WO2019010539A9 - Poulie et système de transmission - Google Patents

Poulie et système de transmission Download PDF

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Publication number
WO2019010539A9
WO2019010539A9 PCT/AU2018/050724 AU2018050724W WO2019010539A9 WO 2019010539 A9 WO2019010539 A9 WO 2019010539A9 AU 2018050724 W AU2018050724 W AU 2018050724W WO 2019010539 A9 WO2019010539 A9 WO 2019010539A9
Authority
WO
WIPO (PCT)
Prior art keywords
support surface
pulley
transmission system
side assembly
cable
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.)
Ceased
Application number
PCT/AU2018/050724
Other languages
English (en)
Other versions
WO2019010539A1 (fr
Inventor
Jochen Franke
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.)
Advanced Transmission Systems Holdings Ltd
Original Assignee
Advanced Transmission Systems Holdings Ltd
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
Priority claimed from AU2017902759A external-priority patent/AU2017902759A0/en
Application filed by Advanced Transmission Systems Holdings Ltd filed Critical Advanced Transmission Systems Holdings Ltd
Priority to CN201880058814.7A priority Critical patent/CN111448405A/zh
Priority to EP18831892.7A priority patent/EP3652469A4/fr
Priority to AU2018299208A priority patent/AU2018299208A1/en
Publication of WO2019010539A1 publication Critical patent/WO2019010539A1/fr
Publication of WO2019010539A9 publication Critical patent/WO2019010539A9/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M23/00—Transmissions characterised by use of other elements; Other transmissions
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M6/00—Rider propulsion of wheeled vehicles with additional source of power, e.g. combustion engine or electric motor
    • B62M6/40—Rider propelled cycles with auxiliary electric motor
    • B62M6/55—Rider propelled cycles with auxiliary electric motor power-driven at crank shafts parts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M9/00—Transmissions characterised by use of an endless chain, belt, or the like
    • 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
    • F16H9/12—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 built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members

Definitions

  • the present invention generally relates to a pulley.
  • the present invention relates to a pulley which is capable of presenting a variable diameter.
  • the present invention also relates to a transmission system, or pulley driven system, which incorporates the pulley.
  • Transmission systems are used in various vehicles and industrial equipment to transfer power from a power source to an output, typically to a drive wheel to move the vehicle.
  • a power source typically to a drive wheel to move the vehicle.
  • One such vehicle which employs a drive train is a bicycle.
  • the transmission system of a bicycle is typically in the form of a centrally located chain ring integrating two crank arms.
  • a rider engages the crank arms to rotate the chain ring.
  • the chain ring is spaced from a rear sprocket but is interconnected using a chain which spans between the chain ring and the sprocket.
  • the rear sprocket is secured to the axle of the rear wheel of the bicycle such that as the rear sprocket rotates the rear wheel will simultaneously rotate.
  • the transmission system of a bicycle will typically further comprise a gearing system to enable a rider to manipulate the effect the rotational force of the chain ring has on the rear wheel.
  • This gear system general comprises a plurality of co-axially mounted rear sprockets of different diameter and a plurality of co-axially mounted chain rings (usually between one and three) of different diameter.
  • a bike can either be set up with a large gearing range thereby not featuring the smallest possible gears, or with a small 'compact' gearing range thereby not featuring the largest possible gears. Therefore when setting up a bicycle it is necessary to choose one of the subset ranges.
  • a large gearing range is used for relatively flat terrain but inevitably leads to undesirable limitations when sections of the predominantly flat terrain lead uphill at a notable gradient, as these cannot be ridden with the preferred small gearing. This in turn leads to rider fatigue and a competitive disadvantage.
  • a small gearing range is used for relatively steep uphill terrain but leads to undesirable limitations when riding downhill as large gearing to facilitate pedalling downhill at high speeds is not available. This leads to lower than possible speeds and hence a competitive disadvantage.
  • Another disadvantage of conventional chain driven derailleur systems is the inability to change gear when stationary.
  • Chain driven systems require a pedalling cadence to be applied in order to facilitate gear change.
  • rider energy and ultimately chain drive train efficiency As the rider must first change to a smaller gear starting from a much too large gear. This consumes a disproportionate amount of energy and the cumulative effect of that over long rides leads to reduced rider endurance.
  • Chain driven derailleur systems are sensitive to physical shocks to the bike, lack of mechanical calibration quality or other misalignment, componentry mismatch, and lack of sensible rider operation. If any of the above exceeds the limitation of their operational design, the chain will come off the chain ring or the sprocket and, in the worst case, the chain can break. Chain derailment is common in recreational cycling and even regularly occurs during professional road racing even though great care is taken to provide equipment in peak condition. Other mechanical failures for conventional chain drives include blockage of some of the gear ratios by dirt ingress or ice formation.
  • 'cable' is used to describe a rope, a belt, a chain, webbing or any other rope-like device which may be used to assist in transmitting force from a pulley to another object.
  • 'cable' can denote a single unitary cable, or a cable made from many smaller cables entwined, joined in an end to end arrangement or otherwise formed to provide a substantially unitary member.
  • the present invention provides a transmission system, the transmission system comprising a first pulley and an output which is spaced therefrom, a cable extends between the first pulley and the output such that movement of the first pulley causes movement of the output, the first pulley comprising:
  • first side assembly spaced from a second side assembly, the first side assembly and second side assembly are rotatably fixed together;
  • variable annular recess defined between the first side assembly and the second side assembly, the annular recess being adapted to receive the cable;
  • each of the first side assembly and the second side assembly providing a support surface for supporting the cable
  • the support surface is laterally movable between a first position and a second position, the first position being spaced outwardly from the second position, the support surface of the first side assembly and the support surface of the second side assembly co-operate to engage the cable when the support surface of each side assembly is in the second position, whereupon the cable moves from a first diameter to be supported at a second diameter
  • the support surface comprises a plurality of support surface units, define the support surface, each support surface unit may move relative to each other;
  • width of the first pulley remains constant as the support surface moves between the first diameter and the second diameter, and vice versa.
  • the transmission further comprises at least one actuator apparatus for moving each support surface between the first position and the second position, the at least one actuator apparatus moves radially relative to the first side assembly and the second side assembly.
  • the at least one actuator apparatus may move radially relative to an axis of rotation of the first pulley.
  • the at least one actuator apparatus may be variably positioned along a radial extent of the first pulley.
  • the at least one actuator apparatus comprising a first actuator and a second actuator connected therebetween by a bridge member.
  • the first actuator co-operates with the support surface of the first side assembly and the second actuator simultaneously co-operates with the support surface of the second side assembly to move each support surface between the first position and the second position.
