WO2016172013A1 - Procédés de vitesse de rotation de changement de position axiale maximale - Google Patents

Procédés de vitesse de rotation de changement de position axiale maximale Download PDF

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Publication number
WO2016172013A1
WO2016172013A1 PCT/US2016/027989 US2016027989W WO2016172013A1 WO 2016172013 A1 WO2016172013 A1 WO 2016172013A1 US 2016027989 W US2016027989 W US 2016027989W WO 2016172013 A1 WO2016172013 A1 WO 2016172013A1
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cone
cvt
axial position
transmission
adjuster
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Armin Tay
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
    • F16H61/66272—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members characterised by means for controlling the torque transmitting capability of the gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/40—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism comprising signals other than signals for actuating the final output mechanisms
    • F16H63/42—Ratio indicator devices
    • F16H2063/426—Ratio indicator devices with means for advising the driver for proper shift action, e.g. prompting the driver with allowable selection range of ratios

Definitions

  • This invention relates to torque/speed transmissions, specifically to methods that can be used to "limit the maximum shaft rpm (speed) at which axial position changing of a variator mounted on if is performed to a "maximum axial position changing rpm value" for all variator mounted shafts of a CVT, while still allowing a safe driving experience and also allowing the driver to use the full power of the engine when needed.
  • variators are: a cone with one torque transmitting member, a cone with two oppositely mounted torque transmitting members, a cone with two opposite teeth, a push belt pulley, etc.
  • the methods of this invention are referred to as the "Maximum Axial Position Changing RPM Method", the "Alternate Maximum Axial Position Changing RPM
  • CVT that has the potential to replace automatic and manual transmissions in vehicles is a CVT 4, which is described in U.S. Patent Applications 13/829,613, 13/730,958, and 13/889,049.
  • a CVT 4 which is shown in Figs. 1 to 4, has one cone with one torque transmitting member mounted on one shaft/spline that is coupled to another cone with one torque transmitting member mounted on another shaft/spline by a transmission belt.
  • a CVT 4 is promising design because it can allow for the construction of non-friction dependent CVT's without using ratcheting or reciprocating mechanisms. However, if a CVT 4 is transmitting a large torque, then the tension in the transmission belt of the CVT 4 is also large. And sliding a transmission belt under large tension from small diameter of its cone to a large diameter of its cone, as required for transmission ratio change, will also require a large force,
  • the axial position of a cone of a CVT 6 has to be changed within less than a full revolution of that cone.
  • the duration available for changing the axial position of a cone of a CVT 6 depends on the rotational speed (rpm) at which the cones of the CVT 6 are rotating.
  • the force needed to change the axial position of a cone can be limited to 40 lbs.
  • the maximum rpm of the engine which we assume is 6000 rpm, will determine the force needed to change the axial position of a cone, which for 6000 rpm is 162 lbs, or more than 4 times larger than that for 3000 rpm.
  • the shock ioads due to axial position changing of a cone will also be about 4 times larger than that for 3000 rpm.
  • a CVT 6 can be unpractical for configurations where a cone rotates at high speed, such as 12000 rpm for example.
  • a cone can rotate at 12000 rpm for a maximum engine rpm of 6000 rpm and a transmission ratio (output speed/input speed transmission ratio) of 2: 1.
  • sequence/method can allow for an unsafe driving experiences such as when the CVT is stuck in a low transmission ratio because the "maximum axial position changing rpm value" is exceeded; or can limit the power of an engine, such when the engine is only allowed to run up to 3000 rpm instead of 6000 rpm so as not to exceed the "maximum axial position changing rpm value".
  • the "Maximum Axial Position Changing RPM Method", the “Alternate Maximum Axiai Position Changing RPM Method”, and the “Alternate Maximum Axiai Position Changing RPM Method 2" of this disclosure will disclose a control sequence/method that will limit the "maximum rotating speed at which axiai position changing of a cone is performed” while also providing a safe driving experience and also allowing the driver to use the full power of the engine when needed.
  • Patent # 7,713, 153; Issue Date: May 11 , 2010; Patentee: Naude.
  • Fig. 1 shows a front-view of a CVT 4,
  • Fig. 2 shows a top-view of a CVT 4.
  • Fig. 3 shows another front-view of a CVT 4.
  • Fig. 4 shows another top-view of a CVT 4.
  • Fig. 5 shows a top-view of the preferred CVT 8.
  • Fig. 6 shows front-view of the preferred CVT 6.
  • Fig. 7 shows front-view of a tensioning pulley 14 that is not engaged with its maximum contraction stop 15.
  • Fig. 8 shows a top-view of a CVT 6 that uses an adjuster 8 for each cone.
  • Fig. 9 shows a top-view of a preferred CVT 6 for which the adjusters 8 are each mounted on a different shaft/spline.
  • Fig. 0 shows a schematic diagram for CVT that uses a pre-transmission.
  • Fig. 1 shows a schematic diagram for CVT that uses a post-transmission.
  • Fig. 12 shows a schematic diagram for CVT that uses a pre-transmission and post- transmission.
  • Fig. 13 shows a schematic diagram for Drive System 1.
  • Fig. 4 shows a front-view of a "Tensioning Pulleys Tensioning System".
  • Fig. 15 shows a partial top-view of a "Tensioning Pulleys Tensioning System".
  • Fig. 16 shows a partial sectional-view of a "Tensioning Pulleys Tensioning System".
  • Fig. 17 shows a front-view of a slider mounting plate 20.
  • Fig. 8 shows a side-view of a slider mounting plate 20.
  • Fig. 19 shows a front-view of a slider 21.
  • Fig. 20 shows a side-view of a slider 21.
  • Fig. 21 shows a top-view of a cone 3D on which a marked disk 26 is attached.
  • Fig, 22 shows a front-view of a marked disk 26, marker 27, and a sensor 28.
  • Fig. 23 shows a top-view of a CVT 8 that uses a clutch 29 for each cone.
  • Fig. 24 shows a partial front-view of an adjuster that uses an indexing mechanism.
  • Fig. 25 shows a partial side-view of an adjuster that uses an indexing mechanism.
  • Fig. 26 shows a partial top-view of an adjuster that uses an indexing mechanism.
  • Fig. 27 shows a partial front-view of an adjuster that uses a brake.
  • Fig. 28 shows a partial side-view of an adjuster that uses a brake.
  • Fig. 29 shows a partial top-view of an adjuster that uses a brake.
  • Fig. 30 shows a partial front-view of an adjuster that uses an electric motor.
  • Fig. 31 shows a partial side-view of an adjuster that uses an electric motor.
  • Fig. 32 shows a partial top-view of an adjuster that uses an electric motor.
  • Fig. 33 shows a partial front-view of an adjuster that uses an indexing mechanism which uses a gear train 41.
  • Fig. 34 shows a partial side-view of an adjuster that uses an indexing mechanism which uses a gear train 41 (gear train 41 is not shown).
  • Fig. 35 shows a partial top-view of an adjuster that uses an indexing mechanism which uses a gear train 41 ,
  • a CVT 6 comprises of two substantially identical CVT 4's.
  • the basic configuration of a CVT 4 is described U.S. Patent Application No.: 13/629,613.
  • one CVT 4 is referred to as CVT 4A, and the other CVT 4 is referred to as CVT 4B.
  • the driving cones (which each are a cone with one torque transmitting member and which preferably have the same dimensions) of CVT 4A and CVT 4B are mounted on a common spline through a slider sleeve each (which allow axial but not rotational movements relative to its spline) in manner so that the larger end of one cone is facing the smaller end of the other cone; and the driven cones (which each are also a cone with one torque transmitting member and which also preferably have the same dimensions) of CVT 4A and CVT 4B are also mounted on a common spline through a slider sleeve each (which allow axial but not rotational movements relative to its spline) in manner so that the larger end of one cone is facing the smaller end of the other cone. It is recommended that the axial positions of the driving cones can be changed independent of each other, and that the axial positions of the driven cones can also be changed independent of each other.
  • one of its cones is mounted on its slider sleeve through the use of an adjuster (labeled as adjuster 8 in Fig. 5) that can: a) provide/allow rotational adjustment between its cone and the spline on which it is mounted when needed; and b) prevent any rotational movements between its cone and the spline on which it is mounted when needed.
  • an adjuster labeled as adjuster 8 in Fig. 5
  • the adjuster that uses a gear that is driven by a worm gear, described in US Patent 7,722,490 B2 and U.S. Patent
  • Application No. V 978,456 can be used as the adjusters; and here a cone can be mounted on its spline through the use of an adjuster and a slider sleeve in a similar manner as a transmission pulley of a CVT 2 is mounted on its shaft/sp!ine through the use of an adjuster and a slider sleeve (see US
  • the rotational position sensor that is used to determine the rotational position of that cone needs to be mounted on that cone or a portion that rotates with that cone.
  • the rotational position sensor of a cone is needed to determine/estimate the rotational position of the torque transmitting member of said cone, which is needed to know when to change the axial position of a cone (see U.S. Patent Application #13/889,049).
  • a CVT 6 can also comprise of two substantially identical CVT 4's for which the cones are mounted on shafts instead of splines.
  • the transmission diameter of a cone is changed by changing the axial position of its torque transmitting member and its non- torque transmitting member (if used) while holding still the axial position of said cone; instead of changing the axial position of said cone while holding still the axial position of its torque transmitting member and its non- torque transmitting member (if used) as is the case for a CVT 6 for which the cones are mounted on splines.
  • a CVT 6 can be operated so that the tension in the transmission belt of one CVT 4 can be reduced when desired through the use of the adjusters 8.
  • the adjuster 8 for that CVT 4 allows its cone to rotate relative to its shaft/spline so as to provide a releasing torque, while the adjuster 8 of the other CVT 4 is locked/braked (or provides a slower rotating releasing torque) so that full torque transfer between its cone and its shaft/spline occurs. If the shaft/spline on which an adjuster is mounted is the input shaft spline, than the direction of rotation of its cone for a releasing torque is the direction opposite from the rotation of the input shaft/spline. And if the shaft/spline on which an adjuster is mounted is the output shaft/spline, than the direction of rotation of its cone for a releasing torque is the direction of rotation of the output shaft/spline.
  • the duration that a releasing torque is provided/allowed by an adjuster before axial position changing of its cone is started can be based on a "set time duration".
  • the ideal "set time duration" can be obtained through experimentation. For example, let's say we select the "set time duration" to be 1 second; here if this duration is sufficient for the adjuster to sufficiently reduce the tension in the transmission belt for all operating conditions/situations, than 1 second can be used as the "set time duration" for that adjuster, or if desired further experiments can be performed in order to obtain a smaller "set time duration”; and if 1 second does not allow the adjuster to sufficiently reduce the tension in the transmission belt for all driving conditions, than additional experiment(s) with larger than 1 second "set time duration(s)" need to be performed until a "set time duration" that allows the adjuster to sufficiently reduce the tension in the transmission belt for all driving conditions is obtained.
  • axial position changing of said cone can be started.
  • the adjuster 8 stops providing/allowing a releasing torque and is stopped/locked or used for other purposes.
  • proper coordination can be performed by a controlling computer that controls the axial position changing of said cone, and the adjuster 8 that provides/allows the releasing torque.
  • torque sensor(s) can also be used to determine when the tension in a transmission belt is sufficiently reduced so that axial position changing of a cone can be started.
  • an adjuster 8 that uses a motor can eventually stall or slip.
  • the torque of the adjuster 8 motor is limited so that it will be enough to release the tension in the pulling side of the transmission belt of its cone, but not large enough to significantly increase the tension in the slack side of the transmission belt.
  • Transmission ratio change rotation has to be “allowed” or “compensated for during axial position change of a cone relative to its transmission belt, otherwise large tension in the transmission belt can develop.
  • adjusters 8 can be used for the adjusters 8, such as an adjuster that uses a worm gear-gear drive that uses a worm gear brake so that its worm gear- gear drive can be made locking or non-locking. Or an adjuster that uses a main gear that is identical to the gear of a worm gear-gear drive that is than coupled directly or through other spur gears to a braking gear (which has more speed but less torque than said main gear) that can be braked as needed. Many other design for an adjuster 8 are also possible.
  • said cone mounted on an adjuster 8 in order to compensate/allow for "Transmission ratio change rotation” of said cone, said cone mounted on an adjuster 8 "needs to be rotated” or “needs to be allowed to rotate” by its adjuster 8 in the direction of the "Transmission ratio change rotation” of said cone during axial position change of said cone relative to its transmission belt, so that said cone can rotate relative to its spline in the direction of its "Transmission ratio change rotation”.
  • the adjuster mounted cone in order to compensate/allow for "Transmission ratio change rotation" of said non-adjuster mounted cone, the adjuster mounted cone to which said non-adjuster mounted cone is coupled and which is mounted on an adjuster 8, "needs to be rotated” or “needs to be allowed to rotate” by adjuster 8 in the direction opposite of the direction of rotation of the "Transmission ratio change rotation” of said non-adjuster mounted cone during axial position change of said non-adjuster mounted cone relative to its transmission belt.
  • This is performed so as to provide or remove slack as needed in the tense side and slack side of the transmission belt of said non-adjuster mounted cone so as to compensate for "Transmission ratio change rotation”.
  • the direction of "Transmission ratio change rotation” of a cone can depend on the configuration of the CVT 4's of the CVT 8, the axial movement of said cone ("increasing transmission diameter change of said cone” or “decreasing transmission diameter change of said cone"), and the rotational position of said cone.
  • the direction of "Transmission ratio change rotation” of a cone for ail possible cases can be easily determined through experimentation (there are only two possible directions for ail cases).
  • An experiment to determine the direction of "Transmission ratio change rotation” of the cone(s) of a CVT 6 can be made by using a Test CVT.
  • a Test CVT can be a CVT 6 for which the cones are mounted so that they can each be set to either "freely rotate relative to the shaft/spline on which they are mounted” or “locked relative to the shaft/spline on which they are mounted”.
