JP2009281403A - Synchronous control device for continuously variable transmission and continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a synchronous control device for a continuously variable transmission capable of securely synchronizing tilting of a plurality of power rollers, and the continuously variable transmission. <P>SOLUTION: In the synchronous control device 100 for the continuously variable transmission 1, nipping force for nipping the plurality of power rollers 4 between an input disk 2 and an output disk by a nipping means 15 can be applied, and by synchronously tilting the plurality of power rollers 4, a transmission ratio which is a rotating speed ratio between the input disk 2 and output disk can be steplessly changed. The synchronous control device 100 is provided with a control means 66 for executing synchronous control for synchronizing the plurality of power rollers 4 by lowering the nipping force by the nipping means 15. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a synchronous control device for a continuously variable transmission and a continuously variable transmission. The present invention relates to a synchronous transmission control device and a continuously variable transmission.

  In general, a vehicle has a transmission on the output side of the drive source in order to transmit a driving force from an internal combustion engine or an electric motor that is a drive source, that is, an output torque, to the road surface under an optimal condition according to the traveling state of the vehicle. Is provided. This transmission includes a continuously variable transmission that controls the gear ratio steplessly (continuously) and a stepped transmission that controls the gear ratio stepwise (discontinuously). Here, in such a continuously variable transmission, so-called CVT (CVT: Continuously Variable Transmission), for example, torque is transmitted between the disks via a power roller sandwiched between the input disk and the output disk. In addition, there is a so-called toroidal continuously variable transmission that tilts the power roller to change the gear ratio.

  This toroidal-type continuously variable transmission has a rotating means such as a power roller whose outer peripheral surface is a curved surface corresponding to the toroidal surface between an input disc having a toroidal surface and an output disc. Torque is transmitted using the shear force of the oil film of traction oil formed between the power rollers. The power roller is rotatably supported by a trunnion. The trunnion can be swung around a swing shaft, and, for example, can be placed in a transmission control hydraulic chamber with respect to a piston provided in the trunnion. The shift control pressing force is applied by the hydraulic pressure of the supplied hydraulic oil so as to be movable in the direction along the swing shaft. Therefore, when the power roller supported by the trunnion moves with the trunnion from the neutral position to the input disk and the output disk to the shift position, a tangential force acts between the power roller and the disk, and a side slip occurs. The power roller swings, that is, tilts about the swing axis with respect to the input disk and the output disk, and as a result, the speed ratio, which is the rotational speed ratio between the input disk and the output disk, is changed. The speed ratio, which is the rotational speed ratio between the input disk and the output disk, is determined based on the angle at which the power roller tilts with respect to the input disk and the output disk, that is, the tilt angle. It is determined based on an integral value of a stroke amount (offset amount) as a movement amount from the neutral position of the power roller to the shift position side.

  As such a conventional toroidal-type continuously variable transmission, for example, a method for assembling a toroidal-type continuously variable transmission for a vehicle described in Patent Document 1 is provided between an input side disk and an output side disk. By assembling the power roller so that the speed change between the disks is in the maximum deceleration state, the vehicle can be started without having to perform idle driving to obtain a startable gear ratio after assembly and before mounting on the vehicle. Is possible.

JP 2003-329095 A

  However, in the method for assembling the toroidal type continuously variable transmission for a vehicle described in Patent Document 1 described above, for example, it is very difficult to accurately assemble a plurality of power rollers between an input disk and an output disk. Work. That is, high assembly accuracy is required for assembly in a state in which the tilt angles of all the power rollers are matched and synchronized. For this reason, there is a possibility that the plurality of power rollers are not completely synchronized immediately after assembly. As a result, for example, the tilting of the plurality of power rollers cannot be synchronized by a synchronization mechanism such as a synchronization wire, and power circulation may occur, which may require a large input torque to the disk at the start. Then, it becomes difficult to start the toroidal continuously variable transmission immediately after the assembly of the power roller, and it may be difficult to start a vehicle equipped with the toroidal continuously variable transmission.

  Accordingly, an object of the present invention is to provide a continuously variable transmission synchronization control device and a continuously variable transmission that can reliably synchronize the tilting of a plurality of power rollers.

  In order to achieve the above object, the continuously variable transmission synchronous control device according to the first aspect of the present invention is capable of applying a pinching pressure for pinching a plurality of power rollers between the input disk and the output disk by the pinching means. And a continuously variable transmission synchronization control device capable of steplessly changing a speed ratio, which is a rotational speed ratio between the input disk and the output disk, by synchronizing and tilting the plurality of power rollers. And a control means for executing a synchronous control for synchronizing the plurality of power rollers by reducing the clamping pressure by the clamping means.

  In the synchronous control device for a continuously variable transmission according to the second aspect of the present invention, the control means is configured such that the input disk or the output disk cannot rotate even if power is input to the input disk or the output disk. The synchronization control is executed, and the clamping pressure is reduced until at least the input disk or the output disk rotates.

  In the synchronous control device for a continuously variable transmission according to a third aspect of the invention, the continuously variable transmission supports the plurality of power rollers rotatably and tiltably, and tilts the power roller. The gear ratio changing means capable of changing the gear ratio and a regulating means for regulating the tilting of the plurality of power rollers at a predetermined tilt angle, and the control means executes the synchronization control. In this case, the predetermined tilt angle is set to a target tilt angle that is a target tilt angle, and the transmission gear ratio changing means is configured so that the actual tilt angle that is the actual tilt angle of the power roller is the target tilt angle. The power roller is tilted so as to have a tilt angle.

  To achieve the above object, a continuously variable transmission according to a fourth aspect of the present invention includes an input disk to which a driving force is input, an output disk to which the driving force is output, the input disk, and the output disk. A plurality of power rollers provided between the input disk and the output disk by supporting the power roller rotatably and tiltably and tilting the plurality of power rollers synchronously. A speed ratio changing means capable of changing a speed ratio, which is a rotational speed ratio of the motor, a pressure-holding means capable of acting a pinching pressure to sandwich the power roller between the input disk and the output disk, and the pressure-pressing means And a control unit that executes synchronous control for synchronizing the plurality of power rollers by reducing the clamping pressure.

  According to the synchronous control device for a continuously variable transmission according to the present invention, since the control means for performing the synchronous control for synchronizing the plurality of power rollers by reducing the clamping pressure by the clamping means, The tilt can be reliably synchronized.

  According to the continuously variable transmission according to the present invention, since the control unit that performs the synchronous control for synchronizing the plurality of power rollers by reducing the clamping pressure by the clamping unit, the tilting of the plurality of power rollers is ensured. Can be synchronized.

  Embodiments of a continuously variable transmission synchronization control device and a continuously variable transmission according to the present invention will be described below in detail with reference to the drawings. In addition, this invention is not limited by this embodiment. In addition, constituent elements in the following embodiments include those that can be easily replaced by those skilled in the art or those that are substantially the same.

(Embodiment)
FIG. 1 is a schematic sectional view of a toroidal continuously variable transmission to which a synchronous control device for a toroidal continuously variable transmission according to an embodiment of the present invention is applied. FIG. 2 is a toroidal continuously variable transmission according to an embodiment of the present invention. FIG. 3 is a configuration diagram of a main part of a toroidal continuously variable transmission to which a synchronous control device for a transmission is applied, and FIG. 3 is a toroidal continuously variable to which a synchronous control device for a toroidal continuously variable transmission according to an embodiment of the present invention is applied. FIG. 4 is a schematic diagram illustrating a neutral position of the power roller included in the transmission with respect to the input disk, and FIG. 4 is provided in the toroidal continuously variable transmission to which the synchronous control device for the toroidal continuously variable transmission according to the embodiment of the present invention is applied. FIG. 5A is a schematic diagram for explaining a shift position of the power roller with respect to the input disk, and FIG. 5A includes a toroidal continuously variable transmission to which the synchronous control device for the toroidal continuously variable transmission according to the embodiment of the present invention is applied. FIG. 5B is a side view of the stopper portion, FIG. 5-2 is a plan view of the stopper portion provided in the toroidal continuously variable transmission to which the synchronous control device for the toroidal continuously variable transmission according to the embodiment of the present invention is applied, and FIG. FIG. 7 is a flowchart for explaining synchronization control execution determination control in the toroidal continuously variable transmission synchronization control device according to the embodiment of the present invention, and FIG. 7 is in the toroidal continuously variable transmission synchronization control device according to the embodiment of the present invention. FIG. 8 is a time chart for explaining an example of the synchronization control execution determination control and the synchronization control in the synchronization control device for the toroidal continuously variable transmission according to the embodiment of the present invention.

  In the embodiment described below, a case will be described in which the synchronous control device 100 for a continuously variable transmission according to the present invention is incorporated in an ECU 60 as shown in FIG. That is, in the embodiment described below, the case where the synchronization control apparatus 100 is also used by the ECU 60 will be described. However, the continuously variable transmission synchronization control device 100 of the present invention may be configured separately from the ECU 60 and connected to the ECU 60.

  FIG. 2 is a diagram showing an arbitrary power roller among the power rollers constituting the toroidal-type continuously variable transmission as the continuously variable transmission, and an input disk in contact with the power roller. 3 and 4 are views of the input disk as viewed from the output disk side, and schematically show only one input disk and one power roller.

  Here, in the embodiment described below, an internal combustion engine (gasoline engine, diesel engine, LPG engine, or the like) that generates engine torque is used as a drive source that generates drive force transmitted to the continuously variable transmission of the present invention. However, the present invention is not limited to this, and an electric motor such as a motor that generates motor torque may be used as a drive source. Moreover, you may use an internal combustion engine and an electric motor together as a drive source.

  As shown in FIG. 1, a toroidal continuously variable transmission 1 as a continuously variable transmission according to the present embodiment uses a driving force from an engine 21 as a drive source mounted on a vehicle, that is, an output torque, as the vehicle travels. This is a so-called CVT (CVT: Continuously Variable Transmission) that can be transmitted to the drive wheels 27 under the optimum conditions according to the state and can control the gear ratio steplessly (continuously). The toroidal-type continuously variable transmission 1 transmits torque between each input disk 2 and output disk 3 via a power roller 4 sandwiched between the input disk 2 and the output disk 3, and It is a so-called toroidal continuously variable transmission that tilts and changes the gear ratio. That is, the toroidal continuously variable transmission 1 includes a power roller 4 having an outer peripheral surface curved between the input disk 2 and the output disk 3 having the toroidal surfaces 2a and 3a and corresponding to the toroidal surfaces 2a and 3a. The torque is transmitted using the shear force of the oil film of traction oil formed between the input disk 2, the output disk 3 and the power roller 4.

  Specifically, as shown in FIGS. 1 and 2, the toroidal continuously variable transmission 1 includes an input disk 2, an output disk 3, a power roller 4, and a speed ratio changing unit as speed ratio changing means. 5. The gear ratio changing unit 5 includes a trunnion 6 as a support unit and a moving unit 7 as a moving unit. Further, the moving unit 7 includes a hydraulic piston unit 8 and a hydraulic control device 9. The toroidal continuously variable transmission 1 includes an electronic control unit (ECU) 60 that controls each part of the toroidal continuously variable transmission 1. In this toroidal continuously variable transmission 1, the power roller 4 provided in contact with the input disk 2 and the output disk 3 is moved from the neutral position to the shift position with respect to the input disk 2 and the output disk 3 by the moving unit 7. As a result, the gear ratio, which is the rotational speed ratio between the input disk 2 and the output disk 3, is changed.

  The input disk 2 transmits (inputs) a driving force (torque) from the engine 21 via, for example, a torque converter 22 that is a starting mechanism and a fluid transmission device, a forward / reverse switching mechanism 23, and the like. .

  The engine 21 outputs an engine torque, that is, a driving force for moving forward or backward the vehicle on which the engine 21 is mounted. Further, the engine 21 is electrically connected to the ECU 60, the driving of the engine 21 is controlled by the ECU 60, and the driving force to be output is controlled. The driving force from the engine 21 is transmitted to the torque converter 22 via the crankshaft 21a.

  The torque converter 22 transmits the driving force from the engine 21 to the toroidal continuously variable transmission 1 via the forward / reverse switching mechanism 23. The torque converter 22 includes a pump (pump impeller), a turbine (turbine runner), a stator, and a lockup clutch. The pump is connected to the crankshaft 21a of the engine 21 via a front cover or the like, and is rotatably provided together with the crankshaft 21a and the front cover. The turbine is arranged to face the pump. The turbine is connected to the input shaft 10 via an input shaft 22a and a forward / reverse switching mechanism 23, and is provided so as to be rotatable about the same axis as the crankshaft 21a together with the input shaft 10. The stator is disposed between the pump and the turbine. The lockup clutch is provided between the turbine and the front cover, and is connected to the turbine.