  • the bridge member maintains the first actuator and the second actuator in a fixed relation. This ensures each support surface, when engaged by the at least one actuator apparatus, is held in position by the at least one actuator apparatus and not caused to move laterally outward due to the force exerted thereon by the cable.
  • At least one or both of the first actuator and the second actuator provides a first guide means to cause the support surface to move to the second position.
  • the first guide means may comprise a first guide surface which engages the support surface.
  • At least one or both of the first actuator and the second actuator provide a second guide means to guide the support surface to the first position.
  • the second guide means may comprise a second guide surface which causes the support surface to move to the first position.
  • the second guide surface may comprise an actuator channel which cooperates with a portion of the support surface to cause the support surface to move to the first position.
  • the pulley may comprise a control means to control the movement of the at least one actuator apparatus.
  • the control means may constrain the at least one actuator apparatus such that the at least one actuator apparatus is limited to radial movement relative to each side assembly.
  • the control means may comprise at least one support channel which engages the at least one actuator apparatus to limit movement along the at least one support channel.
  • the at least one support channel may extend in a radial direction relative to each side assembly such that the at least one actuator apparatus is limited to radial movement relative to each side assembly.
  • the at least one actuator apparatus may be variably positioned along the radial extent.
  • the control means may comprise a support housing which supports the at least one actuator apparatus.
  • the support housing may comprise a backing plate and a movement mechanism.
  • the backing plate may be located at a position between the support surface and the movement mechanism.
  • the backing plate may incorporate the at least one support channel for restricting the movement of the at least one actuator apparatus to a radial direction.
  • the movement mechanism may cause the at least one actuator apparatus to move along the radial extent.
  • the movement mechanism comprises a motor and a series of gears which co-operate with the at least one actuator apparatus to move the at least one actuator apparatus along the radial extent.
  • the movement mechanism comprises a guide plate which is rotatable relative to the backing plate, where rotation of the guide plate causes the at least one actuator apparatus to move along the at least one support channel of the guide plate.
  • the movement mechanism also comprises a motor and a series of gears which rotatably co-operate with the guide plate to move the at least one actuator apparatus along the radial extent.
  • the motor may be housed in a spindle and/or a bottom bracket of the bicycle frame.
  • the control means may also comprise one or more levers to cause the at least one actuator apparatus to move along the radial extent wherein the action of the levers determines the direction of the motor and the period in which it is activated.
  • the one or more levers may be in wireless/Bluetooth communication with the motor,
  • the guide plate is in the form of a scroll plate.
  • the scroll plate may comprise a spiral formation.
  • the spiral formation may be in the form of a spiral groove.
  • the groove may be continuous.
  • the groove may be continuous from a first end adjacent an outer periphery of the guide plate to a second end adjacent an inner periphery of the guide plate.
  • the spiral formation may engage an end of the at least one actuator apparatus whereby rotation of the scroll plate will cause the end of the at least one actuator apparatus to move along the spiral, causing the at least one actuator apparatus to move along the at least one support channel in the backing plate.
  • the at least one support channel may be substantially perpendicular to the portion of the spiral passing across the at least one support channel.
  • the guide plate incorporates at least one groove positioned to be in association with the at least one support channel of the backing plate.
  • the at least one groove may engage with an end of the at least one actuator apparatus.
  • the at least one groove may be angularly orientated relative to the at least one support channel such that rotation of the guide plate causes the at least one groove to move relative to the at least one support channel, the at least one actuator apparatus being forced to move by the at least one groove so as to move radially along the at least one support channel.
  • the end of the at least one actuator apparatus may provide a roller, the roller being adapted to engage with the groove, the roller assisting movement of the at least one actuator apparatus as the guide plate rotates.
  • the support surface comprises a plurality of support segments arranged in a circular configuration wherein the overall appearance of each support segment is that of a truncated pie segment.
  • Each support segment comprises a subset of the plurality of support surface units. Considering a single support segment, each support surface unit is stacked one on top of the other wherein, in one embodiment, the support surface unit positioned closest to the rotational axis of the pulley is the smallest inner support surface unit, with each support surface unit thereafter increasing in length.
  • each support surface unit is restricted to axial movement relative to adjacent support surface units.
  • Each support surface unit may have a spline arrangement therebetween, wherein the spline arrangement prevents tangential movement between adjacent support surface units.
  • Each support surface unit may comprise a limiting mechanism to limit axial movement between adjacent support surface units.
  • the limiting mechanism may comprise a projection incorporated in each support surface unit wherein the projection is adapted to co-operate with a recess in an adjacent support surface unit.
  • the limiting mechanism at least maintains the support surface units in the second position until the at least one actuator apparatus causes the support surface unit to move back to the first position.
  • each support surface comprises a plurality of support surface units. Each unit is independently movable between the first position and the second position. Each unit is restricted to movement between the first position and the second position.
  • Each support unit is adapted to co-operatively engage the at least one actuator apparatus wherein the at least one actuator apparatus causes each support unit to move between the first position and the second position.
  • the at least one actuator apparatus engages the support surface units to cause the support surface unit to move between the first position and the second position as the at least one actuator apparatus moves radially outward along the at least one support channel.
  • the first guide surface of the at least one actuator apparatus engages the one or more support surface units.
  • the at least one actuator apparatus engages one or more support surface units to cause the support surface unit to move between the second position and the first position as the at least one actuator apparatus moves radially inward along the at least one support channel.
  • the second guide surface of the at least one actuator apparatus engages the one or more support surface units.
  • the present invention further provides a transmission system, the transmission system comprising a first pulley and an output which is spaced therefrom, a cable extends between the first pulley and the output such that movement of the first pulley causes rotation of the output, the first pulley comprising:
  • first side assembly and second side assembly spaced from each other, the first side assembly and second side assembly are co-axially mounted and rotatably fixed together; an annular recess between the first side assembly and second side assembly, the annular recess being adapted to receive the cable such that the cable is supported by the first pulley at a first diameter;
  • each of the first side assembly and second side assembly comprising a support surface comprising a plurality of independently mounted support surface units adapted to engage the cable, each support surface unit being laterally movable between at least a first position, wherein the cable is at a first diameter, and a second position, wherein the cable is at a second diameter, the second position being spaced inwardly from the first position.
  • the present invention further provides a transmission system, the transmission system comprising a first pulley and an output which is spaced therefrom, a cable extends between the first pulley and the output such that movement of the first pulley causes rotation of the output, the first pulley comprising:
  • each of the first side assembly and second side assembly comprising a support surface, the support surface comprises a plurality of support surface units, each support surface unit being movable relative to each other, the support surface is laterally movable, the support surface is selectively movable between at least a first position and a second position, the second position being spaced inwardly from the first position, wherein all or any part of the support surface can be in the first position or the second position, the support surface being adapted to engage the cable wherein when the entire support surface of each side assembly is in the first position the cable is supported at a first diameter of the first pulley, when the entire support surface of each side assembly is in the second position the cable is supported at a second
  • the support surface may be selectively positioned such that the third diameter is any sized diameter between the first diameter and the second diameter.
