JP2002276751A - Toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a toroidal type continuously variable transmission capable of ensuring slide motion of a power roller inner ring, even with a power roller supporting structure simplified and low in cost without requiring thrust needle bearing. SOLUTION: A color member 96 is provided between a power roller shaft 95 and a power roller inner ring 93. The slide structure for supporting the power roller inner ring 93 to be relatively movable only in a horizontal directions to the power roller shaft 95 is a slide engaging structure by an across flat shape in which two vertically parallel surfaces 96a, 96a and parallel surfaces 95a, 95a of the color member 96 and of the power roller shaft 95 come into contact and are engaged with each other, and slide tolerance gap t, t are interposed between the color member 96 and the power roller shaft 95 in a horizontal direction.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention belongs to the technical field of a toroidal type continuously variable transmission applied to a vehicle or the like.

[0002]

2. Description of the Related Art A continuously variable transmission for an automobile has a smoothness,
In recent years, research and development have been promoted in consideration of ease of driving and improvement of fuel efficiency. Among these, power is transmitted by shearing of an oil film formed between the input / output disk and the power roller, and has a larger capacity and responsiveness than the V-belt type continuously variable transmission previously put to practical use. A good toroidal type continuously variable transmission (hereinafter, toroidal type CVT) has already been put to practical use.

[0003] Toroidal CVTs can be classified into full toroidal types and half toroidal types according to their shapes.
The half-toroidal type CVT is selected from both types mainly because the half-toroidal type CVT has smaller spin loss of the power roller with respect to the input / output disk than the full-toroidal type CVT.

The half toroidal type CVT is mounted on a transmission case such that an input disk and an output disk are coaxially opposed to each other, a power roller sandwiched between the input and output disks so as to transmit power, and a transmission case. And a trunnion for rotatably supporting the power roller, and a gear shifting operation for obtaining a gear ratio according to the magnitude of the tilt angle of the power roller is performed in a tilt axis direction perpendicular to the power roller rotation axis. By slightly displacing the power roller, the power roller is offset from the disk rotation center position,
By this offset, the power roller is tilted by the side slip force generated at the contact portion between the power roller and the input disk, and when the predetermined tilt angle is reached, the displacement applied to the trunnion is returned to the original disk rotation center position. This is performed by stopping the tilting operation of the power roller.

During the shifting operation, the spacing between the input and output disks is changed by a loading cam device in order to always maintain the contact state between the power rollers and the input and output disks regardless of the tilt of the power rollers. At this time, while only the input disk is moved in the disk axial direction by the loading cam device with respect to the fixed output disk, the tilting axis of the trunnion is a fixed axis with no fluctuation in the axial position. In order to keep the power roller in contact with the disk by following the change in the distance between the input and output disks by the device, it is necessary to move the power roller in a direction (left-right direction) perpendicular to the power roller rotation axis and the trunnion tilt axis. In addition, when the input / output disk is deformed during power transmission or misalignment that can occur during assembly occurs, the relative displacement between the power roller and the input / output disk occurs, and this relative displacement is absorbed. For this purpose, it is necessary to move the power roller in the left-right direction.

As a power roller support structure for securing the movement of the power roller in the left-right direction, a support structure using an eccentric pivot shaft is employed. In this case, the power roller is slightly shifted from the center of rotation of the disk, thereby causing unnecessary shifting. .

Therefore, for example, Japanese Patent Laid-Open No. 7-198014
In the publication, as shown in FIG.
A power roller housing 91 disposed in the direction of the rotation axis of the input / output disk is formed, and a linear bearing 96 is interposed between the power roller 35 and the power roller housing 91 of the trunnion 38, and the power roller 35 is There has been proposed a power roller support structure that supports the power roller so as to be able to move in a parallel direction.

[0008]

However, in the power roller support structure of the conventional toroidal type continuously variable transmission, the power roller inner ring 35a and the power roller outer ring 35 are not provided.
b has a structure that slides with respect to the trunnion 38, so that both the thrust force and the radial force from the power roller 35 act on the slide portion, and the rear surface of the power roller outer ring 35b and the trunnion 38 A linear bearing 96 (needle bearing) is required between the power roller supporting surface and the power roller supporting surface, which causes a problem of high cost.

That is, the slide portion of the power roller 35 receives the thrust force in the power roller rotation axis direction which the power roller 35 receives. Further, since the input / output disk contact position of the power roller 35 and the position of the slide portion are separated from each other in the direction of the rotation axis of the power roller, the moment (= reaction force × reaction force) of the traction force, which is a radial force, is obtained. Span) occurs in the linear bearing 96 that is the slide portion, and this is twisted.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems. It is an object of the present invention to provide a simplified and low-cost power roller supporting structure which does not require a thrust needle bearing, and which has a low power roller inner ring. An object of the present invention is to provide a toroidal-type continuously variable transmission that can ensure a sliding motion.