  Therefore, in the torque converter 22, the driving force (engine torque) of the engine 21 is transmitted from the crankshaft 21a to the pump via the front cover. When the lock-up clutch is released, the driving force transmitted to the pump is transmitted to the turbine, the input shaft 22a, and the input shaft via hydraulic oil that is a working fluid interposed between the pump and the turbine. 10 is transmitted. At this time, the torque converter 22 can obtain a predetermined torque characteristic by changing the flow of the working oil circulating between the pump and the turbine by the stator. In the torque converter 22, when the lockup clutch connected to the turbine is engaged with the front cover, the driving force transmitted from the engine 21 to the pump via the front cover does not pass through the hydraulic oil. To the input shaft 10 directly. Here, the engagement / disengagement of the lock-up clutch, that is, ON / OFF control for performing ON / OFF is performed by hydraulic oil supplied from a hydraulic control device 9 described later. The hydraulic control device 9 is connected to an ECU 60 described later. Therefore, the ECU 60 performs ON / OFF control of the lockup clutch.

  The forward / reverse switching mechanism 23 transmits the driving force transmitted from the engine 21 via the torque converter 22 to the input disk 2 of the toroidal continuously variable transmission 1. The forward / reverse switching mechanism 23 includes, for example, a planetary gear mechanism, a forward clutch (friction clutch), a reverse brake (friction brake), and the like, and transmits the driving force of the engine 21 to the input disk 2 directly or reversely. Is. That is, the driving force of the engine 21 via the forward / reverse switching mechanism 23 is a positive rotational driving force that acts in the direction in which the input disk 2 rotates forward (the direction in which the input disk 2 rotates when the vehicle moves forward), or The input disk 2 is transmitted to the input disk 2 as a reverse rotation driving force that acts in the direction in which the input disk 2 rotates in the reverse direction (the direction in which the input disk 2 rotates when the vehicle moves backward). The switching control of the driving force transmission direction by the forward / reverse switching mechanism 23 is performed by executing ON / OFF control for engaging and releasing the forward clutch and reverse brake, that is, ON / OFF. Switching control of the transmission direction of the driving force by the forward / reverse switching mechanism 23, in other words, ON / OFF control of the forward clutch and the reverse brake is performed by hydraulic oil supplied from a hydraulic control device 9 described later. Therefore, the switching control of the forward / reverse switching mechanism 23 is performed by the ECU 60.

  In the forward / reverse switching mechanism 23, for example, when the vehicle travels forward, the forward clutch is turned on and the reverse brake is turned off. When the vehicle is traveling backward, the forward clutch is turned off and the reverse brake is turned on. Thereby, the forward / reverse switching mechanism 23 can switch the rotational direction of the torque. In the forward / reverse switching mechanism 23, the forward clutch is turned off and the reverse brake is turned off at the neutral time.

Two input disks 2 are coupled to an input shaft 10 that is rotated based on the rotation of the engine 21, and is rotatably provided by the input shaft 10. More specifically, each input disk 2 is rotated by a variator shaft 11 that rotates in the same manner as the input shaft 10. Accordingly, each input disk 2 can rotate around the rotation axis X1 of the input shaft 10 as a rotation center. The toroidal type continuously variable transmission 1, with respect to the variator shaft 11, a front side (engine 21 side) front input disk 2 _F is provided, in the direction along the rotation axis X1 in front input disk 2 _F A rear side input disk _2R is provided on the rear side (drive wheel 27 side) at a predetermined interval.

Front input disk 2 _F is supported on the variator shaft 11 via the ball spline 11a. That is, the front-side input disk 2 _F, together with the rotatable with the rotation of the variator shaft 11 is supported by the movable variator shaft 11 along the rotation axis X1 direction with respect to the variator shaft 11 . Still other words, the front-side input disk 2 _F, to the variator shaft 11, whereas no relative rotational displacement about the rotational axis X1, in the direction along the rotation axis X1 can be relatively displaced. On the other hand, the rear input disk 2 _R, together are supported by a variator shaft 11 through a spline fitting portion, along the rotation axis X1 by a snap ring 11b provided on the rear end of the variator shaft 11 direction Movement to is restricted. In other words, the rear input disk 2 _R, together with the rotatable with the rotation of the variator shaft 11, is supported movably on the variator shaft 11 along with the movement direction along the rotation axis X1 of the variator shaft 11 Yes. Still other words, the rear input disk 2 _R, to the variator shaft 11, with no relative rotational displacement about the rotation axis X1, is not relatively displaced in the direction along the rotation axis X1. In the following description, when it is not necessary to distinguish the front side input disc 2 _F and the rear-side input disk 2 _R, abbreviated as "input disk 2".

  Each input disk 2 is formed with an opening at the center and gradually protruding from the outside toward the center. The slope of the protruding portion of each input disk 2 is formed so that the cross section along the direction of the rotation axis X1 is substantially arc-shaped, and forms a toroidal surface 2a of each input disk 2. The two input disks 2 are provided such that the toroidal surfaces 2a face each other.

The output disks 3 transmit (output) the driving force transmitted (input) to each input disk 2 to the drive wheel 27 side, and two output disks 3 are provided, one for each input disk 2. . The toroidal type continuously variable transmission 1, with respect to the variator shaft 11, the front side output disc 3 _F is provided on the front side (engine 21 side), a rear side output disc 3 to the rear side (driving wheel 27 side) _R Is provided. A front output disk 3 _F and the rear-side output disc 3 _R is provided between the front input disc 2 _F and the rear-side input disk 2 _R with respect to the direction in which both along the rotation axis X1, More , rear output disk 3 _R is provided between the front side output disc 3 _F and the rear-side input disk 2 _R. That is, the toroidal continuously variable transmission 1 has a front side input disk 2 _F , a front side output disk 3 _F , a rear side output disk 3 _R , and a rear side input in the direction along the rotation axis X 1. It is provided in the order of the disc 2 _R. In the following description, the front side output disc 3 _F and the rear-side output disc 3 when there is no need to distinguish between _R, abbreviated as "the output disc 3 '.

Each input disk 2 and each output disk 3 are provided so as to be rotatable relative to the input shaft 10 coaxially with the rotation axis X1. Accordingly, each output disk 3 can rotate around the rotation axis X1. Each output disk 3 has substantially the same shape as each input disk 2, that is, each output disk 3 has an opening at the center and gradually protrudes from the outside toward the center. The slope of the protruding portion of each output disk 3 is formed such that the cross section along the direction of the rotation axis X1 is substantially arc-shaped, and forms a toroidal surface 3a of each output disk 3. Each output disk 3 is provided between the two input disks 2 in the direction along the rotation axis X1 as described above, and each toroidal surface 3a faces the toroidal surface 2a of each input disk 2. To be provided. That is, in the cross section along the rotation axis X1, one of the front input disk 2 _F toroidal surface 2a and the front output disk 3 _F toroidal surface 3a and front side facing in (engine 21 side) semicircular cavity forming a C _F, the other of the rear input disk 2 toroidal surfaces 2a and the rear-side output disc 3 _R another rear toroidal surface 3a is opposite of the _R (driving wheel 27 side) semicircular cavity C _R Forming.

  Each output disk 3 is rotatably supported by the variator shaft 11 via a bearing. An output gear 12 is connected between the two output disks 3, and the output gear 12 can rotate together with the two output disks 3. A counter gear 13 is engaged with the output gear 12, and an output shaft 14 is connected to the counter gear 13. Therefore, the output shaft 14 rotates as each output disk 3 rotates. The output shaft 14 is connected to the drive wheel 27 via a power transmission mechanism 24, a differential gear 25, and the like, and the driving force is transmitted to the drive wheel 27 via the power transmission mechanism 24, the differential gear 25, and the like. (Output).

  The power transmission mechanism 24 transmits driving force between the toroidal-type continuously variable transmission 1 and the differential gear 25. The power transmission mechanism 24 is disposed between the output disk 3 and the differential gear 25. The differential gear 25 transmits driving force between the power transmission mechanism 24 and the driving wheel 27. The differential gear 25 is disposed between the power transmission mechanism 24 and the drive wheel 27. A drive shaft 26 is coupled to the differential gear 25. Drive wheels 27 are attached to the drive shaft 26.

  The power roller 4 is provided between the input disk 2 and the output disk 3 in contact with the input disk 2 and the output disk 3, and transmits the driving force from the input disk 2 to the output disk 3. That is, the power roller 4 is formed as a curved contact surface 4a whose outer peripheral surface corresponds to the toroidal surfaces 2a and 3a. The power roller 4 is sandwiched between the input disk 2 and the output disk 3, and the contact surface 4a can contact the toroidal surfaces 2a and 3a. Each power roller 4 is contacted by a trunnion 6 described later. While the surface 4a is in contact with the toroidal surfaces 2a and 3a, the surface 4a is supported rotatably about the rotation axis X2. The power roller 4 is configured to shear an oil film formed between the toroidal surfaces 2a and 3a of the input disk 2 and the output disk 3 and the contact surface 4a of the power roller 4 by traction oil supplied to the toroidal continuously variable transmission 1. The driving force (torque) is transmitted using force.

A total of four power rollers 4 are provided, two for each of the cavities formed by the pair of input disks 2 and output disks 3. That is, the toroidal type continuously variable transmission 1 comprises two power rollers 4 to the front side semicircular cavity C _F is provided with a pair, two power rollers 4 against the rear semicircular cavity C _R pair Provided.

  More specifically, the power roller 4 includes a power roller main body 41 and an outer ring 42. The power roller main body 41 has the above-described contact surface 4a in contact with the toroidal surfaces 2a and 3a of the input disk 2 and output disk 3 on the outer peripheral surface. The power roller main body 41 is rotatably supported via a radial bearing RB with respect to a rotation shaft 42a formed on the outer ring 42. Further, the power roller main body 41 is rotatably supported on the surface of the outer ring 42 facing the power roller main body 41 via a thrust bearing SB. Therefore, the power roller main body 41 can rotate around the rotation axis X2 of the rotation shaft 42a.

  The outer ring 42 is formed with an eccentric shaft 42b together with the rotating shaft 42a. The eccentric shaft 42b is formed such that the rotation axis X2 'is shifted from the rotation axis X2 of the rotation shaft 42a. The eccentric shaft 42b is rotatably supported via a radial bearing RB with respect to a fitting portion 6d formed as a recess in a roller support portion 6a of the trunnion 6 described later. Accordingly, the outer ring 42 can rotate around the rotation axis X2 'of the eccentric shaft 42b. That is, the power roller 4 can rotate with respect to the trunnion 6 about the rotation axis X2 and the rotation axis X2 ′, that is, can revolve around the rotation axis X2 ′ and can rotate about the rotation axis X2. Become. As a result, the power roller 4 is configured to be movable in the direction along the rotation axis X1, and for example, it is possible to allow component deformation and variations in component accuracy.

  Here, the input shaft 10 is connected to a hydraulic pressure (end load) mechanism 15 as a clamping means. The hydraulic pressing mechanism 15 brings the input disk 2 and output disk 3 into contact with the power roller 4 and applies a clamping pressure for sandwiching the power roller 4 between the input disk 2 and the output disk 3. The hydraulic pressing mechanism 15 includes a clamping pressure generating hydraulic chamber 15a and a clamping pressure piston 15b. The hydraulic pressure pressing mechanism 15 is configured such that the pressure of the hydraulic oil as the working medium supplied to the clamping pressure generating hydraulic chamber 15a, that is, the front input disk clamping as the pressure acting surface that rotates the hydraulic pressure as the input disk 2 rotates. By acting on the pressing pressure acting surface 28 and the rear side input disk clamping pressure acting surface 29, a clamping pressure for sandwiching the power roller 4 between the input disk 2 and the output disk 3 can be applied.

Specifically, the clamping pressure generating hydraulic chamber 15a is provided on one side in the direction along the rotation axis X1 with respect to the two input disks 2. Here, squeezing force generating hydraulic chamber 15a is provided on the front side input disc 2 _F side against along the rotation axis X1 direction, it is disposed between the input shaft 10 and the front input disk 2 _F. The hydraulic pressure chamber 15a is supplied with hydraulic oil from the hydraulic control device 9 in accordance with the operating state.

The clamping pressure piston 15b is formed in a disc shape and is provided at one end of the variator shaft 11 so that the center thereof substantially coincides with the rotation axis X1. Nipping and pressing force piston 15b is the end rear input disk 2 _R of the variator shaft 11 is provided opposite end, that is, on the front side (engine 21 side). Nipping and pressing force piston 15b, to the direction along the rotation axis X1, it is spaced front input disk 2 _F and distance between the input shaft 10 and the front input disk 2 _F. Clamping force generating hydraulic chamber 15a of the above is provided between the nipping and pressing force piston 15b and the front input disk 2 _F.

