JP2001116096A - Toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a durable toroidal type continuously variable transmission for preventing looseness of trunnions by fitting/supporting both end parts of the trunnions to/by a casing. SOLUTION: Large force such as separating force acting on trunnions 33, 37 for rotatably supporting power rollers 6, 9 of a toroidal type continuously variable transmission is supported by a yoke 80 swingably extended between opposed end parts 65, 65. Since an integrally protrusively formed rod 70 is fitted to a fitting part 72 formed in a casing 25 in both end parts 65 of the trunnions 33, 37 via a radial bearing 71 such as a sliding bearing, the turnnions 33, 37 do not cause looseness, and a contact point of power rollers 6, 9 and an input/output disk do not become unstable so that durability is improved.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an input disk having a toroidal curved surface and an output disk, in which a power roller is tiltably disposed, and the rotation of the input disk is steplessly changed and transmitted to the output disk. To a toroidal type continuously variable transmission.

[0002]

2. Description of the Related Art Conventionally, as a toroidal type continuously variable transmission,
An input disk driven by the input shaft, an output disk disposed opposite to the input disk and connected to the output shaft, and a power roller frictionally contacting the two disks constitute a toroidal transmission unit, and a tilt angle of the power roller Is known, the rotation of the input disk is steplessly changed and transmitted to the output disk.

FIG. 3 is a sectional view showing an example of a conventional double-cavity toroidal type continuously variable transmission in which two sets of toroidal transmission portions 1 and 2 are arranged in parallel on the same shaft. With respect to the input shaft 13 to which the torque output to the output shaft of the engine is input via a torque converter or the like, the toroidal transmission units 1 and 2 respectively have the input disks 4 and 7 driven by the input shaft 13 and the input disks 13. Output disks 5, 8 arranged opposite the disks 4, 7 and connected to the output shaft 22, and input disks 4, 7 and output disks 5, 8
And a pair of power rollers 6, 6 and 9, 9 frictionally engaging the toroidal surfaces of the disks 4, 5 and 7, 8. Each power roller 6, 9 is rotatable about its own rotation axis 10 and is capable of tilting movement about a tilt axis 11 perpendicular to the rotation axis 10. By simultaneously changing the tilt angles of the power rollers 6, 9, the rotation of the input disks 4, 7 is transmitted to the output disks 5, 8 by continuously changing the rotation according to the tilt angle of the power rollers 6, 9. Is done.

In the toroidal transmission section 1, the input disk 4 is attached to one end of a main shaft 3 disposed on the same axis as the input shaft 13 via a ball spline 12, and is movable in the axial direction of the main shaft 3. And can rotate integrally with the main shaft 3. The distal end portion 14 of the input shaft 13 is fitted to and supported by a center hole 15 formed at one end of the main shaft 3 by, for example, a bearing so as to be relatively rotatable. The input flange 16 formed at the tip of the input shaft 13 and the loading cam 18 disposed opposite to the input flange 16 are provided with claws 17 and 19 that mesh with each other.
Part of the torque from the engine is
7, 19 and the input shaft 1 via the loading cam 18.
3 to the input disk 4. When transmitting torque,
By the action of the cam roller 36 of the loading cam 18,
A thrust corresponding to the transmission torque is generated as a pressing force acting between the input disk 4, the power roller 6, and the output disk 5.

[0005] The input disk 7 of the toroidal transmission 2 is
It is attached to the other end of the main shaft 3 via a ball spline 28. The input disk 7 is a ball spline 2
Since they are connected to the main shaft 3 via the respective shafts 8, they rotate integrally with the main shaft 3 but are slidable in the thrust direction of the main shaft 3. The remainder of the torque from input shaft 13 is transmitted to input disk 7. As a reaction of the thrust force in the toroidal transmission unit 1 by the cam roller 36, a thrust reaction force corresponding to the transmission torque is transmitted to the toroidal transmission unit 2 via the main shaft 3, and the input disk 7, the power roller 9, and the output of the toroidal transmission unit 2 A pressing force is applied between the rotating elements of the disk 8. The power transmission between the input disks 4, 7 and the output disks 5, 8
This is performed based on the shearing force of oil sandwiched between the power rollers 5, 9, 8 and the power rollers 6, 9.

