JP6791591B2 - Torque cam device and continuously variable transmission - Google Patents

Description

The present invention relates to a torque cam device suitable for use in a continuously variable transmission, and a continuously variable transmission provided with the torque cam device.

A system using a torque cam mechanism has been developed as a thrust generating mechanism of a speed change mechanism of a belt-type continuously variable transmission (see, for example, Patent Document 1).
This torque cam mechanism generates a thrust according to the rotational phase difference between the two cam members, and each cam member is formed with a cam slope inclined in the axial direction with respect to an annular surface orthogonal to the rotation axis. When the two cam members slide each other on the cam slopes and rotate relative to each other, the cam members are separated from each other and their total length (axial length) changes. As a result, a force (thrust) in the direction of the rotation axis is generated, and torque is transmitted.

The transmission mechanism of the vehicle transmits torque in two modes, a drive state in which torque is transmitted from the drive source side to the wheel side and a coast state in which torque is transmitted from the wheel side to the drive source side. It is equipped with a first torque cam mechanism and a second torque cam mechanism corresponding to the coast state, and these are used properly according to the torque transmission state.

However, in the torque cam mechanism that switches from the state in which power is not transmitted to the state in which power is transmitted when these two torque cam mechanisms are switched, a time lag or shock occurs in torque transmission due to backlash between the cam members. That is, when torque is transmitted by one torque cam mechanism, the two cam members do not follow each other in the rotational direction in the other torque cam mechanism. Therefore, in order to transmit torque by the other torque cam mechanism, 2 It is necessary to rotate one cam member relative to the required amount. Therefore, a time lag occurs in torque transmission while the two cam members are relatively rotated, and a torque shock occurs because the two cam members are instantly in the torque transmission state after the relative rotation.

Patent Document 1 also proposes a technique for suppressing the occurrence of a time lag or a shock in torque transmission when the torque cam mechanism is switched. In this technology, even when the torque cam mechanism does not transmit torque, the cam surfaces of the two cam members are pressed against each other by a spring so that the rotational phases of the two cam members follow each other, and the backlash between the cam members is performed. I'm trying to suppress.

Japanese Unexamined Patent Publication No. 2006-300123

However, in the technique of Patent Document 1, since the cam slopes of the two cam members are only pressed against each other by the spring, it is considered that the follow-up cannot be reliably performed and the backlash increases from various points.

That is, when the sliding resistance between the cam slopes is large, the urging force of the spring is insufficient and the follow-up operation becomes difficult. Further, if the relative rotation amount of the two cam members is set to be large, the required follow-up amount (rotation for follow-up) increases and the follow-up operation becomes difficult. Further, the follow-up operation becomes difficult even when the vehicle is accelerating. It is considered that the backlash increases when the tracking cannot be performed reliably in this way.

The present invention has been devised in view of this problem, and includes a torque cam mechanism that transmits torque in the forward direction and a torque cam mechanism that transmits torque in the reverse direction, even when the torque cam mechanism does not transmit torque. An object of the present invention is to provide a torque cam device and a stepless transmission provided with the torque cam device, which can suppress the occurrence of backlash between two cam members of the torque cam mechanism.

(1) The torque cam device of the present invention is connected to an input rotating element, serves as an input side when torque is forwardly transmitted from the input rotating element to the output rotating element, and has a spiral first drive cam slope. 1 The input side cam member and the output rotating element are supported so as to be non-movable in the axial direction and relatively rotatable, and serve as the output side when the torque is transmitted in the forward direction, and the first drive cam slope and the transmission torque become the same. A first torque cam mechanism composed of a first output-side cam member having a spiral first driven cam slope that slides in contact with a corresponding force, and a support that is axially immovable and relative to the output rotating element. , It becomes the output side when torque is transmitted from the output rotating element to the input rotating element in the opposite direction, and is connected to the input rotating element with a second output side cam member having a spiral second driving cam slope. It is an input side when transmitting torque in the opposite direction, and is composed of a second input side cam member having a spiral second driven cam slope that is in sliding contact with the second drive cam slope with a force corresponding to the transmission torque. A pinion carrier interposed between the second torque cam mechanism, the input rotating element and the output rotating element, and connected to the input rotating element so as to be relatively non-rotatable and axially movable, and the output rotating element. A planetary gear mechanism including a connected ring gear and a sun gear, and when torque is transmitted in the forward direction, the first output side cam member is connected to the output rotating element so as not to rotate relative to the second output side cam member. And the sun gear are connected, and when torque is transmitted in the opposite direction, the second output side cam member is connected to the output rotating element so as not to rotate relative to the output rotating element, and the first output side cam member and the sun gear are connected. It is characterized by having a switching mechanism.