The clamping pressure piston 15b is rotatable with respect to the variator shaft 11 around the rotation axis X1 together with the variator shaft 11 and is movable in the direction along the rotation axis X1. That is, the clamping pressure piston 15b can be rotated with the rotation of the variator shaft 11, and is supported by the variator shaft 11 so as to be movable with the movement of the variator shaft 11 along the rotation axis X1. Yes. In other words, the clamping pressure piston 15b is not relatively displaced relative to the variator shaft 11 around the rotational axis X1 and is not relatively displaced in the direction along the rotational axis X1. Therefore, the rear side input disk 2 _R , the variator shaft 11 and the clamping pressure piston 15 b can rotate together around the rotation axis X 1 and can move in the direction along the rotation axis X 1. The front-side input disk 2 _F is rear input disc 2 _R, together with the variator shaft 11 and the nipping and pressing force piston 15b while being rotatable about a rotation axis X1 together, by a ball spline 11a, The rear side input disk 2 _R , the variator shaft 11, and the pressing pressure piston 15 b are relatively movable in the direction along the rotation axis X 1.

Further, the clamping pressure piston 15b is also connected to the input shaft 10, can be rotated around the rotation axis X1 together with the input shaft 10, and relatively moves in the direction along the rotation axis X1. Provided possible. That is, the rear side input disk 2 _R , the variator shaft 11, and the pressing pressure piston 15 b are integrated with the input shaft 10 and can rotate about the rotation axis X 1, while rotating with respect to the input shaft 10. It is relatively movable in the direction along the axis X1. The driving force from the input shaft 10 is transmitted to the variator shaft 11, and is transmitted from the variator shaft 11 to the front side input disk 2 _F and the rear side input disk 2 _R.

The front-side input disk 2 _F, while having a front input disk nipping and pressing force acting surface 28 above, nipping and pressing force piston 15b has a rear input disk nipping and pressing force acting surface 29 of the above . Front input disk nipping and pressing force acting surface 28 at the front side input disc 2 _F, provided on the back of the toroidal surface 2a which is a contact surface between the power roller 4. The rear side input disk clamping pressure operating surface 29 is provided on the surface facing the front side input disk clamping pressure operating surface 28 in the direction along the rotation axis X1 at the clamping pressure piston 15b. The rear side input disk clamping pressure operating surface 29 is provided to face the front side input disk clamping pressure operating surface 28 with the above-described clamping pressure generating hydraulic chamber 15a interposed therebetween. Clamping force generating hydraulic chamber 15a, depending the front input disk nipping and pressing force acting surface 28 and the rear-side input disk nipping and pressing force acting surface 29 between the nipping and pressing force piston 15b and the front input disk 2 _F It is partitioned with respect to the direction along the rotation axis X1. That is, the front-side input disk clamping pressure application surface 28 and the rear-side input disk clamping pressure application surface 29 are arranged such that the front-side input disk clamping pressure application surface 28 enters the clamping pressure generating hydraulic chamber 15a on the rear side. The rear-side input disk clamping pressure operating surface 29 faces the clamping pressure generating hydraulic chamber 15a on the front side.

Therefore, the hydraulic pressing mechanism 15 clamps the front side input disk clamping pressure application surface 28 and the rear side input disk clamping pressure application surface 29 by the hydraulic pressure of the hydraulic oil supplied into the clamping pressure generation hydraulic chamber 15a. by exerting a pressure force to move the front input disk 2 _F from the hydraulic pressing mechanism 15 side in a direction away to the rear side, the hydraulic pressing mechanism 15 side from the rear side of rear input disc 2 _R together with the variator shaft 11 Move in the direction approaching. At this time, the front-side input disk 2 _F moves relative to the variator shaft 11 in the direction along the rotation axis X1. The hydraulic pressing mechanism 15, the front-side input disk 2 _F is moved from the hydraulic pressing mechanism 15 side to the rear side, by moving the rear input disk 2 _R direction toward the front side along with the variator shaft 11, The front side input disc 2 _F is brought closer to the front side output disc 3 _F side, and the rear side input disc 2 _R is brought closer to the rear side output disc 3 _R side, and the front side input disc 2 _F and the front side output disc 3 _F are generating a clamping force between and between the rear input disk 2 _R and the rear side output disc 3 _R a. Thus, the hydraulic pressing mechanism 15, since to generate a clamping pressure between and between the rear input disk 2 _R and the rear side output disc 3 _R between the front input disc 2 _F and the front output disk 3 _F , between the front-side input disk 2 _F and the front output disk 3 _F at a predetermined clamping pressure power rollers 4, respectively, can be sandwiched between the rear-side input disk 2 _R and the rear side output disc 3 _R . As a result, it is possible to prevent slipping between the input disk 2, the output disk 3 and the power roller 4 and maintain an appropriate traction state.

  Here, the clamping pressure by the hydraulic pressing mechanism 15, in other words, the clamping pressure, is controlled by the hydraulic control device 9 described later by controlling the amount of hydraulic oil supplied to the clamping pressure generating hydraulic chamber 15 a, so It is controlled to a predetermined magnitude based on the input torque to the step transmission 1. The hydraulic control device 9 is connected to an ECU 60 described later. Therefore, the ECU 60 controls the magnitude of the pressing pressure by the hydraulic pressing mechanism 15.

  As described above, the gear ratio changing unit 5 includes the trunnion 6 and the moving unit 7. The moving unit 7 moves the power roller 4 together with the trunnion 6 with respect to the rotation axis X 1 of the input disk 2 and the output disk 3. The gear ratio is changed by moving and tilting the power roller 4 with respect to the input disk 2 and the output disk 3. Here, the transmission gear ratio is the rotation speed ratio between the input disk 2 and the output disk 3, and typically represented by [transmission ratio = output-side contact radius (contact radius where the power roller 4 and the output disk 3 are in contact with each other). (Distance between the contact point and the rotation axis X1) / input side contact radius (contact radius where the input disk 2 and the power roller 4 are in contact)].

  Specifically, each trunnion 6 rotatably supports the power roller 4 and moves the power roller 4 with respect to the input disk 2 and the output disk 3 to tilt with respect to the input disk 2 and the output disk 3. It supports to roll freely. The trunnion 6 has a roller support portion 6a and a swing shaft 6b. The roller support portion 6a has a space portion 6c in which the power roller 4 is disposed, and a recessed fitting portion 6d is formed in the space portion 6c. The trunnion 6 rotatably supports the power roller 4 by inserting the eccentric shaft 42b of the power roller 4 into the fitting portion 6d as described above in the space 6c. Further, the roller support portion 6a is provided so as to be movable integrally with the swing shaft 6b. The oscillating shaft 6b is formed in a columnar shape so as to be rotatable about the rotation axis X3. Therefore, the trunnion 6 is supported by a casing (not shown) via the lower link 16 and the upper link 17 so that the roller support portion 6a can rotate around the rotation axis X3 together with the swing shaft 6b. The trunnion 6 is supported by a casing (not shown) via a lower link 16 and an upper link 17 so as to be movable in a direction along the rotation axis X3, and is moved along the rotation axis X3 by a moving unit 7 described later. It can be moved in any direction.

Four trunnions 6 are provided in total, two for each of the cavities formed by the pair of input disks 2 and output disks 3, and support four power rollers 4 one by one. That is, the toroidal type continuously variable transmission 1 comprises two trunnions 6 supporting each two power rollers 4 to the front side semicircular cavity C _F is provided with a pair, on the rear side semicircular cavity C _R On the other hand, two trunnions 6 that support the two power rollers 4 are provided as a pair.

  Here, the trunnion 6 supports the power roller 4 so that the rotation axis X2 of the power roller 4 is parallel to a plane perpendicular to the rotation axis X3 of the swing shaft 6b. The trunnion 6 is arranged so that the rotation axis X3 of the swing shaft 6b is parallel to a plane perpendicular to the rotation axis X1 of the input disk 2 and the output disk 3. That is, the trunnion 6 moves along the rotation axis X3 in a plane perpendicular to the rotation axis X1 so that the power roller 4 moves along the rotation axis X3 with respect to the rotation axis X1 of the input disk 2 and the output disk 3. Can be moved. Further, the trunnion 6 rotates and swings about the rotation axis X3, so that the power roller 4 can be moved with respect to the input disk 2 and the output disk 3 about the rotation axis X3 in a plane perpendicular to the rotation axis X3. It can be tilted freely. In other words, the trunnion 6 supports the power roller 4 so that the power roller 4 can be tilted when a tilting force described later acts on the power roller 4.

  The moving unit 7 moves the power roller 4 together with the trunnion 6 in the direction along the rotation axis X3, and includes the hydraulic piston unit 8 and the hydraulic control device 9 as described above.

  The hydraulic piston portion 8 includes a transmission control piston 81 and a transmission control hydraulic chamber 82, and receives the hydraulic pressure of the hydraulic oil introduced into the transmission control hydraulic chamber 82 by the flange portion 84 of the transmission control piston 81. Thus, the trunnion 6 is moved in two directions (A1 direction and A2 direction) along the rotation axis X3. That is, the hydraulic piston portion 8 applies a shift control pressing force to the flange portion 84 provided in the trunnion 6 by the hydraulic pressure of the hydraulic oil supplied to the shift control hydraulic chamber 82.

  Specifically, the transmission control piston 81 includes a piston base 83 and a flange portion 84. The piston base 83 is formed in a cylindrical shape, is inserted into one end of the swing shaft 6b, and is fixed with respect to the direction of the rotational axis X3 and the direction around the rotational axis X3.

  The flange portion 84 is fixedly provided so as to protrude from the piston base 83 in the radial direction of the piston base 83, in other words, in the radial direction of the swing shaft 6b, and the swing shaft 6b of the piston base 83 and the trunnion 6 is provided. At the same time, it can move in the direction along the rotation axis X3. The flange portion 84 is formed in an annular plate shape around the rotation axis X3 of the swing shaft 6b.

  The shift control hydraulic chamber 82 is configured by a hydraulic chamber constituent member 85. The hydraulic chamber constituent member 85 includes a cylinder body 86 as a first constituent member and a lower cover 87 as a second constituent member. That is, the hydraulic chamber constituting member 85 forms the wall surface of the transmission control hydraulic chamber 82 and is divided into the cylinder body 86 and the lower cover 87 with respect to the direction along the rotation axis X3 that is the movement direction (stroke direction) of the trunnion 6. Has been. The cylinder body 86 is formed with a recess that becomes a space portion of the transmission control hydraulic chamber 82. The lower cover 87 is fixed to the cylinder body 86 so as to close the opening of the concave portion of the cylinder body 86, whereby the transmission control hydraulic chamber 82 is formed in a cylindrical shape centered on the rotation axis X3 by the cylinder body 86 and the lower cover 87. Comparted into a cylinder. The cylinder body 86 and the lower cover 87 are fixed to a casing (not shown) on the opposite side of the cylinder body 86 from the lower cover 87 side.

  The flange portion 84 is accommodated in the transmission control hydraulic chamber 82 into which hydraulic oil is introduced, and two hydraulic chambers, that is, the first hydraulic chambers in the direction along the rotation axis X3 in the transmission control hydraulic chamber 82 are provided. The partition is divided into a hydraulic chamber OP1 and a second hydraulic chamber OP2. The first hydraulic chamber OP1 moves the trunnion 6 together with the flange portion 84 in the first direction A1 along the rotation axis X3 by the hydraulic pressure of the hydraulic oil supplied to the inside, while the second hydraulic chamber OP2 is supplied to the inside. The trunnion 6 together with the flange 84 is moved in the second direction A2, which is the reverse direction of the first direction, by the hydraulic pressure of the hydraulic oil. An annular seal member S is provided at the distal end portion on the radially outer side of the flange portion 84. Therefore, the first hydraulic chamber OP1 and the second hydraulic chamber of the shift control hydraulic chamber 82 defined by the flange portion 84. The OP2 is sealed by the seal member S so that the hydraulic oil does not leak from each other.

  Since each of the pair of input disks 2 and output disks 3 is provided with two power rollers 4 and trunnions 6, the first hydraulic chamber OP1 and the second hydraulic chamber OP2 have a pair of input disks 2 and output disks. Two for every three will be provided. At this time, in the pair of trunnions 6, the positional relationship between the first hydraulic chamber OP1 and the second hydraulic chamber OP2 is switched for each trunnion 6. That is, the hydraulic chamber that is the first hydraulic chamber OP1 of one trunnion 6 is the second hydraulic chamber OP2 of the other trunnion 6, and the hydraulic chamber that is the second hydraulic chamber OP2 of one trunnion 6 is the second hydraulic chamber OP2 of the other trunnion 6. 1 hydraulic chamber OP1. Therefore, in the toroidal continuously variable transmission 1 shown in FIG. 2, the two power rollers 4 provided for each of the pair of input disks 2 and output disks 3 are driven by the hydraulic pressure in the first hydraulic chamber OP1 or the second hydraulic chamber OP2. , And move in opposite directions along the rotation axis X3.

  The hydraulic control device 9 supplies hydraulic oil to each part of the transmission, for example, the hydraulic pressure pressing mechanism 15, the torque converter 22, the forward / reverse switching mechanism 23, and the hydraulic pressure of the hydraulic oil in the transmission control hydraulic chamber 82. Is to control. The hydraulic control device 9 includes an oil tank 91, an oil pump 92 as a pressurizing means, a first flow control valve 93 as a flow control valve, a second flow control valve 94, and a first passage as a hydraulic oil passage. 95, a second passage 96, a supply passage 97, a discharge passage 98, and a hydraulic oil supply passage 99.

