JP2016217419A5 - - Google Patents

Description

As a result, the hydraulic pressure introduced into the hydraulic chamber 45 of the pressing device 5 is, from the target value, wherein the differential pressure extraction valve 47 is set, subtracting the correction value based on the hydraulic pressure introduced into the third pilot portion 44 It is corrected (reduced pressure) to a required value proportional to the measured value. The oil pressure introduced into the third pilot section 44 is such that the oil temperature decreases as the shift ratio increases from a predetermined value (a value that requires the largest oil pressure, for example, 1.32). Make each higher. As described above, in the case of the toroidal continuously variable transmission 4 that uses a hydraulic device as a pressing device for securing the surface pressure of each traction portion, including the structure described in Patent Document 3. Obtains the pressing force to be generated by the pressing device from the passing torque, transmission ratio, oil temperature, etc. of the toroidal type continuously variable transmission 4, and supplies the hydraulic pressure corresponding to the pressing force in the hydraulic chamber 45 of the pressing device 5. I am trying to introduce it.

(2) Delay in calculation of the gear ratio of the toroidal continuously variable transmission 4 The gear ratio of the toroidal continuously variable transmission 4 is determined by the rotational speed of the input side disk 6 detected by the input side rotation sensor 9, and It is calculated as a ratio with the rotational speed of the output side disk 8 detected by the output side rotation sensor 10. However, in order to detect the rotational speeds of the two disks 6 and 8 detected by the both rotation sensors 9 and 10 with necessary accuracy, it is necessary to rotate the both disks 6 and 8 by a predetermined angle or more. For this reason, there is a delay until the rotational speeds of the discs 6 and 8 are detected and the gear ratio of the toroidal continuously variable transmission 4 is calculated.

[First example of embodiment]
A first example of the embodiment of the present invention will be described with reference to FIG.
The continuously variable transmission of this example includes a toroidal continuously variable transmission 4a (see FIG. 3), a planetary gear device 12 (see FIG. 3) which is a gear-type differential unit formed by combining a plurality of gears, and these which was a clutch device 13 for switching the power transmission state between the toroidal type continuously variable speed change unit 4a and the planetary gear unit 12 (see FIGS. 3-4), its basic structure and operation principle This is the same as the continuously variable transmission shown in FIGS.

In this example, in order to temporarily increase the hydraulic pressure introduced into the hydraulic chamber 45 of the pressing device 5 in this way, in the case of this example, an accumulator is provided as a hydraulic source separately from the oil pump 18 driven by the engine 1. 55. The accumulator 55 via the auxiliary line 57, connects to the input port of the high-speed solenoid valve 56, the output port of the high-speed solenoid valve 56 is connected to the high pressure line 49. That is, by energizing the solenoid of the high-speed solenoid valve 56, these inputs, by communicating the output both ports, the pressure oil in the accumulator 55, via the high pressure line 49, constituting the loading mechanism 51 It can be introduced into the hydraulic chamber 45 of the pressing device 5. For this reason, in the case of this example, in the state immediately before the power to at least the solenoid of the high-speed solenoid valve 56, the hydraulic auxiliary line 57 and the accumulator 55 side, from the hydraulic pressure of the high pressure line 49 side Is also high. In the case of this example, pressure oil can be supplied to the accumulator 55 by an electric pump 58 provided separately from the oil pump 18. That is, the pressure oil is supplied through the auxiliary line 57 through the auxiliary line 57 while the energization to the solenoid of the high-speed solenoid valve 56 is stopped and the pressure oil sucked from the oil reservoir 39 and discharged by the electric pump 58 is discharged. This is done by introducing it into the accumulator 55. At this time, the hydraulic pressure on the auxiliary line 57 and the accumulator 55 side is set higher than the hydraulic pressure on the high pressure line 49 side.

Claims (1)

At least one pair of disks arranged coaxially with each other for relative rotation, a plurality of power rollers sandwiched between these disks, and a plurality of supports that rotatably support each of these power rollers A member, an actuator that displaces each of these support members to change the speed ratio between the two disks, and a pressing device that presses the two disks toward each other,
The pressing device is of a hydraulic type that generates a pressing force proportional to the hydraulic pressure with the introduction of the hydraulic pressure into the hydraulic chamber, and the hydraulic pressure introduced into the hydraulic chamber of the pressing device is between the two disks. It is adjusted according to the magnitude of the force transmitted between
As a hydraulic source for introducing a hydraulic pressure to the hydraulic chamber of the pressing device includes an oil pump, an accumulator,
Toroidal continuously variable transmission.