, to the next position where its teeth are aligned with the teeth of the other transmission pulley” than “the value for the amount of adjustment needed in order to rotate one transmission pulley from a position where its teeth are aligned with the teeth of the other transmission pulley, to the next position where its teeth are aligned with the teeth of the other transmission pulley” should be subtract from that “phase for cone assembly CS 3 D  23 D” value. In addition, the “phase for cone assembly CS 3 C  23 C” value obtained from the first adjuster and the second adjuster and the “phase for cone assembly CS 3 D  23 D” value obtained from the first adjuster and the second adjuster, should reset each time the adjusters have rotated one transmission pulley relative to the other transmission pulley such that the teeth of the transmission pulleys are aligned again. 
   And in order to compensate for transmission ratio change rotation and in order to distribute the torque loading on the cone assemblies when both torque transmitting members are transmitting torque, if desired, only the adjuster that need to provide a releasing torque can be made active so as to reduce the required torque capacity of the adjusters, see last paragraph of the Adjuster System for CVT  2  section. 
   CVT  2 . 4  ( FIG. 34 ) 
   CVT  2 . 4 , shown in  FIG. 34 , is identical to CVT  2 . 3 , except that here no torque sensors are used. Here only the rotational position sensors are used to control the adjusters in order to reduce transition flexing and compensate for transmission ratio change rotation. In order to reduce transition flexing any or both adjusters can be used. And in order the compensate for transmission ratio change rotation, the active adjuster, which is the adjuster that is providing a releasing torque, can be controlled by using the equation shown in  FIG. 25  or its adjusted equation as described in the CVT  2 . 2  section; or by using the over adjustment method describe later in this section. 
   When the equation shown in  FIG. 25  or its adjusted equation is used, in instances where the active adjuster, which is the adjuster that is providing a releasing torque, is providing too little adjustments then the transmission ratio changing actuator should stall before excessive flexing of the transmission belts occur. And in instances where the active adjuster is providing too much adjustment, then the active adjuster should stall or slip before excessive flexing of the transmission belts occur. Stalling of the active adjuster might be preferred over stalling of the transmission ratio changing actuator, since stalling of the active adjuster will not reduce the duration at which the transmission ratio can be changed. Therefore, a more conservative estimation for the equation shown in  FIG. 25  or its adjusted equation, see the CVT  2 . 2  Section, might be preferred. 
   Furthermore, instead of using the equation shown in  FIG. 25  or its adjusted equation to control the adjusters, a simpler and more effective method might be to use the over adjustment method. In this method, during transmission ratio change, when both torque transmitting members are in contact with their transmission belt, the active adjuster, which should be the adjuster that is providing a releasing torque, continuously rotates so as to provide more adjustment than required. Here when adjustment is required, the active adjuster will provide adjustments and when not, the adjuster will simply stall or slip and flex the transmission belts within an acceptable limit. In order to ensure this, the torque of the adjusters should be small enough so that the adjusters cannot excessively flex the transmission belts or a slipping clutch that ensures this can also be used. Also for the over adjustment method, in instances where the active adjuster is not providing sufficient adjustment the transmission ratio changing actuator should stall or stop. 
   CVT  2 . 5  ( FIG. 35 ) 
   CVT  2 . 5 , which is shown in  FIG. 35 , is almost identical to CVT  2 . 1 ; however here in order to reduce transition flexing, the relative rotational movements between torque transmitting member  11  and torque transmitting member  22 , as described for CVT  1 . 1 , is used for torque transmitting member CS 3 C-M 1   23 C-M 1  and torque transmitting member CS 3 D-M 1   23 D-M 1 . In order to achieve this, cone assembly CS 3 C, has to be rotated relative to cone assembly CS 3 D  23 D or vice-versa. Hence here an adjuster AD 4   104 , that can adjust the rotational position of cone assembly CS 3 D  23 D relative to cone assembly CS 3 C  23 C is used. 
   Differential Adjuster Shaft for CVT  2  ( FIGS. 36 ,  37 ,  38 ,  39 ,  40 ,  41 ,  42 ,  43 A,  43 B,  43 C,  44 ,  45 ,  46   47 ,  48 ) 
   In this section differential adjuster shafts which can be used to replace the shaft on which the transmission pulleys are mounted of a CVT  2  will be presented. Here first the advantages of using a differential adjuster shaft, which is a shaft or spline that uses a differential, in a CVT  2  will be described. Then, the preferred and alternate configurations for differential adjuster shafts will be described. Next, the mounting details of a differential adjuster shaft, so as to allow axial movements for it&#39;s transmission pulleys, will be described. 
   As described in the previous sections, in a configuration where each transmission pulley is mounted on an adjuster, in order to distribute the torque loading on the cone assemblies when both torque transmitting members are transmitting torque and in order to compensate for transmission ratio change rotation, only the adjuster that needs to provides a releasing torque can be made active. Hence under this configuration, unlike the configuration where only one adjuster is used, the adjusters do not have to provide a pulling torque. And not having to provide a pulling torque can significantly lower the torque requirements of the adjuster. However, the obvious disadvantage for this configuration is that here two adjusters are needed instead of one. 
   By the use of a differential adjuster shaft, such as differential adjuster shaft  1  shown in  FIG. 36 , the need for an adjuster to provide a pulling torque can be eliminated while only using one adjuster. In  FIG. 36 , the power from the driving source is directed to the differential  212  through the engagement of power gear  210 , keyed on differential adjuster input shaft  211 , and the differential outer teeth  212 -S 1 . Differential  212  has a differential shaft  213 A and a differential shaft  213 B, which are mounted in the same manner as the rear axles of a car are mounted on their rear differential. Using this mounting, the rotational position of differential shaft A  213 A and differential shaft B  213 B can be adjusted relative to the rotational position of the differential, in manner such that any rotation of differential shaft A  213 A relative to the housing of the differential results in the same amount but oppositely directed rotation of the differential shaft B  213 B relative to the housing of the differential and vice-versa. Then a transmission pulley PU 2 A  42 A is keyed to differential shaft A  213 A and transmission pulley PU 2 B  42 B is keyed to differential shaft B  213 B. In order to reduce transition flexing and compensate for transmission ratio change rotation the rotational position of transmission pulley PU 2 A  42 A relative to transmission pulley PU 2 B  42 B needs to be controllably adjusted. In order to achieve this, an adjuster AD 5   105 , which has an adjuster body AD 5   105 -M 1 , fixed to an adjuster shaft A  214 A, and an adjuster output member AD 5   105 -M 2 , fixed to an adjuster shaft B  214 B, is used. Here adjuster AD 5   105  is used to controllably adjust the rotational position of adjuster shaft A  214 A relative to adjuster shaft B  214 B. In order to reduce transition flexing, adjuster AD 5   105  needs to provide proper clockwise or counter-clockwise rotation. Here the amount of adjustment provided is measured by a relative rotational position sensor  133 , which is mounted on the shaft end of adjuster body AD 5   105 -M 1  so that it can measure the amount that adjuster output member AD 5   105 -M 2  rotates relative to adjuster body AD 5   105 -M 1 . And in order to compensate for transmission ratio change rotation, adjuster AD 5   105  continuously rotates the transmission pulley that tends to rotate clockwise relative to the other transmission pulley, clockwise at full capacity so as to provide more adjustment than required. Here when adjustment is required the active adjuster will provide adjustment and when not, the adjuster will simply stall or slip and flex the transmission belts within an acceptable limit. In order to ensure this, the torque of the adjusters should be small enough or a slipping clutch that ensures this can also be used. Adjuster shaft A  214 A is then coupled to differential shaft A  213 A through the engagement of an adjuster shaft gear  215 , keyed on adjuster shaft A  214 A, and a differential shaft gear  216 , keyed on differential shaft A  213 A. And like adjuster shaft A  214 A, adjuster shaft B  214 B is then also coupled to differential shaft B  213 B through the engagement of a adjuster shaft gear  215  and a differential shaft gear  216 . 
   An alternate configuration for a differential adjuster shaft, which is referred to differential adjuster shaft  2 , is shown in  FIG. 37 . This design is identical to differential adjuster shaft  1 ; except here, in order to control the rotational position between its differential shafts, which here are labeled as differential shaft C  213 C and differential shaft D  213 D, instead of using adjuster shafts coupled by gears, here the adjuster body AD 5   105 -M 1  is fixed to the housing of its differential, which here is labeled as differential A  212 A; and the adjuster output member AD 5   105 -M 2  is keyed to differential shaft C  213 C. And as in differential adjuster shaft  1 , here a relative rotational position sensor  133  is mounted on the shaft end of adjuster body AD 5   105 -M 1 . 
   Another alternate configuration for a differential adjuster shaft, which is referred to differential adjuster shaft  3 , is shown in  FIG. 38 . This design is identical to differential adjuster shaft  2 ; except here, in order to control the rotational position between the differential shafts, the rotational position of differential pinion, which here is labeled as differential B pinion  2   212 B-M 3  of its differential, which here is labeled as differential B  212 B, is adjusted. The details of differential B  212 B is shown in  FIG. 39 , it consists of differential B pinion  212 B-M 1  and differential B pinion  2   212 B-M 3 , which are rotatable mounted on the housing of the differential and which engage with a differential B gear  1   212 B-M 2  and a differential B gear  2   212 B-M 4 . Each differential gear is fixed to a differential shaft. Here differential B pinion  2   212 B-M 3  has a differential B pinion  2  shaft  212 B-M 3 -S 1 , which extends through the housing of the differential. And to this shaft, the adjuster output member AD 5   105 -M 2  is keyed, while the adjuster body AD 5   105 -M 1  is fixed to the housing of the differential, via differential B attachment sleeve  212 B-S 2 , which is shaped like a cylinder for which two opposite wall sections have been removed, see  FIG. 38 . And as in differential adjuster shaft  1 , here a relative rotational position sensor  133  is mounted on the shaft end of adjuster body AD 5   105 -M 1 . In order to properly balance the differential, a differential B counter-weight  212 B-S 3  is fixed opposite of the adjuster AD 5   105  on the housing of the differential. Furthermore, since the differential is rotating relative to the frame, the ring and brush connection described earlier can be used to transmit electrical signals from the computer to adjuster AD  105  via electrical rings mounted on the body of the differential and cables. 
   Another alternate configuration for a differential adjuster shaft, which is referred to differential adjuster shaft  4 , is shown in  FIG. 40 . This design is identical to differential adjuster shaft  3 , except here, no adjuster output member is attached to a pinion shaft of its differential and no adjuster body is attached to the differential, via an attachment sleeve. Instead, here a differential brake  217  is used to brake or release a pinion shaft of its differential, see  FIG. 40 , which shows the details of the differential used here, which is labeled as differential C  212 C. In order to achieve this, differential brake  217  has a differential brake pad, not shown, which can be controlled to brake or release differential C pinion  2  shaft  212 C-M 3 -S 1  of differential C pinion  2   212 C-M 3 . And in order to properly balance the differential, a differential C counter-weight  212 C-S 3  is fixed opposite of the differential brake  217  on the housing of the differential. And in order to control differential brake  217 , the computer of the CVT is used. Since the differential is rotating relative to the frame, the ring and brush connection described earlier can be used to transmit electrical signals from the computer to the differential brake via electrical rings mounted on the differential. Braking the differential C pinion shaft  2   212 C-M 3 -S 1  locks the differential, so that no relative rotation between the differential shafts  213 A and  213 B, and the housing of the differential is allowed. And releasing the pinion shaft releases the differential, and this allows the differential shafts to rotate freely relative to the housing of the differential. The differential should be locked under all conditions, except in instances where the rotational position of the transmission pulleys relative to each other need to be adjusted in order to reduce transition flexing and during transmission ratio change. As described earlier, in order to reduce transition flexing, the rotational position between the transmission pulleys is adjusted while only one torque transmitting member is in contact with its transmission belt. In this instance, the pulling load on the transmission pulleys is different, one pulley is transmitting torque while the other is not. So by releasing the differential, the rotational position between the transmission pulleys can be adjusted. And in order to accurately adjust the rotational position between the transmission pulleys, a relative rotational position sensor  133  is mounted on the housing of differential C  212 C so that it can measure the amount that differential shaft  213 A rotates relative to the housing of differential C  212 C. Furthermore, as described earlier, during transmission ratio change, it is desirable to maintain an equal pulling load on the transmission pulleys, and releasing the differential will achieve this, since here the pulley that is transmitting more torque is forced to rotate slower than the other pulley, and this increases the pulling load on the other pulley. In any case, since releasing the differential allows free relative rotation between the transmission pulleys, excessive stresses in the transmission belts due to transmission ratio change rotation can not occur. 
   In addition, for differential adjuster shaft  4 , it is difficult to accurately control the relative rotational position between the differential shafts using the differential brake  217 . Since when differential C pinion shaft  2   212 -M 3 -S 1  is rotating, it does not stop immediately after the brake is applied. In order to better control differential adjuster shaft  4  using the same locking and releasing method an index wheel mechanism shown partially in  FIGS. 42 ,  43 A,  43 B, and  43 C might be used. Like the differential brake, the index wheel mechanism is used to lock or release its differential, which here is labeled as differential D  212 D, see  FIG. 42 . The Index wheel mechanism consist of an index wheel mechanism frame  220 , an index wheel  21 , a locking pin  222 , a locking pin spring  223 , a solenoid A  224 , a solenoid A spring  225 , and a solenoid B  226 . The index wheel  221 , which rotational movements is controlled by locking pin  222 , solenoid A  224 , and solenoid B  226 , is used to control the rotational movements of differential D pinion  2   212 D-M 3 . In order to achieve this, index wheel  221  can be keyed to differential D pinion  2  shaft  212 -M 3 -S 1 . However, in order to increase the resolution of the index wheel mechanism, it is recommended that one or several set of gears, that reduces the amount of rotation of the index wheel that is transmitted to the pinion shaft are used. In  FIG. 42 , which shows a partial side-view of differential  212 D, which utilizes the index wheel mechanism, the rotational output of index wheel  221  is reduced by using a small index wheel mechanism gear  227  that is coupled to a large index wheel mechanism gear  228 . The large index wheel mechanism gear  228  is then keyed to differential D pinion  2  shaft  212 -M 3 -S 1 . More gears can be used for further refinements. And in order to properly balance the differential, a differential D counter-weight  212 D-S 3  is fixed opposite of the index wheel mechanism on the housing of the differential. 
   The physical description of the index wheel mechanism is described below. A partial top-view of the index wheel mechanism is shown in  FIG. 43A . In order to lock index wheel  221 , locking pin  222  is inserted into a groove of index wheel  221 , see  FIG. 43A . Locking pin  222  consist of two shapes, a locking pin lock  222 -S 1  and a locking pin rod  222 -S 2 . The locking pin rod  222 -S 2  is slideably inserted into a matching hole of solenoid A  224 , so that it can only slide axially relative to solenoid A  224 . However, before locking pin rod  222 -S 2  is inserted, a locking pin spring  223  is slid into locking pin rod  222 -S 2 . The locking pin spring  223  forces locking pin lock  222 -S 1  away from solenoid A  224 . Furthermore, locking pin lock  222 -S 1  is magnetized, so that by energizing solenoid A  224 , locking pin lock  222 -S 1  can be pulled towards solenoid A  224 . In addition, on the surface of solenoid A  224 , which is facing away from index wheel  221 , two solenoid A rods  224 -S 1  exist. The solenoid A rods  224 -S 1 , are slideably inserted into a matching holes of solenoid B  226  so that they can only slide axially relative to solenoid B  226 . However, before the solenoid A rods  224 -S 1  are inserted, a solenoid A spring  225  is slid into each solenoid A rod  224 -S 1 . The solenoid A springs  225  force solenoid A  224  away from solenoid B  226 . 
   The operation of the index wheel mechanism, which is used to either lock or release index wheel  221 , is described below. The locking position of the index wheel mechanism is shown in  FIG. 43A . Here locking pin lock  222 -S 1  is positioned inside a groove of index wheel  221 , and this prevents index wheel  221  from rotating. In order to stepwise control the rotational position of index wheel  221 , solenoid A  224  is energized. This lifts locking pin lock  222 -S 1  out of the groove of index wheel  221 , but not out of the triangular portion of that groove, see  FIG. 43B . Here by using a pulse signal for solenoid A, the index wheel  221  is released one groove at a time. This method can be used to adjust the rotational position between the transmission pulleys to adjust for transition flexing. The amount of adjustment provided can be determined from the amount of pulse signals provided, or from a relative rotational position sensor  133  mounted on the housing of differential D  212 D so that it can measure the amount that differential shaft  213 A rotates relative to the housing of differential D  212 D. And in order to completely release the index wheel, solenoid A  224  and solenoid B  226  should be energized. This lifts locking pin lock  222 -S 1  out of the triangular portion of its groove, see  FIG. 43C . This method should be used during transmission ratio change. Although releasing the index wheel can also be accomplished by continuously energizing solenoid A  224 , it is preferably to also use solenoid B  226 . By only energizing solenoid A  224 , the locking pin lock  222 -S 1  is not lifted out of the triangular portion of the index wheel, so that loss of energy due to the compression of the solenoid A spring  225  occurs as the index wheel is rotating. 
   Furthermore, since the index wheel mechanism is rotating relative to the frame where its controlling computer is attached, the ring and brush connection described earlier can be used to direct signals from the computer to the solenoids. An alternate index wheel  221 B is shown in  FIG. 43D . It is basically a wheel that has cavities for locking pin  222  evenly spaced along its circumference. 
   If friction torque transmitting members are used then an alternate configuration for a differential adjuster shaft, which is referred to as differential adjuster shaft  5 , can be used. A configuration for a CVT that uses a differential adjuster shaft  5  is shown as a top-view in  FIG. 44 . This CVT is similar to a CVT  2  except that here the shaft on which the transmission pulleys are mounted is replaced with a differential adjuster shaft  5 . On the housing of the differential of differential adjuster shaft  5  a gear that engages with a gear on the output shaft is keyed. For differential adjuster shaft  5 , the differential does not have an adjuster so that the transmission pulleys are free to rotated relative to each other. For the CVT utilizing differential adjuster shaft  5 , the shaft or spline on which the cone assemblies are mounted should be the input shaft/spline. If the arc length of the torque transmitting arc of the friction torque transmitting members is limited such that each transmission belt will never cover the entire non-torque transmitting arc of the cone assembly to which they are coupled, then there might be instances were only one cone assembly is engaged with its transmission belt, and since the transmission pulleys are free to rotate relative to each other here occasional slippage, where torque at the input shaft/spline is not transmitted to the output shaft/spline, might occur. This can be eliminated by ensuring that both torque transmitting arcs are always engaged with their transmission belt, this can be achieved by selecting the proper arc length for the torque transmitting arcs and if necessary by sufficiently increasing the engagement coverage of the transmission belts by using supporting pulleys. A supporting pulley, which is labeled as supporting pulley  1700 , is shown in  FIGS. 45 and 46 , which show partial front views of a CVT utilizing differential adjuster shaft  5 . The position of the supporting pulleys at different transmission ratios can be controlled in the same manner as the tensioning wheels described in the description for CVT  2 . Depending on the configuration of the CVT, the mounting method described in the Sliding Cone Mounting Configuration or the spring-loaded slider pulley assemblies C  720 C described latter in this patent in the Alternate CVT&#39;s section can also be used for supporting pulleys  1700 . Under this configuration, there might be instances where a transmission belt covers the entire non-torque transmitting arc of a cone assembly; hence during transmission ratio change occasional stalling of the actuator that is used to change the transmission ratio might occur. If it is undesirable to have occasional stalling of the actuator that is used to change the transmission ratio during transmission ratio change, then the arc lengths of the torque transmitting arcs should be limited such that the transmission belts will never cover an entire non-torque transmitting arc. Under this configuration, slippage can be limited by locking the differential of differential adjuster shaft  5  during all instances except during transmission ratio change. Here the locking devices used for differential adjuster shaft  4  can be used. 
   Furthermore, in order to change the transmission ratio unless the axial position of the cones can be changed, the axial position of the transmission pulleys need to be changed. In order to emphasize the function of the differential adjuster shaft in addressing the transition flexing and transmission ratio change issue, such detail have been previously omitted. In the following paragraphs, details on how to allow the axial position of the differential adjuster shaft mounted transmission pulleys to be changed will be described. The following details can be applied to any of the differential adjuster shafts described earlier. 
   A simple method to allow the axial position of the differential adjuster shaft mounted transmission pulleys to be changed can be achieved by simple connecting the differential adjuster shaft and its adjuster shaft, if applicable, to a mover frame  230 , which is connected to the mover gear rack  231  which engages a transmission ratio gear that is used to control the transmission ratio, see  FIG. 47 . Here the differential adjuster shaft and the adjuster shaft should be connected to mover frame  230  so that they move axially with the mover frame but are allowed to rotate relative to the mover frame. This can be achieved by simple having a differential shaft flange  213 A-S 1  and an adjuster shaft flange  214 A-S 1  at the end of the shafts. The mover flanges, can than be inserted into a matching cavity in mover frame  230  and secured by mover frame flange plates  230 -M 1 , which are partially glued to mover frame  230 . Also since here it might be unpractical to have differential adjuster input shaft  211  move axially with the mover frame  230 . The input gear  210  can be mounted on an input gear sleeve  232 , which can slide axially on an input gear spline  233 , which is used instead of differential adjuster input shaft  211 . The input gear sleeve  232  can then be connected by the use of mover arm  230 -S 1 , which has a mover arm bearing  230 -M 2 , to mover frame  230  so that it moves axially with the mover frame. Here mover arm bearing  230 -M 2  is used to allow the input gear sleeve  232  to rotate relative to the mover arm  230 -S 1 . A more detailed description of the input gear sleeve  232  can be found in the next paragraph, which describes in detail the configuration of a differential spline sleeve  241 , which is nearly identical to the input gear sleeve  232 . 
   Another configuration that allows the axial position of the differential adjuster shaft mounted transmission pulleys to be changed is shown in  FIG. 48 . Here differential shaft A  213 A is replaced with differential spline A  240 A and differential shaft B  213 B is replaced with differential spline B  240 B. In addition, here each transmission pulleys is keyed to a differential spline sleeve  241  using a differential spline set-screw  241 -M 1 , so that they are rotatably and axially fixed relative to their differential spline sleeve. The differential spline sleeves  241  have a splined profile that matches the profile of a differential spline  240 A and  240 B; so that the differential spline sleeves can slide axially relative to their differential spline, but can not rotate relative to their differential spline. Each differential spline sleeve  241  consists of two main shapes, a differential spline sleeve pulley mount shape  241 -S 1  and a differential spline sleeve bearing mount shape  241 -S 2 . Each differential spline sleeve pulley mount shape  241 -S 1  is shaped like a round cylinder that has a radial oriented threaded hole that does not extruded through the inner surface of the differential spline sleeve. This hole will be used for a differential spline sleeve set-screw  241 -M 1 . The differential spline sleeve bearing mount shape  241 -S 2  is also shaped like a round cylinder; however, it is smaller in diameter than the differential spline sleeve pulley mount shape  241 -S 1  so that a shoulder is formed between the differential spline sleeve pulley mount shape  241 -S 1  and the differential spline sleeve bearing mount shape  241 -S 2 . Furthermore, the free end of differential spline sleeve bearing mount shape  241 -S 2  is threaded. The transmission pulleys  42 A and  42 B are each mounted on their differential spline sleeve pulley mount shape  241 -S 1  and secured using a differential spline sleeve set-screw  241 -M 1 . And a mover arm A bearing  242 -M 1 , which is a thrust bearing that is tightly inserted into a matching hole of each mover arm A  242 -S 1  so as to prevent any relative movements between them, is slid into each differential shaft sleeve bearing mount shape  241 -S 2 . Then a differential spline sleeve nut  241 -M 2  is threaded onto the threaded end of each differential shaft sleeve bearing mount shape, so that the mover arm A bearings  242 -M 1  are tightly sandwiched between the shoulder formed by their differential spline sleeve pulley mount shape  241 -S 1  and their differential spline sleeve bearing mount shape  241 -S 2 , and their differential spline sleeve nut  241 -M 2 . Under this set-up, the axial position of the differential spline sleeves  241  depend on the axial position of their mover arms A  242 -S 1 . Also, here the mover arm A bearings  242 -M 1  allow their differential spline sleeves  241  to rotate without much frictional resistance relative to their mover arms A  242 -S 1 . The mover arms A  242 -S 1  are then connected to a mover rod  242 -S 2 , which is part of a mover frame A  242 , which is used to change the axial position of the torque transmitting members and the transmission pulleys via a gear rack A  243 . This mounting configuration can be used for differential adjuster shafts  2 , 3 ,  4 , and  5 . 
   In order to support the differential adjuster shafts, support bearings positioned so that they do not interfere with its operation of can be used. As before, the method of supporting the shafts will not be explained in this application, since the technique to do this is well known and a details for this will unnecessarily complicated the description for the invention without adding to the essence of the invention. 
   Spring-Loaded Adjuster 
   Another simple method to reduce transition flexing is by using a spring-loaded adjuster that biases a spring-loaded adjuster mounted torque transmitting member towards a neutral position from which it can rotate clockwise and counter-clockwise relative to the shaft on which it is attached. Here first a spring-loaded adjuster AS 1   171 , which can be used to replace the adjusters AD 1 A  101 A or AD 1 B  101 B of CVT  1 . 1  will be described, then a spring-loaded adjuster AS 2   172  that can be used as an adjuster AD 4   104  for CVT  2 . 4  will be described. It is also recommended that the spring-loaded adjusters are mounted such that they will not affect the accuracy of the sensors of their CVT. 
   —Spring-Loaded Adjuster AS 1   171  ( FIGS. 49A-49D ) 
   Another simple method to reduce transition flexing is by having a parallel gap in the slots where the attachment pins used to attach a torque transmitting member to its cone assembly are inserted; and using a spring-loaded adjuster to bias the attachment pins of the gap mounted torque transmitting member towards the center of the gap. This allows for some rotational movement of the gap mounted torque transmitting member in instances where the pitch diameter of the gap mounted torque transmitting member is increased and decreased. In order to achieve this, a spring-loaded adjuster AS 1   171  is needed. The spring-loaded adjuster AS 1   171  consists mainly of a spring-loaded adjuster shaft  171 -M 2  that can rotate relative to a spring-loaded adjuster body  171 -M 1 , and is biased by an adjuster spring  171 -M 3  towards a neutral position, see  FIG. 49D . Also in order to mount the telescopes of a gap mounted torque transmitting member to the spring-loaded adjuster shaft  171 -M 2 , a shaft end attachment  171 -M 4  is attached to the end of the spring-loaded adjuster shaft, see  FIG. 49A . The shaft end attachment consist mainly of three shapes that form an inverted U-shape. One leg of the inverted U-shape, which is labeled as shaft end attachment extension arm  171 -M 4 -S 1 , is shaped like the long leg of the adjuster extension arm AD 1 A-M 2 -S 2   101 A-M 2 -S 2  of adjuster AD 1 A  101 A of CVT  1 . 1 , see  FIG. 13 , and is used in the same manner, hence it also has a constrainer mechanism CN 1 A  111 A. The other leg of the inverted U-shape, which is labeled as shaft end attachment balancing arm  171 -M 4 -S 2 , is shaped like the long leg of the adjuster balancing arm AD 1 A-M 2 -S 3   101 A-M 2 -S 3  and is used to balance the centrifugal forces of the shaft end attachment extension arm  171 -M 4 -S 1  and its attachments. And the top horizontal member of the inverted U-shape, which is labeled as shaft end attachment mounting plate  171 -M 4 -S 3 , is shaped like elongated rectangular plate that has a hexagonal cavity at its center. The hexagonal cavity of the shaft end attachment mounting plate  171 -M 4 -S 3  is used to securely press in a matching hexagonal notch located at the top end of the spring-loaded adjuster shaft  171 -M 2 , see  FIG. 49B . The spring-loaded adjuster body  171 -M 1  is basically shaped like a hollow cylinder, which has an open top end and a closed bottom end. And the spring-loaded adjuster shaft  171 -M 2  is basically shaped like a hollow cylinder, which has an open bottom end and a closed top end, see  FIGS. 49C and 49D . The inner top end of the spring-loaded adjuster shaft  171 -M 2  and the bottom end of the spring-loaded adjuster body  171 -M 1 , each have a square shaped notch, which function will be explained later. And the outer top end of the spring-loaded adjuster shaft  171 -M 2  has a hexagonal notch, which is used to attach the shaft end attachment  171 -M 4 . The outer diameter of the spring-loaded adjuster shaft  171 -M 2  is slightly smaller than the inner diameter of the spring-loaded adjuster body  171 -M 1 , so that when the spring-loaded adjuster shaft  171 -M 2  is inserted into the spring-loaded adjuster body  171 -M 1 , only significant rotational movements between them is allowed. Also, the outer surface of the top end portion of the spring-loaded adjuster body is threaded. And the outer surface of the spring-loaded adjuster shaft  171 -M 2  has a spring-loaded adjuster flange  171 -M 2 -S 1 , which diameter is slightly smaller than the outside diameter of the spring-loaded adjuster body. The spring-loaded adjuster flange  171 -M 2 -S 1  is positioned somewhere between the top end and the bottom end of the spring-loaded adjuster shaft  171 -M 2 . The spring-loaded adjuster flange  171 -M 2 -S 1  should be positioned so that a sufficient amount of the spring-loaded adjuster shaft  171 -M 2  can be inserted into the spring-loaded adjuster body  171 -M 1  so that sufficient amount of moment and deflection can be resisted by the assembled spring-loaded adjuster AS 1   171 . An adjuster spring  171 -M 3  is inserted into the cavity formed by the inner top end surface and inner side surface of the spring-loaded adjuster shaft, and the inner bottom end surface and the bottom portion of the inner side surface of the spring-loaded adjuster body. At both ends of the adjuster spring  171 -M 3 , the wire of the adjuster spring is shaped such that a square shaped loop, on which the square notches of the spring-loaded adjuster shaft and the spring-loaded adjuster body can be tightly inserted, is formed. The length of the adjuster spring  171 -M 3  is designed such that when the spring-loaded adjuster flange  171 -M 2 -S 1  is engaged with the top end surface of the spring-loaded adjuster body, the top end and the bottom end of the adjuster spring is always in contact with the top surface of the spring-loaded adjuster shaft  171 -M 2  and the bottom surface of the spring-loaded adjuster body  171 -M 1 . 