  The oil tank 91 stores hydraulic oil supplied to each part of the transmission. The oil pump 92 operates, for example, in conjunction with rotation of the crankshaft 21a that is an output shaft of the engine, and sucks, pressurizes, and discharges the hydraulic oil stored in the oil tank 91. The pressurized hydraulic oil is supplied to the first flow control valve 93, the second flow control valve 94, another flow control valve, and the like via a pressure regulator valve (not shown). In addition, this pressure regulator valve removes the hydraulic oil on the downstream side when the hydraulic pressure on the downstream side of the pressure regulator valve exceeds a predetermined hydraulic pressure, that is, the line pressure used as the original pressure of the hydraulic control device 9. The pressure is returned to the oil tank 91 and adjusted to a predetermined line pressure.

  The first flow rate control valve 93 supplies hydraulic oil to the first hydraulic chamber OP1 and discharges hydraulic fluid from the second hydraulic chamber OP2, while the second flow rate control valve 94 is supplied to the second hydraulic chamber OP2. The hydraulic oil is supplied, and the hydraulic oil is discharged from the first hydraulic chamber OP1. The first flow rate control valve 93 includes an oil passage structure main body 93a, a spool valve element 93b, a hydraulic oil supply port 93c, a hydraulic oil discharge port 93d, a first hydraulic chamber communication port 93e, and a second hydraulic chamber communication. The port 93f, the first elastic member 93g, and the first solenoid 93h are included. On the other hand, the second flow rate control valve 94 includes an oil passage configuration main body portion 94a, a spool valve element 94b, a hydraulic oil supply port 94c, a hydraulic oil discharge port 94d, a second hydraulic chamber communication port 94e, and a first hydraulic pressure. The chamber communication port 94f, the second elastic member 94g, and the second solenoid 94h are configured. The first flow rate control valve 93 and the second flow rate control valve 94 are a first solenoid 93h and a second solenoid 94h as drive means that are driven by a drive current based on a control command value input from the ECU 60, respectively. By shifting the positions of the sub-units 93b and 94b, the hydraulic oil supply ports 93c and 94c, the hydraulic oil discharge ports 93d and 94d, the first hydraulic chamber communication ports 93e and 94f, and the second hydraulic chamber communication ports 93f and 94e flow out. It controls the flow rate of the hydraulic fluid that enters.

  Specifically, the oil passage configuration main body portions 93a and 94a constitute an oil passage, and each of the hydraulic oil supply ports 93c and 94c and the hydraulic oil discharge ports 93d and 94d communicate with the configured oil passage. First hydraulic chamber communication ports 93e and 94f and second hydraulic chamber communication ports 93f and 94e are formed. Spool valve elements 93b and 94b are inserted in the oil paths configured in the oil path configuration main body portions 93a and 94a, respectively. The spool valve elements 93b and 94b are for switching the communication state of each port.

  The hydraulic oil supply ports 93c and 94c are connected to an oil pump 92 through a supply passage 97, and hydraulic oil pressurized to the line pressure by the oil pump 92 is supplied to the hydraulic oil supply ports 93c and 94c. The The hydraulic oil discharge ports 93 d and 94 d are connected to the oil tank 91 via the discharge passage 98. The first hydraulic chamber communication port 93e of the first flow rate control valve 93 is connected to the first hydraulic chamber OP1 via the first passage 95 and also connected to the first hydraulic chamber communication port 94f of the second flow rate control valve 94. Is done. The second hydraulic chamber communication port 93f of the first flow control valve 93 is connected to the second hydraulic chamber OP2 through the second passage 96, and the second hydraulic chamber communication port 94e of the second flow control valve 94. Connected.

  The first elastic member 93g and the second elastic member 94g are provided on one end side of the spool valve elements 93b and 94b, respectively, while the first solenoid 93h and the second solenoid 94h are respectively provided with the spool valve elements 93b and 94b. Is provided on the other end side. The first elastic member 93g and the second elastic member 94g apply a biasing force that moves the spool valve elements 93b and 94b toward the first solenoid 93h and the second solenoid 94h (OFF side), while the first solenoid 93h and the second elastic member 94g The 2 solenoid 94h resists the urging force by the electromagnetic force generated according to the supplied drive current, and causes the spool valve elements 93b and 94b to move toward the first elastic member 93g and the second elastic member 94g (ON side). The pressing force to move is applied.

  Further, the first solenoid 93h and the second solenoid 94h are electrically connected to the ECU 60 and are driven and controlled by the ECU 60. Accordingly, a pressing force according to the drive current supplied to the first solenoid 93h and the second solenoid 94h acts on the spool valve elements 93b and 94b.

  For example, the ECU 60 sets the drive current supplied to the first solenoid 93h to 0 A when the first flow control valve 93 is in the OFF state (OFF portion shown in FIG. 2). Accordingly, since the pressing force by the first solenoid 93h does not act on the spool valve element 93b, only the urging force by the first elastic member 93g acts, and the spool valve element 93b is positioned at the OFF position on the first solenoid 93h side. . At this time, the communication between the hydraulic oil supply port 93c and the first hydraulic chamber communication port 93e is blocked, and the communication between the hydraulic oil discharge port 93d and the second hydraulic chamber communication port 93f is blocked. That is, when the first flow control valve 93 is OFF, the hydraulic oil pressurized by the oil pump 92 is not supplied to the first hydraulic chamber OP1, and the hydraulic oil in the second hydraulic chamber OP2 is not discharged.

  On the other hand, the ECU 60 supplies a drive current to the first solenoid 93h when the first flow control valve 93 is in the ON state (the ON portion shown in FIG. 2). At this time, the ECU 60 sets the drive current based on the gear ratio, the speed of the toroidal-type continuously variable transmission 1, and the like. Therefore, the pressing force by the first solenoid 93h and the urging force by the first elastic member 93g act on the spool valve element 93b. When the pressing force by the first solenoid 93h becomes larger than the urging force by the first elastic member 93g, the spool valve element 93b moves to the first elastic member 93g side, and an ON position other than the OFF position (the maximum ON position is shown in FIG. 2). ON part). At this time, the hydraulic oil supply port 93c and the first hydraulic chamber communication port 93e are communicated, and the hydraulic oil discharge port 93d and the second hydraulic chamber communication port 93f are communicated. That is, when the first flow control valve 93 is in the ON state, the hydraulic oil pressurized by the oil pump 92 is supplied to the first hydraulic chamber OP1, and the hydraulic oil in the second hydraulic chamber OP2 is discharged. As a result, the hydraulic pressure in the first hydraulic chamber OP1 acts on the flange portion 84 and [the hydraulic pressure in the first hydraulic chamber OP1> the hydraulic pressure in the second hydraulic chamber OP2], whereby the flange portion 84 of the hydraulic piston portion 8 is rotated. Pressed in the first direction A1 along X3, the power roller 4 moves along with the trunnion 6 in the first direction A1 along the rotation axis X3. At this time, the movement of the power roller 4 in the first direction A1 is adjusted according to the amount of movement of the spool valve element 93b toward the ON side.

  Similarly, in the OFF state of the second flow control valve 94 (OFF portion shown in FIG. 2), the ECU 60 sets the drive current supplied to the second solenoid 94h to 0A. At this time, the communication between the hydraulic oil supply port 94c and the second hydraulic chamber communication port 94e is blocked, and the communication between the hydraulic oil discharge port 94d and the first hydraulic chamber communication port 94f is blocked and pressurized by the oil pump 92. The hydraulic oil is not supplied to the second hydraulic chamber OP2, and the hydraulic oil in the first hydraulic chamber OP1 is not discharged. In the ON state of the second flow rate control valve 94 (the ON portion shown in FIG. 2), the ECU 60 supplies a drive current to the second solenoid 94h. At this time, the hydraulic oil supply port 94c and the second hydraulic chamber communication port 94e communicate with each other, the hydraulic oil discharge port 94d and the first hydraulic chamber communication port 94f communicate with each other, and the hydraulic oil pressurized by the oil pump 92 is The hydraulic oil is supplied to the second hydraulic chamber OP2, and the hydraulic oil in the first hydraulic chamber OP1 is discharged. As a result, the hydraulic pressure in the second hydraulic chamber OP2 acts on the flange portion 84 to be [the hydraulic pressure in the first hydraulic chamber OP1 <the hydraulic pressure in the second hydraulic chamber OP2], whereby the flange portion 84 of the hydraulic piston portion 8 is rotated. Pressed in the second direction A2 along X3, the power roller 4 moves along with the trunnion 6 in the second direction A2 along the rotation axis X3.

  Accordingly, the moving unit 7 is driven by the ECU 60 by the hydraulic control device 9 to control the hydraulic pressure in each of the shift control hydraulic chambers 82 of the hydraulic piston unit 8 so that the flange unit 84 of the shift control piston 81 has a predetermined shift. By applying a control pressing force, the power roller 4 together with the trunnion 6 can be moved in two directions along the rotation axis X3, that is, in the first direction A1 and the second direction A2. Then, the gear ratio changing unit 5 causes the moving unit 7 to move the power roller 4 together with the trunnion 6 from a neutral position (see FIG. 3) relative to the input disk 2 and the output disk 3 to a gear position corresponding to the gear ratio (see FIG. 4). The gear ratio can be changed by tilting the power roller 4 with respect to the input disk 2 and the output disk 3.

  The hydraulic oil supply passage 99 is downstream of the oil pump 92 in the supply passage 97, upstream of the first flow rate control valve 93 and second flow rate control valve 94, the hydraulic pressing mechanism 15, the torque converter 22, the forward / reverse switching mechanism 23, and the like. And hydraulic oil pressurized to the line pressure by the oil pump 92 is supplied to the hydraulic pressing mechanism 15, the torque converter 22, the forward / reverse switching mechanism 23, and the like.

  Here, as shown in FIG. 3, the neutral position of the power roller 4 with respect to the input disk 2 and the output disk 3 is a position where the gear ratio is fixed, and the power roller 4 is positioned with respect to the input disk 2 and the output disk 3. In this position, the tilting force to be tilted cannot act on the power roller 4. That is, when the power roller 4 is in the neutral position and the transmission gear ratio is fixed, the rotation axis X2 of the power roller 4 is set in a plane that includes the rotation axis X1 and that is perpendicular to the rotation axis X3. Is done. In other words, at the neutral position of the power roller 4 (when the transmission ratio is fixed), the position of the power roller 4 in the direction along the rotational axis X3 is such that the rotational axis X2 of the power roller 4 passes through the rotational axis X1 (orthogonal). Set to position. At this time, the rotation direction (rolling direction) of the power roller 4 and the rotation direction of the input disk 2 coincide with each other at the contact point between the power roller 4 and the input disk 2. Therefore, the power roller 4 continues to rotate together with the input disk 2 while remaining in the neutral position, and the gear ratio during this period is fixed.

  At this time, since the force acting on the power roller 4 from the input disk 2 is only the driving force (torque), the hydraulic piston portion 8 of the moving portion 7 and the hydraulic control device 9 only resist this driving force by the hydraulic pressure. Is applied to the trunnion 6. That is, when the power roller 4 and the trunnion 6 that supports the power roller 4 are in the neutral position, as described above, the tangential force F1 acting on the contact point between the input disk 2 and the output disk 3 and the power roller 4 according to the input torque. By causing the shift control pressing force F2 (see FIG. 3) of a magnitude that resists (see FIG. 3) to act on the flange portion 84, the tangential force F1 acting on the power roller 4 and the shift control pressing force F2 are balanced. The positions of the power roller 4 and the trunnion 6 that supports the power roller 4 are fixed to the neutral position, and the gear ratio is fixed.

  On the other hand, as shown in FIG. 4, the speed change position of the power roller 4 is a position where the speed ratio is changed, and the tilting force that tilts the power roller 4 with respect to the input disk 2 and the output disk 3 is this power. It is a position that acts on the roller 4. That is, when the power roller 4 is in the speed change position and the speed ratio is changed, the rotation axis X2 of the power roller 4 is a plane including the rotation axis X1 and the rotation axis from the plane perpendicular to the rotation axis X3. It is set at a position moved in the first direction A1 or the second direction A2 along X3. In other words, at the speed change position of the power roller 4 (at the time of speed change), the position of the power roller 4 in the direction along the rotation axis X3 is the position where the rotation axis X2 of the power roller 4 passes the rotation axis X1, that is, the neutral position. Is set to a position offset from. At this time, at the contact point between the power roller 4 and the input disk 2, the rotation direction of the power roller 4 is shifted from the rotation direction of the input disk 2, whereby a tilting force acts on the power roller 4. As a result, a side slip occurs between the power roller 4 and the input disk 2 and the output disk 3 due to the tilting force acting on the power roller 4, and the power roller 4 tilts with respect to the input disk 2 and the output disk 3. In turn, the input side contact radius between the power roller 4 and the input disk 2 and the output side contact radius between the power roller 4 and the output disk 3 are changed, so that the gear ratio is changed.