  • the first diameter may be the smallest diameter possible for the first pulley.
  • the second diameter may be the largest diameter possible for the first pulley.
  • the movement of the support surface of the first side assembly between the first position and second position may be just after or just before the movement of the support surface of the second side assembly between the first position and second position.
  • Each support surface unit may be laterally movable between at least a first position and a second position.
  • the first side assembly may be connected to the second side assembly.
  • the plurality of support surface units may co-operate to provide the support surface whereby selective movement of the support surface units causes the cable to transition to be positioned between different diameters of the first pulley.
  • the first side assembly and the second side assembly may be co-axially mounted.
  • the cable is supported on the first pulley which is presenting a constantly increasing diameter.
  • the cable is supported on the first pulley which is presenting a constantly decreasing diameter.
  • the support surface comprises a plurality of support surface segments wherein each support surface segment provides one or more support surface units.
  • the support surface segments may take the shape of a pie segment, such that the combined configuration of the plurality of support surface segments is circular.
  • Each support surface unit provides at least one contact surface adapted to engage the cable.
  • Each contact surface extends laterally from the support surface unit in a generally central direction. That is to say that each contact surface of each support surface unit extends towards a central plane of the first pulley wherein the central plane is substantially perpendicular to the pulleys axis of rotation.
  • the contact surfaces of the first side assembly are offset from corresponding contact surfaces of the second side assembly.
  • the contact surfaces of the first side assembly may be offset from corresponding contact surfaces of the second side assembly such that the contact surfaces of the first side assembly may be at a different diameter/radial position to corresponding contact surfaces of the second side assembly.
  • the contact surfaces of the first side assembly may be offset from corresponding contact surfaces of the second side assembly such that when the contact surfaces of the first side assembly are in the second position and the contact surfaces of the second side assembly are in the second position, the contact surfaces overlap.
  • each of the support surface units moves to the second position to cause a portion of the contact surface of the first side assembly to be received between radially adjacent contact surfaces of the second side assembly.
  • the support surface units effectively mesh together to provide a substantially continuous recess for supporting the cable.
  • the first pulley may comprise a support cradle for supporting the cable when the cable is at a position corresponding to the smallest possible diameter of the first pulley.
  • the support cradle is fixed.
  • the support cradle may be in the form of one or more support surface units fixed in the second position.
  • the support cradle may be movable.
  • the support cradle may be provided by the innermost support surface units wherein the innermost support surface units are prevented from moving to their first position, instead being movable between an intermediate position and the second position, the intermediate position being between the first position and the second position.
  • the backing plate may also comprise a cradle portion which forms part of the support cradle.
  • the cable may connect the first pulley and the output.
  • the cable may extend between the first pulley and the output such that the cable loops partially around the pulley and partially around the output.
  • the cable may be in the form of a continuous belt which frictionally engages the first pulley.
  • the cross section of the belt may be V-shaped, and may be truncated.
  • the cable may have a face which is adapted to be supported by the support surface of each of the first side assembly and second side assembly, wherein the cross section of the belt is V-shaped, and may be truncated.
  • Preferably at least 80% of the vee-shaped face is supported by the support surface.
  • at least 85% of the vee-shaped face is supported by the support surface.
  • the belt may comprise a plurality of wedge shaped segments depending from a belt portion.
  • the cross sectional profile of the belt changes between a tensioned state wherein the profile represents a narrow V-shape, and a relaxed state wherein the profile represents a broader V-shape.
  • the belt may adopt the tensioned state when it spans between the pulley and the output.
  • the belt may adopt the relaxed state when the belt engages the pulley and when the belt engages the output.
  • the broader V-shaped cross section presents a greater surface area to engage the annular recess of the pulley, and the output.
  • the V-shape complements the annular recess.
  • the narrower V- shape When in the tensioned state the narrower V- shape presents a reduced surface area such that the cross section is narrower than the cross section of the annular recess. As a result the belt does not engage with the pulley until further around the pulley, and disengages from the pulley earlier than if the belt only had one state. This configuration reduces friction losses encountered at the transition of the belt engaging and disengaging from the pulley.
  • the frictional forces between the belt and the pulley are the same when considered from all directions.
  • the ratio of the friction between the belt and the pulley in the belt driving direction to the friction between the belt and the pulley in a direction at or near normal to the driving direction is as high as possible, being higher than 1 :1 , in that the driving direction friction is lower than the normal friction.
  • friction between the belt and the pulley in the belt driven direction is high, and the friction between the belt and the pulley in a direction normal to the driven direction is low, power transmission is possible without belt slip. It also allows for improved shifting of gearing to overcome non-drive directional friction between belt and pulley.
  • the surface of the belt and/or the surface of the pulley may comprise surface irregularities such as projections and/or knurls, to increase friction between the belt and the pulley.
  • the surface of the belt and/or the surface of the pulley may comprise surface irregularities such as projections, knurls, grooves, and/or patterns to assist in increasing the ratio of the friction between the belt and the pulley in the belt driving direction to the friction between the belt and the pulley in a direction at or near normal to the driving direction.
  • the cable may be in the form of a composite material.
  • the cable may have a core.
  • the core may be formed from a non-yielding material such as aramid or carbon fibre. While the core is flexible the length of the core, once formed into the belt, does not significantly yield.
  • the output is in the form of a second pulley.
  • the second pulley may be a smaller, or larger, version of the first pulley.
  • the second pulley may comprise a first side assembly and a second side assembly spaced from each other, the first side assembly being connected to the second side assembly such that the first side assembly and second side assembly are co-axially mounted.
  • each of the first side assembly and second side assembly of the second pulley comprise a support surface.
  • the first pulley comprises an activation means to cause movement of the support surface units of each side assembly between the first position and the second position.
  • the first pulley controls the position of the cable, effectively determining the gearing of the transmission system.
  • the second pulley reacts to the movement of the at least one ring of each side assembly of the first pulley.
  • the second pulley is a passive pulley.
  • the second pulley comprises an activation means to cause movement of the at least one ring of each side assembly between the first position and the second position.
  • the second pulley controls the position of the cable, effectively determining the gearing of the transmission system.
  • the first pulley reacts to the movement of the support surface units of each side assembly of the second pulley.
  • the activation means may comprise at least one guide means wherein the at least one guide means selectively moves the support surface units between the first position and the second position.
  • the at least one guide means may be provided by at least one actuator apparatus.
