WO2010070718A1 - 無段変速機 - Google Patents
無段変速機 Download PDFInfo
- Publication number
- WO2010070718A1 WO2010070718A1 PCT/JP2008/072772 JP2008072772W WO2010070718A1 WO 2010070718 A1 WO2010070718 A1 WO 2010070718A1 JP 2008072772 W JP2008072772 W JP 2008072772W WO 2010070718 A1 WO2010070718 A1 WO 2010070718A1
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- WO
- WIPO (PCT)
- Prior art keywords
- hydraulic
- pressure
- hydraulic chamber
- continuously variable
- variable transmission
- Prior art date
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/664—Friction gearings
- F16H61/6649—Friction gearings characterised by the means for controlling the torque transmitting capability of the gearing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
- F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
- F16H15/04—Gearings providing a continuous range of gear ratios
- F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
- F16H15/32—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line
- F16H15/36—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface
- F16H15/38—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/04—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism
- F16H63/06—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions
- F16H63/065—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions hydraulic actuating means
Definitions
- the present invention relates to a continuously variable transmission, and more particularly to a so-called toroidal continuously variable transmission in which a gear ratio is changed by movement of a power roller disposed between an input disk and an output disk.
- 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.
- 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).
- CVT Continuously Variable Transmission
- torque is transmitted between the disks via a power roller sandwiched between the input disk and the output disk.
- 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 rotated about a rotation axis, and is supplied to, for example, a shift control hydraulic chamber with respect to a piston provided in the trunnion. It is configured to be movable in the direction along the rotation axis by applying a shift control pressing force by the hydraulic pressure of the hydraulic oil.
- the power roller supported by the trunnion moves together with the trunnion from the neutral position with respect to the input disk and the output disk to the speed change position, so that a tangential force acts between the power roller and the disk, and a side slip occurs.
- the power roller rotates around the rotation axis with respect to the input disk and the output disk, that is, tilts, and as a result, the speed ratio which is the rotation 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 moving amount from the neutral position of the power roller to the shift position side.
- such a toroidal-type continuously variable transmission for example, by applying a predetermined clamping pressure for clamping the power roller between the input disk and the output disk by the clamping means, the input disk and the output disk The traction state is maintained at the contact portion between the power roller and the power roller.
- a continuously variable transmission described in Patent Document 1 is composed of the inner surface of both the input side and output side disks and the peripheral surface of the power roller.
- the continuously variable transmission has a high creep rate of the traction portion, and suppresses torque fluctuations of the output shaft by suppressing the torque transmitted to the output shaft.
- such a toroidal type continuously variable transmission has a tangential force acting on the contact points of the input disk, the output disk and the power roller in accordance with the input torque when the power roller and the trunnion supporting the power roller are in the neutral position.
- a shift control pressing force of a magnitude against the trunnion piston to balance the tangential force acting on the power roller and the shift control pressing force, the position of the power roller and the trunnion that supports it is in the neutral position.
- the gear ratio is fixed.
- the vehicle equipped with this toroidal-type continuously variable transmission is moved by traction or coasting in a state where the trunnion does not act on the trunnion and the output disc rotates, the output disc rotates and the tangential force is applied from the output disc to the power roller.
- the gear ratio is shifted to the reduction side (speed increase side) and may be upshifted.
- an object of the present invention is to provide a continuously variable transmission that can appropriately prevent an unintended shift.
- a continuously variable transmission is provided between an input disk to which a driving force is input, an output disk to which the driving force is output, and the input disk and the output disk.
- the power roller and the power roller can be rotated and tilted, and the speed ratio of the input disk and the output disk can be changed by tilting the power roller.
- a clamping means capable of acting a clamping pressure for clamping the power roller, and the operation of the clamping pressure generating hydraulic chamber provided in the connecting oil passage through an opening according to an operating state.
- Pressure release means capable of releasing the pressure of the medium, and the pressure release means is located on the upper side of the clamping pressure generating hydraulic chamber with respect to the vertical direction in a state where the pressure release means is mounted on a vehicle.
- the pressure release means releases the pressure of the working medium in the clamping pressure generating hydraulic chamber through the release portion when the drive source that generates the drive force is in a stopped state.
- the driving source when the driving source is in the operating state, it is preferable to set the blocking state in which the release of the pressure of the working medium in the clamping pressure generating hydraulic chamber through the opening portion is blocked.
- the pressure release means may be configured such that the clamping pressure via the release portion is when the drive source that generates the drive force is in a temporary stop state in idling stop control that automatically stops idling operation. It is preferable to set a shut-off state that shuts off the release of the pressure of the working medium in the generation hydraulic chamber.
- the pressure releasing means has a branch opening oil passage whose one end side can communicate with the connection oil passage and whose opening on the other end side forms the opening portion.
- the pressure release means may be in a closed state in which the clamping pressure generating hydraulic chamber is connected to the hydraulic control means, and an open state in which the clamping pressure generating hydraulic chamber is connected to the opening portion. It is preferable to have switchable switching means.
- the switching means is constituted by an electromagnetic valve that is in the closed state when energized and is in the open state when de-energized.
- the switching means is located above the clamping pressure generating hydraulic chamber with respect to the vertical direction in a state where the switching means is mounted on a vehicle.
- the speed ratio changing unit applies the shift control pressing force to the support unit that supports the power roller by the pressure of the working medium, whereby the power roller is input together with the support unit.
- the power roller is tilted by moving the disk and the output disk from a neutral position to a shift position, and the hydraulic control means is driven in conjunction with rotation of an output shaft of a drive source that generates the drive force.
- the pressure release means can pressurize the working medium, and the pressure release means, when the shift control pressing force cannot act on the support means, is operated via the release portion. It is preferable to set the open state in which the pressure of the working medium in the clamping pressure generating hydraulic chamber is released.
- the continuously variable transmission includes pressure release means provided in the connecting oil passage and capable of releasing the pressure of the working medium in the clamping pressure generating hydraulic chamber through the opening according to the operating state. Since the opening means is located on the upper side of the clamping pressure generating hydraulic chamber with respect to the vertical direction in a state where it is mounted on the vehicle, it is possible to appropriately prevent an unintended shift.
- FIG. 1 is a schematic sectional view of a toroidal continuously variable transmission according to an embodiment of the present invention.
- FIG. 2 is a schematic configuration diagram of a main part of the toroidal continuously variable transmission according to the embodiment of the present invention.
- FIG. 3 is a schematic diagram for explaining a neutral position of the power roller with respect to the input disk included in the toroidal continuously variable transmission according to the embodiment of the present invention.
- FIG. 4 is a schematic diagram for explaining the shift position of the power roller with respect to the input disk of the toroidal continuously variable transmission according to the embodiment of the present invention.
- FIG. 5 is a schematic configuration diagram showing a hydraulic oil supply system to the clamping pressure generating hydraulic chamber of the toroidal continuously variable transmission according to the embodiment of the present invention.
- FIG. 6 is a schematic configuration diagram showing a hydraulic oil supply system to a clamping pressure generating hydraulic chamber of a toroidal continuously variable transmission according to a modification of the present invention.
- FIG. 1 is a schematic cross-sectional view of a toroidal continuously variable transmission according to an embodiment of the present invention.
- FIG. 2 is a schematic configuration diagram of a main part of the toroidal continuously variable transmission according to the embodiment of the present invention. These are the schematic diagrams explaining the neutral position with respect to the input disk of the power roller with which the toroidal continuously variable transmission which concerns on embodiment of this invention is equipped,
- FIG. 4 is provided with the toroidal continuously variable transmission which concerns on embodiment of this invention.
- FIG. 5 is a schematic diagram illustrating a hydraulic oil supply system to a clamping pressure generating hydraulic chamber of the toroidal continuously variable transmission according to the embodiment of the present invention. .
- 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.
- an internal combustion engine gasoline engine, diesel engine, LPG engine, etc.
- an electric motor such as a motor that generates motor torque may be used as a drive source.
- a toroidal continuously variable transmission 1 as a continuously variable transmission uses a driving force from an engine 21 as a drive source mounted on a vehicle, that is, an output torque.
- This is a so-called CVT (CVT: Continuously Variable Transmission) that can be transmitted to the drive wheel 27 under the optimum conditions according to the state and can control the gear ratio steplessly (continuously).
- CVT Continuously Variable Transmission
- This toroidal-type continuously variable transmission 1 transmits torque between each input disk 2 and output disk 3 via a power roller 4 sandwiched between an input disk 2 and an output disk 3, and This is a so-called toroidal continuously variable transmission that tilts and changes the gear ratio.
- 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.
- 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 means and a moving unit 7. Furthermore, the moving part 7 has a hydraulic piston part 8 and a hydraulic control device 9 as hydraulic control means.
- the toroidal continuously variable transmission 1 includes an electronic control unit (ECU) 60 as a control means for controlling each part of the toroidal continuously variable transmission 1.
- ECU electronice control unit
- 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.
- 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 engine torque, that is, 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.
- the driving force (engine torque) of the engine 21 is transmitted from the crankshaft 21a to the pump via the front cover.