  For example, as shown in FIG. 4, when the input disk 2 is rotating in the direction of arrow B (counterclockwise) in FIG. 4, the power roller 4 is moved in the second direction A2 along the rotation axis X3 (power The roller 4 and the input disk 2 are offset in the direction opposite to the moving direction of the input disk 2 at the contact point, that is, the direction opposite to the rotation direction of the input disk 2 (the direction along the rotation direction of the output disk 3). Then, the force in the circumferential direction of the input disk 2 acts on the power roller 4 at the contact point between the power roller 4 and the input disk 2, and the power roller 4 is moved to the peripheral side of the input disk 2 (power roller 4 Tilting force acts in the direction of separating the input disk 2 from the rotation axis X1. As a result, the power roller 4 moves so that the contact point with the input disk 2 moves radially outward of the input disk 2 and the contact point with the output disk 3 moves radially inward of the output disk 3. The gear ratio is changed to the decreasing side and upshifted. Then, the changed gear ratio is fixed by returning the power roller 4 to the neutral position again.

  Conversely, when downshifting, the power roller 4 is moved in the first direction A1 along the rotation axis X3 (the moving direction of the input disk 2 at the contact point between the power roller 4 and the input disk 2, that is, the rotation of the input disk 2). In the direction along the direction (the direction opposite to the rotation direction of the output disk 3)). Then, the force in the circumferential direction of the input disk 2 acts on the power roller 4 at the contact point between the power roller 4 and the input disk 2, and the power roller 4 moves to the center side of the input disk 2 (power roller 4 Is applied to the rotation axis X1 of the input disk 2). As a result, the power roller 4 moves so that the contact point with the input disk 2 moves radially inward of the input disk 2 and the contact point with the output disk 3 moves radially outward of the output disk 3. The gear ratio is changed to the increasing side and downshifted. Then, the changed gear ratio is fixed by returning the power roller 4 to the neutral position again.

  Here, the position of the power roller 4 is determined by the stroke amount and the tilt angle with respect to the input disk 2 and the output disk 3. The stroke amount of the power roller 4 is set from the neutral position to the first direction A1 or the second direction A2 with a neutral position where the rotation axis X2 of the power roller 4 passes through the rotation axis X1 of the input disk 2 and the output disk 3 as a reference position. This is an amount corresponding to the stroke amount as the amount of movement, more specifically, the stroke amount (offset amount) from the neutral position. The tilt angle of the power roller 4 is input from this reference position with the position where the rotation axis X2 which is the rotation center of the power roller 4 is orthogonal to the rotation axis X1 which is the rotation center of the input disk 2 and the output disk 3 as a reference position. The tilt angle (acute angle on the acute angle side) with respect to the disk 2 and the output disk 3, in other words, the rotation angle around the rotation axis X3. The transmission ratio of the toroidal continuously variable transmission 1 is determined by the tilt angle of the power roller 4 with respect to the input disk 2 and the output disk 3, and this tilt angle is determined by the stroke amount from the neutral position of the power roller 4 ( It is determined by the integral value of the offset amount.

  Here, the toroidal-type continuously variable transmission 1 is a mechanism for synchronizing movements in the reverse direction along the rotation axis X3 of the two power rollers 4 and the trunnion 6 provided for each of the pair of input disks 2 and output disks 3. As shown, a link mechanism including a lower link 16 and an upper link 17 is provided. The lower link 16 connects the pair of trunnions 6 via a radial bearing RB on one end side (between the cylinder body 86 and the roller support portion 6a) where the speed change control piston 81 is provided on the swing shaft 6b. On the other hand, the upper link 17 connects the pair of trunnions 6 via the radial bearing RB on the other end side of the swing shaft 6b. The lower link 16 and the upper link 17 are respectively supported by lower post and upper post support shafts 16a and 17a fixed to a casing (not shown). The support shafts 16a and 17a are extended in a direction parallel to the rotation axis X1, and the lower link 16 and the upper link 17 are configured to be swingable in a seesaw shape with the support shafts 16a and 17a as fulcrums. Yes. Therefore, the lower link 16 and the upper link 17 can synchronize the movement of the pair of trunnions 6 in the reverse direction along the rotation axis X3.

  In addition, the toroidal continuously variable transmission 1 includes a synchronization mechanism 18 as a mechanism for promoting the synchronization of rotation around the rotation axis X3 of the plurality of trunnions 6. The synchronization mechanism 18 includes a synchronization wire 19 and a plurality of fixed pulleys 20. The synchronization mechanism 18 is inverted so as to intersect once between the fixed pulley 20 fixed to the swing shaft 6b of each trunnion 6 and the fixed pulley 20 adjacent in the rotation axis X1 direction or the rotation axis X2 direction. By transmitting the rotational torque of one trunnion 6 to the other trunnion 6 by the frictional force with the tensioned synchronous wire 19, the rotation synchronization about the rotation axis X3 of the plurality of trunnions 6 is promoted. be able to.

  As a result, in the tilting operation (transmission operation) of each power roller 4 and each trunnion 6, due to variations in the member accuracy and assembly accuracy of the trunnion 6 that is the support structure of the plurality of power rollers 4, the plurality of power rollers 4 Even when the clamping pressure of the hydraulic pressure pressing mechanism 15 does not act evenly or even when a slight shift is likely to occur in the shift response due to the difference in the oil path resistance of the hydraulic control device 9, the synchronizing mechanism 18 Since the rotations of the plurality of trunnions 6 are linked and synchronized with each other and the tilting operations of the plurality of power rollers 4 can be synchronized with each other, the shift control accuracy of the toroidal continuously variable transmission 1 can be improved.

  The ECU 60 controls the driving of the toroidal-type continuously variable transmission 1, and in particular controls the speed ratio γ. Here, various input signals inputted from sensors attached to various places of the vehicle on which the engine 21 is mounted. Based on the map and various maps, operation control of the engine 21, for example, injection control of a fuel injection valve (not shown), throttle opening control of a throttle valve (not shown) for controlling the intake air amount of the engine 21, ignition control of an ignition plug, etc. Is. Then, the ECU 60 controls the driving of each part of the toroidal continuously variable transmission 1 according to the operating state of the toroidal continuously variable transmission 1 to obtain the actual gear ratio that is the actual gear ratio of the toroidal continuously variable transmission 1. Control. That is, the ECU 60 detects, for example, engine speed, throttle opening, accelerator opening, engine speed, input speed, output speed, shift position, and other operating states, tilt angles, and stroke amounts detected by various sensors. The target speed ratio, which is the target speed ratio, is determined and the speed ratio changing unit 5 is driven to move the power roller 4 from the neutral position to the speed position side to a predetermined stroke amount. The gear ratio is changed by tilting to the turning angle. Furthermore, the ECU 60 performs duty control on the drive current supplied to the first solenoid 93h and the second solenoid 94h based on the control command value, thereby turning on / off the first flow control valve 93 or the second flow control valve 94. The OFF state is controlled, thereby controlling the hydraulic pressures of the first hydraulic chamber OP1 and the second hydraulic chamber OP2 of the hydraulic piston unit 8, and the power roller 4 together with the trunnion 6 from the neutral position to the shift position side by a predetermined stroke amount. The actual speed ratio is controlled so as to become the target speed ratio by moving to a predetermined tilt angle.

  Specifically, as shown in FIG. 2, as described above, the ECU 60 is electrically connected to the first solenoid 93h and the second solenoid 94h, and duty-controls the first solenoid 93h and the second solenoid 94h. is doing. Further, the ECU 60 is electrically connected to the tilt angle sensor 50 and the stroke sensor 51. The ECU 60 further includes an engine speed sensor 52, an input speed sensor 53 and an output speed sensor 54, an accelerator opening sensor 55, a vehicle speed sensor 56, a throttle opening sensor 57, and a shift position sensor 58. Various sensors such as the line pressure sensor 59 are electrically connected.

  The tilt angle sensor 50 detects a tilt angle of the power roller 4 with respect to the input disk 2 and the output disk 3 and transmits the detected tilt angle to the ECU 60. Here, the tilt angle detected by the tilt angle sensor 50 is detected as a rotation angle around the rotation axis X3 of the trunnion 6 rotating around the rotation axis X3 together with the power roller 4. The stroke sensor 51 detects the stroke amount of the power roller 4 and transmits the detected stroke amount to the ECU 60. Here, the stroke amount of the power roller 4 detected by the stroke sensor 51 is detected as the stroke amount of the trunnion 6 that moves together with the power roller 4 in the direction along the rotation axis X3.

  The engine speed sensor 52 detects the engine speed as the rotational speed of the engine 21 that is a drive source, and transmits the detected engine speed to the ECU 60. Here, for example, a crank angle sensor that detects the crank angle of the engine can be used as the engine speed sensor 52, and the ECU 60 performs an intake stroke, a compression stroke, and an expansion stroke in each cylinder based on the detected crank angle. The exhaust stroke is determined, and the engine speed (rpm) is calculated as the engine speed. Here, in other words, the engine speed corresponds to the rotational speed of the crankshaft 21a. If the rotational speed of the crankshaft 21a increases, the rotational speed of the crankshaft 21a and the engine rotational speed also increase. Hereinafter, unless otherwise specified, the rotation speed will be described as the number of rotations.

  For example, a Hall element rotation sensor with a forward / reverse determination function can be used as the input rotation speed sensor 53, and the input rotation speed and rotation direction that are the rotation speed of the input disk 2 are detected, and the detected input rotation speed and rotation direction are detected. Is transmitted to the ECU 60. For example, a Hall element rotation sensor with a forward / reverse determination function can be used as the output rotation speed sensor 54, and the output rotation speed and rotation direction, which are the rotation speeds of the output disk 3, are detected, and the detected output rotation speed and rotation direction are detected. Is transmitted to the ECU 60. The input rotation speed sensor 53 and the output rotation speed sensor 54 are based on the rotation speeds of members that rotate at a rotation speed (rotation speed) proportional to the rotation speed (rotation speed) of the input disk 2 and output disk 3, respectively. It may be detected. Further, the input rotation speed and the output rotation speed correspond to the rotation speeds of the input disk 2 and the output disk 3 in other words.

  The accelerator opening sensor 55 detects the accelerator opening of a vehicle on which the toroidal continuously variable transmission 1 is mounted, and transmits the detected accelerator opening to the ECU 60. The vehicle speed sensor 56 detects the vehicle speed of the vehicle on which the toroidal continuously variable transmission 1 is mounted, and transmits the detected vehicle speed to the ECU 60. The throttle opening sensor 57 detects the throttle opening of the vehicle in which the toroidal continuously variable transmission 1 is mounted, and transmits the detected throttle opening to the ECU 60.

  The shift position sensor 58 detects a shift position (for example, a parking position, a reverse position, a neutral position, a drive position, etc.) of a shift position device (not shown) provided in the vehicle on which the toroidal continuously variable transmission 1 is mounted. The detected shift position is transmitted to the ECU 60. The line pressure sensor 59 detects the line pressure used as the original pressure of the hydraulic control device 9 and transmits the detected line pressure to the ECU 60.

  When the driving force (torque) is input to the input disk 2, the toroidal continuously variable transmission 1 as described above transmits the driving force to the power roller 4 that is in contact with the input disk 2 via traction oil. Further, the driving force is transmitted from the power roller 4 to the output disk 3 via traction oil. During this time, the traction oil is changed to glass by being pressurized, and the driving force is transmitted by the accompanying large shearing force, so that each of the input disks 2 and output disks 3 has a clamping force corresponding to the input torque with the power roller 4. It is pressed by the hydraulic pressing mechanism 15 so as to occur between the two. Further, the peripheral speed of the power roller 4 and the peripheral speed at the torque transmission point of each input disk 2 and output disk 3 (contact point where the power roller 4 is in contact via the traction oil) are substantially the same. Depending on the radius from the rotation axis X1 of the contact point between the input disk 2 and the power roller 4 and the radius from the rotation axis X1 of the contact point between the power roller 4 and the output disk 3, each input disk 2, output The rotational speed (rotational speed) of the disk 3 is different, and the ratio of the rotational speed (rotational speed) becomes the transmission ratio.