The output disks 5 and 8 have their backs connected to cylindrical portions 22A provided on both sides of the output shaft 22 by spline fitting or the like, and rotate integrally. The output shaft 22 is a hollow shaft fitted to the main shaft 3, and a sprocket 2 is provided at an intermediate portion of the hollow shaft.
3 are integrally formed. The output disks 5, 8
The two rear surfaces are supported by the wall 26 of the casing 25 by the ball bearings 24 that support the loads in the thrust direction and the radial direction via the output shaft 22 so that the casing 2
5 regulates in the axial direction.

The other end of the main shaft 3 is connected to a casing 25 by a bearing 2.
7 so as to be rotatable. Input disk 7
A disc spring 29 is mounted in a compressed state by tightening a nut 31 using the sun gear 30 as a spacer. The repulsive force of the disc spring 29 presses the input disk 7 against the output disk 8 via the power roller 9 in the toroidal transmission portion 2, and urges the main shaft 3 rightward in FIG. Acting on the loading cam 18 via the bearing 20 and the bearing 21, the input disk 4 is pressed against the output disk 5 via the power roller 6 in the toroidal transmission unit 1.
Thus, the gap between the rotating elements is absorbed.

The power rollers 6 and 9 are rotatably supported by trunnions 33 and 37 by rotating shafts 34 and 38, respectively. The trunnions 33, 37 are displaced in the axial direction of the tilt shaft 11 with respect to the casing 25 by a hydraulic actuator described later, and the power rollers 6, 9 and the input / output disk 4 are moved in accordance with the axial displacement of the tilt shaft 11. , 5, 7, and 8, the tilting shaft 11 receives the tilting force from the input / output disks 4, 5, 7, 8
Can be turned around. When the power rollers 6 and 9 are tilted, the tilt angle displacement amount θ of the power rollers 6 and 9 becomes the turning displacement of the trunnions 33 and 37 about the tilt axis 11 as it is.

The rotation of the output shaft 22 is transmitted from, for example, a sprocket 23 fixed to the output shaft 22 to a counter shaft via a chain transmission, and the forward rotation is transmitted via a suitable gear mechanism to the transmission output shaft. (Not shown). As for the rotation of the input shaft 13, the reverse rotation is output from the planetary gear mechanism (not shown) with the reverse clutch to the transmission output shaft directly from the main shaft 3 via the sun gear 30. The main shaft 3 has an oil passage 32 extending in the axial direction, and the oil passage 32 constitutes a passage for lubricating oil. The oil passage 32 is branched to form a toroidal curved surface of each of the toroidal transmission portions 1 and 2,
2. Lubricating oil is supplied to the ball bearings 24 and the like.

The input disks 4, 7 and the output disks 5,
8 is a power roller 6, 9 and an input / output disk 4, 5,
When the point of contact with 7, 8 changes, the main shaft 3 is displaced in the axial direction. The reference of the axial position of the toroidal transmission units 1 and 2 is determined by a casing 25 in which the output disks 5 and 8 are supported by ball bearings 24.
Rotary support shaft 3 that rotatably supports power rollers 6 and 9
The main shafts 3 of the power rollers 6 and 9 are eccentric with respect to the pivot shafts 35 and 39 (see FIG. 4) which are rotatably supported by the trunnions 33 and 37.
In the axial direction is absorbed by the swinging motion of the power rollers 6 and 9 around the swing support shafts 35 and 39. When the positions of the output disks 5, 8 in the thrust direction are determined with respect to the casing 25, the positions of the power rollers 6, 9 and the input disks 4, 7 in the thrust direction are determined. Disc spring 29
Indicate that the disks 4, 7, 5,
8 is returned to the original state.