  • the at least one actuator apparatus may comprises a first actuator head and a second actuator head held in fixed relation. Each actuator head may provide the at least one guide means.
  • the at least one guide means may be in the form of a first guide means and a second guide means.
  • the first guide means may cause the support surface to move to the second position.
  • the first guide means may comprise a first guide surface which engages each support surface unit of the support surface.
  • the second guide means may guide the support surface to the first position.
  • the second guide means may comprise a second guide surface which causes the support surface to move to the first position.
  • the second guide surface may comprise an actuator channel which cooperates with a portion of each support surface unit to cause the support surface to move to the first position.
  • the activation means may comprise a control means to control the movement of the at least one actuator apparatus.
  • the control means may constrain the at least one actuator apparatus such that the at least one actuator apparatus is limited to radial movement relative to each side assembly.
  • the transmission system is arranged such that as the first pulley moves from the first diameter to the second diameter, the second pulley moves from the second diameter to the first diameter.
  • the belt As the belt is fixed in length, the belt must move relative to the second pulley in order to compensate for movement of the belt relative to the first pulley. Therefore, as the belt is positioned to rotate about the larger second diameter of the first pulley, the belt is caused to move to rotate about the smaller first diameter of the second pulley or vice versa.
  • the present invention further provides a transmission system, the transmission system comprising a first pulley and an output which is spaced therefrom, a cable extends between the first pulley and the output such that movement of the first pulley causes rotation of the output, the first pulley comprising:
  • each ring comprises a plurality of support surface units, each support surface unit of each ring being independently movable
  • the present invention provides a transmission system, the transmission system comprising a first pulley connected to an output by a cable such that movement of the first pulley causes rotation of the output, the first pulley comprising:
  • annular recess between a first side of the first pulley and a second side of the first pulley, the annular recess being adapted to receive the cable such that the cable is supported by the first pulley;
  • a pair of support surfaces located in the annular recess, the pair of support surfaces being moveable in a lateral direction relative to the sides of the pulley between a spaced condition, wherein the first pulley is at a first diameter and the pair of support surfaces do not engage the cable, and a meshed condition, wherein the first pulley is at a second diameter and the pair of support surfaces support the cable, the second diameter being larger than the first diameter.
  • the present invention provides a variable diameter pulley, the pulley comprising:
  • a pair of support surfaces located in the annular recess, the pair of support surfaces being moveable in a lateral direction between a spaced condition, wherein the pair of support surfaces do not engage the cable, and a meshed condition, wherein the pair of support surfaces support the cable at a second diameter of the pulley, the second diameter being larger than the first diameter.
  • the present invention provides a variable diameter pulley, the pulley comprising:
  • annular recess adapted to receive a cable at a first diameter of the pulley
  • the annular recess providing a support surface for supporting the cable when received therein, the support surface being movable to present the first diameter and a second diameter;
  • the support surface is positionable to present any diameter between the first diameter and the second diameter.
  • the support surface presents a substantially continuous surface to the cable when received on the pulley.
  • the cross sectional profile of the support surface may be complementary to the cross sectional shape of that portion of the cable which engages the support surface so that the cable is retained in the annular recess.
  • the cable when supported thereon, remains in the same radial plane.
  • the support surface is formed from a first set of support surface units and a second set of support surface units, each support surface unit being movable relative to each other.
  • the first set of support surface units and the second set of support surface units may mesh together or overlap with each other to form the support surface.
  • the first set of support surface units and the second set of support surface units may be moveable in a lateral direction between a spaced condition, wherein the cable may be supported at the first diameter pf the pulley, and a meshed condition, wherein the cable may be supported at the second diameter of the pulley, whereby during movement of the set of support surface units between conditions the cable may be supported on the support surface which is presenting a changing diameter.
  • Circumferentially adjacent support surface units may define a ring. Each ring may not be continuous. Preferably a gap is defined between adjacent support surface units of the same ring.
  • Each ring of the first set of support surface units has a complementary ring of the second set of support surface units, whereby complementary rings are in a staggered relation to each other to provide a ring pair. Meshing of each ring pair provides the support surface for engaging the cable.
  • Each ring pair may move between a first position and a second position.
  • the complementary rings of a ring pair may be spaced away from each other in the axial/lateral direction. In this position the cable cannot be supported by the ring pair.
  • the complementary rings of the ring pair may be in the meshed condition to provide the support surface. In this position the cable is supported by the ring pair.
  • Each ring pair may move to a third position which is between the first position and the second position.
  • Each ring of support surface units may be arranged so that as a ring approaches the second position the adjacent upper/outer ring thereto commences moving towards the second position.
  • Each ring of each set of support surface units may be arranged so that as a ring approaches the first position the adjacent lower/inner ring thereto commences its movement towards the first position.
  • Each support surface unit may be wedge shaped to provide a sloped contact surface which engages the cable.
  • the pulley may comprise a first side housing for housing the first set of support surface units.
  • the pulley may comprise a second side housing for housing the second set of support surface units.
  • first side housing and the second side housing may be co-axially mounted with respect to each other to define the annular recess therebetween.
  • the pulley may comprise activation means to cause movement of the ring pairs between the first position and the second position.
  • the activation means may comprise a plurality of actuator apparatus.
  • Each actuator apparatus may be movable in a radial direction between a first position, central of the pulley and a second position, adjacent the outer diameter of the pulley.
  • Each actuator apparatus may have at least one head adapted to cause movement of the support surface units as each actuator apparatus moves between positions.
  • each actuator apparatus has a first head, adapted to cause movement of the support surface units of the first side assembly, and a second head, adapted to cause movement of the support surface units of the second side assembly as each actuator apparatus moves between positions.
  • the first head and second head may be interconnected by a bridge extending therebetween such that they are held in fixed relation to each other.
  • Each actuator apparatus is supported in corresponding channels in the first side housing and second side housing.
  • the plurality of actuator apparatus may be spaced from each other radially in a spider web type arrangement.
  • each support surface unit moves to its second position.
  • each support surface unit moves back to its first position.
  • the activation means may be manually activated or automatically activated.
  • the activation means may be activated mechanically as a result of an input force from an operator.
  • the activation means may be activated by a motor wherein the motor is adapted to cause movement of the actuator apparatus.
  • the activation means further comprises a control means.
  • the control means may provide a guide plate.
  • each set of support surface units has a guide plate which is rotatable relative thereto.
  • Each end of the actuator apparatus incorporates a rotatable wheel, wherein the wheel is received in a guide of the guide plate.
  • the guide may be spiral in configuration such that as the guide plate rotates each wheel rotates around the spiral guide.
  • rotation of the guide plate causes the actuator apparatus to move in a radial direction dictated by the radial channels incorporated in each of the first housing and the second housing, wherein movement of the actuator apparatus causes movement of the support surface units between the first position and the second position.