(2) The switching mechanism is connected to the output rotating element so as to be relatively non-rotatable and axially movable, and the first output-side cam member and the second output-side cam member are connected by axial movement. A fork member that is connected to the output side cam member and releases the other output side cam member, and the other output side cam member that is supported by the fork member so as to be relatively rotatable and axially immovable, and the other output side cam member to the sun gear. It is preferable to have a meshing ring member to be connected.

(3) The continuously variable transmission of the present invention includes a primary pulley, a secondary pulley, a belt-shaped member hung around the primary pulley and the secondary pulley, and a first thrust applying mechanism for applying thrust to the primary pulley. And a second thrust applying mechanism for applying thrust to the secondary pulley, and at least one of the first thrust applying mechanism and the second thrust applying mechanism is equipped with the torque cam device described in the previous stage. It is characterized by being.

According to the present invention, when the first torque cam mechanism transmits torque in the forward direction, the second output side cam member of the second torque cam mechanism is connected to the sun gear of the planetary gear mechanism with respect to the rotation of the input rotating element. Since the speed is increased, the second output side cam member can be brought close to or in contact with the second input side cam member, and backlash occurs between the second input side cam member and the second output side cam member. Is suppressed.
Further, when the second torque cam mechanism transmits torque in the opposite direction, the first output side cam member of the first torque cam mechanism is connected to the sun gear of the planetary gear mechanism and is accelerated with respect to the rotation of the input rotating element. Therefore, the first output side cam member can be brought close to or in contact with the first input side cam member, and the occurrence of backlash between the first input side cam member and the first output side cam member is suppressed. ..
In this way, the occurrence of backlash between the input side cam member and the output side cam member is suppressed, so that the occurrence of a torque transmission time lag and the occurrence of torque shock are suppressed when the torque transmission direction is switched. Toque.

It is a schematic block diagram of the continuously variable transmission which concerns on embodiment of this invention. It is sectional drawing of the torque cam device which concerns on embodiment of this invention. It is a perspective view which shows each torque cam mechanism of the torque cam device which concerns on embodiment of this invention by being disassembled by the input side cam member and the output side cam member, (a) shows the 1st torque cam mechanism, (b). Indicates a second torque cam mechanism. FIG. 2 is an enlarged view showing a portion surrounded by the alternate long and short dash line X. FIG. 2 is a cross-sectional view taken along the line YY.

Hereinafter, embodiments of the torque cam device according to the present invention and the continuously variable transmission for a vehicle equipped with the torque cam device will be described with reference to the drawings. Although the case where the vehicle is an electric vehicle whose drive source is an electric motor is illustrated here, the drive source of the vehicle may be an engine, and the vehicle is a hybrid whose drive source is an engine and an electric motor. It may be a car. In addition, the embodiments shown below are merely examples, and there is no intention of excluding the application of various modifications and techniques not specified in the following embodiments. Such an embodiment can be partially used, partially modified, or replaced with another mechanism or device having the same function.

FIG. 1 is a configuration diagram schematically showing a continuously variable transmission according to the present embodiment, and a drive source 2 including an internal combustion engine (engine) for running a vehicle, an electric motor, etc. is provided with a planetary gear mechanism or the like. The rotating shaft 10 coupled to the fixed sheave 8 of the primary pulley 6 of the continuously variable transmission 5 is connected via the configured forward / backward switching mechanism 4. A movable sheave 12 having a sheave surface that forms a V-shaped groove of a pulley facing the sheave surface of the fixed sheave 8 is arranged on the rotating shaft 10 so as to be slidable in the axial direction and non-relatively rotatable. There is.