   In order to securely fix the axial position of the spring-loaded adjuster shaft  171 -M 2  relative to the spring-loaded adjuster body  171 -M 1 , a spring-loaded adjuster cap  171 -M 5  is used. The spring-loaded adjuster cap  171 -M 5  is shaped like a short cylinder, which has a top surface but not a bottom surface. The top surface of the spring-loaded adjuster cap has a hole at its center, which diameter is slightly larger than the diameter of the spring-loaded adjuster shaft  171 -M 2 , but smaller than the diameter of the spring-loaded adjuster flange  171 -M 2 -S 1 . And the inner side surface of the spring-loaded adjuster cap  171 -M 5  has internal threads that can engage with the external threads of the spring-loaded adjuster body  171 -M 1 . 
   The spring-loaded adjuster  171  is assembled by first inserting the adjuster spring  171 -M 3  into the spring-loaded adjuster body  171 -M 1  such that the bottom square shaped loop of the spring-loaded adjuster spring is fully inserted into the square shaped notch of the spring-loaded adjuster body. Then the spring-loaded adjuster shaft  171 -M 2  is slid into the spring-loaded adjuster body  171 -M 1 , in a manner such that the open end of the spring-loaded adjuster shaft is facing the open end of the spring-loaded adjuster body, and the top square shaped loop of the spring-loaded adjuster spring  171 -M 3  is fully inserted into the square shaped notch of the spring-loaded adjuster shaft  171 -M 2 . Then the spring-loaded adjuster cap  171 -M 5  is inserted through the top-end of the spring-loaded adjuster shaft  171 -M 2  and tighten unto the spring-loaded adjuster body  171 -M 1  through the engagement of the internal threads of the spring-loaded adjuster cap with the external threads of the spring-loaded adjuster body. The spring-loaded adjuster cap  171 -M 5  should be tighten unto the spring-loaded adjuster body  171 -M 1  until the inner top surface of the spring-loaded adjuster cap pushes the spring-loaded adjuster flange  171 -M 2 -S 1  of the spring-loaded adjuster shaft  171 -M 2  towards the top surface of the spring-loaded adjuster body  171 -M 1 , so that axial movements between the spring-loaded adjuster shaft  171 -M 2  and the spring-loaded adjuster body  171 -M 1  is minimized. Since the spring-loaded adjuster shaft has to rotate relative to the spring-loaded adjuster body, friction between the engaging surfaces of the spring-loaded adjuster cap, the spring-loaded adjuster shaft, and the spring-loaded adjuster body should be minimized. This can be done by coating the engaging surfaces of the spring-loaded adjuster flange of the spring-loaded adjuster shaft with bronze. However in order to prevent the spring-loaded adjuster cap from loosening, no low friction coating should be applied to internal and external threads. Next in order to be able to properly mount the telescopes of a gap mounted torque transmitting member and a constrainer mechanism to the spring-loaded adjuster shaft  171 -M 2 , the shaft end attachment  171 -M 4  is attached to the spring-loaded adjuster shaft. In order to achieve this, the hexagonal notch at the outer top surface of the spring-loaded adjuster shaft  171 -M 2  is pressed into the hexagonal cavity of the shaft end attachment mounting plate  171 -M 4 -S 3 . Here the dimension of the hexagonal cavity should be slightly smaller than the dimension of the hexagonal notch, so that sufficient friction between them, as to prevent any axial movements between them, is developed when separating forces encountered during normal operation is applied to them. 
   —Spring-Loaded Adjuster AS 2   172  ( FIGS. 50A &amp; 50B ) 
   The spring-loaded adjuster AS 2   172 , shown in  FIGS. 50A and 50B , can be used to replace the adjuster AD 4   104  in CVT  2 . 5 . The spring-loaded adjuster AS 2   172  is identical to the spring-loaded adjuster AS 1   171 , except that here two radially opposite positioned threaded holes for two limiter rods  172 -M 1 , are drilled into the spring-loaded adjuster shaft  171 -M 2 . And two pairs of radially opposite positioned cylindrical limiter notches  172 -M 2  are welded on to the outer top surface of the spring-loaded adjuster cap  171 -M 5 . The limiter rods  172 -M 1  and the limiter notches  172 -M 2  should be positioned, such that the adjuster spring  171 -M 3  biases each limiter rod towards the midpoint of the space created between a pair of limiter notches  172 -M 2 . Also here the hexagonal notch of the spring-loaded adjuster shaft  171 -M 2  is not used to attach shaft end attachment  171 -M 4 , but it is used to mount a cone assembly, which here should have a matching square opening, which should have a dimension such that sufficient friction between the notch and the opening exist as to prevent any significant relative movements between the cone assembly and its spring-loaded adjuster shaft. This adjuster can be further modified by drilling a hole through its entire length. Through this hole a shaft can be slid through. The hole can also have a notch for a key at its spring-loaded adjuster body, which can be used to key the spring-loaded adjuster body to its shaft. 
   Mechanical Adjuster 
   In this section a design for a mechanical adjuster AM 1   181 , that can be used as an adjuster AD 4   104 , and a mechanical adjuster AM 2   182 , that can be used as transition flexing adjuster AD 1   101  is described. Since it is simpler, here the mechanical adjuster AM 1   181 , which is for CVT  2 . 5 , will be described before the mechanical adjuster AM 2   182 , which is for CVT  1 . 1 , is described. 
   —Mechanical Adjuster AM 1   181  ( FIGS. 51A ,  51 B,  52 , and  53 ) 
   Like the electrical adjuster  160 , the mechanical adjuster AM 1   181 , which is shown in  FIGS. 51A and 51B , mainly consists of an adjuster body and an adjuster output member. However here, the rotational position between them is controlled by an adjustable ratio cam mechanism instead of an electrical motor. Here the adjuster body consist mainly of a cam  181 -M 1 , cam sleeve  181 -M 2 , a follower  181 -M 4 , and a follower spring  181 -M 5 . The cam  181 -M 1  is stationary relative to the shaft where the mechanical adjuster AM 1   181  is used. The cam  181 -M 1  consist mainly of four shapes. The top shape of the cam, top cam shape  181 -M 1 -S 1 , and the bottom shape of the cam, bottom cam shape  181 -M 1 -S 3 , have a diameter D C . The right shape of the cam, right cam shape  181 -M 1 -S 2  has a diameter D 1 , and the left shape of the cam, left cam shape  181 -M 2 -S 4 , also has a diameter D 1 . Here the diameter D C  is larger than the diameter D 1 . Between the different shapes of the cam, transition shapes exist so that cam  181 -M 1  has a smooth continuous surface. The cam sleeve  181 -M 2  is shaped like a hollow cylinder, which has an open end and a closed end. The closed end of the cam sleeve  181 -M 2  is shaped like a disk that has an cam sleeve attachment sleeve  181 -M 2 -S 2 , which is used to attach the shaft where the mechanical adjuster AM 1   181  is used, which here is labeled as shaft SH 0   10 . In order to fix the cam sleeve  181 -M 2  axially and rotatably to shaft SH 0   10 , cam sleeve attachment sleeve  181 -M 2 -S 2  has a threaded hole for a cam sleeve set screw  181 -M 3 . In addition, cam sleeve  181 -M 2  has a radial hole, through which follower  181 -M 4  is inserted. And on top of the radial hole of cam sleeve  181 -M 2 , a cam sleeve constrainer sleeve  181 -M 2 -S 3 , which has the same inside diameter as the radial hole exist. Also, in order to balance the centrifugal forces due to cam sleeve constrainer sleeve  181 -M 2 -S 3 , cam follower  181 -M 4 , and portions of the centrifugal forces due to a link AM 1 -M 6   181 -M 6  and a link AM 1 -M 7   181 -M 7 , a cam sleeve counter-weight  181 -M 2 -S 4  is shaped opposite of the cam sleeve constrainer sleeve  181 -M 2 -S 3  on the surface of constrainer sleeve  181 -M 2 . Also extending radially outwards from the surface of the cam sleeve  181 -M 2  is a controller rod counter-weight arm  181 -M 2 -S 5 . The controller rod counter-weight arm  181 -M 2 -S 5  has a hole through which a controller rod counter-weight  181 -M 11  will be slid through, so as to constrain the rotational position of the controller rod counter-weight  181 -M 11  relative to cam sleeve  181 -M 2 . The controller rod counter-weight arm  181 -M 2 -S 5  is positioned so that a controller rod  181 -M 10  can be properly slid through the controller slot of the link AM 1 -M 6   181 -M 6 . Also in order to balance the centrifugal forces of the controller rod counter-weight arm  181 -M 2 -S 5 , a counter-weight arm counter-weight  181 -M 2 -S 6  is positioned opposite of the controller rod counter-weight arm  181 -M 2 -S 5 . The counter-weight arm counter-weight  181 -M 2 -S 6  is positioned on the inside surface of cam sleeve  181 -M 2 , so that it does not interfere with the movements of link AM 1 -M 6   181 -M 6 . The follower  181 -M 4  consist mainly of four shapes. The top shape of the follower, which is labeled as follower top  181 -M 4 -S 1 , is shaped like a flat bar that has a hole. The shape below it, which is labeled as follower round  181 -M 4 -S 2 , is shaped like a round rod. During normal operation of the mechanical adjuster AM 1   181 , this shape of the follower is in contact with the radial hole and the hole of the constrainer sleeve  181 -M 2 -S 3  of cam sleeve  181 -M 2 . Follower round  181 -M 4 -S 2  should have a dimension such it can only move radially in and out relative to cam sleeve  181 -M 2 . The shape below it, which is labeled as follower shoulder  181 -M 4 -S 3 , is the shoulder of follower  181 -M 4 . It is shaped like a round disk, which diameter is larger than the diameter of the shape above it. And the bottom shape, which is labeled as follower bottom  181 -M 4 -S 4 , is shaped like a half sphere. In the mechanical adjuster AM 1   181  assembled state, cam  181 -M 1 , which is stationery relative to the shaft, is inserted into the open end of cam sleeve  181 -M 2  such that they are concentric. And in order to ensure that the follower  181 -M 4  is always in contact with cam  181 -M 1 , a follower spring  181 -M 5  is placed between the inner surface of cam sleeve  181 -M 2  and follower shoulder  181 -M 4 -S 3 . 
   The adjuster output member of the mechanical adjuster AM 1   181  is shaped like disk, and it will be referred to as the output disk  181 -M 8 . The output disk  181 -M 8  has two opposite positioned bolt holes, which will be used to attach a cone assembly or a transmission pulley to the output disk. In addition, output disk  181 -M 8  has an output disk arm  181 -M 8 -S 1 , which is a radial extension that has a hole. And in order to balance the centrifugal force due the output disk arm  181 -M 8 -S 1 , and portions of the centrifugal forces due to link AM 1 -M 6   181 -M 6  and link AM 1 -M 7   181 -M 7 , an output disk counter-weight  181 -M 8 -S 2  is shaped opposite of the output disk arm  181 -M 8 -S 2  on the surface of output disk  181 -M 8 . In order to control the relative rotation between cam sleeve  181 -M 2  and output disk  181 -M 8 , a link AM 1 -M 6   181 -M 6  and link AM 1 -M 7   181 -M 7 , which connect the cam sleeve to the output disk, are used. Link AM 1 -M 6   181 -M 6  is shaped like a monkey wrench. It has a middle shape, and two end shapes. Each end shape, which is labeled as link shape AM 1 -M 6 -S 1   181 -M 6 -S 1 , is shaped like a square plate that has a hole. And the middle shape, which is labeled as link shape AM 1 -M 6 -S 2   181 -M 6 -S 2 , is shaped like a slender rectangular plate that has a controller slot. The end shapes are parallel relative to each other but the middle shape is positioned diagonally relative to the end shapes. The other link, link AM 1 -M 7   181 -M 7  is shaped like flat and slender bar that has two link holes at each of its ends. In addition, the ends of link AM 1 -M 7   181 -M 7  have a half disk shape, which center is positioned at the center of the holes of link AM 1 -M 7   181 -M 7 . 
   In order for link AM 1 -M 6   181 -M 6  and link AM 1 -M 7   181 -M 7  to connect the cam sleeve  181 -M 2  to the output disk  181 -M 8 , one end of link AM 1 -M 6   181 -M 6  is connected to follower  181 -M 4  by inserting a link bolt  181 -M 9  through the hole of follower  181 -M 4 , and then securing that bolt using a link nut  181 -M 12 . And the other end of link AM 1 -M 6   181 -M 6  is connected to one end of link AM 1 -M 7   181 -M 7  by inserting a link bolt  181 -M 9  through the other hole of link AM 1 -M 6   181 -M 6  and a hole of link AM 1 -M 7   181 -M 7 , and then securing that link bolt using a link nut  181 -M 12 . And the other end of link AM 1 -M 7   181 -M 7  is connected to the output disk arm  181 -M 8 -S 1  by inserting a link bolt  181 -M 9  through the other hole of link AM 1 -M 7   181 -M 7  and the hole of the output disk arm  181 -M 8 -S 1 , and then securing that link bolt using a link nut  181 -M 12 . The surfaces of the link bolts and the link nuts that are in contact with follower  181 -M 4 , link AM 1 -M 6   181 -M 6 , link AM 1 -M 7   181 -M 7 , or output disk arm  181 -M 8 -S 1 , are preferably coated with a low friction material such as oil-impregnated bronze, so that the link AM 1 -M 6   181 -M 6  and link AM 1 -M 7   181 -M 7  can rotate without much frictional resistance. 
   In order to control the relative rotation between cam sleeve  181 -M 2  and output disk  181 -M 8 , a controller rod  181 -M 10  is used. The controller rod  181 -M 10  is a slender steel rod that is bent repeatedly such that a zigzag profile is formed. The zigzag profile consist of two alternating shapes, a pivot shape  181 -M 10 -S 1  and a parallel shape  181 -M 10 -S 2 , that can be slid through the controller slot of link AM 1 -M 6   181 -M 6 . The angle between the pivot shape  181 -M 10 -S 1  and the parallel shape  181 -M 10 -S 2  should be 90°. The pivot shapes  181 -M 10 -S 1  are positioned perpendicular to the long surfaces of link AM 1 -M 6   181 -M 6 , so that they can act as pivots for link AM 1 -M 6   181 -M 6 . And the parallel shapes  181 -M 10 -S 2  are positioned parallel to the long surfaces of link AM 1 -M 6   181 -M 6 , so that they can act as constrainers for link AM 1 -M 6   181 -M 6 . The function of the controller rod  181 -M 10  is to properly adjust the rotation of the output disk  181 -M 8  relative to the cam sleeve  181 -M 2  due the profile of the cam  181 -M 1 , by adjusting the pivot location of link AM 1 -M 6   181 -M 6  or by constraining link AM 1 -M 6   181 -M 6 . By changing the axial position of the controller rod  181 -M 10  relative to link AM 1 -M 6   181 -M 6 , it can be selected whether a pivot shape  181 -M 10 -S 1  or a parallel shape  181 -M 10 -S 2  is positioned inside the controller slot of link AM 1 -M 6   181 -M 6 . In instances where a pivot shape  181 -M 10 -S 1  is located in the controller slot of link AM 1 -M 6   181 -M 6 , the position of the pivot for link AM 1 -M 6   181 -M 6  can be changed by changing the axial position of the controller rod  181 -M 10  relative to link AM 1 -M 6   181 -M 6 . And changing the position of the pivot for link AM 1 -M 6   181 -M 6 , by changing the axial position of controller rod  181 -M 10  relative to link AM 1 -M 6   181 -M 6 , changes the amount of relative rotation between cam sleeve  181 -M 2  and output disk  181 -M 8  due to the profile of cam  181 -M 1 . Furthermore, by inserting a parallel shape  181 -M 10 -S 2  into the controller slot of link AM 1 -M 6   181 -M 6 , link AM 1 -M 6   181 -M 6  is constrained from pivoting, so that despite the profile of cam  181 -M 1 , no relative rotation between cam sleeve  181 -M 2  and output disk  181 -M 8  exist. When follower  181 -M 4  is in contact with a diameter D 1  of cam  181 -M 1 , a positive angle, which is referred to as the controller angle, is formed between the flat profile of the controller rod  181 -M 10  and the controller slot of link AM 1 -M 6   181 -M 6 . The controller angle increases as the pivot is moved towards the follower  181 -M 4 . The amount of relative rotation between the cam sleeve  181 -M 2  and the output disk  181 -M 8  increases proportionally with an increase in the controller angle. The diameters D 1  should be selected as to eliminate transition flexing. When the follower  181 -M 4  is in contact with a diameter D C  of cam  181 -M 2 , link AM 1 -M 6   181 -M 6  is aligned such that the flat profile of controller rod  181 -M 10  is parallel to the controller slot of link AM 1 -M 6   181 -M 6 . In this configuration the axial position of controller rod  181 -M 10  relative to link AM 1 -M 6   181 -M 6  can always be changed. 
   Furthermore, the zigzag profile of the controller rod  181 -M 10  and its pattern of axial movements relative to link AM 1 -M 6   181 -M 6  should be designed based on the information shown in  FIGS. 21A and 21C . Here in instances were the circumference of the surface of the cone were the torque transmitting members are positioned is an even multiple of the width of their teeth, so that no relative rotation between cam sleeve  181 -M 2  and output disk  181 -M 8  is required, the parallel shape  181 -M 10 -S 2  of the controller rod  181 -M 10  should be positioned inside the controller slot of link AM 1 -M 6   181 -M 6 . And from  FIG. 21A , it can be observed that the required amount of rotational adjustment linearly increases as the critical non-torque transmitting arc is increased from an integer space, were it is a multiple of the width of the teeth of the torque transmitting members, until the next integer space is reached. Furthermore, from  FIG. 21A , it can be observed that the required amount of rotational adjustment linearly decreases as the critical non-torque transmitting arc is decreased from an integer space until the next integer space is reached. A slightly different set-up is shown in  FIG. 21C , here the required amount of rotational adjustment linearly decreases as the critical non-torque transmitting arc is increased from an integer space until the next integer space is reached; and the required amount of rotational adjustment linearly increases as the critical non-torque transmitting arc is decreased from an integer space until the next integer space is reached. Here the pivot shape  181 -M 10 -S 1  of controller rod  181 -M 10  and its pattern of axial movement should be designed so that the position of the pivot can be properly adjusted with the change in pitch diameter so that transition flexing is eliminated or at least minimized. The axial distance between a parallel shape  181 -M 10 -S 2  to the next parallel shape  181 -M 10 -S 2  should correspond to the same axial distance that corresponds to an increase or decrease of a circumferential length of one tooth of the circumferential surface of the cone assembly where its torque transmitting member is positioned. The proper dimension and shape of the cam  181 -M 1 , the follower  181 -M 4 , the link AM 1 -M 6   181 -M 6 , the link AM 1 -M 7   181 -M 7 , the output disk arm 181 -M 8 -S 1 , the controller rod  181 -M 10 , and the cones, can be determined experimentally. One method would be to first estimate the proper dimension for each part and then adjusting the dimension of the controller rod  181 -M 10  and its controller rod slot. If that does not work-out then the dimensions of the cam  181 -M 1  can be adjusted. If this still does not work-out then the dimension of a different part can adjusted and so forth. 
   Also the controller rod  181 -M 10  has to be slid through the controller slot of link AM 1 -M 6   181 -M 6 , which is rotating with the cam sleeve  181 -M 2 , which in turn is rotating with shaft SH 0   10 . Hence, the controller rod  181 -M 10  has to be attached such that it rotates with shaft SH 0   10  but can be moved axially relative to shaft SH 0   10 . In order to achieve this a controller rod mechanism, that consist of the controller rod  181 -M 10 , a controller rod counter-weight  181 -M 11 , a controller rod slider  181 -M 13 , and a controller rod disk  181 -M 14 , is used. Here in order to constrain the rotational position of the controller rod  181 -M 10  relative to the controller rod counter-weight  181 -M 11 , the back end of the controller rod  181 -M 10  and the back end of an controller rod counter-weight  181 -M 11  are connected to the controller rod slider  181 -M 13 , which slides freely on shaft SH 0   10  and is positioned in the back of the controller rod disk  181 -M 14 . And the front end of the controller rod  181 -M 10  and the front ends of the controller counter-weight  181 -M 11  are connected to the controller rod disk  181 -M 14 , which is positioned in front of the cam sleeve  181 -M 2 . As described earlier the controller rod counter-weight  181 -M 11  is slid through controller rod counter-weight arm  181 -M 2 -S 5  of cam sleeve  181 -M 2  so that the controller rod counter-weight  181 -M 11  rotates with cam sleeve  181 -M 2 . And since controller rod  181 -M 10  and controller rod counter-weight  181 -M 11  are rotatably constrained relative to each other, controller rod  181 -M 10  is rotatably constrained relative to cam sleeve  181 -M 2 . Therefore, controller rod  181 -M 10  rotates with cam sleeve  181 -M 2 . 
   The controller rod  181 -M 10  and the controller rod counter-weight  181 -M 11 , except their ends, are made from a round wire. And in order to avoid any vibrations due to unbalanced centrifugal forces, the weight of controller rod  181 -M 10  should be identical to the weight of controller rod counter-weight  181 -M 11 . In order to attach controller rod  181 -M 10  and controller rod counter-weight  181 -M 11  to controller rod slider  181 -M 13  and controller rod disk  181 -M 14 , the front-end and the back-end of the controller rod and the controller rod counter-weight are shaped like a straight square wire. The controller rod slider  181 -M 13  is shaped like a hollow cylinder with an plain end and a flanged end. The inner diameter of the controller rod slider  181 -M 13  is slightly larger than the diameter of shaft SH 0   10 , so that only significant relative axial movements between the controller rod slider  181 -M 12  and shaft SH 0   10  is allowed. Furthermore, the plain end of the controller rod slider  181 -M 13  is facing away from cam sleeve  181 -M 2  and the flanged end of the controller rod slider is facing towards the cam sleeve. To the flanged end of the controller rod slider  181 -M 13 , the back end of the controller rod  181 -M 10  and the back end of the controller rod counter-weight  181 -M 11  are attached. In order to achieve this, the flanged end of the controller rod slider has two opposite positioned square holes into which the back end of the controller rod and the back end of the controller counter-weight are securely pressed in. They are attached opposite of each other so that the centrifugal force of the controller rod is canceled out by the centrifugal force of the controller rod counter-weight. In addition, the controller rod and the controller rod counter-weight are also aligned so that their center-axis is parallel to the center-axis of shaft SH 0   10 . And the front end of the controller rod  181 -M 10  and the front end of the controller rod counter-weight  181 -M 11  are attached to the controller rod disk  181 -M 14 , which also has two opposite positioned square holes into which the front end of the controller rod and the front end of the controller rod counter-weight are securely pressed in. And in order to control the axial position of the controller rod mechanism, a member of the controller rod mechanism can be connected to a member of the CVT where it is used, that moves axially with the torque transmitting members as the transmission ratio is changed, so that the axial position of the controller rod is automatically adjusted as the transmission ratio is changed. This method is shown in  FIG. 52 . Another method to control the axial position of the controller rod  181 -M 10  is to attach a controller rod mover mechanism, that is used to change the axial position of the controller rod relative to the link AM 1 -M 6   181 -M 6 , to the controller disk  181 -M 14 . This method is shown in  FIG. 53 . For the configurations shown in  FIGS. 52 and 53 , the rotational adjustments provided by the mechanical adjuster should be based on the information shown in  FIG. 21C . 
   A configuration of a CVT, where a mechanical adjuster AM 1   181  can be utilized is shown in  FIG. 52 . For this CVT, which is referred to as CVT  2 . 6 , the controller rod slider  181 -M 13  is directly connected to the mover sleeve CS 4 B-M 6   24 B-M 6  of cone assembly CS 4 B  24 B, which is identical to cone assembly CS 3   23 , except that it does not have a non-torque transmitting member. Here the mechanical adjuster AM 1   181  is used to properly adjust the rotational position between cone assembly CS 4 A  24 A and cone assembly CS 4 B  24 B, and hence the rotational position between torque transmitting member CS 4 A-M 1   24 A-M 1  and torque transmitting member CS 4 B-M 1   24 B-M 1 . Also as noted earlier the axial position of the controller rod  181 -M 10  can only be changed when its flat profile is parallel to the controller slot of link AM 1 -M 6   181 -M 6 , hence some stalling of the transmission ratio changing actuator is to be expected. The strength of transmission ratio changing actuator should be small enough such that it can not cause damaging internal stresses in the parts of mechanical adjuster AM 1   181  or anywhere else in the CVT, when it tries to change the transmission ratio when the flat profile of the controller rod is not parallel to the controller slot of link AM 1 -M 6   181 -M 6 . A limiting clutch mounted on the output of the transmission ratio changing actuator that causes slippage between the output of the transmission ratio changing actuator and the rest of the mechanism used to change the transmission ratio when the torque at the transmission ratio changing actuator exceeds a limiting value can also be used. One problem with connecting a member of the controller rod mechanism directly or indirectly to the mover sleeve of a cone assembly is the fact that the controller rod  181 -M 10  and the link AM 1 -M 6   181 -M 6  have a finite thickness so that when the axial positions of the controller rod and the torque transmitting members are changed, the parallel shape  181 -M 10 -S 2  of the controller rod and the controller slot of link AM 1 -M 6   181 -M 6  are engaged for a finite axial distance. Since no rotational adjustment between the cam sleeve  181 -M 2  and the output disk  181 -M 8  is allowed when the parallel shape of the controller rod is engaged with controller slot of link AM 1 -M 6   181 -M 6 , no rotational adjustment is allowed for a finite axial distance. However since the critical non-torque transmitting arc(s), continuously change as the axial positions of the torque transmitting members and the controller rod is changed, the torque transmitting members are at an even space, where no rotational adjustment between the torque transmitting members is required, for an infinitesimal axial distance. Therefore, there are instances where no rotational adjustments is provided despite the fact that some adjustment in the rotational position of one torque transmitting member relative to the other is required. Hence here some transition flexing has to occur. Here, transition flexing can be reduced by reducing the thickness of link AM 1 -M 6   181 -M 6  and the thickness of controller rod  181 -M 10  or by also using a spring-loaded adjuster AS 2   172 . 
   The following configuration of a CVT, as shown in  FIG. 53 , can be used to control the axial position of the controller rod  181 -M 10  so that transition flexing can be minimized without having to reduce the thickness of controller rod  181 -M 10  and the thickness of link AM 1 -M 6   181 -M 6 . For this CVT, which is referred to as CVT  2 . 7 , the mechanical adjuster AM 1   181  is used to adjust the rotational position of a cone assembly CS 4 C  24 C relative to a cone assembly CS 4 D  24 D, and hence the rotational position of torque transmitting member CS 4 C-M 1   24 C-M 1  relative to torque transmitting member CS 4 D-M 1   24 D-M 1 . Here a cam adjuster gear rack  181 -M 16 , which engages with a cam adjuster gear  181 -M 18 , is attached to the front surface of the controller rod disk  181 -M 14  via a rotatable coupling  190 . The rotatable coupling  190 , which is shown in detail in  FIG. 17 , allows one end of the rotatable coupling to rotate relative to the other end of the rotatable coupling. It mainly consists of two coupling sleeves  190 -M 1 , which each have an upper shape and a larger lower shape. The larger lower shapes are inserted into a joiner sleeve  190 -M 2 . In order to prevent the coupling sleeves from moving axially relative to each other, joiner sleeve ends  190 -M 3 , that engage with the shoulder created between the upper shapes and the lower shapes of the coupling sleeves, are glued on each end of joiner sleeve  190 -M 2 . The upper shapes of the coupling sleeves  190 -M 1 , each have two opposite positioned threaded holes, which are used to screw in coupling sleeve set-screws. Here for mounting purposes a controller rod disk shaft  181 -M 15  is centrically welded on to the front surface of the controller rod disk  181 -M 14 ; and a gear rack shaft  181 -M 17 , is glued on to the back surface of the cam adjuster gear rack  181 -M 16 . And in order to attach one end of a rotatable coupling  190  to the controller rod disk  181 -M 14 , the controller rod disk shaft  181 -M 15  is inserted into one coupling sleeve, and a coupling sleeve set-screw is threaded through the controller rod disk shaft  181 -M 15 ; and in order to attach the other end of that rotatable coupling to the cam adjuster gear rack  181 -M 16 , the gear rack shaft  181 -M 17  is inserted into the other coupling sleeve of the rotatable coupling  190 , and a coupling sleeve set-screw is threaded through the gear rack shaft  181 -M 17 . The cam adjuster gear  181 -M 18 , which is keyed to a controller rod motor and engages with the cam adjuster gear rack  181 -M 16 , will be used to control the axial position of the controller rod. In addition, the cam adjuster gear  181 -M 18  has a marked wheel attached to it, which will also be used to monitor the axial position of the controller rod via a rotational position sensor SN 2   132 . In order to properly control the axial movement of the controller rod, the controller rod motor is connected to the computer that controls CVT  2 . 7 . The computer will then properly control the transmission ratio changing actuator and the controller rod motor as the eliminate or minimize the stretching of the transmission belts in instances where the circumferences of the cone assemblies where the torque transmitting members are positioned is not a an even multiple of the width of the teeth of the torque transmitting members. Changing the axial position of the controller rod when the follower is not in contact with the diameter D C  of the cam can damage the mechanical adjuster. In order to prevent this the strength of the controller rod motor should be small enough such that it can not cause damaging internal stresses in the mechanical adjuster AM 1   181  or anywhere else in the CVT. In order to ensure this a limiting clutch can also be mounted on the output of the controller rod motor. 
