EP1552190A2 - Kegel mit drehmomentübertragungsgliedern verwendende einstellsysteme für stufenloses getriebe - Google Patents

Kegel mit drehmomentübertragungsgliedern verwendende einstellsysteme für stufenloses getriebe

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Publication number
EP1552190A2
EP1552190A2 EP03808196A EP03808196A EP1552190A2 EP 1552190 A2 EP1552190 A2 EP 1552190A2 EP 03808196 A EP03808196 A EP 03808196A EP 03808196 A EP03808196 A EP 03808196A EP 1552190 A2 EP1552190 A2 EP 1552190A2
Authority
EP
European Patent Office
Prior art keywords
adjuster
torque transmitting
torque
cvt
transmitting member
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP03808196A
Other languages
English (en)
French (fr)
Other versions
EP1552190A4 (de
Inventor
Armin S. Tay
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP1552190A2 publication Critical patent/EP1552190A2/de
Publication of EP1552190A4 publication Critical patent/EP1552190A4/de
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/04—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism
    • F16H63/06—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions
    • F16H63/062—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions electric or electro-mechanical actuating means
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/52—Pulleys or friction discs of adjustable construction
    • F16H55/54—Pulleys or friction discs of adjustable construction of which the bearing parts are radially adjustable
    • 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
    • F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
    • F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
    • F16H9/10—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley provided with radially-actuatable elements carrying the belt