  • the present invention provides a transmission system, the transmission system comprising a variable diameter pulley as herein before described connected to an output by a belt such that movement of the pulley causes rotation of the output, the activating means being activated by a motor wherein the motor is powered by a power supply located within the spatial foot print of the transmission system, such as for example, in the crank arm or inside the spindle.
  • the power supply may be recharged through a charging socket, eliminating the need to remove the battery for re-charging.
  • Figure 1 is a side view of a front pulley assembly of a transmission system of a bicycle according to a first embodiment of the invention
  • Figure 2 is a perspective view of the first pulley of figure 1 ;
  • Figure 3 is a side view of figure 2;
  • Figure 4 is a view similar to figure 3 with a side housing removed;
  • Figure 5 is a partial exploded view of figure 3 with the housing and a backing plate from one side being in an exploded format;
  • Figure 6 is a view similar to figure 5 with the housing and the backing plate from one side removed;
  • Figure 7 is a partial exploded view of figure 3 with the housing, the backing plate and a support surface from one side being in an exploded format;
  • Figure 8 is an exploded front view of the first pulley shown in figure 3;
  • Figure 9 is a view similar to figure 8 with the housing, the backing plate and the support surface from one side removed;
  • Figure 10 is a side view of figure 9;
  • Figure 1 1 is a view similar to figure 10 with a plurality of actuator apparatus removed;
  • Figure 12 is a perspective view of one side of the first pulley and plurality of actuator apparatus shown in an exploded view;
  • Figures 13 to 15 are various views of support surface units;
  • Figure 16 are various views of one of the support surface units shown in figures 13 to 15;
  • Figure 17 (a,b) is a close up view of one support surface unit engaging an adjacent support surface unit
  • Figure 18 is a perspective view of an actuator apparatus without guide wheels'
  • Figure 19 is a perspective view of a plurality of actuator apparatus
  • Figure 20 is a perspective view of a two actuator apparatus supporting one support surface unit
  • Figure 21 is a cut away section of the first pulley
  • Figure 22 is a perspective view of a guide plate of an activation means
  • Figures 23, 24, 25 are side views of figure 22 wherein the guide plate is at a different angular position to show movement of the plurality of actuator apparatus;
  • Figure 26 is a cross sectional perspective view of the first pulley taken through a vertical plane
  • Figure 27 is an end view of figure 26
  • Figure 28 is a close up view of the upper section of figure 26;
  • Figure 29 is a schematic representation of an end view of figure 28
  • Figure 30 is a schematic representation of the transmission system of the first embodiment when at the smallest/lowest gear ratio (one side of each pulley being removed for illustrative purposes);
  • Figures 31 to 34 are various schematic representations of a section of the first pulley showing the position of the plurality of support surface units of the pulley of figure 30 when supporting the cable at its lowermost position, representing the smallest diameter;
  • Figures 35 and 36 are schematic representations of a section of the first pulley showing the change in position of the plurality of support surface units as the actuator apparatus begins to move outwardly relative to the central region of the first pulley;
  • Figures 37 and 38 are schematic representations of a section of the first pulley showing the change in position of the plurality of support surface units as the actuator apparatus continues to move outwardly relative to the central region of the first pulley;
  • Figures 39 and 40 are schematic representations of a section of the first pulley showing the change in position of the plurality of support surface units as the actuator apparatus further continues to move outwardly relative to the central region of the first pulley;
  • Figures 41 , 42 and 43 are schematic representations of the transmission system (one side of each pulley being removed for illustrative purposes) and a section of the first pulley showing the change in position of the plurality of support surface units as the actuator apparatus approaches its outermost position relative to the central region of the first pulley;
  • Figures 44 and 45 are schematic representations of the transmission system (one side of each pulley being removed for illustrative purposes) and a section of the first pulley showing the change in position of the plurality of support surface units as the actuator apparatus is at its outermost position relative to the central region of the first pulley;
  • Figure 46 (a, b, c, d) are schematic representations of a section of the first pulley showing the change in position of the plurality of support surface units as the actuator apparatus returns to its lowermost position;
  • Figure 47 is a perspective view of the backing plate of figure 5.
  • Figure 48 is a schematic view of the first pulley with crank arm and a motor positioned therein. DESCRIPTION OF EMBODIMENTS
  • the present invention according to a first embodiment of the invention, as depicted in the figures, is in the form of a transmission system 12 comprising a first variable diameter pulley 1 1.
  • the pulley 1 1 is particularly adapted for use with a transmission system which functions in a similar/same manner as a continuously variable transmission (CVT).
  • CVT continuously variable transmission
  • the pulley of the present invention is configured to maintain a relatively narrow gauge. This enables the pulley and associated transmission system to be used in applications which have minimal space for a transmission system, such as, for example, bicycles including conventional bicycles, e-bicycles and pedelecs.
  • Previous CVT's comprise relatively thick front and/or rear pulley arrangements which could not be readily utilised in applications which have limited space to house the pulley arrangement.
  • prior art CVTs could not be applied to bicycles as it would impede the pedal action, not provide a sufficient range in gear ratios, place significant stress on the chain and/or are too heavy.
  • the relatively narrow pulley of the present invention provides the transmission system with a practical and efficient drive train geometry. When applied to a bicycle the thickness of the pulley of the present invention is similar to the thickness of a crank set of a conventional bicycle with two or more chain rings.
  • the present invention also allows the diameter of the pulley to be increased with minimal or no change in the width of the pulley. This provides for a large range of gear ratios. This further enhances the vast array of applications the present invention is suited.
  • the pulley 1 1 is adapted to support two crank arms 13 to which pedals/clips 15 are secured.
  • a rider (not shown) can engage pedals 15 to cause the pulley 1 1 to rotate, this arrangement being well known.
  • the pulley 1 1 is secured to a frame of the bicycle (not shown) so that the pulley 1 1 is located adjacent the frame.
  • the pulley 1 1 comprises a first side assembly 17 and a second side assembly 19.
  • the first side assembly 17 and the second side assembly 19 are co-axially mounted.
  • crank arms 13a is connected to a shaft or spindle which passes through a bottom bracket of the bicycle frame before being secured relative to the second side assembly 19.
  • the second crank arm 13b is secured directly to an outer surface of the first side assembly 17.
  • the first side assembly 17 and the second side assembly 19 are spaced a distance from each other such that when the pulley 1 1 is assembled the first side assembly 17 and second side assembly 19 define an annular recess 25 therebetween.
  • the annular recess 25 being adapted to receive a cable in the form of a v-shaped belt 40, as best shown in figure 32.
  • Each side assembly 17, 19 comprise a housing 27, a backing plate 29 and a support surface 31 .
