MXPA00003788A - Continuously variable transmission - Google Patents

Abstract

A continuously variable transmission (100) having a plurality of rotatable power adjusters (122) for transmitting power from a driving member (120) to a driven member (170). Each power adjuster (122) is frictionally interposed between the driving member (120), the driven member (170), and a rotatable support (154), so that the power adjusters (122) each make three point fractional contact against the driving member (120), the driven member (170), and the support member (154). The transmission ratio is determined by a pivot support (134) which varies the axis upon which each power adjuster rotates.

Description

CONTINUOUSLY VARIABLE TRANSMISSION BACKGROUND OF THE INVENTION Field of the Invention The field of the invention relates to transmissions. More particularly, the invention relates to continuously variable transmissions. Description of the Related Technology In order to provide an infinitely variable transmission, several traction roller transmissions have been developed in which the power is transmitted through the traction rollers supported in a casing between the torsion input and the traction rollers. output discs. In these transmissions, the traction rollers are mounted on support structures which, when mounted on pivots, cause the engagement of the traction rollers with the torsion discs in circles of various diameters depending on the desired transmission ratio. However, the success of these traditional solutions has been limited. . For example, in U.S. Patent No. 5,236,403 to Schievelbusch, an impeller hub for a vehicle with a variable adjustable transmission ratio is disclosed. Schievelbusch teaches that the use of two iris plates, one on each side of the traction rollers, tilt the axis of rotation of each of the rollers. However, the use of iris plates can be very complicated due to the large number of parts that are required to adjust the iris plates during the change of the "transmission." Another limitation of this design is that it requires the use of two half shafts , one on each side of the rollers, to provide a gap in the middle of the two half axes.The gap is necessary because the rollers are changed with rotary motion instead of sliding linear movement.The use of two axes and it requires a complex clamping system to prevent the axes from bending when the transmission is accidentally hit, as is often the case when using a transmission in a vehicle.Although another limitation of this design is that it is not provided for a transmission Therefore, there is a need for a continuously variable transmission to have a simpler and single-axis shifting method. Automatic traction roller drive that is configured to make changes automatically. Additionally, the practical commercialization of traction roller transmissions requires improvements in reliability, ease of making changes, function and simplicity of transmission. SUMMARY OF THE INVENTION The present invention includes a transmission for use in linear or rotary driven machines or vehicles. For example, the present transmission can be used in vehicles such as automobiles, motorcycles and bicycles. The transmission can, for example, be driven through a power transfer mechanism such as a gear wheel, a gear, a pulley or a lever by optionally driving a one-way clutch fixed to one end of the main shaft. One of the embodiments of the invention includes a transmission comprising a shaft, a rotatable driving member rotatably mounted on the shaft, a rotatable driving member rotatably mounted on the shaft, a plurality of power adjusting devices interposed with friction between the driving member rotatable and the rotatable driven member and adapted to transmit power from the driving member to the driven member, and to the pivotable support member located concentrically on the shaft and between the shaft and the power adjusting devices, and frictionally engaged the plurality of the power adjusting devices, such that each of the power adjusting devices makes frictional contact at three points against the driving member, the driven member and the support member. Still another version of the invention includes a shaft, a rotatable driving member rotatably mounted to the shaft, a rotatable driving member rotatably mounted to the shaft, a plurality of power adjusting devices interposed with friction between the rotatable driving member and the driven member rotatable and adapted to transmit power between the driving member to the driven member, wherein a driving member is rotatable. rotatable support located concentrically on the shaft and between the shaft and the power adjusting devices, and frictionally engaged to a plurality of power adjustment devices, such that each of the power adjustment devices make three points of frictional contact against the thrust member, the driven member and the support member, and at least one outwardly extending weight coupled to the plurality of power adjusting devices and rotatably fixed to the shaft, where at least one of the weights is adapted to drive a change in an axis of rotation of the plurality of power adjustment devices. BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a partial perspective view of the transmission of the present invention. Figure 2 is a partial exploded view of the transmission of Figure 1. Figure 3 is a cut away elevated view of the end of the transmission of Figure 1. Figure 4 is a cutaway side elevational view of the transmission of the Figure 1. Figures 5 and 6 are side elevational views cut away from the transmission of Figure 1 illustrating the transmission of Figure 1 changed to different positions. Figure 7 is a cut-away view of the end of an alternative embodiment of the transmission of the invention where the transmission makes the changes automatically. Figure 8 is a side elevational view of a transmission of Figure 7. Figure 9 is a cut-away view of the end of an alternative embodiment of the transmission of the invention where the transmission includes a fixed hub. Figure 10 is a cutaway side elevational view of the transmission of Figure 9. Figure 11 is a cutaway side elevational view of an alternate embodiment of the transmission of Figure 1, where the transmission has two thrust bearings. Figure 12 is a cut-away side elevational view of one of the alternative embodiments of the invention where a one-way rotary impeller and a second one-way rotatable impeller provide an input torque to the transmission. Figure 13 is an elevated view of the schematic cut-away end of another alternative embodiment of the transmission of the invention. Figure 14 is a schematic cropped front raised view of the transmission of Figure 13. Figure 12 is a schematic end view of a housing for the transmission of Figures 13 and 14. Figure 16 is a schematic cropped front elevational view. of another alternative embodiment of the transmission of the invention. Figure 17 is a side elevational view of an alternative embodiment of a support member. Figure 18 is a side elevational view of an alternative embodiment of a support member. Figure 19 is a side elevational view of an alternative embodiment of a support member. Fig. 20 is a schematic cropped side elevational view of an alternative embodiment of the invention including: a thrust bearing, a pulley and a tension member. Figure 21 is a schematic cut-away side elevational view of an alternative embodiment of the invention where the support member has at each end a thrust bearing, a sheave and the pivot supports have legs. Figure 22 is a front elevational view of a transmission pulley of Figure 21. Figure 23 3s a side elevational view of a pivot support of the transmission of Figure 21. Figure 24 is a bottom floor view. of a pivot support of the transmission of Figure 21. Figure 25 is a front elevational view of an alternative embodiment of a fixed support. Figure 25 is a cutaway side elevational view of the fixed support of Figure 25. Figure 27 is a front elevational view of an alternative embodiment of a stationary support. Figure 28 is a cutaway side elevational view of the stationary support of Figure 27. Figure 29 is a partial top plan view of the fixed support of Figure 27. Figure 30 is a front elevational view of an alternate embodiment of a fixed support. Figure 31 is a cutaway side elevational view of the fixed support of Figure 20. Figure 32 is a cut-away side elevational view of an alternate embodiment of the main shaft of Figure 2. Figure 33 is a cut away elevated end view. of the shaft of Figure 32. Figure 34 is a schematic cropped front raised view of an alternative embodiment of the transmission of the invention. Figure 35 is a schematic cut-away side elevational view of an alternative embodiment of the transmission that automatically changes. Figure 36 is an elevational view of the schematic cut-away end of the annular bearing shown in Figure 35. Figure 37 is a schematic cut-away side elevational view of an alternative embodiment of the invention having a gravity bearing mechanism. Figure 38 is a front elevated view of the rolling mechanism by. alternative gravity of Figure 37. Detailed Description of the Invention The following detailed description is directed to certain specific embodiments of the invention. Nevertheless, the invention can be encompassed in a multitude of different ways as defined and covered by the claims. In this description, reference is made to the drawings where the equal parts are designated with equal numbers completely. The present invention includes a continuously variable transmission that can be used in connection with any type of machine that needs a transmission. For example, the transmission may be used in (i) a motorized vehicle such as a car, a motorcycle, a watercraft, (ii) non-motorized equipment such as a bicycle, a tricycle, a skateboard, exercise equipment, or (iii) equipment industrial power, such as a drilling dam or a power generating equipment such as a mill.