Definitions

  • TITLE ADJUSTER SYSTEMS FOR CONTINUOUS VARIABLE TRANSMISSIONS UTILIZING CONES WITH TORQUE TRANSMITTING MEMBERS
  • This mvention describes an improvement for an invention described in Patent #. Furthermore, this invention is entitled to the benefit of Provisional Patent Application (PPA) Ser.# 60/416828 filed on Oct. 8 2002, PPA Ser. #60/423503 filed on Nov. 4 2002, PPA Ser. #60/431921 filed on Dec. 92002, PPA Ser. # 60/475461 filed on June 2 2003, PPA Ser. #60/478651 filed on June 13 2003, and PPA Ser. #60/487626 filed on July 15 2003.
  • PPA Provisional Patent Application
  • This invention relates to positional adjusters. Specifically to positional adjusters that can increase the performance of CVTs that utilize one or several cone assemblies with torque transmitting members.
  • the adjusters can improve the performance of the CVTs in the following manner. First of all, they can eliminate or significantly reduce flexing of the torque transmitting member(s) and coupling member(s), if applicable, due to instances were the circumference of the cone assembly where the torque transmitting member(s) are positioned is not a multiple of the width of the teeth of the torque transmitting member(s). This flexing will be referred to a transition flexing. And excessive cycles of transition flexing can reduce the life of the torque transmitting member(s) and the coupling member(s). Furthermore, the adjusters of this application can also be used so that a CTTM CVT is maintained in a moveable position regardless of the rotational position of its input shaft and its output shaft so as to increase the transmission ratio changing responsiveness of a CTTM CVT.
  • the objects and advantages of the present invention are: a) To provide an adjuster system which eliminates or reduces transition flexing in a CTTM CVT, which increases the live of the CTTM CVT. b) To provide a positional adjuster system that maintains a CTTM CVT in a moveable configuration during transmission ratio changes, which will reduce the time it takes to change the transmission ratio of the CTTM CVT.
  • Fig.lA is a sectional-view of CVT 1 of Patent #.
  • Fig. IB is a top-view of CVT 1 of Patent #.
  • Fig. 2 is a sectional-view of CVT 1.1.
  • Fig. 3 is a top-view of CVT 1.1.
  • Fig. 4 is a side-view of transition flexing adjuster AD1A 101 A.
  • Fig. 5 is a side-view of mover adjuster AD2A 102A.
  • Fig. 6 is a another side-view of transition flexing adjuster AD1 A 101A.
  • Fig. 7 is a side-view of transition flexing adjuster AD1A 101.
  • Fig. 8 is a side-view of rotatable coupling 190.
  • Fig. 9 shows a ring and brush electrical connection.
  • Fig. 10 is a detailed sectional-view of constrainer mechanism CN1A 111A
  • Figs. 11 A-l ID shows how the relative rotational position between the torque transmitting members need to be adjusted in order to eliminate transition flexing.
  • Fig. 12A-12C show graphs that show the required rotational rotation vs. arc length of the critical non-torque transmitting arc.
  • Fig. 13 is a top- view of CVT 2.
  • Fig. 14 is atop-view of CVT 2.1.
  • Figs. 15A-15D show sectional- views of CVT 2.1.
  • Fig. 16 shows the equation that can be used in order to calculate transmission ratio change rotation.
  • Figs. 17A-17C, 18A, 18B, 19A, 19B, 20A, 20B illustrated the required compensating rotation of transmission pulley 41 C due to transmission ratio change rotation.
  • Figs. 21A shows the top-view of electrical adjuster 160.
  • Fig. 2 IB shows the front- view of electrical adjuster 160.
  • Fig. 23 shows a top-view of CVT 2.2.
  • Fig. 24 shows a top-view of CVT 2.3.
  • Fig. 25 shows a top-view of CVT 2.4.
  • Figs. 26A, 26C, and 26D show a side-view of spring-loaded adjuster AS1 171.
  • Fig. 26B shows the top-view of spring-loaded adjuster AS1 171.
  • Fig. 27 A shows the top-view of spring-loaded adjuster AS2 172.
  • Fig. 27B shows the side-view of spring-loaded adjuster AS2 172.
  • Fig. 28 A shows the end-view of mechanical adjuster AMI 181.
  • Fig. 28B shows the top-view of mechanical adjuster AMI 181.
  • Fig. 29 shows the top-view of CVT 2.5.
  • Fig. 30 shows the top-view of CVT 2.6.
  • Fig. 31 shows the top-view of CVT 1.3.
  • Fig. 32 show a sectional view showing the guiding wheels 200.
  • 160-M5 electrical adjuster set-screw 160-M6 electrical rings 160-M7 adjuster motor holder 160-M8 counter-weight 160-M2 adjuster worm gear
  • 160-M9 electrical cable 160-M10 electrical adjuster nut
  • the purpose of this invention is to introduce an adjuster system for a CTTM CVT, hence specific details such as the method of attaching the torque transmitting members, and the method of changing the axial position of the torque transmitting members are not described in this invention. These details are described in Patent #.
  • CVT 1.1 is almost identical to CVT 1 of Patent #., as shown in Fig. 1A & IB.
  • CVT 1 mainly consist of a cone assembly CS1A 21A and a cone assembly CS1B 21B, which are identical and each have two opposite positioned torque transmitting members which are rotatably constrained but are allowed to slide axially relative to the surface of their cone assembly.
  • the torque transmitting members of cone assembly CS1A 21A are labeled as torque transmitting member CSIAMI 21A-M1 and torque transmitting member CS1A-M2 21A-M2, while the cone of cone assembly 21A is labeled as cone CS1A-M3 21A-M3.
  • torque transmitting members of cone assembly 2 IB are labeled as torque transmitting member CS1B-M1 21B-M1 and torque transmitting member CS1B-M2 21B-M2, while the cone of cone assembly 21B is labeled as cone CS1B-M3 21B-M3.
  • the cone assembly CS21A 21A is keyed to the input shaft SHI 11, and the cone assembly CS1B 21B is keyed to the output shaft SH2 12.
  • the torque transmitting members of cone assembly CS1A 21A are coupled with the torque transmitting members of cone assembly CS1B 21B by transmission belt BL1A 31A.
  • each cone assembly has a mover sleeve, which can slide axially relative to its shaft.
  • each torque transmitting member is connected to a mover sleeve by two telescopes so that the axial position of the torque transmitting members depend on the axial position of the mover sleeves.
  • Detailed description of the mover sleeves and the telescopes can be found in Patent #.
  • the transmission ratio should only be changed when for both cone assemblies only one torque transmitting member is in contact with transmission belt BL1 A 31 A. Otherwise excessive stretching of the transmission belt BL1A 31A might occur.
  • the configuration where the transmission ratio can be changed with out excessive stretching of the transmission belt BL1A 31 A is referred to as a moveable configuration. Also as described earlier, here transition flexing is not eliminated.
  • CVT 1.1 which is shown in Fig. 2 and Fig. 3, is slightly different than CVT 1, for CVT 1.1 like for CVT 1 a cone assembly with two transmitting members is coupled by a transmission belt, which here is labeled as transmission belt BL1B 3 IB to another cone assembly with two torque transmitting members.
  • a transition flexing adjuster AD1A 101 A is added to a slightly modified version of cone assembly CS1A 21 A, which is labeled as cone assembly CS2A 22A
  • a transition flexing adjuster AD1B 101B is added to a slightly modified version of cone assembly CS1B, which is labeled as cone assembly CS2B 22B.
  • transition flexing adjuster AD1A 101A which is shown in detail in Fig. A, 6, and 7, has an adjuster body AD1 A-Ml 101A-M1 and an adjuster output member AD1 A-M2 101A- M2.
  • transition flexing adjuster AD IB 101B is identical to transition flexing adjuster AD1A 101A.
  • the adjuster body AD1A-M1 101A-M1 of transition flexing adjuster AD1A 101 A is fixed to the end of a mover sleeve CS2A-M6 22A-M6, where the two telescopes CS2A-M422A-M4 of torque transmitting member CS2A-M1 22A-M1 are attached.
  • the adjuster output member AD1A-M2 of transition flexing adjuster AD1 A is used to mount the two telescopes CS2A-M5 22A-M5 of torque transmitting member CS2A-M222A-M2.
  • a constraining mechanism CN1A 111 A which will be described in detail later, is used such that the adjuster output member AD1A-M2 101A-M2 of transition flexing adjuster AD1A 101 A can be used to adjust the rotational position of torque transmitting member CS2A-M2 22A-M2.
  • the adjuster body AD1A-M1 101A-M1 of transition flexing adjuster AD1 A 101 A is fixed to the end of the mover sleeve CS2A-M622A-M6, where the telescopes CS2A-M4 22A-M4 of torque transmitting member CS2A-M1 22A-M1 are attached.
  • the adjuster output member AD1A-M2 101A-M2 of transition flexing adjuster AD1A 101A is used to mount the telescopes CS22A-M5 22A-M5 of torque transmitting member CS2A-M2 22A- M2.
  • a constraining mechanism CN1B 111 A is used such that the adjuster output member AD1B-M2 101 A-M2 of transition flexing adjuster AD1A 101 A can be used to adjust the rotational position of torque transmitting member CS2A-M2 22A-M2.
  • cone assembly CS2B 22B is identical to cone assembly CS2A 22A, except that is mounted on the output shaft SH4 14 instead on the input shaft SH3 13, the only difference between constraining mechanism CN1B 11 IB and constraining mechanism CN1A 111A is that is mounted on cone assembly CS2B 22B instead of cone assembly CS2A 22A.
  • a mover adjuster AD2A 102A and a mover adjuster AD2B 102B which are basically identical to the transition flexing adjuster 101 A and is shown in detail in Fig. 6, are used.
  • Mover adjuster AD2A 102A has an adjuster body AD2A-M1 102A-M1 and an adjuster output member AD2A-M2 102A-M2.
  • mover adjuster AD2B 102B has an adjuster body AD2B-M1 102B-M1 and an adjuster output member AD2B-M2 102B-M2.
  • the adjuster body AD2A-M1 102A-M1 of mover adjuster AD2A 102A is keyed to the input shaft SH3 13, and cone assembly CS2A 22A is fixed to the adjuster output member AD2A-M2 102A-M2 of mover adjuster AD2A 102A.
  • the body of mover adjuster AD2B 102B is keyed to the output shaft SH4 14, and cone assembly CS2B 22B is fixed to the output member AD2B-M2 of mover adjuster AD2B 102B.
  • a computer CPl 121 which controls these adjusters based on the input of a transmission ratio sensor SN1A 131 A, a rotational position sensors SN2A 132A, a rotational position sensor SN2B 132B, a relative rotational position sensor SN3A 133A, which shown in detail in Fig. 7, and a relative rotational position sensor SN3B 133B, is used.
  • the transmission ratio sensor SN1 131 is mounted on a frame so that it ban be used to monitor the rotation of the transmission ratio gear rack gear via a sensor strip attached to the transmission ratio gear rack gear, so that computer CPl 121 can determine the transmission ratio, and hence the axial position of the torque transmitting members relative to the cones on which they are attached. And from that information computer CPl 121 can determine the pitch diameter, which as described earlier is the diameter of the surfaces of the cones where the torque transmitting members are positioned. A detailed description on how the transmission ratio gear rack and the transmission ratio gear rack gear are used to change the transmission ratio can be found in Patent #.
  • the rotational position sensors SN2A 132A is mounted on a frame so that it can monitor the rotational position of cone assembly CS2A 22A via a sensor strip attached to cone assembly CS2A 22A.
  • the rotational position sensors SN2B 132B is mounted on a frame so that it can monitor the rotational position of cone assembly CS2B 22B via a sensor strip attached to cone assembly CS2B 22B.
  • the relative rotational position sensor SN3A 133A consist of a sensor inner sleeve SN3A-M1 133AM1 and a sensor outer sleeve SN3A-M2 133AM2, were the sensor inner sleeve SN3A-M1 133A- Ml is located inside the sensor outer sleeve SN3A-M2 133A-M2.
  • the sensor inner sleeve SN3A-M1 133A-M1 and the sensor outer sleeve SN3A-M2 133A-M2 can rotate relative to each other.
  • the amount of rotation between the sensor inner sleeve SN3A-M1 133A-M1 and the sensor outer sleeve SN3A-M2 133 A-M2 can be monitored by computer CPl 121.
  • the sensor inner sleeve SN3A-M1 133A-M1 is keyed to the adjuster output member AD1A-M2 101A-M2 of transition flexing adjuster ADIA 101 A, and the sensor outer sleeve SN3A-M2 is mounted on the adjuster body AD1-M2 of transition flexing adjuster ADIA 101A.
  • the computer CPl 121 can determine the rotational position of the adjuster output member AD1A-M2 101 A-M2 relative to the rotational position of the adjuster body AD1A-M1 101A-M1. And hence the rotational position of torque transmitting member CS2A-M222A-M2 relative to torque transmitting member CS2A-M1 22A-M1.
  • a sensor SN3B 133B is mounted on the transition flexing adjuster AD1B 101B in the same manner as sensor SN3A 133A is mounted on transition flexing adjuster ADIA 101 A.
  • transition flexing adjuster AD3A 101 A, transition flexing adjuster AD3B 101B, relative rotational position sensor SN3A 133A, and relative rotational position sensor SN3B 133B are rotating relative to computer CPl 121, in order to connect the transition flexing adjusters and a relative rotational position sensors to the computer CPl 121, the ring and brush connection, is used.
  • An example of a ring and brush connection is shown in Fig. 9.
  • two output connections of computer CP 120 are directed to two pair of brushes, labeled as brush BR1A 141A and brush BR1B 141B, by cables.
  • Brush BR1 A 141 A is in contact with the positive electrical ring RN1A 151 A.
  • brush BR1B 141B is in contact with the negative electrical ring RN1B 15 IB.
  • the electrical rings are attached to the body of the adjuster by insulated fins RNlA-Sl 151 A-Sl and insulated fins RN1B-S1 151B-S1. And cables are used to direct the current or signal from the electrical rings to the electrical poles of the adjuster.
  • a configuration for the transition flexing adjuster ADIA 101 A which has an adjuster body ADl A-Ml 101A-M1 and an adjuster output member AD1A-M2 101A-M2 is shown in Fig. 4.
  • the adjuster output member AD1A-M2 101A-M2 can rotate relative to the adjuster body AD1A-M1 101 A-Ml, which is mounted at the end of the mover sleeve CS2A- M6 23A-M6.
  • the mover sleeve CS2A-M6 23A-M6 is almost identical to the mover sleeve used in CVT 1, hence it can also slide axially relative to its cone and is used to change the axial position of tits torque transmitting members.
  • the adjuster body ADl A-Ml 101A-M1 is fixed to the mover sleeve CS26-M5 23A-M6, but the adjuster output member ADl A-Ml 101A-M1 can rotate relative to the mover sleeve CS2A-M6 23A-M6.
  • the telescopes CS2A- M4 23A-M4, described in detail in Patent #, of torque transmitting member CS2A-M1 23 A- Ml are attached to the mover sleeve CS2A-M623A-M6, and the telescopes CS2A-M5 23A- M5 of torque transmitting member CS2A-M2 23A-M2 are attached to the adjuster output member AD1A-M2 101A-M2.
  • the adjuster output member AD1A-M2 101A-M2 has the following shapes, it has an adjuster output shaft ADl A-M2-S1 101 A-M2S1 on which an adjuster extension arm AD1A-M2-S2 101A-M2-S2 is attached.
  • the adjuster extension arm AD1A-M2-S2 101A-M2-S2 has an L-shape.
  • the short leg of the L-shaped adjuster extension arm ADl A-M2-S2 101 A-M2-S2 is extending radially outwards from the center of the front surface of the adjuster output shaft ADl A-M2-S1 101 A-M2-S1.