  Then, when changing the gear ratio to the set target gear ratio, that is, in the case of gear ratio shifting, the ECU 60 determines whether the first solenoid 93h or the first solenoid 93h or the first solenoid 93h is based on the rotational direction of the input disk 2 (or output disk 3). 2 The drive current is supplied to the solenoid 94h and the first flow rate control valve 93 or the second flow rate control valve 94 is turned on, so that the trunnion 6 is maintained until the power roller 4 has an inclination angle corresponding to the target gear ratio. Are moved from the neutral position in the first direction A1 or the second direction A2. For example, in a state where the input disk 2 is rotating in the direction of arrow B (counterclockwise) in FIG. 2, the first flow control valve 93 is turned on, the second flow control valve 94 is turned off, and the first hydraulic pressure is set. When the power roller 4 is moved from the neutral position in the first direction A1 along the rotation axis X3 by the hydraulic pressure in the chamber OP1, the gear ratio is increased and the downshift is performed as described above. On the other hand, in a state where the input disk 2 is rotating in the direction of arrow B (counterclockwise) in FIG. 2, the first flow control valve 93 is turned off and the second flow control valve 94 is turned on, so that the second hydraulic pressure When the power roller 4 is moved from the neutral position in the second direction A2 along the rotation axis X3 by the hydraulic pressure in the chamber OP2, as described above, the speed ratio is reduced and an upshift is performed. When the set transmission gear ratio is fixed, the drive current is supplied to the first solenoid 93h or the second solenoid 94h, and the first flow rate control valve 93 or the second flow rate control valve 94 is turned on. The trunnion 6 is moved in the first direction A1 or the second direction A2 until the roller 4 reaches the neutral position.

  The ECU 60 determines that the actual speed ratio (actual speed ratio) is the target speed ratio (actual speed ratio) based on the tilt angle of the power roller 4 detected by the tilt angle sensor 50 and the stroke amount detected by the stroke sensor 51. Cascade feedback control is performed so that the target gear ratio after shifting). That is, the ECU 60 determines a target tilt angle that is a target tilt angle corresponding to the target gear ratio based on the accelerator opening and the vehicle speed, and detects the target tilt angle and the actual detected by the tilt angle sensor 50. Based on the deviation from the actual tilt angle that is the tilt angle, the target speed ratio, the target stroke amount that is the target stroke amount corresponding to the target tilt angle is determined, and the stroke amount detected by the stroke sensor 51 is determined. The first flow rate control valve 93 and the second flow rate control valve 94 of the moving unit 7 are controlled so as to achieve this target stroke amount.

  That is, the ECU 60 determines a target gear ratio, which is a target gear ratio, from the accelerator opening detected by the accelerator opening sensor 55 and the vehicle speed detected by the vehicle speed sensor 56. Here, for example, the required driving force is calculated based on the required driving amount represented by the accelerator opening degree and the vehicle speed, and the target output is obtained from the required driving force and the vehicle speed, and the target output is reduced to the minimum fuel consumption. And the target speed ratio is set so that the input rotational speed to the toroidal continuously variable transmission 1 becomes a target rotational speed corresponding to the rotational speed of the engine, that is, the target input rotational speed. Desired. If the contact point between the power roller 4 and the input disk 2 and the output disk 3 is known, the relationship between the gear ratio and the tilt angle is determined only by the geometric shape, so that the target tilt angle is obtained from the target gear ratio. Can do.

  In such shift control of the toroidal-type continuously variable transmission 1, basically, only the tilt angle (in other words, the gear ratio) detected by the tilt angle sensor 50 needs to be feedback-controlled, but the stroke amount Since this corresponds to the derivative of the tilt angle, the damping effect for suppressing the vibration in the tilt control can be obtained by performing the feedback control of the stroke amount detected by the stroke sensor 51 together. Further, the ECU 60 may perform feed-forward control together with this feedback control in order to improve the response of the gear ratio.

  By the way, in the toroidal type continuously variable transmission 1 as described above, for example, it is very difficult to assemble a plurality of power rollers 4 between the input disk 2 and the output disk 3 with high accuracy. That is, it is required to have a high assembling accuracy when assembling in a state where the tilt angles of all the power rollers 4 are matched and synchronized. For this reason, the tilt angles of the plurality of power rollers 4 are different immediately after the assembly, so that they are completely synchronized. It may not have been done. In this case, the synchronization of the plurality of power rollers 4 is disturbed immediately after the assembly, and the tilt angles of the plurality of power rollers 4 are different. The tilt of the power roller 4 cannot be synchronized and power circulation occurs, and as a result, a large input torque may be required to rotate the input disk 2 at the start. This makes it difficult to start the toroidal continuously variable transmission 1 immediately after the power roller 4 is assembled, and it may be difficult to start the vehicle on which the toroidal continuously variable transmission 1 is mounted.

  Therefore, the toroidal-type continuously variable transmission 1 of the present embodiment executes the synchronous control in which the ECU 60 that is also used as the synchronous control device 100 reduces the clamping pressure by the hydraulic pressing mechanism 15 and synchronizes the plurality of power rollers 4. Thus, the tilting of the plurality of power rollers 4 is reliably synchronized. Note that the synchronous control of the present embodiment is performed by, for example, an operator at the first start after assembling the toroidal continuously variable transmission 1 or at a restart after disassembling, repairing, and assembling the toroidal continuously variable transmission 1. This control is executed in response to a predetermined input operation, and is different from the gear ratio control during normal operation. This synchronous control is performed when the input disk 2 and the output disk 3 do not start rotating even when idle torque is input, for example, when the driving wheel 27 is floated on a test stand or the like. This is the control to be executed.

  Specifically, as shown in FIG. 2, the ECU 60 that is also used as the synchronous control device 100 of the present embodiment includes a torque converter control unit 61, a forward / reverse switching control unit 62, a clamping pressure control unit 63, an engine It has a control unit 64, a gear ratio control unit 65, and a synchronization control unit 66 as control means.

  Here, the ECU 60 is configured around a microcomputer and includes a processing unit, a storage unit, and an input / output unit, which are connected to each other and can exchange signals with each other. The input / output unit includes a drive circuit (not shown) that drives each unit such as the toroidal continuously variable transmission 1 and the engine 21, the tilt angle sensor 50, the stroke sensor 51, the engine speed sensor 52, and the input speed sensor 53 described above. Various sensors such as an output speed sensor 54, an accelerator opening sensor 55, a vehicle speed sensor 56, a throttle opening sensor 57, a shift position sensor 58, and a line pressure sensor 59 are connected. Input / output signals to / from sensors. In addition, the storage unit stores a computer program for controlling each unit such as the toroidal continuously variable transmission 1 and the engine 21. This storage unit is a hard disk device, a magneto-optical disk device, a non-volatile memory such as a flash memory (a storage medium that can only be read such as a CD-ROM), or a volatile memory such as a RAM (Random Access Memory). The memory can be configured by a combination of these, or a combination thereof. The processing unit includes a memory (not shown) and a CPU (Central Processing Unit). The above-described torque converter control unit 61, forward / reverse switching control unit 62, clamping pressure control unit 63, engine control unit 64, The transmission ratio control unit 65 and the synchronization control unit 66 are provided. In the synchronous control execution determination control described in FIG. 6 and the synchronous control described in FIG. 7, the processing unit reads the computer program into a memory incorporated in the processing unit based on the detection result by the sensor provided in each unit. The calculation is performed by sending a control signal according to the calculation result. At that time, the processing unit appropriately stores a numerical value in the middle of the calculation in the storage unit, and retrieves the stored numerical value and executes the calculation. In addition, when controlling each part, such as this toroidal-type continuously variable transmission 1 and the engine 21, you may control by the dedicated hardware different from ECU60 instead of the said computer program.

  The torque converter control unit 61 controls the lockup clutch of the torque converter 22. The torque converter control unit 61 controls the hydraulic control device 9 to perform engagement / disengagement of the lock-up clutch of the torque converter 22, that is, ON / OFF control.

  The forward / reverse switching control unit 62 controls the forward / reverse switching mechanism 23. The forward / reverse switching control unit 62 controls the hydraulic control device 9 to engage and disengage the forward clutch and reverse brake of the forward / reverse switching mechanism 23, that is, to perform ON / OFF control, so that the forward / reverse switching is performed. Switching control of the mechanism 23 is performed.

  The clamping pressure control unit 63 controls the hydraulic pressing mechanism 15 that applies a clamping pressure to sandwich the power roller 4 between the input disk 2 and the output disk 3. The clamping pressure control unit 63 controls the hydraulic control device 9 to control the amount of hydraulic oil supplied to the clamping pressure generating hydraulic chamber 15a, thereby controlling the clamping pressure by the hydraulic pressing mechanism 15 to a predetermined target clamping pressure. To do. The target clamping pressure in the hydraulic pressing mechanism 15 is basically set to a clamping pressure of a predetermined magnitude based on the input torque to the toroidal continuously variable transmission 1 in normal gear ratio control, that is, The slipping force between the input disk 2 and the output disk 3 and the power roller 4 is prevented, and the holding pressure is set to a magnitude that can maintain an appropriate traction state.

  The engine control unit 64 controls the operation of the engine 21. The engine control unit 64 controls the output from the engine 21 by controlling the injector, spark plug, and electronic throttle valve, and controls the engine torque as the output torque of the engine 21 and the engine speed.

  The gear ratio control unit 65 controls the gear ratio changing unit 5 so that the actual gear ratio that is the actual gear ratio becomes the target gear ratio that is the target gear ratio. In other words, the gear ratio control unit 65 controls the gear ratio changing unit 5 to control the actual gear ratio so that the actual input rotational speed to the input disk 2 becomes the target input rotational speed corresponding to the target gear ratio. Is. That is, as described above, the gear ratio control unit 65 operates the engine speed, the throttle opening, the accelerator opening, the engine speed, the input speed, the output speed, the shift position, etc. Based on the amount or the like, the target speed ratio, which is the target speed ratio, is determined, and the speed ratio changing unit 5 is driven to move the power roller 4 from the neutral position to the speed position to a predetermined stroke amount. The gear ratio is changed by tilting to the tilt angle. As described above, the gear ratio control unit 65 performs cascade feedback control so that the actual gear ratio (actual gear ratio) becomes the target gear ratio (target gear ratio after the gear shift), and the gear ratio In order to improve responsiveness, feedforward control may be performed together with this feedback control.

  For example, the synchronization control unit 66 receives a predetermined input from an operator at the first start after assembling the toroidal continuously variable transmission 1 or at the time of restart after disassembling, repairing and reassembling the toroidal continuously variable transmission 1. In accordance with the operation, synchronous control is performed to synchronize the plurality of power rollers 4 by reducing the clamping pressure by the hydraulic pressing mechanism 15. Specifically, the synchronization control unit 66 executes the synchronization control when the input disk 2 and the output disk 3 are not rotatable even when power is input to the input disk 2 or the output disk 3, and the synchronization control unit 66 executes the synchronization control. The clamping pressure by the hydraulic pressing mechanism 15 is reduced until the output disk 3 rotates.

  That is, the synchronization control unit 66 sets the target clamping pressure in the synchronous control of the power roller 4 to a value that is smaller than the target clamping pressure based on the input torque to the toroidal continuously variable transmission 1 in the normal gear ratio control. Then, the target clamping pressure is gradually reduced until the input disk 2 or the output disk 3 rotates. The clamping pressure control unit 63 controls the hydraulic control device 9 based on the target clamping pressure set by the synchronization control unit 66 in the synchronous control of the power roller 4 and is supplied to the clamping pressure generating hydraulic chamber 15a. By controlling the amount of oil, the clamping pressure by the hydraulic pressing mechanism 15 is controlled to a target clamping pressure that is lower than the target clamping pressure in the normal gear ratio control.

  Therefore, the toroidal continuously variable transmission 1 is used when the input disk 2 and the output disk 3 cannot rotate even when the ECU 60 that is also used as the synchronous control device 100 inputs power to the input disk 2 or the output disk 3. By performing the synchronous control that synchronizes the plurality of power rollers 4 by reducing the pinching force by the hydraulic pressing mechanism 15, the friction between each power roller 4, the input disk 2, and the output disk 3 is decreased. As a result, for example, immediately after assembly of the plurality of power rollers 4 at the first start after assembling the toroidal continuously variable transmission 1 or at the time of restart after disassembling, repairing and reassembling the toroidal continuously variable transmission 1 In this case, even when the tilt angles of the plurality of power rollers 4 are different and the tilt angles are not completely synchronized, the friction between each power roller 4 and the input disk 2 and output disk 3 can be reduced. Therefore, the input disk 2 and the output disk 3 can be rotated with a small input torque (power). As a result, the input disk 2 and the output disk 3 rotate with a small input torque, so that the tilt synchronization of the power rollers 4 can be recovered and the tilts of the plurality of power rollers 4 can be reliably synchronized. Therefore, the toroidal continuously variable transmission 1 can be reliably started immediately after the power roller 4 is assembled, and the vehicle on which the toroidal continuously variable transmission 1 is mounted can be started reliably. In addition, when assembling a plurality of power rollers 4 between the input disk 2 and the output disk 3, it is not necessary to have a high assembling accuracy so that the tilt angles of all the power rollers 4 coincide with each other. The efficiency of the assembly operation of the machine 1 can be improved, and for example, the manufacturing cost can be suppressed.