Figures 1 to 4 reveal one of the embodiments of the present invention. Figure 1 is a partial perspective view of a transmission 100. Figure 2 is an exploded view of the transmission 100 of Figure 1. Figure 3 shows a partial cross-sectional end view of the transmission 100 of the Figure 1. Figure 3 shows a partial cross-sectional end view of the transmission 100. Figure 4 shows a cutaway side elevational view of the transmission 100. Generally with reference to Figures 1 to 4, a hollow main shaft 102 is fixed to a structure of a machine (not shown). The shaft 102 may be threaded at each end to allow a fastener (not shown to secure the transmission 100 on the main shaft 102 and / or to secure the main shaft 102 to the machine.) A rotatable impeller 401 ( Figure 4) comprising a sprocket or a pulley that is rotatably fixed to the main shaft 102, such that an input torque is provided to the transmission 100. A pulse jacket 104 coupled coaxially to the rotatable impeller (Figure 4) and rotatably disposed about the main shaft 102. A surface 106 (FIG. 2) of the impulse sleeve 104, opposite the rotatable pusher 401 (FIG. 4), may include a plurality of shallow grooves 108. A first assembly of the roller holder ring 110 has a plurality of cylindrical rollers 112 arranged radially about a mid-point of the roller ring assembly 110. Each of the cylindrical rollers 112 is rotatably mounted in the first row. The roller ring 110 is assembled in such a way that each of the rollers can rotate about the length of its axis. Preferably, there is a one-to-one correlation between each of the shallow grooves 108 of each of the cylindrical rollers 112. Optionally, the cylindrical rollers 112 can be replaced with rollers of an alternative geometric shape, such as with spherical rollers. A tension inductor 118 (Figure 2), like a spring, is rotatably disposed on the main shaft 102 and frictionally coaxially coupled to the first roller ring assembly 110 opposite the pulse sleeve 104. In addition, a rotatable driver member 120 is fixed to the main shaft 102 and coaxially coupled to the side of the first roller ring 110 opposite the pulse sleeve 104. A surface 107 (Figure 4) of the rotatable driving member 120 opposite the pulse sleeve 104 includes a plurality of shallow grooves 109 (Figure 4). The relative rotation of the roller ring 110 with respect to the pulse sleeve 104 causes the cylindrical rollers 112 to roll over the shallow grooves 108, 109 and move the shallow grooves 109, 109 towards each other and away from each other along the main shaft axis 102. A plurality of spherical power adjusting devices 122A, 122B, 122C, are in frictional contact with one side of the rotatable driving member 120 opposite to the assembly of roller ring 110. In one embodiment of the invention , the power adjustment devices 122A, 122B, 122C, are spheres made of hardened steel; however, the power adjustment devices 122A, 122B, 122C may alternatively include other shapes and be fabricated from other materi A plurality of rods 130A, 130B, 130C (Figure 2) extend respectively through multiple passages 128A, 128B, 128C (Figure 2) in the power adjustment devices 122A, 122B, 122C. The radial bearings (not shown) can be arranged on each of the rods 130A, 130B, 130C (Figure 2) to facilitate rotation of the power adjustment devices 122A, 122B, 122C. A plurality of pivot supports 134A, 134B, 134C (Figure 2) respectively hold the rods 130A, 130B, 130C (Figure 2). The support 134A includes two legs 135A and 137B for connection to a ratio change 166 which will be discussed in greater detail below. In a similar way, the support 134B includes two legs 135B and 137B, and the pivot support 134C includes two legs 135C and 137C. Pivot brackets 134A, 134B 134C respectively include pivot rings 136A, 136B, 136C. The pivot ring 136A has four openings 138A, 140A, 142A, 144A, (Figure 2). Similarly, the pivot support 134B has four openings 138B, 140B, 142B and 144B, and the pivot support 134C has four openings 138C, 140C, 142C and 144C (Figure 2). The openings 138A, 138B, 138C are located respectively opposite the openings 140A, 140B, 140C on the pivot rings 136A, 136B, and 136C. Together, the openings 138A, 138B, 138C, and the openings 140A, 140B, 140C are respectively configured to receive the rods 130A, 130B, 130C (Figure 2). The openings 142A, 142B, 142C (Figure 2) are respectively located opposite the openings 144A, 144B, 144C (Figure 2) in the pivot rings 136A, 136B, 136C. Together, openings 142A, 142B, 142C and openings 144A, 144B, 144C are configured to receive multiple immobilizers 150A, 150B, 150C (Figure 2). In one embodiment of the invention, the immobilizers 150A, 150B, 150C are each rigid cylindrical rods, slightly angled at the end. A central portion of each of the immobilizers 150A, 150B, 150C is fixed to one of the multiple legs 153 (Figure 2) of a fixed support 152 (Figure 2). The fixed support 152 is fixedly attached to the main shaft 102. A support member 154 is slidably and rotatably disposed on the main shaft 102 proximate a side of the fixed support 152 (Figure 2) which is opposite the rotatable driving member 120. The member of support 154 is in frictional contact with each of the power adjustment devices 122A, 122B, 122C. In one embodiment of the invention, the support member 154 is a cylindrical ring having a substantial uniform outer circumference from the cross-sectional view of the end. In another embodiment of the invention, the support member 154 is a cylindrical ring having a first flange and a second flange (not shown) extending radially outward from the first end and the second end of the support member 154. in such a way that the power adjusting devices 122A, 122B, 122C are prevented from disengaging from the support member 154. In still another embodiment of the invention, the support member 154 is a cylindrical ring having a concave outer surface nominally (Figure 17). The support member 154 may contact and rotate about the main shaft 102, or may be suspended on the main shaft 102 without contacting it substantially due to the centering pressures applied to the power adjusting devices 122A, 122B, 122C . Referring in particular to Figure 2, a shift member -160, like a non-flexible rod, is slidably engaged to an interior passage of the main shaft 102. Two extensions 162, 164 extend perpendicularly from the member making changes 160 to through an opening 165 in the main shaft 102. A first end 161 of the shift member 160 proximate to the drive side of the transmission 100 is connected to a linkage 163, such as a cable. The linkage 163 is connected at an opposite end of the main shaft 102 to a shift actuator (not shown). A tension member 202, like a spring, is connected to a second end of the shift member 160 through a fastener 204. Still with reference in particular to Figure 2, the extensions 162, 164 are connected to the ratio changer 166. The ratio changer 166 includes a flat platform 168 and a plurality of legs 171A, 171B, 171C extending perpendicularly from a surface of the platform 168 proximate the support member 154. The leg 171A includes two linkage pins 172A, 173A. Similarly, leg 171B includes two linkage pins 172B and 173B, and leg 171C includes two linkage pins 172C and 173C. The linkage bolts 172A, 172B, 172C, and the linkage pins 173A, 173B, 173C are used to couple the ratio changer 166 to each of the pivot supports 134A, 134B and 134C. With reference to the coupling of the support 134A and the ratio changer 166, the linkage pin 172A engages one end of the leg 137A of the support 134A opposite the pivot ring 136A, and the linkage pin 172B engages one end of the opposite 135A to the pivot ring 136A. Further in relation to the engagement between the pivot bracket 134B and the ratio changer 166, the link bolt 173B engages one end of the leg 137B opposite the pivot ring 136B and the linkage pin 172C engages one end of the opposite leg 135B to the pivot ring 136. Finally, with respect to the coupling between the pivot bracket 134C and the ratio changer 166, the link bolt 173C engages one end of the leg 137C opposite the pivot ring 136C and the linkage pin. 173C engages one end of the leg 137B opposite the pivot ring 136C. Although only three power adjusting devices 122A, 122B, 122C are disclosed, the transmission 100 of the invention can be configured with less (for example 2) or with more (for example 4, 5, 6 or more) power adjustment devices . In addition, the number of legs in the ratio changer 166, the number of legs in the fixed support 152, the number of immobilizers, the number of pivot supports in the transmission can be adjusted accordingly according to the number of adjustment devices of power that are used. Referring again in general to Figures 1-4, a rotatable driven member 170 is rotatably engaged with the main shaft 102 proximate to the ratio changer 166 (Figure 2). The rotatable driven member 170 is in frictional contact with each of the power adjusting devices 122A, 122B, 122C. A surface 174 of a rotatable driven member 170 opposite the power adjusting devices 122A, 122B, 122C, includes a plurality of shallow grooves 176. The driven member 170 is in frictional coaxial contact with a second tension inductor 178 ( Figure 2), like a spring, and a second roller ring assembly 180 which is similar in design to the roller ring assembly 110. The second tension inductor 178 (Figure 2) and the second roller ring assembly 180 are rotatably disposed on the main shaft 102. A hub driver 186 (Figure 4) is rotatably disposed on the main shaft 102 and coaxially engaged to one side of the second roller ring assembly 180 opposite the rotatable driven member 170. The hub driver 186 (Figure 4) ) can be attached to a bucket hull 302 (Figures 3 and 4) using any traditional gear mechanism. In one embodiment of the invention, the hub