  • the long leg of the L-shaped adjuster extension arm AD1A-M2-S2 101A-M2-S2 is parallel to the adjuster output shaft ADl A-M2-S1 101 A-M2-S1 and is extending axially backwards so that the telescopes CS2A-M5 23A-M5 of torque transmitting member CS2A-M2 23A-M2 can be attached at the same axial position as the telescopes CS2A-M4 23A-M4 of torque transmitting member CS2A-M1 23A-M1.
  • This leg has two telescopes attachment plates AD1A-M2-S4 101A-M2- S4, used to attach the bottom end of the telescopes CS2A-M5 23A-M5 to this leg; and the constrainer slide 111 A-Ml is also attached to this leg.
  • an adjuster balancing arm AD1A-M2-S3 101A-M2-S3 which has the same shape as the adjuster extension arm ADl A- M2-S2 101A-M2-S2, is positioned opposite from the adjuster extension arm AD1A-M2-S2 101A-M2-S2 on the front surface of the adjuster output shaft adjuster ADl A-M2-S1 101 A- M2-S1.
  • a constrainer mechanism CN1A 111 A shown in Fig. 10 is attached to the long leg of the L- shaped adjuster extension arm ADl A-M2-S2 101 A-M2-S2.
  • the constrainer mechanism consist of a constrainer slide CN1A-M1 111A-M1, that is placed between the mover telescopes attachment plates of the long leg of the L-shaped adjuster extension arm ADl A- M2-S2 101 A-M2S2; a constrainer slider CN1A-M2 111 A-M2, that is slideably inserted into the constrainer slide CN1A-M1 111 A-Ml; and two constrainer links CN1 A-M3 111A-M3, each connecting the bottom member of telescope CS2A-M5 22A-M5 to the constrainer slider CN1 A-M2 111 A-M2.
  • the constrainer slide CN1 A-Ml 111 A-Ml is shaped like slender round rod, on which the constrainer slider CN1 A-M2 111A-M2 is slideably inserted.
  • the constrainer slider CN1 A-M2 111 A-M2 is shaped like a sleeve, which has two identical slider clevises CN1A-M2-S1 11A-M2-S1 which are positioned opposite of each other.
  • Each slider clevis of the constrainer slider consist of two slider clevis plates, which are parallel flat plates, which flat surfaces are perpendicular to the surface of the constrainer slider. And each slider clevis plate has a hole and the outer edge of each slider clevis pivot plate is rounded- off.
  • Each constrainer link CN1 A-M3 111 A-M3 is shaped like slender flat bar that has a hole, which is slightly larger than the holes of the slider clevis plates, at each end.
  • the end of each constrainer link is rounded-off so that a half disk shape, which diameter is identical to the width of the constrainer link and which center is located at the center of the constrainer link hole, exist at each end of the constrainer link.
  • the bottom member of each telescopes CS2A-M5 22A-M5 for torque transmitting member CS2A-M222A-M2 also has a telescope constrainer clevis CS2A-M5-S1 22A-M5-S1.
  • Each telescope constrainer clevis consist of two parallel telescope constrainer clevis plates.
  • the telescope constrainer clevis plates are flat plates, which flat surfaces are perpendicular to the surfaces of their mover telescopes.
  • Each telescope constrainer clevis plate has a hole, which is slightly smaller than the constrainer link holes, and the outer edge of each telescope constrainer clevis plate is rounded-off.
  • constrainer pins CNl A-M3 111 A-M4 are used.
  • the constrainer pins CNl A-M4 111A-M4 are shaped like slender round rods.
  • one hole of each constrainer link CNl A-M3 111 A-M3 is placed between the slider clevis plates of a slider clevis CN1A-M2-S1 111A-M2S1, such that a constrainer pin CN1A-M2 111A-M2 can be inserted through the constrainer link holes and those slider clevis holes.
  • the body of a constrainer pin CNl A-M4 111 A-M4 has a diameter small enough such that a constrainer link CNl A-M3 111 A-M3 can freely rotate on it, but large enough such that a constrainer pin CNl A-M3 111A-M3 can be securely held in place relative to the slider clevises CNl A-M2- S 1 111 A-M2-S 1 by friction between the slider clevis holes and the body of constrainer pin CNl A-M4 111A-M4.
  • the constrainer pins CNl A-M4 111 A-M4 are long enough such that sufficient engagement between the constrainer pins CNl A-M2 111 A-M4 an a set of slider clevis plates of a slider clevis CN1A-M2-S1 111A-M2-S1 can exist.
  • each constrainer link CN1A-M2-S1 111A-M2-S1 is placed between a set of telescope constrainer clevis plates of a telescope constrainer clevis CS2A-M5-S1 22A-M5-S1, such that a constrainer pin CN1A-M3 111 A-M4 can be inserted through the holes of the constrainer links and the telescope constrainer clevis plates holes.
  • the constrainer pin has a diameter small enough such that the constrainer link can freely rotate on it, but large enough such that it can be securely held in place relative to the telescope constrainer clevises by friction between the telescope constrainer clevis holes and the constrainer pin.
  • the constrainer pins are long enough such that sufficient engagement between the constrainer pins and a set of telescope constrainer clevis plates can exist.
  • the torque transmitting member CS2A- Ml 22A-Ml is rotatably constrained relative to mover sleeve CS2A-M622A-M6, and torque transmitting member CS2A-M2 22A-M2 is rotatably constrained relative to the adjuster output member AD2A-M2 102A-M2, and since the adjuster output member AD2-M2 102A- M2 can rotate relative to the mover sleeve CS2A-M6 22A-M6, the transition flexing adjuster AD2A 102A can be used by computer CPl 121 to adjust the rotational position of the torque transmitting member CS2A-M2 22A-M2 relative to torque transmitting member CS2A-M1 22 A-Ml.
  • CVT 1.1 has two identical cone assemblies, one on the input shaft SH3 13, which is labeled as cone assembly CS2A 22 A, and another one on the output shaft SH4 14, which is labeled as cone assembly CS2B 22B.
  • the transition flexing adjuster AD2B is identical to transition flexing adjuster AD2A, and is mounted on cone assembly CS2B 22B in the same manner as transition flexing adjuster AD2A is mounted on cone assembly CS2A 22A.
  • mover adjusters AD2A and AD2B which will be used to maintain CVT 1.1 in a moveable configuration regardless of the rotational position of the input shaft SH3 13 and the output shaft SH4 14, are described.
  • movable adjuster AD2A is used to allow cone assembly CS2A 22A, positioned on the input shaft SH3 13, to slip relative to the input shaft SH3 13.
  • movable adjuster AD2B is used to allow cone assembly CS2B 22B, positioned on the output shaft SH4 14, to slip relative to the output shaft SH4 14.
  • the adjuster body AD2A-M1 102A-M1 of movable adjuster AD2A is keyed to the input shaft SH3 13 so that it is constrained from rotating and moving axially relative to input shaft SH3 13.
  • the cone assembly CS2A 22A is fixed to the adjuster output member AD2A- M2 102A-M2 of movable adjuster AD2A 102A so that is constrained from rotating and moving axially relative the adjuster output member AD2A-M2 102A-M2.
  • mover adjuster AD2A 102A In order to mount mover adjuster AD2A 102A to input shaft SH3 13, mover adjuster AD2A 102A has a mounting hole, which center is located at the center-axis of mover adjuster AD2A 102 A and goes through the entire axial length of mover adjuster AD2A 102A, except through the adjuster attachment flange, which has a mounting hole of smaller diameter.
  • the diameter of mounting hole of mover adjuster AD2A 102A is considerably larger than the diameter of output shaft SHI 3 13 so that output shaft SHI 3 13 can freely rotate relative to mover adjuster AD2A 102 A.
  • the adjuster body AD2A-M1 102A-M1 has an adjuster attachment flange AD2A-M1-S1 102A-M1-S1 that extends axially backwards from the adjuster body AD2A-M1.
  • the diameter of the mounting hole of the adjuster attachment flange is slightly larger than the diameter of input shaft SH3 13, so that the adjuster body AD2A-M1 102 A-Ml can be securely mounted on input shaft SH3 13.
  • the adjuster attachment flange has a set-screw that is used to prevent the adjuster body AD2A-M1 102A-M1 from rotating relative to input SH3 13.
  • the mover adjuster AD2B 102B is used to mount cone assembly CS2B 22B on output shaft SH4 14 in the same manner as the mover adjuster AD2A 102A is used to mount cone assembly CS2A 22A on input shaft SH3 13.
  • the rotational position of the cone assembly CS2A 22A which is mounted on the input shaft SH3 13
  • the rotational position of cone assembly CS2B 22B, which is mounted on the output shaft SH4 14 is monitored by computer CPl 121 via rotational position sensor SN2A 132A.
  • transition flexing adjuster ADIA 101 A transition flexing adjuster AD1B 101B, mover adjuster AD2A 102A, and mover adjuster AD2B 102B will described.
  • torque transmitting member 1 1 is in contact with the transmission belt 3 while torque transmitting member 22 is not.
  • the lower positioned space between the torque transmitting members which in this case is non-torque transmitting arc A 4 needs to be a multiple of the width of the teeth of the torque transmitting members. If this is the case then no adjustment for the rotational position of torque transmitting member 22 relative to torque transmitting member 1 1 is needed.
  • a transition flexing adjuster needs to rotate one torque transmitting member clockwise or counter-clockwise relative to the other torque transmitting member such that the non-torque transmitting arc A 4 is a multiple of the width of the teeth of the torque transmitting members.
  • the rotation provided by the transition flexing adjuster is shown as ⁇ a.
  • the transition flexing adjuster maintains the relative rotational position between the torque transmitting members, such that the non-torque transmitting arc A 4, which is covered by the transmission belt 3 remains a multiple of the width of the teeth of the torque transmitting members.
  • torque transmitting member 1 1 comes out of contact with the transmission belt 3, as shown in Fig. 1 IC.
  • the lower positioned space between the torque transmitting members which in this case is non-torque transmitting arc B 5
  • the lower positioned space between the torque transmitting members which in this case is non-torque transmitting arc B 5 needs to be a multiple of the width of the teeth of the torque transmitting members.
  • the rotation provided by the transition flexing adjuster is also shown as ⁇ a.
  • both the torque transmitting member 1 1 and the torque transmitting member 2 2, as shown in Fig. 1 ID, are in contact with the transmission belt 3.
  • the transition flexing adjuster maintains the relative rotational position between the torque transmitting members, such that the non-torque transmitting arc B 5, which is covered by the transmission belt 3 remains a multiple of the width of the teeth of the torque transmitting members.
  • the lower positioned non- torque transmitting arc is the critical non-torque transmitting arc, since it is the non-torque transmitting arc that is about to be covered by the transmission belt so that it has to be adjusted immediately.
  • the upper positioned non-torque transmitting arc is the critical torque transmitting arc.
  • Graphs showing the required relative rotation between the torque transmitting members (1 ⁇ ) vs. the arc length of the critical non-torque transmitting arc (lc) are shown in Fig. 12A, 12B, 12C.
  • the y-axis represents the required arc length 1 ⁇ that one torque transmitting member has to be rotated relative to the other.
  • a positive value for theta represents counter-clockwise rotation
  • a negative value for theta represent clockwise rotation.
  • the x-axis represents the arc length of the critical non-torque transmitting arc lc.
  • the width wt corresponds to the width of the teeth of the torque transmitting members.
  • the computer CPl 121 monitors the rotational position of the cone assemblies CS2A 22A and CS2B 22B using the rotational position sensors SN2A 132A and SN2B 132B, and once the cone assemblies are in a moveable configuration, such as shown in Fig. 3, the moveable adjusters AD2A 102 A and AD2B 102B allow the cone assemblies to slip relative to their shaft such that they are maintained in a movable configuration. Then the transmission ratio is changed. In cases where the adjusters can not be maintained in a moveable configuration, then the moveable adjusters can be used to at least increase the duration that the cone assemblies are in a moveable configuration.
  • CVT 2.1 is almost identical to CVT 2 of Patent #.
  • CVT 2 which is shown in Fig. 13, consist mainly of two transmission pulleys, transmission pulley PUl A 41 A and transmission pulley PU1B 41B, and two cone assemblies which each have a torque transmitting member and a non-torque transmitting member, cone assembly CS3A 23A and cone assembly CS3B 23B.
  • the torque transmitting member of cone assembly CS3A 23A is labeled as torque transmitting member CS3A-M1 23A-M1; and the torque transmitting member of cone assembly CS3B 23B is labeled as torque transmitting member CS3B-M1 23B-M1.
  • non-torque transmitting member of cone assembly CS3A 23 A is labeled as non-torque transmitting member CS3A-M2 23A-M2; and the non-torque transmitting member of cone assembly CS3B 23B is labeled as non-torque transmitting member CS3B-M223B-M2.
  • the cone of cone assembly CS3A is labeled as cone CS3A-M3 23A-M3
  • the cone of cone assembly CS3B is labeled as cone CS3B-M3 23B-M3.
  • Each torque transmitting member is attached to its cone such that it can slide axially relative to its cone, but is restrained from rotating relative to the its cone.
  • the transmission pulleys PUl A 41 A and PU1B 41B are keyed to a spline sleeve SP1A 51 A, which is slideably mounted on the input spline shaft SH5 15, and the cone assemblies CS3A 23 A and CS3B 23B are keyed to the output shaft SH6 16 in a manner such that the torque transmitting member of one cone assembly is positioned opposite from the torque transmitting member of the other cone assembly.
  • a transmission belt BL2A 32A is used to couple transmission pulley PU1A 41 A with cone assembly CSB3A 23A, in a manner such that torque transmitting member CS3A-M1 23A-M1 can properly engage with transmission belt BL2A 32A.
  • a transmission belt BL2B 32B is used to couple transmission pulley PU1B 41B with cone assembly CS3B 23B, in a manner such that torque transmitting member CS3B-M1 can properly engage with transmission belt BL2B 32B.
  • the transmission ratio is changed by changing the axial position of the torque transmitting members and the transmission pulleys relative to surface of their cone assembly, in a manner such that for all transmission ratios, the torque transmitting members can properly engage with their transmission pulley.
  • the transmission ratio should only be changed when only one torque transmitting member is in contact with its transmission belt.
  • each transmission belt has two tensioning wheels.
  • the tensioning wheels for transmission belt BL2A 32A are labeled as tensioning wheel TW1 A 61 A and tensioning wheel TW1B 6 IB.
  • tensioning wheel TW1C 61 C tensioning wheel TW1D 6 ID.
  • Each tensioning wheel is always in contact with the inner surface of its transmission belt, and is positioned between its cone assembly and its transmission pulley. For each transmission belt, one tensioning wheel is in contact with the slack side of the transmission belt, and the other tensioning wheel is in contact with the tight side of the transmission belt.