Next, the toroidal transmission units 1 and 2 and their shift control will be described with reference to FIG. FIG.
Line AA and line B of the toroidal type continuously variable transmission shown in FIG.
It is the figure which juxtaposed each sectional view about -B.
In order to displace the trunnions 33 and 37 in the tilt axis direction,
Hydraulic actuators 40 and 44 are disposed at the lower ends of the trunnions 33 and 37, respectively. Hydraulic actuator 4
Reference numerals 0 and 44 denote pistons 41 and 45 extending around the tilt shafts 11 of the trunnions 33 and 37, cylinders 42 and 46 formed in the casing 25 and slidably receiving the pistons 41 and 45, respectively. Consists of The cylinders 42 and 46 are formed with deceleration-side cylinder chambers 43A and 47A and speed-increasing cylinder chambers 43B and 47B, respectively, which are defined by pistons 41 and 45, respectively. From the spool valve 50 through the oil passage 48A, the deceleration side cylinder chamber 43
When the deceleration hydraulic pressure Pd is supplied to A and 47A, the speed-increasing cylinder chambers 43B and 47B are drained, and the speed-increasing hydraulic pressure Pd is supplied to the speed-increasing cylinder chambers 43B and 47B through an oil passage 48B.
When u is supplied, the deceleration-side cylinder chambers 43A and 47A are drained, and a pressure difference is generated between the deceleration-side cylinder chambers 43A and 47A and the speed-increasing cylinder chambers 43B and 47B. , 9 in the axial direction of the tilt shaft 11 according to the differential pressure, and the transmission shifts to the reduction side or the speed increase side.

The spool valve 50 has a sleeve 51 slidably provided in a valve body (valve case). The first spring 53 abutting on both ends of the sleeve 51
Is biased in a direction to maintain the neutral position. Sleeve 5
A spool 52 is slidably provided in 1. The spool 52 is biased rightward in FIG. 4 by a second spring 54 disposed at one end, and the other end of the spool 52 is connected to a precess cam 56 described later via a lever 55 pivotally mounted.
Is in contact. At one end and the other end of the spool valve 50,
SA port and SB port are formed respectively,
The control oil pressure P is applied to the SA port through the solenoid valve 57A.
A is supplied, and the control oil pressure PB is supplied to the SB port through the solenoid valve 57B. Also, the spool valve 50
A is a PL port connected to a line pressure (hydraulic pressure source), and A is connected to the deceleration side cylinder chamber 43A through an oil passage 48A.
It has a port, a B port communicating with the speed increasing side cylinder chamber 43B via the oil passage 48B, and an R port communicating with the reservoir.

In the toroidal type continuously variable transmission, the vehicle speed v detected by the vehicle speed sensor and the accelerator pedal depression amount A
Shift information detected by various sensors 59 such as an accelerator pedal depression amount sensor for detecting cc is input to the controller 58. The controller 58 outputs a control signal corresponding to the target gear ratio calculated based on the gear change information to the solenoid valves 57A and 57B. Solenoid valve 57
A and 57B are an output port C for outputting control oil pressure PA and PB to the SA port and SB port of the spool valve 50, a drain port D, and a control oil pressure source (pilot oil pressure source) P.
It has a hydraulic pressure source port E communicating with S. The solenoid valves 57A and 57B can be duty solenoid valves capable of changing a time ratio of a valve operating position taken by a valve body by changing a duty ratio of a pulse current for exciting an electromagnetic coil.

Since the solenoid valves 57A and 57B are the same normally-open solenoid valves, the controller 58
Solenoid valves 57A and 57A are set so that a differential pressure is generated between the SA port and the SB port corresponding to the target gear ratio.
For B, dutyA and dutyB indicate the total duty.
(100%) is obtained as a duty. The sleeve is controlled by controlling the ratio of time during which the hydraulic pressure from the control hydraulic pressure source PS is supplied to the SA and SB ports of the solenoid valves 57A and 57B or the period during which the control hydraulic pressure at the SA and SB ports is released to the drain. 51 is moved in the axial direction according to the target gear ratio. The sleeve 51 has a P
A communication hole corresponding to each of the L, R, A, and B ports is formed, and the ports PL,
R is connected to port A or port B. Spool valve 5
0, the control oil pressure P supplied to the ports SB and SA at both ends.
The sleeve 51 moves to a position indicating the target gear ratio so that the differential pressure between A and PB balances the spring force of the first spring 53.