driver 186 extends proximal to the hub hull 302 and s-e connects to the one-way rotary impeller 300, such as the one-way roller clutch. The one-way rotary impeller 300 (Figures 3 and 4) is rotatably coupled to hub hub 302 (Figures 3 and 4). Note that the power adjusting devices 122A, 122B, 122C are suspended at three frictionally adjusted contact points with the drive member 120, the support member 154, and the driven member 170. The hub helmet 302 (FIGS. and 4) has a plurality of holes 304 (Figure 3) that provide an element for attaching hub hub 302 to the wheel, propeller or other propulsion element. The hub hull 302 is supported and is free to rotate on the main shaft 102 through hub bearing members 410 (Figure 4) which fits within the slots in the hub driver 186. A sheave 412 (Figure 4 ) is attached to the main shaft 102 near one side of the hub driver 186 opposite the second roller ring assembly 180 to facilitate rotation of the hub bearing 410 (Figure 4). Figures 5 and 6 are side elevational views cut away from the transmission of Figure q illustrating the transmission of Figure 1 in two different gear positions. With reference to Figures 5 and 6, a method of changes in the transmission 100 is then revealed. Before an input force, the impulse sleeve 104 starts to rotate in the clockwise direction. (It should be noted that the transmission 100 is also designed to be driven in the counterclockwise direction). At the start of the rotation of the pulse sleeve 104, the nominal axial pressure is supplied through the voltage inductors 118, 178 (FIG. 2) to ensure that the rotatable driving member 120, the rotatable driven member 170, and the member of support 154 are in tensile contact with power adjusting devices 122A, 122B, 122C. The rotation of the pulse sleeve 104 in a clockwise direction engages the first assembly of the roller ring 110 to rotate in a similar direction. At low torsion, the rollers 112 remain centered between the shallow grooves 108, 109 of the rotatable driving member 120 and the driving sleeve 104. While additional twisting is applied, the rollers 112 climb the sloping sides of the grooves 108. and forces the impulse sleeve 104 and the rotatable driving member 120 to move farther apart. The same action occurs at an opposite end of the transmission 100 where the rotatable driven member 170 engages the hub driver 186 through the second roller ring assembly 180. It is thus, the first ring assembly of the roller holder 110 and the second roller ring assembly 180 compresses rotatable driving member 120 and rotatable driven member 170 together against power adjusting devices 122A, 122B, 122C, which increase frictional contact of power adjusting devices 122A, 122B, 122C against the support member 154, the impulse member 120 and the driven member 170. Since the first rotatable impeller member 120 rotates clockwise through the roller ring assembly 110, the first rotatable driver member 120 rotates the power adjusting devices 122A 122B, 122C with friction. The clockwise rotation of the power adjusting devices 122A, 122B, 122C causes a clockwise rotation of a rotatable driven member 170. Rotation clockwise of the driven member The handle 170 engages the roller ring assembly 180 to rotate clockwise, whereas the clockwise rotation of the second roller ring 180 engages the hub driver 186 (Figure 4). to rotate clockwise The clockwise rotation of the bucket driver 186 causes a one-way rotary impeller 300 to rotate clockwise The one-way rotary impeller 300 then drives the hub 302 (Figures 3 and 4) to rotate clockwise The shift member 160 is used to modify the axis of a ro tion by the power adjustment devices 122A, 122B, 122C. To change the transmission 100, the shift actuator (not shown) slides the shift member 160 in a first direction 500 (FIG. 5). A release in the tension of the linkage 163 by the shift actuator (not shown) causes the shift member 160 to slide in a second and opposite direction 600 (Figure 6) through the tension member 202. The particular construction of the present invention 100 provides the facility to make the changes that the design of traction rollers of the previous technology. When the shift member 160 is moved in any of the directions by a user, the extensions 162, 164 engage the ratio changer 166 to move axially through the main shaft 102. With reference to Figure 5, when the member changes 160 moves, the ratio changer 166 pivots the supports 134A, 134B 134C. The pivoting movement of the supports 134A, 134B, 134C, inclines the ball rods 130A, 130B, 130C and changes the axis of rotation of each of the power adjustment devices 122A, 122B, and 122C. When the shift member 160 moves in the direction 500, the axis of rotation of each of the power adjusting devices 122A, 122B, 122C is modified so that the rotatable driving member 120 contacts a surface of the driving device. power setting, 120A, 120B, 120C closest to the rotation axis of the power devices 120A, 120B, 120C. In addition, the rotatable driven member 170 contacts the power adjustment device at a point on a surface of each of the power adjusting devices 120A, 120B, 120C, furthest from the axis of rotation of the adjustment devices of power 120A, 120B, 120C. The adjustment of the rotation axis of the power adjusting devices increases an angular output speed of the transmission 100 due to each revolution of the rotatable driving member 120, the rotatable driven member 170 rotates more than once. With reference to Figure 6, the transmission 100 of the invention is shown in a position causing a decrease in the output angular velocity for transmission 100. While the shift member 160 is directed in direction 600, opposite the first direction 500, the rotation axis of each of the power adjusting devices 122A, 122B, 122C is modified in such a way that the rotatable driven member 170 makes contact with a surface of each of the power adjusting devices 122A, 122B, 122C closest to the axis of rotation of each of the power adjustment devices 122A, 122B, 122C. In addition, the rotatable driving member 120 makes contact with each of the power adjustment devices 122A, 122B, 122C at a point on a surface of each of the power adjustment devices 122A, 122B, 122C, furthest from the axis of rotation of each of the power adjustment devices 122A, 122B, 122C. The adjustment of the rotation axis of the power adjusting devices 122A, 122B, 122C decreases the angular output speed for the transmission 100 because for each revolution of the rotatable driving member 120m the rotatable driven member 170 rotates less than once. Figures 7 and 8 illustrate an automatic transmission 700 of the present invention. For purposes of simplicity of description, only the differences between the transmission 100 of Figures 1-6 and the automatic transmission 700 are described. Figure 7 is an elevated view of the partial end of the transmission 700, and Figure 8 is a partial side elevational view of transmission 700. A plurality of tension members 702A, 702B, 702C, which can each be a spring, interconnect each of the pivot rings 136A, 136B, 136C. The tension member 702A is connected to the first end of the pivot ring 136A and to the second opposite end of the first end to the pivot ring 136B. In addition, the tension member 702B is connected to the first end of the pivot ring 136B near the opening 138B and the second opposite end of the first end of the pivot ring 136C near the opening 138C. In addition, the tension member 702C is connected to the first end of the pivot ring 136C near the opening 138C and the second opposite end of the first end towards the pivot ring 136 near the opening 138A. The transmission 700 also includes flexible extension members 708A, 708B, 708C respectively connected to the first end towards the pivot rings 136A, 136B, 136C. The transmission 700 also includes a first annular bearing 806 a second annular bearing 816 to assist in the changes of the transmission 700. The first annular bearing 806 is slidably connected to the hub helmet 302 so that the annular bearing 806 can also be directed towards the pivotable driving member 120 or rotatable driven member 170. The second annular bearing 816 is also configured to slide to either of the rotatable driving members 120 or the rotatable driven member 170, however, the second ring bearing 816 is not rotatable about the shaft 102, as opposed to the first annular bearing 806. The first annular bearing 806 and the second annular bearing 816 supports the multiple bearing pellets 808. A second end of each of the extension members 708A, 708B, 708C connects the second ring bearing (Figure 8). The members of multiple extension 718A, 719B, 718C respectively connect the first annular bearing 806 to the multiple weights 720A, 720B, 720C. Optionally, a plurality of pulleys 822 may be used to direct the extension members 718A, 718B, 718C of the first annular bearing 806 toward the weights 720A, 720B, 720C, and direct the extension members 708A, 708B, 708C toward the second annular bearing 816. Even with reference to Figures 7 and 8, an operation method for the transmission 700 is disclosed. Similar to the embodiment of the invention disclosed in Figure 1, a torsion input in the clockwise direction causes a clockwise rotation of the impulse sleeve 104, of the first roller ring assembly 110, and a rotatable driving member 120. The rotatable driving member 120 engages the power adjusting devices 122A, 122B, 122C to rotate , and therefore driving the rotatable driven member 170. The rotation of the rotatable driving member 170 drives the second roller ring assembly 180 and produces an output twist. However, to distinguish itself from the transmission 100 illustrated in Figure 1, the rotational relationship between the rotatable driving member 120 and the rotatable driven member 170 is automatically