  • CVT 2.1 which is shown in Fig. 14, 15A, 15B, 15C, and 15D is slightly different than CVT 2, like CVT2, CVT 2.1.
  • the two transmission pulleys are mounted on the input spline shaft, which here is labeled as input spline shaft SH7 17, by the use of an spline sleeve SP1B 5 IB.
  • each transmission pulley is coupled to a cone assembly with a torque transmitting member and a non-torque ttansmitting member that are directly mounted on an output shaft, which here is labeled as output shaft SH8 18 by a transmission belt.
  • cone assemblies are labeled as cone assembly CS3C 23C and cone CS3D 23D
  • the transmission belts are labeled as transmission belt BL2C 32C and transmission belt BL2D 32D.
  • torque transmitting member of cone assembly CS3C 23C is labeled as torque transmitting member CS3C-M1 23C-M1
  • torque transmitting member of cone assembly CS3D 23D is labeled as torque transmitting member CS3D-M1 23D-M1.
  • non-torque transmitting member of cone assembly CS3C 23C is labeled as non-torque transmitting member CS3C-M223C-M2, and the non-torque transmitting member of cone assembly CS3D 23D is labeled as torque transmitting member CS3D-M1 23D-M2.
  • the cone of cone assembly CS3C is labeled as cone CS3C-M223C-M3
  • the cone of cone assembly CS3C is labeled as cone CS3C-M3 23C-M3.
  • CVT 2 for CVT 2.1 for each transmission belt, only one tensioning wheel is used.
  • tensioning wheels operate and are mounted in the same manner as the tensioning wheels mounted on the slack side of the transmission belts of CVT 2.
  • tensioning wheel for ttansmission belt BL2C 32C is labeled as tensioning wheel TW1E 6 IE
  • tensioning wheel for transmission belt BL2D 32D is labeled as tensioning wheel TW1E 61F.
  • an adjuster AD3 103 is used for CVT 2.1.
  • adjuster AD3 103 has an adjuster body AD3-M1 103-M1 and an adjuster output member AD3-M2 103-M2, that can rotate relative to the adjuster body AD3-M1 103-M1.
  • the adjuster body AD3-M1 is mounted on spline sleeve 5 IB so that it is axially and rotatably constrained relative to spline sleeve 5 IB using a set-screw.
  • the transmission pulley PU1B 41B is fixed via a load cell SN4C 134C, so that they are virtually axially and rotatably constrained relative to each other.
  • transmission pulley PU1B 41B can rotate relative to spline sleeve 51B.
  • no adjuster is used to mount transmission pulley PU1D 4 ID to spline sleeve 5 IB.
  • transmission pulley PU1D 4 ID is mounted to spline sleeve 5 IB via load cell SN4D 134D, so that transmission pulley PU1D 41D virtually axially and rotatably constrained relative to spline sleeve 5 IB.
  • a computer CP2 122 which controls adjuster AD3 103 based on the input from a transmission ratio sensor 131 , a rotational position sensor SN2C 132C, a rotational position sensor SN2D 132D, a rotational position sensor SN2D 132D, a load cell SN4C 134C, and a load cell SN4D 134D is used.
  • the transmission ratio sensor 131 is mounted on a frame so that it can be used to monitor the rotation of the transmission ratio gear rack gear via a sensor strip attached to the transmission ratio gear rack gear, so that computer CP2 122 can determine the transmission ratio, and hence the axial position of the torque transmitting members relative to the cones on which they are attached. And from that information computer CP2 122 can determine the pitch diameter, which as described earlier is the diameter of the surfaces of the cones where the torque transmitting members are positioned.
  • Patent # A detailed description on how the transmission ratio gear rack and the transmission ratio gear rack gear are used to change the ttansmission ratio can be found in Patent #.
  • the rotational position sensors SN2E 132E is mounted on a frame so that it can be used to monitor the rotational position of output shaft SH8 18 via a sensor strip attached indirectly to output shaft SH8 18. And from that information computer CP2 122 can determine the rotational position of the torque transmitting members.
  • the rotational position sensor SN3C 133C is mounted on a frame so that it can be used to monitor the rotational position of ttansmission pulley PU1C 41C via a sensor strip attached to transmission pulley PU1C 41C.
  • rotational position sensor SN3D 133D is mounted on a frame so that it can be used to monitor the rotational position of transmission pulley PU1D 41D via a sensor strip attached to transmission pulley PU1D 4 ID.
  • computer CP2 122 can determine the absolute rotational position of the ttansmission pulleys and the rotational position of one transmission pulley relative to the other.
  • the load cells SN4C 134C and SN4B 134D which each have a body and an output shaft, can measure the torque applied between their body and their output shaft. However unlike and adjuster, no significant rotation between the body and the output shaft of an adjuster is allowed.
  • Load cell SN4A 134C is used to measure the pulling load on ttansmission pulley PU1C 41C due to the torque at input spline shaft SH7 17 and the rotational resistance provided by the cone assembly CS3C 23C.
  • load cell SN4B 134B is used to measure the pulling load on ttansmission pulley PU1C 41D due to the torque at input spline shaft SH7 17 and the rotational resistance provided by cone assembly CS3D 23D.
  • load cell SN4C 134C is fixed to the adjuster output member AD3-M2 103-M2 and the output shaft of load cell SN4C 134C is fixed to transmission pulley PUIC 41C; and the body of load cell SN4B 134B is keyed to the input spline SPIB 51B, and ttansmission pulley PUIC 41C is keyed to the output shaft of load cell SN4A 134A.
  • the rotational position between transmission pulley PUIC 41C and transmission pulley PUID 41D is adjusted by adjuster AD3A 103A.
  • the procedure to eliminate transition flexing is similar to the procedure to eliminate transition flexing for CVT 1.2 as shown in Figs. 11 A-l ID.
  • the rotational position of torque transmitting member 1 1 relative to torque transmitting member 2 2 is adjusted, here the rotational position of transmission pulley PUID 41D relative to ttansmission pulley PUIC 41C is adjusted.
  • point N is the neutral point, where almost no sliding between the transmission belts and the surfaces of the cone assembly occur when the pitch diameter of the cone assembly is changed. This is because the length of the transmission belts from point N to the point where the vertical-mirror line of the ttansmission pulleys intersect the surfaces of the transmission pulleys remain almost constant, since the center distance between the cone assemblies and the transmission pulleys does not change. However this is only true for a reasonable change in diameter of the cone assemblies.
  • point N might be positioned elsewhere.
  • the amount of transmission ratio change rotation depends on the angle ⁇ , which is the angle between the midpoint of the torque transmitting member, point M, and point N.
  • the direction of transmission ratio change rotation depends on whether the midpoint of the torque transmitting member is positioned to the left or to the right of point N, and on whether the pitch diameter of the torque transmitting member is increased or decreased.
  • clockwise ttansmission ratio change rotation occurs when the pitch diameter is increased and the center of the torque transmitting member is positioned to the left of point N, and when the pitch diameter is decreased and the center of the torque transmitting member is positioned to the right of point N.
  • counter-clockwise transmission ratio change rotation occur when the pitch diameter is increased and the center of the torque transmitting member is positioned to the right of point N, and when the pitch diameter is decreased and the center of the torque transmitting member is positioned to the left of point N.
  • adjuster AD3 103 is used to adjust the rotational position of transmission pulley PUIC 41C relative to ttansmission pulley PUIC 41C.
  • adjuster AD3 103 is used to rotate transmission pulley PUID 41D relative to transmission pulley PUIC 41 C such that the pulling loads on the transmission pulleys, as measured by load cell SN4C 134C and load cell SN4D 134D, are about equal.
  • the adjuster system for CVT 4 can also be used to compensate for wear that causes unequal pulling loads in the transmission pulleys.
  • adjuster AD3 103 is used to eliminate transition flexing in instances where the circumferences of the surfaces of the cone assemblies where the torque transmitting members are positioned are not a multiple of the width of the teeth of the torque transmitting members. Note, the operation to eliminate transition flexing of adjuster AD3 103 also occurs in instances where the transmission ratio is not changed. Hence in this instance adjuster AD3 103 is not used to compensate for transmission ratio change rotation, despite the fact that due to transition ratio change rotation the cone assemblies are rotated counter-clockwise.
  • the ttansmission ratio change rotation of cone assembly CS3D 23D is always counter-clockwise. From Fig. 17B and 17C it can be seen that here if torque ttansmitting member CS3C-M1 23C-M1 is positioned to the left of point N, ⁇ D is always greater than ⁇ c. Hence, regardless of whether the transmission ratio change rotation of cone assembly CS3C 23C is clockwise or counter-clockwise, here changing the transmission ratio causes cone assembly CS3D 23D to rotate counter-clockwise relative to cone assembly CS3C 23C. In order to compensate for the transmission ratio change rotation, adjuster AD3 103 needs to rotate transmission pulley PUIC 41C counterclockwise relative to transmission pulley PUIC 41D.
  • the pulling load in the transmission pulleys PUIC 41C and PUID 41D will be used to conttol the rotation of adjuster AD3 103.
  • the adjuster AD3 103 rotates transmission pulley PUIC 41C counter-clockwise relative to transmission pulley PUIC 41D.
  • the adjuster AD3 103 stops rotating.
  • the adjuster AD3 103 is active in instances where the circumferences of the surfaces of the cone assemblies where the torque ttansmitting members are positioned are not a multiple of the width of the teeth of the torque ttansmitting members. Since in this instance only one torque transmitting member is contact with its ttansmission belt, it is not necessary for adjuster AD3 103 to compensate for transmission ratio change rotation, despite the fact that due to transmission ratio change rotation cone assembly CS3D 23D, and hence the output shaft SH8 18, is rotated counter-clockwise. Since some counter-clockwise rotation applied to cone assembly CS3D 23D, which causes slippage at the output shaft SH8 18, slightly reduces the performance of the CVT but is not damaging the CVT.
  • the adjuster AD3 103 is used to compensate for transition flexing in instances where the circumferences of the surfaces of the cone assemblies where the torque transmitting members are positioned are not a multiple of the width of the teeth of the torque ttansmitting members. Since in this instance only one torque transmitting member is in contact with its transmission belt, it is not necessary for adjuster AD3 103 to compensate for transmission ratio change rotation, despite the fact that due to transition ratio change rotation the cone assemblies are rotated counter-clockwise. Since some counter-clockwise rotation of the cone assemblies, which causes slippage at the output shaft, slightly reduces the performance of the CVT but is not damaging the CVT.
  • the adjuster AD3 103 is used to compensate for transmission ratio change rotation.
  • the adjuster AD3 103 needs to rotate ttansmission pulley PUIC 41C clockwise relative to transmission pulley PUID 41D.
  • the pulling load in the transmission pulleys PUIC 41 C and PUID 4 ID will be used to control the rotation of adjuster AD3 103.
  • the adjuster AD3 103 rotates transmission pulley PUIC 41C clockwise relative to transmission pulley PUID 41C. And once the difference in pulling load between ttansmission pulleys has reached an acceptable value, the adjuster AD3 103 stops rotating.
  • the adjuster AD3 103 is used to eliminate transition flexing in instances where the circumferences of the surfaces of the cone assemblies where the torque ttansmitting members are positioned are not a multiple of the width of the teeth of the torque transmitting members.
  • adjuster AD3 103 is not used to compensate for ttansmission ratio change rotation, despite the fact that ttansmission ratio change rotation rotates cone assembly CS3C-M1 23C-M1, and hence output shaft SH8 18, clockwise. Since some counter-clockwise rotation applied to cone assembly CS3D 23D, which causes slippage at the output shaft SH8 18, slightly reduces the performance of the CVT but is not damaging the CVT.
  • adjuster AD3 103 is used to eliminate transition flexing in instances where the circumferences of the surfaces of the cone assemblies where the torque ttansmitting members are positioned are not a multiple of the width of the teeth of the torque ttansmitting members. Since in this instance only one torque transmitting member is in contact with its transmission belt, the adjuster AD3 103 is not used to compensate for transmission ratio change rotation, despite the fact that due to transition ratio change rotation the cone assemblies are rotated clockwise for the same reason discussed earlier.
  • adjuster AD3 103 is used to compensate for transmission ratio change rotation. As discussed earlier, here the direction of the transmission ratio change rotation is simply opposite from that were the transmission ratio is decreased. And as described before here a larger angle between the midpoint of a torque ttansmitting member and point N, results in a larger ttansmission ratio change rotation.
  • the adjuster AD3 103 rotates ttansmission pulley PUID 41D counter-clockwise relative to ttansmission pulley PUIC 41C. And once the difference in the pulling load between transmission pulleys has reached an acceptable value, the adjuster AD3 103 stops rotating.
  • the adjuster AD3 103 is active in instances where the circumferences of the surfaces of the cone assemblies where the torque transmitting members are positioned are not a multiple of the width of the teeth of the torque transmitting members. Since in this instance only one torque ttansmitting member is in contact with its transmission belt, the adjuster AD3 103 is not used to compensate for ttansmission ratio change rotation, despite the fact that transmission ratio change rotation rotates cone assembly CS3D-M1 23D-M1, and hence output shaft SH8 18, clockwise. Since some clockwise rotation applied to the output shaft SH8 18 is not damaging the CVT, and actually increases the total amount of rotation at the output shaft SH8 18.
  • the adjuster AD3 103 is not used to compensate for ttansmission ratio change rotation in instances where the circumferences of the surfaces of the cone assemblies where the torque transmitting members are positioned are not a multiple of the width of the teeth of the torque transmitting members. In this instance the adjuster AD3 103 is not used to compensate for transmission ratio change rotation, despite the fact that due to transition ratio change rotation the cone assemblies are rotated clockwise for the same reasons discussed earlier.