- the lock-up clutch is released, the driving force transmitted to the pump is transmitted to the turbine, the input shaft 22a, the input shaft via the working oil that is a working fluid interposed between the pump and the turbine. 10 is transmitted.
- 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.
- 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.
- ON / OFF control for engaging and releasing the lock-up clutch 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.
- 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.
- 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 the disk rotation axis.
- 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.
- 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.
- 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.
- 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.
- input disk 2 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 has an opening at the center and gradually protrudes from the outside toward the center.
- the slope of the protruding portion of each input disk 2 is formed such 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. .
- 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.
- 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.
- 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.
- each toroidal surface 3a faces the toroidal surface 2a of each input disk 2.
- 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 the output disks 3 rotate.
- 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 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 connected 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 a rotation axis X2 as a power roller rotation axis.
- the power roller 4 is formed by shearing 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.
- 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.
- Front semicircular cavity C F, the power roller 4 provided with a pair respectively rear semicircular cavity C R are provided opposite to each other across the rotation axis X1.
- the power roller 4 includes a power roller 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 body 41 is rotatably supported by a rotating shaft 42a formed on the outer ring 42 via a bearing portion (radial bearing) 43a.
- the power roller main body 41 is rotatably supported on a surface of the outer ring 42 facing the power roller main body 41 via a bearing portion (thrust bearing) 43b. 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 bearing portion (radial bearing) 43c 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.
- 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.
- 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.
- 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.
- 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.
- 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).
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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
- the rear side input disc 2 R is brought closer to the rear side output disc 3 R side
- 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.
- 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.
- the clamping pressing force by the hydraulic pressing mechanism 15 is controlled by the hydraulic control device 9 described later by controlling the amount of hydraulic oil or the hydraulic pressure 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 continuously variable 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.
- the gear ratio changing unit 5 includes the trunnion 6 and the moving unit 7.
- 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.
- the transmission ratio is a rotation speed ratio between the input disk 2 and the output disk 3, in other words, a rotation speed ratio.
- [transmission ratio output-side contact radius (power roller 4 and output disk 3 (contact radius (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)].
- 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 rotation shaft 6b as a shaft portion.
- roller support portion 6a a space portion 6c in which the power roller 4 is disposed is formed, 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.
- the roller support 6a is provided so as to be movable integrally with the rotating shaft 6b.
- the rotation shaft 6b is formed so as to protrude from the shoulder portion 6e of the roller support portion 6a.
- the shoulder portion 6e of the roller support portion 6a is a wall surface portion provided so as to stand up with respect to the wall surface portion where the fitting portion 6d is provided in the roller support portion 6a.
- the shoulder portions 6e are provided as a pair with respect to the wall surface portion where the fitting portion 6d is provided in the roller support portion 6a, and the pair of shoulder portions 6e are provided so as to face each other.
- the above-described space portion 6c is formed by the pair of shoulder portions 6e facing each other.
- the roller support portion 6a is integrally formed with a wall surface portion on which the fitting portion 6d is provided and a pair of shoulder portions 6e.
- the rotating shaft 6b is formed so as to protrude from the pair of shoulder portions 6e of the roller support portion 6a as described above.
- Each rotary shaft 6b is formed in a columnar shape and is provided to be rotatable about a rotation axis X3 coaxial with each other.
- the trunnion 6 is supported by the casing 1a via a lower link 16a, an upper link 17a, a cylinder body 86, etc., which will be described later, so that the roller support portion 6a can rotate about the rotation axis X3 together with the rotation shaft 6b.
- the trunnion 6 is supported by the casing 1a via the lower link 16a, the upper link 17a, the cylinder body 86, and the like so that the roller support portion 6a can move along the rotation axis X3 together with the rotation shaft 6b.
- the moving unit 7 is configured to be movable in the direction along the rotation axis X3.
- the lower link 16a and the upper link 17a will be described later in detail.
- 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
- two trunnions 6 that support the two power rollers 4 are provided as a pair.
- 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 rotation shaft 6b.
- the trunnion 6 is arranged so that the rotation axis X3 of the rotation 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, thereby moving the power roller 4 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.
- the trunnion 6 rotates around the rotation axis X3 to tilt the power roller 4 with respect to the input disk 2 and the output disk 3 around the rotation axis X3 in a plane perpendicular to the rotation axis X3. It can be made 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 speed change control piston 81 as a piston and a speed change control hydraulic chamber 82, and hydraulic pressure of hydraulic fluid introduced into the speed change control hydraulic chamber 82 is transmitted by the flange portion 84 of the speed change control piston 81.
- the trunnion 6 is moved in two directions (A1 direction and A2 direction) along the rotation axis X3.
- 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.
- the speed change control piston 81 includes a piston base 83 and a flange portion 84.
- the piston base 83 is formed in a cylindrical shape, and one end of the rotary shaft 6b is inserted therein, and is fixed with respect to the direction of the rotation axis X3 and the direction around the rotation 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 rotation shaft 6b, and rotates together with the piston base 83 and the rotation shaft 6b of the trunnion 6. It is movable in the direction along the axis X3.
- the flange portion 84 is formed in an annular plate shape around the rotation axis X3 of the rotation shaft 6b.
- the transmission control hydraulic chamber 82 is formed by a hydraulic chamber forming member 85.
- the hydraulic chamber forming member 85 includes a cylinder body 86 as a first forming member and a lower cover 87 as a second forming member. That is, the hydraulic chamber forming 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.
- the cylinder body 86 is formed with a recess serving as a space 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 the casing 1a on the opposite side of the cylinder body 86 from the lower cover 87 side.
- a gasket 88 is provided between the cylinder body 86 and the lower cover 87 to prevent leakage of hydraulic oil in the transmission control hydraulic chamber 82 to the outside.
- 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.
- annular seal member S1 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 S1 so that the hydraulic oil does not leak from each other.
- annular seal members S2, S3, and S4 are provided on the outer peripheral portion of the piston base 83 between a cylinder body 86 that is a hydraulic chamber forming member 85 that forms a shift control hydraulic chamber 82, and a lower cover 87. Accordingly, the outer periphery of the piston base 83 and the cylinder body 86 and the lower cover 87 are sealed by the seal members S2, S3, and S4 so that the hydraulic oil in the transmission control hydraulic chamber 82 does not leak to the outside. .
- 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.
- the positional relationship between the first hydraulic chamber OP ⁇ b> 1 and the second hydraulic chamber OP ⁇ b> 2 is switched for each trunnion 6.
- 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.
- the hydraulic control device 9 supplies hydraulic oil to each part of the transmission, for example, the shift control hydraulic chamber 82 of the hydraulic piston unit 8, the clamping pressure generating hydraulic chamber 15a of the hydraulic pressing mechanism 15, the torque converter 22, the forward / reverse switching mechanism 23, and the like. To do.
- the hydraulic control device 9 controls at least the amount of hydraulic oil or the hydraulic pressure supplied to the clamping pressure generating hydraulic chamber 15a and the shift control hydraulic chamber 82.
- the hydraulic control device 9 sucks, pressurizes, and discharges the hydraulic oil stored in the oil tank and supplied to each part of the transmission by the oil pump 9a as the pressurizing means.
- the oil pump 9a is driven in conjunction with, for example, rotation of the crankshaft 21a that is an output shaft of the engine 21 that generates driving force, and sucks and pressurizes hydraulic oil stored in the oil tank, and discharges it. To do.
- hydraulic oil pressurized by the oil pump 9a is supplied to various flow control valves through a pressure regulator valve.
- the various flow control valves include a spool valve element, an electromagnetic solenoid, and the like, supply hydraulic oil to the first hydraulic chamber OP1 and the second hydraulic chamber OP2, or the first hydraulic chamber OP1 and the second hydraulic chamber OP2. And a flow rate control valve for controlling the discharge of hydraulic oil from the hydraulic pressure chamber, a supply of hydraulic oil to the clamping pressure generating hydraulic chamber 15a, or a flow rate control valve for controlling the discharging of hydraulic fluid from the clamping pressure generating hydraulic chamber 15a.
- the flow rate control valve of the hydraulic control device 9 is configured such that, for example, an electromagnetic solenoid driven by a drive current based on a control command value input from the ECU 60 displaces the position of the spool valve element so that the first hydraulic chamber OP1, 2 Controls the flow rate or hydraulic pressure of hydraulic fluid supplied to and discharged from the hydraulic chamber OP2 and the clamping pressure generating hydraulic chamber 15a.
- the pressure regulator valve oils the hydraulic oil on the downstream side when the hydraulic pressure on the downstream side of the pressure regulator valve exceeds the 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 tank and adjusted to a predetermined line pressure.
- the ECU 60 controls the flow rate control valve of the hydraulic control device 9, supplies the hydraulic oil pressurized by the oil pump 9a to the first hydraulic chamber OP1, and discharges the hydraulic oil in the second hydraulic chamber OP2.