adjusted through a centrifugal movement out of the weights 720A, 720B, 720C . While the weights 720A, 720B, 720C extend outwards, the extensions 718A, 718B, 718C pull the first annular bearing 806 towards the rotatable driving member 120. The movement of the first annular bearing 806 towards the rotatable driving member 120 similarly causes the movement of the bearings 808 and the second annular bearing 816 towards the rotatable driving member 120. The movement of the first annular bearing 806 towards the rotating driving member 120 causes the extension members 708A, 708B 708C to pivot the pivot rings respectively 306A, 306B, 306C and adjust the axis of rotation of each of the power adjustment devices 122A, 122B, 122C. After adjustment, the rotatable driven member 170 contacts a surface of the power adjustment devices 122A, 122B, 122C. Conversely, the rotatable driving member 120 contacts the power adjusting devices 122A, 122B, 122C at a point on the surface of each of the power adjustment devices 122A, 122B, 122C away from the axis of rotation of the devices of power adjustment 122A, 122B, 122C. The adjustment of the rotation axis for the power adjusting devices 122A, 122B, 122C decreases an angular output speed for the transmission 100 due to each revolution of the rotatable driving member 120, the rotatable driven member rotates less than once. When the hub shell 302 rotates more slowly, the compression members 702A, 702B, 702C adjust the axis of rotation of the power adjusting devices 122A, 122B, 122C to provide a lower angular output speed compared to the angular velocity of entry. Figures 9 and 10 illustrate an alternative embodiment of the invention. For purposes of simplicity of the description, only the differences between the transmission 100 of Figure 1 and a transmission 900 of Figures 9 and 10 are described. Figure 9 is an elevated view of the partial end of the transmission 900, Figure 10 is a partial side elevational view of the transmission 900. The transmission 900 includes flexible extension members 908A, 908B, 908C respectively connected to the first end of the pivot rings 136a, 136B, 126C. A second end of the extension members 908A, 908B, 908C is connected to a synchronization member 912. In addition each of the extension members 908A, 908B, 908C are slidably engaged to a plurality of pulleys 916 (Figure 9) that are attached to bucket hull 302. It is noted that the number and location of each of the pulleys 916 (Figure 9) can be varied. For example, a different pulley configuration can be used to direct the extension members 908A, 908B, 908C depending on the selected structure of the machine or vehicle employing the transmission 900. Additionally, pulleys 916 and extension members 908A , 908B, 908C may be located within the hub hull 302. The hub hull 302 of the transmission 900 is not rotatable. In addition, the hub hull 302 includes a plurality of openings (not shown) which are used to guide the extension members 908A, 908B, 908C to the synchronization member 912. It should be noted, that according to the embodiment of the invention illustrated in Figures 9 and 10, the gear shift assembly 100 of Figure 2 can be eliminated, including the main shaft 1092 (Figure 2), the tension member 202 (Figure 2) the extensions 162, 164 (Figure 2) and the shift actuator (not shown). Even with reference to Figures 9 and 10, a method of operation for the transmission 900 is disclosed. Similar to the embodiment of the invention disclosed in Figure 1, an input twist causes a clockwise rotation. of the impulse sleeve 104, the first roller ring assembly 110, and the rotatable driving member 120. The rotatable driving member 120 engages the power adjusting devices 122A, 122B, 122 to rotate, and thereby urge the driven member. rotatable 170. The rotation of the rotatable driven member 170 drives the roller ring assembly 180 and produces an output twist. In the transmission 900, the rotational relationship between the rotatable driving member 120 and the rotatable driven member 170 is adjusted through the manipulation of the synchronizing member 912. Since the synchronizing member 912 is directed out of the hub helmet 302 , the extension members 908A, 908B, 908C respectively pivotally pivot the pivot rings 136A, 136B, 136C such that the axis of rotation of each of the power adjusting devices 122A, 122B, 122C moves with pivoting similarly. The axis of rotation of each of the power adjusting devices 122A, 122B, 122C is modified in such a way that the rotatable driving member 120 makes contact with a surface of the power adjustment devices 122A, 122B, 122C remote from the axis of rotation of each of the power adjustment devices 122A, 122B, 122C. Conversely, the driven member 170 contacts the power adjusting devices 122A, 122B, 122C at a point on the surface of each of the power adjusting devices 122A, 122B,? 122C closest to the axis of rotation of each of the power adjustment devices 122A, 122B, 122C. The adjustment of the rotation axis for the power adjusting devices 122A, 122B, 122C decreases an angular output speed for the transmission 100 because at each of the revolutions of the rotatable driving member 120, the rotatable driven member 170 rotates less of one. time. When the synchronization member 912 is directed towards the hub helmet "302, the tension members 702A, 702B, 702C are compressed, This compression causes one end of the pivot rings 136A, 136B, 136C near the rotatable driven member 170 move with pivoting towards the main shaft 102. The pivotal movement of the pivot rings 136a, 136b, 136C causes the axis of rotation of each of the power adjustment devices 122A, 122B, 122C to be modified in such a way that the rotatable driven member 170 rotates more slowly than the rotatable driving member 120. Figure 11 illustrates another alternative embodiment of the invention, including a transmission 1100 having a first thrust bearing 1106 and a second thrust bearing 1108. The first thrust bearing 1106 is rotatably disposed on the main shaft 102 and is positioned between the support member 154 and the extensions 162, 164. The second thrust bearing 1108 is arranged on the main shaft 103 on one side of the support member 154 opposite the first thrust bearing 1106. The transmission 1100 may also optionally include a second ratio changer as a ratio changer 1110, which is disposed on the main shaft 1023 and It is axially slidable. When the ratio changers 166, 1110 slide axially to cause a change in the transmission 1100, the ratio changers 166, 1110 also slide the thrust bearings 1106, 1108. The sliding of the thrust bearings 1106, 1108 forces the member of support 154 so that it slides in unison with the ratio changers 166, 1110. A small amount of play is provided between the support member 154 and the thrust bearing 1106, 1008, so that the thrust bearings 1106, 1108 do not make contact with the support member 154 except when the transmission 1100 is in the process of making changes. Figure 12 illustrates an alternative embodiment of the invention. Figure 12 illustrates a transmission 1200 that operates similarly to the embodiment of the invention disclosed in Figure 10.; however, the transmission 1200 of Figure 12 includes two rotatable impellers 1204, 1206 and a rotatable driving shaft 1211. The rotatable driving shaft 1212 is fixedly attached to the driving sleeve 104. Even with reference to Figure 12; the first rotatable impeller 1204 includes a one-way clutch 1208 which is configured to rotate the rotatable driving shaft 1212 before rotation of the clutch 1210. The second rotatable impeller 1206 is configured to engage the impulse sleeve 104 before rotation the second rotatable impeller 1206 in a second direction, which is opposite to the direction of activation of the first rotatable impeller 1204. The second rotatable impeller 1206 is fixedly attached to the impulse sleeve 104. Figure 13 schematically illustrates another alternative embodiment of the present invention that has a 1300 transmission that is configured to make changes automatically. Three pulleys 1306, 1308, 1310 are respectively connected to the pivot rings 136a, 136B, 136C. A cable 1312 is guided around the pulley 1306 and connects a first end of the main shaft 102 and connects a second end to an annular ring (not shown), similar to the annular ring 816 of Figure 8. Similarly, a cable 1314 it is guided around the pulley 1308 and connected to the main shaft 102 at the first end and connected to a second end of the annular ring (not shown). Finally, a cable 1316 is guided around the pulley 1310 and a first end is connected to the main shaft 102 and connected at a second end of the annular ring (not shown). Figure 14 schematically illustrates the transmission 1300 of Figure 13 from one end of the front. A plurality of tension members 1404, 1406, 1408 interconnect each of the pivot rings 136A, 136B, 136C. The tension member 1404 is connected at a first end to the pivot ring 136A and is connected to a second opposite end of the first end to the pivot ring 136B. The tension member 1406 is connected at a first end to the pivot ring 136B and is connected at a second opposite end of the first end to the pivot ring 136C. The tension member 1408 is connected at a first end to the pivot ring 136A and is connected at a second opposite end of the first end to the pivot ring 136C. Figure 15 schematically illustrates a housing 1500 for the transmission 1300 of Figures 13 and 14. The housing 1500 includes three hollow guide tubes 1504, 1506, and 1508. Each of the hollow guide tubes 1504, 1506, 1508 are connected in a first end to a hub 1512 holding the transmission 1300 and at a second end opposite the first end to a transmission wheel 1514. Three tension members 1516, 1518, 1520 are respectively disposed within the guide tubes 1504, 1506, 1508 