In the toroidal transmission section 1, the lever 55
The precess cam 56 with which one end thereof abuts is attached to a shaft end of the one trunnion 33 extending along the tilt shaft 11. The precess cam 56 is a trunnion 33
Is detected as a combined displacement amount of the displacement axis direction displacement amount Y and the displacement angle displacement amount θ. The spool 52 of the spool valve 50 moves in accordance with the resultant displacement. To control the gear ratio, the spool valve 50 and the solenoid valves 57A and 57B receive a control signal relating to the target gear ratio from the controller 58 and a signal regarding the combined displacement amount from the precess cam 56 to receive the hydraulic actuators 40 and 44. And a speed ratio control valve for adjusting the hydraulic pressure of the engine.

When the trunnions 33 and 37 are in the neutral position where the displacement amount Y in the displacement axis direction is zero, the displacement angle θ of the power rollers 6 and 9 is maintained at that time, and the gear ratio is changed. The constant value at that time is held. That is, in this neutral position, the trunnions 33 and 37 are positioned in the tilt axis direction such that the rotation center lines of the input disks 4 and 7 and the output disks 5 and 8 intersect with the rotation axis 10 of the power rollers 6 and 9. The power rollers 6 and 9 rotate in a state of tilting with a tilt angle displacement amount corresponding to the gear ratio. Further, the spool 52 moves following the sleeve 51 which is shifted in accordance with the target gear ratio, and moves the A port and the B port.
The port is closed.

The gear ratio is changed by displacing the trunnions 33, 37 in the axial direction of the tilt shaft 11 from the neutral position. That is, when the target gear ratio is changed while both disks are rotating and the sleeve 51 shifts, the sleeve 51 is shifted.
A according to the relative movement amount generated between
The port or the B port is electrically connected to the PL port communicating with the line pressure, and the trunnions 33 and 37 are displaced in the tilt axis direction. Power rollers 6, 9 with trunnions 33, 37
Are also displaced in the tilt axis direction, and the contact positions of the power rollers 6, 9 with the input disks 4, 7 and the output disks 5, 8 are displaced from the contact positions at the neutral position. As a result, the power rollers 6 and 9 receive the tilting force from both disks, and the displacement direction along the tilt axis 11 (that is, the direction of Y> 0 or Y <0) and the displacement amount (the absolute value of Y) ), The tilting is started around the tilting shaft 11 in a direction and at a speed corresponding to the above, and the contact point between the two disks and the power roller is changed, so that the continuously variable transmission is started.

The trunnion 3 detected by the precess cam 56
The combined displacement amount of the tilting axial displacement amount Y and the tilting angular displacement amount 3, 37 acts on the other end of the spool 52 of the spool valve 50 via the lever 55, and acts on one end side of the spool 52. The spool 52 is moved against the spring force of the second spring 54. A sleeve 51 provided as a target gear ratio;
The A port and the B port connected to the oil passages 48A, 48B are switched to the PL port or the R port depending on the positional relationship between the spool 52 and the spool 52 provided by the precess cam 56. The displacement of the trunnions 33, 37 in the tilt axis direction is controlled by the differential pressure between the hydraulic pressure Pd and the hydraulic pressure Pu introduced into the cylinder chambers 43A and 43B and 47A and 47B, and the tilt angle θ
Approaches the target tilt angle and the displacement Y in the tilt axis direction of each of the trunnions 33 and 37 approaches zero, the spool 52 representing the actual speed ratio follows and approaches the position of the sleeve 51 representing the target speed ratio, The gradual convergence concludes and the shift operation ends.