- the hydraulic pressure in the first hydraulic chamber OP1 acts on the flange portion 84, so that [the hydraulic pressure in the first hydraulic chamber OP1> the hydraulic pressure in the second hydraulic chamber OP2].
- the flange part 84 of the hydraulic piston part 8 is pressed in the first direction A1 along the rotation axis X3, and the power roller 4 moves together with the trunnion 6 in the first direction A1 along the rotation axis X3.
- the ECU 60 controls the flow rate control valve of the hydraulic control device 9, discharges the hydraulic oil pressurized by the oil pump 9a from the first hydraulic chamber OP1, and supplies it into the second hydraulic chamber OP2.
- the hydraulic pressure in the hydraulic chamber OP2 acts on the flange portion 84, so that [the hydraulic pressure in the first hydraulic chamber OP1 ⁇ the hydraulic pressure in the second hydraulic chamber OP2].
- the flange part 84 of the hydraulic piston part 8 is pressed in the second direction A2 along the rotation axis X3, and the power roller 4 moves in the second direction A2 along the rotation axis X3 together with the trunnion 6.
- the movement of the power roller 4 in the first direction A1 or the second direction A2 is adjusted according to the amount of movement of the spool valve element of the flow control valve.
- the moving unit 7 is driven by the ECU 60 by the hydraulic control device 9 and the hydraulic pressure in each shift control hydraulic chamber 82 of the hydraulic piston unit 8 is controlled.
- 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.
- the gear ratio changing unit 5 causes the moving unit 7 to move the pair of power rollers 4 together with the pair of trunnions 6 from a neutral position (see FIG. 3) with respect to the input disk 2 and the output disk 3 (see FIG. 3).
- the gear ratio can be changed by moving the power rollers 4 with respect to the input disk 2 and the output disk 3 by moving them in opposite directions to each other (see FIG. 4).
- 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. 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.
- 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.
- the rotation direction (the rolling direction) of the power roller 4 and the rotation direction of the input disk 2 and the output disk 3 coincide with each other at the contact point between the power roller 4 and the input disk 2 and the output disk 3.
- the tilting force does not act on the power roller 4, so that the power roller 4 continues to rotate with the input disk 2 while remaining in this neutral position, and the gear ratio during this period is fixed.
- the hydraulic piston unit 8 of the moving unit 7 and the hydraulic control device 9 are driven by hydraulic pressure.
- the trunnion 6 is made to act to resist the force. 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.
- the shift control pressing force F2 see FIG. 3 having a magnitude against (see FIG.
- 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.
- 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.
- the rotation direction of the power roller 4 and the rotation direction of the input disk 2 and the output disk 3 are deviated at the contact point between the power roller 4 and the input disk 2 and the output disk 3.
- 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.
- 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.
- the power roller 4 is moved in the second direction A2 along the rotation axis X3 (power The offset is made in the direction opposite to the moving direction of the input disk 2 at the contact point between the roller 4 and the input disk 2, 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).
- 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.
- 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.
- the power roller 4 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).
- 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.
- 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 determined based on the position where the rotation axis X2 that is the rotation center of the power roller 4 is orthogonal to the rotation axis X1 that is the rotation center of the input disk 2 and the output disk 3 from the reference position.
- the tilt angle (a tilt angle on the acute angle side) with respect to the input 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.
- the toroidal continuously variable transmission 1 is for synchronizing the movement of the pair of power rollers 4 and the trunnion 6 in the reverse direction along the rotational axis X3 provided for each of the pair of input disks 2 and output disks 3.
- a lower link mechanism 16 and an upper link mechanism 17 are provided.
- the lower link mechanism 16 has a lower link 16a as a link member, while the upper link mechanism 17 has an upper link 17a as a link member.
- the lower link 16a is a bearing that is a spherical bearing on one end side (between the cylinder body 86 and one shoulder 6e of the roller support portion 6a) where the speed change control piston 81 is provided on the rotation shaft 6b of the trunnion 6.
- a pair of trunnions 6 are connected via a portion (radial bearing) 6f.
- the upper link 17a has a pair of trunnions 6 via a bearing portion (radial bearing) 6f which is a spherical bearing on the other end side (the other shoulder portion 6e side of the roller support portion 6a) of the rotation shaft 6b of the trunnion 6.
- a bearing portion (radial bearing) 6f which is a spherical bearing on the other end side (the other shoulder portion 6e side of the roller support portion 6a) of the rotation shaft 6b of the trunnion 6.
- the lower link 16a and the upper link 17a are supported by the lower support shaft 16c of the lower post 16b fixed to the casing 1a and the upper support shaft 17c of the upper post 17b fixed to the casing 1a via the cylinder body 86, respectively.
- the lower support shaft 16c and the upper support shaft 17c are both formed in a cylindrical shape, and are fixedly provided so as not to move relative to the casing 1a so that the center axis thereof is in a direction parallel to the rotation axis X1.
- the lower link 16a and the upper link 17a are supported by the lower support shaft 16c and the upper support shaft 17c, respectively, so that the lower support shaft 16c and the upper support shaft 17c serve as fulcrums, that is, the lower support shaft 16c,
- the center axis of the upper support shaft 17c is set as a swing axis X4 so that it can swing like a seesaw.
- the lower link mechanism 16 and the upper link mechanism 17 are configured such that the lower link 16a and the upper link 17a swing about the swing axis X4 that is the center axis of the lower support shaft 16c and the upper support shaft 17c, thereby forming a pair of trunnions.
- the movement in the reverse direction along the rotation axis X3 of 6 can be synchronized.
- a nozzle 17d is attached to the upper post 17b, and an injection hole 17e is provided in the nozzle 17d, and the above-described traction oil is injected from the injection hole 17e.
- the toroidal continuously variable transmission 1 includes a synchronization mechanism 18 as a mechanism for promoting the synchronization of rotation about 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 reversed and stretched so as to intersect once between the fixed pulley 20 fixed to the rotation shaft 6b of each trunnion 6 and the fixed pulley 20 adjacent in the rotation axis X1 direction or the rotation axis X2 direction.
- the rotation torque of one trunnion 6 is transmitted to the other trunnion 6 by the frictional force with the synchronization wire 19 to be laid, thereby promoting the synchronization of rotation about the rotation axis X3 of the plurality of trunnions 6. Can do.
- the ECU 60 controls the driving of the toroidal-type continuously variable transmission 1, and in particular controls the speed ratio ⁇ .
- various input signals inputted from sensors attached to various places of the vehicle on which the engine 21 is mounted.
- 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.
- 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.
- the ECU 60 detects, for example, the 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
- 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 turning angle.
- the ECU 60 performs duty control on the drive current supplied to the flow rate control valve of the hydraulic control device 9 based on the control command value, so that the first hydraulic chamber OP1 and the second hydraulic chamber OP2 of the hydraulic piston portion 8 are controlled.
- the actual gear ratio becomes the target gear ratio. To control.
- 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. Therefore, each input disk 2 and output disk 3 has a clamping pressure 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.
- peripheral speed of the power roller 4 and the peripheral speed of the torque transmission point (contact point where the power roller 4 is in contact via the traction oil) of each input disk 2 and output disk 3 are substantially the same.
- 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 gear ratio.
- the ECU 60 changes the flow rate of the hydraulic control device 9 based on the rotational direction of the input disk 2 (or the output disk 3) in the case of changing the gear ratio to the set target gear ratio, that is, in the case of gear ratio shifting.
- the trunnion 6 is in a neutral position until the power roller 4 has an inclination angle corresponding to the target gear ratio.
- 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.
- the power roller 4 is moved from the neutral position to the first direction along the rotation axis X3 by the hydraulic pressure of the first hydraulic chamber OP1.
- the gear ratio increases and a downshift is performed.
- the power roller 4 is moved from the neutral position to the second direction along the rotation axis X3 by the hydraulic pressure of the second hydraulic chamber OP2.
- the gear ratio decreases and an upshift is performed.
- the trunnion 6 is moved in the first direction A1 or the second direction A2 until the power roller 4 again reaches the neutral position.
- the ECU 60 determines the actual gear ratio (actual speed ratio) based on, for example, the tilt angle of the power roller 4 detected by the tilt angle sensor (not shown) and the stroke amount detected by the stroke sensor (not shown). Cascade feedback control is performed so that the gear ratio) becomes the target gear ratio (target gear ratio after the gear shift). 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 actual tilt detected by the target tilt angle and the tilt angle sensor.
- 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 is the target stroke amount.
- the hydraulic control device 9 of the moving unit 7 is controlled so that the stroke amount is obtained.
- the ECU 60 determines a target gear ratio that is a target gear ratio from the accelerator opening and the vehicle speed.
- the required driving force is calculated based on the required driving amount represented by the accelerator opening degree and the vehicle speed
- the target output is obtained from the required driving force and the vehicle speed
- the target output is reduced to the minimum fuel consumption.
- 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 points between the power roller 4 and the input disk 2 and the output disk 3 are 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.
- the hydraulic pressure of the hydraulic fluid supplied to the shift control hydraulic chamber 82 for causing the shift control pressing force to act on the trunnion 6 decreases, and the shift control is performed on the trunnion 6.