   The following control scheme can be used to properly control the controller rod motor and the transmission ratio changing actuator. First of all as described earlier, the axial position of the controller rod  181 -M 10  should only be changed when follower  181 -M 4  is in contact with the diameter D C  of cam  181 -M 1 , otherwise stalling of the controller rod actuator or slipping of its limiting clutch has to occur. Although not absolutely necessary, it is nice to prevent this by attaching a rotational position sensor on one of the cone assemblies of the CVT shown in  FIG. 53 , preferably cone assembly CS 4 C  24 C, and connect this sensor to the computer of this CVT; and program the computer so that it only changes the axial position of the controller rod when the follower is in contact with the diameter D C  of cam  181 -M 1 . The same method can also be used for the CVT shown in  FIG. 52 . Furthermore, the axial position of the controller rod  181 -M 10  should be changed such that it corresponds with the axial position of the torque transmitting members. Here a certain limit value is set as to limit the discrepancy between the required axial position of the controller rod based on the axial position of the torque transmitting members and the actual axial position of the controller rod. For example, when the controller rod has moved too far ahead relative to its required axial position based on the position of the torque transmitting members, the movement of the controller rod will be put on hold until the torque transmitting members have moved to a corresponding axial position which is within the required limit range. And when the torque transmitting members have moved too far ahead relative to the controller rod, the movement of the torque transmitting members will be put on hold until the controller rod has moved to a corresponding axial position which is within the required limit range. When the pivot shape of the controller rod is in the controller slot of link AM 1 -M 6   181 -M 6 , a corresponding movement of the torque transmitting members should result in a corresponding movement of the controller rod. And when the parallel shape of the controller rod is engaged with the controller slot of link AM 1 -M 6   181 -M 6 , then despite the movement of the controller rod, no movement of the torque transmitting members should occur. 
   —Mechanical Adjuster AM 2   182  ( FIG. 54 ) 
   For the mechanical adjuster AM 1   181 , shown in  FIGS. 51A and 51B , the adjuster output member, output disk AM 1 -M 8   181 -M 8 , is axially fixed relative to the shaft where it is used. Hence this mechanical adjuster can not be used as an adjuster AD 1 A  101 A or AD 1 B  101 B of CVT  1 . 1 , since these adjusters move axially relative to their shaft when the axial position of the torque transmitting members is changed. In order to reduce transition flexing for a CVT similar to CVT  1 . 1 , which is shown in  FIG. 54  and is referred to as CVT  1 . 3 , a slightly modified version of mechanical adjuster AM 1   181 , which is labeled as mechanical adjuster AM 2   182 , is used. Mechanical adjuster AM 2   182 , is shown in detail on the left cone assembly, cone assembly CS 2 C  22 C, of  FIG. 54 . It is identical to mechanical adjuster AM 1   181 , except that here in order to have an adjuster output member that can move axially with the torque transmitting members, an adjuster slider plate  182 -M 1  is added. Most of the members used for mechanical adjuster AM 1   181  are also used for mechanical adjuster AM 2   182 . Here only the members that are different, or are not used in mechanical adjuster AM 1   181  are labeled differently than in mechanical adjuster AM 1   181 . The adjuster slider plate  182 -M 1  is shaped like an elongated plate. On one side of the adjuster slider plate  182 -M 1 , a cam adjuster extension arm  182 -M 2  and a cam adjuster balancing arm  182 -M 3  are welded on. The cam adjuster extension arm  182 -M 2  is shaped like the long leg of the adjuster extension arm AD 1 A-M 2 -S 2   101 A-M 2 -S 2  of transition flexing adjuster AD 1 A  101 A, which is used in CVT  1 . 1 , see  FIG. 13 . And the cam adjuster balancing arm  182 -M 3  is shaped like the long leg of the adjuster balancing arm AD 1 A-M 2 -S 3   101 A-M 2 -S 3  of transition flexing adjuster AD 1 A  101 A. The cam adjuster extension arm  182 -M 2  is used to mount a gap mounted torque transmitting member, which here is torque transmitting member CS 2 C-M 2   22 C-M 2 , in the same manner as a gap mounted torque transmitting member is mounted on adjuster extension arm AD 1 A-M 2 -S 2   101 A-M 2 -S 2 . And like in adjuster AD 1 A  101 A, the cam adjuster balancing arm  182 -M 3  is used to balance the centrifugal forces of the cam adjuster extension arm  182 -M 2  and its attachments. Also as in transition flexing adjuster AD 1 A  101 A, here a constrainer mechanism CN 1 A  111 A, that constrains the movements of the telescopes of torque transmitting member CS 2 C-M 2   22 C-M 2 , is attached to the cam adjuster extension arm  182 -M 2 . Also for mounting purposes, on the same side and near the center of the adjuster slider plate  182 -M 1 , an adjuster slider plate back tube  182 -M 4 , which inner diameter is slightly larger than the diameter of the input shaft, is welded on. And on the other side of the adjuster slider plate  182 -M 1 , two cam adjuster sliders  182 -M 5  are welded on in manner such that in the mechanical adjuster&#39;s AM 2   182  assembled state, there are no members that prevent the cam adjuster sliders  182 -M 5  from moving axially. Also in order to ensure that the adjuster slider plate  182 -M 1  rotates with the output disk AM 2 -M 8   182 -M 8 , the output disk AM 2 -M 8   182 -M 8  has two slider holes, into which the cam adjuster sliders  182 -M 5  can be slideably inserted. Also, the cam adjuster sliders  182 -M 5  are long enough such that they are engaged with the output disk AM 2 -M 8   182 -M 8  for every axial position of the torque transmitting members. Also for mounting purposes, on the same side and near the center of the adjuster slider plate  182 -M 1 , an adjuster slider plate front tube  182 -M 6 , which inner diameter is slightly larger than the diameter of the input shaft, is welded on. 
   A configuration where two mechanical adjusters AM 2   182  are used to reduce transition flexing for a CVT  1 . 3  is shown in  FIG. 54 . For this CVT, a mechanical adjuster AM 2   182  is used to properly adjust the rotational position of torque transmitting member CS 2 C-M 2   22 C-M 2  of cone assembly CS 2 C  22 C, and to properly adjust the rotational position of torque transmitting member CS 2 D-M 2   22 D-M 2  of cone assembly CS 2 D  22 D. Here a rotatable coupling  190 , described in the previous section, is used to mount an adjuster slider plate  182 -M 1  to mover sleeve CS 2 C-M 6   22 C-M 6  and to mount an adjuster slider plate  182 -M 1  to mover sleeve CS 2 D-M 6   22 D-M 6 . Here in order to attach one end of a rotatable coupling  190  to a mover sleeve, a portion of that mover sleeve is inserted into one coupling sleeve of coupling  190 , and two coupling sleeve set-screws, positioned opposite from each other, are partially threaded through the walls of that mover sleeve; and in order to attach the other end of that rotatable coupling to an adjuster slider plate, the adjuster slider plate back tube  182 -M 4  is inserted into the other coupling sleeve, and two coupling sleeve set-screws, positioned opposite from each other, are partially threaded through the walls of that adjuster slider plate back tube. And another rotatable coupling  190  is used to rotatably connect an adjuster slider plate  182 -M 1  to its controller rod slider  181 -M 13 , so that the axial position of the controller rod sliders  181 -M 13  are properly adjusted as the axial position of the torque transmitting members is changed. In order to attach one end of this rotatable coupling  190  to an adjuster slider plate, the adjuster slider plate front tube  182 -M 6  is inserted into one coupling sleeve of coupling  190 , and two coupling sleeve set-screws, positioned opposite from each other, are partially threaded through the walls of that adjuster slider plate front tube; and in order to attach the other end of this rotatable coupling  190  to a controller rod slider  181 -M 13 , a portion of the controller rod slider  181 -M 13  is inserted into the other coupling sleeve, and two coupling sleeve set-screws, positioned opposite from each other, are partially threaded through of the walls of the controller rod slider. 
   Also for a cone assembly CS 4   24 , such as cone assembly CS 4 A/B/C/D  24 A/B/C/D, no non-torque transmitting member is used. Hence in order to maintain the longitudinal shape of the transmission belts as the transmission ratio is changed, guiding wheels  200  or a guides can be mounted on the tense side of the transmission belts such as shown  FIGS. 55A and 55B . Like the tensioning wheels, which in  FIGS. 55A and 55B  are tensioning wheels TW 1   61 , the guiding wheels  200  move axially with the torque transmitting members, which in  FIGS. 55A and 55B  are torque transmitting members CS 4 -M 1   24 -M 1 , and the transmissions pulleys, which in  FIGS. 55A and 55B  are transmission pulleys PU 1   41 , as the transmission ratio is changed. However, while the tensioning wheels move vertically up or down as their axial position is changed, so that they can maintain proper tension in their transmission belts, the vertical positions of the guiding wheels do not need to change as their axial position is changed. 
   Gap in Teeth ( FIG. 56 ) 
   In order to compensate for the inaccuracy or absence of any adjusters in order to reduce transition flexing another method besides relaying on the flexibility of the transmission belts or using spring-loaded adjusters is by having gaps between the teeth of the torque transmitting members and the torque transmitting devices coupled to them. This method will be referred to as the “gaps between teeth” method. Here, the pitch, p, of the teeth of the torque transmitting members and the pitch, p, of the teeth of their transmission belts are equal, but the width of the space between the teeth are slightly wider than the width of the teeth so that gaps between the teeth are formed. It is recommended that the gaps are wide enough so that despite the inaccuracy of the adjusters, transition flexing can be eliminated. A partial sectional view of a torque transmitting member about to be engaged with a transmission belt, where between their teeth gaps, g 1  and g 2 , exist is shown in  FIG. 56 , which shows the teeth of a torque transmitting member, which are individually labeled as torque transmitting member tooth  7 , and a cross-section of the teeth of a transmission belt, which are individually labeled as transmission belt tooth  6 . 
   In order to reduce transition flexing, when only one torque transmitting member is engaged, the adjuster(s) ensure that when the torque transmitting member about to be engaged is mated with its transmission belt, the teeth of that torque transmitting member are positioned between the teeth of its transmission belt but not touching the teeth of its transmission belt. Here a “gap offset value” can be added to the value of adjustments needed as based on the graphs in FIGS.  21 A/B/C. The “gap offset value” is based on the amount of rotational adjustments needed in order to position the torque transmitting member or tooth about to be engaged in the middle of the space between the teeth of its transmission belt instead of being engaged with the teeth of its transmission belt. If the torque transmitting member or tooth currently engaged is engaged with the teeth or tooth of its transmission belt, the adjustments based on the graphs in FIGS.  21 A/B/C will position the torque transmitting member or tooth about to be engaged so that it is engaged with the teeth of its transmission belt. In order to position the torque transmitting member or tooth about to be engaged in the middle of the space between the teeth of its transmission belt, the transmission belt about to be engaged has to be moved relative its torque transmitting member which is about to be engaged by an amount that corresponds to (“the width of a tooth shape of a torque transmitting member that is positioned between a space between two teeth of its transmission belt” minus “the width of a space between two teeth of its transmission belt”) divided by two, this rotational adjustment is designated as the “gap offset value”, which should be programmed into the controlling computer so that to each adjustment value obtained from the graph in  FIG. 21A , the “gap offset value” is either subtracted or added depending on whether the leading surfaces or the trailing surfaces of the teeth of the engaged torque transmitting members are engaged with the teeth of their transmission belt during normal operation. The arc length of the “gap offset value” should be measured at the pitch-lines of the torque transmitting members; hence, “the width of a tooth shape of a torque transmitting member that is positioned between a space between two teeth of its transmission belt” and “the width of the space between two teeth of its transmission belt” should be measured at the pitch-lines of the torque transmitting members. 
   If the leading surfaces of the teeth of the engaged torque transmitting members are engaged with the teeth of their transmission belt during normal operation, then to each “phase arc length for cone assembly CS 3 C  23 C” and “phase arc length for cone assembly CS 3 D  23 D” values obtained from the graph in  FIG. 21A , the “gap offset value” is subtracted. If a negative value is obtained for the subtracted “phase arc length for cone assembly CS 3 C  23 C” or the “phase arc length for cone assembly CS 3 D  23 D” value, then “the arc length value for the amount of adjustment needed in order to rotate one transmission pulley from a position where its teeth are aligned with the teeth of the other transmission pulley, to the next position where its teeth are aligned with the teeth of the other transmission pulley, as measured at the pitch-lines of the torque transmitting members” is added to that negative value. The leading surfaces of the teeth of the engaged torque transmitting members are engaged with the teeth of their transmission belt during normal operation when the cone assemblies are mounted on the input shaft. 
   If the trailing surfaces of the teeth of the engaged torque transmitting members are engaged with the teeth of their transmission belt during normal operation, then to each “phase arc length for cone assembly CS 3 C  23 C” and “phase arc length for cone assembly CS 3 D  23 D” values obtained from the graph in  FIG. 21A , the “gap offset value” is added. If the value for the added “phase arc length for cone assembly CS 3 C  23 C” value is greater than “the arc length value for the amount of adjustment needed in order to rotate one transmission pulley from a position where its teeth are aligned with the teeth of the other transmission pulley, to the next position where its teeth are aligned with the teeth of the other transmission pulley, as measured at the pitch-lines of the torque transmitting members” than “the arc length value for the amount of adjustment needed in order to rotate one transmission pulley from a position where its teeth are aligned with the teeth of the other transmission pulley, to the next position where its teeth are aligned with the teeth of the other transmission pulley, as measured at the pitch-lines of the torque transmitting members” should be subtract from that added “phase arc length for cone assembly CS 3 C  23 C” value. And if the value for the added “phase arc length for cone assembly CS 3 D  23 D” value is greater than “the arc length value for the amount of adjustment needed in order to rotate one transmission pulley from a position where its teeth are aligned with the teeth of the other transmission pulley, to the next position where its teeth are aligned with the teeth of the other transmission pulley, as measured at the pitch-lines of the torque transmitting members” than “the arc length value for the amount of adjustment needed in order to rotate one transmission pulley from a position where its teeth are aligned with the teeth of the other transmission pulley, to the next position where its teeth are aligned with the teeth of the other transmission pulley, as measured at the pitch-lines of the torque transmitting members” should be subtract from that added “phase arc length for cone assembly CS 3 D  23 D” value. The trailing surfaces of the teeth of the engaged torque transmitting members are engaged with the teeth of their transmission belt during normal operation when the cone assemblies are mounted on the output shaft. 
   If based on experimentation a different “gap offset value” works better than the one described previously, than that “gap offset value” can be programmed into the controlling computer. The “gap offset value” can be any value as long as the teeth of the transmitting members about to be engaged are positioned between the teeth of their transmission belt without any interference. And once one or several teeth of the torque transmitting member about to be engaged is positioned between the teeth of its transmission belt, the adjuster adjust the relative rotational position between the torque transmitting member about to be engaged and its transmission belt so that the teeth are touching the teeth of their transmission belt such that the engagement between the teeth can be used for desired torque transmission. This can be done by adjusting the rotational position of the transmission pulley of the transmission belt about to be engaged, adjusting the rotational position of the cone assembly about to be engaged by adjusting the rotational position of the other transmission pulley, or by a combination of the two previous adjustment methods for example. Once the teeth are engaged as desired, the adjuster can stop rotating. This type of adjustment will be referred to as “engagement adjustment”. 
   Ideally “engagement adjustment” should start once one tooth of the torque transmitting member about to be engaged is positioned between the teeth of its transmission belt. And ideally engagement adjustment should stop once the teeth of that torque transmitting member are touching the teeth of their transmission belt. If this kind of adjustment is not practical because of accuracy limitations, then engagement adjustment can start during a window when say two to three teeth of the torque transmitting member about to be engaged are positioned between the teeth of its transmission belt, or during an even later and larger window. This can be done by adding a delay value in degrees as to when “engagement adjustment” should start after the beginning of engagement statuses  3  and  7 . However, the delay value selected should be small enough so that engagement between the teeth about to be engaged occurs before the currently engaged torque transmitting member disengages. Also a second delay value that starts at the end of the delay value discussed previously can be used to program when “engagement adjustment” should stop. Engagement adjustment can be stopped at any time before that torque transmitting member disengages with its transmission belt. Engagement adjustment is not absolutely necessary, but it can eliminate shock loads if the “gaps between teeth” method is used. In order to control the adjuster(s) to perform “engagement adjustment”, the controlling computer uses the delay value and second delay value described in this paragraph in conjunction with the engagement statuses described previously. 
   Also here because of the space between the teeth of the torque transmitting member and the transmission belt, in instances when the output shaft is pulling the input shaft, which might occur due to friction in the engine and inertia that wants to keep the output shaft rotating, the currently engaged teeth of the torque transmitting member will rotate relative to its transmission belt so that under this condition the engaged surfaces are different than the engaged surfaces during normal operation. For example for a certain configuration, under this condition the leading surfaces are engaged instead of the trailing surfaces, which are engaged during normal operation. This problem can be avoided by avoiding having the output shaft pulling the input shaft, which can be done by mounting a one way clutch between the output shaft and the output device being rotated, so that the output shaft can rotate the output device in the driving direction but the output device can not rotate the output shaft in the driving direction, and by ensuring that the friction in the output shaft is larger than in the engine. A one way clutch which can be locked or which direction can be reversed on command can be used in case reverse rotation is required. Another method to solve this problem is by using a tension measuring load-cells on the tense side and slack side of the transmission belt or transmission belts. Here a tension measurement on the side that is slack during normal operation that is larger than that of the side that is tense during normal operation indicates that the output shaft is pulling the input shaft, and this information can then be used by the controlling computer to appropriately control the adjuster(s). 
   Friction Clutch Mounting 
   In order to account for transition flexing and transmission ratio change rotation, the cone assemblies and transmission pulleys of a CVT, which rotational positions need to be adjusted can be mounted using friction clutches, which slip once their torque limit is exceeded. Slipping of the friction clutches allow the rotational position of the cone assemblies and transmission pulleys mounted on them to be adjusted. Although simple and cheap, this method of adjustment might cause significant energy loses due to frictional slippage and limit the amount of torque that can be transmitted. However, the friction clutch mounting method can be used as a safety measure in case the adjusters malfunction. 
   Tension Measuring Load Cell ( FIG. 57 ) 
   For CVT  2 . 1 , torque sensors are used to measure the pulling loads on the transmission pulleys. Another method to measure, or in this case estimate, the pulling load on a transmission pulley is by measuring the tension in the tense side of transmission belt BL 2   32  via a load cell  135 , see  FIG. 57 . Here the slider used to mount a tensioning wheel, which here is labeled as load cell wheel  62 , is identical to the tensioning slider  1106  one described in Continuous Variable Transmission Variation  2  (CVT  2 ) section of this patent except that here it is horizontally cut into two halves. The lower half, which includes the hole for the slide, is labeled as load cell lower slider  70 . And the upper half, which includes the shaft for mounting the tensioning wheel, is labeled as load cell upper slider  71 . Between load cell lower slider  70  and load cell upper slider  71 , load cell  135  is positioned. In order to maintain the position of load cell  135 , load cell  135  is glued to the top surface of load cell lower slider  70 . Also like for the tensioning sliders  1106 , vertical guides  72 , which here are inserted into vertical holes of the load cell lower slider  70  and load cell upper slider  71 , are used to change the axial position of the load cell lower slider  70  and load cell upper slider  71  and maintain their proper orientation. 
   Furthermore, the angle between the horizontal plane and the tense side of transmission belt BL 2   32  will be referred to as angle α 1  and angle α 2 . Smaller values for angle α 1  and angle α 2  are preferred, so that a load cell  135  with a smaller load rating can be used. In order to determine the tension in transmission belt BL 2   32 , besides monitoring the measurement of load cell  135 , the controlling computer of the CVT also needs to determine the angle α 1  and angle α 2 . This can be done by programming the values for angle α 1  and angle α 2  for every transmission ratio, which is monitored, into the computer. Another method that can be used is by programming into the computer an equation for angle α 1  and angle α 2  based on the transmission ratio. 
   Additional Embodiments 
   In this section some additional embodiments for CVT  1  and CVT  2  or parts for CVT  1  and CVT  2  are described. The adjuster systems and the adjustment methods described earlier in this patent can be used for all of the additional embodiments described below. 
   Sliding Cone Mounting Configuration ( FIGS. 58 ,  59 ,  60 ) 
   In the sliding cone mounting configuration, in order to change the transmission ratio, the axial positions of the cones relative to their frame are changed, while the axial positions of the torque transmitting members and the transmission pulleys are held fixed relative to their frame. Using the sliding cone mounting configuration, the design for some CVT&#39;s can be simplified. Especially the design where a differential adjuster shaft is used. 
   A portion of the sliding cone mounting configuration is shown as a partial top-view in  FIG. 58 , which shows a portion of one of its cone assembly, which is labeled as sliding cone cone assembly  25 . Here the sliding cone rotors  25 -M 1 , on which the telescopes of the torque transmitting members and the non-torque transmitting members are mounted, are keyed to a sliding cone spline  250  so as to constrain any rotational and axial movements between the sliding cone rotors and the sliding cone spline. And sliding cone assembly  25  is slideably mounted on a sliding cone spline  250 . Here sliding cone assembly  25  has a sliding cone slider  25 -S 1  at the smaller end of its cone. The inner surfaces of sliding cone slider  25 -S 1  form a splined profile that match the splined profile of the sliding cone spline  250  so that torque can be transmitted between them while also allowing sliding cone slider  25 -S 1 , and hence sliding cone cone assembly  25 , to slide freely on sliding cone spline  250 . And the outer surface of sliding cone slider  25 -S 1  is shaped like a round cylinder, which center axis is the rotational axis of its cone. Furthermore, the outer diameter of sliding cone slider  25 -S 1  is smaller in diameter than the smaller end of its cone so that a shoulder is formed between a sliding cone slider  25 -S 1  and the smaller end of its cone. In addition, the free end of sliding cone slider  25 -S 1  is threaded. A mover arm B bearing  251 -M 1 , which is a thrust bearing that is tightly inserted into a matching hole of a mover arm B  251 -S 1  so as to prevent any relative movements between them, is slid into sliding cone slider  25 -S 1 . Then a sliding cone slider nut  25 -M 2  is threaded onto the threaded end of sliding cone slider  25 -S 1 , so that mover arm B bearing  251 -M 1  is tightly sandwiched between the shoulder formed by sliding cone slider  25 -S 1  and the smaller end of its cone. Under this set-up, the axial positions of sliding cone slider  25 -S 1 , and hence the axial positions of sliding cone assembly  25 , depend on the axial positions of mover arms B  251 -S 1 . Also, here mover arm B bearing  251 -M 1  allow sliding cone assembly  25  to rotate without much frictional resistance relative to mover arm B  251 -S 1 . Mover arm B  251 -S 1  is then connected to a mover rod B  251 -S 2 , which is part of a mover frame B  251 , which is used to change the axial position of the cone assemblies and the tensioning slides via a gear rack B  252 . 
   In addition, in case the sliding cone configuration is used for a CVT  1 . 2  or CVT  2 , in order to properly maintain the tension of the transmission belts the tensioning mechanism shown in  FIG. 59  can be used. Here a tensioning slide A  253  and tensioning slide B  254  are connected by a tensioning slide end A  255  and a tensioning slide end B  256 . Tensioning slide end A  255  is then connected to mover frame B  251 , shown in  FIG. 58 , by a tensioning slide connector  257 . Sliding on tensioning slide A  253  is a tensioning slider A  258  and sliding on tensioning slide B  254  is a tensioning slider B  259 . Tensioning slider A  258  consists of two main shapes, a tensioning slider A block  258 -S 1  and a tensioning slider A clevis  258 -S 2 . Tensioning slider A block  258 -S 1  has a horizontal slide hole through which the tensioning slide A  253  is inserted, see  FIG. 60 , which shows a partial front-view of a tensioning slider A  258 . And to the left and to the right of the horizontal slide hole of tensioning slider A  258 , two vertical holes through which the fixed vertical guides  260 , which are fixed to the frame of the CVT, are inserted. Near the top of the tensioning slider A block  258 -S 1 , the tensioning slider A clevis  258 -S 2  is shaped. The tensioning slider A clevis  258 -S 2  is used to mount a guiding wheel  200  or a tensioning wheel  61 . Tensioning slider B  259  is identical to tensioning slider A  258 , except that here the tensioning slider B block  259 -S 1  has a angled slide hole through which tensioning slide B  254  is inserted instead of the horizontal slide hole through which the tensioning slide A  253  is inserted. 
   Torque Transmitting Member for Chain ( FIGS. 61A ,  61 B,  62 A,  62 B,  63 A,  63 B,  64 A,  64 B,  65 A,  65 B,  66 ,  67 A,  67 B, &amp;  68 ) 
   In case a chain is preferred instead of a belt, then a torque transmitting member that can accommodate a chain can be designed. For example, if a slightly modified bicycle chain is used, then links forming a torque transmitting member chain or a single tooth link can be used. The front-view of a modified bicycle chain link is shown in  FIG. 61A , this chain link is identical to a regular bicycle chain link, except that here left chain link  1  side plate  268 -M 1  is deeper than right chain link  1  side plate  268 -M 2  and the bottom surfaces of the left chain link  1  side plate  268 -M 1  and left chain link  1  side plate  268 -M 1  are angled so that the chain link  1  pin  268 -M 3  is parallel to the shaft of its cone when that chain link rest on the surface of its cone. A front-view of another modified bicycle chain link is shown in  FIG. 61B , this chain link is identical to a regular bicycle chain link except that here a left chain link  2  rubber leg  269 -M 1  and right chain link  2  rubber leg  269 -M 2  are attached to the chain link plates so that chain link  2  pin  269 -M 3  is parallel to the shaft of its cone when that chain link rest on the surface of its cone. Now a torque transmitting member chain or a single tooth link that can be used with the modified bicycle chain described above will be described. Here,  FIG. 62A  shows a side-view of a link A  270 , as seen from the right side of the link, and  FIG. 62B  shows a front-view of a link A  270 . Each link A  270  consist of a link A tooth  270 -S 1 , which is shaped so that can properly engage with the pins of its chain, a left link A plate  270 -S 2 , a right link A plate  270 -S 3 , and a link A base  270 -S 4 , which connects the link A tooth to the left link A plate and the right link A plate. The link A tooth and the link A plates are parallel relative to each other. But the link A base  270 -S 4  is positioned at an angle relative to the link A tooth and the link A plates, so that when link A base  270 -S 4  is resting on the surface of the cone on which it is attached, the link A tooth and the link A plates are parallel relative to the end surface(s) of their cone. In case a single tooth link is used, then the link A plates are not needed. The left link A plate  270 -S 2 , which is longer than the right link A plate  270 -S 3 , and the right link A plate  270 -S 3  each have two rivet holes, which are used to insert link rivets  271 , used to connect links A  270  to links B  272  to from a torque transmitting member chain, see  FIGS. 63A and 63B . For smooth operation, it is recommended that the rivet holes are located so that when the links formed torque transmitting member is properly engaged with its chain, the bending axis of the links formed torque transmitting member chain coincides with the bending axis of the chain. Here, if this is the case, then a smooth arc can be drawn through the centers of the rivet holes and the centers of the pins of the chain. In addition to links A  270 , links B  272  will also be used to from a torque transmitting member chain. A torque transmitting member chain is formed by connecting a link A  270  to a link B  272 , which is then connected to another link A  270 , and so forth, so that a chain that consist of alternating links A  270  and links B  272  is formed. A link B  272  is identical to a link A  270 , except that the parallel distance between its link plates is slightly larger than that of link A  270  so that the link plates of a link A  270  can be placed between the link plates of a link B  272 . Link rivets  271  are then used to connect the ends of the left link plates of links A  270  to the ends of the left link plates of links B  272 ; and to connect the ends of the right link plates of links A  270  to the ends of the right link plates of links B  272 . The dimensions and materials of link rivets  271  should be selected so that once riveted together, the links A  270  can rotate with ease relative to their links B  272 . Also the base of each link A  270  and the base of each link B  272  should be short enough so that they do not interfere with the required flexing motion of the torque transmitting member chain. And if the left link plates interfere with the required flexing motion of the torque transmitting member chain, than they can be reshaped to accommodate this. An example of a reshaped left link plate, which is labeled as left link plate  274 , is shown in  FIG. 66 . 
   Furthermore, in order to attach a torque transmitting member chain to a cone assembly, the end links of the torque transmitting member chain each have a base to which a link attachment plate is attached. Each link attachment plate is identical to the attachment plate  1048  described in the Mover Mechanism section of this patent except that the disk shape at the top end of attachment plate  1048  is omitted. Hence the link attachment plates can be used to secure the end links to their cone and mover telescope in the same manner as an attachment plate  1048  is used to secure the ends of a torque transmitting member to its cone and mover telescope. The end link configuration for a link A  270 , and its link A attachment plate  270 -S 5 , which in its cone assembly&#39;s assembled state is slit into a slot of its cone and attached to a mover telescope, is shown as a side-view as seen from the right side of the link in  FIG. 64A  and as a front-view in  FIG. 64B . The end link for a link B  272  has an identical link attachment plate as a link A  270 . And in case single tooth link is used, which is shown in  FIGS. 65A and 65B , than that tooth link needs to have an attachment plate at its base. For the single tooth link shown in  FIGS. 65A and 65B , the tooth is labeled as single link tooth  273 -S 1 , the base is labeled as single link base  273 -S 2 , and the attachment plate is labeled as single link attachment plate  273 -S 3 . 