and are connected to the first end of the transmission wheel 1514. A second end of the tension members 1516, 1518, 1520 opposite the transmission wheel 1514 are respectively connected with spherical weights 1526, 1528, 1530. In the forms of alternative embodiments of the invention, the weights 1526, 1528, 1530 can be adapted to other geometric shapes. Members of multiple linkage 1532, 1534, 1536, respectively, extend from weights 1526, 1528, 1530 to an annular member (non-counter), as does the annular member 806 of the Figure 8. Switching to the operation method of the housing 1500 of Figure 15, rotation of the hub shell 1512 causes rotation of the hollow guide tubes 1504, 1506, 1508. While the guide tubes 1504, 1506, 1058 rotate, the weights 1526, 1528, 1530 extend outwardly towards the transmission wheel 1514. The outward movement of the weights 1526, 1328, 1530 causes a change in the axis of rotation of the power adjusting devices 122A, 122B, 122C of Figures 13 and 14. Figure 16 is another alternative embodiment of the invention. Figure 16 is a schematic illustration of the manual version of the transmission 1300 shown in Figures 13 and 14. For purposes of simplicity of description, only the differences between the transmission 1600 of Figure 16 and the transmission 1300 of the Figures 13 and 14. The transmission 1600 includes a flexible cable 1602 that is connected to a first end to a shift actuator (not shown). The cable 1602 extends from the shift actuator (not shown), through the central passage of the main shaft 102 and then extends through an opening (not shown) in the main shaft 102. From the opening (not shown) the cable 1602 extends around the pulley 1308. From the pulley 1308, the cable is guided around the pulley 1306. From the pulley 1306, the cable extends towards the pulley 1308. Finally, from the pulley 1308, the cable is connects to the main shaft 102. Still with reference to Figure 16, since the cable 1602 is directed towards the shift actuator (not shown), the cable 1602 pulls on the pulleys 1304, 1306, 1308 thus causing a change in the ee of rotation of each of the power adjustment devices 122A, 122B, 122C. Conversely, when the shift actuator (not shown) releases the cable 1602, the tension members 1404, 1406, 1408 cause each of the rotation axes of the power adjustment devices 122A, 122B, 122C to change in a second and opposite direction. With reference to Figures 17-19, three embodiments of the support member 154 are disclosed. In Figure 17, the support member 154 is a cylindrical ring having a nominally concave outer surface. In Figure 18, the circumference of the support member 1800 is the narrowest near midpoint 1802 of the support member. From the midpoint, the outer circumference of the support member 154 is increased to each of the ends of the support member 154. It is noted that the slope created by the outer surface of the support member 154 increases gradually from the horizontal state, relative to its longitudinal axis at the midpoint 1802 about an angle of 30 degrees at each of the ends of the support member 154. The shape of the support member 1800 allows axial movement of the support member 1800, thereby aiding the ease of changing the transmission and also preventing the support member 154 from dislocating at either end during the change. Figure 19 depicts a support member 1900 having a concave outer surface. The shape of the support member 1900 prevents the support member 1900 from wandering through the main shaft 102 while the transmission 100 is in use. Figure 20 illustrates an alternative embodiment of the present invention. The first thrust bearing 1106 is rotatably disposed on the main shaft 102 and is positioned between the support member 154 and a first thrust sheave 2006. The second thrust bearing 1108 is disposed on the main shaft 102 on the side of the thrust member. support 154 opposite to the first thrust bearing 1106. The second thrust bearing 1108 is positioned between the support member 154 and a second thrust sheave 2008. The second thrust sheave 2008 is operatively connected to a tension inductor 2018. The inductor of tension 2018 provides a force that returns the support member 154 to its neutral position when the transmission 200 is not making changes. Opposed to the second thrust sheave 2008, the voltage inductor 2018 can be secured to the main shaft 102, to the fixed support 152 (not shown) or to another component of the transmission 2000. A first end of a tension inductor 2016 makes contact with the first thrust sheave 2006. The other end of the tension inductor 2016 can be secured to the main shaft 102, the fixed support 152 (Figure 2), or another component of the transmission 2000. Preferably, to minimize friction, a small amount of play is allowed between the first thrust bearing 1106, and the second thrust bearing 1108, and the support member 154. Figure 21 illustrates an alternative embodiment of the invention using the first thrust bearing 1106 (also shown in Figure 11) and the second thrust bearing. 1108 (also shown in Figure 11). The first thrust bearing 1106 is rotatably disposed on the main shaft 102 and is positioned between the support member 154 and a first thrust sheave 2106. The second thrust bearing 1108 is disposed on the main shaft 102 and placed between the thrust member. support 154 and a second thrust washer 2108. Each of the pivot supports 134A, 134B, 134C has four extensions 2110, 2112 (Figure 24), 2114, 2116 (Figure 24) that fit the interface with the ring support 154. The extensions 2110, 2112, 2114, 2116 of the pivot supports 134A, 134B, 134C are adapted to direct the support member 154 such that it is constantly positioned below the power adjustment devices 122A, 122B, 122C during the transmission operation 2000. A first end of a tension inductor 2016 makes contact with the first thrust sheave 2006. The other end of the tension inductor 2016 can be secured to the main shaft 102 , the fixed support 152 (Figure 2) or another component of the transmission 2000. Preferably, to minimize friction a small amount of play is allowed between the first thrust bearing 1106, the second thrust bearing 1108, and the support member 154. Figure 21 illustrates an alternative embodiment of the invention using the first thrust bearing 1106 (also shown in Figure 11) and the second thrust bearing 1108. (also shown in Figure 11). The first thrust bearing 1106 is rotatably disposed on the main shaft 102 and is positioned between the support member 154 and the first thrust sheave 2106. The second thrust bearing 1108 is disposed on the main shaft 102 and placed between the thrust member. support 154 and a second thrust sheave 2108. Each of the pivot supports 134A, 134B, 134C, has four extensions 2110, 2112 (Figure 21), 2114, 2116 (Figure 24) which are adapted to interconnect with the ring. support 154. The extensions 110, 2112, 2114, 2116 of the pivot supports 134A, 134B, 134C are adapted to direct the support member 154 in such a way that they are constantly positioned below the power adjusting devices 122A, 122B, 122C during the transmission operation. The first thrust sheave 2106 is positioned between the first thrust bearing 1106, and the extensions 2110, 2112, 2114, 2116 of the pivot supports 134A, 134B, 134C. Preferably, to minimize friction, a small amount of play is allowed between the first thrust bearing 1106, and the second thrust bearing 1108, and the support member 154. Figure 22 shows a front raised view of the thrust sheave. 2108 of the transmission 2100 of Figure 21. The thrust sheave 2108 has a plurality of grooves on its outer edge to prevent the second thrust sheave 2108 from coming into contact with the power adjusting devices 122A, 122B, 122C during the change. Figures 23 and 24 show a pivot support, like the one shown in Figure 21, where the pivot support has a two-part construction. Figure 23 is a side elevational view of the pivot support of Figure 24 illustrating a bottom plan view of the pivot support. To form the pivot bracket of Figure 23 and 24, a first part of the pivot bracket 2120A and a second part of the pivot bracket 2188A are pressed together. The first pivot support 2120A and the second part of the pivot support 2118A are each approximately semi-cylindrical in shape from the top floor view. This first part of the pivot support 2120A includes the extensions 2212 and 2110 (Figure 24). In addition, the second support part 2118A includes the extensions 2116 and 2114 (Figure 24). The first part of the pivot support 2118A and the second part of the pivot support 2120A can be clamped together through any number of traditional fastening techniques. For example, the indentations 2130A can be formed in the second part of the pivot support 2120A and the indentation 2134 A can be formed in the second part of the pivot support 2118A in such a way that the support part of the pivot 2120A and the support part of the pivot 2118A they can be adjusted with hinge together. The slots 2122A in the first part of the pivot support 2120A is designed to allow the transverse connection of each of the pivot supports in the transmission, such as through an interconnector 2720 (Figure 27). Figures 25 and 26 illustrate an alternative embodiment of the fixed support 152. The fixed support 152 has a plurality of immobilizers 2510, 2512, 2514, 2516, 2518, and 2520. The immobilizers 2510, 2512, 2514, 2516, 2518, and 2520 may optionally be formed as an integral part of the legs 153 of the fixed support 152. The fixed support 152 further includes pivot tips 2530, 2532 and 2534 which are disposed radially about a midpoint of the fixed support 152. The stops of pivot 2530, 2532, 2534 prevent the pivot supports 134A, 134B, 134C from rotating too far and striking the rotatable driven member 170 and / or the rotatable driving member 120.