- the gear ratio may be shifted to the decreasing side (accelerating side) and upshifted. That is, for example, when the oil pump 9a for pressurizing the hydraulic oil supplied to the shift control hydraulic chamber 82 is driven in conjunction with the rotation of the crankshaft 21a of the drive source such as the engine 21 as described above.
- a vehicle in which the toroidal continuously variable transmission 1 is mounted in an operating state where the oil pump 9a is stopped together with the engine 21 and an appropriate shift control pressing force cannot be applied to the flange portion 84 provided in the trunnion 6.
- the driving wheel 27 rotates due to towing or coasting, the rotational force is reversely input to the output disk 3 via the propeller shaft or the like, and the output disk 3 is also rotated.
- the friction on the input disk 2 side is counteracted.
- a tangential force acts on the power roller 4 from the output disk 3.
- the toroidal continuously variable transmission 1 of the present embodiment is in an operating state in a connecting oil passage 101 that connects the hydraulic control device 9 and the clamping pressure generating hydraulic chamber 15a as hydraulic control means. Accordingly, by providing a pressure release mechanism 100 as pressure release means capable of releasing the hydraulic pressure (pressure) of the hydraulic oil (working medium) in the clamping pressure generating hydraulic chamber 15a via the release portion 102, an unintended shift can be prevented. ing. Furthermore, in the toroidal continuously variable transmission 1 of the present embodiment, the pressure release mechanism 100 is located above the pinching pressure generation hydraulic chamber 15a with respect to the vertical direction when the pressure release mechanism 100 is mounted on the vehicle. Thus, the responsiveness of the reduction of the hydraulic pressure of the clamping pressure generating hydraulic chamber 15a and the return of the hydraulic pressure of the clamping pressure generating hydraulic chamber 15a is improved, and an unintended shift is appropriately prevented.
- the disk clamping and pressing force acting surface 29 is partitioned in the direction along the rotation axis X1. More specifically, the hydraulic pressing mechanism 15, is provided an annular seal member S5 is between the outer peripheral surface of the inner peripheral surface and the front input disk 2 F cylindrical portion of the cylindrical portion of the nipping and pressing force piston 15b It has been. Therefore, the hydraulic oil supplied to the inside of the clamping force generating hydraulic chamber 15a is sealed so as not to leak to the outside by the sealing member S5 is between nipping and pressing force piston 15b and the front input disk 2 F .
- the clamping pressure generating hydraulic chamber 15a supplies hydraulic oil to the clamping pressure generating hydraulic chamber 15a, or the connecting oil passage 101 is connected to an introduction / discharge port 15c through which hydraulic oil is discharged from the clamping pressure generating hydraulic chamber 15a. It is connected.
- the connecting oil passage 101 allows hydraulic oil to flow therethrough, and connects the clamping pressure generating hydraulic chamber 15 a and the hydraulic control device 9. That is, the clamping pressure generating hydraulic chamber 15 a is connected to the hydraulic control device 9 via the connecting oil passage 101. Therefore, the hydraulic pressure pressing mechanism 15 has the input disk 2 and the output disk 3 by the hydraulic pressure of the hydraulic oil supplied from the hydraulic control device 9 for controlling the hydraulic pressure of the hydraulic oil to the clamping pressure generating hydraulic chamber 15a via the connecting oil passage 101. (See FIG. 1) and the power roller 4 (see FIG. 1) are brought into contact with each other, and a clamping pressure for sandwiching the power roller 4 between the input disk 2 and the output disk 3 can be applied.
- the pressure release mechanism 100 is provided in the connecting oil passage 101 and can release the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a via the release portion 102 according to the operating state.
- the opening part 102 releases the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15 a through a part of the connecting oil passage 101.
- the open part 102 is a part where the space part on the inner side of the connecting oil passage 101 and the space part on the outer side of the connecting oil path 101 communicate with each other, and the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a according to the operating state Is released to the atmosphere in the space portion on the outside of the connecting oil passage 101, for example, and the pressure is reduced to a predetermined opening pressure (for example, equivalent to atmospheric pressure).
- the pressure release mechanism 100 includes a branch opening oil passage 103 and a switching valve 104 as switching means.
- the branch open oil passage 103 is an oil passage that branches off from the connecting oil passage 101, and allows hydraulic oil to flow therethrough.
- One end of the branch opening oil passage 103 is connected to the switching valve 104, and can communicate with the connection oil passage 101 via the switching valve 104.
- an open opening 103 a that is an opening on the other end side forms the open portion 102. That is, the branch open oil passage 103 is provided with the switching valve 104 on one end side, and provided with an open opening 103a forming the open portion 102 on the other end side.
- the opening 103a which makes the opening part 102 of this embodiment is a state where the toroidal type continuously variable transmission 1 is mounted on the vehicle, and the position with respect to the vertical direction is set to the upper side in the vertical direction than the clamping pressure generating hydraulic chamber 15a.
- the opening 103a is disposed at a vertical position H2 that is vertically above the vertical position H1 of the vertical upper end of the clamping pressure generating hydraulic chamber 15a.
- the opening 103a that forms the opening 102 is provided so as to face the lower side in the vertical direction at the vertical position H2 that is higher than the vertical position H1 in the vertical direction.
- the pressure release mechanism 100 is provided with a storage portion 105 that can store hydraulic oil discharged from the opening 103a on the lower side in the vertical direction of the opening 103a that forms the opening 102.
- the storage part 105 is provided at a position facing the opening 103a that forms the opening 102 in the vertical direction.
- the switching valve 104 is provided on the connecting oil passage 101 and switches the connection state between the connecting oil passage 101 and the branch opening oil passage 103 according to the operating state.
- the branch opening oil passage 103 is configured to branch from the connection oil passage 101 by the switching valve 104.
- the connecting oil passage 101 includes a hydraulic chamber side oil passage 101a located on the clamping pressure generating hydraulic chamber 15a side with the switching valve 104 as a boundary, and a control device side oil passage 101b located on the hydraulic control device 9 side. Consists of.
- the hydraulic chamber side oil passage 101a is an oil passage located between the switching valve 104 and the clamping pressure generating hydraulic chamber 15a in the connection oil passage 101.
- One end of the hydraulic chamber side oil passage 101a is connected to the introduction / discharge port 15c of the clamping pressure generating hydraulic chamber 15a, and the other end is connected to the switching valve 104.
- the control device side oil passage 101 b is a portion of the oil passage 101 located between the switching valve 104 and the hydraulic control device 9 in the connection oil passage 101.
- the control device side oil passage 101b has one end connected to the hydraulic control device 9 and the other end connected to the switching valve 104.
- the switching valve 104 is an electromagnetic valve that is driven when a predetermined current is supplied to the solenoid 104a.
- the hydraulic chamber 15a can be switched to an open state in which the hydraulic chamber 15a is connected to the open portion 102. In the closed state, the switching valve 104 communicates the clamping pressure generating hydraulic chamber 15a with the hydraulic control device 9 and blocks communication with the opening portion 102.
- the switching valve 104 connects the hydraulic chamber side oil passage 101a and the control device side oil passage 101b, so that the hydraulic fluid between the hydraulic chamber side oil passage 101a and the control device side oil passage 101b is transferred. Allow distribution. In other words, in the closed state, the switching valve 104 connects the hydraulic chamber side oil passage 101a and the control device side oil passage 101b, so that the clamping pressure is obtained via the hydraulic chamber side oil passage 101a and the control device side oil passage 101b.
- the generating hydraulic chamber 15a and the hydraulic control device 9 are connected.
- the pressure release mechanism 100 can be in a shut-off state that shuts off the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a through the opening 103a that forms the opening 102, and the hydraulic control device 9
- the clamping pressure by the hydraulic pressing mechanism 15 is set to a predetermined magnitude based on the input torque to the toroidal continuously variable transmission 1. Can be controlled.
- the switching valve 104 connects the hydraulic chamber side oil passage 101 a and the branch opening oil passage 103, thereby allowing the hydraulic oil to flow between the hydraulic chamber side oil passage 101 a and the branch opening oil passage 103.
- the switching valve 104 connects the hydraulic chamber side oil passage 101 a and the branch opening oil passage 103, so that the clamping pressure generating hydraulic pressure is connected via the hydraulic chamber side oil passage 101 a and the branch opening oil passage 103.
- the chamber 15a and the opening 103a that forms the opening 102 are connected.
- the pressure release mechanism 100 can be in an open state in which the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a is released through the open opening 103a that forms the open portion 102.
- the switching valve 104 of the present embodiment is connected to the ECU 60, and the drive is controlled by the ECU 60.
- the switching valve 104 is constituted by an electromagnetic valve that is closed when the solenoid 104a is energized (ON control), and opened when the solenoid 104a is not energized (OFF control).
- the switching valve 104 includes, for example, an elastic member 104b together with a solenoid 104a.
- the switching valve 104 has a pressing force by a solenoid 104a acting on a spool valve element (not shown) biased by an elastic member 104b acting on the spool valve element.