   In addition, in order to maintain the shape of the torque transmitting member chain, it is recommended that the torque transmitting member chain is maintained under slight tension. Hence the engaging surfaces of the slots should be narrow enough and have sufficient depth to maintain the proper alignment of the link attachment plates. 
   Also, a molded torque transmitting member made out of flexible material, such as rubber for example, can also be used to accommodate a chain. In cases, where torque transmission is between the side surfaces of the torque transmitting members and their transmission belts, the neutral-axis of the torque transmitting members and their transmission belts coincide, almost coincide, or can be easily made to coincide by proper reinforcement placement or dimensioning. As should be known by somebody skilled in the art, the location of the neutral-axis of a torque transmitting member can easily be adjusted by adjusting the location of the reinforcement, as shown in  FIG. 67A , and by adjusting the dimensions, as shown in  FIG. 67B . In  FIGS. 67A and 66B  solid lines represent actual reinforcement location or dimension and dotted lines represent adjusted reinforcement location or dimension. Here the height of the neutral-axis increases as the location of the reinforcement is raised or the height of the side members of the torque transmitting member is increased, and the height of the neutral-axis decreases as the location of the reinforcement is lowered or the height of the side members is decreased. The same method of adjusting the neutral-axis of a torque transmitting member can also be used for a transmission belt. Here the location of the neutral-axis can also be adjusted by adjusting the location of the reinforcement, if used, and by adjusting the dimensions. However, for a molded torque transmitting member that can engage with a bicycle chain, torque transmission is not between the side surfaces of the torque transmitting member and the chain, hence the neutral-axis does not coincide, almost coincide, or can be easily made to coincide with the bending axis of the chain, which is located at the center-point of the pins of the chain. Here in order to adjust the location of the neutral-axis of the torque transmitting member, compensating shapes have to be used. An example of a torque transmitting member that can engage with a bicycle chain, which will be referred to as a chain torque transmitting member is shown as a front-view in  FIG. 68 . Here the chain torque transmitting member, consist of a chain torque transmitting member tooth  275 -S 1 , a chain torque transmitting member base  275 -S 2 , a chain torque transmitting member left compensating shape  275 -S 3 , and a chain torque transmitting member right compensating shape  275 -S 4 . The dimensions for the chain torque transmitting member left compensating shape  275 -S 3  and the chain torque transmitting member right compensating shape  275 -S 4  should be selected such that when the chain torque transmitting member is properly engaged with its chain, the neutral-axis of the chain torque transmitting member coincides with the bending axis of the chain. 
   For the designs described above for optimum performance, the surface of the cone utilizing a torque transmitting member chain, a single link tooth, or a chain torque transmitting member, should be shaped to accommodate the base(s) of the torque transmitting member chain links, single link tooth, or a chain torque transmitting member so that during operation no or minimal deformation of the transmission chain occurs as it comes in and out of contact with its torque transmitting member. This can be achieved by increasing the thickness of the side surface(s) of the cone which are never covered a torque transmitting member chain, single link tooth, or chain torque transmitting member, as to compensate for the thickness of the base(s) of the torque transmitting member chain links, single link tooth, or a chain torque transmitting member. 
   Using the description above, somebody skilled in the art should be able to construct a torque transmitting member for other chains, such as an inverted chain for example. And he/she should also be able to construct a torque transmitting member made out of chain links for various transmission belts. Here for smooth operation, the bending axis of the torque transmitting member made out of chain links, which location is determined by the location of the chain rivet holes, should coincide with the neutral-axis of its transmission belt. 
   Torque Transmitting Side Members ( FIGS. 69 ,  70 A,  70 B,  70 C) 
   Previously it was mentioned that a torque transmitting member can be constructed out of two separate side members. For smooth operations, it is recommended that the location of the height center-line of the teeth used for torque transmission of the side members and the neutral-axis of the side members, which under this configuration will be referred to as torque transmitting side members, are located in the same horizontal plane, see  FIG. 69 . In  FIG. 69 , the torque transmitting member is formed by a left torque transmitting side member  280 A and by a right torque transmitting side member  280 B. 
   A detailed view of a torque transmitting side member  280 , which can be used as a left torque transmitting side member, is shown in  FIG. 70A , which shows a partial top-view, in  FIG. 70B , which shows a side-view, and in  FIG. 70C , which shows an end-view. Here on the right surface of torque transmitting side member  280 , its side member teeth  280 -S 1  are formed. And since torque transmitting side member  280  does not have a base that connects it to its opposite torque transmitting side member, which helps maintain the longitudinal shape of the torque transmitting member as torque is being transmitted, here on the left surface of torque transmitting side member  280 , a lateral bending reinforcement  280 -S 2  is formed. Furthermore, in order to attach torque transmitting side member  280  to its cone, side member attachment pins  281  are inserted near each end of torque transmitting side member  280 . The side member attachment pins  281  are tied together by a side member reinforcement  282 , which is a rope embedded in the torque transmitting side member  280  that has looped shaped ends into which the side member attachment pins  281  are inserted. It is recommended that side member reinforcement  282  is located in the same horizontal plane as the center-line of side member teeth  280 -S 1 . Furthermore, for attachment purposes each side member attachment pin  281  has a side member attachment plate  281 -S 1  shaped at its bottom end. In the assembled state of a cone assembly utilizing torque transmitting side members, the side member attachment plates  281 -S 1  are slid into the slots of their cone and then secured using an attachment wheel and a mover telescope, in the same manner as the torque transmitting member  1046  described earlier are attached to their cone. Here a pair of mover telescopes is needed for each torque transmitting side member. Hence here, a complete torque transmitting member needs four mover telescopes mounted on a common rotor instead of two, unless another method of attachment is used, such as joining the side member attachment plates of a pair of torque transmitting side members together so that only one mover telescopes is needed for the two side member attachment plates, which are joined together. And joining the side member attachment plates of a pair of torque transmitting side members together also increases the lateral stability of the torque transmitting side members. It is also recommended that frictional engagement between the members of the mover telescopes is used as to prevent the mover telescope members from sliding up and down relative to each other as its cone assembly is rotating. For even better performance, the frictional engagement between the members of the mover telescopes can be selected such that the mover telescopes extend and contract in a predetermined fashion. For example, for a three member mover telescope, the frictional engagement of the top mover telescope member with the middle mover telescope member can be made lower than the frictional engagement of the middle mover telescope member with the bottom mover telescope member so that when extended, the top mover telescope member extends before the middle mover telescope member does. Besides mover telescopes, slider and slides, which can also be used to transmit torque, can also be used to change the axial position of a torque transmitting side member or a torque transmitting member. Here the slider is preferably attached to the outer side surface of a torque transmitting member at the length mid-point of the torque transmitting member. And its slide can be welded, so that it extends radially outwards, on a collar that can be keyed to the shaft on which the torque transmitting member is rotating about. And the ends of the torque transmitting member can again be attached to their cone by the use of attachment plates. However, here the attachment plates are not used to transmit torque. Also here the torque transmitting member needs to be stiff enough or properly reinforced so that it can maintain its shape when torque is transmitted near its ends and when its teeth are only partially engaged. Furthermore, for a CVT  2 , instead of having the base of the transmission belts angled, the leveling loop used for a CVT  1  can also be used here. 
   Alternate Cone Assemblies ( FIGS. 71 ,  72 ,  73 A,  73 B,  74 A,  74 B,  75 ,  76 ) 
   An example of other CVT&#39;s that can benefit from the concepts and adjuster systems of this application are slightly modified CVT  2 s that instead of the cone assemblies with torque transmitting members, uses a single tooth cone, which is a cone that has one fixed tooth  290 -S 3  that elongates from the single tooth cone smaller end  290 -S 1  to the cone&#39;s larger end on the single tooth cone side surface  290 -S 2 , as shown as a top-view in  FIG. 71 . The main difference here is that for these CVT&#39;s an inverted chain or belt, for which an example is shown in  FIG. 73A , which shows a side-view, and in  FIG. 73B , which shows as sectional-view, has to be used. Another difference is that in most cases a fixed tooth  290 -S 3  covers a smaller arc length on the surface of its cone than torque transmitting members does. As described in this patent, for proper operation of a CVT  2 , it is recommended that during its operation at all instances a torque transmitting surface is engaged with its transmission belt. Here, because of the smaller arc length covered by the fixed tooth  290 -S 3 , the transmission ratio range is most likely more limited. Since here for proper operation, for all transmission ratios at least half of the surfaces of the single tooth cones need to be covered by their transmission belts. 
   One method to increase the transmission ratio range for a single tooth cone CVT  2  is by using a supporting wheel, which is used to increase the coverage of the transmission belt on the surface of its cone for transmission ratios where it is required. In order to properly adjust the position of the supporting wheel as the transmission ratio is changed, a slide and a slider similar to the ones used for a tensioning wheel can be used for the supporting wheel. An example of this configuration is shown in  FIG. 76 , which shows a sectional-view of a single tooth cone CVT  2  cut near the smaller end of one of its cones, which is labeled as single tooth cone  290 , where its transmission belt, labeled as inverted belt  292 , is currently positioned. The inverted belt  292  is used to couple single tooth cone  290  to an inverted belt pulley  295 . And the tensioning wheel, which here is labeled as inverted belt tensioning wheel  294  and the supporting wheel  296  are positioned on the tense side of the belt. Placing the inverted belt tensioning wheel  294  and the supporting wheel  296  on the slack side of the belt should also work; however here it might be necessary to take precautions that prevent the transmission belt to lose contact with its tensioning wheel due to excessive slack. In some set-ups, placing the supporting wheel opposite of the tensioning wheel will also work. Furthermore, if desired supporting wheels can also be used in CVT&#39;s that use cone with a torque transmitting members. As for a CVT  2  utilizing cone assemblies, here the tensioning wheels and supporting wheel should also have side surface to help maintain the axial position of their transmission belt. And the base of the tensioning wheels and supporting wheels should also be shaped or tapered so as to prevent its transmission belt or chain from twisting. 
   Another method to increase the transmission ratio range for a single tooth cone CVT  2  is by using an adjuster to compensate for the limited coverage of the single tooth cones. Here in instances where the transmission belts are not providing sufficient coverage, the adjuster(s) rotate the cone currently not engaged in the direction that the cone is rotating a sufficient amount so that the cone currently not engaged comes into engagement before the cone currently engaged comes out of engagement. 
   Also in order to prevent bending of a tooth of a transmission belt due to the moment created by the force applied by the fixed tooth on a tooth of the transmission belt, a supporting surface can be shaped on the side surface of a single tooth cone, see  FIG. 72 . In  FIG. 72 , which shows as a top-view, the smaller end of the cone is labeled as supported single tooth cone smaller end  291 -S 1 , the side surface of the cone is labeled as supported single tooth cone side surface  291 -S 2 , the fixed tooth is labeled as supported single tooth cone fixed tooth  291 -S 3 , and the supporting surface is labeled as supported single tooth cone supporting surface  291 -S 4 . For smoother operation and less flexing of the teeth of the transmission belt used, it is recommended, but not necessary that the supported single tooth cone supporting surface  291 -S 4  is shorter than the supported single tooth cone fixed tooth  291 -S 3 . The inverted belt shown in  FIG. 73A  and in FIG.  73 B can also be used with this cone. Here the supported single tooth cone supporting surface  291 -S 4  has to be positioned and shaped so that it can properly engage with the back surfaces of the teeth of the inverted belt. 
   And a specialized transmission belt that can be used with a supported single tooth cone is shown as a top-view in  FIG. 74A  and as a side-view in  FIG. 74B . This transmission belt, which is labeled as supported single tooth cone inverted belt  293  has a tooth constraining surface  293 -S 1  shaped at the base of its tooth which can engage with the supporting surface of its cone. The engagement of the tooth constraining surface  293 -S 1  with the supported single tooth cone supporting surface  291 -S 4  prevents excessive twisting of the tooth of a transmission belt. For smoother engagement and less flexing of the tooth constraining surfaces  293 -S 1 , it is recommended that the surface of the tooth constraining surface  293 -S 1  is rounded about the z-axis, which is the axis that is horizontal and parallel to the engagement surfaces to the teeth. The supported single tooth cone supporting surface  291 -S 4  should be positioned so that it is parallel to the supported single tooth cone fixed tooth  291 -S 3 . Here for better engagement some fine adjustment to the position of the single tooth cone supporting surface  291 -S 4  based on experimentation to account for the changing curvature of the side surface of the cone and the flexing of the bases of the teeth of the supported single tooth cone inverted belt  293  can also be made. Here if the supported single tooth cone supporting surface  291 -S 4  is not parallel to the supported single tooth cone fixed tooth  291 -S 3 , it is recommended that the surface of the tooth constraining surface  293 -S 1  is rounded about the y-axis, which is the axis that is vertical. Also if an inverted belt that has a constraining surface shaped on its teeth is used, only the surfaces of the teeth that do not have a constraining surface should be used for torque transmission. 
   Many variation of a single tooth cone can be devised. For example, instead of being straight, the fixed tooth and the supporting surface, if used, can be positioned at an angle relative to the surface of their cone; or an involute or modified involute shaped surfaces can be used for the fixed tooth and/or the supporting surface; or an inverted chain which has links for which a tooth profile is cut out, which engagement with the fixed tooth help maintain the orientation of the link currently engaged during torque transmission, can also be used. Such an inverted chain can be construct from links and pins in a similar manner as the chains described in the Torque Transmitting Member for Chain section are constructed. However here, it is desirable to have the centers of the pins of the chain located at the height mid-point of the tooth cut out profile at the mid-cross-sections of the link or mid-section of a pair of parallel links. If this the case, then torque transmission does not cause the link transmitting torque to bend out of its ideal alignment. This allows the tooth cut-out profile of a link to be slightly wider than its mating fixed tooth, since the engagement of the back surface of the fixed tooth with the tooth cut-out profile of a link is not needed in order to main ideal alignment of that link.  FIG. 75  shows a side-view of such a chain link. Here the chain link, which is labeled as inverted chain link  297 , has a inverted chain pin hole  297 -S 1  and an inverted chain tooth cut out profile  297 -S 2 . 
   Basically a cone with a single fixed tooth, can be treated like a cone with a torque transmitting member except that here the coverage provided by a fixed tooth is most likely less than the coverage provided by a torque transmitting member. Also here an inverted belt or chain has to be used as a transmission belt. The main disadvantage of a cone with a single fixed tooth over a cone with a torque transmitting member is that here uneven wear of the fixed tooth can cause problem during transmission ratio change; and an inverted belt or chain is most likely less efficient in transmitting torque than a belt or chain that can be used with a cone with a torque transmitting member. 
   Reinforced Transmission Belt ( FIG. 77 ) 
   Since the adjusters can minimize transition flexing, it is desirable to stiffen the transmission belt using reinforcement. A reinforced transmission belt  300  is shown as a top-view in  FIG. 77 . Here a steel reinforcement plate  301  is embedded at each reinforced transmission belt tooth  300 -S 1 . The steel reinforcement plate  301  is then connected to a wire reinforcement  302 . 
   Alternate CVT&#39;s 
   Below is an alternate belt, which will be referred to as the pin belt that can be used as a means for coupling for a CVT  2 . This belt, which is shown as side-view in  FIG. 78A  and as an end-view in  FIG. 78B , can be used with torque transmitting members that have sprocket shaped tooth or teeth. This belt consists of two rubber belt members, belt member  1   411  and belt member  2   412 , that are joined by pins  414 , which are tightly and securely pressed into the belts. Adhesives can be added to the portions of the pins inserted into the belt members to further secure the axial position of the pins relative to the belt members. On the pins  414 , tubes  415  are placed. The tubes are not absolutely necessary but they reduce the friction between the belts and the torque transmitting members during initial engagement. Hence it is recommended that friction between the tubes and the pins is minimized. If desired, the tubes can also be omitted. The neutral-axis of belt member  1   411  and belt member  2   412  should be at the same height, and the center of pins  414  should be located at the neutral-axis of belt member  1   411  and belt member  2   412 . The area of belt member  1   411  is equal to the area of belt member  2   412 , this is optional but recommended. In order to have the neutral-axis of belt member  1  and belt member  2  at the same height, the height of belt member  1  and belt member  2  is adjusted accordingly. And in order to have the area of belt member  1  equal to the area of belt member  2 , the width of belt member  1  and belt member  2  is adjusted accordingly. In case only one tooth is used than the pins do not have to be located at the neutral-axis of their belt members, but it should be ensured that the tooth can properly engage with its belt for all diameters. For increased strength belt member  1  and belt member  2  are reinforced. In  FIG. 78B , the reinforcement, which is labeled as reinforcement  416  is molded into belt member  111  and belt member  2   12 . Since it is desirable to have the reinforcement located at the neutral-axis, in this case the ends of the pins can have pins cut  414 -S 1  into which the reinforcement can be slid-in. Furthermore in order to help align the belt when it is about to be engaged with its torque transmitting member, the upper outer surfaces of belt member  1  and belt member  2  are tapered inwards so that they can be better guided by tensioning/maintaining pulleys. In case no adjuster or adjustment device is used, the pin belt should be flexible enough so that it can stretch without failure to account for instances were the arc length(s) of the non-torque transmitting arc(s) of the cone(s) with which is used, do not correspond to a multiple of the width of the teeth or tooth of the cone assembly or cone assemblies with which is used. If necessary the reinforcement  416  can be omitted to ensure this or the transmission ratios where transition flexing occurs can be skipped. 
   A cone assembly that can be used with this belt and a chain is a cone assembly with a one tooth or two oppositely placed teeth, although many other conceivable cone assemblies could also be used. A design for a cone assembly with one tooth is shown as a front-view for which the front half surface of a cone  440  and its larger end cover  445  has been removed in  FIG. 79 , and as a partial sectional right-end-view in  FIG. 80 . It mainly consists of a cone  440 , which right-end-view is shown in  FIG. 81 , that has a smaller end surface  440 -S 2  and an open larger end, which has flange  440 -S 4 , which is used to bolt on a larger end cover  445 , shown in  FIG. 82 . Cone  440  has a longitudinal cut  440 -S 1 , which is located on a radial plane of spline  430 , through which the tooth of a tooth carriage  450  can protrude. The tooth carriage  450 , which is also shown in  FIG. 80 , consists of tooth  450 -S 1 , which can engage with a pin or tube of a pin belt. It also has two radial slide holes  450 -S 2  and a longitudinal slide hole  450 -S 3 . The cone  440  is slid onto a spline  430 , which is shaped like a round shaft for which material has been removed so that a cross profile is formed. The outer surfaces of spline  430  form sections of a round shaft so that a matching round sleeve that can freely rotate relative spline  430  can be slid onto spline  430 . Also spline  430  is used so that torque from the cone assemblies can be transferred to the spline and vice-versa, hence the smaller end of cone  440  has a profile that matches the profile of spline  430 . For better performance purposes, the spline profile on the smaller end of cone  440  is shaped into a round rod, made out of a low friction material such as oil-impregnated bronze for example. This round rod is then tightly and securely pressed into the smaller end of cone  440 , so as to prevent any movement between it and smaller end of cone  440 . If very large loads are transmitted between spline  430  and its cone assembly, then in order to avoid any movement between the round rod, pressed into the smaller end of cone  440 , and smaller end of cone  440 , the round rod can be replaced with a square or hexagonal rod made out of a low friction material into which the spline profile is shaped. 
   In order to mount the tooth carriage  450  to cone  440 , two radial slides  460  and one longitudinal slide  480  are used. The radial slides  460  are parallel to each other and extend radially outwards from spline  430 . They are fixed to a radial slides sleeve  461  that can freely slide and freely rotate relative to spline  430 . The radial slides  460  should be long enough so that they are engaged with their tooth carriage at the smallest pitch diameter and the largest pitch diameter of their cone. Although this is not absolutely required, in order to reduce the vibration due to the centrifugal force of the tooth carriage  450  and its mounting parts, a radial counter-balance slide  462  is fixed opposite of the radial slides  460  on the radial slides sleeve  461 . The dimension of the radial counter-balance slide  462  should designed so that it weighs the same amount as the two radial slides  460 , and it should be positioned in between the two radial slides an equal distance from each radial slide. The radial counter-balance slide  462  is used to control the axial position of a counter-balance  464  described later. Furthermore, at each end of the radial slides sleeve  461 , an oversized flange is shaped. The longitudinal slide  480  is parallel to the centerline of longitudinal cut  440 -S 1  of cone  440 , on the removed surface of cone  440 . Because of the radial slides  460 , which are positioned so that they can extend out through the longitudinal cut  440 -S 1  of the cone, the longitudinal slide cannot be placed directly below the longitudinal cut of the cone, hence the longitudinal slide  480  is placed either sufficiently in front of the longitudinal cut or to the back of the longitudinal cut. The ends of the longitudinal slide are threaded for mounting purposes. In order to mount the longitudinal slide to the cone  440 , the smaller end of the cone, see  FIG. 81 , has a cone slide mounting hole  440 -S 3  through which the longitudinal slide can be slid in. At the outer surface of this hole, a tapered surface that can properly engage with a longitudinal slide nut  481  that is used to secure this end of the longitudinal slide to the smaller end of cone  440  is shaped. In order to mount the other end of the longitudinal slide to the cone, first the larger end cover  445  is bolted on to the cone using cover nuts  446  and cover bolts  447 , that are inserted through radially positioned holes on flange  440 -S 4  of the cone and the matching holes on the larger end cover  445 . The larger end cover  445  of the cone, for which a left-end-view is shown in  FIG. 82 , also has an end cover longitudinal slide hole  445 -S 1  through which the longitudinal slide  480  can be slid in. At the outer surface of this hole, a tapered surface that can properly engage with a nut that is used to secure this end of the longitudinal slide to the larger end cover is also shaped. Also spline  430  is used so that torque from the cone assemblies can be transferred to the spline and vice-versa, hence the larger end cover  445  has a profile that matches the profile of spline  430 . For better performance purposes, the spline profile on the larger end cover  445  is shaped into round rod, made out of a low friction material such as oil-impregnated bronze for example. This round rod is then tightly and securely pressed into the larger end cover  445 , so as to prevent any movement between it and larger end cover  445 . If very large loads are transmitted between spline  430  and its cone assembly, then in order to avoid any movement between the round rod, pressed into the larger end cover  445 , and larger end cover  445 , the round rod can be replaced with a square or hexagonal rod made out of a low friction material into which the spline profile is shaped. 
   Although this is not absolutely necessary, in order to reduce or eliminate vibrations due to the centrifugal forces, a counter-balance longitudinal slide  482  is mounted opposite of the longitudinal slide  480 . However, unlike the longitudinal slide, which is parallel to the tapered surface of the cone, the counter-balance longitudinal slide is parallel to spline  430 , this will simplify the design considerably, although using this configuration, the counter-balance  464 , which should have the same weight as the tooth carriage  450  and which has a vertical hole that can engage with the radial counter-balance slide  462 , mounted on the counter-balance longitudinal slide  482 , will not always be positioned perfectly opposite of the tooth carriage  450 , hence the cone assembly will not always be perfectly balanced. In order to perfectly balance the cone assembly, a set-up identical to the tooth carriage, except that its tooth carriage is toothless while still having the same weight can be used. The counter-balance longitudinal slide  482  is mounted to the cone assembly in a similar manner as longitudinal slide  480 . Here for cone  440 , a counter-balance longitudinal slide hole  440 -S 5 , through which one end of the counter-balance longitudinal slide  482  can be slid through, exist. And for the larger end cover  445 , an end cover counter-balance longitudinal slide hole  445 -S 2  exist. 
   A slightly modified cone  440  that has two oppositely positioned tooth carriages  450 , which are both toothed, can be used in a CVT  1 . For this CVT  1  an adjuster can be used to increase the duration at which the transmission ratio can be changed, but no adjuster can be used to reduce transition flexing. Therefore, sufficient flexing in the pin belts needs to be allowed or the transmission ratios where transition flexing occurs can be skipped. 
   In order to mount the tooth carriage  450  to the radial slides  460 , the tooth carriage has two parallel radial slider holes  450 -S 2 , which should have an inner surface made out of a low friction material, that are straddling the tooth  450 -S 1  of the tooth carriage  450 . Here the radial slides are simply slid into the radial slider holes of the tooth carriage. In order to mount the tooth carriage to the longitudinal slide  480 , a longitudinal slider hole  450 -S 3 , which should also have an inner surface made out of a low friction material, exists on the tooth carriage. Here the longitudinal slide is simply slid into the longitudinal slider hole  450 -S 3 . Also, in order to mount the radial slides sleeve  461  to spline  430 , radial slides sleeve  461  is slid onto spline  430  and then its axial position is secured by two spline collars  470  that are sandwiching the radial slides sleeve  461 . For better performance, a radial slides sleeve axial bearing  72 , which is a washer shaped item made out a low friction material, is placed between each spline collar  470  and the radial slides sleeve  461 . In order secure the axial position of the spline collar  470  and hence the axial position of radial slides sleeve  461 , at the positions where a spline collar  470  needs to be attached, a portion of the outer surface of spline  430  is machined down. The spline collar  470 , which is of the split collar type (two halves joined and secured by set screws), has the profile of the machined down portion of spline  430 . An end-view of a spline collar  470  mounted on a machined down portion of spline  430  is shown in  FIG. 83 . 
   Furthermore, a CVT needs two cones  440  in order to operate. The mounting of each cone is slightly different. Hence one cone assembly is labeled as front sliding tooth cone assembly  420 A and the other cone assembly is labeled as back sliding tooth cone assembly  420 B. Front sliding tooth cone assembly  420 A is identical to back sliding tooth cone assembly  420 B, the only difference between them is the front end portions of their cones used for mounting purposes, and the back end portions of their larger end covers used for mounting purposes. For front sliding tooth cone assembly  420 A, shown in  FIG. 79  and  FIG. 81 , the front end of cone  440  has a front cone bearing stop surface  440 A-S 1 ; a front cone bearing shaft  440 A-S 2 , on which a mounting bearing is slid on; and a front cone locking ring groove  440 A-S 3 , which is shaped on the front cone bearing shaft  440 A-S 2  and is used to lock the axial position of the mounting bearing relative to cone  440 . The larger end cover  445  of front sliding tooth cone assembly  420 A, see  FIGS. 79 and 82 , has front cone larger end cover bearing stop surface  445 A-S 2 ; and a front cone larger end cover bearing shaft  445 A-S 3 , on which a mounting bearing for larger end cover  445  is slid on. For back sliding tooth cone assembly  420 B, which is shown in  FIG. 84  and which uses a back cone  440 B, the front end of back cone  440 B has a back cone bearing stop surface  440 B-S 1 , which has the same diameter as the front cone bearing stop surface  440 A-S 1 ; and a back cone bearing shaft  440 B-S 2 , on which the mounting bearing is slid on, this shaft has the same diameter as the front cone larger end cover bearing shaft  445 A-S 3 . The larger end cover for back sliding tooth cone assembly  420 B, which is also shown in  FIG. 84  is labeled as back cone larger end cover  445 B. Back cone larger end cover  445 B is identical to larger end cover  445  except for the shaft and shoulder items used for mounting purposes described below. Back cone larger end cover  445 B has a back cone larger end cover bearing stop surface  445 B-S 1 , which has the same diameter as the front cone bearing stop surface  440 A-S 1 ; a back cone larger end cover bearing shaft  445 B-S 2 , which has the same diameter as the front cone bearing shaft  440 A-S 2  and on which a mounting bearing for back cone larger end cover  445 B is slid on; and a back cone larger end cover locking ring groove  445 B-S 3 , which is shaped on the back cone larger end cover bearing shaft  445 B-S 2  and is used to lock the axial position of the mounting bearing relative to cone  440 . 
   In order to transmit torque from or to the cone assemblies a gear  500 , shown in  FIG. 86 , is used. In order to mount a gear  500 , which has a gear set screw sleeve  500 -S 1 , to spline  430 , a spline shaft extension  432 , shown in detail as a front-view in  FIG. 85A  and as a top-view in  FIG. 85B , is used. The spline shaft extension  432 , is shaped like round shaft, that along its length has three different diameters. At its left end, spline shaft portion A  432 -S 1  is shaped, which diameter is smaller than the next shaft portion which is spline shaft portion B  432 -S 2  so that a shaft shoulder is formed between spline shaft portion A  432 -S 1  and spline shaft portion B  432 -S 2 . Also, the end of spline shaft portion A  432 -S 1  has a cavity that is shaped like spline  430  but is slightly smaller than the shape of spline  430 , so that spline  430  can be tightly and securely pressed into spline shaft portion A  432 -S 1 . And near the right end of spline shaft portion B  432 -S 2 , a hole that runs through surface to surface exist, this hole will be used for the set-screw of a gear  500 . After spline shaft portion B  432 -S 2 , spline shaft portion C  432 -S 3  is shaped. Spline shaft portion C  432 -S 3  has a diameter that is smaller than the diameter of spline shaft portion B  432 -S 2  so that a shaft shoulder is formed between spline shaft portion B  432 -S 2  and spline shaft portion C  432 -S 3 . 
   An assembled CVT  2  input/output shaft utilizing a front sliding tooth cone assembly  420 A and a back sliding tooth cone assembly  420 B is shown as a side-view in  FIGS. 86 and 87  and as a top-view in  FIG. 88 . In  FIG. 86 , the tooth carriages  450  are positioned near the smallest end of their cone and in  FIG. 87 , the tooth carriages  450  are positioned near the largest end of their cone. 