Further, a drive wheel (not shown) is connected to the drive shaft 18 coupled to the fixed sheave 16 of the secondary pulley 14 of the continuously variable transmission 5 via a differential mechanism or the like, and the fixed sheave 16 is connected to the drive shaft 18. A movable sheave 20 having a sheave surface that forms a V-shaped groove of the pulley facing the sheave surface of the above is arranged so as to be slidable in the axial direction and non-relatively rotatable.

Further, a spring 22 for applying an urging force in the direction of narrowing the V-shaped groove and a torque cam device 90 are interposed between the sheaves 16 and 20 of the secondary pulley 14.
A belt 26 is wound between the pulleys 6 and 14.
Further, the spring 22 and the torque cam device 90 function as a thrust adjusting mechanism for adjusting the thrust of the secondary pulley 14 to adjust the pinching pressure of the belt 26.

Note that FIG. 1 shows the gear ratios of the primary pulley 6, the secondary pulley 14 and the belt 26 on the low side and the high side. Each outer half of the primary pulley 6 and the secondary pulley 14 shows the low side state, and each inner half shows the high side state. Regarding the belt 26, the state on the low side is shown by a solid line, and the state on the high side is shown by a broken line. However, the high state shown by the broken line only indicates the positional relationship between the pulley and the belt in the radial direction, and the actual belt position does not appear in the inner half of the pulley.

On the back surface (the surface opposite to the sheave surface) 13 side of the movable sheave 12 of the primary pulley 6, a mechanical pulley moving mechanism 30 that moves the movable sheave 12 in the axial direction to adjust the gear ratio is arranged. .. Although the mechanical pulley moving mechanism 30 is described in an extremely simplified manner in FIG. 1, the mechanical pulley moving mechanism 30 includes a torque cam mechanism 40 having a drive cam 42 and a fixed cam 44 connected to the movable sheave 12. It is provided with two power transmission mechanisms 50 and 60 for transmitting power from the electric motor 70 as an actuator to the torque cam mechanism 40.

The torque cam device 90 according to the present embodiment is mounted on the secondary pulley 14 of such a continuously variable transmission as a thrust generating mechanism.
Hereinafter, the torque cam device 90 will be described.

As shown in FIGS. 1 to 3, the torque cam device 90 of the present embodiment has a movable sheave 20 of the secondary pulley 14 as an input rotating element, a fixed sheave 16 of the secondary pulley 14 as an output rotating element, and a rotating shaft 18. It is intervened in between. The torque cam device 90 includes a first torque cam mechanism 91 that generates thrust and transmits torque during drive travel in which torque is forwardly transmitted from the movable sheave 20 which is an input rotating element to the rotating shaft 18 which is an output rotating element. , A second torque cam mechanism 92 that generates thrust and transmits torque during coastal travel in which torque is transmitted in the opposite direction from the rotating shaft 18 that is the output rotating element to the movable sheave 20 that is the input rotating element is arranged in parallel. The first torque cam mechanism 91 is arranged on the inner peripheral side of the second torque cam mechanism 92.

The first torque cam mechanism 91 is connected to the cylindrical (cylindrical body) first input side cam member 91A fixed to the movable sheave 20 of the secondary pulley 14 via the switching mechanism 80 described in detail later on the rotating shaft 18. It has a cylindrical (cylindrical body) first output side cam member 91B that can be provided, and as shown in FIG. 3A, the first input side cam member 91A has one end (upper end in the drawing). ) Is fixed to the movable sheave 20, and has a spiral first drive cam slope 91a at the other end.

On the other hand, the first output side cam member 91B is formed with a spiral first driven cam slope 91b facing the first driven cam slope 91a at one end, and has a gap at the other end along the circumferential direction. The annular first clutch member 91D is connected via the four connecting members 91C arranged therein. Spline teeth 91E (see FIG. 4) are formed on the outer peripheral surface of the first clutch member 91D so that they can mesh with the switching mechanism 80.

The first driven cam slope 91a and the first driven cam slope 91b are spiral slopes extending in the circumferential direction at the same angle, and these cam slopes 91a and 91b are via balls (not shown). It slides smoothly. Here, two cam slopes 91a and 91b are provided with the phase angles shifted by 180 degrees.