- the ON state (the state of the ON portion shown in FIG. 5), that is, the closed pressure generating hydraulic chamber 15 a is connected to the hydraulic control device 9.
- the switching valve 104 is caused by the pressing force of the solenoid 104a acting on the spool valve element (not shown) by the urging force of the elastic member 104b acting on the spool valve element.
- the OFF state (the state of the OFF portion shown in FIG. 5), that is, the open state in which the clamping pressure generating hydraulic chamber 15a is connected to the open opening 103a forming the open portion 102. It becomes.
- the switching valve 104 of the present embodiment is set such that the position in the vertical direction is higher than the clamping pressure generating hydraulic chamber 15a in the vertical direction in a state where the toroidal continuously variable transmission 1 is mounted on the vehicle. More specifically, the switching valve 104 is disposed vertically above the vertical position H1 of the upper end in the vertical direction of the clamping pressure generating hydraulic chamber 15a. Here, the switching valve 104 is provided on the uppermost position in the vertical direction on the connecting oil passage 101.
- the ECU 60 controls the operating state of the pressure release mechanism 100 by controlling the drive current supplied to the solenoid 104a according to the driving state of the vehicle on which the toroidal continuously variable transmission 1, the engine 21 and the like are mounted.
- the pressure release mechanism 100 is basically driven in conjunction with the rotation of the crankshaft 21a when, for example, the engine 21 is in a normal stop state when the shift control pressing force cannot act on the trunnion 6.
- the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a is released by being controlled by the ECU 60.
- the ECU 60 controls the switching valve 104 to an open state in which the clamping pressure generating hydraulic chamber 15a is connected to the open portion 102, so that the open portion An open state is set in which the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a is released through the open opening 103a forming 102.
- the pressure release mechanism 100 is controlled by the ECU 60 to a closed state in which the switching valve 104 is connected to the hydraulic pressure control device 9 so that the opening portion 102 is open. It is set as the interruption
- the ECU 60 can determine the stop state and the operation state of the engine 21 based on various input signals input from sensors attached to various parts of the vehicle on which the toroidal continuously variable transmission 1 and the engine 21 are mounted.
- the switching valve 104 is connected to the hydraulic pressure control device 9 by the switching valve 104 by the ECU 60.
- the release state of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a through the open opening 103a forming the open portion 102 is set to a cut-off state.
- the idling stop control of the engine 21 is control for automatically stopping the idling operation.
- the ECU 60 detects, for example, a stop of the vehicle, temporarily stops the engine 21, detects a start operation, and restarts the engine 21.
- the ECU 60 executes the idling stop control when it is determined that the vehicle is stopped and it is clear that the vehicle does not travel for a predetermined period. That is, the ECU 60 automatically stops the engine 21 (idling stop) when the driver temporarily stops by operating the brake pedal of the vehicle, for example, waiting for a signal at an intersection.
- the pressure release mechanism 100 is controlled by the ECU 60. Under the control, the release state of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a through the open opening 103a forming the open portion 102 is set to a cut-off state. Thereafter, the ECU 60 restarts the engine 21 when the operation of the brake pedal is released and the accelerator pedal is depressed.
- the ECU 60 can determine the temporary stop state in the idling stop control of the engine 21 based on various input signals input from sensors attached to various parts of the vehicle on which the toroidal continuously variable transmission 1 and the engine 21 are mounted. it can.
- the oil pump 9a is driven and the shift control is performed on the flange portion 84 of the shift control piston 81.
- An operating state in which the pressing force can be applied is obtained.
- the switching valve 104 of the pressure release mechanism 100 is closed by the ECU 60 when the engine 21 is in an operating state and the shift control pressing force can act on the flange portion 84 of the shift control piston 81. And the release of the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a through the opening 103a that forms the opening 102 is cut off.
- the toroidal continuously variable transmission 1 is controlled by the hydraulic control device 9 by controlling the amount of hydraulic oil or the hydraulic pressure supplied to the inside of the clamping pressure generating hydraulic chamber 15a of the hydraulic pressing mechanism 15.
- Each input disk 2 is brought close to each output disk 3 by the pressing pressure of the hydraulic oil, and the clamping pressure for sandwiching the power roller 4 between the input disk 2 and the output disk 3 is determined based on the input torque. It works with the size of.
- the toroidal continuously variable transmission 1 can prevent slipping between the input disk 2 and output disk 3 and the power roller 4 and maintain an appropriate traction state. Power can be properly transmitted to and from the power roller 4.
- the toroidal-type continuously variable transmission 1 causes the trunnion to apply a predetermined shift control pressing force to the flange portion 84 of the shift control piston 81 by the hydraulic control device 9 when the gear ratio is changed (during shift). 6 and the power roller 4 can be tilted with respect to the input disk 2 and the output disk 3 to change the gear ratio. Further, when the transmission ratio is fixed (when the transmission ratio is fixed), the toroidal-type continuously variable transmission 1 applies the input disk 2 and the output disk to the flange portion 84 of the transmission control piston 81 by the hydraulic control device 9 according to the input torque.
- the position of the power roller 4 and the trunnion 6 that supports it is set to the neutral position.
- the gear ratio can be fixed.
- the toroidal continuously variable transmission 1 when the engine 21 is in a stopped state due to, for example, the operation being stopped by turning off the ignition key, the driving of the oil pump 9a is stopped and the shift control push on the flange portion 84 of the shift control piston 81 is performed. It becomes an operation state in which pressure cannot act.
- the oil pump 9a is driven in conjunction with the rotation of the crankshaft 21a of the engine 21 that generates the driving force, thereby operating the hydraulic oil and the hydraulic pressure pressing mechanism that operates the hydraulic piston portion 8 of the transmission ratio changing unit 5.
- the hydraulic oil which operates 15 is pressurized.
- the hydraulic fluid that operates the hydraulic piston portion 8 of the transmission ratio changing portion 5 and the hydraulic fluid that operates the clamping pressure piston 15b of the hydraulic pressure mechanism 15 are pressurized to a line pressure by a common oil pump 9a.
- the original pressure of the hydraulic oil that operates the hydraulic piston portion 8 of the transmission ratio changing section 5 and the original pressure of the hydraulic oil that operates the clamping pressure piston 15b of the hydraulic pressure pressing mechanism 15 are common pressure. Therefore, the toroidal continuously variable transmission 1 is also clamped by the clamping pressure piston 15b of the hydraulic pressing mechanism 15 in an operating state in which the shift control pressing force cannot act on the flange portion 84 of the transmission control piston 81. The pressing force becomes inoperable.
- the switching valve 104 of the pressure release mechanism 100 is operated by the ECU 60 when the engine 21 is stopped and the shift control pressing force cannot act on the flange portion 84 of the shift control piston 81. Is controlled to the open state, and the hydraulic oil pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a is released through the open opening 103a that forms the open portion 102. In the toroidal continuously variable transmission 1, the switching valve 104 is controlled to be in the open state, and the hydraulic pressure of the hydraulic oil in the pinching pressure generating hydraulic chamber 15a is released through the open opening 103a that forms the open portion 102.
- the hydraulic pressure of the hydraulic oil in the pressure generating hydraulic chamber 15a can be quickly reduced to a predetermined opening pressure (for example, equivalent to atmospheric pressure).
- a predetermined opening pressure for example, equivalent to atmospheric pressure.
- the toroidal-type continuously variable transmission 1 is in a state where the hydraulic pressure of the hydraulic oil supplied to the shift control hydraulic chamber 82 is reduced and the shift control pressing force does not act on the trunnion 6, in this case, the engine 21 is stopped.
- the transmission of power between the input disk 2, the output disk 3 and the power roller 4 is cut off, so that the drive wheels 27 are driven by the traction or inertia of the vehicle on which the toroidal continuously variable transmission 1 is mounted. Even when the output disk 3 rotates and the output disk 3 rotates, the tangential force from the output disk 3 to the power roller 4 can be prevented.
- the toroidal continuously variable transmission 1 prevents the tangential force from acting on the power roller 4 from the output disk 3, thereby preventing the power roller 4 from tilting and preventing an unintended shift. That is, it is possible to prevent the gear ratio from being shifted to the decreasing side and upshifting to the high speed side gear ratio. Thereby, the toroidal type continuously variable transmission 1 can prevent the startability from deteriorating due to insufficient torque or the like. Further, for example, in order to apply a pressing force against the tangential force acting on the power roller 4 from the output disk 3 when the driving wheel 27 is rotated to the trunnion 6, an output that is not particularly used during normal traveling.
- the predetermined shift control must be continuously executed while the vehicle is being pulled, but the toroidal continuously variable transmission according to the present embodiment. If 1, the transmission of power between the input disk 2, the output disk 3 and the power roller 4 is cut off, so there is no need to execute shift control during towing of the vehicle. Power consumption can be suppressed.
- the toroidal continuously variable transmission 1 operates the clamping pressure generating hydraulic chamber 15a with respect to the stop of the engine 21 by switching the switching valve 104 to the open state when the engine 21 is stopped.