The power rollers 6, which are provided opposite to each other with the main shaft 3 interposed therebetween, have input disks 4, 7 and output disks 5, 8
And the trunnions 33, 33 and 37, 37, which rotatably support the power rollers 6, receive forces in directions away from each other. In order to oppose this separating force, the ends of the trunnions 33, 33 and 37, 37 of each pair at opposing positions are connected to the yoke 60.
To maintain the distance between the axes of the two trunnions 33, 33, 37, 37.

Each of the yokes 60 is fitted and supported by a post 61 which is integrally or fixedly provided upright on the casing 25. The yoke 60 has a fitting hole 6 at a central position in the longitudinal direction.
Reference numeral 2 denotes a long member having circular holes 63 formed at both ends. The yoke 60 can swing around the engaging portion 64 in a state where the engaging portion 64 of the post 61 is fitted in the fitting hole 62 and the center position is restricted. In addition, the circular hole 6
A bearing 66 for rotatably supporting the end portion 65 of each of the trunnions 33 and 37 is fitted into 3. Bearing 66
Functions as a spherical bearing having a spherical surface on the outer peripheral side so as to maintain the fitted state with the end 65 of the trunnions 33 and 37 even when the yoke 60 is inclined with respect to the circular hole 63. In order to rotatably support the end portions 65 of the trunnions 33 and 37, the inner peripheral side functions as a radial bearing holding a needle.

FIG. 5 is an exploded perspective view showing the yoke and the post shown in FIG. Since the yoke 60 can only swing with respect to the post 61 in a plane including the tilt axes 11 and 11 of the trunnions 33 and 37, as shown in FIG. Presenting engaging part 6
A flat chamfered portion 69 (only one is shown) is formed on both sides of the yoke 60, and a flat inner surface 67 with which the chamfered portion 69 of the engaging portion 64 engages is fitted in the fitting hole 62 of the yoke 60. And an inner surface 68 with which the spherical surface of the engaging portion 64 engages. However, in order to allow the relative movement between the yoke 60 and the post 61, it is inevitable that the backlash is generated. Even if the play between the yoke 60 and the post 61 is kept small,
Since the distance from the post 61 to each trunnion 33 (37) fitted into the circular hole 63 is longer than the width of the chamfered portions 69, 69 of the post 61 in the yoke longitudinal direction, the trunnion 3
In 3 (37), the displacement caused by the play is amplified and appears.

When the trunnions 33, 37 deviate from their original positions, the positional relationship between the power roller 6 and the input / output disks 4, 5 and the positional relationship between the power roller 9 and the input / output disks 7, 8 become the target gear ratio. Therefore, the speed ratio may change or the durability of the power rollers 6 and 9 may be significantly impaired.

The trunnion, both ends of which are swingably supported by a link (yoke) via a support portion composed of a rolling bearing and a spherical joint, undergoes bending deformation due to the force during transmission. By increasing the clearance between the servo piston provided at one end of the trunnion and the guide hole that guides the servo piston as the distance from the spherical joint increases, the friction type prevents interference between the servo piston and the guide hole. A step transmission has been proposed (JP-A-7-217716).

An expensive ball as an actuator for supporting the end of each of the opposing trunnions at both ends thereof in a casing of a transmission by a support member and displacing one end of the trunnion in the axial direction of the tilting shaft. Japanese Patent Laid-Open Publication No. 5-45302 discloses a structure in which a trunnion is connected to a screw mechanism and only the other end of the trunnion is supported by a post attached to a housing.

Further, the ends of the opposite ends of the trunnion are supported by a casing of the transmission by supporting members, and one end of the trunnion is used as a hydraulic actuator as an actuator for displacing the trunnion in the axial direction of the tilt shaft. Japanese Patent Laid-Open Publication No. Sho 63-130954 proposes a connector in which a protrusion formed at the other end of the trunnion is fitted into a recess formed in a casing. Although the details of the fitting state are unknown, special considerations such as bearings have not been taken, and if there is a large gap, play will occur.
Small gaps can hinder smooth operation of the trunnion. Further, as means for solving the problem of trunnion position regulation, there has been proposed a method in which a trunnion is directly supported on a casing via a bearing without using a yoke or a post (Japanese Patent Laid-Open No. Hei 10-274300).