  • the adjuster AD3 103 is used to compensate for transmission ratio change rotation.
  • the direction of the transmission ratio change rotation is simply opposite from that were the transmission ratio is decreased.
  • a larger angle between the midpoint of a torque ttansmitting member and point N results in a larger ttansmission ratio change rotation.
  • the adjuster AD3 103 rotates ttansmission pulley PUIC 41C counter-clockwise relative to ttansmission pulley PUID 41D. And once the difference in pulling load between transmission pulleys has reached an acceptable value, the adjuster AD3 103 stops rotating.
  • adjuster AD3 103 is used to eliminate transition flexing in instances where the circumferences of the surfaces of the cone assemblies where the torque transmitting members are positioned are not a multiple of the width of the teeth of the torque ttansmitting members.
  • the adjuster AD3 103 is not used to compensate for the transmission ratio change rotation, despite the fact that transmission ratio change rotation rotates cone assembly CS3C-M1 23C-M1, and hence output shaft SH8 18, clockwise. Since some clockwise rotation applied to the output shaft SH8 18 is not damaging the CVT, and actually increases the total amount of rotation at the output shaft SH8 18.
  • the adjuster AD3 103 needs to rotate ttansmission pulley PUID 41D clockwise relative to transmission pulley PUIC 41 C, the adjuster AD3 103 needs to provide a pulling torque, which might be quite large, since it has to overcome the rotational resistance of cone assembly CS3C 23C. This situation is similar to a situation where a load is pulled up a cliff. And in instances where adjuster AD3 103 needs to rotate transmission pulley PUIC 41C counter-clockwise relative to ttansmission pulley PUIC 41C, adjuster AD3 103 needs to provide a releasing torque, which allows cone assembly CS3C 23C to slip.
  • the releasing torque does not have to provide torque that overcomes the rotational resistance of cone assembly CS3C 23C.
  • the only load adjuster AD3 103 needs to exert is due to friction This situation is similar to a situation where a load is lowered down a cliff using a winch which has a locking mechanism that prevents the load from going down the cliff without any input at the which.
  • All the adjusters described in this invention consist of an adjuster body and an adjuster output member, that can rotate relative to the adjuster body.
  • the adjuster output member In order for the adjuster to transmit torque from a ttansmission pulley or a cone assembly that is fixed to the adjuster output member to the shaft to which the adjuster body is fixed, the adjuster output member has to be able to hold the adjuster output member fixed relative to the adjuster body despite the fact that torque is applied at the adjuster output member. This can be can be achieved by using an electrical brake or a holding mechanism.
  • a holding mechanism is used for the electrical adjuster 160, shown in Fig 21 A and 2 IB.
  • the adjuster motor 160-Ml drives a worm gear 160-M2, which engages with an adjuster gear 160-M3.
  • the helix angle of the worm gear 160-M2, ⁇ is designed such that the worm gear 160-M2 can drive the adjuster gear 160-M3 but the adjuster gear 160-M3 can't drive the worm gear 160-M2.
  • the worm gear 160-M2 and the adjuster gear 160-M3 form the holding mechanism that allows the torque applied at the adjuster output member to be transmitted to the adjuster body.
  • the body of the adjuster consist mainly of an attachment sleeve 160-M4, which has an attachment sleeve arm 1 160-M4-S1 and an attachment sleeve arm 2 160-M4-S2, an adjuster motor holder 160-M6, and a counter-weight 160-M7.
  • the attachment sleeve 160-M4 is fixed to an input shaft, output shaft, or a mover sleeve, so that it is rotatably and axially constrained relative to the shaft or sleeve on which it is attached using a electrical adjuster set screw 160- M5.
  • attachment sleeve arm 1 160-M4-S1 Extending radially outwards from the side surfaces of the attachment sleeve 160-M4 are the two attachment sleeve arms 160-M4S1 and 160-M4S2. Attached to attachment sleeve arm 1 160-M4-S1 is the adjuster motor holder 160-M7, on which the adjuster motor 160-Ml is pressed in such that due to friction, the adjuster motor 160-Ml can not move axially or rotate relative to the adjuster motor holder 160-M7.
  • counter-weight 160-M8 is attached to the attachment sleeve arm 160-M4-S2 to counter-weight 160-M8, which is used to counter-balance the centrifugal force of the adjuster motor holder 160-M7, the adjuster motor 160-Ml, and the worm gear 160-M2.
  • the additional adjuster motor can be used to increase the torque capacity of the electrical adjuster 160, or it can be used as a back- up in case the main adjuster motor 160-Ml fails.
  • attachment sleeve fins 160-M4-S3 extending axially backwards from the attachment sleeve 160-M4 are four attachment sleeve fins 160-M4-S3 , spaced at 90 deg. from each other, on which two electrical rings 160- M6 are securely pressed in, as to prevent them from rotating or from moving axially relative to the attachment sleeve fins 160-M4S3.
  • Each electrical ring 160-M6 is connected to a pole/connection of the electrical motor 160-Ml.
  • the surfaces of the attachment sleeve fins 160-M4-S3 in contact with the electrical rings 160-M6 are insulated such that the electricity directed to the electrical rings 160-M6 by some electrical brushes are directed to the electrical poles of the adjuster motor 160-Ml by electrical cables 160-M9. If an electric motor that requires more than two input signals is used, than additional electrical rings 160-M6 and electrical cables 160-M9 are needed.
  • an attachment sleeve flange 160-M4-S4 Positioned axially in front of the attachment sleeve 160-M4 is an attachment sleeve flange 160-M4-S4, which is larger in diameter than the main body of attachment sleeve 160-M4. And positioned axially in front of the attachment sleeve flange 160-M4-S4 is an attachment sleeve extension 160-M4-S5, which is shaped like a hollow cylinder which has a smooth side surface, except at its front end, were it is threaded.
  • the adjuster gear 160-M3, with which the worm gear 160-M2 engages, is shaped like a spur gear, that has a centrically positioned cylindrical extension at its front surface.
  • the spur gear shaped portion of adjuster gear 160-M3 is labeled as spur gear 160-M3-S1.
  • an adjuster gear extension 160-M3- S2 which is shaped like a hollow cylinder, which center is positioned at the center of the spur gear 160-M3-S1.
  • And positioned axially in front of the adjuster gear extension 160-M3-S2 is an adjuster gear flange 160-M3-S3.
  • the adjuster gear flange 160-M3-S3 is shaped like a disk that has a thick rim.
  • the rim portion of adjuster gear flange 160-M3-S3 extends forwards beyond the surface of its disk shape.
  • two bolt holes that can be used to attach the electrical adjuster 160 to torque ttansmitting device such as a cone assembly, a transmission pulley, an attachment disk on which the mover telescopes of a torque transmitting member can be attached, etc.
  • the adjuster gear 160-M3 also has a centrically positioned hole that goes through all shapes of the adjuster gear 160-M3, so that it can be slid onto the attachment sleeve extension 160-M4-S5.
  • adjuster gear 160-M3 is slid onto attachment sleeve extension 160-M4-S5 until the back surface of adjuster gear 160-M3 is in contact with the attachment sleeve flange 160-M4- S4
  • the threaded portion of attachment sleeve extension 160-M4-S5 is not covered by the disk shaped portion of adjuster gear adjuster gear 160-M3 but is only covered by the flange shaped portion.
  • adjuster gear 160-M3 The engagement between the back surface of adjuster gear 160-M3 and the attachment sleeve flange 160-M4-S5 prevents the adjuster gear 160-M3 from moving axially backwards relative to the attachment sleeve 160-M4, and in order to prevent the adjuster gear 160-M3 from moving axially forwards relative to the attachment sleeve 160-M4, an electrical adjuster nut 160-Ml 0 is threaded onto the threaded portion of the attachment sleeve extension 160-M4-S5.
  • the adjuster gear 160-M3 Since the adjuster gear 160-M3 has to rotate relative to the attachment sleeve 160-M4, friction between the engaging surfaces of the attachment sleeve 160-M4, the adjuster gear 160-M3, and the electrical adjuster nut 160-Ml 0 should be minimized. This can be done by coating the engaging surfaces of the adjuster gear with bronze.
  • This CTTM CVT which is shown in Fig. 22, is almost identical to CVT 1.1, except that here one cone assembly is replaced with a pulley, and a tensioning mechanism, such as the one used in CVT 2.1, is needed. In this case only one moveable adjuster, one transition flexing adjuster, one rotational position sensor, and one relative rotational position sensor is needed.
  • CVT 2.2 shown in Fig. 23, is identical to CVT 2.1, except that here no load cells are used to properly control the relative rotational position of the ttansmission pulleys.
  • the rotational position sensors and relative rotational position sensors are used to conttol the rotational position of the transmission pulley.
  • the rotational position of the adjuster mounted ttansmission pulley is controlled based on the results obtained from the equation shown in Fig. 16, which should be continuously recalculated at short enough intervals.
  • CVT 2.3 shown in Fig. 24, is identical to CVT 2.1, except that here two adjusters are used, one for each ttansmission pulley. Under this configuration only the adjuster that needs to provide a releasing torque can be made activ, see last paragraph for CVT 2.1.
  • CVT 2.4 which is shown in Fig. 25, is almost identical to CVT 2.1; however here in order to eliminate transition flexing, the relative rotational movements between torque ttansmitting member 1 1 and torque ttansmitting member 2, as described for CVT 1.1, is used for torque transmitting member CS3C-M1 23C-M1 and torque transmitting member CS3D-M1 23D- Ml.
  • the front cone assembly, cone assembly CSB2 has to be rotated relative to the back cone assembly or vice- versa.
  • an adjuster AD4 104 that can adjust the rotational position of cone assembly CS3D 23D relative to cone assembly CS3C 23C is used.
  • a another simple method to eliminate transition flexing is by using a spring-loaded adjuster that biases a spring-loaded adjuster mounted torque ttansmitting member towards neutral position from which it can rotate clock-wise and counter-clockwise relative to the shaft on which it is attached.
  • a spring-loaded adjuster AS1 171 which can be used to replace the adjusters ADl of CVT 1.1 will be described
  • a spring-loaded adjuster AS2 172 that can be used as an adjuster AD4 104 for CVT 2.4 will be described.
  • triangular-shaped teeth are used.
  • Another simple method to eliminate transition flexing is by having a parallel gap in the slots where the pins used to attach a torque ttansmitting member to a cone assembly are inserted; and using a spring-loaded adjuster to bias the gap mounted torque transmitting member towards the center of the gap. This allows for some rotational movement of the gap mounted torque transmitting member in instances where the pitch diameter of the gap mounted torque ttansmitting member is increased and decreased.
  • a spring-loaded adjuster 171 is needed.
  • the spring-loaded adjuster 171 mainly consist spring-loaded adjuster shaft 171-M2 that can rotate relative to a spring-loaded adjuster body 171-M1, and is biased by a adjuster spring 171-M3 towards a neutral position.
  • a shaft end attachment 171-M4 is attached to the end of the spring-loaded adjuster shaft.
  • the shaft end attachment consist mainly of three shapes that form an inverted U-shape.
  • One leg of the inverted U-shape which is labeled as shaft end attachment extension arm 171- M4-S1, is shaped like the long leg of the adjuster extension arm AD1A-M2-S1 101A-M2-S1 of adjuster AD 1 A 101 A of CVT 2.1 and is used in the same manner, hence it also has a constrainer mechanism CNl A 111A.
  • the other leg of the inverted U-shape which is labeled as shaft end attachment balancing arm 171-M4-S2, is shaped like the long leg of the adjuster balancing arm AD1A-M2-S3 101A-M2-S3 and is used to balance the centrifugal forces of the shaft end attachment extension arm 171-M4-S1.
  • the top horizontal member of the inverted U-shape which is labeled as shaft end attachment mounting plate 171-M4-S3, is shaped like elongated rectangular plate that has a hexagonal cavity at its center.
  • the hexagonal cavity of the shaft end attachment mounting plate 171-M4-S3 is used to securely press in a matching hexgonal notch located at the top end of the spring-loaded adjuster shaft 171-M2.
  • the spring-loaded adjuster body 171-M1 is basically shaped like a hollow cylinder, which has an open top end and a closed bottom end.
  • the spring-loaded adjuster shaft 171 -M2 is basically shaped like a hollow cylinder, which has an open bottom end and a closed top end.
  • the outer top end of the spring-loaded adjuster shaft has a hexagonal notch, which is used to attach the shaft end attachment 171-M4.
  • the outer diameter of the spring-loaded adjuster shaft is 171-M2 slightly smaller than the inner diameter of the spring loaded adjuster body 171-M1, so that when the spring-loaded adjuster shaft 171 -M2 is inserted into the spring loaded adjuster body 171 -Ml, only significant rotational movements between them is allowed.
  • the outer surface of the top end of the spring-loaded adjuster body is threaded.
  • the outer surface of the spring loaded adjuster shaft 171-M2 has a spring-loaded adjuster flange 171-M2-S1, which diameter is slightly smaller than the outside diameter of the spring-loaded adjuster body.
  • the spring-loaded adjuster .flange 171-M2-S1 is positioned somewhere between the top end and the bottom end of the spring-loaded adjuster shaft 171-M2.
  • the spring-loaded adjuster flange should be positioned so that a sufficient amount of the spring-loaded adjuster shaft can be inserted into the spring loaded adjuster body so that sufficient amount of moment and deflection can be resisted by the assembled spring loaded adjuster 171.
  • An adjuster spring 171-M3 is inserted into the cavity formed by the inner top end surface and inner side surface of the spring-loaded adjuster shaft, and the inner bottom end surface and the inner side surface of the spring loaded adjuster body.
  • the wire of the adjuster spring is shaped such that a square shape, on which the square notches of the spring-loaded adjuster shaft and the spring loaded adjuster body can be tightly inserted, is formed.
  • the length of the adjuster spring is designed such that when the spring-loaded adjuster flange is engaged with the top end surface of the spring-loaded adjuster body, the top end and the bottom end of the adjuster spring is always in contact with the top surface of the spring- loaded adjuster shaft and the bottom surface of the spring-loaded adjuster body.