[0011]

To achieve the above object, according to the first aspect of the present invention, an input disk and an output disk which are coaxially opposed to each other, and a pressure is transmitted between the input and output disks so as to transmit power. A power roller, and a trunnion attached to the transmission case so as to be tiltable and rotatably supporting the power roller, wherein the power roller has a power roller inner ring that frictionally contacts an input / output disk, and the trunnion. A toroidal-type continuously variable transmission including: a power roller outer ring provided so that relative movement is restricted, and a power roller bearing interposed between the power roller inner ring and the power roller outer ring. In the power roller, a power roller shaft that rotatably supports a power roller inner ring is provided, and the power roller shaft and Between Warora inner ring, characterized in that a sliding structure that only the relatively movable supported tilt axis and power roller rotation axis direction perpendicular trunnions power rollers inner ring relative to the power roller shaft. Here, the power roller outer ring provided with its relative movement restricted with respect to the trunnion is not limited to the one that integrally fixes the trunnion and the power roller outer ring, and in a configuration in which the power roller outer ring is independent. In other words, the term includes a part integrated as a part of the trunnion and a part fixed integrally with the trunnion via a power roller shaft.

According to a second aspect of the present invention, in the toroidal type continuously variable transmission according to the first aspect, a collar member is provided between the power roller shaft and a power roller inner ring, and the slide structure includes a collar member. The power roller shaft has a two-sided width slide-fitting structure in which two parallel surfaces in the up-down direction, which is the direction of the tilt axis of the trunnion, are in contact with each other and a sliding allowable gap is interposed in the left-right direction. It is characterized by the following.

According to a third aspect of the present invention, in the toroidal type continuously variable transmission according to the first or second aspect, the power roller bearing of the power roller is a tapered roller type thrust bearing. .

According to a fourth aspect of the present invention, in the toroidal type continuously variable transmission according to the third aspect, the tapered roller type thrust bearing has a flat bearing support surface on a power roller outer ring side. .

According to a fifth aspect of the present invention, in the toroidal type continuously variable transmission according to the third aspect, the tapered roller type thrust bearing has a flat bearing support surface on the power roller inner ring side. .

[0016]

According to the first aspect of the present invention, the power roller is provided with a power roller shaft for rotatably supporting the power roller inner ring, and the power roller shaft is connected to the power roller inner ring. Between the power roller shaft and the power roller shaft, a sliding structure is provided to support the power roller inner ring in a direction perpendicular to the trunnion tilt axis and the power roller rotation axis, that is, only in the left and right directions, so that the power When a force to move the input / output disk in the left / right direction acts on the roller inner ring, only the power roller inner ring moves in the left / right direction according to the force applied from the input / output disk.

For example, when the input cam follows a change in the distance between the input and output disks by the loading cam device, only the inner race of the power roller can be moved in the left and right direction in accordance with the movement of the input disk in the disk axial direction. When the power roller is deformed or misalignment that can occur during assembly occurs, the relative positional deviation between the power roller inner ring and the input / output disk can be absorbed by moving the power roller inner ring alone in the left-right direction.

Further, the slide structure supports the power roller inner ring so as to be relatively movable only in the left-right direction, and the force in the thrust direction, which is the rotation direction of the power roller, is applied to the power roller outer ring via the power roller bearing. Since it supports, the thrust force applied to the inner race of the power roller does not act on the slide structure. In addition, since the position of the input / output disk contact of the power roller inner ring and the position of the slide structure substantially coincide with the direction of the rotation axis of the power roller, the moment due to the reaction force of the traction force, which is a radial force, is reduced by the slide structure. And no prying occurs in the slide structure. Thus, the slide structure according to the present invention eliminates the need for the needle bearing that was required for the conventional slide portion for the trunnion.

Therefore, the sliding motion of the inner race of the power roller can be ensured while the thrust needle bearing is not required and the power roller support structure is simplified and inexpensive.

According to the second aspect of the present invention, a collar member is provided between the power roller shaft and the power roller inner ring, and the sliding structure of the power roller inner ring is such that the collar member and the power roller shaft are connected to the trunnion. Two parallel surfaces in the up-down direction, which is the tilt axis direction, are in contact with each other, and have a two-sided width slide fitting structure in which a slide allowable gap is interposed in the left-right direction.

Accordingly, the slide function is realized by a simple shape with a reduced number of parts, that is, a slide fitting structure with a two-plane width shape, and the cost can be further reduced.