[0026]

As described above, in the conventional structure, since the trunnion is insufficiently supported, problems arise in the gear shifting stability and the durability of the trunnion support due to the operation of the trunnion. Sometimes. Therefore, in a toroidal type continuously variable transmission in which both ends of a trunnion shaft are rocked by a yoke and supported by a casing, the trunnion is supported as a trunnion support means in addition to the conventional support by a yoke that can be freely rocked by a post. By directly supporting the casing, the deflection of the tilting shaft is prevented, the operation of the trunnion is stabilized, and the problem is solved in that stable shifting performance and high durability as a transmission are secured at low cost. There are issues to be addressed.

[0027]

SUMMARY OF THE INVENTION An object of the present invention is to solve the above-mentioned problems, and to provide a trunnion for tiltably supporting a power roller at both ends thereof with a stable and durable structure with respect to a casing. A toroidal stepless type that supports and holds the gear, ensures reliable gear shifting and power transmission between the input / output disk and the power roller, and can be mounted on automobiles, especially on commercial vehicles with a long product life. It is to provide a transmission.

According to the present invention, there is provided an input disk driven by an input shaft, an output disk disposed opposite to the input disk and connected to an output shaft, and disposed and tilted between the input disk and the output disk. A pair of power rollers that incline around a rotation axis to continuously change the rotation of the input disk and transmit the rotation to the output disk; rotatably support each of the power rollers; A pair of trunnions that can be displaced in the axial direction, an actuator disposed in the casing for displacing each of the trunnions in the axial direction of the tilt axis, and a force acting on the trunnions in a direction intersecting the tilt axis. Therefore, it is pivotally fitted to the post attached to the casing in a state where the position is regulated at the center, and the two trunnies are fitted at both ends. A rod provided at one of the both ends of the trunnion and the casing is provided to prevent rattling of the trunnion. The present invention relates to a toroidal-type continuously variable transmission which is supported via radial bearings at both ends of a trunnion and a fitting portion provided on the other side of the casing.

Since the rods provided at both ends of each trunnion and one of the casings are supported via the radial bearings at the both ends of each trunnion and the fitting portions provided at the other side of the casing, each trunnion is provided with a rod. The tilt axis position is regulated by the casing, and rattling is prevented. At the time of torque transmission, each trunnion has a force in a direction intersecting the tilt axis, that is, a separating force due to a pressing force between disks generated in accordance with a transmission torque by a cam action of a loading cam, and a force in a main shaft direction. Works. However, the yoke is swingably fitted to the post attached to the casing in a state where the position is regulated at the center, and the opposite ends of both trunnions are swingably connected at both ends. Therefore, the force acting on these power rollers is supported by the casing via the trunnion, the yoke, and the post as in the related art, and the ratio transmitted through the rod and the fitting portion is small. The position of the tilting shaft of the trunnion is regulated by the rod and the fitting portion, and the radial bearing allows the movement of the trunnion in the tilting axis direction and rotation about the tilting axis. The positional relationship is maintained. Therefore, the gear ratio is stably maintained, and the contact portion of the power roller with the disk is held at a predetermined position.

It is preferable that the radial bearing is a slide bearing because it is simple and inexpensive to manufacture as a structure that allows the trunnion to move in the tilt axis direction and to rotate around the tilt axis. Further, the rod is formed integrally extending from the both ends of each trunnion, and the fitting portion is formed in the casing. The diameter of the rod is preferably smaller than the diameter of the end of the trunnion.