Figures 27, 28 and -29 illustrate yet another embodiment of the fixed support 152. Each of the legs 153 of the fixed support 152 has a slot 2760 which is configured to receive one of the three immobilizers 2702A, 2702B 2702C. Each immobilizer 2702A, 2702B, 2702C includes a crank 2730 that fits into the slot 2760. The slot 2760 has a radius equal to or slightly greater than the radius of the crank 2730. The crank 2730 has a cylindrical or spherical design allowing it to rotate in the slot 2760. The ends of the crank 2730 are respectively connected to an angular support 2710A and to an angular support 2710B. The angular support 2710A and the angular support 2710B are respectively connected, opposite the slot 2760, for the interconnectors 2720A, 2720B. The interconnects 2720A, 2720B connect the pivot supports 134A, 134B, 134C, thereby anchoring the pivot supports 134A, 134B, 134C to the fixed support 152 and also ensuring that all the pivot supports 134A, 134B, 134C, rotate in unison. The interconnects 2720A and 2720B fit within the slots 2122A (Figure 23) of the first part of the pivot support 2120 or the openings 142, 144 (Figure 21) of the pivot supports 134A, 134B, 134C. The interconnects 2720A and 2720B are respectively connected, at one end opposite the angle supports 2710A and 2710B, to the pivot members 2710A and 2740B. The pivot members 2740A and 2740B are respectively inserted into the openings 142, 144, of each of the pivot supports 134A, 134B, 134C thereby providing for a pivot for each of the pivot supports 134A, 134B, 134C. In one embodiment of the invention, the main shaft 102 can be adapted to make the fixed support 152 fit in such a way that the fixed support 152 is prevented from rotating around the main axis 102. For example, in the embodiment of the invention disclosed in Figure 27, an opening with flat edge 2780 in the center of the fixed support 152 prevents the fixed support 152 from rotating. An exemplified main shaft 102 having an adapted outer diameter is shown in Figures 32 and 33. In addition, the flat edge opening 2780 allows quick assembly of the fixed support 152 to the shaft 102. Alternatively, the fixed support 152 can be attached to the shaft. principal 102 through traditional elements. Figures 20 and 31 illustrate an alternate embodiment of the fixed support 152 of Figures 27-29. The fixed support 152 has a leg 153. In this embodiment, the immobilizer 2702B (Figure 27) and the immobilizer 2702C (FIG. 27) are adapted to connect directly to the other pivot supports 134A, 134B, 134C in the transmission. Since the immobilizer 2702A is anchored to the main shaft 102, each of the power adjusting devices 122A, 122B, 122C are also anchored to the main shaft 102 through its connection to the immobilizer 2702A. Advantageously, the use of a single leg 153 reduces the manufacturing costs on the embodiments of the invention having multiple legs. Figures 32 and 33 illustrate an alternate embodiment of the main shaft 102. The main shaft 102 of Figures 32 and 33 can be used in conjunction with "various embodiments of the invention including the 1600 transmission (shown in Figure 16) At least one of the flexible cables 1602 is positioned within the main shaft 102, passes around a pulley 3212, through a hole 3210 and exits the main shaft 102 at one end.A fastener 3214, such as a bolt or The shank secures the pulley in position The main shaft 102 has a groove 3216 which allows the pulley 3212 to be easily inserted into the main shaft 102 during manufacture Optionally, the main shaft 102 can be strengthened in the vicinity of the pulley 3212 by increasing the size of the hull of the main shaft 102. In addition, the main shaft 102 can be adapted to define a pivot stop 3218 for the pivot supports 134a, 134B, 134C. The pivot stop 3218 acts to prevent the pivot supports 134A, 134B, 134C from moving with pivoting away too far during the change and striking the rotatable driving member 120 and / or the rotatable driven member 170. Also, a flange 3220 from the stop of the pivot 3218 can be used to prevent the support member 154 (Figure 2) from moving too far axially. In addition, a tension inductor 2016 (Figure 20), such as a spring may be placed against the flange 3220, to help keep the support member 154 centrally positioned below the power adjusting devices 122A, 122B, 122C. Figure 33 shows a cross section of the main shaft 102 having a flat area formed on the main shaft 102 to allow the flat edge hole 2780 of the fixed supports 152 described in Figures 27-31 to be quickly assembled on the main shaft 102. However, the shape of the main shaft 102 and the fixed support 154 can be adapted within other equalization configurations. Figure 34 illustrates yet another alternative embodiment of the invention. Figure 34 is a schematic illustration of a manual version of the transmission 1300 shown in Figures 13 and 14. For purposes of simplicity of description, only the differences between the transmission 3400 of Figure 34 and the transmission 1300 of the Figure 13. The transmission 3400 includes three flexible cables 1312, 1314, 1316 that differ from the transmission 1300 in that the second end of the cables extends through three openings (not shown) in the main shaft 102 and enter the passageway. central axis 102.

The three flexible cables 1312, 1314, and 1316, then extend through one of the ends of the main shaft 102 and the end in a conventional shift actuator. Figure 35 illustrates still another alternative embodiment of the invention. Figure 35 is a schematic side elevational view of a transmission 3500 that makes the changes automatically. Figure 36 is an elevated view of the schematic cut-away end of the annular bearing of the transmission 3500 of Figure 35. The characteristics of the transmission 3500 shown in Figures 35 and 36 can be used in conjunction with the characteristics of Figures 13-15. The 3500 transmission includes multiple cable assemblies identically configured for each of the power adjustment devices 122A, 122B, 122C. However, for purposes of simplicity of description, only one of the cable assemblies will be explained. The flexible cable 1316 is attached to the first end of the main shaft 102 (not shown). From the main shaft 102, the flexible cable 1316 travels around the pulley 1310, and continues to the pulley 3520A. attached to one of the legs 153 of the fixed support 152. After wrapping around the pulley 3520A, the flexible cable 1316 passes through the opening 3614 (Figure 36) and ends joining the second annular bearing 816. The second annular bearing 816 It is fixed and does not rotate. From a first end where it is joined to the first annular bearing 806, the flexible cable 1532 passes through the opening 3624 and travels to the pulley 3522A. From the 3522A pulley, the cable passes through the opening 3624 and travels to the 3522A pulley. From the pulley 3522A, the cable 1532 passes through the opening (not shown) in the bucket hull 302 to the pulley 3524A. In the embodiment of the invention shown in Figure 35, the first annular bearing 806 rotates with the bucket hull 302. The rotation of the first annular bearing 806 is facilitated by the bearings 808 which are located between the first annular bearing 806 and the second annular bearing 816. From the pulley 3524A, a flexible cable 1532 can pass around one or more of the other pulleys (not shown) or continue directly and attach to the weight 1526 (shown in Figure 15).

Figures 37 and 38 illustrate an alternative embodiment of the transmission 3700 including a gravity bearing mechanism 3710. The gravity bearing mechanism 3710 can be used in connection with bicycles, motorcycles, automobiles and machinery where it is desired to disengage the transmission. The gravity bearing mechanism 3710 is positioned between the hub driver 186 and the second roller ring assembly 180. When the torque is applied to the rotatable driven member 170, the second roller ring assembly 180 responds by rotating in the same direction as the rotatable driven member 170. The rollers 112 roll in the shallow grooves of the rotatable driven member 170. The action of the rollers 112 causes the gravity bearing mechanism 3710 to be directed towards the hub driver 186. The rolling mechanism by severity 3710 does not rotate with the rotatable driving member 170 because the two slots 3716A and 3716B in the gravity bearing mechanism 3710 engage a clutch ring 3714. The clutch ring 3714 is frictionally attached to the main shaft 102 and has two protrusions that extend into the two slots 3716A and 4716B of the gravity bearing mechanism 3710. The bearing mechanism by gravity 3710 touches the hub driver 186 creating friction between the gravity bearing mechanism 3710 and the bucket driver 186. The notches 3711 can be cut into a chamfer of the gravity bearing mechanism 3710 to increase the friction. The friction causes the rollers 112 to continue to roll to the sides of the shallow grooves of the rotatable driven member 170 and the gravity bearing mechanism 3710 until sufficient force is applied against the hub driver 186 and attached and rotated with the mechanism of bearing by gravity. The clutch ring 3714, then rotates with the gravity bearing mechanism 3710. When the torque is released, a clutch tension inductor 3712 pushes the gravity bearing mechanism 3710 away from the hub driver 186, disengaging the gravity bearing mechanism 3710 from the bucket impeller 186 and allowing the bucket impeller 186 and bucket hull 302 to continue to rotate. Even with reference to Figure 37, an alternative method for making changes to the 3700 transmission is described. For purposes of simplicity of the description, only the differences between the transmission 3700 and other previously described embodiments will be noted. Pivot brackets 134A, 134B, 134C, when shifted upward cause the legs of pivot bracket 3730 to be attached to pivot brackets 134A, 134B, 134C, to contact and push the first thrust sheave 2006 toward the drive flange of the transmission 3700. The movement of the first thrust sheave 2006 causes both the first thrust bearing 1106 and the support member 154 to be pushed towards the fixed support 152. The tension inductor 2018 prevents the support member 154 moves too far and when the transmission 3700 is switched to low, it causes the support member 154 to be pushed towards the legs of the pivot support 3730. The present invention provides an innovative transmission that provides an angular velocity ratio of input / variable output offering up to 900% angular speed range of input / output. In addition, the transmission can be operated both manually and automatically. Additionally, the transmission of the invention provides a simple design that requires a minimum number of parts to be implemented, and is therefore easy to manufacture, compact, lightweight and produces little friction. The transmission eliminates the duplicate, overlapped or unsuitable gears found in gear drives. The transmission eliminates the need for clutches that are traditionally used to make speed changes. Finally, the transmission can save energy or gas by providing an angular velocity ratio of input and output. While the above detailed description has shown, described, and highlighted the innovative features of the invention while being applied to various embodiments, it will be understood that various omissions, substitutions, and changes in the form and details of the device can be made or to the process illustrated by the people qualified in technology, without departing from the spirit of the invention. The scope of the invention is indicated by the appended claims in lieu of the detailed description. All the changes that come within the meaning and range of the equivalence of the claims that are encompassed within its scope.

