An apparatus and methods are provided for an air-cooled CVT clutch. The air-cooled CVT clutch includes a first cooling fan coupled with a primary clutch and a second cooling fan coupled with a secondary clutch. An outboard housing mates with an inboard housing to enclose the primary clutch and the secondary clutch. The first cooling fan is coupled to a moveable sheave comprising the primary clutch and configured to draw a cooling airstream through an air duct disposed in the outboard housing. The second cooling fan is coupled to a moveable sheave comprising the secondary clutch and configured to draw the cooling airstream from the primary clutch to the secondary clutch. The first cooling fan pushes the cooling airstream to the secondary clutch when the second clutch is not rotating.

When a chain is wound around a pulley, a pin-pulley contact point as a contact point of a pin of the chain with the pulley slides and moves on a conical surface of the pulley. A contact point slip distance, namely the distance by which the pin-pulley contact point moves on the conical surface at this time, is associated with an offset. The offset is the distance between a pin-pin contact point, which is a contact point between the pins at the time the chain is in a linear state, and the pin-pulley contact point in a y-axis direction. Offsets that minimize the contact point slip distance at the maximum running radius and the minimum running radius of the chain are obtained, and the offset is set between these values. The pin-pulley contact point is set close to the pin-pin contact point of the chain in the linear state.

When a chain is wound around a pulley, a pin-pulley contact point as a contact point of a pin of the chain with the pulley slides and moves on a conical surface of the pulley. A contact point slip distance, namely the distance by which the pin-pulley contact point moves on the conical surface at this time, is associated with an offset. The offset is the distance between a pin-pin contact point, which is a contact point between the pins at the time the chain is in a linear state, and the pin-pulley contact point in a y-axis direction. Offsets that minimize the contact point slip distance at the maximum running radius and the minimum running radius of the chain are obtained, and the offset is set between these values. The pin-pulley contact point is set close to the pin-pin contact point of the chain in the linear state.

The present concept is a continuously variable speed transmission and steering differential. It includes a laterally extending central drive axle driven by an external power source, two pairs of drive sheaves mounted to drive axles, and a means for transmitting rotational energy from the drive sheaves to the drive axles. There are two extended shift arms spaced apart for controlling the positioning of movable drive sheaves. Narrowing or increasing the gap between shift arms, does the same for the gap between the drive sheaves, increasing or decreasing the gear ration respectively which provides speed control. Shifting the shift arms left or right varies the gear ratio between the left and right pair of sheaves, providing differential speed between the left and right driven axles, which provides steering control.

The present concept is a continuously variable speed transmission and steering differential. It includes a laterally extending central drive axle driven by an external power source, two pairs of drive sheaves mounted to drive axles, and a means for transmitting rotational energy from the drive sheaves to the drive axles. There are two extended shift arms spaced apart for controlling the positioning of movable drive sheaves. Narrowing or increasing the gap between shift arms, does the same for the gap between the drive sheaves, increasing or decreasing the gear ration respectively which provides speed control. Shifting the shift arms left or right varies the gear ratio between the left and right pair of sheaves, providing differential speed between the left and right driven axles, which provides steering control.

Described are an oscillation amplitude control component, home electrical equipment and an oscillation amplitude control method and device. The component includes: a V-shaped grooved gear, a pressure pump, a roller with a pre-formed groove and a transmission belt; the V-shaped grooved gear includes a central shaft and two frustoconical members mounted on the central shaft; lateral surfaces of two frustoconical members and the central shaft enclose a V-shaped groove; a gear is arranged on a circumference of a frustoconical member, and joined with an oscillating switch selectively; the transmission belt is configured to surround the V-shaped groove and the pre-formed groove; two frustoconical members regulate a surrounding radius of the transmission belt surrounding the V-shaped groove under control of pressure generated by the pressure pump; and the roller is fixed in an oscillating plate, and controls an oscillation amplitude of the home electrical equipment through the oscillating plate.

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 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.