  • "Transmission ratio change rotation" of a cone for a given axial movement and a given rotational position can be easily be observed by first allowing said cone to "freely rotate relative to the shaft/spline on which if is mounted” while keeping all other cones “locked relative to the shaft/spline on which they are mounted”, and then changing the axial position of said cone and observing the rotation due to it.
  • the "Transmission ratio change rotation” for ail axial movements and ail rotational positions of a cone can be determined for all cones.
  • the direction of rotation of "Transmission ratio change rotation” of a cone depends on the rotational position of said cone relative to its transmission belt. If so, this depends on where the neutral point (referred to as Point N) is positioned relative to the Point M of its cone.
  • Point N is the contact point between a cone and its transmission belt that doesn't substantially rotate/move due to changes in the transmission diameter of said cone.
  • Point M of a cone is the point were no rotational sliding between said cone and its torque transmitting member occur due to axial position change of said torque transmitting member relative to said cone. See US Patent 7,722,490 B2 for detailed explanation regarding this.
  • the axial position of said cone can be changed during an interval where changes in the direction of rotation of "Transmission ratio change rotation” of said cone occur.
  • One method to allow axial position change of a cone during an interval where changes in the direction of rotation of "Transmission ratio change rotation” of said cone occur is by using motorized adjusters 8 and having both adjusters 8 of the cones that are mounted on the same spline/shaft rotate in the same direction (preferably faster than required) during axial position change of one of said cones or a cone to which said cones are coupled. This allows/compensates for clockwise and counter-clockwise
  • Another method to allow axial position change of a cone during an interval where changes in the direction of rotation of "Transmission ratio change rotation” of said cone occur is by using a configuration of a CVT 6 where ail cones are mounted on an adjuster (see Fig. 8), and for the CVT 4 for which the axial position of a cone is changed, having the adjusters 8 of the cone on the input shaft/spline and the adjuster 8 of the cone on the output shaft/spline rotate in the same direction during axial position change of said cone.
  • one adjusters 8 allows/compensates for "Transmission ratio change rotation” in one direction and the other adjusters 8 allows/compensates for "Transmission ratio change rotation” in the other direction.
  • the torque of the adjusters 8 should be limited so that they only allow “Transmission ratio change rotation” in the direction they are rotating.
  • the direction of rotation of the adjusters 8 (besides rotating in opposite directions) should be in the direction such that at least one cone of the CVT 4 for which the axial position of a cone is changed is rotated in the direction "the cone needs to rotate” or “the cone will need to rotate after its axial position is changed” due to having cones of different diameters mounted on the same shaft/spline; here the adjusters 8 can simply stall or slip when their rotation are not needed.
  • This method is referred to as the "Active adjusters on the same CVT method".
  • the tension in the transmission belt for which the tension was reduced and for which the axial position of its cone(s) is changed can significantly increase due to "Transmission ratio change rotation”. Unless it can be ensure that this is not happening under all operating conditions of the CVT 6, the "Active adjusters on the same CVT method” is preferred over the “Active adjusters on the same shaft method", since otherwise there is no advantage in reducing the tension in a transmission belt.
  • Transmission ratio change rotation can be attributed to: a) “belt curvature change rotation”, which is rotation due to longitudinal movements of the slack side and/or tense side of a transmission belt relative to its cone in order to provide/remove slack due to changes in the transmission diameter of its cone; and b) “member curvature change rotation”, which is rotation due to changes in the curvature of the torque transmitting member of the cone which axial position is changed.
  • Transmission ratio change rotation which is due to "belt curvature change rotation” and “member curvature change rotation” is two teeth.
  • the angular distance of two teeth depends on the total amount of teeth width of the transmission circumference. If the transmission circumference of a cone is 20 teeth, then the angular distance of two teeth is 2/20 times 380 deg. This angular distance has to be covered during the axial position changing interval of said cone. From this theory, a ball park estimate for the required rotational speed and angular acceleration of the adjusters 8 for the most demanding operating condition (which should occur when the axial position changing interval duration of a cone is shortest and the transmission circumference of a cone is smallest) of the CVT 6 can be obtained.
  • This bail park estimate and trial-and-error experimentation can then be used to obtain the actual minimum required rotational speed and angular acceleration of the adjusters 8 that allows for axial position change of ail cones without interruption due to "Transmission ratio change rotation" for all operating conditions of the CVT 6.
  • Transmission ratio change rotation due to "belt curvature change rotation” in the slack side portion of the transmission belt can also be compensated by having the tensioning pulley/support pulley on the slack side of the transmission belt provide and remove slack in the slack side of the transmission belt as needed in order to compensate for "Transmission ratio change rotation” due to "belt curvature change rotation” in the slack side of the transmission belt.
  • a tensioning pulley/support pulley on the slack side of the transmission belt is shown in Fig. 6 where it is labeled as Tensioning Pulley 13.
  • a tensioning pulley/support pulley on the tense side of the transmission belt that provides and removes slack in the tense side of the transmission belt as needed in order to compensate for "Transmission ratio change rotation” "due to "belt curvature change rotation” in the tense side of the transmission belt can also be used.
  • the term tensioning pulley/support pulley is used to specify that the pulley is used for “tensioning its transmission belt” and for “supporting the shape of its transmission belt in manner as to ensure that a portion of a torque transmitting member of its cone is always engaged with its transmission belt”.
  • the tense side tensioning memeley/support pulley can be designed so that if only provides and removes slack when the tension in its transmission belt has been reduced.
  • a maximum contraction stop which engages with the tense side tensioning pulley/support pulley and stops the movement of the tense side tensioning memeley/support pulley when the tension in the transmission belt is not reduced, can be used.
  • the tense side tensioning pulley/support pulley is pushed away from its maximum contraction stop by its tensioning force, which can be provided by spring(s), weight(s), etcetera; and this should give the tense side tensioning memeley/support pulley a "contracting and extending movements range" that can be used to provide and remove slack when required.
  • the contracting movements range allow the tense side tensioning pulley/support pulley to move away from its transmission belt
  • the extending movements range allow the tense side tensioning memeley/support pulley to move towards from its transmission belt.
  • FIG. 6 A front-view of a CVT 4 that uses slack side tensioning memeley/support pulley and a tense side tensioning memeley/support pulley is shown in Fig. 6.
  • Fig. 8 the slack side tensioning pulley/support pulley is labeled tensioning pulley 13
  • the tense side tensioning pulley/support pulley is labeled tensioning pulley 14
  • Tensioning pulley 4 is also shown in Fig. 7.
  • tensioning pulley 14 is engaged with its maximum contraction stop 15 since the tension in its transmission belt has not been reduced
  • tensioning pulley 14 is not engaged with its maximum contraction stop 15 since the tension in its transmission belt has been reduced.
  • tensioning pulley 13 can have the same directions. If desired other directions of the contracting and extending movements of the tensioning pulleys can be used, such as diagonally for example, since the directions of the contracting and extending movements of the tensioning pulleys can be any directions that can remove and provide transmission belt slack. It is also recommended that the slack side tensioning pulley/support pulley (labeled as tensioning pulley 13 in Fig. 6 also has a maximum contraction stop 15.
  • the maximum contraction stop can be used to prevent excessive contracting movement of the slack side tensioning pulley/support pulley due to increase in tension in the slack side of its transmission belt, which can be due to a releasing torque provide by its adjuster(s) 8 or due to rotations of its cone(s) due to having to compensate for having cones of different diameters mounted on the same shaft/spline.
  • the contracting and extending movements of the pulleys can “compensate for Transmission ratio change rotation” and can “compensate for having cones of different diameters mounted on the same shaft/spline during axial position changing of a cone”; in addition to “accommodating for the transmission diameter change of a cone”. If the transmission belts of a CVT 6 are removed, then "changing the axial position of a cone of a shaft/spline while not changing the axial position of the other cone of that shaft/spline" or "having cones with different
  • both a slack side tensioning puliey/support pulley and a tense side tensioning pulley/support pulley are used, the tensioning forces of the pulleys should be balanced such that when the tension in the transmission belt has been reduced, both pulleys are positioned so that they have a sufficient “contracting and extending movement range” to provide and remove slack as needed to "compensate for Transmission ratio change rotation", to "accommodate for the transmission diameter change of a cone", "to compensate for having cones of different diameters mounted on the same shaft/spline during axial position changing of a cone", and by compensating for any other
  • the tensioning forces of the pulleys are provided by springs, since here slightly unbalanced tensioning forces of the pulleys can be balanced/equaled by slight movements of the pulleys.
  • the required "contracting and extending movement ranges" of the pulleys can be obtained through “trial and error” experimentation; as a conservative estimate that can be refined through “trial and error” experimentation, a movement range that allows for 3 teeth rotation of a cone in both directions can be used.
  • the axial position of a cone should only be changed after the slack side tensioning pulley/support pulley and the tense side tensioning pulley/support pulley have reached their balanced positions.
  • the axial positions of the cones of a CVT 6 are changed in manner such that when there are "cones with different transmission diameters mounted on a same shaft spline", the next axial position change of a cone is always such that the transmission diameters of said "cones with different transmission diameters mounted on a same shaft/spline" are equal. Therefore, since during regular operations (non- “transmission ratio changing” operations) of a preferred CVT 8 the transmission diameters of all cones mounted on the same shaft/spline are equal, there should be only one shaft/spline at a time for which there are "cones with different transmission diameters mounted on a same shaft/spline".
  • one adjuster 8 of a cone (referred to as the rotated cone) needs to "rotate preferably faster than required” or “have its worm gear-gear drive unlocked” in the direction "the rotated cone will need to rotate in order to "compensate for having cones with different transmission diameters mounted on a same shaft/spline" after the axial position of the moved cone is changed".
  • the adjuster 8 can be used to rotate its cone before the axial position of a cone is changed; since this type of adjusters 8 only allows rotation in one direction and here the adjuster 8 can simply stall, slip, or stop when its rotation is "not” or “not yet” needed. If a non-motorized adjuster 8 is used and the rotated cone is not a cone of the "CVT 4 which transmission belt tension has been reduced", then it is recommended that the adjuster 8 is only unlocked immediately after the axial position of a cone has been changed, so that it does not rotate in the direction that reduces the tension in its transmission belt.
  • rotated cone is only “rotated” or “allowed to rotate” in the direction that increases the tension in the tense side of its transmission belt; the selection of whether the rotated cone is a cone that is coupled to the transmission belt which tension was reduced, or a cone that is coupled to the transmission belt which tension was not reduced should depend only on this.
  • the tension in the transmission belt of the "CVT 4 with which the CVT 4 of the rotated cone is alternately used to transfer torque" can be reduced by using one of its adjuster 8 to rotate one of its cone in the direction needed to "compensate for having cones with different transmission diameters mounted on the same shaft" (which is also the direction of rotation for a releasing torque for the "CVT 4 with which the CVT 4 of the rotated cone is alternately used to transfer torque"), so that said rotated cone can be slowed-down and eventually locked by its adjuster 8.
  • the smaller cone needs to be “rotated” or “allowed to rotate” by its adjuster 8 in the direction said common input shaft/spline is rotating; or a cone that is mounted on an output shaft/spline and that is coupled to said smaller cone, needs to be “rotated” or “allowed to rotate” in the opposite direction said output shaft/spline is rotating (here the transmission diameters of the cones mounted said output shaft/spline should be identical).
  • the larger cone needs to be “rotated” or “allowed to rotate” by its adjuster 8 in the opposite direction said common output shaft/spline is rotating; or a cone that is mounted on an input shaft/spline and that is coupled to said larger cone, needs to be “rotated” or “allowed to rotate” in the direction said input shaft/spline is rotating (here the
  • the transmission diameters of all cones mounted on a same shaft/spiine should be equal so that there is no need to have an adjuster 8 "compensate for having cones with different transmission diameters mounted on a same shaft/spiine"; so that the active/unlocked adjuster 8 can simply be stopped/braked/" locked when possible".
  • the transmission belt of the cone which axial position is to be changed due to changes in the transmission diameter of the cone which axial position is changed (which occurs when the transmission diameter for a cone mounted on the input shaft/spline is increased, or when the transmission diameter for a cone mounted on the output shaft/spline is decreased), the contracting and extending movements of the slack side tensioning pulley/support pulley and the tense side tensioning pulley/support pulley should be able to "compensate for having cones with different transmission diameters mounted on a same shaft/spline" during axial position changing of a cone.
  • the tension in the transmission belt of a "CVT 4 for which the transmission belt tension was reduced” can be increased by rotating a cone of the other CVT 4 in the direction that reduces its transmission belt tension, and if necessary siowing-down and eventually locking all cones of said "CVT 4 for which the transmission belt tension was reduced". Since increasing the tension in the transmission belt of one CVT 4 reduces the tension in the transmission belt of the other CVT 4.
  • the "preferred transmission ratio changing procedure for a CVT 6" that can be used to reduce the torque requirements of the adjusters (adjusters 8) of a preferred CVT 6 is described.
  • the torque requirements of the adjuster motors can be reduced to a level where the adjuster motors only need sufficient torque to unlock their worm gear-gear drives (the worm gear-gear drives of their adjusters) when needed and sufficient torque (braking torque if necessary) to relock their worm gear-gear drives when they are "slowing-down and about to change their direction of rotation”.
  • the adjuster motors are assisted by the "static locking friction" of their worm gear-gear drives, and during unlocking the adjuster motors need to overcome the "static locking friction" of their worm gear-gear drives.
  • An adjuster is mounted on a shaft/spline and is used to controliabiy lock and unlock a cone mounted on it. When an adjuster is locked, it does not allow relative rotation between its cone and the shaft/spline on which it is mounted; and when an adjuster is unlocked, it allows relative rotation between its cone and the shaft/spline on which it is mounted.
  • An example of an adjuster is an adjuster that comprises of a housing that can be mounted on a shaft/spline in a manner so that it is fixed for rotation relative to said shaft/spline. Attached to said housing are a worm gear, an adjuster motor that can rotate said worm gear directly or through means for coupling (coupling gears, etc), and a gear that engages with said worm gear.