According to the third aspect of the present invention, the power roller bearing of the power roller is a taper roller type thrust bearing.

Therefore, as compared with the case of using a ball bearing, a loss due to spin in the bearing portion is small, and the efficiency of the unit can be improved.

According to the fourth aspect of the present invention, the bearing support surface of the tapered roller type thrust bearing on the power roller outer ring side is a flat surface.

Accordingly, when the inner race of the power roller slides, the displacement of the inner and outer races of the power roller is absorbed by the displacement of the bearing support surface on the outer race of the power roller, and the durability of the bearing can be improved.

According to the fifth aspect of the invention, the bearing support surface of the tapered roller type thrust bearing on the inner side of the power roller is flat.

Accordingly, the bearing support surface on the power roller inner ring side can be made flat, so that the cost of the power roller inner ring is reduced, and even if the power roller inner ring is deformed by the pressing force from the input / output disk, the collar portion is formed. Since there is no friction, the friction at the end of the tapered roller does not increase.

[0028]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view showing a toroidal type continuously variable transmission according to a first embodiment of the present invention;
A description will be given based on a second embodiment corresponding to the first embodiment, a third embodiment corresponding to the first to fourth aspects, and a fourth embodiment corresponding to the first to third aspects and the fifth aspect.

(First Embodiment) [Overall Configuration] FIG. 1 is an overall configuration diagram showing a toroidal type continuously variable transmission according to a first embodiment. Reference numeral 10 denotes a toroidal type continuously variable transmission. Is input via the torque converter 12. The torque converter 12 includes a pump impeller 12a, a turbine runner 1
2b, stator 12c, lock-up clutch 12d,
It comprises an apply-side oil chamber 12e, a release-side oil chamber 12f, and the like, and an input shaft 14 penetrates a central portion thereof.

The input shaft 14 is connected to a forward / reverse switching mechanism 36, which is connected to the planetary gear mechanism 4
2, a forward clutch 44 and a reverse brake 46 are provided. The planetary gear mechanism 42 has a pinion carrier 42a that supports a double pinion, a ring gear 42b that meshes with each of the double pinions, and a sun gear 42c.

The pinion carrier 42a of the planetary gear mechanism 42 is connected to the torque transmission shaft 16, and the first continuously variable transmission mechanism 18 and the second continuously variable transmission mechanism 20 are connected to the torque transmission shaft 16 in the transmission case 22. Is arranged in tandem on the downstream side (dual cavity type). A control valve system body is disposed on a base indicated by reference numeral 64.

The first continuously variable transmission mechanism 18 includes a pair of input disk 18a and output disk 18b having opposing surfaces formed as toroidal curved surfaces, and these input / output disks 18a,
A pair of power rollers 18 c, which are arranged between the opposing surfaces of the power rollers 18 b and symmetrically with respect to the torque transmission shaft 16,
18d and trunnions 17a and 17b (FIG. 2) for rotatably supporting the power rollers 18c and 18d, respectively. Similarly, the second continuously variable transmission mechanism 20 has a pair of input disks 20a and an output disk 20b whose opposing surfaces are formed as toroidal curved surfaces, and a pair of power rollers 20c,
20d, and trunnions 27a and 27b (FIG. 2) for rotatably supporting the power rollers 20c and 20d, respectively.

On the torque transmission shaft 16, the two continuously variable transmission mechanisms 18 and 20 are arranged in opposite directions so that the output disks 18b and 20b face each other.
The input disk 18a of No. 8 is pressed rightward in the axial direction in the figure by a loading cam device 34 that generates a pressing force according to the input torque passed through the torque converter 12.

The loading cam device 34 has a loading cam 34a and is supported by the shaft 16 via a slide bearing 38. The input disk 20a of the second continuously variable transmission mechanism 20 is urged by a disc spring 40 toward the left side in the axial direction in the figure.

The input disks 18a and 20a are supported by the transmission shaft 16 via the ball splines 24 and 26 so as to be rotatable and movable in the axial direction.

In the above mechanism, each power roller 18
c, 18d, 20c, and 20d are tilted by an operation described later so that a tilt angle corresponding to the gear ratio is obtained.
The input rotation of the input disks 18a, 20a is changed in a stepless (continuous) manner and transmitted to the output disks 18b, 20b.

The output disks 18b and 20b are spline-coupled to an output gear 28 rotatably fitted on the torque transmission shaft 16, and the transmission torque is transmitted to the output shaft (counter shaft) 30 via the output gear 28. Combined gear 3
0a, and these gears 28, 30a constitute a torque transmission mechanism 32. Further, a transmission mechanism 48 including gears 52 and 56 provided on the output shafts 30 and 50 and an idler gear 54 meshing with them is provided. The output shaft 50 connects the propeller shaft 60 to the transmission mechanism 48.