   In order to assemble the CVT, first spline shaft extension  432  is securely pressed into spline  430 , so that it is axially and radially fixed to spline  430 . Then gear  500  is secured to spline shaft portion B  432 -S 2  of spline shaft extension  432  using a set-screw. Next spline  430  is slid into a spline bearing A  490 A until the left shoulder of spline shaft extension  432  engages with the side surface of spline bearing A  490 A facing it, obviously it should be a surface that allows the left shoulder of spline shaft extension  432  to rotate easily relative to the frame on which spline bearing A  490 A is mounted. Next spline bearing A  490 A is secured to a frame using bolts that engage with a spline bearing A mounting base  490 A-S 1 . Next the spline bearing B  490 B is slid into spline shaft portion C  432 -S 3  until the right shoulder of spline shaft extension  432  engages with the side surface of spline bearing B  490 B facing it, obviously it should be surface that allows the right shoulder of spline shaft extension  432  to rotate easily relative to the frame on which spline bearing B  490 B is mounted. Next spline bearing B  490 B is secured to a frame using bolts that engage with a spline bearing B mounting base  490 B-S 1 . 
   Once spline  430  is secured into position, front sliding tooth cone assembly  420 A and back sliding tooth cone assembly  420 B will be mounted on spline  430 . In order to reduce the stress on spline  430 , the cone assemblies are supported by cone supporting members. A cone supporting member is shaped like a 90 degree L with equal length legs. At the intersection of the legs a cone bearing, which has a round shaft shape low friction inner surface, exist. At the end of each leg a support slider, which also has a round shaft shape low friction inner surface, exist. Here, the cone bearings will be slid into the front or back portion of the cone assemblies; and one support slider will be slid unto a vertical supporting pipe  510 , which is shaped like a round pipe, and the other support slider will be slid unto a horizontal supporting pipe  515 , which is also shaped like a round pipe. Therefore, first a cone axial bearing  492  is slid into the front cone bearing shaft  440 A-S 2 . Then cone bearing A  491 A-S 1  of cone supporting member A  491 A is slid into the front cone bearing shaft  440 A-S 2 . Next another cone axial bearing  492  is slid into the front cone bearing shaft  440 A-S 2 . And finally a cone locking ring  493  is inserted into front cone locking ring groove  440 A-S 3 . Here due to engagement of the front cone bearing stop surface  440 A-S 1  and the cone locking ring  493  with the cone axial bearings  492  sandwiching the cone bearing A  491 A-S 1 , the axial position of front sliding tooth cone assembly  420 A is fixed relative to the axial position of cone bearing A  491 A-S 1 . Next the vertical support slider A  491 A-S 3 , which is connected to cone bearing A  491 A-S 1  by a vertical support rod A  491 A-S 2 , is slid into the vertical supporting pipe  510 , while at the same time the horizontal support slider A  491 A-S 5 , which is connected to the cone bearing A  491 A-S 1  by a horizontal support rod A  491 A-S 4 , is slid into the horizontal supporting pipe  515 , see  FIGS. 86 and 88 . During this assembly stage only the right end of the vertical supporting pipe  510  and the horizontal supporting pipe  515  are supported by a pipe support  511 , the rest of the supporting pipes can be supported by temporary supports, which can be repositioned as required during the assembly stage, so that the vertical supporting pipe  510  and the horizontal supporting pipe  515  are parallel to spline  430 . The temporary supports should be used until the left ends of the vertical supporting pipe  510  and the horizontal supporting pipe  515  are support by pipe supports  511 . A pipe support  511  is shaped like a cylinder with one open end and one closed that can be tightly slid onto one end of a supporting pipe. In addition, pipe support  511  has a pipe support leg  511 -S 1 , which extends radially outward and runs lengthwise along pipe support  511 ; and at the end of pipe support leg  511 -S 1 , a pipe support base plate  511 -S 2  used to bolt pipe support  511  to the frame of the CVT exist. 
   Next the longitudinal slide  480  is slid through the cone slide mounting hole  440 -S 3 , bolted to the front surface of that hole, and temporarily support. Then the counter-balance longitudinal slide  482  is also bolted on to the front surface of the cone and temporarily supported, see  FIGS. 79 and 81 . Next the spline collar  470  is fastened to the machined down portion of spline  430  adjacent to the smaller end of cone  440  and a radial slides sleeve axial bearing  472  is slid onto spline  430 . Next the tooth carriage  450  is slid into the radial slides  460  of radial slides sleeve  461 , and the counter-balance  464  is slid unto the radial counter-balance slide  462  of radial slides sleeve  461 . Then the tooth carriage  450  is aligned with the longitudinal slide  480 , the counter-balance  464  is aligned with the counter-balance longitudinal slide  482 , and the radial slides sleeve  461  is aligned with spline  430 . Once properly aligned the tooth carriage  450 , the counter-balance  464 , and the radial slides sleeve  461  are slid unto the items they were aligned with. Then another radial slides sleeve axial bearing  472  is slid unto spline  430 . Then the radial slides sleeve  461  with its radial slides sleeve axial bearings  472  are secured to spline  430  so that they are axially fixed to spline  430  but are able to rotate relative to spline  430  using another spline collar  470 . Next, the unsupported end of the longitudinal slide  480  and the counter-balance longitudinal slide  482  are slid into their designated holes of larger end cover  445 , and the larger end cover  445  is secured to cone  440  of front sliding tooth cone assembly  420 A using cover nuts  446  and cover bolts  447 . Then the longitudinal slide  480  and the counter-balance longitudinal slide  482  are secured to larger end cover  445  using bolts. 
   Next a cone axial bearing  492 , is slid unto front cone larger end cover bearing shaft  445 A-S 3  and this end of front sliding tooth cone assembly  420 A is supported by sliding in cone bearing B  491 B-S 1  of cone supporting member B  491 B into front cone larger end cover bearing shaft  445 A-S 3 , see  FIGS. 79 and 86 . Next the vertical support slider B  491 B-S 3 , which is connected to the cone bearing B  491 B-S 1  by a vertical support rod B  491 B-S 2 , is slid into the vertical supporting pipe  510 , while at the same time the horizontal support slider B  491 B-S 5 , which is connected to the cone bearing B  491 B-S 1  by a horizontal support rod B  491 B-S 4 , is slid into the horizontal supporting pipe  515 , see  FIGS. 86 and 88 . 
   Then a cone axial bearing  492  is slid onto back cone bearing shaft  440 B-S 2  of back sliding tooth cone assembly  420 B, see  FIGS. 84 and 86 , and back cone  440 B is slid unto spline  430 , in an orientation where the slot for tooth carriage  450  of back sliding tooth cone assembly  420 B is positioned opposite of the slot for tooth carriage  450  of front sliding tooth cone assembly  420 A until the front cone bearing shaft  440 A-S 2  is sufficiently inserted into the open end of cone bearing B  491 B-S 1  so that the cone axial bearing  492  mounted on back cone bearing shaft  440 B-S 2  is tightly sandwiched by the back cone bearing stop surface  440 B-S 1  and the open end surface of cone bearing B  491 B-S 1 . Next the longitudinal slide  480 , counter-balance longitudinal slide  482 , spline collars  470 , radial slides sleeve axial bearings  472 , radial slides sleeve  461 , tooth carriage  450 , counter-balance  464 , and back cone larger end cover  445 B of back sliding tooth cone assembly  420 B are attached in the same manner as the same or similar parts of front sliding tooth cone assembly  420 A are attached. 
   Then the larger end of back sliding tooth cone assembly  420 B is supported by first sliding in a cone axial bearing  492  into the back cone larger end cover bearing shaft  445 B-S 2  and then sliding in cone bearing C  491 C-S 1  of cone supporting member C  491 C unto back cone larger end cover bearing shaft  445 B-S 2 , while at the same time the vertical support slider C  491 C-S 3 , which is connected to the cone bearing C  491 C-S 1  by a vertical support rod C  491 C-S 2 , is slid into the vertical supporting pipe  510 , and the horizontal support slider C  491 C-S 5 , which is connected to the cone bearing C  491 C-S 1  by a horizontal support rod C  491 C-S 4 , is slid into the horizontal supporting pipe  515 , see  FIGS. 84 ,  86  and  88 . Next another cone axial bearing  492  is slid into back cone larger end cover bearing shaft  445 B-S 2 . Then a cone locking ring  493  is inserted into back cone larger end cover locking ring groove  445 B-S 3 . And finally, a pipe support  511  is slid onto the left end of vertical supporting pipe  510  and onto the left end of horizontal supporting pipe  515 , and then secured to the frame of the CVT. Since now the supporting pipes are supported by the pipe supports  511 , the temporary supports can be removed. 
   In order to attach the actuator used to change the transmission ratio to the CVT  2  input/output shaft described above, a cone supporting member actuator bar  1700  is attached to each cone supporting member, which for the CVT  2  input/output shaft described above are cone supporting member A  491 A, cone supporting member B  491 B, and cone supporting member C  491 C. For each cone supporting member, the cone supporting member actuator bar  1700  is positioned so that it connects the horizontal support slider, which slides on a horizontal supporting pipe  515 , with the vertical support slider, which slides on a vertical supporting pipe  510 , of a cone supporting member. The cone supporting member actuator bar  1700  can be seen in  FIG. 89 , which show a front-view of a CVT utilizing a CVT  2  input/output shaft. The cone supporting member actuator bar  1700  should be shaped so that it does not interfere with any parts of the CVT  2  input/output shaft during transmission ratio change. In order to connect all cone supporting members to the actuator used to change the transmission ratio, each cone supporting member actuator bar has a actuator bar hole  1700 -S 1  at its the mid-length, see  FIG. 89 . Through each actuator bar hole  1700 -S 1  of the cone supporting member actuator bars, an actuator threaded rod  1701  is inserted; and the position of the cone supporting members relative to each other and relative to the actuator threaded rod  1701  is secured by having nuts, screwed on the actuator threaded rod  1701 , that clamp each cone supporting member actuator bar  1700 . This can be seen in  FIG. 90 , which show a partial top-view of a CVT utilizing a CVT  2  input/output shaft. In order to connect the CVT  2  input/output shaft to the actuator used to change the transmission ratio, on one end of the actuator threaded rod  1701 , a threaded rod holed bar  1702  is attached. The threaded rod holed bar  1702  can then be used to connect a linear actuator, used to change the transmission ratio, to actuator threaded rod  1701 . In  FIG. 13 , the linear actuator is connected to actuator threaded rod  1701  using a clevis and a locking pin. For proper operation the linear actuator should have a linear position sensor. 
   The design methods for the tooth carriage cone assembly described above, can also be used to design a cone assembly with one torque transmitting member, which here is labeled as pin belt torque transmitting member  590 , and one non-torque transmitting member, which here is labeled as pin belt non-torque transmitting member  690  and is used to counter-balance the centrifugal force of pin belt torque transmitting member  590  and help maintain the alignment of the transmission belt when the transmission belt is not engaged with the torque transmitting member. Here this cone assembly, which labeled as front pin belt cone assembly  520 A is shown in as a front-view where portions of it front surface has been removed in  FIG. 91A , as a front-view where its entire front surface has been removed in  FIG. 92A , and as an end-view in  FIG. 91B  and  FIG. 91B . In  FIGS. 91A and 91B , the pin belt torque transmitting member  590  and pin belt non-torque transmitting member  690  are positioned near the smaller end of the cone, and in  FIGS. 92A and 92B  they are positioned near the larger end of the cone. In addition, partial sectional-views referenced in  FIG. 91A  are shown in  FIGS. 93 and 94 , which only show the cut sections. Front front pin belt cone assembly  520 A, which uses a pin belt cone  540  shown in  FIGS. 91A ,  91 B,  92 A, and  92 B, is almost identical to the tooth carriage cone assembly described previously. However, here in order to balance the centrifugal forces better, two pin belt longitudinal slides  580 , which are identical and attached in the same manner as longitudinal slide  480 , are used. One pin belt longitudinal slide  580  will be used to mount a torque transmitting member carriage  550 A, and the other pin belt longitudinal slide  580  will be used to mount a non-torque transmitting member carriage  550 B, see  FIGS. 92A and 93 . The torque transmitting member carriage  550 A like the tooth carriage  450 , have a longitudinal slide hole and two radial slide holes, into which torque transmitting member slides  560 -S 2  of a torque transmitting member radial slider sleeve  560  are inserted. The sleeve of torque transmitting member radial slider sleeve  560  is shaped like the radial slides sleeve  461 . The torque transmitting member radial slider sleeve  560  has two sets of oppositely positioned radial torque transmitting member slides  560 -S 2 , one set will be used to maintain the axial position of the torque transmitting member carriage  550 A relative to torque transmitting member radial slider sleeve  560 , and the other set will be used to maintain the axial position of the non-torque transmitting member carriage  550 B relative to torque transmitting member radial slider sleeve  560 . The only difference between the tooth carriage  450  and torque transmitting member carriage  550 A is that torque transmitting member carriage  550 A does not have a tooth and that while for tooth carriage  450 , its radial slides are positioned inside its radial slider holes, for torque transmitting member carriage  550 A, the lower portions of a torque leading plate left sleeve  592 -S 1  and a torque leading plate right sleeve  592 -S 2  of a pin belt torque transmitting member  590 , see  FIGS. 97 and 92A , are positioned inside its radial slider holes and secured using torque leading plate locking rings  600 ; while the radial slides are positioned inside the torque leading plate left sleeve  592 -S 1  and the torque leading plate right sleeve  592 -S 2 . The non-torque transmitting member carriage  550 B which is identical to the torque transmitting member carriage  550 A, except that here the lower portions of a non-torque leading plate left sleeve  692 -S 1  and a non-torque leading plate right sleeve  692 -S 2  of a pin belt non-torque transmitting member  690 , see  FIG. 106 , are positioned inside the radial slider holes and secured using torque leading plate locking rings  600 , while the radial slides are positioned inside the non-torque leading plate left sleeve  692 -S 1  and the non-torque leading plate right sleeve  692 -S 2 . Also, in order to properly guide the other ends, which will be referred to as the trailing ends of pin belt torque transmitting member  590  and pin belt non-torque transmitting member  690  a trailing end slides sleeve  565  will be used. Trailing end slides sleeve  565  consist of sleeve, which can freely rotate relative to pin belt cone assembly spline  530 , and two oppositely positioned trailing end slides  565 -S 1 , see  FIG. 94 . The trailing end slides  565 -S 1  will be inserted into trailing end cuts  540 -S 6 , see  FIG. 112A , and will be used to secure the trailing plate  593  of pin belt torque transmitting member  590  and non-torque trailing plate  693  of pin belt non-torque transmitting member  690 . 
   The pin belt torque transmitting member  590  and its parts are shown as a top-view in  FIG. 95 , and as sectional-views in  FIGS. 96-98 , it is channel shaped with two sides and a base and consist of a rubber segment that is reinforced with reinforcement plates and reinforcement wires. It consists of reinforcement plates  591  that are placed at regular intervals along the length of a pin belt torque transmitting member  590 . The surface of the reinforcement plates should be selected or coated so that they can properly bond with the rubber of the torque transmitting member. Here epoxy might be used. Pin belt torque transmitting member  590  should have sufficient compressive and lateral stiffness so that pin belt torque transmitting member  590  can maintain its proper shape as required for smooth operation in instances when a load in the direction from trailing plate  593  to leading plate  592  is applied to pin belt torque transmitting member  590 . The load in this direction should be carried by pin belt torque transmitting member  590  when the output shaft of the CVT where its cone assembly is used is pulling the input shaft of that CVT. 
   The reinforcement plates are flat channel shaped plates that have a round flange  591 -S 1  on which a pin belt tooth  591 -S 2 , is shaped on both its inner facing surfaces. A pin belt tooth  591 -S 2  is shaped from a tubular section for which a radial section is removed. It consists of a tubular section, which starts at the center height of a round flange  591 -S 1  and ends near the bottom of round flange  591 -S 1 , but extends slightly beyond the bottom of round flange  591 -S 1 , see  FIGS. 98 and 92B . The extension beyond the bottom of round flange  591 -S 1  of each pin belt tooth  591 -S 2  should be short enough so that the torque transmitting member can smoothly engage with its transmission belt. The exact dimension for the extension can easily be obtained experimentally or by using a CAD program. Also if required for smooth operation, the tooth shape does not have to start at the center height of the tooth, if required it can start slightly below that. The pin belt teeth  591 -S 2  are used for torque transmission. During operation the pin belt teeth  591 -S 2  engage with the transmission belt pins  630 -M 1  of a pin transmission belt  630 , shown as a side-view in  FIG. 102A  and as an end-view in  FIG. 102B . For pin transmission belt  630 , the neutral-axis is located at the center-axis of the transmission belt pins  630 -M 1 . 
   In addition, for reinforcement plate  591 , near each round flange, a hole for a reinforcement wire  594  exist. For increased strength, once mounted on the reinforcement wires, before being coated with rubber, the reinforcement plates can be bonded to the reinforcement wires using epoxy. For smooth engagement and optimal performance, the neutral-axis of pin belt torque transmitting member  590  is positioned so that the centers of the round flanges  591 -S 1  are located on the neutral-axis, and the reinforcement wires  594  should also be located on the neutral-axis. And the area of the left channel side is identical to the area of the right channel side, although this might be ignored if this increases the cost of pin belt torque transmitting member  590  significantly. Also since the rubber surfaces of torque transmitting member are not used for torque transmission, in order minimize friction loses and wear, they have a low friction surface. 
   Furthermore, in order secure pin belt torque transmitting member  590  to front pin belt cone assembly  520 A, the leading end of pin belt torque transmitting member  590 , has a leading plate  592  molded in it. Leading plate  592 , see  FIG. 97 , is identical to a reinforcement plate  591 , except that to its left and right outer sides sleeves, labeled as torque leading plate left sleeve  592 -S 1  and torque leading plate right sleeve  592 -S 2 , are shaped. As discussed earlier the lower portions of torque leading plate sleeves, which are not covered by rubber, are inserted into torque transmitting member carriage  550 A. And in order to secure leading plate  592  and hence the leading end of pin belt torque transmitting member  590  to torque transmitting member carriage  550 A, each torque leading plate right sleeve  592 -S 2  has two leading plate locking ring grooves  592 -S 3 . 
   In addition, in order to secure the trailing end, of pin belt torque transmitting member  590  to front pin belt cone assembly  520 A, at the trailing end, a trailing plate  593  is molded into pin belt torque transmitting member  590 . Trailing plate  593 , shown in  FIG. 99 , is identical to a reinforcement plate  591 , except that to its right outer side a sleeve, labeled as trailing plate sleeve  593 -S 1  is shaped. In order to secure the trailing end of pin belt torque transmitting member  590  to pin belt cone  540 , the lower portions of trailing plate sleeve  593 -S 1 , which is not covered by rubber, is inserted into a trailing end cut  540 -S 6  of pin belt cone  540  and slid into trailing end slide  565 -S 1 . Then a ball clamp  620  is slid onto trailing plate sleeve  593 -S 1  so that the surface of pin belt cone  540  is clamped by the bottom surface of the trailing end of pin belt torque transmitting member  590  and the balls  620 -M 1  of ball clamp  620 , see  FIG. 100 . Ball clamp  620  consist of a ball plate  620 -S 1 , which is a plate on which has two cavities into which two balls are pressed in exist. The balls  620 -M 1  can rotate without much friction relative to ball plate  620 -S 1 . Below ball plate  620 -S 1 , a ball clamp sleeve  620 -S 2 , which is slid on trailing plate sleeve  593 -S 1 , is shaped. The inner surface of ball clamp sleeve  620 -S 2  has a low friction coating so that ball clamp  620  can freely rotate relative to trailing plate sleeve  593 -S 1 . Ball plate  620 -S 1  is shaped at an angle relative to ball clamp sleeve  620 -S 2  so that in its assembled state, ball plate  620 -S 1  can be oriented so that it is parallel relative to the surface of its pin belt cone  540 . During assembly, ball plate  620 -S 1  should be oriented so that it is parallel relative to the surface of its pin belt cone  540 . Since ball clamp  620  is free to rotate on trailing plate sleeve  593 -S 1 , ball plate  620 -S 1  can reoriented itself so that it is always parallel to the surface of its pin belt cone  540  when its slide to a different position. During normal operation ball plate  620 -S 1  should be parallel to the surface of pin belt cone  540 , since the surface of pin belt cone  540  will force it in that orientation. In order to secure ball clamp  620  to trailing plate sleeve  593 -S 1 , a ball clamp locking ring  601 , which is inserted into trailing plate locking ring grooves  593 -S 2 , is used. If a simpler method is desired, ball clamp  620  can be replaced with a dome shaped nut  621 , see  FIG. 101 . In order to allow some slight play between dome shaped nut  621  and the surface of the cone on which it is attached, it is recommended that dome shaped nut  621  is allowed to slightly slide axially relative to trailing end slides  565 -S 1  when it is secured to trailing plate sleeve  593 -S 1 . 
   Also the pin belt torque transmitting member  590 , has an extension  595 , see  FIG. 95 , which is not used for torque transmission but is used to provide a resting surface for pin belt torque transmitting member  590 , so as to minimize the uncovered surface of pin belt cone  540 . Ideally, extension  595  is shaped so that it provides maximum coverage on the surface of pin belt cone  540  without ever overlapping the leveling surfaces  540 -S 7  of pin belt cone  540 . The neutral-axis for extension  595 , which is shown as an end-view in  FIG. 101 , should coincide with the neutral-axis of pin transmission belt  630 . The tapered cut for extension  595  can be selected arbitrarily as long as it never overlaps leveling surfaces  540 -S 7  as pin belt torque transmitting member  590  is slid from its position for its largest pitch diameter to its position for its smallest pitch diameter. 
   Also, the arc length of a pin belt torque transmitting member  590  should be short enough so that for the CVT where it is used, its transmission belt will never cover the entire non-torque transmitting arc of its cone. However, the arc length of pin belt torque transmitting member  590  should be long enough so that for the CVT where it is used, at least a torque transmitting surface of at least one pin belt torque transmitting member  590  is always engaged with its transmission belt. 
   Furthermore, an increase in lateral stiffness of pin belt torque transmitting member  590  allows more torque to be transmitted when a load in the direction from trailing plate  593  to leading plate  592  is applied to pin belt torque transmitting member  590 . Since this allows more load to be carried through the engagement of the lower portion of trailing plate sleeve  593 -S 1  with trailing end cuts  540 -S 6 . Without sufficient lateral stiffness of pin belt torque transmitting member  590 , a too big of a load carried through the engagement of trailing plate sleeve  593 -S 1  with trailing end cuts  540 -S 6  would cause too much lateral bending of pin belt torque transmitting member  590 . 
   The lateral stiffness of pin belt torque transmitting member  590  can be increased by the following or combination of the following, by increasing the width of pin belt torque transmitting member  590 ; by increasing the stiffness of the rubber of pin belt torque transmitting member  590 ; by increasing the size of the reinforcements of pin belt torque transmitting member  590 , by increasing the lateral distance between the reinforcements of pin belt torque transmitting member  590 ; by adding additional reinforcements, which like the reinforcements of pin belt torque transmitting member  590  should also be located at the neutral-axis of pin belt torque transmitting member  590 , to pin belt torque transmitting member  590 ; and/or by having reinforcement shapes shaped on the outside side surfaces of pin belt torque transmitting member  590 , similar to the lateral bending reinforcement  280 -S 2  of the torque transmitting side member  280  described in the Torque Transmitting Side Members section of this application and shown in  FIGS. 69 ,  70 A,  70 B, and  70 C. 
   Front pin belt cone assembly  520 A and back pin belt cone assembly  520 B, described later, are primarily designed to carry a large amount of load in the direction from leading plate  592  to trailing plate  593 . The load in this direction should be carried when the input shaft of the CVT where the cone assemblies are used is pulling the output shaft of that CVT. Front pin belt cone assembly  520 A and back pin belt cone assembly  520 B are not designed to carry a large amount of load in the direction from trailing plate  593  to leading plate  592 , which should be carried when the output shaft of the CVT where the cone assemblies are used is pulling the input shaft of that CVT. The load in the direction from trailing plate  593  to leading plate  592  can be limited by using friction clutches, or even eliminated by using one-way clutches. 
   The pin belt non-torque transmitting member  690  and its parts are shown in  FIGS. 103-106 . It is identical to pin belt torque transmitting member  590  except that its non-torque reinforcement plates  691 , shown in  FIG. 104 , its non-torque leading plate  692 , shown in  FIG. 105 , and its non-torque trailing plate  693 , shown in  FIG. 106 , do not have any teeth, which for the plates of pin belt torque transmitting member  590  are formed by the round flanges and the partial circular surfaces. Hence pin belt non-torque transmitting member  690  will be slightly lighter than pin belt torque transmitting member  590 . If this significantly affects the balance of the cone assembly, the plates for pin belt non-torque transmitting member  690  can be made slightly thicker so that they weight about the same as the plates of the pin belt torque transmitting member  590 . Pin belt non-torque transmitting member  690  will not be used for torque transmission, its primary function is to maintain the axial alignment of a rotational energy conveying device, such as a transmission belt, when it is not in contact with a pin belt torque transmitting member  590 . Hence for increased performance, it is recommended that the inner side surfaces of pin belt non-torque transmitting member  690  are coated with a low friction material. 
   Furthermore, if its desirable to use friction to transmit torque than a torque transmitting member similar to pin belt torque transmitting member  590 , labeled as alternate friction torque transmitting member  1590 , shown as a top-view in  FIG. 107  can be used instead of pin belt torque transmitting member  590 . Alternate friction torque transmitting member  1590  also has channel shaped cross-section, however since alternate friction torque transmitting member  1590  will be used with a tapered base V-belt, its cut-out portion has the shape of a tapered base V-belt. A tapered base V-belt is similar to regular V-belt except that it is base is tapered. Since the base of a tapered base V-belt rests on the outer surface of a cone assembly, the taper of the base of tapered base V-belt should match the taper of the outer surface of its cone assembly. Alternate friction torque transmitting member  1590  is identical to pin belt torque transmitting member  590 , except that it&#39;s a rubber segment is not reinforced with reinforcement plates. However, it&#39;s a rubber segment is reinforced with reinforcement wires, which here are labeled as friction member reinforcement wires  1594 , in the same manner pin belt torque transmitting member  590  is reinforced with reinforcement wires. Also, like pin belt torque transmitting member  590 , alternate friction torque transmitting member  1590  has a leading plate, which is labeled as friction leading plate  1592 , that is identical to leading plate  592  except that it does not have round flanges and pin belt teeth, and has a cut-out that has the shape of a tapered base V-belt. The friction leading plate  1592  can also be seen in  FIG. 108 , which shows a sectional-view of alternate friction torque transmitting member  1590 . Alternate friction torque transmitting member  1590  also has a trailing plate, which is labeled as friction trailing plate  1593 , that is identical to trailing plate  593  except that it does not have round flanges and pin belt teeth, and has a cut-out that has the shape of a tapered base V-belt. Friction trailing plate  1593  is also shown as a front-view in  FIG. 109 . 
   As described earlier, alternate friction torque transmitting member  1590  should have a cross-section that has a cut-out portion that has the shape of a tapered base V-belt. For smooth engagement and optimal performance, the neutral-axis of alternate friction torque transmitting member  1590  is positioned so that when it is engaged with its tapered base V-belt, the neutral-axis of the tapered base V-belt used with alternate friction torque transmitting member  1590  is located on the neutral-axis of alternate friction torque transmitting member  1590 . Also, the reinforcement wires of alternate friction torque transmitting member  1590  should be located on the neutral-axis of alternate friction torque transmitting member  1590 ; and the reinforcement wires of its tapered base V-belt should also be located on the neutral-axis of that tapered base V-belt. A drawing that shows a cross-sectional-view of alternate friction torque transmitting member  1590  that is engaged with its V-belt, which is labeled as V-belt  1600 , is shown in  FIG. 110 . 
   In order to have a wedging action between alternate friction torque transmitting member  1590  and its tapered base V-belt so as obtain proper frictional engagement, the width of the base of the cut-out portion of alternate friction torque transmitting member  1590  is slightly less than the width of the base of its tapered base V-belt. For optimal torque transmission, the surface finish or surface coating of alternate friction torque transmitting member  1590  should be selected such that a large coefficient of friction between alternate friction torque transmitting member  1590  and its tapered base V-belt can be obtained. Also if alternate friction torque transmitting member  1590  is used instead of pin belt torque transmitting member  590 , than for its non-torque transmitting member instead of pin belt non-torque transmitting member  690 , an alternate friction non-torque transmitting member  1690  is used. Alternate friction non-torque transmitting member  1690  is identical to alternate friction torque transmitting member  1590 , except that instead of having a cut-out portion that has a base with a width that is slightly less than the width of the base of its tapered base V-belt, it has a cut-out portion that has a base with a width that is slightly more than the width of the base its tapered base V-belt so as to eliminate the wedging action. In order to maintain the radial position of the tapered base V-belt when it is engaged with alternate friction non-torque transmitting member  1690 , the increase in the width of the base of the cut-out portion of alternate friction non-torque transmitting member  1690  has to accompanied by a corresponding increase in height of the base of the cut-out portion of alternate friction non-torque transmitting member  1690 . Also the surfaces of alternate friction non-torque transmitting member  1690  that engage with its tapered base V-belt should have a low-friction surface finish. If a leveling loop, which was described earlier, is used, alternate friction torque transmitting member  1590  and alternate friction non-torque transmitting member  1690  can be used with a regular V-belt. A drawing that shows a cross-sectional-view of alternate friction non-torque transmitting member  1690  that is engaged with its tapered base V-belt, which is labeled as tapered base V-belt  1600 , is shown in  FIG. 111 . The control method during transmission ratio change for a CVT that uses a cone assembly or cone assemblies that use alternate friction torque transmitting members  1590  and alternate friction non-torque transmitting members  1690 , should be identical to the control method used in a CVT that uses cone assemblies with toothed torque transmitting members as described previously. However, here if desired, a control method were sliding between the torque transmitting surfaces occur, as is the case in most conventional CVT&#39;s, can also be used. 