  • said gear When said worm gear is rotating, said gear rotates relative to said housing. Attached to said gear is an output shat that is used to attach the cone of the adjuster, in a manner so that the rotation of said gear can be used to rotate said cone relative to its shaft/spline. Also, an adjuster motor should also be able to rotate at a sufficient speed to keep its worm gear-gear drive unlocked. See the "Adjusters for a CVT 6" section for additional details for an adjuster.
  • An unlocked adjuster should allow rotation at the speed required even when the "speed its adjuster motor rotates its adjuster output shaft/spline" is less than the "speed applied on its adjuster output shaft/spline (such as due to transmission ratio change rotation, having cones of with different diameters mounted on the same shaft/spline, etc.)".
  • the worm gear-gear drive should be selected such that: a) the static friction of the worm gear-gear drive is large enough to have the worm gear-gear drive be self-locking; and b) the dynamic (rotating) friction of the worm gear-gear drive is not be large enough to have the worm gear-gear drive be self-locking.
  • the worm gear-gear drive can also be selected such that: a) the static friction of the worm gear-gear drive is large enough to have the worm gear-gear drive be self-locking; and b) the dynamic friction of the worm gear-gear drive at "the rotating speed of the worm gear as can be provided by the adjuster motor” is not be large enough to have the worm gear- gear drive be self-locking (here the dynamic friction of the worm gear-gear drive at a rotating speed of the worm gear that is slower than "the rotating speed of the worm gear as can be provided by the adjuster motor” can still be self-locking; but at speeds “equal to and higher” than "the rotating speed of the worm gear as can be provided by the adjuster motor", the worm gear-gear drive should not be self-locking).
  • the adjuster motor should be operated so that it will not add resistance that will stop the released adjuster from being released, as can occur in situations where the cone of an adjuster needs to rotate at a higher speed than the speed that can be supplied by its adjuster motor (released means being able to rotate at any speed required).
  • the adjuster motor is operated so as to provide as little rotating resistance as possible when its speed is slower than the speed of its cone, if a brushed electric motor is used as the adjuster motor, it might be desirable to leave it ON, since the switching of the poles are controlled by the rotation of the rotor. And if a brushiess electric motor is used as the adjuster motor, it might be desirable to turn it off, since the switching of the poles are controlled by an electric motor controller and not the rotation of the rotor.
  • a rotation sensor or a rotational speed sensor that measures the rotation or rotational speed of the worm gear can be used to turn an electric motor off "once an adjuster is released” or "once an adjuster is released and once the worm gear has reached a pre ⁇ set rpm speed”.
  • an external motor (which avoids the speed reduction gearing of the worm gear-gear drive of the adjuster) can be used to rotate the cone of an adjuster as required.
  • an adjuster can also be designed so that the "kinetic locking friction force" of its worm gear-gear drive is never less than the rotational force applied to its adjuster output shaft. Since here the adjuster will not allow free rotation at any speed required, its adjuster motor needs to be able rotate its adjuster output shaft at the speed required or faster for all operating conditions of its CVT,
  • a brake can be used instead of using an adjuster motor to controilably lock and unlock an adjuster.
  • the brake applies braking friction (directly or through means for coupling such as gears, etc.) to the shaft of the worm gear of the worm gear-gear drive; and when an adjuster needs to be unlocked, the brake does not apply braking friction to the shaft of the worm gear of the worm gear-gear drive, if desired, a brake can also be used in conjunction with an adjuster motor to controilably lock and unlock an adjuster.
  • a brake If a brake is used by itself, then the brake needs to be able to provide sufficient braking that prevents a worm gear-gear drive from becoming unlocked for ail regular operating conditions of its CVT.
  • the worm gear-gear drive itself should not be self- locking, since if needs to be unlocked when the brake is released.
  • a brake can comprise of a braking disk that is coupled directly or through means for coupling to the shaft of the worm gear of the worm gear-gear drive, and a braking shoe that is pushed towards the braking disk by a spring and that can be controilably pulled away from the braking disk by a solenoid.
  • the brake and the adjuster motor should be selected so that they can lock and unlock their adjuster as needed for all regular operating conditions of their CVT.
  • an indexing mechanism that can be controilably locked and unlocked can be used instead.
  • the indexing mechanism can comprise of an index wheel with cavities, which is coupled directly or through means for coupling to the shaft of the worm gear of the worm gear-gear drive, and a locking mechanism for controilably locking and unlocking the index wheel.
  • Said locking mechanism can comprise of a lock that can be inserted into a cavity of the index wheel, wherein said lock is pushed towards said index wheel by a spring and wherein said lock can be controilably pulled out of an index wheel cavity by a solenoid.
  • the worm gear-gear drive of the adjuster should not be self- locking, since it needs to be unlocked when the indexing mechanism is unlocked. If desired an indexing mechanism by itself, without a worm gear-gear drive can be used to controllably lock and unlock an adjuster. But for this design, the force needed to unlock an adjuster are most likely larger; and the shock-loads during relocking of an adjuster are also most likely larger.
  • the indexing mechanism used here can comprise of an index wheel with cavities that is coupled directly or through means for coupling to the output shaft of its adjuster, which is the shaft that is fixed for rotation relative to the cone of said adjuster; and a locking mechanism for controllably locking and unlocking the index wheel, which is fixed for rotation relative to the spline/shaft of the cone of said adjuster.
  • Said locking mechanism can comprise of a lock that can be inserted into a cavity of the index wheel, wherein said lock is pushed towards said index wheel by a spring and wherein said lock can be controllably pulled out of an index wheel cavity by a solenoid.
  • an adjuster of a cone is to either "lock the rotational position of said cone relative to its spline/shaft" or “unlock said cone for rotation in the direction it is being pulled by its transmission belt relative to its spline/shaft".
  • the process of using an adjuster that uses an adjuster motor, a brake, or an indexing mechanism are basically identical. But, while an adjuster that uses an adjuster motor can lock itself once the speed of its worm gear has reduced to a speed where the friction of the worm gear-gear drive has sufficiently increased, an adjuster that uses a brake or an indexing mechanism has to be controllably locked. An adjuster should only be controllably locked once "the rotation it allows" is not needed anymore.
  • a preferred CVT 6 (a CVT 8 is a CVT that uses two substantially identical CVT 4's, see Figs. 5 and 9 for examples) is a CVT 8 that uses one adjuster for each CVT 4 (it doesn't matter on which shaft/spline of their CVT 4 the adjusters are mounted); and a CVT 6 for which each CVT 4 has both a slack side tensioning pulley/support pulley and a tense side tensioning pulley/support pulley (see Fig. 8).
  • the slack side tensioning pulleys/support pulleys and the tense side tensioning pulleys/support pulleys have sufficient (preferably slightly more, to prevent exhaustion of their ability to provide and remove slack during axial position changing of a cone of their CVT) "contracting and extending movement ranges" to provide and remove slack (slack throughout this disclosure refers to transmission belt slack) needed to allow for axial position changing of a cone of their CVT for all operating conditions of their CVT even when no adjuster is active, by "compensating for Transmission ratio change rotation, by "accommodating for the transmission diameter change of a cone”, by “compensating for having cones of different transmission diameters mounted on the same shaft/spline", and by compensating for any other rotations/needs that might occur during axial position changing of their cone.
  • a tense side tensioning pulley/support pulley (labeled as 14 in Fig. 6) can be designed such that it can only provide and remove slack when the tension in its transmission belt has been reduced.
  • a maximum contraction stop (labeled as 15 in Fig. 6), which engages with the tense side tensioning puliey/support pulley (labeled as 14 in Fig. 6) and stops the movement of the tense side tensioning
  • the tense side tensioning pulley/support pulley when the tension in the transmission belt is not reduced, can be used.
  • the tense side tensioning pulley/support pulley should be pushed away from its maximum contraction stop by its tensioning force (as shown as in Fig. 7); and this should give the tense side tensioning puliey/support pulley a "contracting and extending movements range" that can be used to provide and remove slack when required.
  • both the slack side tensioning pulley/support pulley and the tense side tensioning pulley/support pulley have each a “maximum contraction stop”.
  • the “maximum contraction stops” should be used to limit the movements of the tensioning pulleys/support pulleys to a range that allows for proper operation.
  • tensioning forces of the tensioning pulleys/support pulleys are provided by compression springs, which tensioning forces increase as they are compressed more. Since here slightly unbalanced tensioning forces of the tensioning pulleys/support pulleys can be balanced/equaled by slight movements of the tensioning pulleys/support pulleys.
  • the larger tensioning force of the spring of the tense side tensioning puliey/support pulley can reduce the compression in the spring of the tense side tensioning puliey/support pulley and increase the compression in the spring of the slack side tensioning pulley/support pulley until the tensioning pulleys/support pulleys have reached their equilibrium position.
  • tensioning springs or other tensioners for which their transmission belt tensioning force increase as their "available contraction distance" is reduced can also be used.
  • the "available contraction distance" of a tensioning pulley/support pulley is the distance a tensioning pulley/support pulley can be moved towards its “maximum contraction stop” (see Fig, 6), and it determines the amount of slack that can be provided by that tensioning pulley/support pulley when needed.
  • the stiffness of the tensioners of the tensioning pulleys/support pulleys, the ranges of the tensioning pulleys/support pulleys, and the parameters (torque, speed, unlocked frictional resistance, etc.) of the adjusters should be selected so that when the tension in their transmission belt has been reduced, the tense side tensioning pulley/support pulley and the slack side tensioning pulley/support pulley each have a sufficient “contracting and extending movement range” to provide and remove slack as needed to allow for axial position changing of a cone for ail operating conditions of their CVT without excessively stretching a transmission belt, by "compensating for Transmission ratio change rotation”, by “accommodating for the transmission diameter change of a cone”, by “compensating for having cones of different transmission diameters mounted on the same shaft/spline",
  • the tensioning pulleys/support pulleys can each be mounted on a spring loaded vertical slider.
  • a spring loaded vertical slider can comprise of a vertical slider that allows for sufficient vertical movements as required, and a spring that provides sufficient tensioning forces as required. If the tensioning pulleys/support pulleys are also to be allowed to move horizontally, the spring loaded vertical sliders can each be mounted on a horizontal sliders; or the spring loaded vertical sliders can each have slotted holes into which the shafts of tensioning pulleys/support pulleys are inserted and fastened using bolts or locking rings, as partially shown in Fig. 6.
  • tensioning pulleys/support pulleys moves vertically as required is shown and described in the "Detailed Design for Tensioning Pulleys Tensioning System".
  • the tensioning forces for the tensioning pulleys/support pulleys can also be provided by elastomers, pneumatics/hydraulics (such as through linear actuators for example), etc.
  • the adjuster needs to rotate its cone relative to its shaft/spline so as to provide a releasing torque
  • the shaft/spline on which an adjuster is mounted is the input shaft/spline
  • the direction of rotation of its cone for a releasing torque is the direction opposite from the rotation of the input shaft/spline.
  • the shaft spline on which an adjuster is mounted is the output shaft/spline
  • the direction of rotation of its cone for a releasing torque is the direction of rotation of the output shaft/spline.
  • step c First axial position changing of a cone
  • step c First axiai position changing of a cone
  • the "tension of the tensioning pulleys/support pulleys” can be selected independently from the “rotational frictional resistance of the worm gear-gear drive of the adjuster”. But here, unlike the set-up of the previous paragraph, the adjuster is locked while it is transmitting torque; as such, if the set-up of the previous paragraph can be easily achieved, it is recommended.
  • the index wheel of an adjuster is locked during axial position changing of a cone, otherwise it has to be locked after axial position changing of a cone has been completed.
  • an unlocked index wheel of an adjuster should be able to get locked when its cone has rotated less than 1/4 of a tooth width of said cone.
  • a speed increasing gear train (such as a larger gear coupled to a smaller gear for example) can be used to couple the rotation of the worm to the index wheel.
  • a speed increasing gear train will also reduce the torque at the index wheel, which is desirable.
  • Another approach to reduce the amount of rotation required to lock an unlocked index wheel is by using several index wheels that are constrained relative to each other for rotation (such as by stacking several index wheels to common shaft) and that are rotationaily offset relative to each other; wherein each index wheel has its own lock, ail locks are forced toward their index wheel at the same time, and only one index wheel is fully locked at any instance.
  • Step b) Reducing transmission belt tension in order to avoid changes in the “contracting and extending movement ranges” of the “tensioning pulleys/support pulleys for which the tension in their transmission belt has been reduced” due to slight differences in the transmission diameters of the cones mounted on same shaft/spline or any other factors.
  • step c First axial position changing of a cone
  • step b) Reducing transmission belt tension If the "adjuster of the rotated cone” is the adjuster that is used to reduce the tension in the transmission belt of "the CVT 4 for which the axial position of a cone is to be changed", which was performed in the previous step ("step b) Reducing transmission belt tension"), then the adjuster does not have to be locked after it was used to reduce the tension in the transmission belt of "the CVT 4 for which the axial position of a cone is to be changed".
  • the “adjuster of the rotated cone” is the adjuster of "the CVT 4 for which the axial position of a cone is to be changed”.
  • the "adjuster of the rotated cone” is not the adjuster that is used to reduce the tension in the transmission belt of "the CVT 4 for which the axial position of a cone is to be changed"; then here “immediately after the axial position of a cone (referred to as the moved cone) has been changed", the “adjuster of the rotated cone” should be unlocked so that it can “compensate for having cones with different transmission diameters mounted on a same shaft/spline" after the axial position of the moved cone is changed”; unless motorized adjusters are used in which case the “adjuster of the rotated cone” can be unlocked before the axial position of a cone is changed (see below).
  • the adjuster used to reduce the tension in the transmission belt of "the CVT 4 for which the axial position of a cone is to be changed" is not locked yet, it should be locked first before the “adjuster of the rotated cone” is unlocked, unless motorized adjusters are used (see below); since here this is one requirement to ensure that at least one CVT 4 is always used for torque transmission.