FIG. 2 is a schematic diagram showing a shift control system for tilting the power rollers 18c, 18d, 20c, and 20d so as to obtain a tilt angle corresponding to the speed ratio. This will be described below.

First, each of the power rollers 18c, 18d, 2
0c and 20d are trunnions 17a, 17b, 27a,
27b, which is supported at one end of the power roller rotating shaft 1.
It is rotatable around 5a, 15b, 25a, 25b. The trunnions 17a, 17b, 27a, 27b
Of the trunnions 17a, 17b, 27a, 2
7b is moved in the axial direction so that each power roller 18c, 18
Servo pistons 70a, 70b, 72a, 72b are provided as hydraulic actuators for tilting d, 20c, 20d.

The servo pistons 70a, 70b, 72
As a hydraulic control system for controlling the operation of a and 72b, a high-side oil path 74 connected to the high-side oil chamber, a low-side oil path 76 connected to the low-side oil chamber, and a high-side oil path 74 are connected. A shift control valve 78 having a port 78b connecting the port 78a and the low-side oil passage 76 is provided. An oil pump 80 is connected to a line pressure port 78c of the shift control valve 78.
And a line pressure from a hydraulic source having a relief valve 82. Transmission spool 78d of the transmission control valve 78
Detects the axial direction and tilt direction of the trunnion 17a,
The lever 84 and the precess cam 86 that feed back to the shift control valve 78 are interlocked. The speed change sleeve 78e of the speed change control valve 78 is driven by a step motor 88 so as to be displaced in the axial direction.

A CVT controller 110 is provided as an electronic control system for controlling the drive of the step motor 88. The CVT controller 110 includes a throttle opening sensor 112, an engine rotation sensor 114, an input shaft rotation sensor 116, an output shaft rotation. Sensor (vehicle speed sensor) 11
Input information from 8 etc. is taken in.

[Power Roller Support Structure] With respect to the support structure of the power roller 18c selected as a representative from the above power rollers 18c, 18d, 20c, 20d,
The configuration will be described with reference to FIGS. The same structure is adopted for the other power rollers 18d, 20c and 20d.

The trunnion 17a is provided in the transmission case 2
2 tilting shaft 1 orthogonal to power roller rotating shaft 15a
9a so as to be tiltable around the power roller 1
8c rotatably supports the power roller inner ring 93.

The power roller 18c has a power roller inner ring 93 that comes into frictional contact with the input / output disks 18a and 18b.
A power roller outer ring 94 provided so as to be restricted in relative movement with respect to the trunnion 17a, and a ball bearing 92 (power roller bearing) interposed between the power roller inner ring 93 and the power roller outer ring 94. The power roller outer ring 94 receives a contact load input from the input / output disks 18a and 18b to the power roller inner ring 93 due to the pinching pressure via the ball bearing 92.

The power roller 18c is provided with a power roller shaft 95 which rotatably supports the power roller inner ring 93. This power roller shaft 95
Are fixed to the trunnion 17a by press-fitting, and have two flat surfaces 95a, 95 having two parallel surfaces in the vertical direction which is the direction of the tilt axis 19a of the trunnion 17a.
a is formed. Also, the power roller shaft 95
, The power roller outer ring 94 is fitted, and the relative movement of the power roller outer ring 94 with respect to the trunnion 17a is regulated via the power roller shaft 95, and the power roller outer ring 94 is provided integrally.

A collar member 96 and a needle bearing 97 are provided between the power roller shaft 95 and the power roller inner ring 93, and are provided between the cylindrical outer peripheral surface of the collar member 96 and the shaft hole 93 a of the power roller inner ring 93. , A needle bearing 97 is interposed.

On the inner surface of the collar member 96 are formed two flat widths 96a, 96a having two parallel surfaces in the vertical direction. The two flat widths 96a, 96a and the two flat widths 95a of the power roller shaft 95 are formed. , 95a are in contact with each other in the up-down direction, and are allowed to slide in the left-right direction.
The two surfaces that support the power roller inner ring 93 so as to be relatively movable only in a direction (left-right direction) perpendicular to the tilt axis 19a of the trunnion 17a and the power roller rotation axis 15a with respect to the power roller shaft 95 by interposing the t. It has a width-shaped slide fitting structure.

The track groove 93b of the ball bearing 92 formed on the power roller inner ring 93 is provided with a ball bearing 92 to secure the sliding movement of the power roller inner ring 93 as shown in FIGS. Are formed in a groove shape with a clearance margin between them. The position of the collar member 96 and the needle bearing 97 in the axial direction is regulated by an E-ring 98 hooked on the tip of the power roller shaft 95.