  • a spring-loaded adjuster cap 171-M5 is used.
  • the spring loaded adjuster cap 171-M5 is shaped like a short cylinder, which has a top surface but not a bottom surface.
  • the top surface of the spring-loaded adjuster cap has a hole at its center, which diameter is slightly larger than the diameter of the spring loaded adjuster shaft 171 -M2, but smaller than the diameter of the spring-loaded adjuster flange 171-M2-S1.
  • the inner surface of the side surface of the spring-loaded adjuster cap has internal threads that can engage with the external threads of the spring-loaded adjuster body 171-M1.
  • the spring-loaded adjuster 171 is assembled by first inserting the adjuster spring 171-M3 into the spring-loaded adjuster body 171 -Ml such that the bottom square shaped loop of the spring-loaded adjuster spring is fully inserted into the square shaped notch of the spring loaded adjuster body. Then the spring-loaded adjuster shaft is slid into the spring-loaded adjuster body, in a manner such that the open end of the spring-loaded adjuster shaft is facing the open end of the spring-loaded adjuster body, and the top square shaped loop of the spring- loaded adjuster spring is fully inserted into the square shaped notch of the spring-loaded adjuster shaft.
  • the spring-loaded adjuster cap is inserted through the top-end of the spring-loaded adjuster shaft and tighten unto the spring-loaded adjuster body through the engagement of the internal threads of the spring-loaded adjuster cap with the external threads of the spring loaded adjuster body.
  • the spring-loaded adjuster cap should be tighten unto the spring-loaded adjuster body until the inner top surface of the spring-loaded adjuster cap pushes the spring-loaded adjuster flange of the spring-loaded adjuster shaft towards the top surface of the spring-loaded adjuster body, so that axial movements between the spring- loaded adjuster shaft and the spring-loaded adjuster body is minimized.
  • the spring- loaded adjuster shaft has to rotate relative to the spring-loaded adjuster body, friction between the engaging surfaces of the spring-loaded adjuster cap, the spring-loaded adjuster shaft, and the spring-loaded adjuster body should be minimized. This can be done by coating the engaging surfaces of the spring loaded adjuster flange of the spring-loaded adjuster shaft with bronze.
  • the shaft end attachment 171-M4-S2 is attached the spring-loaded adjuster shaft.
  • the hexagonal notch at the outer top surface of the spring-loaded adjuster shaft 171-M2 is pressed into the hexagonal cavity of the shaft end attachment mounting plate 171 -M4-S3.
  • the dimension of the hexagonal cavity should be slightly smaller than the dimension of the hexagonal notch, so that sufficient friction between them to prevent any axial movements between them is developed when separating forces encountered during normal operation is applied to them.
  • the spring loaded adjuster AS2 172 shown in Fig. 27 A and 27B, can be used to replace the adjuster AD4 104 in CVT 2.4.
  • the spring loaded adjuster AS2 172 is identical to the spring- loaded adjuster AS1 171, except that here two radially opposite positioned threaded holes for two limiter rods 172-M1, are drilled into the spring-loaded adjuster shaft 170-M2. And two pairs of radially opposite positioned cylindrical limiter notches 142-M2 are welded on to the outer top surface of the spring-loaded adjuster cap 140-M5.
  • the limiter rods 142-M1 and the limiter notches 142-M2 should be positioned, such that the adjuster spring 140-M3 biases each limiter rod towards the midpoint of the space created between a pair of limiter notches 142-M2.
  • the mechanical adjuster AMI 181 which is shown in Fig. 28A and 28B, mainly consists of an adjuster body and an adjuster output member. However here, the rotational position between them is controlled by an adjustable ratio cam mechanism.
  • the adjuster body consist mainly of a cam 181-Ml, cam sleeve 181-M2, a follower 181-M4, and a follower spring 181-M5.
  • the cam 181-Ml is stationary relative to the shaft where the mechanical adjuster 1 181 is used.
  • the cam 181-Ml consist mainly of four shapes.
  • the top shape of the cam, top cam shape 181-Ml-Sl has a diameter Dl
  • the bottom shape of the cam, bottom cam shape 181-M2-S3 also has a diameter Dl
  • the right shape of the cam, right cam shape 181-M1-S2, and the left shape of the cam, left cam shape 181-M1-S4, have a diameter Dc.
  • the diameter Dc is larger than the diameter Dl.
  • ttansition shapes exist so that the cam 181-Ml has a smooth continuous surface.
  • the cam sleeve 181-M2 is shaped like a hollow cylinder, which has an open end and a closed end.
  • cam sleeve 181-M2 The closed end of the cam sleeve 181-M2 is shaped like a disk that has an cam sleeve attachment sleeve 181-M2-S2, which used to attach the shaft where the mechanical adjuster AMI 181 is used, which is labeled as shaft SH0 10.
  • cam sleeve attachment sleeve 181-M2-S2 has a threaded hole for a cam sleeve set screw 181-M3.
  • the cam sleeve 181-M2 has a radial hole, through which the follower 181-M4 is inserted.
  • cam sleeve constrainer sleeve 181-M2-S3 which has the same inside diameter as the radial hole exist.
  • cam sleeve constrainer sleeve 181-M2-S3 and cam follower 181-M4, and portions of the centrifugal forces due to a link AM1-M6 181-M6 and a link AM1-M7 181- M7, a cam sleeve counter- weight 181-M2-S4 is shaped opposite of the cam sleeve constrainer sleeve 181-M2-S3 on the surface of constrainer sleeve 181-M2.
  • controller rod counterweight arm 181-M2-S5 Also extending radially outwards from the surface of the cam sleeve 181-M2 is a controller rod counterweight arm 181-M2-S5.
  • the controller rod counter-weight arm 181-M2-S5 has a hole through which a controller rod counter-weight 181-Ml 1 will be slid through, so as to constrain the rotational position of the controller rod counter- weight 181-Ml 1 relative to the cam sleeve 181-M2.
  • the controller rod counter-weight arm 181-M2-S5 is positioned so that a controller rod 181-M10 can be properly slid through the controller slot of the link AM1-M6 181-M6.
  • a counter- weight arm counter- weight 181-M2-S6 is positioned opposite of the controller rod counter- weight arm 181-M2-S5.
  • the counter- weight arm counter-weight 181-M2-S6 is positioned on the inside of cam sleeve 181-M2, so that it does not interfere with the moving link AM1-M6 181-M6.
  • the follower 181-M4 consist mainly of four shapes.
  • the top shape of the follower which is labeled as follower top 181-M4-S1, is shaped like a flat bar that has a hole.
  • follower round 181 -M4-S2 The shape below it, which is labeled as follower round 181 -M4-S2, is shaped like a round rod. During normal operation of the mechanical adjuster AMI 181, this shape of the follower is in contact with the radial hole and the hole of the constrainer sleeve 181 -M2-S3 of cam sleeve 181 -M2, so that the follower 181 -M4 can only move radially in and out relative to cam sleeve 181-M2.
  • follower shoulder 181-M4-S3 is the shoulder of follower 181-M3. It is shaped like a round disk, which diameter is larger than the diameter of the shape above it.
  • the bottom shape which is labeled as follower bottom 181-M4-S4, is shaped like a half sphere.
  • the cam 181-Ml which is stationery relative to the shaft, is inserted into the open end of cam sleeve 181-M2 such that they are concentric; so that the bottom shape of the follower 181-M4 has a contacting surface on the cam 181-Ml.
  • a follower spring 181 -M5 is placed between the inner surface of cam sleeve 181 -M2 and follower shoulder 181-M4-S4.
  • the adjuster output member of the mechanical adjuster AMI 181 is shaped like disk, and it will be referred to as the output disk AM1-M8 181-M8.
  • the output disk AM1-M8 181-M8 has two opposite positioned bolt holes, which will be used to attach a cone assembly or a ttansmission pulley to the output disk.
  • the output disk AM1-M8 181-M8 has an output disk arm AM1-M8-S1 181-M8-S1, which is a radial extension that has a hole.
  • an output disk counter-weight AM1-M5-S2 181-M5-S2 is shaped opposite of the output disk arm AM1-M8-S2 181-M8-S2 on the surface of output disk AM1-M5 181-M8.
  • Link AM1-M6 181-M6 is shaped like a monkey wrench. It has a middle shape, and two end shapes. Each end shape, which is labeled as link shape AM1- M6-S1 181-M6-S1, is shaped like a square plate that has a hole.
  • link shape AM1-M6-S2 181-M6-S2 is shaped like a slender rectangular plate that has a controller slot.
  • the end shapes are parallel relative to each other but the middle shape is positioned diagonally relative to the end shapes.
  • the other link, link AM1- M7 181 -M7 is shaped like flat and slender bar that has two link holes at each of its ends.
  • the ends of link AM1-M7 181-M7 have half disk shape, which center is positioned at the center of the holes of link AM1-M7 181-M7.
  • link AM1-M6 181-M6 and link AM1-M7 181-M7 to connect the cam sleeve 181-M2 to the output disk 181-M3, one end of link AM1-M7 181-M7 is connected to the follower 181-M4 by inserting a link bolt 181-M9 through the hole of the follower 181-M4, and then securing that bolt using a link nut 181 -M12.
  • link AMI -M6 181-M6 is connected to one end of link AM1-M7 181-M7 by inserting a link bolt 181-M9 through the other hole of link AM1-M6 181-M6 and a hole of link AM1-M7 181-M7, and then securing that link bolt using a link nut 181-M12.
  • link AM1-M7 181-M7 is connected to the output disk arm AM1-M8-S1 181-M5-S2 by inserting a link bolt 181-M9 through the other hole of link AM1-M7 181-M7 and the hole of the output disk arm AM1-M8-S1 181-M8-S1, and then securing that link bolt using a link nut 181-M12.
  • the surfaces of the link bolts and the link nuts that are in contact with the follower, the link AM1- M6 181-M6, the link AM1-M7 181-M7, or the output disk arm AM1-M8-S1 181-M8-S1, are preferably coated with a low friction material such as oil-impregnated bronze, so that the link AM1-M6 181-M6 and link AM1-M7 181-M7 can rotate without much frictional resistance.
  • a controller rod 181-M10 is used.
  • the controller rod 181-M10 is slender steel rod that is bent repeatedly such that a zigzag profile is formed.
  • the zigzag profile consist of two alternating shapes, a pivot shape 181-M10-S1 and a parallel shape 181-M10-S2, that can be slid through the controller slot of link AM1-M6 181-M6.
  • the angle between the pivot shape 181-M10-S1 and the parallel shape 181-M10-S2 should be 90°.
  • the pivot shapes 181- Ml 0-S1 are positioned perpendicular to the long surfaces of link AM1-M6 181-M6, so that they can act as pivots for link AM1-M6 181-M6.
  • the parallel shapes 181-M10-S2 are positioned parallel to the long surfaces of link AM1-M6 181-M6, so that they can act as constrainers for link AM 1 -M6 181 -M6.
  • the function of the controller rod 181 -M 10 is to properly adjust the rotation of the output disk 181-M8 relative to the cam sleeve 181-M2 due the profile of the cam 181-Ml, by adjusting the pivot of link AM1-M6 181-M6 or by constraining link AM1-M6 181-M6.
  • the position of the pivot for link AM1-M6 181-M6 can be changed by changing the axial position of the controller rod 181-M10 relative to link AMI -M6 181-M6. And changing the position of the pivot for link axial position of the controller rod 181-M10 relative to link AM1-M6 181-M6, changes the amount of relative rotation between the cam sleeve 181 -M2 and the output disk 181 -M8 due to the profile of the cam 181-Ml.
  • link AM1-M6 181-M6 is constrained from pivoting, so that despite the profile of the cam 181- Ml, no relative rotation between the cam sleeve 181-M2 and the output disk 181-M3 exist.
  • a positive angle which is referred to as the controller angle, is formed between the flat profile of the controller rod 181-M10 and the controller slot of link AM1-M6 181-M6. The controller angle increases as the pivot is moved towards the follower 181-M5.
  • the amount of relative rotation between the cam sleeve 181-M2 and the output disk 181-M8 increases proportionally with an increase in the controller angle.
  • the diameter Dl should be selected as to eliminate transition flexing.
  • the zigzag profile of the controller rod 181-M6 and its pattern of axial movements relative to link AM1-M6 181-M6 should be designed based on the information shown in Fig. 12A and 12C.
  • the circumference of the surface of the cone were the torque transmitting members are positioned is a multiple of the width of their teeth, so that no relative rotation between the cam sleeve 181-M2 and the output disk 181-M8 is required
  • the parallel shape 181-M10-S2 of the controller rod 181-M10 should be positioned inside the controller slot of link AM1-M6 181-M6.
  • the required amount of rotational adjustment linearly decreases as the critical non- torque transmitting arc is increased from an even space until the next even space is reached; and the required amount of rotational adjustment linearly increases as the pitch diameter is decreased from an even pitch diameter until the next even pitch diameter is reached.
  • the pivot shape 181-M10-S2 of the controller rod 181-M10 and its pattern of axial movement should be designed so that the position of the pivot can be properly adjusted with the change in pitch diameter so that transition flexing is eliminated or at least minimized.
  • controller rod 181-M10 has to be slid through the controller slot of link AM1-M6 181-M6, which is rotating with the cam sleeve 181-M2, which in turn is rotating with shaft SHO.
  • the controller rod 181-M10 has to be attached such that it rotates with shaft SHO but can be moved axially relative to shaft SHO.
  • a controller rod mechanism that consist of the controller rod 181-M10, a controller rod counter- weight 181- Ml 1, a controller rod slider 181-M13, and a controller rod disk 181-M14, is used.
  • the back end of the controller rod 181-M10 and the back end of an controller rod counter- weight 181-Ml 1 are connected to the controller rod slider 181-Ml 3, which slides freely on shaft SHO and is positioned in the back of the controller rod disk 181-M14.
  • the front end of the controller rod 181-M10 and the front end of the controller counter-weight 181-Ml 1 are connected to the controller rod disk 181- Ml 4, which positioned in front of the cam sleeve 181 -M2.
  • controller rod counter-weight 181-Ml 1 is slid through controller rod counter-weight arm 181-M2-S5 of cam sleeve 181-M2 so that the controller rod counter-weight 181-Ml 1 rotates with cam sleeve 181-M2.
  • controller rod 181-M10 and controller rod counterweight 181 -Ml 1 are rotatably constrained relative to each other, controller rod 181 -Ml 0 is rotatably constrained relative to cam sleeve 181-M2. Therefore, controller rod 181-M10 rotates with cam sleeve 181-M2.
  • the controller rod counter- weight 181-M11 is shaped like a round wire that has the same length and weight as the controller rod 181-Ml 0. And in order to attach the controller rod 181-M10 to the controller rod slider 181-M12 and the controller rod disk 181- Ml 3, the front-end and the back-end of the controller rod is shaped like a straight square wire.