  • pulley/support pulley of the CVT 4 for which the axial position of a cone is to be changed hits its maximum contraction stop can be used to inform the controlling computer when to lock the "adjuster of the rotated cone”; but if the "duration for the slack in the tense side tensioning pulley/support pulley of the CVT 4 for which the axial position of a cone Is to be'/'was' changed to exhaust" is insignificant, it might be more practical to ignore this requirement even if it is desired to have at least one CVT 4 always used for torque transmission.
  • Another potential benefit of using a "sensor that informs the controlling computer when the tense side tensioning pulley/support pulley of the CVT 4 for which the axial position of a cone is to be changed hits its maximum contraction stop" for unlocking the "adjuster of the rotated cone” is that through its usage sudden increase in tension in the transmission belts can be minimized.
  • the "adjuster that was used to reduce the tension in the transmission belt of the CVT 4 for which the axial position of a cone is to be changed” is locked during axial position changing of a cone (so as to avoid shock loads due to locking under load), if this is not practical (such as because the friction in the adjusters is too large to be sufficiently rotated by the tension of the tensioning
  • the "adjuster that was used to reduce the tension in the transmission belt of the CVT 4 for which the axial position of a cone is to be changed" can only be locked after the slack in the tense side tensioning pulley/support pulley of the CVT 4 for which the axial position of a cone Is to be'/'was' changed" is exhausted.
  • a “sensor that informs the controlling computer when the tense side tensioning pulley/support pulley of the CVT 4 for which the axial position of a cone is to be changed hits its maximum contraction stop” or better yet a “sensor that informs the controlling computer when the adjuster that was used to reduce the tension in the transmission belt of the CVT 4 for which the axial position of a cone is to be changed is locked” is used to inform the controlling computer when to unlock the "adjuster of the rotated cone”.
  • a motorized adjuster which is an adjuster that uses an adjuster motor
  • the adjuster motor should rotate the rotated cone in the direction "the rotated cone will need to rotate in order to "compensate for having cones with different transmission diameters mounted on a same shaft/spline" after the axial position of the moved cone is changed”; here the adjuster motor can simply stall or slip when its rotation is "not” or “not yet” needed.
  • a motorized adjuster only allows rotation in the direction its adjuster motor rotates (so that it does not allow rotation in the direction that reduces the tension in its transmission belt in situations where "the adjuster of the rotated cone is not the adjuster that is used to reduce the tension in the transmission belt of the CVT 4 for which the axial position of a cone is to be changed"), and can simply stall, slip, or stop when its rotation is "not” or “not yet” needed. It is recommended that in situations where "the adjuster of the rotated cone is not the adjuster that is used to reduce the tension in the transmission belt of the CVT 4 for which the axial position of a cone is to be changed", a motorized adjuster is unlocked before the axial position of a cone is changed.
  • the adjuster should be released/unlocked.
  • the rotated cone should be a cone which needs to be rotated in the direction that increases the tension in the tense side of its transmission belt in order to
  • the CVT 4 for which a cone (the rotated cone) has to be "unlocked for rotation” in the direction that increases the tension in the tense side of its transmission belt in order to "compensate for having cones with different transmission diameters mounted on a same shaft/spline” is a CVT 4 for which its cone on the input shaft/spline has the smaller transmission diameter relative to the other cone on the input shaft /spline after the axial position changing of a cone of "step c) First axial position changing of a cone” has been completed, or a CVT 4 for which its cone on the output shaft/spline has the larger transmission diameter relative to the other cone on output shaft/spline after the axial position changing of a cone of "step c) First axial position changing of a cone” has been completed.
  • the cone's direction of rotation that increases the tension in the tense side of its transmission belt is in the direction of rotation of the input shaft/spline.
  • the cone's direction of rotation that increases the tension in the tense side of its transmission belt is in the direction opposite from the rotation of the output shaft/spline.
  • step c First axial position changing of a cone of this step is performed. Axial position changing of a cone of this step is performed on a cone (referred to as the moved cone) of "the CVT 4 for which the transmission belt tension was reduced (due to a releasing torque)"; note: transmission belt tension was reduced in step b).
  • the transmission diameter of the cone on the input shaft /spline can be decreased or the transmission diameter of the cone on the output shaft /spline can be increased.
  • the transmission diameter of the cone on the input shaft /spline can be increased or the transmission diameter of the cone on the output shaft /spline can be decreased.
  • the CVT 4 for which a cone has to be "unlocked for rotation” in the direction that increases the tension in the tense side of its transmission belt in order to "compensate for having cones with different transmission diameters mounted on a same shaft/sp!ine" (which is the CVT 4 of the rotated cone) is the “CVT 4 for which the transmission belt tension is reduced (due to required tensioning compensating rotation)" after the axial position changing of a cone of this step (“step c) First axial position changing of a cone") has been completed; since for this CVT 4, a cone has to be “allowed to rotate rotated” in the direction that increases the tension in the tense side of its transmission belt in order prevent an excessive increase in tension in the transmission belt of the other CVT 4, and since the torque capacity of an adjuster motor (if used) should be much smaller than the pulling torque of its CVT 6 under all operating conditions so that an adjuster motor will stall/slip before it can increase the tension in its transmission belt to above the pulling torque of its CVT 8. d
  • step c) First axial position changing of a cone if desired the axial position of a cone of the "CVT 4 for which the transmission belt tension is reduced (due to required tensioning compensating rotation)" can be changed; this axial position changing of a cone is referred to as “step d) Second axial position changing of a cone Option 1 of 2",
  • step e) Second axial position changing of a cone Option 2 of 2 (which is described below) can be performed instead of “step d) Second axial position changing of a cone Option 1 of 2”.
  • the "CVT 4 for which the transmission belt tension is reduced (due to required tensioning compensating rotation)" is the CVT 4 of the rotated cone (see step c).
  • the rotated cone is the cone that is unlocked so that it can rotate in the direction that increases the tension in the tense side of its transmission belt in order to "compensate for having cones with different transmission diameters mounted on a same shaft/spline" relative to its shaft/spline.
  • step c) First axial position changing of a cone If the "CVT 4 for which the transmission belt tension is reduced (due to required tensioning compensating rotation)" is not the CVT 4 for which the axial position of a cone was changed in "step c) First axial position changing of a cone", then the transmission belt tension in the "CVT 4 for which the transmission belt tension is reduced (due to required tensioning compensating rotation)" is reduced after "step c) First axial position changing of a cone” has been completed, and after the slack in the tense side tensioning pulley/support pulley of the CVT 4 for which the axial position of a cone was changed has been exhausted.
  • the slack side of the transmission belt (which is the slack side of the transmission belt during regular torque transmission) becomes the tense side of the transmission belt
  • the tense side of the transmission belt (which is the tense side of the transmission belt during regular torque transmission) becomes the slack side of the transmission belt
  • tensioning forces and the movement ranges of the tensioning pulleys/support pulleys should be selected so that once the tense side tensioning pulley/support pulley and the slack side tensioning pulley/support pulley have reached their equilibrium positions, the tense side tensioning pulley/support pulley and the slack side tensioning pulley/support pulley each have a sufficient "contracting and extending movement range" to provide and remove slack as needed to allow for axial position changing of their cone during axial position changing of their cone.
  • the torque of the adjuster motor and the tensioning forces and movement ranges of the tense side tensioning pulley/support pulley and the slack side tensioning pulley/support pulley should also be selected so that once the tense side tensioning pulley/support pulley and the slack side tensioning pulley/support pulley have reached their equilibrium positions, the tense side tensioning pulley/support pulley and the slack side tensioning pulley/support pulley each have a sufficient "contracting and extending movement range” to provide and remove slack as needed to allow for axial position changing of their cone.
  • a configuration where the slack side tensioning pulley/support pulley hits its maximum contraction stop can occur when the adjuster that is used to provide/allow compensating rotation is unlocked but the "speed its adjuster motor (when used) rotates its adjuster output shaft" is less than the "speed applied on its adjuster output shaft”; since here the unlocked cone is rotated relative to its shaft/sp!ine due to the increased pulling tension in the slack side of its transmission belt, which when large enough can cause its slack side tensioning pulley/support pulley to hit its maximum contraction stop.
  • the adjuster of the CVT 4 for which the axial position of a cone is changed is "unlocked for rotation" in the direction that removes slack from the side of the tense side tensioning pulley/support pulley and provides slack to the side of the slack side tensioning pulley/support pulley.
  • the tension in the slack side of the transmission belt for a configuration where the slack side tensioning pulley/support pulley hits its maximum contraction stop will be larger than that of the configuration where the tense side tensioning pulley/support pulley and the slack side tensioning pulley/support pulley each have a sufficient "contracting and extending movement range".
  • An increase in tension in a transmission belt (slack side and/or tense side) will increase the force required to axiaily move a cone that is engaged with said transmission belt.
  • the unlocked cone is rotated relative to its shaft/sp!ine due to the pulling tension in the slack side of its transmission belt, then the worm gear of its adjuster (and as such also the unlocked cone) accelerates from standstill until it has reached its steady state speed. Since the friction in the worm gear-gear drive decreases as the speed of the worm gear increases, the pulling tension in the slack side of its transmission belt decreases as the speed of the worm gear increases. As such, here using a "delay to let the unlocked cone speed-up" before changing the axial position of a cone of the CVT 4 of the unlocked cone, can reduce the force required to axiaily move a cone of the CVT 4 of the unlocked cone.
  • step c) First axial position changing of a cone was on the input shaft/spline; then for “step d) Second axial position changing of a cone Option 1 of 2
  • the transmission diameter of the "cone with the smaller transmission diameter” on the input shaft'spline needs to be increased so that its transmission diameter is equal to the transmission diameter of the other cone on the input shaft/spline.
  • the "cone with smaller transmission diameter” on the input shaft/spline is a cone of the "CVT 4 for which the transmission belt tension is reduced (due to required tensioning compensating rotation)".
  • step c) First axial position changing of a cone was on the output shaft/spline; then for “step d) Second axial position changing of a cone Option 1 of 2
  • the transmission diameter of the "cone with larger transmission diameter” on the output shaft/spline needs to be decreased so that its transmission diameter is equal to the transmission diameter of the other cone on the output shaft/spline.
  • the "cone with larger transmission diameter” on the output shaft/spline is a cone of the "CVT 4 for which the transmission belt tension is reduced (due to required tensioning compensating rotation)".
  • Second axial position changing of a cone Option 1 of 2 After the axial position changing of a cone of "step d) Second axial position changing of a cone Option 1 of 2" has been completed, the adjuster that is used to "compensate for having cones with different transmission diameters mounted on a same shaft/spline" should be (but not necessarily) stopped/braked/'locked when possible", since after the axial position changing of a cone of "step d) Second axial position changing of a cone Option 1 of 2" has been completed, the CVT 8 will be at "step a) initial Setup/Regular Operation Setup", where the transmission diameters of all cones mounted on a same shaft/spline are equal. e) Second axial position changing of a cone Option 2 of 2
  • step c) First axial position changing of a cone instead changing the axial position of a cone of the "CVT 4 for which the transmission belt tension is reduced (due to required tensioning compensating rotation)" under “step d) Second axial position changing of a cone Option 1 of 2
  • step e) Second axial position changing of a cone Option 2 of 2 This axial position changing of a cone is referred to as “step e) Second axial position changing of a cone Option 2 of 2”.
  • compensating rotation is in the direction that increases its transmission belt tension, and the direction of rotation to "compensate for having cones with different transmission diameters mounted on a same shaft/spline" of one CVT 4 should be opposite from that of the other CVT 4.
  • a cone of the "CVT 4 for which the transmission belt tension is not reduced” needs to be “unlocked for rotation” in the direction that reduces the tension in its transmission belt (which is also the direction of rotation to "compensate for having cones with different transmission diameters mounted on a same shaft spline") as long as there are cones with different transmission diameters mounted on the same shaft'spline.
  • an adjuster that uses a brake or an indexing mechanism can be braked/locked after the speed of the worm gear to be braked/locked has slowed down, so as to reduce the shock-loads during braking/locking. If this is desired, then a time delay from when the adjuster of the "CVT 4 for which the transmission belt tension is not reduced” is unlocked until braking/locking of the adjuster of the "CVT 4 for which the transmission belt tension is reduced (due to required tensioning compensating rotation)" occurs can be used. The time delay does not have to be accurate, but for better accuracy, the time delay can be based on the current rpm and transmission ratio of the CVT 8.
  • a sensor that measures the speed of the worm gear to be braked/locked can also be used to reduce the shock-loads during braking/locking.
  • the torque of the adjuster motor and the tensioning forces of the tense side tensioning pulley/support pulley and the slack side tensioning pulley/support pulley should be selected so that once the tense side tensioning pulley/support pulley and the slack side tensioning pulley/support pulley have reached their equilibrium positions, the tense side tensioning puliey/support pulley and the slack side tensioning puliey/support pulley each have a sufficient "contracting and extending movement range" to provide and remove slack as needed to allow for axial position changing of their cone.
  • a configuration where the tense side tensioning pulley/support pulley hits its maximum contraction stop can occur when the adjuster that is used to provide/allow compensating rotation is unlocked but the "speed its adjuster motor (when used) rotates its adjuster output shaft" is less than the "speed applied on its adjuster output shaft”; since here the unlocked cone is rotated relative to its shaft/spline due to the increased pulling tension in the tense side of its transmission belt, which when large enough can cause its tense side tensioning memeiey/support pulley to hit its maximum contraction stop.
  • the tense side tensioning puliey/support pulley can only remove slack and the slack side tensioning puliey/support pulley can only provide slack. But, this can also work here, since here the adjuster of the CVT 4 for which the axial position of a cone is changed, is "unlocked for rotation" in the direction that provides slack to the side of the tense side tensioning pulley/support pulley and removes slack from the side of the slack side tensioning pulley/support pulley.