   The pin belt cone  540  used for front pin belt cone assembly  520 A is shown as a front-view in  FIG. 112A  and as an end-view in  FIG. 112B . Except for the features described in the following paragraphs, this cone is identical to cone  440  described previously. While cone  440  has one longitudinal cut  440 -S 1 , pin belt cone  540  has two oppositely positioned leading end cuts  540 -S 1 . The leading end cuts  540 -S 1  and the pin belt cone assembly spline  530  are located on one radial plane, and the pin belt longitudinal slides  580  are aligned parallel to the width centerline of the leading end cuts  540 -S 1 . In the cone&#39;s assembled state, the radial torque transmitting member slides  560 -S 2  will be placed in the leading end cuts  540 -S 1 . Also since front pin belt cone assembly  520 A has two pin belt longitudinal slides  580  and no counter-balance longitudinal slide, cone  540  has two pin belt cone slide mounting holes  540 -S 3 , instead of one cone slide mounting hole  440 -S 3  and one counter-balance longitudinal slide hole  440 -S 5  that cone  440  has. The pin belt cone slide mounting holes  540 -S 3  should be aligned and positioned such that in the cone&#39;s assembled state, the pin belt longitudinal slides  580  are aligned parallel to the width centerline of the leading end cuts  540 -S 1 . 
   In addition, pin belt cone  540  also has two oppositely positioned trailing end cuts  540 -S 6 . In the cone&#39;s assembled state, into the trailing end cuts  540 -S 6 , the lower portions of the sleeves of trailing plate  593  and non-torque trailing plate  693  into which the trailing end slides  565 -S 1  of the trailing end slides sleeve  565  are inserted, are inserted. The trailing end cuts  540 -S 6  are shaped so that for a pin belt torque transmitting member  590  attached between a leading end cut  540 -S 1  and a trailing end cut  540 -S 6 , the neutral-axis arc length of that pin belt torque transmitting member  590  remains constant as that pin belt torque transmitting member  590  is moved to different axial locations on the surface of its cone; in addition, that pin belt torque transmitting member  590  should also wrap tightly around the surface of its cone without lifting. The exact shape of the trailing end cuts  540 -S 6  can be easily obtained experimentally by attaching the leading end of pin belt torque transmitting member  590  to the assembled cone and tracing the movement of the trailing plate sleeve  593 -S 1 . For experimental purposes, a specialized pin belt torque transmitting member  590 , for which the trailing plate sleeve  593 -S 1  does not extend beyond the bottom surface of pin belt torque transmitting member  590 , can be used. Somebody skilled in the art should also be able to determine the shape of the trailing end cuts  540 -S 6  mathematically. 
   Also the percentage of circumferential surface of the axial section of pin belt cone  540  covered by its pin belt torque transmitting member  590  and its pin belt non-torque transmitting member  690  decreases as the pitch diameter is increased. In order to provide a level resting surface for the transmission belt at the surface of pin belt cone  540  that will not be covered by pin belt torque transmitting member  590  and pin belt non-torque transmitting member  690 , leveling surfaces  540 -S 7  are glued on to the surface of pin belt cone  540 . The leveling surfaces  540 -S 7  are rubber sheets that have the same thickness as the thickness of the base of pin belt torque transmitting member  590  and pin belt non-torque transmitting member  690 , and are shaped as to cover as much surface of pin belt cone  540  without interfering with the operation of pin belt torque transmitting member  590  and pin belt non-torque transmitting member  690 . Two identical leveling surfaces  540 -S 7  are glued on the surface of pin belt cone  540  opposite from each other. 
   As in the configuration for a CVT  2  input/output shaft utilizing a front sliding tooth cone assembly  420 A and a back sliding tooth cone assembly  420 B, in addition to a pin belt cone  540 , a back pin belt cone  540 B is also needed. Except the front shaft and shoulder portions of back pin belt cone  540 B, which are identical to back cone  440 B, back pin belt cone  540 B is identical to pin belt cone  540 , see  FIG. 113 . 
   The pin belt cone larger end cover  545  for pin belt cone  540 , which can be seen in  FIGS. 91A , is identical to larger end cover  445  except that it has two pin belt cone end cover longitudinal slide holes  545 -S 1 , instead of one end cover longitudinal slide hole  445 -S 1  and one end cover counter-balance longitudinal slide hole  445 -S 2  that larger end cover  445  has. The pin belt cone end cover longitudinal slide holes  545 -S 1  should be aligned and positioned such that in the cone&#39;s assembled state, the pin belt longitudinal slides  580  are aligned parallel to the width centerline of the leading end cuts  540 -S 1 . And the back pin belt cone larger end cover  545 B, shown in  FIG. 114 , for back pin belt cone  540 B is identical to back cone larger end cover  445 B except that it has two holes for mounting pin belt longitudinal slides  580 , instead of one hole for mounting the longitudinal slide and one hole for mounting the counter-balance longitudinal slide that back cone larger end cover  445 B has. The holes for mounting pin belt longitudinal slides  580  are identical to the pin belt cone end cover longitudinal slide holes  545 -S 1 . They are aligned and positioned such that in the cone&#39;s assembled state, the pin belt longitudinal slides  580  are aligned parallel to the width centerline of the leading end cuts  540 -S 1 . 
   Back pin belt cone  540 B and back pin belt cone larger end cover  545 B are used for a back pin belt cone assembly  520 B. The only difference between back pin belt cone assembly  520 B and front pin belt cone assembly  520 A is the front end portions of their cones used for mounting purposes, and the back end portions of their larger end covers used for mounting purposes. 
   CVT  2  input/output shaft utilizing a front pin belt cone assembly  520 A and a back pin belt cone assembly  520 B is identical to CVT  2  input/output shaft utilizing a front sliding tooth cone assembly  420 A and a back sliding tooth cone assembly  420 B, except that here instead of front sliding tooth cone assembly  420 A, a back sliding tooth cone assembly  420 B, and a spline  430 , here a front pin belt cone assembly  520 A, a back pin belt cone assembly  520 B, and a pin belt cone assembly spline  530  are used. Since the teeth of front sliding tooth cone assembly  420 A and a back sliding tooth cone assembly  420 B are positioned opposite of each other on their CVT  2  input/output shaft, the torque transmitting members of front pin belt cone assembly  520 A and a back pin belt cone assembly  520 B are also positioned opposite of each other on their CVT  2  input/output shaft. Also if a pin belt cone assembly with two oppositely positioned torque transmitting members, toothed or friction dependent, or a sliding tooth cone assembly with two oppositely positioned sliding teeth is used, than the mounting of a single cone assembly on a shaft/spline as shown as a top-view in  FIG. 115  can be used. Here the single mounted cone assembly can be coupled to a pulley or a sprocket; or to another single mounted cone assembly in the configuration of a CVT  1 . 
   In order to assemble pin belt cone assembly  520 A or back pin belt cone assembly  520 B, first the trailing end slides  565 -S 1  of trailing end slides sleeve  565  are inserted into the trailing end cuts  540 -S 6  of a pin belt cone  540 , then a radial slides sleeve axial bearing  472  is placed in front of trailing end slides sleeve  565 . Next pin belt cone  540 , radial slides sleeve axial bearing  472 , and trailing end slides sleeve  565  are aligned with pin belt cone assembly spline  530  and slid onto with pin belt cone assembly spline  530 . Then spline collar  470  is mounted on the designated cut on pin belt cone assembly spline  530  that is positioned near the smaller end of the pin belt cone  540 . 
   The other parts, except the pin belt torque transmitting member  590  and the pin belt non-torque transmitting member  690 , are then assembled in a similar manner as the parts for front sliding tooth cone assembly  420 A are assembled. For example, in order to mount torque transmitting member carriage  550 A and non-torque transmitting member carriage  550 B, first the torque transmitting member slides  560 -S 2  of torque transmitting member radial slider sleeve  560  are inserted into the radial slider holes of torque transmitting member carriage  550 A and non-torque transmitting member carriage  550 B. Next, the torque transmitting member carriage  550 A and non-torque transmitting member carriage  550 B are aligned with their pin belt longitudinal slide  580  and the torque transmitting member radial slider sleeve  560  is aligned with pin belt cone assembly spline  530 . Then torque transmitting member carriage  550 A and non-torque transmitting member carriage  550 B are slid onto their pin belt longitudinal slide  580  and torque transmitting member radial slider sleeve  560  is slid onto pin belt cone assembly spline  530 . Once the torque transmitting member carriage  550 A, non-torque transmitting member carriage  550 B, and trailing end slides sleeve  565  are in position, pin belt torque transmitting member  590  and the pin belt non-torque transmitting member  690  can be mounted by sliding the leading plate sleeves onto the radial sliders and into the radial slider holes of their carriages and securing them using torque leading plate locking rings  600 , and by sliding the trailing plate sleeves into the trailing end slides and into the trailing end cuts and securing them using a ball clamp  620  or dome shaped nut  621 . 
   Pin transmission belt  630 , see  FIGS. 120A and 120B , consists of a rubber belt on which transmission belt pins  630 -M 1 , which extend to the left and to the right of the rubber belt are inserted. The dimensions of the pins are such that they can properly engage with the pin belt teeth  591 -S 2  of pin belt torque transmitting member  590 , and the distance/pitch between the transmission belt pins  630 -M 1  should match the distance/pitch between the pin belt teeth  591 -S 2  of pin belt torque transmitting member  590 . And when pin transmission belt  630  is engaged with its pin belt torque transmitting member  590 , the neutral-axis of bending of pin transmission belt  630  should coincide with the neutral-axis of bending of its pin belt torque transmitting member  590 . For smooth operation and optimal performance the center of the transmission belt pins  630 -M 1  should be located at the neutral-axis of pin transmission belt  630 . For increased strength, holes for reinforcements, labeled as pin reinforcement holes  630 -M 1 -S 1 , are drilled into the transmission belt pins  630 -M 1 . Like for the reinforcement plates, for increased strength, the pins should be bonded to their reinforcements, which here are labeled as pin belt reinforcements  630 -M 2 . The base of pin transmission belt  630  rests on the outer surface of a cone assembly, hence the taper of the base of pin transmission belt  630  should match the taper of the outer surface of its cone assembly. The width of pin transmission belt  630  is slightly narrower than the bottom inner side surfaces of pin belt torque transmitting member  590  and pin belt non-torque transmitting member  690  so that pin transmission belt  630  can engage with the bottom inner side surfaces of pin belt torque transmitting member  590  and pin belt non-torque transmitting member  690  for alignment purposes. Also since the rubber surfaces of the transmission belt are not used for torque transmission, in order minimize friction loses and wear, they should have low friction surfaces. In case no adjuster or adjustment device is used, pin transmission belt  630  should be flexible enough so that it can stretch without failure to account for instances were the arc length(s) of the non-torque transmitting arc(s) of the cone(s) with which is used, do not correspond to a multiple of the width of the teeth or tooth of the cone assembly or cone assemblies with which is used. If necessary the pin belt reinforcements  630 -M 2  can be omitted to ensure this or the transmission ratios where transition flexing occurs can be skipped. 
   CVT  2  input/output shaft utilizing a front pin belt cone assembly  520 A and a back pin belt cone assembly  520 B and the CVT  2  input/output shaft utilizing a front sliding tooth cone assembly  420 A and a back sliding tooth cone assembly  420 B, can than be used to construct a CVT  2  by coupling each cone assembly to a matching transmission pulley or sprocket. 
   If front sliding tooth cone assembly  420 A and a back sliding tooth cone assembly  420 B are used, then each cone assembly can be coupled to a sprocket that can properly engage with the transmission belts used front sliding tooth cone assembly  420 A and a back sliding tooth cone assembly  420 B. Here the pitch of the teeth of the sprocket should match the pitch of its transmission belts. And the width of the teeth of the sprocket should match the width of the tooth of tooth carriage  450 , which should be slightly less than the distance between the inner surfaces of belt member  1   411  and belt member  2   412  of its transmission belts. 
   If front pin belt cone assembly  520 A and a back pin belt cone assembly  520 B are used, then for each transmission pulley of a cone assembly, a twin sprocket pulley  700 , shown as a front-view in  FIG. 116A  and as a sectional-view in  FIG. 116B  can be used. The twin sprocket pulley  700  consist of two pulley sprockets  700 -S 1  that sandwich a pulley conical surface  700 -S 2 , which taper matches the taper of its cone assembly and the bottom surfaces of its transmission belts. The distance between the pulley sprockets  700 -S 1  should be selected such that distance between the inner surfaces of the pulley sprockets  700 -S 1  is slightly wider than the width of its transmission belt or chain. Also in order to mount twin sprocket pulley  700  to its shaft, it has a pulley mounting sleeve  700 -S 3 , which has a threaded hole for keying twin sprocket pulley  700  to its shaft. The twin sprocket pulley  700  can also be replaced by two sprockets  702  mounted parallel to each other on a shaft as shown as a front-view in  FIG. 117A  and as a sectional-view in  FIG. 117B . Each sprocket  702  has a sprocket mounting sleeve  702 -S 1 , which has a threaded hole for keying that sprocket  702  to its shaft. The distance between the sprockets  702  should be selected such that distance between the inner surfaces of the sprockets  702  is slightly wider than the width of its transmission belt or chain. For both, the twin sprocket pulley  700  and the sprockets  702  mounted in parallel, the pitch of the teeth of the sprockets should match the pitch of their transmission belts. If the distance between the teeth of the transmission belt is larger than that of a regular sprocket chain, then the distance between the of the teeth of the sprockets can be increased while the pitch diameter of the teeth are maintained at the same diameter as a regular sprocket of the same tooth size. A transmission pulley for front pin belt cone assembly  520 A and a back pin belt cone assembly  520 B can also be formed by gluing the mid-portion of a pin belt torque transmitting member  590 , such that only reinforcement plates  591  are used, on a matching conical surface in a manner such that the mid-portion of pin belt torque transmitting member  590  provides sufficient coverage for continuous torque transmission. 
   A CVT constructed from a front sliding tooth cone assembly  420 A and a back sliding tooth cone assembly  420 B is shown as a partial top-view in  FIG. 90 , and as partial back-views in  FIGS. 89 and 118 , because of time constraints, some parts such as front transmission sprocket  705 A, are only symbolically drawn. In  FIG. 89 , the tooth carriages  450  are positioned near the largest end of their cone; and in  FIG. 118 , the tooth carriages  450  are positioned near the smallest end of their cone. Here front sliding tooth cone assembly  420 A is coupled by a front transmission belt  704 A to a front transmission sprocket  705 A, and back sliding tooth cone assembly  420 B is coupled by a back transmission belt  704 B to a back transmission sprocket  705 B. Furthermore, front transmission sprocket  705 A is mounted to sliding tooth cone shaft  707  via a sliding tooth cone adjuster  706 , so that the rotational position of front transmission sprocket  705 A relative to the rotational position of sliding tooth cone shaft  707  can be adjusted by sliding tooth cone adjuster  706 . Sliding tooth cone adjuster  706 , is a stepper motor that has an sliding tooth cone adjuster body  706 -M 1  and an sliding tooth cone adjuster output shaft  706 -M 2 , which rotational position can be adjusted relative to sliding tooth cone adjuster body  706 -M 1 . Sliding tooth cone adjuster  706  has an axial hole so that it can be slid into sliding tooth cone shaft  707 . In order to mount sliding tooth cone adjuster body  706 -M 1  on sliding tooth cone shaft  707  a set-screw is used. And in order to mount pulley  310  to sliding tooth cone adjuster output shaft  706 -M 2 , front transmission sprocket  705 A has a pulley sleeve  310 -M 1 , which has two oppositely positioned set-screws, which partially screw into sliding tooth cone adjuster output shaft  706 -M 2 , but do not penetrate into sliding tooth cone shaft  707 . And back transmission sprocket  705 B is also mounted to sliding tooth cone shaft  707  via another sliding tooth cone adjuster  706  in the same manner as front transmission sprocket  705 A is mounted. In order to control the adjusters, the ring and brush method described earlier can be used. Here either spline  430  or sliding tooth cone shaft  707  can be the input shaft/spline. However the portions of the transmission belts under tension, should be the upper portions of the transmission belts. Therefore, if spline  430  is the input spline, then spline  430  should be rotating counter-clockwise; and if sliding tooth cone shaft  707  is the input shaft, then sliding tooth cone shaft  707  should be rotating clockwise. Also sliding tooth cone shaft  707  is supported by sliding tooth cone shaft bearings  708  and a sliding tooth cone shaft end bearing  710 . In order to maintain the axial position of the shaft, the upper end of the shaft has a machined down portion that has threaded end portion for a sliding tooth cone nut  709 . Here the engagement between the shoulder created by the machined down portion of the shaft with sliding tooth cone shaft end bearing  710 , and the engagement of sliding tooth cone nut  709  with sliding tooth cone shaft end bearing  710  will be used to maintain the axial position of sliding tooth cone shaft  707 . 
   Also in order for the CVT to operate properly, it needs to be ensured that at any instance during the operation of the CVT, at least one tooth of a tooth carriage  450  is engaged with its transmission belt. In order to ensure this and in order to maintain the axial alignment of the transmission belts, spring-loaded slider pulley assemblies  720  are used. A spring-loaded slider pulley assembly  720 , shown in  FIGS. 119A and 119B , consist of a spring-loaded slider housing  720 -M 1 ; a spring-loaded slider  720 -M 2 , which lateral and rotational positions are constrained relative to spring-loaded slider housing  720 -M 1  and which is pushed out of spring-loaded slider housing  720 -M 1  by a spring; a spring-loaded slider pulley clevis  720 -M 3 ; a spring-loaded slider pulley  720 -M 4 , which has a bearing; a slider pulley spring-loaded slider shaft  720 -M 5 , which is inserted through designates holes in the spring-loaded slider pulley clevis  720 -M 3  and the bearing of spring-loaded slider pulley  720 -M 4 ; and two spring-loaded slider shaft locking pins  720 -M 6 , which are inserted through designated holes in the spring-loaded slider pulley clevis  720 -M 3  and the slider pulley spring-loaded slider shaft  720 -M 5 . In order to lock the spring-loaded slider shaft locking pins  720 -M 6  into place, they have locking caps that are not wider than then the width of the parallel clevis plates of spring-loaded slider pulley clevis  720 -M 3 . It needs to be ensured that the spring-loaded slider pulley assemblies  720  do not interfere with the operation of the cone assemblies, hence the width of the portions of the spring-loaded slider pulleys  330  that are positioned between the radial slides  460  are less than the distance between their radial slides  460 , see  FIG. 119B . 
   In  FIGS. 89 and 118 , it can be seen that three spring-loaded slider pulley assemblies  720  are used for front sliding tooth cone assembly  420 A, which are spring-loaded slider pulley assembly A  720 A, spring-loaded slider pulley assembly B  720 B, and spring-loaded slider pulley assembly C  720 C. Here spring-loaded slider pulley assembly C  720 C is used to ensure sufficient engagement coverage for the tooth of tooth carriage  450  of front sliding tooth cone assembly  420 A, and spring-loaded slider pulley assembly A  720 A and spring-loaded slider pulley assembly B  720 B are used to maintain the axial alignment of transmission belt  400 A. Depending on the lateral stiffness of the transmission belts and the taper of the cones more or less spring-loaded slider pulley assemblies  720  can be used. Sufficient amount of spring-loaded slider pulley assemblies  720  should be used to prevent bowing of the transmission belts that significantly affects the performance of the CVT. In order to prevent excessive bowing of the transmission belts, it is highly recommended that the taper of the cones, based on a horizontal reference, are less than 45 degrees. In case excessive bowing occurs, bowing of the transmission belts can be reduced by reducing the taper of the cones and by increasing the lateral stiffness and the width of the transmission belts. The same configuration of spring-loaded slider pulley assemblies used for front sliding tooth cone assembly  420 A should also used for back sliding tooth cone assembly  420 B. 
   Also in order to maintain the tension in the transmission belts, each transmission belt has a tensioner pulley assembly  740 . A tensioner pulley assembly  740  is identical to a spring-loaded slider pulley assembly  720 , except that it has a pulling spring and/or a pulling weight instead of a pushing spring. In addition, the sliding range of a tensioner pulley assembly  740  might also be different than the sliding range of a spring-loaded slider pulley assembly  720 . Here the pulling spring and/or a pulling weight of a tensioner pulley assembly  740  is used to maintain the tension in a transmission belt. The pulling force of tensioner pulley assembly  740  should be large enough so that sufficient tension in its transmission belt is maintained so that no movements in the tensioner pulley assembly  740 , hence no change in the shape of the transmission belt, occurs during normal operation and in instances where the direction of rotation is reversed such that the normally slack side of the transmission belt, where tensioner pulley assembly  740  is pulling, becomes the tense of the transmission belt, which occur in instances where the output shaft is pulling the input shaft. In other words, the pulling force of tensioner pulley assembly  740  should be larger than the force that tends to pull the slider of tensioner pulley assembly  740  out due to the tension in the transmission belt. However, the pushing force of spring-loaded slider pulley assembly  720  used to provide sufficient engagement coverage, such as spring-loaded slider pulley assembly C  720 C, should be considerably larger than the pulling force of its tensioner pulley assembly  740  so that the pulling force of tensioner pulley assembly  740  will not affect the position of that spring-loaded slider pulley assembly C  720 C, see  FIG. 118 . 
   In case front pin belt cone assembly  520 A and a back pin belt cone assembly  520 B are used instead of front sliding tooth cone assembly  420 A and a back sliding tooth cone assembly  420 B, then the same CVT configuration shown in  FIGS. 89 ,  90 , and  118  can be used as long as the torque transmitting orientation of the front pin belt cone assembly  520 A and the back pin belt cone assembly  520 B as shown in  FIGS. 91A ,  91 B,  92 A, and  92 B is reversed (a mirror image is taken), see  FIG. 120 . Here in case the spline on which the cone assemblies are mounted is the input spline, it needs to rotate counter-clockwise; and in case the shaft on which its transmission pulleys are mounted is the input shaft, it needs to be rotated clockwise. Here in order to ensure smooth operation, unless the arc lengths of the tubular sections of pin belt pin belt teeth  591 -S 2  are reduced accordingly, the spline on which the cone assemblies are mounted should be the input spline. In addition since for cone assemblies with torque transmitting members, as described earlier, no instance should exist where a complete non-torque transmitting arc is covered by its transmission belt, the spring-loaded slider pulley assemblies  720  should be repositioned to ensure this. 
   In case the configuration shown in  FIGS. 91A ,  91 B,  92 A, and  92 B is used for pin belt cone assembly  520 A and a back pin belt cone assembly  520 B, then the configuration for the CVT is the mirror image of the configuration shown in  FIGS. 89 ,  90 , and  118 , see  FIGS. 121 and 122 . In  FIGS. 121 and 122 , because of time constraints, twin sprocket pulley  700  and pin transmission belt  630 , are only symbolically drawn. Here in case pin belt cone assembly spline  530  is the input spline, it needs to rotate clockwise; and in case the shaft on which the twin sprocket pulleys  700  are mounted is the input shaft, it needs to be rotated counter-clockwise. Here in order to ensure smooth operation, unless the arc lengths of the tubular sections of pin belt pin belt teeth  591 -S 2  are reduced accordingly, the spline on which the cone assemblies are mounted should be the input spline. In addition since for cone assemblies with torque transmitting members, as described earlier, no instance should exist where a complete non-torque transmitting arc is covered by its transmission belt, the spring-loaded slider pulley assemblies  720  should be repositioned to ensure this. Also in case extension  595  gets in the way, it can simply be removed. 
   The spring-loaded slider pulley assemblies  720  and tensioner pulley assembly  740  used for a CVT using a front pin belt cone assembly  520 A and a back pin belt cone assembly  520 B are identical to the spring-loaded slider pulley assemblies  720  and tensioner pulley assembly  740  used for a CVT using a front sliding tooth cone assembly  420 A and a back sliding tooth cone assembly  420 B, except that spring-loaded slider pulley  720 -M 4  is replaced with a pin belt spring-loaded slider pulley  720 -M 4 A, which is shown as a partial end-view in  FIG. 123 , and if required the dimension of the spring-loaded slider pulley assemblies  720  and tensioner pulley assembly  740  can be adjusted accordingly. It needs to be ensured that the spring-loaded slider pulley assemblies  720  using pin belt spring-loaded slider pulleys  720 -M 4 A do not interfere with the operation of the cone assemblies, hence the width of the portions of the spring-loaded slider pulleys  720  using pin belt spring-loaded slider pulleys  720 -M 4 A that are positioned between the pin belt torque transmitting member  590  side members are less than the distance between the side members of pin belt torque transmitting member  590 , see  FIG. 123 . 
   In addition, cross-sections for various alternate pin transmission belts that can be used with front pin belt cone assembly  520 A and back pin belt cone assembly  520 B are shown in  FIGS. 124 ,  125 , and  126 . The centerline of the teeth, which here are also pins, of the pin transmission belts should also be located at the neutral-axis of the pin transmission belts. In  FIG. 124 , the pin transmission belt is labeled as pin transmission belt A  630 A, and it consists of a rubber belt A  630 A-M 1  and pin teeth A  630 A-M 2 , which have the shape of a pin. This pin transmission belt is basically the same as pin transmission belt  630  described earlier. In  FIG. 125 , the pin transmission belt is labeled as pin transmission belt B  630 B, and it consists of a rubber belt B  630 B-M 1  and pin teeth B  630 B-M 2 , which have the shape of a pin. In  FIG. 126 , the pin transmission belt is labeled as pin transmission belt C  630 C, and it consists of a rubber belt C  630 C-M 1  and pin teeth C  630 C-M 2 , which have the shape of a pin. 
   Pulleys that can be used as spring-loaded slider pulleys, which are pulleys that are pressed by the spring-loaded slider pulley assemblies  720  against the surfaces of the cones and are used to maintain the axial alignment of the transmission belts and provide coverage, if required, for pin transmission belt A  630 A, pin transmission belt B  630 B, and pin transmission belt C  630 C are shown in  FIGS. 127 ,  128 , and  129 .  FIG. 127  shows a pin belt spring-loaded slider pulley A  721 A that can be used with pin transmission belt A  630 A.  FIG. 128  shows a pin belt spring-loaded slider pulley B  721 B that can be used with pin transmission belt B  630 B.  FIG. 129  shows a pin belt spring-loaded slider pulley C  721 C that can be used with pin transmission belt C  630 C. In order to use these pulleys, these pulleys are mounted on the spring-loaded slider pulley assemblies  720  in-place of the spring-loaded slider pulleys  720 -M 4  described earlier. These pulleys should be mounted in the same manner slider pulleys  720 -M 4  are mounted. 
   It is recommended that the inner side surfaces of these pulleys, which engage with the side surfaces of their pin transmission belts, have a low friction coating, so as to minimize frictional losses. For optimum performance, friction between the inner side surfaces of these pulleys and the side surfaces of their pin transmission belts should be minimized. Hence for pin belt spring-loaded slider pulley A  721 A and pin belt spring-loaded slider pulley B  721 B, the distance between the inner side surfaces of these pulleys should not be narrower than distance between the side surfaces of their pin transmission belts. Also, here due to its V-shape, pin belt spring-loaded slider pulley C  721 C should have the least amount of friction, since sliding friction between the inner side surfaces of this pulley with the surfaces of its pin transmission belt is minimized because contact between the side surfaces only occur at one section, which is the section where the transmission belt is closest to the center of rotation of pin belt spring-loaded slider pulley C  721 C; and at this section, no relative sliding between side surfaces has to occur. Obviously like pin belt spring-loaded slider pulley  720 -M 4 A, shown in  FIG. 123 , pin belt spring-loaded slider pulley A  721 A, pin belt spring-loaded slider pulley B  721 B, and pin belt spring-loaded slider pulley C  721 C should be shaped so that they don&#39;t interfere with the operation of their torque transmitting members. 
   For the tensioning pulleys of tensioner pulley assemblies  740 , which are used to apply tension to the slack side of the transmission belts, like for the spring-loaded slider pulleys described in the previous paragraph, for optimum performance it is desirable to have the friction between the inner side surfaces of the tensioning pulleys and the side surfaces of their transmission belts minimized. This can be achieved by utilizing alignment wheels pulley assembly  730  shown as a front-view in  FIG. 130A  and as an end-view in  FIG. 130B . The alignment wheels pulley assembly  730 , has a alignment wheels pulley shaft  731 , which is shown as a front-view in  FIG. 131A  and as an end-view in  FIG. 131B . Alignment wheels pulley shaft  731  consists of a round center shape, which is labeled as alignment wheels pulley shaft round shape  731 -S 2 , and two symmetrical square shapes, which are centric to pulley shaft round shape  731 -S 2 , located to the left and right of pulley shaft round shape  731 -S 2 , labeled as alignment wheels pulley shaft square shapes  731 -S 1 . A square cut extrudes through the entire length of alignment wheels pulley shaft  731 . The center of the square cut coincides with the center of alignment wheels pulley shaft  731 , and its surfaces are parallel to the surfaces of the alignment wheels pulley shaft square shapes  731 -S 1 . 
   As described earlier, tensioner pulley assembly  740  is identical to spring-loaded slider pulley assembly  720 , except that it has a pulling spring and/or a pulling weight instead of a pushing spring. There fore, it also has a clevis on which a pulley or in this case an alignment wheels pulley assembly can be mounted. The clevis for tensioner pulley assembly  740  is labeled as tensioner pulley clevis  740 -M 3 . Tensioner pulley clevis  740 -M 3  is identical to spring-loaded slider pulley clevis  720 -M 3 , except that it has square holes for a square rod  732  instead of round holes for a spring-loaded slider shaft  720 -M 5  that spring-loaded slider pulley clevis  720 -M 3  has. And obviously if tensioner pulley clevis  740 -M 3  is used for an alignment wheels pulley assembly  730 , the dimension of tensioner pulley clevis  740 -M 3  has to be adjusted accordingly so that an alignment wheels pulley assembly can be mounted on it as shown in  FIGS. 130A and 130B . 