When the first input side cam member 91A rotates in the direction indicated by the arrow A1 in the drawing, the first drive cam slope 91a comes into pressure contact with the first driven cam slope 91b from the first input side cam member 91A to the first output side. Rotational torque is transmitted to the cam member 91B. At this time, the pressure contact force between the first driven cam slope 91a and the first driven cam slope 91b acts in the direction of axially separating the first input side cam member 91A and the first output side cam member 91B. However, as will be described in detail later, the other end of the first output side cam member 91B cannot move relative to the rotating shaft 18 in the axial direction, so that the pressure contact force is applied to the movable sheave 20. It becomes. Since the reaction force from the belt 26 with respect to this thrust is applied to the movable sheave 20, the total length of the first input side cam member 91A and the first output side cam member 91B has a length that balances this thrust.

The second torque cam mechanism 92 is provided so as to be connectable to the rotary shaft 18 via the switching mechanism 80 with the cylindrical (cylindrical) second input side cam member 92A fixed to the movable sheave 20 of the secondary pulley 14. It has a cylindrical (cylindrical body) second output side cam member 92B, and as shown in FIG. 3B, the second input side cam member 92A has a movable sheave at one end (upper end in the drawing). It is fixed to 20 and has a spiral second drive cam slope 92a at the other end.

On the other hand, the second output side cam member 92B is formed with a spiral second driven cam slope 92b facing the second drive cam slope 92a at one end and a large diameter second clutch member 92D at the other end. Has been done. Similar to the first clutch member 91D, spline teeth 92E (see FIG. 4) are formed on the outer peripheral surface of the second clutch member 92D so that they can mesh with the switching mechanism 80.

The second driven cam slope 92a and the second driven cam slope 92b are spiral slopes extending in the circumferential direction at the same angle, and these cam slopes 92a and 92b are via balls (not shown). It slides smoothly. Here, two cam slopes 92a and 92b are provided with the phase angles shifted by 180 degrees.

When the second output side cam member 92B rotates in the direction indicated by the arrow A2 in the drawing, the second drive cam slope 92b is pressed against the second driven cam slope 92a and input from the second output side cam member 92B. Rotational torque is transmitted to the side cam member 92A. At this time, the pressure contact force between the second driven cam slope 92b and the second driven cam slope 92a acts in the direction of axially separating the second input side cam member 92A and the second output side cam member 92B. However, since the other end of the second output side cam member 92B cannot move relative to the rotating shaft 18 in the axial direction, the pressure contact force becomes a thrust force applied to the movable sheave 20. Since the reaction force from the belt 26 with respect to this thrust is applied to the movable sheave 20, the total length of the second input side cam member 92A and the second output side cam member 92B has a length that balances this thrust.

As shown in FIGS. 1 and 2, the torque cam device 90 further includes a switching mechanism 80 and a planetary gear mechanism 100 interposed between the two torque cam mechanisms 91 and 92 and the rotating shaft 18 as an output rotating element. I have. The rotating shaft 18 as an output rotating element includes a diameter-expanded portion 18A at its output side end (left end in the figure) and a connecting drum 18B extending from the outer peripheral portion of the diameter-expanded portion 18A in the movable sheave 20 direction. The switching mechanism 80 and the planetary gear mechanism 100 are arranged on the inner peripheral side of the connecting drum 18B.

As shown in FIG. 4, the switching mechanism 80 includes a fork member 82 and a ring member 84.
The fork member 82 is an annular shape having a body portion 82a formed of a cylinder coaxial with the rotating shaft 18 and a body portion 82a projecting outward from the axially intermediate portion of the body portion 82a and having spline teeth 82b formed on the outer peripheral surface. Two arm portions 82e, 82g, which are projected inward from both ends of the leg portion 82c and the body portion 82a in the axial direction and have spline teeth 82d, 82f formed on the inner peripheral surface, and a shaft of the body portion 82a. It is provided with an annular engaging portion 82h projecting inward from the intermediate portion in the direction. Then, the fork member 82 rotates relative to the connecting drum 18B (that is, the rotation shaft 18) by engaging the spline teeth 82b of the leg portion 82c with the spline teeth 18C formed on the inner peripheral surface of the connecting drum 18B. It is supported so that it is impossible and can move relative to the axial direction.