  • the tension in the tense side of the transmission belt for a configuration where the tense side tensioning pulley/support pulley hits its maximum contraction stop will be larger than that of the configuration where the tense side tensioning pulley/support pulley and the slack side tensioning pulley/support pulley each have a sufficient "contracting and extending movement range".
  • An increase in tension in a transmission belt (slack side and/or tense side) will increase the force required to axialiy move a cone that is engaged with said transmission belt.
  • the unlocked cone is rotated relative to its shaft spline due to the pulling tension in the tense side of its transmission belt, then the worm gear of its adjuster (and as such also the unlocked cone) accelerates from standstill until it has reached its steady state speed. Since the friction in the worm gear-gear drive decreases as the speed of the worm gear increases, the pulling tension in the tense side of its transmission belt decreases as the speed of the worm gear increases. As such, here using a "delay to let the unlocked cone speed-up" before changing the axial position of a cone of the CVT 4 of the unlocked cone, can reduce the force required to axialiy move a cone of the CVT 4 of the unlocked cone.
  • step c) First axial position changing of a cone was on the input shaft/spline; then for “step e) Second axial position changing of a cone Option 2 of 2
  • the transmission diameter of the "cone with larger transmission diameter” on the input shaft/spline needs to be decreased so that its transmission diameter is equal to the transmission diameter of the other cone on the input shaft/spline.
  • the "cone with larger transmission diameter” on the input shaft/spline is a cone of the "CVT 4 for which the transmission belt tension is reduced (due to releasing compensating rotation)".
  • step c) First axial position changing of a cone was on the output shaft/spline; then for “step e) Second axial position changing of a cone Option 2 of 2
  • the transmission diameter of the "cone with smaller transmission diameter” on the output shaft/spline needs to be increased so that its transmission diameter is equal to the transmission diameter of the other cone on the output shaft/spline.
  • the "cone with smaller transm ssion diameter" on the output shaft/spline is a cone of the "CVT 4 for which the transmission belt tension is reduced (due to releasing compensating rotation)".
  • the adjuster that is used to "compensate for having cones with different transmission diameters mounted on a same shaft/sp!ine" should be (but not necessarily) stopped/braked/'locked when possible", since after the axial position changing of a cone of "step e) Second axial position changing of a cone Option 2 of 2" has been completed, the CVT 8 will be at "step a) Initial Setup/Regular Operation Setup", where the transmission diameters of all cones mounted on a same shaft/spline are equal.
  • Point N is the contact point between a cone and its transmission belt that doesn't rotate due to changes in the transmission diameter of said cone; and Point M of a cone is the point were no rotational sliding between said cone and its torque transmitting member occur due to axial position change of said torque transmitting member relative to said cone (see Fig. 8 for an example).
  • the length of the portion of the transmission belt covering the cone has to be increased; and as the transmission diameter of a cone is decreased, the length of the portion of the transmission belt covering the cone has to be decreased.
  • Increasing the length of the portion of the transmission belt covering the cone requires that the portion(s) of the transmission belt to the left and/or to the right of Point N are slid towards Point N so as to provide more slack; this cause relative rotational movement between the surface of the cone and its transmission belt except at Point N.
  • the direction of “belt curvature change rotation” depends on the position of Point M relative to Point N, and whether the transmission diameter of the cone is increased or decreased.
  • "belt curvature change rotation” should be zero; and when Point M is positioned to the left of Point N, the direction of “belt curvature change rotation” should be in the opposite direction from when Point M is positioned to the right of Point N.
  • the location of Point N and the directions of “belt curvature change rotation” can be obtained through experimentations using a Test CVT.
  • the amount of "belt curvature change rotation" of a cone depends on the distance of the Point M of said cone from Point N. If we ignore the rotations of said cone due to the rotations of its CVT 8 (for illustrative purposes let's assume that the CVT 6 of said cone is not rotating), then the length of the transmission belt segment from Point N to Point M remains constant as the axial position of said cone is changed. If this transmission belt segment is longer than more "belt curvature change rotation" will occur during
  • Transmission ratio change rotation of a cone can also be due to the change in curvature of the torque transmitting member of said cone. This type of “Transmission ratio change rotation” is referred to as “member curvature change rotation”.
  • “Member curvature change rotation” occurs when there are portions of a torque transmitting member that are not covered by its transmission belt.
  • the amount of “member curvature change rotation” depends on the distance from “Point M of the torque transmitting member, which must be not covered by its transmission belt, to "the point of engagement between said torque transmitting member and its transmission belt”. "The point of engagement between said torque transmitting member and its transmission belt”, will be referred to as Point E.
  • the direction of “member curvature change rotation” depends on the position of Point M relative to Point E (note: Point M must not covered by its transmission belt), and whether the transmission diameter of the cone is increased or decreased.
  • Point M When Point M is positioned at Point E, “member curvature change rotation” should be zero; and when Point is positioned to the left of Point E, the direction of “belt curvature change rotation” (if it is not zero) should be in the opposite direction from when Point M is positioned to the right of Point E.
  • the directions of “member curvature change rotation” can be obtained through experimentations using a Test CVT.
  • CVT 6 that uses two CVT 4's for which the tensioning pulleys are positioned on the slack side of the transmission belt. And said CVT 6 uses cones that each have the design of a "cone assembly with one torque transmitting member" described in the "Alternate CVT's" section of U.S. Patent
  • the cones on the input shaft/spline have the longitudinal slides mounted ends of their torque transmitting members at the leading end (which is the end of the torque transmitting member that engages first), and the cones on the output shaft/spline have the longitudinal slides mounted ends of their torque transmitting members at the trailing end (which is the end of the torque transmitting member that engages last).
  • the longitudinal slide mounted end of a torque transmitting member is Point M of the torque transmitting member, which is a point of the torque transmitting member which rotational position relative to its cone does not change as the axial position of the torque transmitting member relative to its cone is changed.
  • a CVT 4 of the CVT 6 (a CVT 8 has two functionally identical CVT 4's) of this section is shown as a front-view in Fig. 8. The following labeling are used for Fig. 8: Driving Cone 9, Torque Transmitting Member 9-M1 , Driven Cone 10, Torque Transmitting Member 10-M1 , Input Spline 1 1 , Output Spline 12, Support Pulley 14, Tensioning Pulley 13.
  • Driving Cone 9 and Driven Cone 10 the rotational position of their Point M, which for each cone is located at the end of the torque transmitting member that is mounted to the longitudinal slide, are marked with M; and the rotational position of their Point N, are marked with N.
  • the adjuster 8 of the cone on the input spline and the adjuster 8 of the cone on the output spline of said CVT 4 are rotated in the same direction during the axial position change of a said cone.
  • the ball park rotational speed and angular acceleration of the adjusters 8 can be estimated by assuming that the maximum “belt curvature change rotation" for the portion of the transmission belt to the right of Point N of "half a tooth” has to be compensated/allowed as Point M is rotated from the 12 o'clock position to the 9 o'clock position.
  • the distance that needs to be traveled is "half a tooth”
  • the time the distance needs to be traveled is the time it takes to rotate Point M from the 12 o'clock position to the 9 o'clock position.
  • Tensioning Pulley 13 can also be used to provide and remove slack as needed in order to allow for "Transmission ratio change rotation" due to movements in the slack side of the transmission belt.
  • Tensioning Pulley 13 cannot allow for
  • Tensioning Pulley 13 to allow for "Transmission ratio change rotation” due to “belt curvature change rotation”, so that said distance becomes “one tooth” (which is due to “member curvature change rotation”). This distance is a conservative estimate, since the distance of "one tooth” due to “member curvature change rotation” is covered during the entire duration that the axial position of Driven Cone 10 is changed and not only the “9 to 3 o'clock interval" of Driven Cone 0.
  • the CVT 6 of this example is designed so that the actual distance to compensate for "Transmission ratio change rotation" for the "3 to 12 o'clock interval" of Driven Cone 10 is less than "half a tooth”, if we estimate that the axial position of Driven Cone 10 is changed during an interval from "9 to 12 o'clock", then the "3 to 12 o'clock interval” represents only 1/3 of the total arc length of the "9 to 12 o'clock" interval.
  • each adjuster 8 comprises of an electric motor that drives a worm gear that drives a gear.
  • the Torque (T) i ⁇ angular acceleration.
  • This torque estimate does not include the torque required to overcome friction, this torque can be calculated/estimated separately and added to torque estimate above.
  • the "input/output ratio" of the worm gear-gear drive is not 1 : 1 , then appropriate adjustments need to be made to the calculations of the previous paragraphs in order to determine the ratings for the motors that drive the worm gears of the adjusters 8. it might also be desirable to use some gearings that increase the output speed of said motors, but reduce the output torque of said motors and add additional inertia that needs to be accelerated by said motors.
  • this ball park estimate can then be used to obtain the actual required speed and torque ratings of the adjuster(s) 8 that allow the axial positions of Driving Cone 9 and Driven Cone 10 to be changed without interruption due to "Transmission ratio change rotation" for the maximum operating speed of the CVT, by simply testing the at what minimum speed and minimum torque of the adjuster(s) 8 the axial positions of Driving Cone 9 and Driven Cone 10 can changed without interruption due to "Transmission ratio change rotation" at the maximum operating speed of the CVT.
  • the motors of the adjusters 8 are always ON when the adjusters 8 are needed to compensate/allow for "Transmission ratio change rotation", even when the adjusters 8 are driven by the "Transmission ratio change rotation”; this is to account for sudden decrease in speed and increase in "locking friction" of the worm gear-gear drive.
  • the definition of an unlocked adjuster is an adjuster for which the "worm rotating force" of its worm gear-gear drive is larger than the "worm locking force" of its worm gear-gear drive.
  • a cone that has the longitudinal slide mounted end of its torque transmitting member at the trailing end can be the mirror image of a cone that has the longitudinal slide mounted end of its torque transmitting members at the leading end; except that if non-symmetrical teeth are used, then for both cones the teeth for their torque transmitting members should be oriented so that they can transfer maximum torque in the direction they are primarily used for torque transmission.
  • leading end and trailing end for the ends of the torque transmitting member of the example of a “cone assembly with one torque transmitting member" described in the "Alternate CVT's" section of U.S. Patent 7,722,490 B2 were arbitrarily selected. Obviously the part of a cone referred to as the "leading end” can be used as the leading end of a torque transmitting member (which is the end of a torque
  • the required relative rotation between the cones on a common shaft/spline to compensate for "Transmission ratio change rotation” can also be provided by adjuster(s) 8 of the CVT 4 other then the CVT 4 for which for a cone rotation to allow for
  • the cones of a CVT 6 should be designed so that they can handle the maximum releasing torque and the maximum torque due to the "rotations to compensate for having cones with different transmission diameters mounted on a same shaft/spline".
  • the pulling direction of a releasing torque is in the direction that increases the tension in the slack side of the transmission belt.
  • the pulling direction due to the "rotations to compensate for having cones with different transmission diameters mounted on a same shaft/spline" is in direction that increases the tension in the slack side of the transmission belt when a cone on the input shaft/spline is pulled in the direction its CVT is rotating by the cone to which it is coupled (which should happen occasionally for the preferred CVT 6), and when a cone on the output shaft/spline is pulled in the opposite direction its CVT is rotating by the cone to which it is coupled (which should also happen occasionally for the preferred CVT 6).
  • the pulling direction in the direction that increases the tension in the slack side of the transmission belt is opposite from the main pulling direction of the cones, which is in the direction that increases the tension in the tense side of the transmission belt.
  • the cones of a CVT 6 should be designed such that can transit torque in both directions as required; although the torque capacity in one direction can be larger than the other.
  • the force needed to change the transmission ratio can be reduced by reducing the tension in the transmission belt of the CVT 4 for which the transmission ratio is changed.
  • the transmission ratio of said CVT 4 can be changed by changing the axial position(s) of the driven cone, driving cone, or both driven cone and driving cone of said CVT 4.
  • the same labeling used for Fig. 5 is used for Fig. 8.
  • the rotational position of one cone at a time of a CVT 4 (driving cone or driven cone) can be rotated by the adjusters into a moveable position during parking.
  • the adjusters of the driving cone and driven cone are rotated in a common direction until the cone that was to be rotated into a moveable position is in that position.
  • the required rotational speed of the adjusters might be different, this problem can be solved by simply letting the adjuster that rotates too fast stall, slip, and/or slowdown.
  • Once a cone is in a moveable position its axial position can be changed.
  • the adjusters When parked, during the axial position changing procedure of a cone, the adjusters are not required to provide a releasing torque unless there is tension in the transmission belt that needs to be relieved.
  • tension in transmission belt is unlikely, especially after the adjusters are used to change the rotational positions of the cones.
  • the tension in transmission belt can be relieved by rotating a cone of that transmission belt in both directions, since one direction will be the direction to relieve tension and the torque of the adjusters are limited so that they should not be able significantly increase the tension in a transmission belt in whichever direction they are rotating.
  • the duration of each rotation of the rotations in both directions can be set by a "set time duration" (the earlier description regarding a "set time duration" is also applicable here).
  • adjusters 8 adjusters
  • the adjusters 8 are only used to release tension, compensate/allow for "Transmission ratio change rotation", and "compensate for having cones with different transmission diameters mounted on a same shaft/spline"
  • the only control required for the adjusters is ON/OFF and the direction of rotation; since here the adjusters can always be rotated up to their maximum capacity when ON.
  • the transmission ratio of a CVT during parking for which rotational position control of a cone is required, is not needed.
  • the cost of an adjuster that allows for rotational position control is not cost prohibitive, being able to change the transmission ratio of a CVT during parking allows the CVT to operate optimally even under extreme driving conditions.
  • a CVT 6 uses two CVT 4's in order to reduce the tension in the transmission belt of one of the CVT 4's
  • the concept of using two CVT's and mounting at least one means for conveying torque (such as a cone, transmission pulley, variator, etc.) of each CVT using an "adjuster that allows a said means for conveying torque to rotate relative to the shaft/spline on which it is mounted" can also be applied to other CVT's.