  Here, as shown in FIGS. 5A and 5B, the toroidal continuously variable transmission 1 has a stopper portion as a restricting means for restricting the tilt of the plurality of power rollers 4 with a predetermined tilt angle. 110. Then, when executing the synchronization control, the synchronization control unit 66 sets a predetermined tilt angle at which the stopper unit 110 restricts the tilt of each power roller 4 as a target tilt angle in the synchronization control. Then, the gear ratio control unit 65 controls the gear ratio change unit 5 so that the actual tilt angle of the power roller 4 becomes the target tilt angle in the synchronization control set by the synchronization control unit 66. That is, the gear ratio changing unit 5 tilts the power roller 4 so that the actual tilt angle of the power roller 4 becomes the target tilt angle set by the synchronization control unit 66. In addition, in FIG. 2, illustration of this stopper part 110 is abbreviate | omitted.

  Specifically, the stopper portion 110 is also used as a stopper portion that regulates the rotation of each trunnion 6 around the rotation axis X3 within the range of the speed ratio that can be realized by the toroidal continuously variable transmission 1 in normal speed ratio control. can do. The stopper part 110 includes a contact part 111 and a stopper 112.

  The abutting portion 111 is a disk-shaped member provided at each end of the swing shaft 6 b of each trunnion 6 (for example, the end on the upper link 17 side). Each abutment portion 111 is fixedly provided on the swing shaft 6b of each trunnion 6, and can rotate around the rotation axis X3 together with the swing shaft 6b of the trunnion 6 and along the rotation axis X3. It can move in any direction. The contact portion 111 is formed with a semi-annular protrusion 111a around the rocking shaft 6b of the circular end surface portion. The protrusion 111a has contact surfaces 111b formed at both end surfaces.

  On the other hand, the stopper 112 is a cylindrical pin member provided in the casing 112a. The stopper 112 is formed so as to protrude toward the contact portion 111 side.

  The contact surface 111b and the stopper 112 formed on the protruding portion 111a of the contact portion 111 are formed at positions where the swing shaft 6b of the trunnion 6 can be contacted by rotating around the rotation axis X3. Yes. Accordingly, the stopper portion 110 has a predetermined tilt angle corresponding to the maximum gear ratio when the swing shaft 6b of the trunnion 6 rotates around the rotation axis X3 and the one contact surface 111b contacts the stopper 112. Thus, the tilt of each power roller 4 can be regulated, and the tilt of each power roller 4 can be tilted at a predetermined tilt angle corresponding to the minimum speed ratio by contacting the other abutment surface 111b with the stopper 112. Can be regulated.

  Then, when executing the synchronization control, the synchronization control unit 66 sets a predetermined tilt angle corresponding to the minimum speed ratio or the maximum speed ratio at which the stopper unit 110 restricts the tilt of each power roller 4 to the target in the synchronization control. Set to tilt angle. Then, the gear ratio control unit 65 controls the gear ratio change unit 5 so that the actual tilt angle of the power roller 4 becomes the target tilt angle in the synchronization control set by the synchronization control unit 66.

  Therefore, when the synchronization control is executed, the target tilt angle is set so that each power roller 4 is tilted to the restriction position by the stopper unit 110 by the synchronization control unit 66, and the gear ratio changing unit 5 is connected to the power roller 4. By tilting the power roller 4 so that the actual tilt angle becomes the target tilt angle, the abutment surfaces 111b of the stopper portions 110 corresponding to all the power rollers 4 and the stoppers 112 abut. Since the tilting of all the power rollers 4 is restricted at the same tilting angle, the plurality of power rollers 4 can be reliably synchronized by the synchronization control by the synchronization control unit 66.

  Here, the stopper portion 110 is also used as a stopper portion that regulates the rotation of each trunnion 6 around the rotation axis X3 within the range of the speed ratio that can be realized by the toroidal continuously variable transmission 1 in normal speed ratio control. However, the present invention is not limited to this, and the stopper portion may be provided separately.

Next, the synchronous control execution determination control and the synchronous control by the ECU 60 (synchronous control device 100) of the toroidal continuously variable transmission 1 will be described with reference to the flowcharts of FIGS. 6 and 7 and the time chart of FIG. This control routine is repeatedly executed at a control cycle of several ms to several tens of ms. In the time chart of FIG. 8, the vertical axis indicates the tilt angle synchronization control execution flag F1 ON / OFF, the tilt stopper control flag F2 ON / OFF, the synchronization completion flag F3 ON / OFF, and the complete stop determination flag. ON / OFF of F4, counter T after reaching the stopper that measures the elapsed time since the tilting of any power roller 4 is restricted by the stopper 110, target stroke amount X _T , tilt angle φ, hydraulic pressure The clamping pressure Pld by the mechanism 15, the input rotation speed Nin of the input disk 2 detected by the input rotation speed sensor 53, and the output rotation speed Nout of the output disk 3 detected by the output rotation speed sensor 54, and the horizontal axis is the time axis.

  Here, the tilt angle synchronization control execution flag F1 is a flag for determining whether or not synchronization control for synchronizing the plurality of power rollers 4 is being executed by the ECU 60 (synchronization control device 100). The tilt stopper control flag F2 is controlled by the ECU 60 to control the tilt stopper, that is, a control for setting a predetermined tilt angle at which the stopper portion 110 restricts the tilt of each power roller 4 to a target tilt angle in the synchronous control. Is a flag for determining whether or not the process is being executed. The synchronization completion flag F3 is a flag for determining whether or not synchronization control for synchronizing the plurality of power rollers 4 by the ECU 60 is completed. For example, the synchronization completion flag F3 is set by a worker at a predetermined start time after assembling the toroidal continuously variable transmission 1 or when restarting after disassembling, repairing, and assembling the toroidal continuously variable transmission 1. When the input operation is performed, the synchronization control unit 66 of the ECU 60 is set to OFF at the initial reset before executing the synchronization control program. The complete stop determination flag F4 is a flag for determining whether or not the input disk 2 and the output disk 3 are rotating. The complete stop determination flag F4 is set to ON by the synchronization control unit 66 of the ECU 60 when the input rotation speed sensor 53 and the output rotation speed sensor 54 have not detected the rotation of the input disk 2 and the output disk 3, while When the rotation speed sensor 53 or the output rotation speed sensor 54 detects the rotation of the input disk 2 or the output disk 3, it is set to OFF by the synchronization controller 66 of the ECU 60.

  First, in the synchronization control execution determination control shown in FIG. 6, the synchronization control unit 66 of the ECU 60 (synchronization control device 100) determines whether or not the synchronization control for synchronizing the plurality of power rollers 4 is completed, that is, the synchronization completion flag F3. Whether or not is ON is determined (S100). When it is determined that the synchronization completion flag F3 is ON (S100: Yes), that is, when it is determined that the synchronization control for synchronizing the plurality of power rollers 4 is completed, the synchronization control execution determination control is ended.

  When it is determined that the synchronization completion flag F3 is OFF (S100: No), that is, when it is determined that the synchronization control for synchronizing the plurality of power rollers 4 has not been completed, the synchronization control unit 66 includes a plurality of synchronization controllers 66. It is determined whether or not the synchronization control for synchronizing the power roller 4 is being executed, that is, whether or not the tilt angle synchronization control execution flag F1 is ON (S102). When it is determined that the tilt angle synchronization control execution flag F1 is ON (S102: Yes), that is, when it is determined that the synchronization control for synchronizing the plurality of power rollers 4 is being executed, this synchronization control execution is performed. The judgment control is terminated.

  When it is determined that the tilt angle synchronization control execution flag F1 is OFF (S102: No), that is, when it is determined that the synchronization control for synchronizing the plurality of power rollers 4 is not being executed, the synchronization control unit 66 Then, it is determined whether or not the driving force transmission system including the toroidal continuously variable transmission 1 is in a state in which the driving force can be transmitted (S104). The synchronization control unit 66 includes, for example, the toroidal continuously variable transmission 1 by determining whether the forward clutch (friction clutch) or the reverse brake (friction brake) of the forward / reverse switching mechanism 23 has been engaged. What is necessary is just to determine whether a driving force transmission system is a state which can transmit a driving force. When it is determined that the driving force transmission system including the toroidal continuously variable transmission 1 cannot transmit the driving force (S104: No), that is, for example, the forward clutch and the reverse brake are both engaged. If it is determined that it is not, the synchronous control execution determination control is terminated.

  When it is determined that the driving force transmission system including the toroidal continuously variable transmission 1 is in a state in which the driving force can be transmitted (S104: Yes), that is, for example, either the forward clutch or the reverse brake is engaged. Is determined to be complete, the synchronization control unit 66 determines whether the input rotation speed sensor 53 and the output rotation speed sensor 54 have not detected the rotation of the input disk 2 and the output disk 3, that is, complete It is determined whether or not the stop determination flag F4 is ON (S106). When it is determined that the complete stop determination flag F4 is OFF (S106: No), that is, it is determined that the input rotation speed sensor 53 or the output rotation speed sensor 54 detects the rotation of the input disk 2 or the output disk 3. If so, the synchronous control execution determination control is terminated.

  When it is determined that the complete stop determination flag F4 is ON (S106: Yes), that is, it is determined that the input rotation speed sensor 53 and the output rotation speed sensor 54 have not detected the rotation of the input disk 2 and the output disk 3. In this case, the synchronization control unit 66 assigns ON to the tilt angle synchronization control execution flag F1, sets the tilt angle synchronization control execution flag F1 to ON (S108, time t1 in FIG. 8), and The synchronous control execution determination control is terminated.

  Next, in the synchronization control shown in FIG. 7, the synchronization control unit 66 of the ECU 60 (synchronization control device 100) determines whether or not the tilt angle synchronization control execution flag F1 is ON (S200). If it is determined that the tilt angle synchronization control execution flag F1 is OFF (S200: No), this synchronization control is terminated.

  When it is determined that the tilt angle synchronization control execution flag F1 is ON (S200: Yes), the synchronization controller 66 determines whether or not the tilt stopper control is being executed, that is, the tilt stopper control. It is determined whether or not the flag F2 is ON (S202).

When it is determined that the tilt stopper control flag F2 is OFF (S202: No), the synchronization control unit 66 assigns ON to the tilt stopper control flag F2, and sets the control flag F2 to the tilt stopper. In addition to being set to ON (S204, time t1 in FIG. 8), here, the tilt angle of each power roller 4 is set to the minimum tilt angle at which the tilt of each power roller 4 is restricted by the stopper 110. The target stroke amount is set to (S206, time t1 in FIG. 8). That is, set the target tilting angle phi _T is as tilting the power rollers 4 by the synchronization control unit 66 to the regulating position by the stopper portion 110 (time t1 in FIG. 8), the gear ratio control unit 65, the power actual tilt angle of the roller 4 controls the transmission ratio changing unit 5 so that the target tilting angle phi _T set by the synchronization control unit 66. Then, the synchronization control unit 66 resets the counter T after reaching the stopper that measures the elapsed time since the tilting of any of the power rollers 4 is restricted by the stopper unit 110, that is, sets the initial value to 0. (S216), this synchronization control is terminated.

  In S202, when it is determined that the tilt stopper control flag F2 is ON (S202: Yes), the synchronization control unit 66 has a value of the counter T after reaching the stopper equal to or greater than a preset threshold ThT. In other words, it is determined whether or not the elapsed period since the tilting of any of the power rollers 4 is restricted by the stopper portion 110 is equal to or longer than a predetermined period (S208). Here, the threshold value ThT set in advance with respect to the value of the counter T after reaching the stopper is the threshold value ThT of any other power roller 4 after any power roller 4 is restricted from tilting by the stopper portion 110. What is necessary is just to set suitably based on a test etc. previously in consideration of the period etc. until inclination is controlled by the stopper part 110. FIG.

When it is determined that the value of the counter T after reaching the stopper is smaller than the threshold value ThT (S208: No), the synchronization control unit 66 detects the actual tilt angle of any power roller 4 detected by the tilt angle sensor 50. It is determined whether or not has reached the vicinity of the stopper regulation tilt angle regulated by the stopper part 110 (S210). Here, the stopper regulating the tilting angle is restricted by the stopper portion 110 is a target tilting angle phi _T corresponding to the restricted position by the stopper portion 110 which is set in S206.

When it is determined that none of the power rollers 4 has reached the vicinity of the stopper tilt angle (the target tilt angle φ _T according to the restriction position by the stopper 110) (S210: No). That is, when it is determined that any of the power rollers 4 is not yet restricted from tilting by the stopper portion 110, the synchronization control portion 66 determines whether or not the complete stop determination flag F4 is ON (S212).

  When it is determined that the complete stop determination flag F4 is ON (S212: Yes), that is, it is determined that the input rotation speed sensor 53 and the output rotation speed sensor 54 have not detected the rotation of the input disk 2 and the output disk 3. In this case, the synchronization control unit 66 calculates the current target clamping pressure by subtracting a certain value from the target clamping pressure in the previous control cycle, and the clamping pressure control unit 63 determines the hydraulic pressure based on the target clamping pressure. The control device 9 is controlled to gradually reduce the clamping pressure by the hydraulic pressing mechanism 15 (S214, time t1 to time t3 in FIG. 8), reset the counter T after reaching the stopper (S216), and perform this synchronous control. finish.

