A drive clutch having an engine braking feature for a continuously variable transmission is provided. The drive clutch includes a post that is coupled to an output of an engine. A fixed sheave, coupled to the post, has a fixed sheave belt engagement face. A movable sheave assembly that includes a movable sheave belt engaging face, is configured to move axially on the post to move the movable sheave belt engaging face in relation to the fixed sheave belt engaging face depending on a rotational speed of the drive clutch. An idler bearing is mounted on the post at least in part between the movable sheave belt engaging face and the fixed sheave belt engaging face. The idler bearing includes a one-way rotational assembly and has an outer belt engaging surface with outward extending cogs configured to engage teeth of a belt to prevent slippage during engine braking.

A flyweight comprises a body. The body of the flyweight comprises a pivot, a cam surface, and a first coupler. The first coupler is configured to selectively couple at least one first weight to the body distal from the cam surface. A flyweight comprises a body having at least 20% of its mass positioned to contribute negative torque about a pivot related to an acceleration of a CVT clutch from an idling condition. A method of tuning a flyweight comprises attaching at least one first weight to a first coupler of a body of the flyweight distal from a cam surface of the body. A CVT clutch comprises at least one flyweight with a first coupler configured to selectively couple at least one first weight to a body of the flyweight distal from a cam surface.

Provided are a support structure whereby the load on a motor drive shaft or bearing can be reduced, and an industrial machine. The support structure according to an embodiment of the present invention comprises a bearing (112) positioned between a motor (102) and a drive pulley (104), and a bearing holder (114) provided to the motor (102). An inner race (120) of the bearing (112) is fixed to the drive pulley (104) so as to be incapable of sliding in the axial direction of a drive shaft (102S), and an outer race (122) of the bearing (112) is allowed to move in the axial direction between the bearing holder (114) and the drive pulley (104).

Provided are a support structure whereby the load on a motor drive shaft or bearing can be reduced, and an industrial machine. The support structure according to an embodiment of the present invention comprises a bearing (112) positioned between a motor (102) and a drive pulley (104), and a bearing holder (114) provided to the motor (102). An inner race (120) of the bearing (112) is fixed to the drive pulley (104) so as to be incapable of sliding in the axial direction of a drive shaft (102S), and an outer race (122) of the bearing (112) is allowed to move in the axial direction between the bearing holder (114) and the drive pulley (104).

A variety of shifter mechanisms are provided for controlling the axial distance between half-pulleys of a split pulley variable transmission, thus controlling the transmission ratio of the variable transmission. Some of these embodiments include a differential such that a variable transmission can be driven and shifted differentially by two inputs. A torque or rotation difference between the inputs results in a change in the transmission ratio and in-common torque or rotation is transmitted through the transmission to an output. The same motors used to drive the output of the transmission are thus also able to effect shifts in the transmission ratio. Accordingly, motor mass that is not being used to effect high-speed shifts may be used to drive the transmission output, and vice versa. The provided shifter embodiments are well-suited to application to nested-pulley variable transmissions, including nested-pulley infinitely variable transmissions.

A variety of shifter mechanisms are provided for controlling the axial distance between half-pulleys of a split pulley variable transmission, thus controlling the transmission ratio of the variable transmission. Some of these embodiments include a differential such that a variable transmission can be driven and shifted differentially by two inputs. A torque or rotation difference between the inputs results in a change in the transmission ratio and in-common torque or rotation is transmitted through the transmission to an output. The same motors used to drive the output of the transmission are thus also able to effect shifts in the transmission ratio. Accordingly, motor mass that is not being used to effect high-speed shifts may be used to drive the transmission output, and vice versa. The provided shifter embodiments are well-suited to application to nested-pulley variable transmissions, including nested-pulley infinitely variable transmissions.

A continuously variable transmission driven pulley movable sheave comprising a beveled face disk, an elongated hollow cylindrical collar extending orthogonally from a center of the beveled face disk, and a triangular shaped tuning pocket disposed in the collar. The tuning pocket is structured and operable to control axial movement of the movable sheave on the elongated neck of the driven pulley. The tuning pocket comprises a first gear side, an acceleration side disposed at a positive angle relative to a reference point on the first gear side, and a deceleration side disposed at a negative angle relative to the reference point on the first gear side.

A continuously variable transmission driven pulley movable sheave comprising a beveled face disk, an elongated hollow cylindrical collar extending orthogonally from a center of the beveled face disk, and a triangular shaped tuning pocket disposed in the collar. The tuning pocket is structured and operable to control axial movement of the movable sheave on the elongated neck of the driven pulley. The tuning pocket comprises a first gear side, an acceleration side disposed at a positive angle relative to a reference point on the first gear side, and a deceleration side disposed at a negative angle relative to the reference point on the first gear side.

Steel materials for continuously variable transmissions sheaves, and methods for manufacturing a continuously variable transmission sheaves, are provided. In the disclosed steel materials for continuously variable transmission sheaves, the steel materials satisfy the following expressions: 13.9≤Fn1≤15.5, and 1.20≤Fn2≤4.35 (in which Fn1=7×Cr−6×Si+4×Mn; and Fn2=Al×N×10.sup.4).

Steel materials for continuously variable transmissions sheaves, and methods for manufacturing a continuously variable transmission sheaves, are provided. In the disclosed steel materials for continuously variable transmission sheaves, the steel materials satisfy the following expressions: 13.9≤Fn1≤15.5, and 1.20≤Fn2≤4.35 (in which Fn1=7×Cr−6×Si+4×Mn; and Fn2=Al×N×10.sup.4).