  • the annular recess 25 is defined by the housing 27a of the first side assembly 17, the housing 27b of the second side assembly 19 and the support surface 31.
  • the support surface 31 are moveable in a lateral direction between a first/spaced condition, wherein the support surface 31 does not engage the belt 40, and a second/meshed condition, wherein the support surface 31 supports the belt 40 at a second diameter of the pulley, the second diameter being larger than the first diameter.
  • Each support surface 31 comprises a plurality of support surface units 33. When arranged the support surface units 33 are in a circular configuration divided into a plurality of support surface segments 35. Each support surface segment 35 has a gap 37 therebetween for reasons which will be described below.
  • each support surface segment 35 comprises a set of the plurality of support surface units 33 arranged to be one on top of the other.
  • each support surface segment 35 comprises one support surface unit 33 stacked on another support surface unit 33.
  • each support surface segment 35 may have two or more support surface units 33 in a side by side relation, with one or more support surface segments 35 stacked thereon.
  • Each support surface unit 33 provides a contact surface 39 which, when in position extends at a sloped orientation towards a central plane of the pulley.
  • the contact surface 39 co-operates with the contact surface 39 of other support surface units 33 to provide the support surface 31 which directly engages and supports a cable in the form of a v-shaped belt 40, as will be described in further detail below.
  • each support surface unit 33 is shaped to engage a complementary shape in a lower surface 43 of the adjacent support surface unit 33.
  • the complementary shape of the upper surface 41 and the adjacent lower surface 43 provide a spline type arrangement 45 whereby movement of adjacent support surface units 33 is restricted by the spline arrangement 45 to lateral movement with respect to each other, as depicted by arrow 'A' in figures 13 and 15.
  • the lower surface 43 of each innermost support surface unit 33c also engages with the backing plate 29a, 29b in the spline arrangement 45 to restrict lateral movement with respect to each other.
  • each outermost support surface units 33d engages with the backing plate 29 in the spline arrangement 45 to restrict lateral movement with respect to each other.
  • Figure 47 shows the backing plate 29 along with splines 46, which cooperate with mating splines on the innermost support surface unit 33c, and outermost support units 33d.
  • each support surface unit 33 also comprises a projection 47. While each upper surface 41 comprises an indent 49 for receiving the projection 47 of the adjacent support surface unit 33. As best shown in figures 16b) and 16c) the projection 47 and indent 49 are located at a position distal from the contact surface 39. When adjacent support surface units 33 are in a second position, the projection 47 is received in the indent 49 of the adjacent support surface unit 33.
  • Figure 17 illustrates two adjacent support surface units coming together wherein the projection 47 of one support surface unit 33 is being received in the indent 49 of an adjacent support surface unit. The cooperation of the projection 47 and the indent 49 restricts the lateral movement of the lower support surface unit 33 such that the lower adjacent support surface unit 33 cannot return to a first position. Before the support surface unit 33 can return to the first position, the upper adjacent support surface unit 33 must first commence its return journey to the first position.
  • Each support surface unit 33 has a pin 51 at each end.
  • the pin 51 is used to move the support surface unit 33 between the first position and the second position as described below.
  • Each support surface unit 33 also has a guide surface 53 at each end.
  • the guide surface 53 is located between the pin 51 and the contact surface 39. In this embodiment the guide surface 53 is parallel to the contact surface 39.
  • Each support surface unit 33 is arcuate in shape whereby support surface units 33 in adjacent support surface segments 35 at the same diameter define a ring, the ring being discontinuous as a result of gaps 37.
  • the pin 51 is utilised to move the support surface unit 33 between the first position and the second position as described below.
  • the guide surface 53 is utilised to move the support surface unit 33 between the first position and the second position as described below.
  • the pulley 1 1 also comprises an activation means 57 to cause the support surface 31 to move between the first position and the second position.
  • the activation means 57 comprises a plurality of actuator apparatus 59 and a control means to control the movement of the actuator apparatus 59.
  • Each actuator apparatus 59 is movable in a radial direction in relation to the pulley 1 1 .
  • the support surface 31 is caused to move from the first position to the second position.
  • the support surface 31 is caused to move from the second position to the first position.
  • the control means is also able to hold the actuator apparatus 59 at any location between their innermost position and outermost position relative to the backing plate 29a, 29b.
  • each actuator apparatus 59 comprises a first head 61 a and a second head 61 b which are held in spaced relation by a bridge 63 extending therebetween.
  • Each head 61 a, 61 b provide a first guide means 65 to cause the support surface units 33 to move to the second position.
  • the first guide means 65 comprises a first guide surface 67 which is adapted to glidingly engage the guide surface 53 of each support surface unit 33.
  • Each head 61 a, 61 b also provides a second guide means 69 to guide the support surface 31 to the first position.
  • the second guide means 69 comprises a second guide surface 71 on each side of the head 61 a, 61 b which engages the pin 51 of each support surface unit 33 to move it to the first position.
  • the second guide surface 71 is in the form of an actuator channel 73 which receives and cooperates with the pin 51 of the support surface unit 33 to move the support surface 31 to the first position.
  • the actuator channel 73 has a first opening 75 in an upper part of the head 61 a, 61 b which is of a sufficient width to receive the pin 51.
  • the pin 51 of each side of the support surface unit 33 is received in the respective first opening 75.
  • Further outward movement of the actuator apparatus 59 results in the first guide surface 67 of the actuator apparatus 59 engaging the guide surface 53 of each support surface unit 33.
  • the support surface unit 33 is caused to move towards its second position.
  • the pin 51 traces along the second guide surface 71 which, in this embodiment is in the form of a sloped wall. Once the support surface unit 33 has reached its second position the pin 51 enters a second opening 77.
  • the actuator apparatus 59 In order to move the support surface unit 33 from the second position to the first position the actuator apparatus 59 is caused to move radially downward. As the actuator apparatus 59 approaches the support surface unit 33, the pin 51 is received in the second opening 77. Further downward movement of the actuator apparatus 59 results in the pin engaging the sloped wall of the second guide surface 71 . This forces the support surface unit 33 to move from the second position to the first position. Once the actuator apparatus 59 has moved sufficiently downward so that the support surface unit 33 is in the first position, the pin 51 exits the actuator channel 53 through the first opening 75.
  • Each end of each actuator apparatus provides a spigot 79 upon which is mounted a rotatable wheel 81 .
  • the rotatable wheel assists in the smooth movement of the actuator apparatus 59 in the radial direction.
  • the control means also comprises a plurality of support channels 83 which restricts movement of the plurality of actuator apparatus 59 to movement in the radial direction.