Then, the input disk 2 and the output disk 3 start to rotate (time t2 in FIG. 8), and the input rotation speed sensor 53 or the output rotation speed sensor 54 detects the rotation of the input disk 2 or the output disk 3, and in S212 When it is determined that the complete stop determination flag F4 is OFF (S212: No, time t3 in FIG. 8), the synchronization control unit 66 skips the process of gradually reducing the clamping pressure by the hydraulic pressing mechanism 15 and The holding pressure is maintained, the counter T after reaching the stopper is reset (S216), and this synchronization control is terminated. At this time, when the input disk 2 and the output disk 3 start to rotate, each power roller 4 starts to tilt, and each actual tilt angle (for example, the actual tilt angle φ1, the actual tilt angle in FIG. 8). φ2) converges toward the stopper regulation tilt angle (the target tilt angle φ _T corresponding to the regulation position by the stopper 110) (after time t2 in FIG. 8).

When it is determined in S210 that the actual tilt angle of any of the power rollers 4 has reached the vicinity of the stopper regulation tilt angle (target tilt angle φ _T according to the regulation position by the stopper portion 110) (S210: Yes), the value of the counter T after reaching the stopper is counted up (S218, after time t4 in FIG. 8), and this synchronous control is terminated.

If it is determined in S208 that the value of the counter T after reaching the stopper is equal to or greater than the threshold ThT (S208: Yes, time t5 in FIG. 8), that is, any power roller 4 is tilted by the stopper 110. When it is determined that the elapsed period from the regulation is over a predetermined period, the synchronization control unit 66 substitutes ON for the synchronization completion flag F3, and sets the synchronization completion flag F3 to ON (S220, FIG. 8 at time t5). Then, the synchronization control unit 66 substitutes OFF for the tilt stopper control flag F2, sets the tilt stopper control flag F2 to OFF (S222, time t5 in FIG. 8), and sets the tilt angle synchronization control execution flag. OFF is substituted for F1, and this tilt angle synchronization control execution flag F1 is set to OFF (S224, time t5 in FIG. 8). Then, the synchronization control unit 66 returns the control of the target stroke amount X _T , the target tilt angle φ _T and the target clamping pressure to the normal control by the clamping pressure control unit 63 and the gear ratio control unit 65 (S226, S228, FIG. 8). At time t5), the counter T after reaching the stopper is reset (S216), and this synchronous control is terminated.

  According to the synchronous control device 100 according to the embodiment of the present invention described above, the clamping pressure that sandwiches the plurality of power rollers 4 between the input disk 2 and the output disk 3 by the hydraulic pressing mechanism 15 can be applied. Synchronous control of the toroidal continuously variable transmission 1 in which the speed ratio, which is the rotation speed ratio between the input disk 2 and the output disk 3, can be changed steplessly by synchronizing and tilting the plurality of power rollers 4. The apparatus 100 includes a synchronization control unit 66 that performs synchronization control for synchronizing the plurality of power rollers 4 by reducing the clamping pressure by the hydraulic pressing mechanism 15.

  Further, according to the toroidal continuously variable transmission 1 according to the embodiment of the present invention described above, the input disk 2 to which the driving force is input, the output disk 3 to which the driving force is output, the input disk 2, A plurality of power rollers 4 provided between the output disk 3 and the power roller 4 are rotatably and tiltably supported, and the plurality of power rollers 4 are tilted in synchronization with the input disk 2. A speed ratio changing unit 5 capable of changing a speed ratio which is a rotational speed ratio between the input disk 2 and the output disk 3, and a hydraulic pressure pressing mechanism 15 capable of applying a pinching force to sandwich the power roller 4 between the input disk 2 and the output disk 3. And a synchronization control unit 66 that performs synchronization control to synchronize the plurality of power rollers 4 by reducing the clamping pressure by the hydraulic pressing mechanism 15.

  Therefore, the synchronization control unit 66 of the synchronization control device 100 executes the synchronization control that synchronizes the plurality of power rollers 4 by reducing the clamping pressure by the hydraulic pressure pressing mechanism 15, so that each power roller 4, the input disk 2, and the output disk 3. As a result, the tilting of the plurality of power rollers 4 can be reliably synchronized.

  Furthermore, according to the toroidal-type continuously variable transmission 1 and the synchronization control device 100 according to the embodiment of the present invention described above, the synchronization control unit 66 can be operated even if power is input to the input disk 2 or the output disk 3. Synchronous control is executed when the input disk 2 or the output disk 3 cannot rotate, and the clamping pressure is reduced at least until the input disk 2 or the output disk 3 rotates. Therefore, even if the synchronization control unit 66 of the synchronization control device 100 inputs a driving force to the input disk 2 or the output disk 3, the clamping pressure by the hydraulic pressing mechanism 15 is reduced when the input disk 2 and the output disk 3 cannot rotate. By executing synchronous control to synchronize a plurality of power rollers 4, for example, at the first start after assembling the toroidal continuously variable transmission 1, the toroidal continuously variable transmission 1 is disassembled, repaired and assembled. At the time of subsequent restart, even if the tilt angles of the plurality of power rollers 4 are different immediately after the assembly of the plurality of power rollers 4, and the tilt angles are not completely synchronized, the input disk 2 can be operated with a small input torque. The output disk 3 can be rotated, the synchronization of the tilting of the power rollers 4 can be recovered, and the synchronization control can be executed appropriately.

  Furthermore, according to the toroidal continuously variable transmission 1 and the synchronous control device 100 according to the embodiment of the present invention described above, the toroidal continuously variable transmission 1 can rotate and tilt the plurality of power rollers 4. A gear ratio changing unit 5 that supports the roll freely and can change the gear ratio by tilting the power roller, and a stopper 110 that restricts the tilting of the plurality of power rollers 4 at a predetermined tilt angle. The synchronization control unit 66 sets a predetermined tilt angle to a target tilt angle that is a target tilt angle when executing the synchronization control, and the gear ratio changing unit 5 The power roller 4 is tilted so that the actual tilt angle, which is the tilt angle, becomes the target tilt angle. Therefore, when the synchronization control is executed, the target tilt angle is set so that each power roller 4 is tilted to the restriction position by the stopper unit 110 by the synchronization control unit 66, and the gear ratio changing unit 5 is connected to the power roller 4. By tilting the power roller 4 so that the actual tilt angle becomes the target tilt angle, the tilt of all the power rollers 4 is regulated by the stopper portion 110 at the same tilt angle. The plurality of power rollers 4 can be reliably synchronized by the synchronization control by the synchronization controller 66.

  In addition, the synchronous control apparatus and continuously variable transmission which concern on embodiment of this invention mentioned above are not limited to embodiment mentioned above, A various change is possible in the range described in the claim. In the above description, the continuously variable transmission has been described as a double-cavity toroidal continuously variable transmission. However, the present invention is not limited to this and may be a single-cavity toroidal continuously variable transmission. In the above description, the hydraulic control device 9 constituting the gear ratio changing unit has been described as including two flow rate control valves. However, the present invention is not limited to this, and may be one or three or more.

  Further, for example, if the contact point between the power roller 4 and the input disk 2 and the output disk 3 is known, the relationship between the actual transmission ratio and the actual tilt angle is determined only by the geometric shape. The actual tilt angle can be replaced with an actual transmission ratio. That is, the gear ratio control unit 65 calculates the actual gear ratio based on the actual actual tilt angle detected by the tilt angle sensor 50, calculates the deviation between the calculated actual gear ratio and the target gear ratio, The target stroke amount may be set based on the deviation. In this case, the actual gear ratio is calculated based on the actual actual tilt angle detected by the tilt angle sensor 50, for example, the input speed and the output speed detected by the input speed sensor 53, for example. It can also be calculated from the output rotation speed detected by the sensor 54.

  In the above description, the actual stroke amounts of the power roller 4 and the trunnion 6 have been described as being detected by the stroke sensor 51. However, the present invention is not limited to this, and changes in the actual tilt angle detected by the tilt angle sensor 50 are described. May be calculated based on the amount, the amount of change in the input speed detected by the input speed sensor 53, or the amount of change in the actual gear ratio.

  In the above description, the control means sets the predetermined tilt angle regulated by the regulation means to the target tilt angle that is the target tilt angle when executing the synchronous control, and changes the gear ratio changing means. Has been described as tilting the power roller so that the actual tilt angle, which is the actual tilt angle of the power roller, becomes the target tilt angle. The tilt can be reliably synchronized.

  As described above, the continuously variable transmission synchronization control device and continuously variable transmission according to the present invention can reliably synchronize the tilting of a plurality of power rollers, The present invention is suitable for application to a synchronous control device for a continuously variable transmission and a continuously variable transmission that transmit driving force from an electric motor to a road surface under optimum conditions according to the running state of the vehicle.

1 is a schematic sectional view of a toroidal continuously variable transmission to which a synchronous control device for a toroidal continuously variable transmission according to an embodiment of the present invention is applied. It is a block diagram of the principal part of the toroidal continuously variable transmission to which the synchronous control apparatus of the toroidal continuously variable transmission which concerns on embodiment of this invention is applied. It is a mimetic diagram explaining the neutral position with respect to the input disk of the power roller with which the toroidal type continuously variable transmission to which the synchronous control device of the toroidal type continuously variable transmission concerning the embodiment of the present invention is applied. It is a schematic diagram explaining the gear shift position with respect to the input disk of the power roller with which the toroidal continuously variable transmission to which the synchronous control device for the toroidal continuously variable transmission according to the embodiment of the present invention is applied. It is a side view of the stopper part with which the toroidal type continuously variable transmission which applied the synchronous control device of the toroidal type continuously variable transmission concerning the embodiment of the present invention is provided. It is a top view of the stopper part with which the toroidal type continuously variable transmission to which the synchronous control apparatus of the toroidal type continuously variable transmission which concerns on embodiment of this invention is applied. It is a flowchart explaining the synchronous control execution determination control in the synchronous control apparatus of the toroidal type continuously variable transmission which concerns on embodiment of this invention. It is a flowchart explaining the synchronous control in the synchronous control apparatus of the toroidal type continuously variable transmission which concerns on embodiment of this invention. It is a time chart explaining an example of synchronous control execution determination control and synchronous control in the synchronous control apparatus of the toroidal type continuously variable transmission which concerns on embodiment of this invention.

Explanation of symbols

1 Toroidal continuously variable transmission (continuously variable transmission)
2 Input disk 3 Output disk 4 Power roller 5 Gear ratio changing unit (speed ratio changing means)
6 trunnion 7 moving part 8 hydraulic piston part 9 hydraulic control device 10 input shaft 11 variator shaft 15 hydraulic pressure pressing mechanism (clamping means)
15a Clamping pressure generating hydraulic chamber 15b Clamping pressure piston 21 Engine 60 ECU
61 Torque converter control unit 62 Forward / reverse switching control unit 63 Nipping pressure control unit 64 Engine control unit 65 Gear ratio control unit 66 Synchronous control unit (control means)
81 Transmission control piston 82 Transmission control hydraulic chamber 93 First flow control valve 94 Second flow control valve 110 Stopper (regulating means)

Claims (4)

The input disk and the output disk can be acted on by clamping the plurality of power rollers between the input disk and the output disk by tilting means and tilting the plurality of power rollers in synchronization. In the continuously variable transmission synchronous control device capable of changing the speed ratio, which is the rotational speed ratio, to a stepless manner,
It is characterized by comprising control means for executing synchronous control for synchronizing the plurality of power rollers by reducing the clamping pressure by the clamping means.
Synchronous control device for continuously variable transmission. The control means performs the synchronization control when the input disk or the output disk is not rotatable even if power is input to the input disk or the output disk, and at least the input disk or the output disk rotates. Until the pinching pressure is reduced,
The synchronous control device for a continuously variable transmission according to claim 1. The continuously variable transmission supports the plurality of power rollers so as to be rotatable and tiltable, and the gear ratio changing means capable of changing the gear ratio by tilting the power roller; Restricting means for restricting the tilt of the power roller at a predetermined tilt angle,
The control means sets the predetermined tilt angle to a target tilt angle that is a target tilt angle when executing the synchronous control,
The transmission ratio changing means tilts the power roller so that an actual tilt angle that is an actual tilt angle of the power roller becomes the target tilt angle.
The synchronous control device for a continuously variable transmission according to claim 1 or 2. An input disk to which driving force is input;
An output disk from which the driving force is output;
A plurality of power rollers provided between the input disk and the output disk;
The power roller can be rotated and tilted, and the gear ratio, which is the rotational speed ratio between the input disk and the output disk, can be changed by tilting the plurality of power rollers in synchronization. Gear ratio changing means,
A clamping means capable of acting a clamping pressure to sandwich the power roller between the input disk and the output disk;
Control means for performing synchronous control to synchronize the plurality of power rollers by reducing the clamping pressure by the clamping means,
Continuously variable transmission.