- the oil pressure of the oil is quickly reduced to a predetermined opening pressure, and the transmission of power between the input disk 2, the output disk 3 and the power roller 4 is interrupted with good responsiveness. It is possible to prevent power from being transmitted between the input disk 2, the output disk 3 and the power roller 4 due to the residual pressure of the hydraulic oil, and to prevent unintended shifts appropriately.
- the toroidal continuously variable transmission 1 releases the oil pressure (that is, The hydraulic oil is discharged from the opening 103a that forms the opening 102 to the reservoir 105 as the hydraulic pressure is reduced.
- the toroidal continuously variable transmission 1 of the present embodiment since the opening 103a that forms the opening 102 is positioned above the clamping pressure generating hydraulic chamber 15a in the vertical direction, the clamping pressure generating hydraulic chamber 15a, the connecting oil passage 101, In the hydraulic control device 9, hydraulic oil remains in a portion below the vertical position H ⁇ b> 2 of the opening 103 a in the vertical direction. In other words, the hydraulic oil remaining in the lower portion in the vertical direction from the vertical position H2 of the opening 103a remains in the clamping pressure generating hydraulic chamber 15a, the connecting oil passage 101, and the hydraulic control device 9 as it is. Yes.
- the switching valve 104 since the switching valve 104 is positioned above the clamping pressure generating hydraulic chamber 15a in the vertical direction, for example, deformation of the switching valve 104, variation according to component accuracy, etc. Even if hydraulic fluid leaks from the connecting portion between the switching valve 104 and the hydraulic chamber side oil passage 101a, the control device side oil passage 101b, the branch opening oil passage 103, etc. In the connecting oil passage 101 and the hydraulic control device 9, the hydraulic oil can be reliably left at least in the vertical direction lower than the vertical position of the hydraulic oil leakage portion.
- the engine 21 is restarted when the ignition key is turned on, the engine 21 is in an operating state, the oil pump 9 a is driven, and the shift control pressing force can act on the flange portion 84 of the shift control piston 81.
- the ECU 60 controls the switching valve 104 of the pressure release mechanism 100 to the closed state when the ECU 60 is in an operating state, and the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a is released through the opening 103a that forms the opening 102. It becomes the cut-off state to be cut off.
- the clamping oil pressure generating hydraulic chamber 15a, the connecting oil passage 101, and the hydraulic control device 9 remain in a state in which the hydraulic oil remaining in the portion below the vertical direction H2 of the opening 103a is filled as it is. Therefore, the clamping pressure is generated from the hydraulic control device 9 via the connection oil passage 101 by the action of the hydraulic oil remaining in the state where the clamping pressure generating hydraulic chamber 15a, the connection oil passage 101, and the hydraulic control device 9 are filled.
- the hydraulic pressure of the hydraulic oil in the generation hydraulic chamber 15a can be quickly raised.
- the toroidal continuously variable transmission 1 promptly increases the clamping pressure of the hydraulic oil of the hydraulic pressing mechanism 15 because the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a is quickly increased.
- the clamping pressure for clamping the power roller 4 between the input disk 2 and the output disk 3 can be applied with good responsiveness to the start of the engine 21.
- the toroidal continuously variable transmission 1 can shift to the speed change control by the speed ratio changing unit 5 with high responsiveness to the start of the engine 21. That is, it is possible to prevent delays in restarting and restarting the vehicle on which the toroidal continuously variable transmission 1 is mounted.
- the connecting oil passage 101 is illustrated as a part of which is located vertically above the vertical position H2 of the opening 103a.
- the hydraulic control device 9 is configured such that the entirety thereof is positioned below the vertical position H2 of the opening 103a that forms the opening 102. That is, in the pressure release mechanism 100, as shown in FIG. It is more preferable to be positioned because the remaining portion of the sandwiching pressure generating hydraulic chamber 15a, the connecting oil passage 101, and the hydraulic control device 9 that are left filled with the working oil is increased.
- the switching valve 104 of the pressure release mechanism 100 is controlled to be closed by the ECU 60, that is, the switching valve 104. Is maintained in a closed state, and is maintained in a shut-off state in which the release of the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a through the open opening 103a forming the open portion 102 is cut off.
- the toroidal continuously variable transmission 1 stops the drive of the oil pump 9a when the engine 21 is temporarily stopped.
- the switching valve 104 is maintained in the closed state, so that the opening portion 102 is formed.
- the system basically constitutes a closed circuit as a system closed to the outside. For this reason, the hydraulic pressure of the hydraulic oil remaining in the hydraulic oil supply system from the hydraulic pressure control device 9 constituting the closed circuit to the clamping pressure generating hydraulic chamber 15 a and filled is supplied from the hydraulic pressure control device 9 including the connecting oil passage 101.
- the toroidal-type continuously variable transmission 1 controls the gear ratio to a predetermined gear ratio by normal gear shifting control when the vehicle travels coasting in this state.
- the toroidal continuously variable transmission 1 moves from the hydraulic control device 9 including the connecting oil passage 101 to the pinching pressure generating hydraulic chamber 15a.
- the hydraulic oil and the hydraulic pressure due to the hydraulic oil remain in the hydraulic oil supply system of the hydraulic oil, so that the residual hydraulic oil and the residual pressure due to the hydraulic oil act to hold the hydraulic oil from the hydraulic control device 9 via the connecting oil passage 101.
- the hydraulic pressure of the hydraulic oil in the pressure generating hydraulic chamber 15a can be quickly raised.
- the toroidal-type continuously variable transmission 1 can increase the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a more quickly, for example, compared to when the normal engine 21 is started.
- the toroidal continuously variable transmission 1 promptly increases the clamping pressure of the hydraulic oil of the hydraulic pressing mechanism 15 because the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a is quickly increased. Therefore, the clamping pressure for clamping the power roller 4 between the input disk 2 and the output disk 3 can be applied with good responsiveness to the start of the engine 21. As a result, the toroidal continuously variable transmission 1 can shift to the shift control by the gear ratio changing unit 5 with more responsiveness to the restart of the engine 21 in the idling stop control. That is, it is possible to prevent delays in restarting and restarting the vehicle on which the toroidal continuously variable transmission 1 is mounted.
- the toroidal continuously variable transmission 1 may further include a pressure accumulator in the hydraulic oil supply system from the hydraulic control device 9 including the connecting oil passage 101 to the clamping pressure generating hydraulic chamber 15a.
- the pressure accumulator retains a predetermined hydraulic pressure by storing hydraulic fluid that flows from the hydraulic control device 9 to the clamping pressure generating hydraulic chamber 15a via the hydraulic fluid supply system.
- the toroidal continuously variable transmission 1 is clamped by the hydraulic control device 9 including the connecting oil passage 101 when the engine 21 is temporarily stopped in so-called idling stop control and the switching valve 104 is maintained in the closed state.
- the hydraulic pressure of the hydraulic oil remaining in the hydraulic oil supply system to the generated hydraulic chamber 15a can be maintained at a predetermined hydraulic pressure over a longer period.
- the switching valve 104 constituting the pressure release mechanism 100 is closed when the solenoid 104a is energized (during ON control), while the solenoid 104a is not energized. It is configured to be in an open state (during OFF control). Therefore, in the toroidal continuously variable transmission 1, for example, when a vehicle equipped with the toroidal continuously variable transmission 1 is traveling, the solenoid 104a is temporarily disconnected or a power supply unit that supplies current to the solenoid 104a has an abnormality.
- the switching valve 104 is shifted to an open state, and this state is maintained, that is, the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a is released through the opening 103a that forms the opening 102. It is possible to immediately shift to the state and maintain this state. As a result, the toroidal continuously variable transmission 1 can cut off the transmission of power between the input disk 2, the output disk 3 and the power roller 4, so that the solenoid 104a is temporarily disconnected while the vehicle is running. Even when an abnormality occurs in the power supply unit that supplies current to the solenoid 104a, it is possible to prevent an unintended shift from occurring, and thus a sudden shift occurs in the above case. For example, it is possible to reliably prevent an abnormality in the behavior of the vehicle due to a shock caused by sudden deceleration, for example.
- 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 and the output disk
- the power roller 4 provided between the input disk 2 and the power roller 4 is rotatably and tiltably supported, and the power roller 4 is tilted so that the rotation speed ratio between the input disk 2 and the output disk 3 is increased.
- This is input by the hydraulic pressure of the hydraulic fluid supplied to the clamping pressure generating hydraulic chamber 15a from the hydraulic pressure control device 9 that controls the hydraulic pressure of the hydraulic fluid and the hydraulic pressure control device 9 that controls the hydraulic pressure of the hydraulic fluid via the connecting fluid passage 101.
- a hydraulic pressing mechanism 15 capable of acting a clamping pressure to sandwich the power roller 4 between the disk 2 and the output disk 3 and a connecting oil passage 101 are provided, and a clamping pressure is provided via an opening 102 according to the operating state.
- a pressure release mechanism 100 capable of releasing the hydraulic pressure of the hydraulic oil in the generated hydraulic chamber 15a.