  • the plurality of support channels 83 are formed in each backing plate 29a, 29b, as best shown in figures 4 and 5. As shown in figure 4, each end of each actuator apparatus 59 is positioned in its respective support channel 83 such that the backing plate 29 is received between the side of the actuator head 61 and the wheel 81.
  • the control means further comprises a movement mechanism 85 which moves each actuator apparatus 59 along its support channel 83.
  • the movement mechanism 85 is provided by a guide plate 87 which is formed integral with each housing 27a, 27b.
  • the guide plate 87 provides a spiral groove 89 having closed ends and which extends from the inner periphery 91 to the outer periphery 93.
  • the guide plate is rotatably mounted relative to the backing plate 29.
  • the groove 89 is adapted to receive the wheels 81 of each actuator apparatus 59 such that as the guide plate 87 rotates, the wheels 81 travel along the groove 89.
  • the support channel 83 in the backing plate 29 restricts the movement of each actuator apparatus 59 to movement in a radial extent, and as each actuator apparatus 59 is angularly fixed, rotation of the guide plate 87 can only translate to radial movement of each actuator apparatus 59.
  • each actuator apparatus 59 must be placed at different positions along the spiral. If each actuator apparatus was identical then each actuator apparatus 59 would be at a different radius. This would mean that portions of the support surface at one diameter will be at the first position, others will be at the second position and others will be in between. In order to ensure the support surface 31 has a uniform diameter at any point therealong (i.e. either all support surface units 33 at that diameter being in the first position, the second position or in between) the first guide means 65 and second guide means of each actuator apparatus need to be at substantially the same radius. To achieve this the spigot 79 is placed at different positions along the head 61 a, 61 b of each actuator apparatus 59, as best shown in figures 10 and 20.
  • control means 58 also comprises a motor 97 and a gearing system 99.
  • the gearing system 99 is in operable engagement with the guide plate 87, activation of the motor 97 results in movement of the gearing system 99 which causes the guide plate 87 to rotate, causing the actuator apparatus 59 to move in a radial direction.
  • each support surface unit 33 is movable in a lateral direction relative to its side assembly 17, 19, between the first position, wherein the support surface unit 33 is adjacent the backing plate 29a, 29b, and the second position wherein the support surface unit 33 is spaced away from the backing plate 29a, 29b.
  • the support surface units 33 are arranged so that support surface units 33a on one side are offset relative to the corresponding support surface units 33b on the other side. In this arrangement the support surface units overlap, when in the second position, to provide the support surface 31 to support a minimum of approximately 75% of the belt 40.
  • the first pulley 1 1 comprises a support cradle 95 for supporting the belt 40 when the belt 40 is at a position corresponding to the smallest possible diameter of the first pulley 1 1 .
  • the support cradle 95 is in the form of support surface units 33c closest to the central axis of the pulley 1 1 (see figure 33) and a cradle portion 101 of the backing plate (see figure 29).
  • the support surface units 33c move between their second position and an intermediate position.
  • the intermediate position of the support surface unit 33c on the right hand side of the figure is closer to the second position than that on the left hand side.
  • the actuator apparatus moves outwardly, as will be described below, the support surface unit 33c on the right hand side is caused to move to its second position followed by the support surface unit 33c on the left hand side.
  • the cradle portion 101 of the backing plate also provides part of the support surface 31 supporting the belt 40.
  • the actuation apparatus 59 can be set at any position between their innermost position and outermost position the location of the belt 40 can be supported by the pulley at any diameter between the smallest diameter and the largest diameter.
  • the first variable diameter pulley 1 1 can be combined with a second variable diameter pulley 1 1 1 to complete the transmission system 12.
  • the belt 40 which is a continuous loop, extends between the two pulleys 1 1 , 1 1 1 1 to transfer movement from the first pulley 1 1 to the second pulley 1 1 1 .
  • the second pulley 1 1 1 acts as a slave pulley whereby it reacts to changes of the first pulley 1 1.
  • the second pulley 1 1 1 is a smaller version of the first pulley 1 1.
  • the pulley presents a substantially continuous support surface to the belt 40 as the belt 40 moves relative to the pulley 1 1 between the smallest diameter and the largest diameter. In the present embodiment approximately 75% of the belt 40 is supported the plurality of support surface units 33 at any one time.
  • Figures 30 to 46 show various views of the transmission system.
  • the transmission system 12 comprises the first variable diameter pulley 1 1 , and the second variable diameter 1 1 1 interconnected by the belt 40.
  • the various views show the belt 40 at various positions of the transmission system 12 wherein the various positions correspond to various gear positions of a conventional bicycle chain driven derailleur system.
  • the transmission system 12 is shown at a position relating to the smallest/lowest gear ratio wherein the actuator apparatus 59 are at their innermost position, whereby the first guide surface 67 of each actuator head 61 a, 61 b engages the guide surface 53 of the support surface unit 33.
  • This is also represented by figure 23 which shows each actuator apparatus 59 at their most inner position possible.
  • the innermost support surface units 33a of the first side assembly 17 of the first pulley 1 1 and the innermost support surface units 33b of the second side assembly 19 of the first pulley 1 1 are each in their second position.
  • the remaining support surface units 33 of the first pulley 1 1 are in their first position.
  • the projection 47 in the lower surface 43 of the support surface unit aligns with and is received in the indent 49 of the upper surface 41 of the lower adjacent support surface unit. This retains the lower adjacent support surface unit in the second position until the actuator apparatus 59 returns inwardly and causes the upper adjacent support surface units to return to their first position. This co-operation ensures the support surface units remain in their second position and do not unintentionally return to their first position until caused to do so by the actuator apparatus 59.
  • the transmission system 12 is shown at a first intermediary position.
  • the actuator apparatus 59 have commenced movement in the radially outward direction.
  • the support surface unit 33c on the right hand side has been moved to the second position, while the support surface unit 33c on the left hand side has moved further towards its second position. This has caused the support surface 31 to move outwardly to a larger diameter, causing the belt 40 to move also to that diameter.
  • the transmission system 12 is shown at a second intermediary position.
  • the transmission system 12 is shown at a third intermediary position.
  • the transmission system 12 is shown at a fourth intermediary position.
  • the transmission system 12 moves away from the smallest/lowest gear ratio. This is achieved by activating the control means to cause the movement mechanism 85 to rotate and move the actuator apparatus 59 to move outwardly towards their outermost position.
  • the second pulley 1 1 1 reacts so that the belt 40 is suitably supported.
  • each actuator head 61 a, 61 b is at its the outermost position.
  • figure 25 which shows each actuator apparatus 59 at their most outermost position as possible.
  • the first guide surface 67 of each actuator head 61 a, 61 b engages the guide surface 53 of the outermost support surface units 33d of each side assembly 17, 19.
  • all support surface units 33 are each in their second position to support the belt 40 at the largest diameter.
