A drive mechanism includes a mount block extending along an axis and a plurality of electric motors supported by the mount block. The electric motors are arranged in series along the axis to define an initial electric motor, one or more intermediate electric motors, and a final electric motor. The drive mechanism also includes a gear mounted to each of the electric motors, and an output member driven by the gear mounted to the final electric motor to receive the combined rotational torque from the gears of the series of electric motors.

A drive mechanism includes a mount block extending along an axis and a plurality of electric motors supported by the mount block. The electric motors are arranged in series along the axis to define an initial electric motor, one or more intermediate electric motors, and a final electric motor. The drive mechanism also includes a gear mounted to each of the electric motors, and an output member driven by the gear mounted to the final electric motor to receive the combined rotational torque from the gears of the series of electric motors.

A power transmission chain (2) for use with a drive member (4) having a plurality of teeth (6), and wherein: (i) the power transmission chain (2) comprises a plurality of chain links (8) which are pivotally connected together by connecting members (9) and pivot arrangements (10) so that the power transmission chain (2) can pass around the drive member (4) in use; (ii) each one of the pivot arrangements (10) comprises first and second pivots (12, 14) which extend towards each other from opposite sides (16, 18) of the chain links (8); (iii) the first and second pivots (12, 14) have adjacent ends (20, 22) which face each other and which are spaced apart; (iv) the power transmission chain (2) comprises a plurality of engaging formations (24) for enabling engagement with the drive member (4); (v) the engaging formations (24) are positioned between the adjacent ends (20, 22) of the first and second pivots (12, 14); and the engaging formations (24) and the spacing apart of the adjacent ends (20, 22) of the first and second pivots (12, 14) cause the power transmission chain (2) in use always to be positioned on the drive member (4) for maximum efficiency of drive transfer between the drive member (4) and the power transmission chain (2), and irrespective of the diameter of the drive member (4).

A kinematic chain comprises a first pulley, arranged to rotate about a rotation axis x, and a second pulley arranged to rotate about a rotation axis y. The kinematic chain comprises then at least one connecting element comprising at least one passage having at least one rotating element, said or each connecting element also comprising at least one interface arranged to connect the connecting element to an adjacent connecting element or to a pulley, generating a rotational constraint about a rotation axis z. The kinematic chain also comprises a transmission element arranged to develop along a determined path for transmitting a rotational motion between the first pulley and the second pulley. The transmission element is adapted to be, in use, fixedly in contact with said or each rotating element by a constraint of rolling friction, in order to allow a modelling the determined path according to a predetermined geometry.

A kinematic chain comprises a first pulley, arranged to rotate about a rotation axis x, and a second pulley arranged to rotate about a rotation axis y. The kinematic chain comprises then at least one connecting element comprising at least one passage having at least one rotating element, said or each connecting element also comprising at least one interface arranged to connect the connecting element to an adjacent connecting element or to a pulley, generating a rotational constraint about a rotation axis z. The kinematic chain also comprises a transmission element arranged to develop along a determined path for transmitting a rotational motion between the first pulley and the second pulley. The transmission element is adapted to be, in use, fixedly in contact with said or each rotating element by a constraint of rolling friction, in order to allow a modelling the determined path according to a predetermined geometry.

A high performance synchronous transmission to be used aboard a motorcycle for transmitting the motion generated by an engine to a driving wheel, between a crankshaft and a hub shaft parallel therebetween and perpendicular to the median plane of the motorcycle, comprising on the crankshaft a centrifugal clutch, for the automatic engagement of the first speed above a predetermined rotation regime, and a driving pulley apt to transmit the motion through a subsequent kinematic chain, is provided with a coupling between crankshaft and driving pulley which connects them directly, by determining with its own engagement the exclusion of said centrifugal clutch, said coupling being controlled in disengagement when a control lever is in active position.

A high performance synchronous transmission to be used aboard a motorcycle for transmitting the motion generated by an engine to a driving wheel, between a crankshaft and a hub shaft parallel therebetween and perpendicular to the median plane of the motorcycle, comprising on the crankshaft a centrifugal clutch, for the automatic engagement of the first speed above a predetermined rotation regime, and a driving pulley apt to transmit the motion through a subsequent kinematic chain, is provided with a coupling between crankshaft and driving pulley which connects them directly, by determining with its own engagement the exclusion of said centrifugal clutch, said coupling being controlled in disengagement when a control lever is in active position.

A power transmission chain (2) for use with a drive member (4) having a plurality of teeth (6), and wherein: (i) the power transmission chain (2) comprises a plurality of chain links (8) which are pivotally connected together by connecting members (9) and pivot arrangements (10) so that the power transmission chain (2) can pass around the drive member (4) in use; (ii) each one of the pivot arrangements (10) comprises first and second pivots (12, 14) which extend towards each other from opposite sides (16, 18) of the chain links (8); (iii) the first and second pivots (12, 14) have adjacent ends (20, 22) which face each other and which are spaced apart; (iv) the power transmission chain (2) comprises a plurality of engaging formations (24) for enabling engagement with the drive member (4); (v) the engaging formations (24) are positioned between the adjacent ends (20, 22) of the first and second pivots (12, 14); and the engaging formations (24) and the spacing apart of the adjacent ends (20, 22) of the first and second pivots (12, 14) cause the power transmission chain (2) in use always to be positioned on the drive member (4) for maximum efficiency of drive transfer between the drive member (4) and the power transmission chain (2), and irrespective of the diameter of the drive member (4).

A drive-side rotor is rotated synchronously with a crankshaft. A driven-side rotor is rotated integrally with a camshaft. An internal gear section is formed at the driven-side rotor. An Oldham coupling includes: a driven Oldham flange that is formed at the drive-side rotor; a drive Oldham flange that is formed at the planetary rotor; and an Oldham intermediate that is configured to synchronize rotation of the driven Oldham flange and rotation of the drive Oldham flange while permitting eccentricity between the driven Oldham flange and the drive Oldham flange. There is satisfied a relationship of θ2<θ1 where: θ1 is a maximum tilt amount of the planetary rotor relative to the driven Oldham flange; and θ2 is a maximum tilt amount of the planetary rotor in a clearance formed at the Oldham coupling.

A sprocket support comprises at least ten internal spline teeth configured to engage with a bicycle hub assembly. The at least ten internal spline teeth of the sprocket support includes at least ten internal-spline driving surfaces. The at least ten internal-spline driving surfaces each include a radially outermost edge and a radially innermost edge. A radial length is defined from the radially outermost edge to the radially innermost edge. A total of the radial lengths of the at least ten internal-spline driving surfaces is equal to or larger than 7 mm. At least one internal-spline driving surface of the at least ten internal-spline driving surfaces has a first internal-spline-surface angle defined between the at least one internal-spline driving surface of the at least ten internal-spline driving surfaces and a first radial line. The first internal-spline-surface angle ranges from 0 degree to 10 degrees.