   In the assembled state of alignment wheels pulley assembly  730 , alignment wheels pulley shaft  731  is placed between the two parallel plates of tensioner pulley clevis  740 -M 3 , and secured by sliding, a square rod  732 , which has slightly smaller dimensions than the square cut of alignment wheels pulley shaft  731  through the square cut of alignment wheels pulley shaft  731  and square holes of the parallel plates of tensioner pulley clevis  740 -M 3 . Once slid through, each end of square rod  732  is then secured in place using a square rod locking pin  733  that is slid into a matching hole at each end of square rod  732 . In the alignment wheels pulley assembly  730  assembled state, a tensioning pulley  734  is positioned on the alignment wheels pulley shaft round shape  731 -S 2  of alignment wheels pulley shaft  731 . Obviously all items on alignment wheels pulley shaft  731  are inserted into alignment wheels pulley shaft  731  before alignment wheels pulley shaft  731  is positioned between the two parallel plates of tensioner pulley clevis  740 -M 3 . At the center of tensioning pulley  734  a tensioning pulley sleeve bearing  734 -M 1  is pressed in. Tensioning pulley sleeve bearing  734 -M 1  extends slightly to the left and right surface of tensioning pulley  734 , so as to minimize friction between tensioning pulley  734  and the alignment frames  735  placed to the left and right of tensioning pulley  734 . The top shape of each alignment frame  735  is shaped like a square frame that can be tightly slid into an alignment wheels pulley shaft square shape  731 -S 1  of alignment wheels pulley shaft  731 . At the midpoint of the bottom surface of each alignment frame  735  a round shaft, that extends vertically downwards, is shaped. The bottom portion of the round shaft of each alignment frame  735  has a smaller diameter then the upper portion of the round shaft. Also, near the bottom end of the bottom portion of the round shaft of each alignment frame  735 , a cut for an alignment wheel locking ring  736  exists. Into the bottom portion of the round shaft of each alignment frame  735 , an alignment wheel  737  is slid in. The axial positions of the alignment wheels  737  are then secured by inserting a alignment wheel locking ring  736  into the designated cuts of the bottom portions of the round shafts of the alignment frames  735 . The inner and side surfaces of the alignment wheels  737  have a low friction coating, so that alignment wheels  737  can rotate without much friction relative to their alignment frames  735  and their alignment wheel locking rings  736 . Since the alignment wheels  737  are wider than the alignment frames  735 , in order to allow the alignment wheels  737  to rotate properly, an alignment frame spacer  738  is positioned between each parallel plate of tensioner pulley clevis  740 -M 3  and alignment frame  735 . 
   The alignment wheels pulley assembly  730  like a regular tensioning pulley should be mounted on a tensioner pulley assembly  740  such as shown in  FIGS. 121 and 122 . Also, the distance between the alignment wheels  737  should correspond to the width of its transmission belt  600 , so that the alignment wheels  737  can sufficiently maintain the axial alignment of its transmission belt without applying any significant frictional resistance to its transmission belt. 
   If desired, in order to position the pulleys that maintain the axial alignment, engagement coverage, and tension of the transmission belts, instead of the spring-loaded sliders, sliders that slide on slides as described in the Sliding Cone Mounting Configuration section and similarly used for the tensioning wheels  1105  described in Continuous Variable Transmission Variation  2  (CVT  2 ) section can be used. If the required pushing force of a spring-loaded slider pulley assembly  720  used to provide sufficient engagement coverage, such as spring-loaded slider pulley assembly C  720 C shown in  FIG. 118 , is quite large, than it might be more practical to use the slide on a slides configuration instead. 
   In order to control the adjusters of the CVT&#39;s described above, the methods described earlier can be used. Although the configuration of the CVT shown in  FIGS. 121 and 122 , is basically a mirror image of the configuration discussed in the Adjuster System for CVT  2  section, the same principles and methods used and described in the Adjuster System for CVT  2  section and other relevant sections of this application also apply here. In the Adjuster System for CVT  2  section, the amount of transmission ratio change rotation depends on the angle θ between point M and point N. For the CVT&#39;s described in this section, point N is identical to point N of the Adjuster System for CVT  2  section. Hence here the points N are also the points where the transmission belts first touch the upper surface of their cone assemblies. However, for the CVT&#39;s described in this section, point M is not the midpoint of the torque transmitting member, for front pin belt cone assembly  520 A and back pin belt cone assembly  520 B, the points M are located at the angular position where the centerline of the torque transmitting member slides  560 -S 2  are positioned see  FIGS. 91B and 92B . And for front sliding tooth cone assembly  420 A and back sliding tooth cone assembly  420 B, the points M are located on the angular position where the mirror line of their teeth  450 -S 1  are located, see  FIG. 80 . From the description of the relevant sections of this application, such as the Adjuster System for CVT  2  section and the CVT  2 . 4  section for example, somebody skilled in the art should be able to determine proper configurations and controls for adjuster(s) for the CVT&#39;s described in the Alternate CVT&#39;s section. 
   Also in order to use the control methods described in the Gap In Teeth section, a gaps method pin belt torque transmitting member  590 A can be used. A gaps method pin belt torque transmitting member  590 A, shown as a front-view in  FIG. 132  and as a top-view in  FIG. 133 , is similar to the pin belt torque transmitting member  590  described previously. The difference between the gaps method pin belt torque transmitting member  590 A and pin belt torque transmitting member  590  is that it has two tooth shapes instead of just one. The leading end or leading end portion of gaps method pin belt torque transmitting member  590 A has a quarter circular tubular section tooth shape, which tubular section starts at the center height of the tooth and ends at bottom surface of the tooth. This tooth shape is labeled as quarter circular pin belt tooth  591 -S 2 A, and can be seen in  FIGS. 132 and 133 . The trailing end or trailing end portion of gaps method pin belt torque transmitting member  590 A has the pin belt teeth  591 -S 2  described earlier, which have an extension that extends slightly beyond the bottom surfaces of their teeth. The distance between the teeth should be large enough such that the quarter circular pin belt teeth  591 -S 2 A can be positioned between the teeth of its transmission belt without being in contact with the teeth of its transmission belt when its gaps method pin belt torque transmitting member  590 A is mated with its transmission belt. However, the distance/pitch between the teeth of the gaps method pin belt torque transmitting member should match the distance/pitch between the teeth of its transmission belt. Here because the quarter circular pin belt teeth  591 -S 2 A do not have front extensions, the gaps method pin belt torque transmitting member  590 A about to be mated, which should be on the input shaft/spline, can be a little bit late relative to its transmission belt. In order to achieve this, the “gap offset value” described in the Gap In Teeth section can be used, so that during initial mating the quarter circular pin belt teeth  591 -S 2 A are positioned between teeth of their transmission belt without touching the teeth of its transmission belt. If “engagement adjustment”, where the adjuster rotates the cone assembly about to be engaged so that its teeth are touching the teeth of their transmission belt so that the engagement between the teeth can be used for desired torque transmission as described in the Gap In Teeth section, is used, then it is recommended that the amount of quarter circular pin belt teeth  591 -S 2 A should be selected such that for all instances “engagement adjustment” occurs before pin belt teeth  591 -S 2  are engaged, otherwise, increase in tension in the respective transmission belt will occur. If “engagement adjustment” is not used, than to ensure smooth operation, the quarter circular pin belt teeth  591 -S 2 A, should cover the leading end portion of gaps method pin belt torque transmitting member  590 A in a manner such that for every transmission ratio of the CVT, while both cone assemblies are engaged, for gaps method pin belt torque transmitting member  590 A just mated with its transmission belt only the quarter circular pin belt teeth  591 -S 2 A are mated, but not necessarily engaged, with the teeth of its transmission belt. 
   Furthermore, in order to prevent damage to the CVT in case the adjusters did not properly position the transmission belt about to be engaged so as to allow smooth engagement, a “tension measurement engagement correction” method can be used. Here the adjustments/corrections provided is based on the amount of tension in the tense side of the transmission belts. The amount tension in the tense side of the transmission belts can be measured by torque sensors mounted on the input shaft/spline of the CVT, which measure the torque on the input shaft/spline of the CVT, or by maintaining pulleys that are positioned and configured so that they can measure the tension in the tense side of the transmission belts. In order for this method to work, the transmission belts should be able to resist flexing that compensates for improper engagement. Here a sudden increase in tension or sudden increase in torque can be an indication that improper engagement occurred. In order to determine whether the increase in tension or torque is an indication of improper engagement, a high torque limit value and/or high torque change limit value, programmed into the controlling computer can be used. Or if a tension measuring load-cell is used than a high tension limit value and/or high tension change limit value, programmed into the controlling computer can be used. The values for the high limit values can be obtained experimentally. 
   If “tension measurement engagement correction” method is used for a CVT that uses gaps method pin belt torque transmitting members  590 A, because of the shape of the quarter circular pin belt teeth  591 -S 2 A, initial improper engagement can only occur between the back portion of the leading circular pin belt tooth  591 -S 2 A and its transmission belt, since circular pin belt teeth  591 -S 2 A do not have a front portion. Hence improper engagement can only occur when the cone assembly about to be engaged is to early. Therefore, when the controlling computer senses that improper engagement occurred through the tension measurement in the transmission belt just engaged, or the torque measurement for the cone assembly just engaged, it rotates the transmission belt just engaged, which is not properly engaged, forward relative to its cone assembly or it rotates its cone assembly, which is not properly engaged, backward relative to its transmission belt, until the tension and/or torque measurement has dropped to an acceptable level. Here rotating forward means rotating in the direction the input and output shaft/spline are rotating and rotating backward means rotating in the opposite direction the input and output shaft/spline are rotating. The controlling computer can use the tension measurement of the currently engaged transmission belt or torque measurement of the currently engaged cone assembly before improper engagement occurred as a reference value, a sudden jump in tension and/or torque measurement is an indication of improper engagement. A high limit tension and/or torque measurement value can also used. 
   If “tension measurement engagement correction” method is used for a CVT that uses pin belt torque transmitting members  590  or other torque transmitting members, then once the controlling computer senses improper engagement, it first has to guess whether it is because the cone assembly about to be engaged is positioned to early or to late relative to its transmission belt and make arbitrary adjustments, and then based on the feed-back from the tension measuring load-cell or torque sensor it can determine whether cone assembly is positioned to early or to late and then provide adjustments until the tension and/or torque measurement has dropped to an acceptable level. For example, in case the torque transmitting member is positioned to early relative to its transmission belt, then because of the increased tension in the respective transmission belt or increased torque in the respective cone assembly, the adjuster arbitrarily rotates the respective transmission belt forward relative to its cone assembly, which is the proper direction. Then the controlling computer should sense that the tension in the respective transmission belt starts to decrease and hence keep on rotating in the same direction until the tension and/or torque measurement has dropped to an acceptable level. In case in the same situation, the adjuster arbitrarily rotates the respective transmission belt backward relative to its cone assembly, then the controlling computer should sense that the tension in the respective transmission belt starts to increase or stay level, and based on this information, the controlling computer knows that it is rotating the respective transmission belt in the wrong direction, hence it immediately changes direction and keeps on rotating in that direction until the tension and/or torque measurement has dropped to an acceptable level. In case the torque transmitting member is positioned to late relative to its transmission belt, then the controlling computer uses the same procedures described before in order to reduce the respective tension and/or torque measurement, except that here, in order to reduce the respective tension and/or torque measurement the adjuster needs to rotate the respective transmission belt backwards relative to its torque transmitting member, while rotating the respective transmission belt forward relative to its cone assembly increases the respective tension and/or torque measurement. 
   In order to ensure that the procedures described in the previous paragraph operate properly, it needs to be ensured that when the adjuster rotates in the proper direction the respective tension and/or torque measurement decreases and it also needs to be ensured that when the adjuster rotates in the wrong direction the respective tension and/or torque measurement increases. In order to ensure this, all surfaces of the pin belt teeth  591 -S 2  that come into contact with the teeth of its transmission belt, are shaped so that the contact surface increase in height as it is positioned further to the left and further to the right from the lowest point, which located at the vertical symmetry line of round flange  591 -S 1 . An example of a tooth shape which end surfaces are reshaped to ensure this is shown in  FIG. 134  and labeled as pin belt tooth B  591 -S 2 B. This reshaping can also be applied to quarter circular pin belt teeth  591 -S 2 A. A reshaped quarter circular pin belt tooth  591 -S 2 A, which is labeled as pin belt tooth C  591 -S 2 C, is shown in  FIG. 135 . for  591 -S 2 C only the back surface since when a little too late no tense increase has no front surface no adjust 
   Furthermore although during normal operation at no instance should a transmission belt cover the entire surface of its cone not covered by its torque transmitting member; an emergency transmission ratio, where this is the case can be added in case one transmission belt fails. For smooth operation for the emergency transmission ratio, the circumferential length of the surface of the cone not covered by its torque transmitting member should be a multiple of the width of its teeth. Also when the emergency transmission ratio is used a warning signal should be send to the user. A warning signal alarm should also be send when continuous or excessive improper engagement occurs. 
   Also if only quarter circular pin belt teeth  591 -S 2 A are used for a torque transmitting member then in order to ensure smooth and proper operation, instances where the output shaft is pulling the input shaft should be minimized or eliminate. This can be done by mounting a one way clutch between the output shaft and the output device being rotated, so that the output shaft can rotate the output device in the driving direction but the output device can not rotate the output shaft in the driving direction, and by ensuring that the friction in the output shaft is larger than in the engine. A one way clutch which can be locked or which direction can be reversed on command can be used in case reverse rotation is required. In addition, if desired the pins on the transmission belts can be replaced with involute tooth shaped pieces that engage with an involute tooth shape or involute tooth shaped pieces mounted on the torque transmitting members. 
   In addition for the CVT&#39;s described previously, if friction torque transmitting members, which are not toothed are used, then a CVT that does not need adjusters can be constructed by using a configuration that is identical to the configuration for a CVT  2 . 
   Chain for Single Tooth Cone and Block Belt for Single Tooth Cone 
   A link labeled as single tooth cone link A  800 A that can be used to form a chain that can be used with a single tooth cone is shown as a side-view in  FIG. 136B , as a front-view in  FIG. 136A , as a sectional-view in  FIG. 136C , and as a partial back-view, only showing the back surface, in  FIG. 136D . The holes of single tooth cone link A  800 A through which the single tooth cone link connecting pins  801  are inserted are labeled as single tooth cone link holes A  800 A-S 1  and the tooth profile of single tooth cone link A  800 A is labeled as single tooth cone tooth profile A  800 A-S 2 . In order to allow smooth engagement, it is recommended that single tooth cone tooth profile A  800 A-S 2  has an involute tooth shape. In  FIGS. 136A-136D  and  FIGS. 137A-137B  the tooth profile of the links might not show a proper involute tooth shape; however, they represent an involute tooth shape. The bottom surfaces of single tooth cone link A  800 A, excluding the cut-out surface of single tooth cone tooth profile A  800 A-S 2 , are labeled as single tooth cone bottom surfaces A  800 A-S 3  and are tapered as to match the taper of the surface of its single tooth cone. The cut-out surface of single tooth cone tooth profile A  800 A-S 2  is tapered as to match the taper of the tooth of its single tooth cone. The taper of the tooth of the single tooth cone might have a taper that matches the taper of the conical surface of the single tooth cone, however for optimum and smooth performance it is recommended that the taper of the tooth is shaped so that it does not affect the radial position of the chain while providing a maximum engagement surface. Here because the links of the chain are mainly supported by their bottom surfaces, the change in curvature at different diameters affects where the tooth profiles of the links, which is located at the center of the links, is positioned relative to the surface of the cone; and this will affect the taper of the tooth of the single tooth cone that perfectly matches the tooth profiles of the links. Also if providing a maximum engagement surface is not that important, then smooth performance can be ensured by making the tooth of the single tooth cone sufficiently shorter than the tooth profile of its chain, so that the chain is only supported by the bottom surfaces of its links. 
   Also it needs to be ensured that when the chain is positioned at the smallest circumference of its cone, no bottom surfaces of any links are interfering with the tooth of its single tooth cone. This can be done by selecting the proper smallest circumference of the single tooth cone, or by slightly modifying the shape and dimension of the links. A shape of an alternate single tooth cone link A  800 A, which is labeled as alternate single tooth cone link A  810 A is shown in  FIG. 137C . Here, as can be seen in  FIG. 137C , the width of the tapered bottom surfaces are reduced. For this modified link shape, the surfaces that can cause interference with the tooth of its single tooth cone are reshaped so that a single tooth cone with a smaller circumference can be used. 
   A single tooth cone, labeled as chain single tooth cone  820 , and its tooth, labeled as chain single tooth cone tooth  820 -S 1 , is shown as a front-view in  FIG. 138A  and as an end-view in  FIG. 138B . Chain single tooth cone tooth  820 -S 1 , should have the same basic profile as the tooth profiles of the links. If with regular involute tooth shapes smooth engagement cannot be achieved then slightly modified involute tooth shapes can be used for the links and for the single tooth. Using a model the interfering surfaces can easily be identified and reshaped. The “gaps between teeth” method described earlier can also be used to resolve this issue. 
   Shown in  FIG. 137A  and  FIG. 137B  is a partial chain section that is constructed from a single tooth cone link B  800 B which right end is sandwiched by single tooth cone link C  800 C, not shown in  FIG. 137A , and a single tooth cone link A  800 A. Single tooth cone link B  800 B and single tooth cone link C  800 C, are identical to single tooth cone link A  800 A, except that their bottom surfaces, labeled as single tooth cone bottom surfaces B  800 B-S 3  and single tooth cone bottom surfaces C  800 C-S 3 , are longer than the bottom surfaces of single tooth cone link A  800 A. Since single tooth cone link B  800 B and single tooth cone link C  800 C are located further towards smaller end of the cone relative to single tooth cone link A  900 A, the bottom surfaces of single tooth cone link B  900 B and single tooth cone link C  900 C are longer so that when the chain portion is aligned in a straight line, the bottom surfaces from its links form a smooth continuous taper that matches the taper of the surface of its cone, see  FIG. 137B . Because of the shape of the bottom surfaces of the links, when an unassembled chain section is placed at an axial position on the surface of its cone, the link holes of the links are aligned so that a pin parallel to the shaft of the cone can be inserted through a link hole of single tooth cone link A  800 A, a link hole of single tooth cone link B  800 B, and a link hole of single tooth cone link C  800 C so that the links can be linked together. If required, a slight play between the link holes of the links and the single tooth cone link connecting pins  801  can be allowed. The chain portion shown in  FIGS. 137A and 137B  is linked together in a similar manner as a bicycle chain is linked together using single tooth cone link connecting pins  801  and single tooth cone link locking rings  802 , which are inserted into designated grooves of single tooth cone link connecting pins  801 . For optimum performance, friction between the parts of discussed above should be minimized. 
   A transmission pulley, labeled as chain transmission pulley  850 , that can be used with a chain constructed in manner the shown in  FIG. 137A  and  FIG. 137B  is shown as front-view in  FIG. 139A  and as an end-view in  FIG. 139B . Chain transmission pulley  850  is shaped like a toothed pulley. It has two chain transmission pulley side surfaces  850 -S 1  that sandwich a toothed conical surface  850 -S 2 . The taper of the toothed conical surface  850 -S 2  should match the taper of its single tooth cone, and the distance between the chain transmission pulley side surfaces  850 -S 1  should correspond to the width of the chain, which in  FIG. 137A  and  FIG. 137B  depends on the length of the single tooth cone link connecting pins  801 . The toothed conical surface  850 -S 2  has chain transmission pulley teeth  850 -S 3 , which should have the same basic profile as the chain single tooth cone tooth  820 -S 1  of its single tooth cone. If interference between chain transmission pulley teeth  850 -S 3  and portions of the links of its chain exist, then some chain transmission pulley teeth  850 -S 3  can be skipped if this helps remedy the problem. However it needs to be ensured that for all transmission ratios of the CVT where chain transmission pulley  850  is used, at least one tooth of chain transmission pulley  850  is always engaged with its chain. For chain transmission pulley  850  shown in  FIG. 139A  and  FIG. 139B , every other chain transmission pulley tooth  850 -S 3  is skipped. Also, the circumference of chain transmission pulley  850  should be large enough so that no bottom surface of any link of its chain is interfering with a chain transmission pulley tooth  850 -S 3 . 
   In case the cone has only one tooth, then changes in the pitch of the teeth of the chain can be allowed. For the chain portion shown in  FIGS. 137A and 137B , the neutral-axis or bending-axis is located at the centers of the single tooth cone link connecting pins  801 . From  FIGS. 136C and 136B , it can be seen that the top height of the tooth cut-out at the mid-cross-sectional surface of single tooth cone link A  800 A is located at the bending-axis. Therefore, the distance between the top height of the tooth cut-out as measured from the center of a pin to the top height of a tooth cut-out to the center a pin to the top height of tooth cut-out and so forth, at the mid-cross-sectional surface of single tooth cone link A  800 A remains constant regardless of the diameter of the surface of the cone where the chain is positioned. Hence in order to determine the arc length of the non-torque transmitting arc as needed for the graphs shown in FIGS.  21 A/B/C, the axial position where the mid-cross-sectional surface of single tooth cone link A  800 A is positioned should be used. And the arc radius that used to determine the arc length of the critical non-torque transmitting arc and the arc length of the required adjustment, as represented by the horizontal-axis and the vertical-axis of the graphs shown in FIGS.  21 A/B/C, should correspond to the radius where the top height of the tooth cut-outs will be at for that axial position. And the width of a tooth, w t , should be measured from the top height of a tooth cut-out to the next top height of a tooth cut-out at the mid-cross-sectional surfaces of single tooth cone links A  800 A. Also, the arc length of the critical non-torque transmitting arc starts at the center-line of the tooth of one single tooth cone and ends at the center-line of the tooth of the other single tooth cone. 
   Since the chain is formed by links, it will not form a perfectly round segment, whereas the cone is perfectly round, hence the graphs shown in FIGS.  21 A/B/C are not perfect for this application. In order to deal with this, the “gaps between teeth” method described earlier can be used to compensate for this. Modified graphs based on the graphs shown in FIGS.  21 A/B/C, which are dependent on transmission ratio can also be made. A modifying term for the graphs, which can dependent on the transmission ratio and compensate for the fact that the chain will not form a perfectly round segment can be obtained experimentally and/or mathematically. An experimental method can also used, by moving the chain from the smaller end to the larger end of its cone and observing the required adjustments needed at different diameters and then programming these values into the controlling computer. 
   Besides the chain described in the previous paragraphs, a blocks transmission belt  842 , shown as a front-view in  FIG. 140A  and as an end-view in  FIG. 140B , that is formed by tooth blocks  840  that are joined together by rubber blocks  841  can be used. The rubber blocks  841  have rubber blocks steel reinforcements  841 -M 1 , which increases the strength of the transmission belt but are optional, and are joined to the tooth blocks  840  using a strong adhesive. In case more flexing is desired, which might be the case if no or inaccurate adjusters are used, then the rubber blocks steel reinforcements  841 -M 1  can be omitted. Since it is desirable to have the transmission belt resting on the rubber blocks  841  instead on the tooth blocks  840 , the tooth blocks  840  are not resting on the surface of their cone. Hence the tooth cut-outs of the tooth blocks  840  are positioned above the surface of their cone. In order to allow smooth engagement, between the tooth cut-outs of the tooth blocks  840  and the tooth of their single tooth cone, the tooth of their single tooth cone has a base that positions the tooth so that it can smoothly engage with the tooth blocks  840 . A single tooth cone that can be used with blocks transmission belt  842  is shown as a front-view in  FIG. 141A  and as an end-view in  FIG. 141B . It is labeled as blocks belt single tooth cone  860 , and its tooth is labeled as blocks belt single tooth cone tooth  860 -S 1 . If desired, this transmission belt can be used with a cone with two opposite positioned teeth as shown as a front-view in  FIG. 142A  and as an end-view in  FIG. 142B . This cone is labeled as opposite teeth cone  861 , and its teeth are labeled as opposite teeth cone teeth  861 -S 1 . A transmission pulley that is identical to chain transmission pulley  850  except that it has teeth that have the same basic profile as blocks belt single tooth cone tooth  860 -S 1  of its single tooth cone can be used here. It is shown as a front-view in  FIG. 143A  and as an end-view in  FIG. 143B . 
   As can be seen from  FIG. 140B , the mid-height of the tooth cut-outs, shown as an angled center-line, at the mid-width of tooth blocks  840 , are located at the neutral-axis, shown as a horizontal center-line, of blocks transmission belt  842 . Therefore, the arc lengths between the mid-height of the tooth cut-outs at the mid-width of the tooth blocks  840  remain constant or almost constant regardless of the diameter of the surface of the cone where blocks transmission belt  842  is positioned. Hence in order to determine the arc length of the non-torque transmitting arc as needed for the graphs shown in FIGS.  21 A/B/C, the axial position where the mid-width of the tooth blocks  840  is positioned should be used. And the arc radius that is used to determine the arc length of the critical non-torque transmitting arc and the arc length of the required adjustment, as represented by the horizontal-axis and the vertical-axis of the graphs shown in FIGS.  21 A/B/C, should correspond to the radius where the mid-height of the tooth cut-outs will be at that axial position. And the arc length of the critical non-torque transmitting arc starts at the center-line of the tooth of one single tooth cone and ends at the center-line of the tooth of the other single tooth cone. Or if an opposite teeth cone  861  is used, it starts at the center-line of one tooth and ends at the center-line of the other tooth of that opposite teeth cone  861 . And the width of a tooth, w t , should be measured from the mid-height of a tooth cut-out to the next mid-height of a tooth cut-out at the mid-width of the tooth blocks  840 . 
   Since the transmission belt described in the previous paragraph will not form a perfectly round segment, the graphs shown in FIGS.  21 A/B/C are not perfect for this application. In order to deal with this, the “gaps between teeth” method described earlier can be used to compensate for this. Modified graphs based on the graphs shown in FIGS.  21 A/B/C, which are dependent on transmission ratio can also be made. A modifying term for the graphs, which can dependent on the transmission ratio and compensate for the fact that the chain will not form a perfectly round segment can be obtained experimentally and/or mathematically. An experimental method can also used, by moving the chain from the smaller end to the larger end of its cone and observing the required adjustments needed at different diameters and then programming these values into the controlling computer. 
   Somebody skilled in the art should be able to construct a CVT  1  or a CVT  2  using the items described in this section based on the description of this patent. If the items described in this section are used to construct a CVT  2 , then the same basic configuration used for a CVT  2  using a front sliding tooth cone assembly  420 A and a back sliding tooth cone assembly  420 B, as described in the Alternate CVT&#39;s section and shown in  FIGS. 89 and 118 , can be used here. 
   If the configuration shown in  FIGS. 89 and 118  is used with the items described in this section, then pin belt spring-loaded slider pulleys  721 B can be used for the pulleys for spring-loaded slider pulley assembly A  720 A, spring-loaded slider pulley assembly B  720 B, and spring-loaded slider pulley assembly C  720 C. An arrangement where a pin belt spring-loaded slider pulley  721 B is used with a chain constructed out of the links of this section is shown in  FIG. 144 . Pin belt spring-loaded slider pulley  721 B can also be used with the blocks transmission belt  842 . Obviously the pin belt spring-loaded slider pulleys  721 B need to dimensioned so that they do not interfere with the tooth or teeth of their cone. And for tensioner pulley assembly  740 , a pin belt spring-loaded slider pulley A  721 A, shown in  FIG. 127 , can be used. Here the taper of the pin belt spring-loaded slider pulley A  721 A should match the taper of the cone where the chain or transmission belt described in this section is used. Also, here during operation pin belt spring-loaded slider pulley  721 B is forced up and down as it is engaged with different portions of the chain or blocks transmission belt. Hence there will be energy loses due to the compression and decompression of the spring of the spring-loaded sliders. Hence it might be better to replace spring-loaded slider pulley assembly A  720 A and spring-loaded slider pulley assembly B  720 B, which are used to maintain the axial alignment of their chain or blocks transmission belt, with guides described latter in this application. And for the chain described in this section, the pulleys for the spring-loaded slider pulley assembly C  720 C and the tensioner pulley assembly  740 , can each be replaced with two sprockets  702  mounted in parallel, as shown in  FIGS. 117A and 117B . The sprockets  702  should be designed so that they can smoothly engage with the single tooth cone link connecting pins  801  of the chain. Hence the pitch of the teeth of the sprockets  702  should match the pitch of the single tooth cone link connecting pins  801  of the chain. And the distance between the sprockets  702  should be selected such that distance between the inner surfaces of the sprockets  702  is slightly wider than the width of the assembled links as shown in  FIG. 119B . For spring-loaded slider pulley assembly C  720 C, it needs to be ensured that the sprockets  702  mounted in parallel do not interfere with the tooth or teeth of its cone. This can be achieved by replacing spring-loaded slider pulley assembly C  720 C with a slider mounted on a slide configuration as described in the Sliding Cone Mounting Configuration section and similarly used for the tensioning wheels  1105  described in the Continuous Variable Transmission Variation  2  (CVT  2 ) section of this patent. Here the slide should be positioned and oriented sufficiently away from its cone so that the respective sprockets  702  mounted in parallel can provide sufficient engagement coverage without interfering with the tooth or teeth of its cone. Pins, labeled as rubber block pins  841 -M 2 , can also be inserted into the rubber blocks  841  of the blocks transmission belt  842  described earlier, as shown in  FIGS. 145A and 145B , so that the two sprockets  702  mounted in parallel described above can be used with the modified blocks transmission belt as shown in  FIGS. 145A and 145B . 