[0031]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a toroidal type continuously variable transmission according to the present invention will be described below with reference to the drawings. FIG. 1 is a sectional view of an embodiment of a toroidal type continuously variable transmission according to the present invention, taken along a plane including a main shaft, and FIG.
FIG. 2 is a perspective view showing a part of the toroidal-type continuously variable transmission shown in FIG. The basic structure of the toroidal continuously variable transmission shown in FIG. 1 is the same as the structure of the toroidal transmission unit in the conventional toroidal continuously variable transmission shown in FIG. The reference numerals are given and duplicate description is omitted.

In the toroidal type continuously variable transmission shown in FIG. 1, both upper and lower ends 65, 57 of each trunnion 33, 37 are provided.
The rod 65 is provided with a rod 70 concentric with the tilt shaft 11 in a state of being integrally protruded, preferably integrally formed. The shaft provided on one trunnion 33 of the toroidal transmission unit 1 and having the precess cam 56 at the tip can be used as a rod 70 as it is. Each of the rods 70 is a radial bearing 71 that allows the axial movement of the tilt shaft 11 and the rotation around the tilt shaft 11 into a fitting portion 72 formed in the casing 25 of the transmission.
Is supported through. That is, the trunnions 33, 37
Is supported by the casing 25 by a fitting portion via a radial bearing 71. With respect to the lower rod 70, the casing 25 is the cylinders 42, 46, in which case
A seal is provided between the cylinders 42 and 46 and the rod 70 together with the radial bearing 71 so that the oil in the hydraulic cylinder chambers 43A, 43B, 47A and 47B does not leak outside.

In each of the trunnions 33 and 37, the position of the axis of the tilt shaft 11 is restricted at the fitting portion 72. Therefore, the trunnions 33 and 37 do not rattle as in the related art with respect to the yoke 60. The power rollers 6, 9 and the input / output disks 4, 5, which are generated by the loading cam 18 according to the transmission torque from the input shaft.
Due to the pressing force between the trunnions 33 and 33 and the trunnions 37 and 37, a separating force for moving the trunnions 33 and 33 away from each other and a force in the direction of the main shaft 3 are applied. Each of the rods 70 attached to the trunnions 33 and 37 receives the above-described separating force and axial force because the respective posts 81 are received by the corresponding posts 81 from the respective yokes 80.
The rate of action is small. The radial bearing 71 moves the tilting shaft 11 of the trunnions 33 and 37 in the axial direction and rotates the tilting shaft 11.
It is preferable to use a sliding bearing from the viewpoint of simple and low-cost production as a structure that allows rotation around the axis.

The axial position of the tilting shaft 11 of the trunnions 33 and 37 is regulated without looseness to the casing 25 by fitting the rod 70 to the fitting portion 72 via the radial bearing 71. 4, 5, 7, 8 and the power rollers 6, 9 are maintained in a predetermined positional relationship. As a result, the speed ratio of the toroidal-type continuously variable transmission is stably maintained, and the durability of the toroidal-type continuously variable transmission is increased without reducing the durability of the power rollers 6 and 9.
Since each rod 70 is set to be thinner than the shaft diameter of the end 65 of each trunnion 33, 37, the trunnion 3
The trunnion 3 supports the forces such as separation force acting on the
The minute deformation and displacement generated in the yoke 80 to cope with the displacements of the rods 3 and 37 are absorbed by the elastic deformation of the rod 70. In the trunnions 33 and 37, the rod 70 is regulated by the casing 25 via the radial bearing 71,
This does not impair the function of the yoke 80.

Further, as shown in FIG. 2, it is not necessary to regulate the position of the yoke 80 around the post 81 by the post 81 itself, so that the post 81 is cut off to form a flat surface and the casing 25 of the post 81 is formed. There is no need to regulate the position when mounting to the device. The shape of the central portion of the yoke 80 mounted on the post 81 is the same as the conventional inner surface 67 shown in FIG.
A fitting hole 82 into which a spherical engaging portion 84 not subjected to surface shaving is fitted can be formed into a round hole that can be easily processed from the square hole provided with the yoke 80, similarly to the circular holes 83 at both ends. Further, the processing cost of the post 81 can be reduced. The rod 70 is provided on the casing 25 side, and the rod 70
The fitting portion 72 into which the fitting portion 72 fits is inserted into the end portions 6 of the trunnions 33 and 37.
5 may be provided.