  • the same concept can be applied to a CVT that uses two CVT 1's or two CVT 3's of U.S. Patent No. 7,722,490 instead of two CVT 4's.
  • the cones of these CVT's are cones with two opposite slideabie teeth.
  • the adjusters 8 are mounted on a common shaft/spline.
  • a preferred CVT 6 uses two substantially identical CVT 4's, for which each CVT 4 uses an adjuster 8 to mount a cone.
  • An adjuster 8 which comprises of an adjuster body 8-M1 and adjuster output shaft 8-M2, can be used to adjust the rotational position of the cone mounted to it relative to the shaft/spline on which it is mounted. It doesn't matter of which shaft/spline of their CVT 4 the adjusters are mounted.
  • the adjusters 8 of a CVT 6 can also be mounted on different shafts/splines.
  • a preferred CVT 6 where the adjusters 8 are mounted on different splines is shown in Fig. 9.
  • a transmission which is referred to as a pre-transmission, can be placed between the engine/motor and the CVT.
  • the pre-transmission should have one gear ratio for regular driving, and at least one gear ratio for high torque driving.
  • the gear ratio for high torque driving should be selected so as to reduce the input speed and increase the torque of the rotation that enters the CVT.
  • the pre-transmission can also have neutral and/or reverse gearing. A configuration of a drive system using a Pre-transmission is shown in Fig. 0.
  • the purpose of the Pre-transmission is to limit the maximum rotational speed of a cone. Another method to accomplish this is by limiting the maximum rotational speed cone is allowed to rotate. Here the engine can still be allowed to rotate at its maximum rpm, but the transmission ratio of the CVT should be limited so that the maximum rotational speed of a cone is limited to a pre-set maximum rotational speed for a cone.
  • a transmission which is referred to as a post- transmission, can be placed after the output of the CVT.
  • the post-transmission should have one gear ratio for regular driving, and at least one gear ratio for high torque driving. If desired, the post-transmission can also have neutral and/or reverse gearing.
  • a configuration of a drive system using a Post-transmission is shown in Fig. 11.
  • drive system can also have a pre-transmission and post-transmission, both which are described earlier.
  • a configuration of a drive system using a Pre-transmission and Post-transmission is shown in Fig. 12.
  • a Drive System 1 An example drive system that has a pre-transmission, a CVT, and a post- transmission is described below and shown in Fig. 13; it is referred to as a Drive System 1.
  • a drive system that has a CVT, and a pre-transmission and/or post-transmission.
  • the pre-transmission of Drive System 1 has the following gearing: Neutral, Reverse, Normal (for regular demand driving conditions), and Hi-demand (for high demand driving conditions).
  • the Hi-demand gearing can consist of one or several gear ratios.
  • the post-transmission of Drive System 1 has the following gearing: Normal (for regular speed driving conditions), and Hi-speed (for high speed driving conditions).
  • the Hi-speed gearing can consist of one or several gear ratios.
  • Switching between Normal gearing and Hi-demand gearing can be performed automatically or manually. Automatic switching can be performed by a control mechanism that monitors the rpm speed of the engine. And manual switching can be performed by the user whenever he senses a Hi-demand condition, such as driving uphill or towing for example.
  • the output transmission ratio of Drive System 1 is the transmission ratio involving the pre-transmission, CVT, and post-transmission.
  • a transmission control system which has the required output transmission ratio for given output speed and demand driving condition programmed into it, is used to control the output transmission ratio of Drive System 1 based on: a) the output speed of Drive System 1 ; b) whether its pre- transmission is in Normal gearing or Hi-demand gearing (the demand driving condition).
  • the transmission control system is programmed so that the output transmission ratio for Hi-demand gearing is lower than that for Normal gearing (for a lower transmission ratio, the torque/speed ratio is higher than that of a higher transmission ratio). And programmed so that for each demand driving condition (Normal and Hi-demand), the lower the output speed, the lower the output transmission ratio.
  • the output transmission ratio of Drive System 1 is adjusted by the transmission control system based on the output speed of Drive System 1 and the demand driving condition (Normal or Hi-demand). This is accomplished by making adjustments in the CVT and/or Post transmission to reach the required programmed output transmission ratio using the "transmission configuration of Drive System 1" for the demand driving condition.
  • Drive System 1 will provide CVT performance, while allowing its CVT to operate at a lower maximum rpm.
  • the Hi-speed gearing of the post-transmission is also only used occasionally.
  • the car's speed is 191 km/h.
  • the transmission ratio range of the CVT is from 4: 1 (lowest trans, ratio) to 1 : 1 (highest trans, ratio), then it will be able to provide a car with a speed up to 191 km/h while running the engine up to 2000 rpm, which is in range of normal operating conditions of a car.
  • the CVT is operated under three operating modes which are: “Normal Driving Conditions” mode, "High Torque Driving Conditions” mode, and “High Speed Driving Conditions” mode.
  • a controlling computer selects which operating mode to be used for the CVT, either automatically or due to the manual selection of the driver.
  • the "High Torque Driving Conditions” mode is separated into two operating modes, which are the “Low Transmission Ratio - High Torque Driving Conditions” mode and the “High Transmission Ratio - High Torque Driving Conditions” mode.
  • maximum axiai position changing rpm value of the output shaft can be identical or different.
  • the input shaft and the output shaft each have their own “maximum axiai position changing rpm value”.
  • the purpose of the "maximum axial position changing rpm value(s)" is to limit the rpm (speed) of the shafts at which axiai position changing of "the cones mounted on them” is performed. As such, axiai position changing of a cone is only performed when the speed of the shaft of said cone has not exceeded its "maximum axiai position changing rpm value”.
  • the "maximum axial position changing rpm value" of the shaft of said cone should be selected such that when said shaft is rotating at said "maximum axial position changing rpm value", then axial position changing of said cone can be performed for all operating conditions of its CVT, even when said shaft is suddenly fully accelerated.
  • the "maximum axial position changing rpm value" of a shaft should also be selected such that a complete sequence of steps of the "preferred transmission ratio changing procedure for a CVT 6" can be performed for ail operating condition of its CVT, even when said shaft is suddenly fully accelerated. Experimentation can be used to determine a "maximum axial position changing rpm value”. In addition, factors of safety, conservative estimates, etc. can be used to ensure the reliability of a "maximum axial position changing rpm value".
  • the maximum rpm of the input shaft and the maximum rpm of the output shaft at which the axial positions of their cones can be changed are limited to their "maximum axial position changing rpm value”
  • the maximum rpm of the input shaft and the maximum rpm of the output shaft are not limited for the "High Torque Driving Conditions” mode and the “High Speed Driving Conditions” mode.
  • the maximum power of an engine can be utilized for the "High Torque Driving Conditions" mode and "High Speed Driving Conditions” mode.
  • the CVT using the "Maximum Axial Position Changing RPM Method” is in the “Normal Driving Conditions” mode when it is not in the "Low Transmission Ratio - High Torque Driving Conditions” mode (see below), and the transmission ratio of the CVT is from the “lowest (intiai) transmission ratio" to a "transmission ratio at which a predetermined cruising speed can be reached at a predetermined reasonable engine rpm".
  • the transmission ratio range of the "Normal Driving Conditions” mode "the maximum rpm of the input shaft” and “the maximum rpm of the output shaft” are limited to their “maximum axial position changing rpm value" regardless of the input (gas pedal depression) of the driver.
  • Transmission Ratio - High Torque Driving Conditions mode is currently not manually selected, and the transmission ratio of the CVT is from the “transmission ratio at which a predetermined cruising speed can be reached at a predetermined reasonable engine rpm" to the “highest (final) transmission ratio", as long as the "maximum axial position changing rpm value" for both the input shaft and the output shaft are not exceeded.
  • the CVT will automatically enter the "High Transmission Ratio - High Torque Driving Conditions" mode.
  • the "maximum rpm of the input shaft” and the “maximum rpm of the output shaft” are not limited to their “maximum axial position changing rpm value”.
  • the CVT is in the "Low Transmission Ratio - High Torque Driving Conditions" mode when the transmission ratio of the CVT is from the “lowest (intiai) transmission ratio" to a "transmission ratio at which a predetermined cruising speed can be reached at a predetermined reasonable engine 80 rpm" and the controlling computer of the CVT senses that its vehicle is in a "high torque required” situation, such as when the controlling computer senses that the depression of the gas pedal results in a lower than usual speed increase of the input shaft or when the gas pedal is suddenly/violently depressed for example.
  • the CVT can also be in the "Low Transmission Ratio - High Torque Driving
  • the CVT is in the "High Transmission Ratio - High Torque Driving Conditions" mode when the transmission ratio of the CVT is in the high transmission ratio range, which is the transmission ratio range from the "transmission ratio at which a predetermined cruising speed can be reached at a predetermined reasonable engine rpm" to the “highest (final) transmission ratio", and the driver depresses the gas pedal deep enough so that the "maximum axial position changing rpm value" for at least one shaft is exceeded. This allows the driver to use the full power of the engine for this transmission ratio range when needed.
  • the CVT will remain in the "Normal Driving Conditions" mode when the "Low Transmission Ratio - High Torque Driving Conditions” mode is not selected (automatically or through manual selection by the driver) by the controlling computer regardless of the input (gas pedal depression) of the driver.
  • the reason for this is because for the "transmission ratios below the high transmission ratio range", less power is needed for acceleration since the transmission ratios are lower, and because this allows a cruising speed to be reached at a reasonable engine rpm without having to slow down the vehicle to allow for transmission ratio changes in the CVT.
  • a transmission/gear ratio where a cruising speed can be reached at a reasonable engine rpm is a 3rd gear, while a 1 st gear is not.
  • the CVT is in the "High Speed Driving Conditions" mode when it is at its final (highest) transmission ratio.
  • the "High Speed Driving Conditions” mode the "High Speed Driving Conditions" mode
  • maximum rpm of the input shaft and the “maximum rpm of the output shaft” are not 81 limited, so as not to limit the speed a vehicle to the "maximum axial position changing rpm value(s)".
  • transmission ratio changing can still be performed as long as the speed of each shaft of "the cone(s) for which the axial position(s) is/are changed" does not exceeded its/their "maximum axial position changing rpm value".
  • a Post Transmission can be placed after the output of the CVT,
  • a Post Transmission can be a regular gear box that has a regular gearing and one or several high speed gearing(s). If desired, the Post Transmission can also have neutral and/or reverse gearing.
  • a configuration of a drive system using a Post Transmission is shown in Fig. 11.
  • the purpose of the "maximum axial position changing rpm value(s)” is to limit the rpm (speed) of the shafts at which axial position changing of "the cones mounted on them” is performed. As such, axial position changing of a cone is only performed when the speed of the shaft of said cone has not exceeded its “maximum axial position changing rpm value”.
  • the "maximum axial position changing rpm value" of the shaft of said cone should be selected such that when said shaft is rotating at said "maximum axial position changing rpm value", then axial position changing of said cone can be performed for ail operating conditions of its CVT, even when said shaft is suddenly fully accelerated.
  • the "maximum axial position changing rpm value" of a shaft should also be selected such that a complete sequence of steps of the "preferred transmission ratio changing 82 procedure for a CVT 6" can be performed for all operating condition of its CVT, even when said shaft is suddenly fully accelerated.
  • the CVT is also operated under three operating modes which are: “Normal Driving Conditions” mode, "High Torque Driving Conditions” mode, and “High Speed Driving Conditions” mode. But unlike the “Maximum Axial Position Changing RPM Method", for the “Alternate Maximum Axial Position Changing RPM Method", the “High Torque Driving Conditions” mode is not separated into the “Low Transmission Ratio - High Torque Driving Conditions” mode and the “High Transmission Ratio - High Torque Driving Conditions” mode.
  • the CVT is in the "Normal Driving Conditions” mode when it is not in the "High Torque Driving Conditions” mode, and the transmission ratio of the CVT is from “its lowest (intia!) transmission ratio” to the “transmission ratio immediately below its “highest (final) transmission ratio".
  • the “Normal Driving Conditions” mode should be the mode that is active when the transmission ratio of the CVT is from “its lowest (intial) transmission ratio” to the “transmission ratio immediately below its highest (final) transmission ratio” during normal daily driving conditions.
  • the CVT is in the "High Torque Driving Conditions” mode when the transmission ratio of the CVT is from “its lowest (intial) transmission ratio” to the “transmission ratio immediately below its “highest (final) transmission ratio” and the controlling computer of the CVT senses that its vehicle is in a "high torque required” situation, such as when the controlling computer senses that the depression of the gas pedal results in a lower than usual speed increase of the input shaft or when the gas pedal is suddenly/violently depressed.
  • the "High Torque Driving Conditions” mode the "maximum rpm of the input shaft” and the
  • maximum rpm of the output shaft are not limited to their “maximum axial position changing rpm value”.
  • the "maximum rpm of the input shaft” and the “maximum rpm of the output shaft” are not limited, so as not to limit the speed of a vehicle to the "maximum axial position changing rpm vaiue(s)" of its CVT.
  • transmission ratio changing can still be performed as long as the speed of each shaft of "the cone(s) for which the axial position(s) is/are changed” does not exceeded its/their "maximum axial position changing rpm value”.
  • the rpm dial indicator is marked to show the maximum engine rpm at which a "maximum axial position changing rpm value" will not be exceeded, a mark that says “CVT Maximum Transmission Ratio Changing RPM” can be used for example.
  • the user of the CVT knows that transmission ratio changing cannot be continuously performed when a "maximum axial position changing rpm value” is exceeded; and knows how much he/she needs to reduce the engine rpm when a "maximum axial position changing rpm value" is exceeded in order to allow for continuous/uninterrupted transmission ratio changes in the CVT.
  • the controlling computer can calculate and determine the engine rpm at which a "maximum axial position changing rpm value" is exceeded based on: 1) the current transmission ratio, 2) the “maximum axial position changing rpm value” of the input shaft, 3) the “maximum axial position changing rpm value” of the output shaft, 4) the speed of the input shaft for a given engine rpm at said current transmission ratio, and 5) the speed of the output shaft for a given engine rpm at said current transmission ratio.