The ring member 84 is projected inward from both ends of the cylindrical body portion 84b in which an annular groove 84a fitted to the engaging portion 82h is formed on the outer peripheral surface in the axial direction. It is provided with two arm portions 84e and 84g having spline teeth 84d and 84f formed on the inner peripheral surface. Further, the ring member 84 is supported by the fork member 82 so as to be relatively rotatable and unable to move in the axial direction by fitting the groove 84a into the engaging portion 82h.

On the other hand, the planetary gear mechanism 100 is composed of a simple planetary gear having a ring gear 100R, a pinion gear 100P, a sun gear 100S, and a carrier 100C supporting the pinion gear 100P. The ring gear 100R is fixedly connected to the connecting drum 18B, and the carrier The 100c is supported by the shaft end (left end in the figure) of the rotary support shaft 18B connected to the movable pulley 20 via the spline mechanism 18A so as to be relatively non-rotatable and relatively movable in the axial direction, whereby the shaft of the movable pulley 20 is supported. Directional movement is allowed.

Further, a connecting shaft 120 for connecting the sun gear 100S to the switching mechanism 80 is coupled to the sun gear 100S, and a disk projecting outward from the axially intermediate portion of the connecting shaft 120. A disk-shaped third clutch member 120B is provided with a shaped flange 120A and a disk-shaped third clutch member 120B projecting outward from the shaft end and having spline teeth 120C (see FIG. 4) formed on the outer peripheral surface.

Further, as shown in FIG. 5, the third clutch member 120B is provided with four arcuate holes 120D having intervals on the same diameter in the radial intermediate portion thereof, and the holes 120D are bored. The connecting member 91C of the first output side cam member 91B penetrates.
As is clear from FIG. 5, since the arc length of the hole 120D is set longer than the arc length of the connecting member 91C, the connecting member 91C can move within the range of the arc length of the hole 120D.
The relationship between the arc length of the hole 120D and the arc length of the connecting member 91C is such that when the connecting member 91C abuts or approaches the inner wall of either one of the holes 120D, the first input side cam member 91A and the first It is preferable that the length ratio is such that the output side cam member 91B is in contact with the cam member 91B (that is, the backlash between the cam members 91A and 91B is eliminated).

As shown in FIG. 2, between the inner side surface 18C of the enlarged diameter portion 18A and one side surface 100C1 of the carrier 100C, between the other side surface 100C2 of the carrier 100C and the shaft end surface of the connecting shaft 120, the side surface of the clutch 120A and the first surface. Thrust bearings 25A, 25B, 25C, and 25D are interposed between the side surface of the clutch member 91D and between the side surface of the third clutch member 120B and the side surface of the second clutch member 92D, respectively. The first and second output side cam members 91B and 92B are supported so as not to be relatively movable in the axial direction with respect to the rotation shaft 18 which is an output rotation element.

Here, the operation mode of the switching mechanism 82 will be described.
The fork member 82 is slidably driven in the axial direction by an actuator (not shown), and in a state in which torque is transmitted in the forward direction, that is, in a driving running state of the vehicle, the fork member 82 is driven to the position shown in FIG. The spline teeth 82f of the first clutch member 91D are meshed with the spline teeth 91E of the first clutch member 91D to connect the first output side cam member 91B to the connecting drum 18B (rotating shaft 18) so as not to rotate relative to each other, and the spline teeth 84f of the ring member 84 are connected. The spline tooth 120C of the third clutch member 120B is meshed, the spline tooth 84d is meshed with the spline tooth 92E of the second clutch member 92D, and the second output side cam member 92B is connected to the sun gear 100S.

In this state, the first torque cam mechanism 91 executes torque transmission, and the second torque cam mechanism 92 does not contribute to torque transmission. Therefore, in the configuration of the conventional torque cam device that does not have the configuration as in this embodiment, the second output The side cam member 92B is in a free state, the rotation is slowed down due to the influence of drag friction and the like, and the backlash is increased apart from the second input side cam member 92A.
On the other hand, according to the configuration of the present embodiment, since the second output side cam member 92B is connected to the sun gear 100S, the rotation of the second output side cam member 92B is equal to the gear ratio of the planetary gear mechanism 100. 2 The speed is increased with respect to the rotation of the input side cam member 92A, and both cam members 92A and 92B can be brought close to each other to suppress or eliminate the occurrence of backlash.