- the pressure release mechanism 100 is mounted on the vehicle so that the opening portion 102 is sandwiched from the clamping pressure generation hydraulic chamber 15a in the vertical direction. Located on the upper side.
- the toroidal continuously variable transmission 1 operates the hydraulic pressure mechanism 15 by the hydraulic pressure release mechanism 100 releasing the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a via the release portion 102 according to the operating state. Since it is possible to quickly reduce the clamping pressure of oil, the transmission of power between the input disk 2, the output disk 3 and the power roller 4 can be interrupted with high responsiveness, preventing unintended shifting. can do.
- the toroidal continuously variable transmission 1 has the opening 102 positioned at least vertically above the clamping pressure generating hydraulic chamber 15a, so that the hydraulic oil of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a is released.
- the toroidal continuously variable transmission 1 can quickly increase the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a when the clamping pressure of the hydraulic oil of the hydraulic pressing mechanism 15 is applied again.
- the clamping pressure for clamping the power roller 4 between the input disk 2 and the output disk 3 can be applied with good response. That is, in the toroidal continuously variable transmission 1, the pressure release mechanism 100 can release the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a via the opening 102, and the opening 102 can at least hold the clamping pressure generating hydraulic pressure.
- the toroidal continuously variable transmission 1 of the present embodiment for example, frictionally engages the trunnion 6 with a friction member to prevent the trunnion 6 from rotating around the rotation axis X3 and restrict the tilt of the power roller 4.
- the generation of wear powder on the friction member can be prevented, so that unintended shift can also be prevented appropriately in this respect.
- the pressure release mechanism 100 is provided via the release portion 102 when the engine 21 that generates the driving force is in a stopped state. While releasing the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a, the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a is blocked through the opening 102 when the engine 21 is in an operating state. It will be in the cut-off state. Therefore, the toroidal continuously variable transmission 1 is in an open state in which the pressure release mechanism 100 releases the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a via the open portion 102 when the engine 21 is stopped.
- the transmission of power between the input disk 2, the output disk 3 and the power roller 4 is cut off, so that the drive wheels 27 are rotated by towing or coasting of the vehicle on which the toroidal continuously variable transmission 1 is mounted. Even if the output disk 3 rotates, unintended shift can be prevented, and deterioration of startability due to insufficient torque can be prevented.
- the toroidal continuously variable transmission 1 has a shut-off state in which the pressure release mechanism 100 shuts off the release of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a via the release portion 102 when the engine 21 is in an operating state. As a result, power can be transmitted between the input disk 2, the output disk 3, and the power roller 4, so that the speed ratio changing unit 5 can appropriately change and fix the speed ratio.
- the pressure release mechanism 100 is temporarily stopped in the idling stop control in which the engine 21 that generates the driving force automatically stops the idling operation.
- the release state of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a through the opening 102 is set to a cutoff state. Therefore, in the toroidal-type continuously variable transmission 1, when the engine 21 is in a temporary stop state in the idling stop control, the release of the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a through the opening portion 102 is blocked.
- the toroidal continuously variable transmission 1 can quickly increase the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a when the engine 21 is restarted from the temporarily stopped state of the engine 21 in the idling stop control.
- the clamping pressure for clamping the power roller 4 between the input disk 2 and the output disk 3 can be applied more responsively.
- the toroidal continuously variable transmission 1 can shift to the shift control by the gear ratio changing unit 5 with higher responsiveness to the start of the engine 21 in the idling stop control. It is possible to prevent delays in restarting and restarting the vehicle equipped with 1.
- the pressure release mechanism 100 has one end side capable of communicating with the connection oil passage 101 and the other end side open opening 103a.
- a branched open oil passage 103 that forms the open portion 102 is provided. Therefore, the toroidal-type continuously variable transmission 1 has the opening 103a that forms the opening portion 102 positioned vertically above the pinching pressure generating hydraulic chamber 15a, thereby preventing unintentional shift and preventing the pinching pressure generating hydraulic chamber 15a. It is possible to achieve both a reduction in hydraulic pressure and a responsiveness of return, and accordingly, an unintended shift can be prevented appropriately.
- the pressure release mechanism 100 includes a closed state in which the clamping pressure generating hydraulic chamber 15a is connected to the hydraulic control device 9, and a clamping pressure.
- a switching valve 104 that can be switched to an open state in which the generated hydraulic chamber 15a is connected to the open portion 102 is provided. Therefore, the toroidal continuously variable transmission 1 is configured such that the switching valve 104 of the pressure release mechanism 100 is in a closed state in which the clamping pressure generating hydraulic chamber 15a is connected to the hydraulic control device 9, thereby causing the clamping pressure generating hydraulic pressure via the opening 102.
- It can be set as the interruption
- the switching valve 104 is configured by an electromagnetic valve that is closed when energized and opened when de-energized. . Therefore, the toroidal continuously variable transmission 1 is, for example, a power source that temporarily disconnects the solenoid 104a of the switching valve 104 or supplies current to the solenoid 104a while the vehicle on which the toroidal continuously variable transmission 1 is mounted. Even when an abnormality occurs in the part, the switching valve 104 shifts to the open state, and the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a immediately shifts to the state where the hydraulic oil is released via the opening part 102. As a result, the transmission of power between the input disk 2, the output disk 3 and the power roller 4 can be cut off, so that a sudden shift can be prevented from occurring.
- the switching valve 104 is located above the clamping pressure generating hydraulic chamber 15a with respect to the vertical direction when mounted on the vehicle. To position. Therefore, the toroidal continuously variable transmission 1 has the switching valve 104 positioned vertically above the clamping pressure generating hydraulic chamber 15a. For example, even if hydraulic oil leaks from the switching valve 104, the clamping pressure is generated. In the hydraulic chamber 15a, the connecting oil passage 101, and the hydraulic control device 9, the hydraulic oil can surely remain at least in a portion lower than the vertical position of the hydraulic oil leakage portion in the vertical direction.
- the transmission ratio changing unit 5 applies a shift control pressing force to the trunnion 6 that supports the power roller 4 by the hydraulic oil pressure.
- the power roller 4 together with the trunnion 6 is moved from the neutral position with respect to the input disk 2 and the output disk 3 to the shift position, and the power roller 4 is tilted.
- the hydraulic control device 9 generates a driving force.
- the oil pump 9 a that can pressurize the working oil is provided, and the pressure release mechanism 100 is an operation in which the shift control pressing force cannot act on the trunnion 6.
- the toroidal continuously variable transmission 1 is in an operation state in which the shift control pressing force cannot act on the trunnion 6 when the engine 21 is in a normal stop state and the drive of the oil pump 9a is in a stop state.
- the toroidal continuously variable transmission 1 is in an open state in which the pressure release mechanism 100 releases the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a via the release portion 102, whereby the input disk 2 and the output Since the transmission of power between the disk 3 and the power roller 4 is cut off, the traction of a vehicle equipped with the toroidal continuously variable transmission 1 when the shift control pressing force cannot act on the trunnion 6 is in operation. Even if the driving wheel 27 is rotated and the output disk 3 is rotated due to coasting or the like, unintended shift can be prevented, and startability can be prevented from deteriorating due to insufficient torque.
- continuously variable transmission according to the above-described embodiment of the present invention is not limited to the above-described embodiment, and various modifications can be made within the scope described in the claims.
- the continuously variable transmission has been described as a double-cavity toroidal continuously variable transmission.
- the present invention is not limited to this and may be a single-cavity toroidal continuously variable transmission.
- the hydraulic control means may be provided separately for the transmission ratio changing means and the clamping means.
- the pressurizing means is described as a mechanical oil pump that is driven in conjunction with the rotation of the output shaft of the drive source.
- the present invention is not limited to this and is an electric oil pump. May be. Even in this case, the continuously variable transmission of the present invention can appropriately prevent unintended shifts. That is, when the pressurizing means is an electric oil pump, regardless of the operating state of the drive source, the electric oil pump can apply a shift control pressing force to the support means.
- the predetermined shift control must be continuously executed while the vehicle is being towed, which may increase the power consumption.
- the pressure release mechanism 100 releases the hydraulic pressure of the hydraulic oil in the clamping pressure generating hydraulic chamber 15a via the release portion 102, and the input disk 2, the output disk 3 and power Since the transmission of power to and from the roller 4 is cut off, for example, it is not necessary to execute the shift control during towing of the vehicle, so that wasteful power consumption can be suppressed.
- the continuously variable transmission of the present invention can achieve both prevention of unintended shift and suppression of wasteful power consumption, and can appropriately prevent unintended shift.
- the switching means is described as being configured by an electromagnetic valve that is in a closed state when energized, and that is in an open state when not energized.
- the electromagnetic valve may be in a closed state when not energized, or may be configured with something other than the electromagnetic valve.
- the switching means is described as being located above the sandwiching pressure generating hydraulic chamber in the vertical direction in a state where it is mounted on the vehicle. It may be located on the lower side in the vertical direction from the clamping pressure generating hydraulic chamber.