  • a "maximum axial position changing rpm value” is exceeded for an engine rpm where 4) is greater than 2) and an engine rpm where 5) is greater than 3).
  • the smaller engine rpm between the engine rpm where 4) is equal to 2) and the engine rpm where 5) is equal to 3) can be used as the engine rpm that is marked as the "CVT Maximum Transmission Ratio Changing RPM" on the rpm dial indicator.
  • the "CVT Maximum Transmission Ratio Changing RPM” changes with the transmission ratio of the CVT, if the CVT has transmission ratios where the output shaft rotates faster than the input shaft, if it is not desired to adjust the value indicated by the "CVT Maximum Transmission Ratio Changing RPM” mark with changes in the transmission ratio of the CVT, then the "CVT Maximum Axial Position Changing RPM” mark can simply be an estimation. Here preferably a conservative estimation, which ensures that no "maximum axial position changing rpm value" is exceeded for all transmission ratios of the CVT when the value indicated by the "CVT Maximum
  • the value indicated by the "CVT Maximum Transmission Ratio Changing RPM” mark can be made to change with changes in the transmission ratio of the CVT, so that the "CVT Maximum Transmission Ratio Changing RPM” mark can be made to always indicate the actual maximum engine rpm value at which no "maximum axial position changing rpm value" is exceeded.
  • animated displays such as LED displays or LCD displays can be used for example.
  • the "Maximum Axial Position Changing RPM Method” and the “Alternate Maximum Axial Position Changing RPM Method” can be implemented so that they can be turned ON and OFF as desired by the driver.
  • the purpose of the "maximum axial position changing rpm value(s)” is to limit the rpm (speed) of the shafts at which axial position changing of "the cones mounted on them” is performed. As such, axial position changing of a cone is only performed when the speed of the shaft of said cone has not exceeded its “maximum axial position changing rpm value”.
  • the "maximum axial position changing rpm value" of the shaft of said cone should be selected such that when said shaft is rotating at said "maximum axial position changing rpm value", then axial position changing of said cone can be performed for all operating conditions of its CVT, even when said shaft is suddenly fully accelerated.
  • the "maximum axial position changing rpm value" of a shaft should also be selected such that a complete sequence of steps of the "preferred transmission ratio changing procedure for a CVT 6" can be performed for ail operating condition of its CVT, even when said shaft is suddenly fully accelerated.
  • the rpm dial indicator is marked to show the maximum engine rpm at which a "maximum axial position changing rpm value" will not be exceeded, a mark that says "CVT Maximum Transmission Ratio Changing RPM” can be used for example.
  • the user of the CVT knows that transmission ratio changing cannot be continuously performed when a "maximum axial position changing rpm value” is exceeded; and knows how much he/she needs to reduce the engine rpm when a "maximum axial position changing rpm value" is exceeded in order to allow for continuous/uninterrupted transmission ratio changes in the CVT.
  • the controlling computer can calculate and determine the engine rpm at which a "maximum axial position changing rpm value" is exceeded based on: 1) the current transmission ratio, 2) the “maximum axial position changing rpm value” of the input shaft, 3) the “maximum axial position changing rpm value” of the output shaft, 4) the speed of the input shaft for a given engine rpm at said current transmission ratio, and 5) the speed of the output shaft for a given engine rpm at said current transmission ratio.
  • a "maximum axial position changing rpm value” is exceeded for an engine rpm where 4) is greater than 2) and an engine rpm where 5) is greater than 3).
  • the smaller engine rpm between the engine rpm where 4) is equal to 2) and the engine rpm where 5) is equal to 3) can be used as the engine rpm that is marked as the "CVT Maximum Transmission Ratio Changing RPM" on the rpm dial indicator.
  • the "CVT Maximum Transmission Ratio Changing RPM” can change with the transmission ratio of the CVT if the CVT has transmission ratios where the output shaft rotates faster than the input shaft. If it is not desired to adjust the value indicated by the "CVT Maximum Transmission Ratio Changing RPM” mark with changes in the transmission ratio of the CVT, then the "CVT Maximum Axial Position Changing RPM” mark can simply be an estimation. Here preferably a conservative estimation, which ensures that no "maximum axial position changing rpm value" is exceeded for all transmission ratios of the CVT when the value indicated by the "CVT Maximum
  • the value indicated by the "CVT Maximum Transmission Ratio Changing RPM” mark can be made to change with changes in the transmission ratio of the CVT, so that the "CVT Maximum Transmission Ratio Changing RPM” mark can be made to always indicate the actual maximum engine rpm value at which no "maximum 88 axial position changing rpm value” is exceeded.
  • animated displays such as LED displays or LCD displays can be used for example.
  • the "maximum axial position changing rpm value(s)" are selected so that it or they (if different values are used for the input shaft and the output shaft) are never exceeded during "regular day to day driving conditions" when the transmission ratio of the CVT is from the “lowest (intial) transmission ratio” to the “highest (final) transmission ratio".
  • the full power of the engine is always available when needed, such as during high torque situations (which include: emergency situations where sudden acceleration is needed, driving uphill, pulling, etc.) and high speed situations (speeds after the highest transmission ratio of the CVT has been reached).
  • high torque situations which include: emergency situations where sudden acceleration is needed, driving uphill, pulling, etc.
  • high speed situations speeds after the highest transmission ratio of the CVT has been reached.
  • the value(s) for the "maximum axial position changing rpm value(s)" can be obtained through experimentation.
  • a bail park figure for the "maximum axial position changing rpm value(s)" is between 3000 rpm to 4000 rpm.
  • the "Maximum Axial Position Changing RPM Method", the “Alternate Maximum Axial Position Changing RPM Method”, and the “Alternate Maximum Axial Position Changing RPM Method 2" can be used for CVT's not described in this disclosure. All CVT's for which "lowering the maximum rpm at which transmission ratio changing has to be performed” is beneficial, can benefit from the "Maximum Axial Position Changing RPM Method", the “Alternate Maximum Axial Position Changing RPM Method”, and the “Alternate Maximum Axial Position Changing RPM Method 2"; this includes CVT's for which the axial position of pulley halves instead of cones have to be changed in order to change the transmission ratio for example.
  • the overall transmission ratio for a vehicle "that uses a CVT” or “that uses a CVT and a Post Transmission” is controlled by a transmission ratio controller based on the speed of said vehicle by following a pre-programmed ideal (but probably not always actual) "speed vs transmission ratio curve/equation(s)".
  • a CVT can have a "High Torque - Speed vs Transmission Ratio Curve” and a “Low Torque - Speed vs Transmission Ratio Curve”; where the "High Torque - Speed vs Transmission Ratio Curve” is actuated when the controlling computer senses thai the driver wants to accelerate the vehicle (as can be sensed by the controlling computer when the driver maintains or increases the depressing of the gas pedal during acceleration), and the "Low Torque - Speed vs Transmission Ratio Curve” is actuated when the controlling computer senses that the driver does not want to accelerate the vehicle (as can be sensed by a controlling computer when the driver maintains the depression of the gas pedal during cruising, or when the driver reduces the depression of the gas pedal).
  • the transmission ratio of a vehicle is changed using the following "transmission ratio configuration according to speed setup".
  • the transmission ratio of the CVT is increased throughout its transmission ratio range as the speed of the vehicle is increased according to "itsTits current" speed vs transmission ratio curve. If the speed of the vehicle is increased further and a Post Transmission is used, the Post
  • Transmission switches to high speed gearing(s) when its pre-set switching speed(s) have been reached.
  • CVT for a vehicle that uses the "Maximum Axial Position Changing RPM Method” is describe below.
  • the "maximum axial position changing rpm value" for both the input shaft and the output shaft are set to 3000 rpm; although the maximum speed that the input shaft and the output shaft can rotate can be higher, such as 6000 rpm for example.
  • axial position changing of a cone is only performed when they are rotating at speeds of 0 to 3000 rpm regardless of the current operating modes.
  • the transmission ratio (output speed/input speed transmission ratio) is from 1 :4 to 1 : 1 ; 1 :4 is the initial (lowest) transmission ratio and 1 : 1 is the final (highest) transmission ratio.
  • the CVT should always be at its initial (lowest) transmission ratio.
  • a "1 :2 output speed/input speed gear reducer" can be used to modify the transmission ratio of the CVT, so that for the CVT itself a transmission ratio of 1 :2 to 2: 1 can be used.
  • predetermined cruising speed can be reached at a predetermined reasonable engine rpm"). This allows the transmission ratio to be changed up to a transmission ratio of 1 :2 even when the user of said vehicle floors the gas pedal.
  • the maximum speeds of the input shaft and the output shaft are not limited. But here when the input shaft or the output shaft exceed their “maximum axial position changing rpm value" of 3000 rpm, the CVT will switch to the "High Transmission Ratio - High Torque Driving Conditions" mode.
  • the CVT is in the "High Speed Driving Conditions" mode when it is at its final
  • a cruising speed of about 70 mph can be reached at an input shaft speed, which is also the engine rpm, of about 2000 rpm. If the maximum speeds of the input shaft and the output shaft are not limited to the "maximum axial position changing rpm value" of 3000 rpm until a "transmission ratio at which a predetermined cruising speed can be reached at a predetermined reasonable engine rpm" has been reached; then it is possible that the transmission ratio cannot be changed when the user of the vehicle floors the gas pedal to above 3000 rpm during start-up so that the transmission ratio remains at 1 :4; if so, a cruising speed of about 70 mph is reached at an input speed of about 4000 rpm. Cruising while the engine runs near rediine can damage the engine, and can be dangerous since almost no additional increase in speed is available when suddenly required.
  • a Post Transmission can be used.
  • the Post Transmission can be a regular gear box that has a regular gearing and one or several high speed gearing(s); and its transmission ratio changing ability is not limited by the "maximum axial position changing rpm value".
  • the primary purpose of the Post Transmission is to provide additional transmission ratios for high speed situations of the vehicle. But if used, it is recommended that a Post Transmission is also used to change the transmission ratio for the vehicle during low speed situations of the vehicle in instances when the "maximum axial position changing rpm value" is exceeded but a transmission ratio that that better fits the current "speed vs transmission ratio curve" can be provided by the Post Transmission.
  • an output shaft speed of 3000 rpm corresponds to vehicle speed of about 223 mph, as such a Post Transmission with high speed gearing(s) might not be necessary for most vehicles.
  • a Post Transmission can be used so thai the transmission ratio range of the CVT can be reduced, such as from “1 :4 to 1 : 1" to "1 :4 to 1 :2" for example; this will reduce the size of the CVT.
  • rpm_max the maximum rotating speed at which axial position changing of the cone is performed
  • axial position changing of the cone has to be performed during a duration of 3/4 of a revolution of the cone.
  • the average acceleration provided by the pre- tensioned tension spring is equal to the average acceleration provided by a constant 20 lbs force.
  • the calculation described here is only a ballpark estimation; the actual initial force needed can be easily obtained and refined through experimentation.
  • a detailed design for a "Tensioning Pulley Tensioning System" for a preferred CVT 6 (which here uses a Driving Cone 3C, a Driven Cone 5C, and a Transmission Belt 4C for one of its CVT4's) is shown as front-view in Fig. 14 and as a partial top-view in Fig. 15. It has two vertical slider beams 16 which slide on slider rounds 7. In order to reduce the friction between the vertical slider beams 16 and the slider rounds 17, each vertical slider beam 16 has two sleeve bearings 18.
  • each vertical slider beam 16 a tensioning pulley is mounted; to the upper vertical slider beam 16 a tensioning pulley 14A is mounted, and to the lower vertical slider beam 16 a tensioning pulley 13A is mounted (see Fig. 14).
  • each connector plate 9 is used to connect a slider mounting plate 20 to a vertical slider beam 16.
  • Each slider mounting plate 20 is used to slide-ably mount a slider 21 ; and each slider 21 is used to attach the ends of a pulley shaft 22 using a locking ring 23.
  • a slider mounting plate 20 is shown by itself as a front- view in Fig, 17 and as a side-view in Fig. 18,
  • a slider 21 which preferably has low friction surfaces, is shown by itself as a front-view in Fig. 19 and as a side-view in Fig. 20.
  • the tensioning forces for the tensioning pulleys are provided by compression springs 24, which push the lower vertical slider beam 16 upwards and which push the upper vertical slider beam 16 downwards.
  • the compression springs 24 for the lower vertical slider beam 16 are inserted into slider rounds 17 and positioned between a fixed bottom end and the lower vertical slider beam 16.
  • the fixed bottom end can be the base of the slider rounds 17, or fasteners (locking rings, nuts, etc.) positioned/fixed below the lower vertical slider beam 16.
  • the compression springs 24 for the upper vertical slider beam 16 are inserted into slider rounds 17 and positioned between a fixed top end and the upper vertical slider beam 16,
  • the fixed top end can be the top of the slider rounds 17, or fasteners (locking rings, nuts, etc.) positioned/fixed above the upper vertical slider beam 16.
  • fasteners locking rings, nuts, etc.
  • locking rings 25 are used as the fixed top end.
  • two maximum contraction stops 15A are used.
  • One maximum contraction stop 15A is used to limit the downward movement of the lower vertical slider beam 16.
  • the other maximum contraction stop 15A is used to limit the upward movement of the upper vertical slider beam 16.
  • a marked disk 26 is a disk that has a marker 27, and a sensor 28 that is connected to the controlling computer of the CVT and that can determine rotational position of the marker 27 (see Fig. 22).
  • markers 27 and sensors 28 are: a dimple and a mechanical switch, a light source/light reflector and a light sensor, a magnet and a magnetic sensor, etc.
  • a marked disk 26 should be mounted so that it is fixed for rotation relative to its cone, in Fig. 21 a set-screw is used to fix a marked disk 26 to a cone 3D.