  • the controller rod slider 181-M13 is shaped like a hollow cylinder with an plain end and a flanged end.
  • the inner diameter of the controller rod slider 181-Ml 2 is slightly larger than the diameter of shaft SHO 10, so that only significant relative axial movements between the controller rod slider 181-Ml 2 and shaft SHO 10 is allowed.
  • the plain end of the controller rod slider 181-Ml 2 is facing away from the cam sleeve 181-M2 and the flanged end of the controller rod slider is facing towards the cam sleeve.
  • the back end of the controller rod 181-M10 and the back end of the controller rod counter- weight 181-Ml 1 are attached to the flanged end of the controller rod slider 181-Ml 2.
  • the flange end of the controller rod slider has two opposite positioned square holes into which the back end of the controller rod and the back end of the controller counter- weight are securely pressed in. They are attached opposite of each other so that the centrifugal force of the controller rod is canceled out by the centrifugal force of the controller rod counter- weight.
  • controller rod and the controller rod counter-weight are also aligned so that their center-axis is parallel to the center-axis of shaft SHO 10.
  • the front end of the controller rod 181-M10 and the front end of the controller rod counter-weight 181-M11 are attached to the back surface of the controller rod disk 181-M14, which also has two opposite positioned square holes into which the front end of the controller rod and the front end of the controller counter- weight are securely pressed in.
  • a member of the controller rod mechanism can be connected to a member of the CTTM CVT, where it is used, that moves axially with the torque transmitting members as the ttansmission ratio is changed, so that the axial position of the controller rod is automatically adjusted as the transmission ratio is changed.
  • This method is shown in Fig. 29.
  • Another method to conttol the axial position of the controller rod disk 181 -Ml 3 is to attach a controller rod mover mechanism, that is used to change the axial position of the controller relative to the link AM1-M6 181-M6, to the controller disk. This method is shown in Fig. 30.
  • FIG. 30 A configuration of a CTTM CVT, where a mechanical adjuster AMI 181 can be utilized in shown in Fig. 30.
  • the controller rod slider 131 -Ml 3 is directly connected to mover sleeve CS4B-M6 24B-M6 of cone assembly CS4B 224B.
  • the mechanical adjuster AMI 181 is used to properly adjust the rotational position between cone assembly CS4A 24A and cone assembly CS4B 24B, and hence the rotational position between torque ttansmitting member CS4A-M1 24A-M1 and torque ttansmitting member CS4B-M1 24B-M1.
  • the axial position of the controller rod 181-M10 can only be changed when its flat profile is parallel to the controller slot of link AM1-M6 181-M6, hence some stalling of the ttansmission ratio changing actuator is to be expected.
  • the strength of transmission ratio changing actuator should be small enough such that it can not cause damaging internal stresses in the parts of mechanical adjuster AMI 181 and anywhere else in the CVT, when it tries to change the transmission ratio when the flat profile of the controller rod is not parallel to the controller slot of link AM1-M6 181-M6 .
  • a limiting clutch mounted on the output of the transmission ratio changing actuator that causes slippage between the output of the ttansmission ratio changing actuator and the rest of the mechanism used to change the transmission ratio when the torque at the transmission ratio changing actuator exceeds a limiting value can also be used.
  • controller rod 181-M10 and the link AM1-M6 181-M6 have a finite thickness so that when the axial positions of the controller rod and the torque transmitting members are changed, the parallel shape 181-M10- S2 of the controller rod and the controller slot of link AM1-M6 181-M6 are engaged for a finite axial distance.
  • transition flexing can be reduced by reducing the thickness of link AMI -M6 181 -M6 and the thickness of the controller rod 181-M10 or by also using a spring-loaded adjuster AS1 172.
  • CTTM CVT The following configuration of a CTTM CVT, as shown in Fig. 30, can be used to control the axial position of the controller rod 181-M10 so that transition flexing can be minimized without having to reduce the thickness of the controller rod 181-M10 and the thickness of link AM1-M6 181-M6.
  • a cam adjuster gear rack 181-Ml 5 which engages with a cam adjuster gear 181-Ml 6, is attached to the front surface of the controller rod disk 181-M13 via a rotatable coupling 190.
  • the rotatable coupling which is shown in detail in Fig.
  • a controller rod disk shaft 181-Ml 5 is centrically welded on to the front surface of the controller rod disk 181-M14; and a gear rack shaft 181-M17, is glued on to the back surface cam adjuster gear rack 181-M16.
  • the controller rod disk shaft 181- M14 is inserted into one coupling sleeve, and a set-screw is threaded through the controller rod disk shaft 181-M15 and that coupling sleeve; and in order to attach the other end of that rotatable coupling to the cam adjuster gear rack 181-M16, the gear rack shaft 181-Ml 7 is inserted into the other coupling sleeve, and a set-screw is threaded through the gear rack shaft 181-M17 and that coupling sleeve.
  • the cam adjuster gear 181-M16 which is keyed to a controller motor, will be used to conttol the axial position of the controller rod.
  • the cam adjuster gear 181-M16 which has a marked wheel attached to it, will also be used to monitor the axial position of the controller rod via sensor IB.
  • the controller rod actuator is connected to the computer that controls CVT 2.6. The computer will then properly control the transmission ratio changing actuator and the controller rod actuator as the eliminate or minimize the stretching of the ttansmission belts in instances where the circumferences of the cone assemblies where the torque transmitting members are positioned is not a multiple of the width of the teeth of the torque transmitting members.
  • Changing the axial position of the controller rod when the follower is not in contact with the diameter Dc of the cam can damage the mechanical adjuster.
  • the strength of the controller motor should be small enough such that it can not cause damaging internal stresses in the mechanical adjuster 181.
  • a limiting clutch can also be mounted on the output of the controller rod actuator.
  • the following control scheme can be used to properly control the controller road actuator and the transmission ratio changing actuator.
  • the axial position of the controller rod 181-M10 should only be changed when the follower 181-M4 is in contact with the diameter Dc of the cam 181-Ml, otherwise stalling of the controller rod actuator or slipping of its limiting clutch has to occur.
  • it is nice to prevent this by attaching a rotational position sensor on one of the cone assemblies of CVT 2.3, preferably cone assembly CS4C 24C, and connect this sensor to the computer of CVT 2.6, and program the computer so that it only changes the axial position of the controller rod when the follower is in contact with the diameter Dc of the cam 181-Ml.
  • the axial position of the controller rod 181-M10 should be changed such that it corresponds with the axial position of the torque transmitting members.
  • a certain limit value is set as to limit the discrepancy between the required axial position of the controller rod based on the axial position of the torque transmitting members and the actual axial position of the controller rod. For example, when the controller rod has moved too far ahead relative to its required axial position based on the position of the torque ttansmitting members, the movement of the controller rod will be put on hold until the torque transmitting members have moved to a corresponding axial position which is within the required limit range.
  • the adjuster output member, output disk AM1-M8 181-M8 is axially fixed relative to the shaft where it is used.
  • the mechanical adjuster can not be used as an adjuster ADIA or AD1B of CVT 1.1, since these adjusters move axially relative to their shaft when the axial position of the torque ttansmitting members is changed.
  • a slightly modified version of mechanical adjuster AMI 181, which is labeled as mechanical adjuster AM2 132 is used.
  • Mechanical adjuster AM2 132 which is shown in Fig. 31, is identical to mechanical adjuster AMI 181, except that here in order to have an adjuster output member that can move axially with the torque ttansmitting members, an adjuster slider plate 182-Ml is added. Most of the members used for mechanical adjuster AMI 181 are also used for mechanical adjuster AM2 182. Here only the members that are different or are not used in mechanical adjuster AMI 181 are labeled differently than in mechanical adjuster AMI 181.
  • the adjuster slider plate 182-Ml is shaped like an elongated plate. On one side of the adjuster slider plate 182- Ml, a cam adjuster extension arm 182-M2 and a cam adjuster balancing arm 182-M3 are welded on.
  • the cam adjuster extension arm 182-M2 is shaped like the long leg of the adjuster extension arm AD1A-M2-S1 101A-M2-S1 of transition flexing adjuster ADIA 101 A, which is used in CVT 1.1.
  • the cam adjuster balancing arm 182-M3 is shaped like the long leg of the adjuster balancing arm AD1A-M2-S3 101A-M2-S3 of ttansition flexing adjuster ADIA 101 A, which is used in CVT 1.1.
  • the cam adjuster extension arm 182-M2 is used to mount the gap mounted torque transmitting member, which here is torque ttansmitting member 22C-M2.
  • the cam adjuster balancing arm 182-M3 is used to balance the centrifugal forces of the cam adjuster extension arm 182- M.
  • a constrainer mechanism that constrains the movements of the telescopes of torque ttansmitting member 22C-M2 is attached to the cam adjuster extension arm.
  • an adjuster slider plate back shaft 182-M4 is welded on.
  • the adjuster slider plate 182-Ml On the other side of the adjuster slider plate 182-Ml, two cam adjuster sliders 182-M5 are welded on in manner such that in the mechanical adjuster's AM2 132 assembled state, there are no members that prevent the adjuster sliders 182-M5 from moving axially. Also in order to ensure that the adjuster slider plate 182-M1 rotates with the output disk AM2-M8 182-M8, the output disk AM2-M8 182-M8 has two slider holes, into which the cam adjuster sliders 182-M5 can be slideably inserted. Also, the cam adjuster sliders 182-M5 are long enough such that they are engaged with the output disk AM2-M8 182-M8 for every axial position of the torque transmitting members. Also for mounting purposes, on the same side and near the center of the adjuster slider plate 182-Ml, an adjuster slider plate front shaft 182-M6 is welded on.
  • FIG. 31 A configuration where two adjusters AM2 132 are used to eliminate transition flexing for a CVT 1.2 is shown in Fig. 31.
  • a rotatable coupling described in the previous section, is used to mount an adjuster slider plate 182-M1 to the mover sleeve 22C-M6 and to mount an adjuster slider plate 182-Ml to the mover sleeve 22D-M6.
  • the adjuster slider plate front shaft 182-M6 is inserted into one coupling sleeve, and a set-screw is threaded through that adjuster slider plate front shaft and that coupling sleeve; and in order to attach the other end of this rotatable coupling to a controller rod slider 181-Ml 2 , a portion of the controller rod slider's 181-M13 plain shape is inserted into the other coupling sleeve, and a set-screw is threaded through that portion of the controller rod slider and that coupling sleeve.
  • guiding wheels 200 or a guides can be mounted on the tense side of the transmission belts such as shown Fig. 32.
  • the guiding wheels move with the torque transmitting members and the transmissions pulleys as their axial position is changed.
  • the tensioning wheels move vertically up or down as their axial position is changed so that they can maintain proper tension in their ttansmission belts, the vertical position of the guiding wheels does not change as their axial position is changed.
  • the designer uses one or several adjusters that can adjust the rotational position of a torque ttansmitting device, such as a torque ttansmitting member of a cone assembly, a ttansmission pulley, a cone assembly, etc, relative to another torque ttansmitting device.
  • the adjuster(s) should be mounted so that ttansition flexing can be eliminated and/or so that ttansmission ratio change rotation can be compensated.
  • an alternating torque transmitting device is a device that alternates between ttansmitting torque and not transmitting torque.
  • the alternating torque ttansmitting devices are the torque transmitting members.
  • the alternating torque ttansmitting devices are the cone assemblies and the ttansmission pulleys, since they alternately transmit torque to or from a shaft from or to a belt.
  • CTTM CVT non-alternating torque transmitting device
  • CTTM CVT comprises of cone assembly with two oppositely positioned torque ttansmitting members which is coupled by a ttansmission belt to a transmission pulley.
  • the transmission pulley is the non-alternating torque ttansmitting device.
  • CTTM CVT were a non-alternating torque ttansmitting device is used, comprises of cone assembly that is sandwiched by two gears, which are then coupled to a common output shaft.
  • the cone assembly is the non-alternating torque ttansmitting device.
  • adjuster When adjuster are only used to adjust the rotational position of the alternating torque ttansmitting members then in most cases the following method can be used to determine how many adjuster are needed.
  • two alternating torque transmitting devices are coupled to a common torque transmitting device, then only one adjuster is needed.
  • the amount of adjusters needed depend on the configuration of the CTTM CVT. In this case it depends on how many alternating torque ttansmitting devices can simultaneously be in contact with their common torque transmitting device.
  • the amount of adjusters needed depends on the configuration of the CVT.
  • the amount of adjusters needed and the proper configuration for the adjusters can be figured out through experimentation
  • the adjuster systems of this invention can be used to improve the performance of a CTTM CVT in the following manner. First of all, they can eliminate or significantly reduce transition flexing. Excessive cycles of transition flexing can reduce the life of the torque transmitting member(s) and the coupling member(s) of a CTTM CVT. Furthermore, the adjuster systems of this invention can also be used so that a CTTM CVT is maintained in a moveable position regardless of the rotational position of its input shaft and its output shaft. Hence the adjuster systems of this invention can be used to increase the life, torque capacity, and responsiveness of a CTTM CVT.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmissions By Endless Flexible Members (AREA)
  • Friction Gearing (AREA)
EP03808196A 2002-10-08 2003-10-08 Kegel mit drehmomentübertragungsgliedern verwendende einstellsysteme für stufenloses getriebe Withdrawn EP1552190A4 (de)