Claims (51)

1. CLAIMS 1. A transmission comprising a rotatable driving member; a plurality of spherical power adjustment devices, each of the spherical power adjusting devices have a central hollow, and each of the spherical power adjustment devices rotate about an axis of rotation that is defined by the hollow; a rotatable substantially cylindrical support member having the ability to have an axial movement, wherein the support member comes into frictional contact with each of the power adjustment devices; a plurality of rods, which each of the rods is inserted through one of the holes, where each of the rods is operably connected to the support member; and wherein the axis of rotation of each of the adjustment devices is capable of substantially simultaneously and also in response to axial movement of the rotatable support member.
2. 2. The transmission of Claim 1, further comprising two bearings and two flat platforms, wherein one of the bearings and one of the flat platforms are placed on each of the ends of the pivotable support member so that each of the Bearings are between one of the flat platforms and one end of the pivotable support member.
3. 3. The transmission of Claim 2, wherein the two bearings and the two flat platforms have the ability to have axial movement, wherein the rotatable support member moves axially in response to the axial movement of the two bearings and the two platforms. flat 4.
4. The transmission of Claim 3, further comprising a plurality of legs, of which at least one of the legs is for each of the rods, and the legs are operably connected from the rods to at least one of the rods. of flat platforms.
5. The transmission of Claim 4, further comprising an axle and a shift member, wherein at least a portion of the shaft is shallow, and the shift member is located at least partly within the hollow portion. of the shaft, wherein the shaft comprises an opening that allows the shift member to be operatively connected to at least one of the flat platforms.
6. The transmission of Claim 5, wherein the shift member has the ability to perform an axial movement, and wherein the pivotable support member, the two bearings and the two flat platforms move axially in direct response to axial movement of the member of changes.
7. The transmission of Claim 3, further comprising a plurality of legs, of which two of the legs respectively support at least in part each of the rods, where the legs operatively connect the rods with a member of rotatable support.
8. 8. The transmission of Claim 1 additionally comprises: Two bearings, of which each of the bearings is mounted coaxially to the shaft, of which the first of the bearings which are in frictional contact with a first end of the bearing member support; the second of the bearings is in frictional contact with a second end of the support member; and two flat platforms that are fixedly attached to the shaft, where one of the first flat platforms and the second end of the rotatable support member each provide a runaway surface for the first of the two bearings, where the second flat platform and the second end of the pivotable support member, each provides a runaway surface for the second of the bearings.
9. 9. The transmission of Claim 8, wherein before the axial movement of the rotatable support member, the two bearings and the two flat platforms, the plurality of the legs are engaged thereby causing the stems to conform to the axis of rotation of the arms. Power adjustment devices substantially equal and simultaneously.
10. 10. A transmission of automatic changes comprising: a rotatable driving member; a plurality of spherical power adjustment devices, wherein each of the spherical power adjustment devices have a central void; a plurality of rods, of which one of the rods is inserted through one of the recesses of the spherical power adjusting devices, a rotatable driving member; a plurality of spherical power adjustment devices, of which each of the power adjustment devices has a central recess; a plurality of rods, of which one of the rods is inserted through one of the recesses of the spherical power adjustment devices; a substantially cylindrical rotatable support member that is in frictional contact with each of the spherical power adjustment devices; at least one outwardly extending weight operatively connected to at least one of the axes; and at least one flexible tension member that operably connects to at least one of the weights with at least one of the rods.
11. The transmission of Claim 10, wherein the outwardly extending weight changes the movements radially in response to variations in a centrifugal force that is applied to the weight, and where an increase in centrifugal force causes the transmission to shift to high speed.
12. 12. The transmission of Claim 10 further comprises an annular bearing, wherein the annular bearing moves in response to the radial movement of at least one weight and thus causes a change in transmission.
13. 13. The transmission of Claim 12 further comprises at least two flexible tension members, of which at least one of the first flexible tension members connects to at least one of the weights extending outwardly with the annular bearing, wherein at least one of the second flexible tension members connects the annular bearing with at least one rod.
14. 14. The transmission of Claim 13, further comprising a tension member, of which the tension member biases the transmission changes in a first direction, where at least one of the outwardly extending weights bias changes of the transmission. the transmission in a second direction.
15. 15. The transmission of Claim 14, further comprising a rotatable wheel and a hub helmet, wherein the wheel has at least one hollow beam, wherein the hub helmet is fixedly attached to the wheel and where at least one of the stretching weights is placed inside the hollow ray.
16. 16. The transmission of Claim 15, further comprising at least one tension member for each of the outwardly extending weights, wherein at least one tension member is attached to at least one end of the body. at least one of the outwardly extending weights and which are operably linked to the wheel rotatable at a second end, in which at least one of the members polarizes outwardly the weight that can be extended.
17. 17. The transmission of Claim 13 further comprises a plurality of guides for the flexible tension members, of which at least one of the guides of the flexible tension member directs the trajectory of at least one of the first flexible members. of tension, in which at least one of the guides of the flexible tension member directs the trajectory of at least one of the second flexible tension members.
18. 18. The transmission of Claim 18 further comprises a guide for flexible tension member e-1, wherein at least one of the guides of the tension member operatively connects to each of the rods.
19. 19. The transmission of Claim 10 further comprises a rotatable annular bearing, wherein the annular bearing comprises: a ball or bearings; a first rush for the ball or the bearings; and a second rush for the ball or the bearings.
20. 20. The transmission of Claim 19, wherein at least one of the flexible tension members connects to at least one of the weights extending outwardly with the first runaway., and at least one of the flexible tension members operatively connects to the second runaway with at least one of the rods.
21. The transmission of Claim 20, wherein the rotatable annular bearing moves axially in response to the radial movement of at least one outwardly extending weight.
22. 22. The transmission of Claim 21, wherein the rotatable annular bearing surrounds the plurality of spherical power adjusting devices and has an inner diameter that is greater than the circumference enclosing the plurality of power adjustment devices.
23. 23. The transmission of Claim 22 further comprises a flat platform for each of the bearings, where the flat platforms are placed coaxially on the shaft and are positioned in such a way that the bearings are between the flat platforms and the supporting member. rotatable
24. 24. The transmission of Claim 20 further comprises a plurality of rods, of which each of the rods defines the axis of rotation of each of the power adjustment devices and is operatively connected to two bearings that are mounted each one coaxial to the support ring.
25. 25. The transmission of Claim 24, wherein at least one of the rods is connected to at least one of the two flat platforms.
26. 26. The transmission of Claim 25, further comprising: at least one tension member attached to each of the rods, wherein the tension member inclines each of the rods in a first direction; wherein at least one of the guides of the flexible tension member is rotatably attached to each of the rods; and at least one of the flexible tension members is configured to tilt the rods in a second direction, wherein at least one of the flexible tension members is supported by at least one of the guides of the flexible tension member.
27. 27. The transmission of Claim 26, wherein at least one of the tension members and at least one of the guides of the flexible tension member are attached to the rods on substantially opposite sides of the rods.
28. 28. The transmission of Claim 26, wherein at least one of the tension members and at least one of the guides of the flexible tension member are attached to the rods at about 160 and 200 degrees away from each other.
29. 29. The transmission of Claim 28, wherein at least two of the tension members are attached to each rod, of which the tension members tilt the rods in a first direction.
30. 30. The transmission of Claim 24 further comprises at least one fixed support attached to a hub helmet enclosing the rotatable driven member and the rotatable driving member.
31. 31. The transmission of Claim 24, further comprising at least one flexible tension member operably connected to the rods, wherein at least one flexible tension member is configured to adjust the axis of rotation of each of the control devices. power adjustment.
32. 32. The transmission of Claim 31 further comprises a plurality of guides of the flexible tension member respectively attached to a plurality of rods, in which at least one of the flexible tension members is supported by each of the guides. of flexible tension members.
33. 33. The transmission of Claim 32 further comprises a plurality of tension members that are fixedly attached to the rods, wherein the tension members are adapted to modify the axis of rotation of each of the power adjustment devices.
34. 34. The transmission of Claim 20 further comprises a tension member attached to each of the outwardly extending weights, wherein the tension member aids outward extension of each of the outwardly extending weights.
35. 35. A transmission comprising: a rotary impeller mounted rotationally and coaxially; a rotatable driving member mounted rotationally and coaxially with respect to the rotatable driving member; a plurality of power adjusting devices interposed with friction between the rotatable driving member and the driven member rotatable and adapted to transmit power from the driving member to the driven member; a pivotable support member frictionally engaged with the plurality of power adjusting devices, such that each of the power adjusting devices makes frictional contact against the driving member, the driven member and the rotatable support member; a first compression member mounted rotationally and coaxially with respect to the driving member and adapted to direct the rotatable driving member toward the rotatable driven member; a second compression member mounted rotationally and coaxially with respect to the rotatable driving member and adapted to direct the pivotable driven member toward the rotatable driving member; a plurality of rods, of which each of the rods defines an axis of rotation for each of the power adjustment devices, of which one rod is in each of the power adjustment devices, where the rods have the ability to modify an axis of rotation of each of the power adjustment devices; at least one annular bearing is connected to at least one of the flexible tension members, where the annular bearing is configured to adjust the axis of rotation of each of the power adjusting devices; and at least one fixed support is fixedly and coaxially mounted, wherein the fixed support prevents the rods from rotating about the same axis as the rotatable driving member.