  • the marker 27 of a marked disk 26 should be positioned at the trailing end of the torque transmitting member of its cone, when said torque transmitting member is positioned at the smallest transmission diameter of its cone; and the sensor 28 should be positioned at the rotational position where the trailing end of the torque transmitting member (when positioned at the smallest transmission diameter of its cone) disengages with its transmission belt.
  • An alternate method for reducing the tension in the transmission belt of a CVT 6 is to use a design where no adjusters 8 are used, but each cone of the CVT 6 is mounted on its shaft/spline using a dutch 29 (see Fig. 23, the labeling of all other parts are identical to the labeling used in Fig. 8).
  • each clutch 29 can be used to controilably “lock its cone for rotation relative to its shaft/spline” or “unlock its cone so as to allow if to rotate relative to its shaft/spline".
  • the dutch 29 of said cone is unlocked. Unlocking the clutch 29 of a cone reduces the transmission belt tension of the CVT 4 of said cone; and allows the cone to freely rotate relative to its shaft/spline, so that tensioning/maintaining pulleys are not needed for compensating for the rotations that occur during the axial position changing of said cone. Also here when there are two cones with different transmission diameters mounted on the same shaft/spline, at least one of said two cones needs to be unlocked by its clutch.
  • an indexing mechanism can also be used to controilably lock and unlock an adjuster of a CVT 6.
  • said indexing mechanism is used to lock and unlock the worm gear of the worm gear-gear drive of said adjuster; then the worm gear- gear drive can be selected in a manner such that the difference between and "the unlocking (rotating) force of the worm gear-gear drive when the worm gear is stationary" and the “locking (frictionai) force of the worm gear-gear drive when the worm gear is stationary" are small, so that the force required to lock and unlock the indexing mechanism is small. This results in a relatively cheap and very reliable adjuster.
  • An indexing mechanism which can only lock in incremental steps, can be used to eontroliab!y lock and unlock an adjuster because: a) when the transmission diameters of all cones mounted on a same shaft/spline are equal, an unlocked adjuster does not have to be locked.
  • the cone of said unlocked adjuster which will be referred to as the unlocked cone, is simply a cone of the "CVT 4 for which transmission belt tension has been reduced", which is also the CVT 4 for which the axial position of a cone is changed when axial position changing of a cone is initiated.
  • CVT 4 for which transmission belt tension has been reduced
  • indexing mechanism which can only lock in incremental steps, can be used eontroliab!y lock and unlock an adjuster because: b) when an adjuster needs to be locked during "step e) Second axial position changing of a cone Option 2 of 2" of the "Preferred transmission ratio changing procedure for a CVT 6", rotations of the index wheel of the adjuster relative to its lock exist; this rotation, which is slowing down, should allow the lock to enter a cavity of its index wheel.
  • the index wheel and its lock should be designed so that the said rotation is sufficient for a lock to enter a cavity of its index wheel; if necessary a speed increasing gear train (such as a larger gear coupled to a smaller gear for example) can be used to couple the rotation of the worm gear to the index wheel.
  • step e) Second axial position changing of a cone Option 2 of 2 when the transmission diameters of the cones mounted on a same shaft/spline are different and the adjuster of the "cone that is rotated in the direction that increases the tension in the tense side of its transmission belt” needs to be locked; then in order to compensate for having cones with different transmission diameters mounted on a same shaft/spline, first the "cone that is not rotated in the direction that increases the tension in the tense side of its transmission belt", which is currently locked and as such used for torque transmission, needs to be unlocked so that it can rotate in the direction that reduces the tension in its transmission belt.
  • the "adjuster to be locked” can be locked after the speed of its worm gear has slowed down, so as to reduce the shock-loads during locking, if this is desired, then a time delay from when the adjuster of the "cone that is rotated in the direction that reduces the tension in its transmission belt” is unlocked until when locking of the
  • the time delay does not have to be accurate, but for better accuracy, the time delay can be based on the current rpm and transmission ratio of its CVT 8. if used, if is recommended the time delay is selected so that for all operating conditions, locking of the adjuster occurs before the worm gear of the "adjuster to be locked" reverses direction, since by then the adjuster to be locked is subjected to the torque that is being transmitted by its CVT 6 (instead of only the torque due to friction).
  • An adjuster that uses an indexing mechanism for controilabiy locking and unlocking its output shaft spline is shown as a partial front-view in Fig. 24, as a partial side-view in Fig. 25, and as a partial top-view in Fig. 26.
  • the adjuster is mounted on a spline 30, and is used to adjust the rotational position of a cone positioned on a spline 30.
  • the wails of housing 37 are cut open to show the inside of the adjuster.
  • the housing of the adjuster which is labeled as housing 37, is fixed for rotation relative to spline 30 but can slide axialiy relative to spline 30 (only relative axial movements between spline 30 and housing 37 are allowed).
  • the details for housing 37 such as the bearings, the spline cut-out profile to allow axial but not rotational movement relative to spline 30, the counter-balance weight(s) to reduce vibration, etc., are not shown. But somebody skilled in the art should be able to construct housing 37 from the details provided here.
  • the adjuster of Figs. 24 - 26 has a gear 32 that is fixed to an output spline 31 , so that gear 32 can be used to rotate output spline 31.
  • Output spline 31 is shaped like hollow spline and is slid-on to spline 30 and supported by parts of housing 37 (bearings, etc., which are not shown) in manner so as to be able to freely rotate and freely move axialiy relative to spline 30. Furthermore, output spline 31 is supported by parts of housing 37 in a manner so that output spline 31 is concentric with spline 30.
  • gear 32 In order to fix the axial position of gear 32 relative to output spline 31 , one or multiple set-screws (which are not shown) can be used. In Figs. 24 - 26 the teeth of gear 32 are not shown, but obviously gear 32 should have teeth.
  • Output spline 31 is mounted on housing 37 through bearings (which are not shown) that allow output spline 31 to rotate relative to housing 37, but any other significant relative movements between output spline 31 and housing 37 are not allowed.
  • the front end of output spline 31 is used to attach a cone in a manner so that said cone is fixed for rotation and axial movements relative to output spline 31 ; for such purpose, the front end of output spline 31 can also have one or multiple set-screws (not shown).
  • Gear 32 is coupled to a worm gear 33.
  • Gear 32 and worm gear 33 should be selected so that the worm gear-gear drive is not self-locking (which means that gear 32 can drive worm gear 33),
  • Worm gear 33 is fixed to a shaft 34 in a manner so that worm gear 33 can be used to rotate shaft 34.
  • Shaft 34 is mounted to housing 37 so that it can rotate about its axis of rotation relative to housing 37, but any other significant relative movements between shaft 34 and housing 37 are not allowed.
  • index wheel 35 Also fixed for axial and rotational movements to shaft 34 is an index wheel 35. Since index wheel 35 is fixed for rotation relative to shaft 34, index wheel 35 can be used to lock and unlock the rotational movements of shaft 34. In order to fulfill its purpose, index wheel 35 has circumferential cavities (the cavities are shown in Fig. 25 but not in Figs. 24 and 26).
  • Locking mechanism 36 comprises of a lock that can be inserted into a cavity of index wheel 35, a spring, and a solenoid. The lock is pushed towards the index wheel cavities so that it can enter the index wheel cavities (one cavity at a time) by the spring, and the lock can be controllabiy pulled out of an index wheel cavity by the solenoid.
  • the lock is in a cavity of index wheel 35, index wheel 35, and as such also the adjuster is locked; and when the lock is not in a cavity of index wheel 35, index wheel 35 and as such also the adjuster, is unlocked.
  • a pneumatic/hydraulic actuator with or without a spring, or other devices that can lock and unlock an index wheel can also be used.
  • an adjuster can also use a brake or an electric motor.
  • An adjuster using a brake is shown in Figs. 27 - 29, where a brake disk 38 and braking shoe mechanism 39 are used in-place of index wheel 35 and locking mechanism 36.
  • an adjuster using an adjuster motor which is preferably an electric motor, is shown in Figs. 30 - 32, where an electric motor 40 is used to rotate shaft 34.
  • Ail parts of the "adjuster shown in Figs. 27 - 29" and the "adjuster shown in Figs. 30 - 32" thai are not mentioned in this paragraph are identical to the "adjuster shown in Figs. 24 - 28" and use the same numbering and labeling.
  • a speed increasing gear train such as a larger gear coupled to a smaller gear for example
  • a speed increasing gear train such as a larger gear coupled to a smaller gear for example
  • gear train 41 is fixed to housing 37 (Fig. 34 does not show gear train 41 since it is behind index wheel 35).
  • Ail parts of the "adjuster shown in Figs. 33 - 35" except for gear train 41 are identical to the "adjuster shown in Figs. 24 - 26" and use the same numbering and labeling.
  • the adjusters of this application are basically used as a clutch, as such they can also be used dutches for other applications.
  • the housing of the adjuster can be construct so that it is fixed for ail relative movements to its shaft or spline; unlike the example described in the paragraphs above, where the housing of the adjuster can slide axiaily relative to its spline.
  • Disclosed in this disclosure are methods that can be used to "limit the maximum shaft rpm (speed) at which axial position changing of a variator mounted on it is performed to a "maximum axial position changing rpm value" for ail variator mounted shafts of a CVT, while still allowing a safe driving experience and also allowing the driver to use the full power of the engine when needed.
  • the methods of this disclosure are: the “Maximum Axial Position Changing RPM Method", the “Alternate Maximum Axial Position Changing RPM Method”, and the “Alternate Maximum Axial Position Changing RPM Method 2".
  • Push belt pulleys are variators that consist of two pulley halves for which either one pulley half or both pulley halves are moved axiaily in order to change the pulley's transmission diameter.
  • a "maximum axial position changing rpm value" of a push belt pulley refers to the maximum rpm at which the axial position of one or both pulley halves of the push belt pulley is/are changed.
  • the description of the "Maximum Axial Position Changing RPM Methods" Section is a for a CVT that uses one or several variators on both the input shaft and the output shaft (such as a CVT 4, CVT 6, or any other CVT where one or several variators on the input shaft is/are coupled to one or several variators on the output shaft); the methods of this disclosure can also be applied to CVT's for which "a variator” or “several variator(s)” are only mounted on either the input shaft or the output shaft (such a CVT 3, a CVT where a variator is coupled to a transmission pulley, or any other CVT that uses only one shaft on which variator(s) is/are mounted). Since only the shafts on which variator(s) are mounted have a "maximum axial position changing rpm value", for these CVT's only one shaft has a "maximum axial position changing rpm value”.
  • the “Maximum Axial Position Changing RPM Methods” Section contains the following sentence: For the “Maximum Axial Position Changing RPM Method", "the maximum speed of the input shaft at which the axial position of a cone mounted on it is changed” and “the maximum speed of the output shaft at which the axial position of a cone mounted on it is changed” are each limited to their “maximum axial position changing rpm value”. This sentence can be rewritten as: For the "Maximum Axial Position Changing RPM Method"
  • the "Maximum Axial Position Changing RPM Methods” Section contains the following sentence: For this transmission ratio range of the "Normal Driving Conditions” mode, "the maximum rpm of the input shaft” and “the maximum rpm of the output shaft” are limited to their “maximum axial position changing rpm value” regardless of the input (gas pedal depression) of the driver. This sentence can be rewritten as: For this transmission ratio range of the "Normal Driving Conditions” mode, the maximum rpm of all variator mounted shafts/splines is/are limited to their “maximum axial position changing rpm value" regardless of the input (gas pedal depression) of the driver.
  • the preferred embodiment of the invention is the "Alternate Maximum Axial Position Changing RPM Method 2" described in the "Maximum Axial Position Changing RPM Methods" Section.
  • this invention can be described as: A method that can be used to "limit the maximum shaft/spline rpm (speed) at which axial position changing of a variator mounted on it is performed to a "maximum axial position changing rpm value" for all variator mounted shafts/splines of a CVT, while still allowing a safe driving experience and also allowing the driver to use the full power of the engine when needed, by:

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Abstract

L'invention concerne des procédés qui peuvent être utilisés pour limiter la vitesse de rotation (t/min) d'arbre/cannelures maximale à laquelle un changement de position axiale d'un variateur monté sur ces derniers est exécuté à une "valeur de vitesse de rotation de changement de position axiale maximale" pour tous les arbres/cannelures montés sur un variateur d'une transmission variable en continu, tout en permettant toujours une expérience de conduite sûre et permettant également au conducteur d'utiliser la pleine puissance du moteur lorsque cela est nécessaire.
PCT/US2016/027989 2015-02-14 2016-04-15 Procédés de vitesse de rotation de changement de position axiale maximale Ceased WO2016172013A1 (fr)

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US201562116391P 2015-02-14 2015-02-14
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US201562118653P 2015-02-20 2015-02-20
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US201562119119P 2015-02-21 2015-02-21
US62/119,119 2015-02-21
US201562119194P 2015-02-22 2015-02-22
US62/119,194 2015-02-22
US201562121056P 2015-02-26 2015-02-26
US62/121,056 2015-02-26
US201562121596P 2015-02-27 2015-02-27
US62/121,596 2015-02-27
US201562161268P 2015-05-14 2015-05-14
US62/161,268 2015-05-14
US201562162807P 2015-05-17 2015-05-17
US62/162,807 2015-05-17
US201562204982P 2015-08-14 2015-08-14
US62/204,982 2015-08-14
US201562208973P 2015-08-24 2015-08-24
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US20130310205A1 (en) * 2012-05-15 2013-11-21 Armin Sebastian Tay Cvt with extended transmission ratio range

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10672207B2 (en) 2017-01-20 2020-06-02 Polaris Industries Inc. Diagnostic systems and methods of a continuously variable transmission
US11430272B2 (en) 2017-01-20 2022-08-30 Polaris Industries Inc. Diagnostic systems and methods of a continuously variable transmission
US12118835B2 (en) 2017-01-20 2024-10-15 Polaris Industries Inc. Diagnostic systems and methods of a continuously variable transmission

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