Applications Claiming Priority (13)

Application Number Priority Date Filing Date Title
US41682802P 2002-10-08 2002-10-08
US416828P 2002-10-08
US42350302P 2002-11-04 2002-11-04
US423503P 2002-11-04
US43192102P 2002-12-09 2002-12-09
US431921P 2002-12-09
US47546103P 2003-06-02 2003-06-02
US475461P 2003-06-02
US47865103P 2003-06-13 2003-06-13
US478651P 2003-06-13
US48762603P 2003-07-15 2003-07-15
US487626P 2003-07-15
PCT/US2003/032161 WO2004033865A2 (en) 2002-10-08 2003-10-08 Adjuster systems for continuous variable transmissions utilizing cones with torque transmitting members

Publications (2)

Publication Number Publication Date
EP1552190A2 true EP1552190A2 (de) 2005-07-13
EP1552190A4 EP1552190A4 (de) 2010-07-07

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EP03808196A Withdrawn EP1552190A4 (de) 2002-10-08 2003-10-08 Kegel mit drehmomentübertragungsgliedern verwendende einstellsysteme für stufenloses getriebe

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Country Link
EP (1) EP1552190A4 (de)
AU (1) AU2003299356A1 (de)
WO (1) WO2004033865A2 (de)

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1446294A (en) * 1920-06-29 1923-02-20 Healey Syndicate Ltd Variable velocity ratio gearing
DE634643C (de) * 1933-07-09 1936-09-01 Kamill Huebner Wechselgetriebe mit Keilriemen, Seilen o. dgl.
DE724539C (de) * 1939-12-16 1942-08-28 Nationale Automobil Ges Ag Stufenloses Getriebe
US2552179A (en) * 1948-08-26 1951-05-08 Kamp Albert Variable speed segment pulley
FR1142775A (fr) * 1956-02-25 1957-09-23 Variateur de vitesse
GB1179575A (en) * 1966-05-17 1970-01-28 Rosen Karl I J A Variable Speed Driving Device
WO1991000446A1 (en) * 1989-07-05 1991-01-10 Cane Alberto High-efficiency steepless speed change gear of mechanical type
WO2002008638A1 (en) * 2000-07-24 2002-01-31 Armin Sebastian Tay Cone with torque transmitting segments
US20020091026A1 (en) * 2000-07-24 2002-07-11 Tay Armin Sebastian Cone with torque transmitting segments for non-friction dependent continuous variable transmissions

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1379504A (en) * 1920-05-20 1921-05-24 Young John Variable-speed transmission
US2941409A (en) * 1955-10-21 1960-06-21 Richard P Witt Variable speed power transmission device
US6152844A (en) * 1999-05-10 2000-11-28 Daugherty; B. Eugene Variable diameter pulley for a transmission

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1446294A (en) * 1920-06-29 1923-02-20 Healey Syndicate Ltd Variable velocity ratio gearing
DE634643C (de) * 1933-07-09 1936-09-01 Kamill Huebner Wechselgetriebe mit Keilriemen, Seilen o. dgl.
DE724539C (de) * 1939-12-16 1942-08-28 Nationale Automobil Ges Ag Stufenloses Getriebe
US2552179A (en) * 1948-08-26 1951-05-08 Kamp Albert Variable speed segment pulley
FR1142775A (fr) * 1956-02-25 1957-09-23 Variateur de vitesse
GB1179575A (en) * 1966-05-17 1970-01-28 Rosen Karl I J A Variable Speed Driving Device
WO1991000446A1 (en) * 1989-07-05 1991-01-10 Cane Alberto High-efficiency steepless speed change gear of mechanical type
WO2002008638A1 (en) * 2000-07-24 2002-01-31 Armin Sebastian Tay Cone with torque transmitting segments
US20020091026A1 (en) * 2000-07-24 2002-07-11 Tay Armin Sebastian Cone with torque transmitting segments for non-friction dependent continuous variable transmissions

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2004033865A2 *

Also Published As

Publication number Publication date
AU2003299356A8 (en) 2004-05-04
WO2004033865A3 (en) 2004-11-25
AU2003299356A1 (en) 2004-05-04
EP1552190A4 (de) 2010-07-07
WO2004033865A2 (en) 2004-04-22

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