   Obviously the engagement statuses for the cone assemblies, as discussed in the Adjuster System for CVT  2  section, can be modified so that they can be used for single tooth cones, such as, 1) single tooth cone A engaged and single tooth cone B not engaged, 2) single tooth cone A engaged and single tooth cone B almost engaged, 3) single tooth cone A engaged and single tooth cone B engaged, 4) single tooth cone A almost not engaged and single tooth cone B engaged, 5) single tooth cone A not engaged and single tooth cone B engaged, 6) single tooth cone A almost engaged and single tooth cone B engaged, 7) single tooth cone A engaged and single tooth cone B engaged, 8) single tooth cone A engaged and single tooth cone B almost not engaged. Also somebody skilled in the art should be able to apply the methods described in this application, such as the engagement statuses, to other CVT&#39;s  1  and CVT&#39;s  2 . 
   Guides 
   In order to maintain the axial position of a transmission belt or a chain of a CVT where the cones move axially and the transmission belts are stationary, guides for moving cones  900 , which is shown as a front-view in  FIG. 146A  and as an end-view in  FIG. 146B , can be used. The guides consist of two parallel round guides for moving cones rods  901 , which are aligned vertically. Each guides for moving cones rod  901  is slidably inserted into a guides for moving cones sleeve  902 , which is fixed to the frame of the CVT. The bottom ends of the guides for moving cones rods  901  are welded on a guides for moving cones connector bar  903 . Welded on the bottom surface of guides for moving cones connector bar  903  are two parallel guides for moving cones guiding plates  904 . If the guides are used with a belt or chain that has tapered side surfaces, then the inner surfaces of the guides for moving cones guiding plates  904  can be tapered as to match the taper of its belt or chain. The inner surfaces of the guides for moving cones guiding plates  904  should have smooth and low friction surfaces, since a portion of a transmission belt or a chain will be placed between them. In order to able to use the guides for moving cones guiding plates  904 , the transmission belt or the chain should be dimensioned so that a portion of the transmission belt or the chain can be placed between the guides for moving cones guiding plates  904 , without having the guides for moving cones guiding plates  904  interfere with the torque transmitting member, non-torque transmitting member, single tooth, opposite teeth, or any other part of its cone or cone assembly. In order to control the vertical position of the guides, a guides for moving cones linear actuator  905  is used. The guides for moving cones linear actuator has a linear actuator extension sensor and is controlled by the controlling computer of the CVT. At the mid-length of the upper surface of the guides for moving cones connector bar  903 , a plate with a hole is welded on. This plate will be used to mount the clevis of the bottom end of the guides for moving cones linear actuator  905  using a locking pin. The clevis of the top end of the guides for moving cones linear actuator  905  will be mounted to another plate with a hole also using locking pin. The plate with a hole for mounting the clevis of the top end of the guides for moving cones linear actuator  905  is fixed to the frame of the CVT and is positioned so that the guides for moving cones linear actuator  905  is oriented parallel to the guides for moving cones rods  901 . In order to properly control the guides for moving cones linear actuator  905  so that the guides for moving cones guiding plates  904  are properly positioned as to help maintain the axial position their transmission belt or their chain without interfering with any part of their cone for all transmission ratios, a linear relationship between the required extension of the guides for moving cones linear actuator  905  versus the axial position of its cone, which gradient depends on the taper of its cone, can be programmed into the controlling computer. Here for each transmission ratio, the controlling computer then controls guides for moving cones linear actuator  905  based on the programmed linear relationship. If for some reasons some other positioning routine to control guides for moving cones linear actuator  905 , which might be obtained experimentally, works better than a controlling routine based on a linear relationship, than that routine can be programmed into the controlling computer. 
   In order to maintain the axial position of a transmission belt or a chain of a CVT where the cones are stationary and the transmission belts move axially, guides for stationary cones  920 , which is shown as an end-view in  FIG. 147 , can be used. Guides for stationary cones  920  is identical to guides for moving cones  900  except that its two parallel round guides are aligned at an angle that matches the angle of their cone instead of being vertical. Hence, like the guides for moving cones  900 , guides for stationary cones  920  also has two parallel round guides, which here are labeled as guides for stationary cones rods  921 , that are slidably inserted into sleeves, which here are labeled as guides for stationary cones sleeves  922 , which are fixed to the frame of the CVT. And as for the guides for moving cones  900 , here the bottom ends of the two parallel round guides are also welded on a horizontal bar, which here is labeled as guides for stationary cones connector bar  923 . And as for the guides for moving cones  900 , here welded on the bottom surface of the connector bar are two parallel guiding plates, which here are labeled as guides for stationary cones guiding plates  924 . And as for the guides for moving cones  900 , here the position of the guiding plates are also controlled by a linear actuator that is parallel to its parallel round rods, which here is labeled as guides for stationary cones linear actuator  925 , that has a linear actuator extension sensor and is controlled by the controlling computer of the CVT. In order to properly control guides for stationary cones linear actuator  925 , the controlling computer of the CVT controls the guides for stationary cones linear actuator  925  so that the axial position of the guides for stationary cones guiding plates  924  corresponds to the axial position of its transmission belt or chain. Based on the alignment of stationary cones linear actuator  925  somebody skilled in the art should be able to determine the relationship between the axial position of the guides for stationary cones guiding plates  924  and the extension of the guides for stationary cones linear actuator  925 . This relationship can than be programmed into the controlling computer so that it can properly control the guides for stationary cones linear actuator  925 . 
   Also if desired the movements of the guiding plates for guides for moving cones  900  and guides for stationary cones  920  can be controlled by connecting their connector bars to their mover frame used to control the transmission ratio. For the guiding plates for guides for moving cones  900 , the connector bar should be connected to its mover frame in manner such that it is axially maintained stationary relative to its mover frame but is allowed to slide vertically relative to its mover frame. Here a similar set-up used to control the position of the tensioning sliders described in the Sliding Cone Mounting Configuration section can be used. For the guiding plates for guides for stationary cones  920 , the connector bar should be connected to its mover frame in a manner such that its moves axially with its mover frame but is allowed to slide vertically relative to its mover frame. Here a similar set-up used to control the position of the tensioning wheels described in the Continuous Variable Transmission Variation  2  (CVT  2 ) section can be used. 
   The guides for moving cones  900  can be used to maintain the axial alignment of a transmission belt for all CVT&#39;s where the change in transmission ratio is achieved by moving the cones. And guides for stationary cones  920  can be used to maintain the axial alignment of a transmission belt for all CVT&#39;s where the change in transmission ratio is achieved by moving the transmission belt. 
   An example on how to use guides for moving cones  900  is shown in  FIG. 148 .  FIG. 148  shows a partial front-view were 3 moving cones guiding plates  904  of guides for moving cones  900  are used to maintain the axial position of a guides transmission belt  930  of a guides cone  931 , which has a guides torque transmitting member  932 . Here depending on the amount of axial bowing of the transmission belt and the accuracy requirement of the CVT more or less moving cones guiding plates  904  can be used. The description in this paragraph also applies to guides for stationary cones guiding plates  924  of guides for stationary cones  920 . 
   Preferred Tooth Shapes 
   Somebody skilled in the art should be able to select a tooth shape for the items described in this patent, since some well established theories about torque transmission using teeth could be applied here. Below the advantages and disadvantage of two tooth shapes recommended by the inventor are discussed. Obviously other tooth shapes can also be used. The simplest tooth shape is a square tooth shape. However the operation of this tooth shape is not very smooth, because some flexing of the transmission belt, if used, and the teeth occur when a tooth is only partially engaged with its mating tooth. If a gap is used between the teeth as described in the Gap in Teeth section of this application, then the gap should be wide enough so that adjusters can be used to adjust the rotational position of a torque transmitting device relative to another so that flexing due to partially engaged teeth can be eliminated. Another preferred tooth shape, is an involute tooth shape, this tooth shape offers the smoothest operation. By slightly modifying this tooth shape by increasing the width of the tooth at the base and continuously reducing the width of the tooth as the height is increased so that only perfectly aligned teeth engage, an even smoother operation can be achieved. However, this tooth shape might be more expensive to manufacture than the square tooth shape. 
   Best Mode Recommendation 
   The most recommended configuration of the invention based on optimal performance is the configuration for CVT  2 . 4 . The recommended cone assemblies and associated parts used to construct the CVT  2 . 4 , are the front pin belt cone assembly  520 A, the back pin belt cone assembly  520 B, and their associated parts as described in the Alternate CVT&#39;s section of this patent. 
   The configuration for this CVT allows the use of positive engagement devices that can theoretically engage perfectly due to the compensation for transition flexing. In addition, the transmission ratio can virtually, although maybe not actually, be changed at any instances due to the compensation of transmission ratio change rotation. Also the usage of two adjusters for CVT  2 . 4  minimizes the torque requirement of the adjusters by allowing the usage of the over adjustment method to compensate for transmission ratio change rotation, and by allowing the compensation for transition flexing by providing adjustments in the direction opposite of the direction the shaft on which the adjusters are mounted is rotating. 
   However other configurations for a CVT described in this patent have some merit as well. For example, for a configuration for a CVT  3 , which uses a cone assembly with two friction torque transmitting members  1046 F that is coupled by a friction belt  1067 F to a friction pulley  1098 F, there is no need for an adjuster to compensate for transition flexing and if some instances where the transmission ratio can not be changed is acceptable, than no adjusters are needed. If no adjusters are needed then no controlling computer, sensors, and source of electrical power are needed. 
   The most suitable configuration of a CVT for a given application depends mainly on the following requirements: torque transmission efficiency and rating, transmission ratio changing responsiveness, endurance, simplicity, weight, cost, and electrical power availability. For example, for an automobile, torque transmission efficiency and rating, transmission ratio changing responsiveness, and reliability is important. And since electrical power is readily available in an automobile, the configuration for CVT  2 . 4  as described in this section might be ideal here. If increased reliability is desired than torque sensors or other items described in this patent can be added to that CVT  2 . 4 . However this will increase the cost of the CVT. For a bicycle on the other hand torque transmission efficiency and rating, and transmission ratio changing responsiveness might not be so important. While weight and no need for an electrical power source is critical. Hence for a bicycle, the configuration for CVT  3  as described in this section might be ideal. 
   Operation 
   In order to design a CVT using the methods described in this patent, it is recommended that the designer first determine the unadjusted configuration of the CVT, which is the configuration of the CVT that does not use any adjusters. Next, if desired or required, the designer adds adjusters to the unadjusted configuration of the CVT based on the performance requirement of the CVT. 
   In order to determine the unadjusted configuration of the CVT, the designer first determines the desired qualities of the CVT the designer wants to build. From there the designer can construct a CVT using one or several cone assemblies  1026  or  1026 (A/B/C) according to the designer&#39;s need, by mounting one or several cone assemblies  1026  or  1026 (A/B/C) to a first shaft, or first group of shafts, and coupling them, directly or by the use of a rotational energy conveying device such as a transmission belt or chain, with one or several rotational energy conveying devices, including but not limited to pulleys, other cone assemblies, or sprockets, mounted on a second shaft, or second group of shafts, in a manner such that for all axial positions of the torque transmitting arc(s) at least a portion of a torque transmitting arc, formed by the torque transmitting surfaces of torque transmitting member(s)  46 , of at least one cone assembly  1026  or  1026 (A/B/C) mounted on the first shaft, or first group of shafts, is always coupled to a torque transmitting surface of a rotational energy conveying device mounted on the second shaft, or second group of shafts. Also, the designer needs to ensure that changing the axial position of the torque transmitting member(s) relative to their cone  1024  or cone  1024 A changes the transmission ratio of the CVT. 
   In addition, the designer also needs to ensure that for the CVT that the designer has designed, for every transmission ratio of the CVT, an instance exist where the transmission ratio can be changed without any significant circumferential sliding between the torque transmitting surfaces of the torque transmitting member(s)  46  and the torque transmitting surfaces(s) of the rotational energy conveying device(s) engaged with them. This can easily be done through experimentation. 
   Next, in order to be able to change the transmission ratio, the designer adds a mechanism controlled by an actuator or manually that can change the axial position of the torque transmitting member(s)  1046  and the rotational energy conveying device(s) directly or indirectly engaged to them relative to the surface of the cones  1024  or cones  1024 A when their axial positions can be changed without causing any significant circumferential sliding between the torque transmitting surfaces of the torque transmitting member(s) and the torque transmitting surfaces(s) of the rotational energy conveying device(s) engaged with them. If required or desired a computer can be used to control the actuator to perform the relative axial position change specified in the previous sentence as specified in the previous sentence. Otherwise stalling of the actuator or slippage at the actuator can be used to ensure that the relative axial position change specified in this paragraph is performed as specified. 
   Next the designer designates the input shaft of the CVT, which is the shaft that will be coupled to the driving source; and the output shaft of the CVT, which is the shaft that will be coupled to the member to be driven. The first shaft, or a shaft from the first group of shafts, can be selected as the input shaft; and the second shaft, or a shaft from the second group of shafts, can be selected as the output shaft. The input and output shafts can be reversed if necessary. 
   Once the unadjusted configuration of the CVT has been determined, one or several adjusters can be added to increase the performance of that CVT. The adjuster system described in this patent can also be used to improve the performance of other CVT&#39;s that are not described in this patent that also suffer from either or both transition flexing and a limited duration at which the transmission ratio can be changed. 
   In order to use an adjuster system described in this patent to improve the performance of a CVT that suffers from either or both transition flexing and a limited duration at which the transmission ratio can be changed, the designer uses one or several adjusters, which can adjust the rotational position of a torque transmitting device, such as a torque transmitting member of a cone assembly, a transmission pulley, a cone assembly, etc., relative to another torque transmitting device. The adjuster(s) should be mounted so that transition flexing can be eliminated and/or so that the duration at which the transmission ratio can be changed can be substantially increased. 
   In order to eliminate transition flexing, the amount of adjusters needed depend on the configuration of the CVT. One method of eliminating transition flexing is to adjust the rotational position of the alternating torque transmitting device(s) that causes transition flexing. Here an alternating torque transmitting device is a device that alternates between transmitting torque and not transmitting torque. For CVT  1 , the alternating torque transmitting devices are the torque transmitting members. And for CVT  2 , the alternating torque transmitting devices are the cone assemblies and the transmission pulleys, since they alternately transmit torque to/from a shaft from/to a transmission belt. Each alternating torque transmitting devices is coupled to a common torque transmitting device, which is a torque transmitting device that transmits torque to/receives torque from at least two alternating torque transmitting devices. For CVT  1 , the common torque transmitting devices are the transmission belt, the input shaft, and the output shaft. And for CVT  2 , the common torque transmitting devices are the input shaft and the output shaft. 
   Another method to eliminate transition flexing is to adjust the rotational position of the common torque transmitting devices. For example, for a CVT that comprises of a cone assembly with one torque transmitting member that is sandwiched by two gears, which are coupled to a common output shaft and alternately transmit torque from the torque transmitting member of the cone assembly, transition flexing can be eliminated by adjusting the rotational position of the cone assembly. The rotational position of the cone assembly should only be adjusted when the torque transmitting member of the cone assembly is only engaged with one gear. Also, for this configuration, the adjusting rotation at the cone assembly also affects the rotation of the gear with which it is engaged, unless there are instances where there is no torque being transmitted between the gears and the cone assembly. Hence, here it might be better to adjust the rotational position of a gear before it is coupled to the common output shaft. 
   When adjusters are used to adjust the rotational position of the alternating torque transmitting devices, then in most cases the following method can be used to determine how many adjuster are needed for a common torque transmitting device and how to mount them. When for a common torque transmitting device two alternating torque transmitting devices, which are coupled to each other, are used to transmit torque, then only one adjuster, which can be used on any of the alternating torque transmitting devices, is needed. 
   When more than two torque transmitting members are used, then the amount of adjusters needed depend on the configuration of the CVT. When for a rotational position two alternating torque transmitting devices can simultaneously be transmitting torque to/receiving torque from their common torque transmitting device, than one of those torque transmitting devices need to be mounted on an adjuster, so that its rotational position can be adjusted relative to the rotational position of the other alternating torque transmitting device. And when for a rotational position three alternating torque transmitting devices can simultaneously be transmitting torque to/receiving torque from their common torque transmitting device, than most likely two of those alternating torque transmitting devices need to be mounted on an adjuster, so that the rotational position of those two alternating torque transmitting devices can be adjusted relative to the rotational position of the non-adjuster mounted alternating torque transmitting device. So basically, if for a rotational position, n number of alternating torque transmitting devices can be simultaneously transmitting torque to/receiving torque from their common torque transmitting device, than most likely n−1 of those alternating torque transmitting devices need to be mounted on an adjuster. For all other rotational positions, the same rule applies. By determining all the different configurations of how the alternating torque transmitting devices can transmit torque to/receive torque from their common torque transmitting device and how many common torque transmitting devices are used, the amount of adjusters needed and how to mount them can be determined. Here for each common torque transmitting device, most likely the configuration obtained consist of groups of adjuster mounted alternating torque transmitting devices, preferably the same amount of adjuster mounted alternating torque transmitting devices in each group, that alternate with non-adjuster mounted torque transmitting devices to form a sequential and continuous torque transmitting means where at any instance only one non-adjuster mounted torque transmitting devices is transmitting torque. 
   Furthermore, in most cases the amount of adjusters needed determined from the method described in the previous paragraph can be reduced by coupling the alternating torque transmitting devices, which need to be mounted on adjusters but are never simultaneously engaged to a common torque transmitting device, to a common adjuster. The common adjuster can then be used to adjust the rotational position of the alternating torque transmitting device about to be engaged or engaged. Also here the common adjuster needs to be able to adjust the rotational position of the alternating torque transmitting device about to be engaged before it becomes engaged. For configuration where an instance exist where an alternating torque transmitting device coupled to a common adjuster is engaged while another alternating torque transmitting device coupled to the same common adjuster is about to come into engagement, the time available for the common adjuster to provide the adjustment can be very short so that an adjuster fast enough is needed. This time can be increased by using more adjusters, which can be common adjusters or otherwise. 
   And when adjusters are used to adjust the rotational position of the common torque transmitting device(s), then in most cases the rotational position of the common torque transmitting device(s) need to be adjustable. This can be achieved by using an adjuster for each common torque transmitting device. For certain configurations this can also be achieved by using one adjuster to adjust the rotational position of one or several common torque transmitting devices. A possible scenario for this method is having an adjuster adjust the rotational position of a shaft on which one or several common torque transmitting device(s) are mounted. In this case, in instances where the rotational position of a common torque transmitting device is being adjusted, it should not be engaged with any alternating torque transmitting device. Since here there might be instances where no torque is transmitted between a common torque transmitting devices and an alternating torque transmitting device, it is recommended to adjust the rotational position of the alternating torque transmitting device(s) instead. 
   Furthermore, adjusters can also be used to substantially increase the duration at which the transmission ratio of a CVT can be changed. One method to achieve this is to use an adjuster to mount each cone assembly to its shaft/spline. If the transmission ratio needs to be changed, these adjusters can then be used to rotate the cone assemblies relative to their shaft such that are maintained in a moveable configuration. This method is used for CVT  1 . 1  described earlier. 
   In a configuration of a CVT where a complete non-torque transmitting arc, which is the space of a cone assembly that is not covered by a torque transmitting member, is never completely covered by its coupled torque transmitting device, then the duration at which the transmission ratio can be changed can be substantially increased by compensating for transmission ratio change rotation. This method is used in CVT  2 . 1 . In order to compensate for transmission ratio change rotation, the rotation of the alternating torque transmitting device(s), for which changes in transmission ratio causes them to rotate differently than a referenced alternating torque transmitting device, need to be adjusted using adjuster(s). The adjustment should aim to eliminate any difference in rotation of the alternating torque transmitting devices due to change in transmission ratio. Or the rotation of the alternating torque transmitting devices engaged or coupled to the alternating torque transmitting devices mentioned in the previous sentence need to be adjusted in the same manner. 
   In order to determine the transmission ratio change rotation of an alternating torque transmitting device, first all other alternating torque transmitting devices should be removed from the CVT while the rest of the CVT should be left alone. Next the CVT should be placed in either its highest or lowest transmission ratio. Then the alternating torque transmitting device, for which its transmission ratio change rotation needs to be determined, should be positioned so that it can transmit torque at a recorded initial rotational position. Next the transmission ratio should be changed while the rotation of that alternating torque transmitting member as the transmission ratio is changed is recorded. The recorded results provide the amount of transmission ratio change rotation for that initial rotational position. Using the same method the amount of transmission ratio change rotation for different initial rotational positions can be determined. From the collected data an equation that estimates the amount of transmission ratio change rotation for different initial rotational positions and different initial and final transmission ratios can be constructed. Mathematics can also be used to obtain such equation. An example on how to obtain such equation mathematically can be found in the Adjuster System for CVT  2  section and the CVT  2 . 2  section of this patent. Based on those examples, it should not be difficult for someone with a mathematics background to obtain such equation for different configurations of CVT&#39;s. 
   When the transmission ratio change rotation of each alternating torque transmitting device is different, then the method to determine the amount of adjusters needed and the basic configuration on how to mount them is identical to the method used in the case where adjusters are used to adjust the rotational position of the alternating torque transmitting devices in eliminating transition flexing. 
   In order to properly control the adjusters to compensate for transmission ratio change rotation the following methods can be used. The first method is by controlling the adjusters so that the differences in torque being transmitted by the alternating torque transmitting devices that are transmitting torque are within a predetermined range. In that predetermined range, the difference in torque being transmitted by the torque transmitting devices due to transmission ratio change rotation can be compensated by flexing of the torque transmitting devices used to transmit torque. And when the differences in torque being transmitted exceed the predetermined range, stalling of the transmission ratio changing actuator should occur. If this method is used, then each alternating torque transmitting device need to have a device that measures the torque being transmitted by it, such as a torque sensor or load cell for example. Another method to compensate for transmission ratio change rotation is to determine the equations that estimates transmission ratio change rotation for each alternating torque transmitting device, and then control the adjusters based on those equations to compensate for the difference(s) in transmission ratio change rotation between the alternating torque transmitting devices. One method of adjustment is by having referenced alternating torque transmitting devices, which rotations are not adjusted, and adjusted alternating torque transmitting devices, which rotations are adjusted. The amount of adjustment rotation for an adjusted alternating torque transmitting devices is calculated by subtracting the amount of transmission ratio change rotation of that adjusted alternating torque transmitting device from the amount of transmission ratio change rotation of its referenced alternating torque transmitting device. Although not absolutely necessary, it is preferred that counter-clockwise rotations are considered positive and clockwise rotations are considered negative. Since the torque transmitting devices are rotating, the amount of adjustments required continuously change. Hence the value for the amount of adjustments needed should be updated at short enough intervals so that the amount of adjustments provided are accurate enough to prevent excessive stalling of transmission ratio changing actuator. An example on how to use this method is discussed in the explanation for CVT  2 . 2 . Furthermore, in case every alternating torque transmitting device is mounted on an adjuster, another method of adjustment is to cancel out transmission ratio change rotation for each alternating torque transmitting device by having the adjusters provide their alternating torque transmitting devices an equal amount of rotation as their transmission ratio change rotation but reversely directed. 
   Furthermore, as discussed in detail in the Adjuster System for CVT  2  section, for an adjuster, it is preferred that in order to compensate for transmission ratio change rotation, it only needs to provide rotation which direction is opposite from the rotation of the shaft on which its alternating torque transmitting device is mounted. Since this will lower the torque requirement of the adjuster, since it only needs to provide releasing rotation. This is can be achieved by using an adjuster on each alternating torque transmitting device. This method is described in the CVT  2 . 3  section and the CVT  2 . 4  section of this patent. And for a CVT that consist of a cone assembly with one torque transmitting member that is sandwiched by two gears, here each gear need to have an adjuster that can adjust its rotational position relative to the rotational position of its shaft, which is coupled to the shaft of the other gear. Besides using an adjuster on each alternating torque transmitting member, another method to having an adjuster compensate for transmission ratio change rotation by only providing a releasing torque can be achieved by using a differential between each alternating torque transmitting device and have an adjuster control the rotational position of one differential shaft relative to the other. Examples of this method are described in the Differential Adjuster Shaft for CVT  2  section of this application. And for a CVT that consist of a cone assembly with one torque transmitting member that is sandwiched by two gears, each gear needs to be coupled to a differential shaft of a differential, while the input/output shaft is coupled to the housing of the differential. 
   Once the proper configuration for the adjuster utilizing CVT has been determined, the designer needs to determine what kind of adjuster the designer wants to or can use. The most versatile adjuster is the electrical adjuster, which can be used to eliminate transition flexing, maintain a cone assembly in a moveable configuration, and compensate for transmission ratio change rotation in almost all applications. However, in order to properly control an electrical adjuster, the designer needs to use a computer and various sensors, such as transmission ratio sensors, rotational position sensors, relative rotational position sensors, torque sensors, etc. The methods of utilizing the sensors and the methods for controlling an electrical adjuster are described in detail in the previous sections of this application. 
   Another, less versatile, adjuster that might be useful for some CVT&#39;s is the mechanical adjuster. This adjuster can only be used to eliminate transition flexing. For the mechanical adjuster, it is not absolutely necessary, although it might be beneficial, to use a computer and various sensors in order to control it. Hence this adjuster might be preferred in machines where electrical power is not available, such as bikes for example. 
   Another adjuster that can be used, is the spring-loaded adjuster. This adjuster can be used to eliminate transition flexing and allow some relative rotation that slightly increase the moveable duration of a CVT. This adjuster is the simplest and most likely cheapest of the adjusters described in this patent. However, for this adjuster, shock loads occur when the pins of its gap mounted torque transmitting member hit a surface of the cone assembly that forms that gap. These shock loads might be negligible in low torque applications. But in high torque applications, unless properly damped, these shock loads can significantly decrease the live of the CVT and can cause undesirable driving conditions. However, damping these shock loads can also significantly reduce the efficiency of the CVT. 
   Based on the description in this patent, a machine designer can determine how to properly mount adjusters so that transition flexing can be eliminated and/or so that the duration at which the transmission ratio can be changed can be substantially increased in CVT&#39;s suffering from these problems. 
   CONCLUSION, RAMIFICATION, AND SCOPE 
   Accordingly the reader will see that the cone assemblies and adjuster systems of this application can be used to construct various Continuous Variable Transmissions (CVT&#39;s), which have the following advantages over existing Variable Transmissions:
         Compared to Discrete Variable Transmissions, they are able to provide a more efficient transmission ratio for a driving source under most circumstances due to their infinite transmission ratios over a predetermined range.   They can be constructed such that torque is transmitted by positive engagement devices, such as teeth. Hence they can provide torque transmission ability and efficiency almost as good as transmissions utilizing gears, sprocket and chains, and timing belts and timing pulleys, which have not yet been effectively used to construct CVT&#39;s. Gears, and sprocket and chains are currently almost used in any high torque transmission application due to their superior torque transmission ability and efficiency over any other torque transmission devices. Hence the CVT&#39;s constructed out of the cone assemblies of this application will most likely have higher torque transmission ability and efficiency than many CVT&#39;s of prior art.   They have less frictional energy losses than many CVT&#39;s of prior art, since significant circumferential sliding between the designated torque transmitting surfaces due to transmission ratio change can be eliminated.       

   Although the description above contains many specificities, these should not be construed as limiting the scope of the invention but as merely providing illustrations of some of the presently preferred embodiments of this invention. For example, by using a gear cone assembly, which is identical to a cone assembly  1026  described in the General Cone section, except for having a torque transmitting member with a square shaped cross-section instead of a channel shaped one, such that it can be coupled to a gear, one or several gear cone assemblies on a driver shaft can be coupled to one or several gears on one or several driven shafts and vice-versa. For example, if the arc length of the torque transmitting member at the largest end of its gear cone assembly is not less than half of the circumference of that gear cone assembly, than a CVT can be constructed where two gears, which are attached so that they can engage with the teeth of the torque transmitting member, are positioned as to sandwich that gear cone assembly. Also a CVT, which consist of several gear cone assemblies, which engage directly with each other can also be designed. 
   Also the designs in this patent are only exemplification on how to utilize the invention. Many other designs utilizing this invention, such as designs that use other types/designs of pulleys, sprockets, belts, chains, teeth, or any other part of this invention can be conceived. 
   Also, although in this patent only cones or cone assemblies with one or two oppositely positioned torque transmitting devices are shown. Cones or cone assemblies with more than one or two torque transmitting devices can also be used as long as for the CVT where they are used, an instance exist where only one torque transmitting device is engaged with it means for coupling. For example, a CVT  3  using a cone or cone assembly with three teeth, evenly spaced on its cone or cone assembly, can be constructed as long an instance where only tooth is engaged with its chain or belt exist. Or a CVT  2  with three single tooth cones or three cone assemblies with one tooth that are mounted on a shaft in a manner such that the teeth are 120 degrees from each other can also be constructed as long an instance where only one tooth is engaged with its chain or belt exist. Obviously more teeth can be used as long as an instance where only one tooth is engaged with its chain or belt exists. In the same manner a CVT  3  using a cone assembly with three torque transmitting members or a CVT  2  using three cone assemblies, each with a torque transmitting member, can be constructed. 
   Given the time and need, detailed designs for the configurations mentioned, as well as many other configurations could be conceived. 
   Furthermore, besides improving the performance of CVT&#39;s utilizing the cones and cone assemblies described in this patent, the adjuster systems described in this patent can also be used to improve the performance of other CVT&#39;s that suffer from either or both transition flexing and/or a limited duration at which the transmission ratio can be changed. First of all, they can eliminate or significantly reduce transition flexing. Excessive cycles of transition flexing can reduce the life of a CVT. Furthermore, the adjuster systems of this invention can also be used so that the duration at which the transmission ratio can be changed can be substantially increased so as to improve the transmission ratio changing responsiveness of a CVT. In addition, the adjuster systems of this invention can also improve the engagement between a means for transmitting torque, such as a pulley, sprocket, or gear for example, and another a means for transmitting torque, such as a belt, chain, or another gear for example, by compensating for tooth wear for example. 
   Accordingly, the scope of the invention should be determined not by the embodiments illustrated, but by the appended claims and their legal equivalents.