  • the second pulley 1 1 1 is a reactionary pulley wherein the operation of the second pulley 1 1 1 is dictated by the operation of the first pulley 1 1.
  • the change in tension in the belt 40 causes the second pulley 1 1 1 to react to support the belt 40 in a new position.
  • the support surface units 33 of the first pulley 1 1 are caused to return to their first position.
  • the head 61 a, 61 b of the actuator apparatus 59 moves inwardly the pin 51 of the below adjacent support surface unit 33 enters the second opening 77 of the actuator channel 73. Further inward movement causes the pin 51 to engage the second guide surface 71 . With further inward movement, the sloping face of the second guide surface 71 acts on the pin 51 to cause the support surface unit 33 to return to its first position.
  • the pin 51 aligns with the first opening 75 of the actuator channel 73 before exiting the actuator channel 73, allowing the actuator apparatus 59 to continue its inward movement.
  • the support surface units of the second pulley 1 1 1 are caused to move such that the belt 40 is supported at larger diameters.
  • the transmission system 12 presents a substantially continuous support surface on both the first pulley 1 1 and the second pulley 1 1 1 as the transmission system moves between the largest/highest gear ratio and the smallest/lowest gear ratio.
  • the control means is operable such that the actuator apparatus 59 may be positioned anywhere between their lowermost and outermost position (inclusive) and may be held in that position. As such the surface which supports the belts can be at any diameter between the largest diameter and smallest diameter.
  • the reason why this malfunction or failure is possible is due to the design and construction of prior art derailleur driven cassette and chain ring systems which do not physically force the chain to be retained in place.
  • the present invention is designed such that it is relatively impossible for the belt to come off the front or rear pulleys because no jockey wheels are in use and the edge perimeters of the pulleys physically constrain the belt under any load including shocks induced by road conditions. This increases the safety for the ride and, in competition, levels the playing field.
  • the present invention mitigates loss of power during gear ratio changes as it provides continuous power transmission during those gear ratio changes. This does not apply to derailleur systems or any other discrete gearing systems of prior art bicycles which suffer from loss of momentum during gear (chain ring or sprocket) changes
  • Loss of momentum is particularly significant for prior art derailleur systems when changing between chain rings requiring associated multiple sprocket (typically 3-4) changes in the cassette at the same time in order to avoid excessive gear ratio adjustments from the current setting.
  • the present embodiment can be activated by single trigger up or down shifting (using existing or dedicated handle bar mounted shifter hardware) on the front crank set.
  • the rear wheel gearing adjusts automatically to the crank setting.
  • Prior art derailleur drive trains require the rider to separately coordinate shifting of rear sprockets as well as front chain rings to achieve continuous gearing during up or down shifts which is not only inefficient as it leads to loss of momentum as between 3 and 4 gears have to be traversed when chain rings are changed, but it also places a strain on the riders in a state of fatigue or needing to respond to race situations without warning.
  • the present embodiment removes the manual coordination requirement of rear (cassette) and front (chain ring) changes making shifting much simpler. This is particularly desirable when riders are fatigued.
  • the present embodiment also removes gear ratio duplication which exists in all prior art chain ring and cassette combinations, thereby simplifying the system further.
  • the present embodiment eliminates the need for drivetrain lubrication which reduces maintenance and does not compromise drive efficiency.
  • the present embodiment also expands on the largest as well as the smallest gear ratios available from prior art derailleur systems.
  • the present invention provides a transmission system having a relatively narrow, fixed width, pulley which is capable of being designed to have near unlimited gear ratios. This is in contrast to current variable diameter pulley systems which must increase in width as gear ratios increase.
  • Example embodiments are provided so that this disclosure will be thorough, and will fully convey the scope to those who are skilled in the art. Numerous specific details are set forth such as examples of specific components, devices, and methods, to provide a thorough understanding of embodiments of the present disclosure. It will be apparent to those skilled in the art that specific details need not be employed, that example embodiments may be embodied in many different forms and that neither should be construed to limit the scope of the disclosure. In some example embodiments, well-known processes, well-known device structures, and well- known technologies are not described in detail.
  • first, second, third, etc. may be used herein to describe various elements, components, regions, layers and/or sections, these elements, components, regions, layers and/or sections should not be limited by these terms. These terms may be only used to distinguish one element, component, region, layer or section from another region, layer or section. Terms such as “first,” “second,” and other numerical terms when used herein do not imply a sequence or order unless clearly indicated by the context. Thus, a first element, component, region, layer or section discussed below could be termed a second element, component, region, layer or section without departing from the teachings of the example embodiments.

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Abstract

La présente invention concerne un système de transmission (12) comprenant une première poulie (11) reliée à une sortie (111) par un câble (40) de sorte que le mouvement de la première poulie provoque la rotation de la sortie. La première poulie comprend un évidement annulaire (25) entre un premier côté (17) de la première poulie et un seconde côté (19) de la première poulie. L'évidement annulaire est conçu pour recevoir le câble de sorte que le câble est supporté par la première poulie. La première poulie comprend également une paire de surfaces de support (31) situées dans l'évidement annulaire. La paire de surfaces de support sont mobiles dans une direction latérale par rapport aux côtés de la poulie entre un état espacé, où la première poulie est à un premier diamètre et la paire de surfaces de support n'entre pas en prise avec le câble, et un état maillé, où la première poulie est à un second diamètre et la paire de surfaces de support supporte le câble, le second diamètre étant supérieur au premier diamètre.
PCT/AU2018/050724 2017-07-13 2018-07-13 Poulie et système de transmission Ceased WO2019010539A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201880058814.7A CN111448405A (zh) 2017-07-13 2018-07-13 皮带轮和传动系统
EP18831892.7A EP3652469A4 (fr) 2017-07-13 2018-07-13 Poulie et système de transmission
AU2018299208A AU2018299208A1 (en) 2017-07-13 2018-07-13 A pulley and transmission system

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
AU2017902759A AU2017902759A0 (en) 2017-07-13 A Pulley and Transmission System
AU2017902759 2017-07-13
AU2017903939A AU2017903939A0 (en) 2017-09-28 A Pulley and Transmission System
AU2017903939 2017-09-28

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CN111448405A (zh) 2020-07-24
CN111094798A (zh) 2020-05-01
EP3652469A1 (fr) 2020-05-20
EP3652468A1 (fr) 2020-05-20
AU2018299208A1 (en) 2020-03-05
WO2019010541A1 (fr) 2019-01-17
AU2018299210A1 (en) 2020-03-05
WO2019010539A1 (fr) 2019-01-17
WO2019010541A9 (fr) 2019-03-07
EP3652468A4 (fr) 2021-08-18
EP3652469A4 (fr) 2021-08-18

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