Further, in the state where the torque is transmitted in the opposite direction, that is, in the coast running state of the vehicle, the spline teeth 82d of the arm portion 82e are moved to the left from the position shown in FIG. 4, and the spline teeth 82d of the arm portion 82e are moved to the second clutch member 92D. The second output side cam member 92B is meshed with the spline tooth 92E so as to be non-rotatably connected to the connecting drum 18B (rotating shaft 18), and the spline tooth 84d of the ring member 84 is meshed with the spline tooth 120C of the third clutch member 120B. Then, the spline teeth 84f are engaged with the spline teeth 91E of the first clutch member 91D, and the first output side cam member 91B is connected to the sun gear 100S.

In this state, the second torque cam mechanism 92 executes torque transmission and the first torque cam mechanism 91 does not contribute to torque transmission, but the first output side cam member 91B is connected to the sun gear 100S to accelerate the speed. Therefore, the occurrence of backlash between the first input side cam member 91A and the first output side cam member 91B is suppressed or eliminated.

Next, the operation of the torque cam device 90 according to the present embodiment will be described.
In the continuously variable transmission 5, when the input torque transmitted from the belt 26 to the secondary pulley 14 is strengthened during driving of the vehicle, the belt pinching pressure of the secondary pulley 14 becomes insufficient, and the fixed sheave 18 of the secondary pulley 14 becomes the belt 26. Causes slippage. However, since the movable pulley 20 that can move relative to the rotating shaft 18 follows the belt 26, the fixed sheave 16 causes a rotational phase lag with respect to the movable sheave 20.

At this time, since the first output side cam member 91B of the first torque cam mechanism 91 is driven and connected to the rotating shaft 16 via the switching mechanism 80, the first input side cam member 91A that rotates integrally with the movable sheave 20 While sliding the first driven cam slope 91a and the first driven cam slope 91b via a ball (not shown), while rotating relative to the first output side cam member 91B which rotates integrally with the fixed sheave 16. , A movable sheave that moves so as to be axially separated from the first output side cam member 91B (that is, in a direction that expands the total length of the first input side cam member 91A and the first output side cam member 91B). Bring 20 closer to the fixed sheave 16. As a result, the groove width of the V groove of the secondary pulley 14 is narrowed and the thrust of the secondary pulley 14 is strengthened, so that the belt pinching pressure is strengthened and the slip of the fixed sheave 16 is eliminated.

On the other hand, when the drive source acts on a negative input torque (braking torque) when the vehicle is traveling on the coast, the rotation phase delay of the fixed sheave 16 is eliminated, and the belt pinching pressure of the secondary pulley 14 with respect to the negative input torque. If the amount is insufficient, the fixed sheave 16 causes a rotational phase advance with respect to the movable sheave 20 (conversely, the movable sheave 20 causes a rotational phase delay with respect to the fixed sheave 16).

At this time, since the second output side cam member 92B of the second torque cam mechanism 92 is driven and connected to the rotating shaft 18, the second output side cam member 92B that rotates integrally with the fixed sheave 16 is placed via a ball (not shown). While sliding the 2 drive cam slope 92b and the 2nd driven cam slope 91b, the 2nd input side cam member rotates relative to the 1st output side cam member 92B which rotates integrally with the fixed sheave 16. The movable sheave 20 approaches the fixed sheave 16 by moving so as to be axially separated from the 92A (that is, in the direction of expanding the total length of the second input side cam member 92A and the second output side cam member 92B). Let me. As a result, the groove width of the V groove of the secondary pulley 14 is narrowed and the thrust of the secondary pulley 14 is strengthened, so that the belt pinching pressure is strengthened and the slip of the fixed sheave 16 is eliminated.

Since neither the driving torque nor the braking torque acts when the vehicle is stopped, the thrust of the pulley by the torque cam device 90 is not applied. Since the present device is equipped with a coil spring 22 that urges the movable pulley 20 in the direction approaching the fixed pulley 16, the belt 26 is prevented from slipping even during the initial drive such as when the vehicle starts. It can be securely clamped.

Since the continuously variable transmission 5 according to the present embodiment is configured as described above, the torque cam device 90 is used to transmit the drive torque at an appropriate gear ratio while applying thrust to the secondary pulley 14.