- a part of the connecting oil passage is illustrated vertically above the sandwiching pressure generating hydraulic chamber.
- the present invention is not limited thereto. It may be located further downward in the vertical direction.
- the open opening 103a forming the open portion 102 is illustrated so as to face the lower side in the vertical direction, but may be provided so as to face the upper side in the vertical direction or the horizontal direction.
- the case where the drive source is in the stop state and the drive of the pressurizing means is in the stop state is described as an example where the shift control pressing force cannot act on the support means.
- the present invention is not limited to this.
- the seal member of each part in the hydraulic control means is damaged, the shift control pressing force cannot be applied to the support means.
- the hydraulic pressure of the hydraulic oil in the pressure generating hydraulic chamber may be released. Even in this case, the continuously variable transmission of the present invention can appropriately prevent unintended shifts.
- the continuously variable transmission according to the present invention can appropriately prevent an unintended shift, and the driving force from the internal combustion engine or the electric motor, which is a driving source, according to the traveling state of the vehicle. It is suitable for application to a continuously variable transmission that transmits to the road surface under optimal conditions.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Friction Gearing (AREA)
- Control Of Transmission Device (AREA)
Abstract
Description
2 入力ディスク
3 出力ディスク
4 パワーローラ
5 変速比変更部(変速比変更手段)
6 トラニオン(支持手段)
7 移動部
8 油圧ピストン部
9 油圧制御装置(油圧制御手段)
9a オイルポンプ(加圧手段)
10 入力軸
11 バリエータ軸
15 油圧押圧機構(挟圧手段)
15a 挟圧力発生油圧室
15b 挟圧押圧力ピストン
15c 導入排出口
21 エンジン(駆動源)
21a クランクシャフト(駆動源の出力軸)
60 ECU
100 圧力開放機構(圧力開放手段)
101 連結油路
101a 油圧室側油路
101b 制御装置側油路
102 開放部
103 分岐開放油路
103a 開放開口
104 切替弁(切替手段)
104a ソレノイド
104b 弾性部材
105 貯留部
図1は、本発明の実施形態に係るトロイダル式無段変速機の概略断面図、図2は、本発明の実施形態に係るトロイダル式無段変速機の要部の模式的構成図、図3は、本発明の実施形態に係るトロイダル式無段変速機が備えるパワーローラの入力ディスクに対する中立位置を説明する模式図、図4は、本発明の実施形態に係るトロイダル式無段変速機が備えるパワーローラの入力ディスクに対する変速位置を説明する模式図、図5は、本発明の実施形態に係るトロイダル式無段変速機の挟圧力発生油圧室への作動油供給系を示す概略構成図である。
なお、このロアリンク16a及びアッパリンク17aについては、後で詳細に説明する。
Claims (8)
- 駆動力が入力される入力ディスクと、
前記駆動力が出力される出力ディスクと、
前記入力ディスクと前記出力ディスクとの間に設けられるパワーローラと、
前記パワーローラを回転自在、かつ、傾転自在に支持すると共に、前記パワーローラを傾転させることで前記入力ディスクと前記出力ディスクとの回転速度比である変速比を変更可能な変速比変更手段と、
作動媒体の圧力を制御する油圧制御手段から連結油路を介して挟圧力発生油圧室に供給される当該作動媒体の圧力により前記入力ディスクと前記出力ディスクとの間に前記パワーローラを挟み込む挟圧力を作用可能な挟圧手段と、
前記連結油路に設けられ、運転状態に応じて開放部を介して前記挟圧力発生油圧室の前記作動媒体の圧力を開放可能な圧力開放手段とを備え、
前記圧力開放手段は、車両に搭載された状態で前記開放部が鉛直方向に対して前記挟圧力発生油圧室より上側に位置することを特徴とする、
無段変速機。 - 前記圧力開放手段は、前記駆動力を発生する駆動源が停止状態にある場合に前記開放部を介して前記挟圧力発生油圧室の前記作動媒体の圧力を開放する開放状態とする一方、前記駆動源が作動状態にある場合に前記開放部を介した前記挟圧力発生油圧室の前記作動媒体の圧力の開放を遮断する遮断状態とする、
請求項1に記載の無段変速機。 - 前記圧力開放手段は、前記駆動力を発生する駆動源がアイドリング運転を自動停止するアイドリングストップ制御における一時停止状態にある場合に前記開放部を介した前記挟圧力発生油圧室の前記作動媒体の圧力の開放を遮断する遮断状態とする、
請求項1に記載の無段変速機。 - 前記圧力開放手段は、一端側が前記連結油路と連通可能であると共に他端側の開口が前記開放部をなす分岐開放油路を有する、
請求項1に記載の無段変速機。 - 前記圧力開放手段は、前記挟圧力発生油圧室を前記油圧制御手段と接続する閉鎖状態と、前記挟圧力発生油圧室を前記開放部と接続する開放状態とに切り替え可能な切替手段を有する、
請求項1に記載の無段変速機。 - 前記切替手段は、通電時に前記閉鎖状態となる一方、非通電時に前記開放状態となる電磁弁により構成される、
請求項5に記載の無段変速機。 - 前記切替手段は、車両に搭載された状態で鉛直方向に対して前記挟圧力発生油圧室より上側に位置する、
請求項5に記載の無段変速機。 - 前記変速比変更手段は、前記パワーローラを支持する支持手段に前記作動媒体の圧力により変速制御押圧力を作用させることで該支持手段と共に前記パワーローラを前記入力ディスク及び前記出力ディスクに対する中立位置から変速位置に移動させ該パワーローラを傾転させるものであり、
前記油圧制御手段は、前記駆動力を発生する駆動源の出力軸の回転と連動して駆動することで、前記作動媒体を加圧可能な加圧手段を有し、
前記圧力開放手段は、前記支持手段に前記変速制御押圧力が作用不能な運転状態である場合に前記開放部を介して前記挟圧力発生油圧室の前記作動媒体の圧力を開放する開放状態とする、
請求項1に記載の無段変速機。
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CN2008801302020A CN102084158B (zh) | 2008-12-15 | 2008-12-15 | 无级变速器 |
US13/001,794 US20110105273A1 (en) | 2008-12-15 | 2008-12-15 | Continuously variable transmission |
JP2010542755A JP5136656B2 (ja) | 2008-12-15 | 2008-12-15 | 無段変速機 |
PCT/JP2008/072772 WO2010070718A1 (ja) | 2008-12-15 | 2008-12-15 | 無段変速機 |
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PCT/JP2008/072772 WO2010070718A1 (ja) | 2008-12-15 | 2008-12-15 | 無段変速機 |
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US (1) | US20110105273A1 (ja) |
JP (1) | JP5136656B2 (ja) |
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WO (1) | WO2010070718A1 (ja) |
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JP2012167790A (ja) * | 2011-02-16 | 2012-09-06 | Nsk Ltd | トロイダル型無段変速機及び無段変速装置 |
JP2014015988A (ja) * | 2012-07-09 | 2014-01-30 | Honda Motor Co Ltd | 車両の制御装置 |
JP2015021564A (ja) * | 2013-07-19 | 2015-02-02 | 本田技研工業株式会社 | トロイダル変速機構の制御装置 |
JP2016217419A (ja) * | 2015-05-19 | 2016-12-22 | 日本精工株式会社 | トロイダル型無段変速機 |
JP2017008992A (ja) * | 2015-06-18 | 2017-01-12 | 日本精工株式会社 | トロイダル型無段変速機 |
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US8285463B2 (en) * | 2009-08-11 | 2012-10-09 | GM Global Technology Operations LLC | Method and system for calibrating a pressure sensor for an automatic transmission |
JP5723312B2 (ja) * | 2012-03-23 | 2015-05-27 | 富士重工業株式会社 | 四輪自動車用のシフトバイワイヤ制御システム |
US9212743B2 (en) * | 2012-05-29 | 2015-12-15 | Gm Global Technology Operations, Llc | Containment control for a continuously variable transmission |
CN103470749B (zh) * | 2013-09-06 | 2015-08-26 | 浙江德孚力汽车变速箱有限公司 | 适用于锥环式无级变速器的故障保护装置 |
US11105417B2 (en) | 2013-10-23 | 2021-08-31 | Antonio Francisco Cesaroni | Traction system for hybrid vehicles |
ITPD20130292A1 (it) * | 2013-10-23 | 2015-04-24 | Antonio Francisco Cesaroni | Gruppo di trazione per veicoli ibridi |
JP6187914B2 (ja) * | 2014-04-23 | 2017-08-30 | 本田技研工業株式会社 | トロイダル型無段変速機 |
JP6505477B2 (ja) * | 2015-03-13 | 2019-04-24 | 川崎重工業株式会社 | 変速装置及びそれを備える発電システム |
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- 2008-12-15 JP JP2010542755A patent/JP5136656B2/ja not_active Expired - Fee Related
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JP5136656B2 (ja) | 2013-02-06 |
CN102084158A (zh) | 2011-06-01 |
CN102084158B (zh) | 2013-06-05 |
US20110105273A1 (en) | 2011-05-05 |
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