[0036]

As described above, in the toroidal type continuously variable transmission according to the present invention, the rods provided at either end of each trunnion and one of the casings are provided at both ends of each trunnion and the other of the casing. The trunnions are supported by the fitted fitting portions via radial bearings, so that the tilting shaft positions of the respective trunnions can be shifted by the rod, the radial bearing, and the fitting portion while allowing the movement of each trunnion in the tilt axis direction and the rotation around the tilt axis. Is restricted by the casing through the fitting portion composed of the above, and rattling of the yoke is prevented. On the other hand, the separating force acting on the opposing trunnion and the force applied in the main axis direction are supported by the yoke and the post via the trunnion as in the related art, so that a large force does not act on the fitting portion. Since the tilt axis position of the trunnion is regulated by the fitting portion, the input / output disk and the power roller are maintained in a predetermined positional relationship,
The gear ratio can be stably maintained, the predetermined position of the contact portion of the power roller with the disk is maintained, and the predetermined position of the contact portion of the power roller with the disk is maintained. A continuously variable transmission with high durability and reliability without deterioration in performance is provided. Furthermore, since it is not necessary to regulate the position of the yoke post around the post, there is no need to perform post-cutting or position regulation when mounting the post, and the hole shape of the yoke post mounting portion can be easily processed from the square hole. Since a round hole can be formed, the processing cost is also reduced.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an embodiment of a toroidal type continuously variable transmission according to the present invention.

FIG. 2 is a perspective view showing a part including a yoke and a post of the toroidal type continuously variable transmission shown in FIG.

FIG. 3 is a sectional view showing a conventional toroidal-type continuously variable transmission.

FIG. 4 is a line AA of the toroidal type continuously variable transmission shown in FIG. 3;
And a sectional view taken along line BB.

5 is an exploded perspective view showing a yoke and a post of the toroidal type continuously variable transmission shown in FIG.

[Explanation of symbols]

 1, 2 Toroidal transmission section 4, 7 Input disk 5, 8 Output disk 6, 9 Power roller 11 Tilt axis 13 Input axis 25 Casing 33, 37 Trunnion 40, 44 Hydraulic actuator 65 End of trunnion 70 Rod 71 Radial bearing 72 Fitting part 80 Yoke 81 Post

Claims (4)

[Claims] An input disk driven by an input shaft;
An output disk disposed opposite to the input disk and connected to an output shaft, disposed between the input disk and the output disk, and tilted around a tilt axis to prevent rotation of the input disk; A pair of power rollers for transmitting to the output disk by changing the speed in stages, a pair of trunnions that rotatably support the respective power rollers and are displaceable in the axial direction of the tilt shaft, and tilt the respective trunnions. An actuator disposed on the casing for displacing in the axial direction of the shaft, and a position regulation at a central portion with respect to a post attached to the casing for supporting a force acting on the trunnion in a direction intersecting the tilt axis. A yoke that swingably fits in a disengaged state and that swingably connects opposite ends of the two trunnions at both ends. In order to prevent rattling of the trunnions, rods provided at either end of each of the trunnions and the casing are provided with radial bearings at fitting portions provided at the both ends of the trunnions and the other of the casing. Toroidal-type continuously variable transmission that is supported via 2. The toroidal-type continuously variable transmission according to claim 1, wherein the radial bearing is a slide bearing. 3. The toroidal according to claim 1, wherein the rod is formed integrally with each end of the trunnion so as to extend from the both ends, and the fitting portion is formed in the casing. Type continuously variable transmission. 4. The toroidal-type continuously variable transmission according to claim 1, wherein a diameter of the rod is smaller than a diameter of the end of the trunnion.