In the torque cam device 90, in the torque cam mechanism that does not contribute to torque transmission, the output side cam member is connected to the sun gear of the planetary gear mechanism, and the input side cam member is always connected to the carrier of the planetary gear mechanism. Since the speed is increased and rotated, the effect of suppressing or eliminating the occurrence of backlash between the input side cam member and the output side cam member can be obtained.
Therefore, for example, when the traveling state of the vehicle is switched from the driving traveling to the coast traveling, the switching mechanism 80 drives and connects the second output side cam member 92B to the rotating shaft 18 to bring the second torque cam mechanism into the torque transmission state. Since the backlash between the second input side cam member 92A and the second output side cam member 92B is suppressed or eliminated, the torque shock associated with the switching can be suppressed or prevented. Further, even when the running state is switched from the coast running to the driving running, the torque shock can be similarly suppressed or prevented.

Although the embodiments have been described above, the present invention can be implemented by appropriately modifying each embodiment.
For example, in the above embodiment, the torque cam device is provided on the secondary pulley side, but the torque cam device may be provided on the primary pulley side.
Further, the torque cam device of the present invention and the continuously variable transmission provided with the torque cam device are suitable for use as a transmission for a vehicle, but can also be applied to various other power transmission systems.

2 Drive source 5 Continuously variable transmission 6 Primary pulley 14 Secondary pulley 16 Fixed pulley (output rotating element)
20 Movable pulley (input rotating element)
80 Switching mechanism 82 Fork member 84 Ring member 90 Torque cam device 91 1st torque cam mechanism 91A 1st input side cam member 91a 1st drive cam slope 91B 1st output side cam member 91b 1st driven cam slope 92 2nd torque cam mechanism 92A 2nd input side cam member 92a 2nd driven cam slope 92B 2nd output side cam member 92b 2nd drive cam slope 100 Planetary gear mechanism 100C Carrier (pinion carrier)
100R ring gear 100S sun gear

Claims (3)

A first input side cam member which is connected to an input rotation element and serves as an input side when torque is forwardly transmitted from the input rotation element to the output rotation element and has a spiral first drive cam slope, and the output rotation. A spiral first that is supported so that it cannot move in the axial direction and can rotate relative to the element, becomes the output side when torque is transmitted in the forward direction, and is in sliding contact with the first drive cam slope with a force corresponding to the transmission torque. 1 A first torque cam mechanism composed of a first output side cam member having a driven cam slope, and
It is supported so that it cannot move in the axial direction and can rotate relative to the output rotating element, and serves as an output side when torque is transmitted from the output rotating element to the input rotating element in the opposite direction, and is a spiral second drive cam slope. A spiral shape that is connected to the input rotating element and serves as an input side when transmitting torque in the opposite direction, and is in sliding contact with the second drive cam slope with a force corresponding to the transmission torque. A second torque cam mechanism composed of a second input side cam member having a second driven cam slope of
A pinion carrier interposed between the input rotating element and the output rotating element, which is connected to the input rotating element so as to be relatively non-rotatable and axially movable, and a ring gear connected to the output rotating element. A planetary gear mechanism consisting of a sun gear and
When torque is transmitted in the forward direction, the first output side cam member is connected to the output rotating element so as not to rotate relative to the output rotating element, and the second output side cam member and the sun gear are connected to transmit torque in the opposite direction. The torque cam device is characterized by comprising a switching mechanism for connecting the second output side cam member to the output rotating element so as not to rotate relative to the output rotating element and connecting the first output side cam member and the sun gear. The switching mechanism
It is connected to the output rotating element so as to be relatively non-rotatable and axially movable, and is connected to the output-side cam member of either the first output-side cam member or the second output-side cam member by axial movement. A fork member that releases the other output side cam member,
The first aspect of the present invention, wherein the fork member is supported so as to be relatively rotatable and relatively immovable in the axial direction, and is provided with a meshing ring member for connecting the other output side cam member to the sun gear. Torque cam device. With the primary pulley
With the secondary pulley
The primary pulley and the belt-shaped member hung around the secondary pulley,
A first thrust applying mechanism that applies thrust to the primary pulley,
A second thrust applying mechanism for applying thrust to the secondary pulley is provided.
A continuously variable transmission characterized in that at least one of the first thrust applying mechanism and the second thrust applying mechanism is equipped with the torque cam device according to claim 1 or 2.

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