36. 36. The transmission of Claim 35, wherein at least one of the fixed supports allows the rods to move upwardly pivotable about fifty degrees from an axis formed by the rotation point of the rotating drive member to the point of rotation. rotation of the rotatable driven member.
37. 37. The transmission of Claim 35 further comprises at least one tension member, wherein at least one of the tension members inclines the rods in a first direction.
38. 38. The transmission of Claim 37, wherein at least one of the guides of the flexible tension member is attached to each of the rods, wherein the guide of the flexible tension member is adapted to tilt the rods in a second direction.
39. 39. The transmission of Claim 35 further comprises at least a second direction of one of the flexible tension members, wherein the flexible tension member is adapted to adjust the axis of rotation to a plurality of power adjustment devices.
40. 40. The transmission of Claim 39 further comprises at least one guide of the flexible tension member, wherein the guide of the flexible tension member supports the flexible tension member,
41. 41. The transmission of Claim 35 further comprises at least less a weight, in which this weight is operatively connected to the rods, where at least one of the weights is adapted to automatically vary the speed of the transmission.
42. 42. The transmission comprises: a rotary impeller mounted rotationally and coaxially; a rotatable driven member mounted rotationally and coaxially with respect to the rotatable driving member; a rotatable support member with substantially a diameter; a plurality of power adjusting devices interposed with friction between the rotatable driven member and the rotatable driven member, and the rotatable support member; the elements for maintaining the support member in frictional contact with the plurality of power adjustment devices; and elements for axially moving the support member.
43. 43. A transmission comprising: a rotary impeller mounted rotationally and coaxially; a rotating driven element mounted rotationally and coaxially with respect to the rotatable driving member; a rotatably mounted rotatable support member; a plurality of rods, of which each of the rods define an adjustable axis; a plurality of power adjusting devices interposed with friction between the rotatable driving member, the rotatable driven member, and the supporting member, wherein each of the power adjusting devices are centrally positioned within one of the rods in the Usable axis; three or more guides of the flexible tension member, wherein at least one of the guides of the flexible tension member is attached to each of the pivot supports, wherein the guides of the flexible tension member tilt the axes in a first direction; at least one flexible tension member operatively connected to the axes; and a plurality of tension members interconnecting each of the rods to the two nearest rods, where the tension members are inclined in a second direction.
44. 44. A continuously variable transmission comprising: a rotary and coaxially rotatable mounted impeller member; a rotatable driven member mounted rotationally and coaxially with respect to the rotatable driving member; a rotatably mounted rotatable support member; a plurality of rods, of which each of the rods is operatively connected to the support member, wherein each of the rods defines an adjustable axis, wherein each of the rods is operatively connected to the support member, where the rods adjust the position of the rotatable support member; a plurality of power adjusting devices interposed with friction between the rotatable driving member, a rotatable driving member, and the supporting member, each of the power adjusting devices centrally positioned with one of the pivot supports in the "adjustable, and at least one leg attached to each of the rods
45. 45. A continuously variable transmission comprising: a rotatable rotating and coaxially mounted rotary impeller member: a rotatable driven member mounted rotationally and coaxially mounted with respect to the driving member rotatable, a rotatable support member rotatably mounted with respect to the rotatable driving member, a plurality of power adjusting devices interposed with friction between the rotatable driving member, the rotatable driving member, and the support member; a plurality of rods, wherein each of the adjustment devices, power, are placed on one of the rods, wherein the support member slides axially in response to the adjustment of the rotation axis of the power adjustment devices; and elements for axially moving the pivotable support member.
46. 46. A continuously variable transmission comprising: a rotary impeller mounted rotationally and coaxially; a rotatable driven member mounted rotationally and coaxially with respect to the rotatable driving member; three or more power adjusting devices mounted rotatably interposed with friction between the rotatable driving member and the rotatable driven member; elements for alternating the axes of rotation of three or more power adjustment devices; control elements for alternating equally the axes of rotation of the three or more power adjustment devices; elements for alternating the axes of rotation of three or more power adjustment devices; control elements for alternating equally the axes of rotation of the three or more power adjustment devices; a support member rotatably mounted such that the three or more power adjusting devices make three points of contact with the support member, the rotatable driving member, and the pivotable driven member, where the support member travels at least 30% of its length along the axis of rotation of the rotatable driving member, and wherein the support member slides axially in response to an adjustment on an axis of rotation of the power adjusting devices; a rotatable input impeller mounted rotationally and coaxially with respect to the rotatable driving member; a first plurality of three or more rollers positioned on the driving side of the rotatable driving member, wherein the first plurality of the three or more rollers allow the force applied to the power adjusting devices to be increased through the driving member rotatable at the time that torsion increases; a rotating mounted rotary output impeller; a second plurality of three or more rollers positioned on the driven side of the rotatable driven member, wherein the second plurality of three or more rollers allow the force applied to the power adjusting devices to be increased through the rotatable driven member while torsion increases; and at least one fixed support rigidly fixedly attached to an immovable surface, wherein at least one of the fixed supports prevents the orbiting of the three or more power adjustment devices.
47. The transmission of Claim 46 further comprises a plurality of rods, where there is a rod for each of the power adjustment devices, of which each rod defines an axis of rotation for each of the power adjustment devices. .
48. 48. The transmission of Claim 46, wherein the support member has a substantially uniform external diameter.
49. 49. The transmission of Claim 46, wherein the support member has a concave outer surface.
50. 50. A continuously variable transmission comprising: a rotatable impeller mounted rotationally and coaxially; a rotatable driven member mounted rotationally and coaxially with respect to the rotary and coaxially mounted rotatable driving member; three or more power adjusting devices interposed with friction between the rotatable driving member and the rotatable driven member; modifying elements for alternating the axes of rotation of the three or more power adjustment devices; control elements for alternating the same and simultaneously, at the time of the change, of the axes of rotation of each of the power adjustment devices; a support member rotatably mounted so that the three or more power adjustment devices make three points of contact with the support member, the rotatable driving member, and the rotatable driven member; a rotatable input impeller mounted rotationally and coaxially with respect to the rotatable driving member; a first plurality of three or more rollers positioned on the driving side of the rotatable driving member, wherein the first plurality of three or more rollers compress the rotatable driving member against the power adjusting devices; a rotary and coaxially mounted rotatable output impeller; a second plurality of three or more rollers positioned on the driven side of the rotated driven member, wherein the second plurality of three or more rollers compress the driven member rotatable against the power adjusting devices; at least one fixed support rigidly attached to a non-rotatable component of the transmission, wherein at least one fixed support anchors three or more of the power adjustment devices; three or more rods, where there is a rod for each of the adjustment devices is powered, where the rods vary when making the transmission change the axis of rotation of the power adjustment devices; at least one flexible tension member operatively connected to the rods; and three or more guides for the flexible tension member, of which at least one of the guides for the flexible tension member is attached to each of the rods, where the guides of the flexible tension member tilt the rods in a first direction.
51. 51. A continuously variable transmission comprising: a rotatable impeller member mounted rotationally and coaxially; a rotatable driven member mounted rotationally and coaxially with respect to the rotary and coaxially mounted rotatable driving member; three or more power adjusting devices interposed with friction between the rotatable driving member and the rotatable driven member; control elements for alternating, simultaneously and simultaneously, at the time of the change, the rotation axes of the power adjustment devices; a support member rotatably mounted so that the three or more power adjustment devices make three points of contact with the support member, the rotatable driving member and the rotatable driven member; a rotatable input impeller mounted rotationally and coaxially with respect to the rotatable driving member; a plurality of three or more rollers positioned on the driving side of the rotatable driving member, wherein the first plurality of three or more rollers compress the rotating driving member against the power adjusting devices; a rotatable output impeller mounted rotationally and coaxially; a second plurality of three or more rollers positioned on the driven side of the rotatable driven member, wherein the second plurality of three or more rollers compress the driven member rotatable against the power adjusting devices; at least one fixed rigidly fixed support, attached to a non-rotating component of the transmission, wherein at least one of the fixed supports anchor the three or more power adjustment devices; at least one leg mounted on each of the rods, of which at least one leg is adapted to adjust the axis of rotation of the power adjustment devices; and three or more rods, of which there is a rod for each of the power adjustment devices, where the rods define an axis of rotation of the power adjustment devices.