Next, the operation will be described.

[Gear ratio control action] Toroidal type CVT
Displaces the trunnions 17a, 17b, 27a, 27b in the direction of the tilt axis 19a,
The gear ratio is changed by tilting d, 20c and 20d.

That is, the step motor 88 is driven by a drive command from the CVT controller 90 for obtaining the target gear ratio.
When the transmission sleeve 78e is displaced by rotating the hydraulic piston, hydraulic oil is guided to one of the servo piston chambers of the servo pistons 70a, 70b, 72a, and 72b, and hydraulic oil is discharged from the other servo piston chamber.
a, 17b, 27a, 27b are displaced in the direction of the tilt axis 19a.

Thus, the power rollers 18c, 18
The rotation centers of d, 20c and 20d are offset from the disk rotation center position. Due to this offset, the power rollers 18c, 18d, 20c, 20d and the power rollers 18c, 18d by the side slip force generated at the contact portion between the input / output disks 18a, 18b, 20a, 20b.
d, 20c and 20d are tilted.

The tilting motion and the offset are transmitted to the speed change spool 78d via the precess cam 86 and the lever 84.
At the balance position with the speed change sleeve 78e displaced by the step motor 88, and when the predetermined tilt angle is reached, the trunnions 17a, 17
b, 27a, 27b are returned to the original disk rotation center position, and the power rollers 18c, 18d, 20
This is performed by stopping the tilting operations c and 20d. The gear ratio is determined by the tilt angle of the power rollers 18c, 18d, 20c, 20d.

[Sliding Action of Power Roller Inner Ring] With reference to the power roller 18c as a representative example, the sliding action of the power roller inner ring 93 of the power roller 18c will be described. Note that the other power rollers 18d, 20c, and 20d exhibit the same operation.

First, the power roller 18c is provided with a power roller shaft 95 for rotatably supporting the power roller inner ring 93, and the power roller inner ring 9 is provided between the power roller shaft 95 and the power roller inner ring 93.
3 with respect to the power roller shaft 95
a, the input / output disks 18a and the power input / output disks 18a, 18b, the input / output disk 18
a, a power roller inner ring 9 according to the force acting from
Only 3 moves left and right.

For example, when following the change in the distance between the input / output disks 18a and 18b due to the loading cam device 34, only the power roller inner ring 93 can be moved in the left and right direction according to the movement of the input disk 18a in the disk axial direction. And the input / output disks 18a, 18
Even when b is deformed or misalignment that can occur during assembly occurs, the relative positional deviation between the power roller inner ring 93 and the input / output disks 18a and 18b is absorbed by the lateral movement of the power roller inner ring 93 alone. can do.

Further, the slide structure supports the power roller inner ring 93 so as to be relatively movable only in the left-right direction. The force in the thrust direction, which is the direction of the power roller rotation shaft 15a, is applied via the ball bearing 92 to the power roller. Since it is supported by the outer ring 94, the thrust force received by the power roller inner ring 93 does not act on the slide fitting structure.

The position where the input / output disk contact of the power roller inner ring 93 (in the vicinity of the BB line position in FIG. 3) and the position of the slide fitting structure substantially coincide with the direction of the power roller rotation shaft 15a (moment). Since the span is substantially zero), a moment due to the reaction force of the traction force, which is a radial force, does not occur in the slide fitting structure, and no prying occurs in the slide fitting structure.

As a result, the slide structure according to the first embodiment of the present invention eliminates the need for a needle bearing which was required for a conventional slide portion for a trunnion.

Next, the effects will be described.

(1) The power roller shaft 9 for rotatably supporting the power roller inner ring 93 on the power roller 18c.
5 and a slide fitting structure is provided between the power roller shaft 95 and the power roller inner ring 93 to support the power roller inner ring 93 so as to be relatively movable only in the left and right directions with respect to the power roller shaft 95. The power roller inner ring 9 has a simplified and low-cost power roller support structure that does not require a thrust needle bearing.
3 can ensure the sliding motion.

(2) A collar member 96 is provided between the power roller shaft 95 and the power roller inner ring 93. The sliding structure of the power roller inner ring 93 is such that the collar member 96 and the power roller shaft 95 Parallel surface 9
6a, 96a and the parallel surfaces 95a, 95a are in contact with each other, and have a slide fitting structure with a two-sided width shape interposed with sliding allowable gaps t, t in the left-right direction. Realizes the slide function,
Further cost reduction can be achieved.

(3) The power roller shaft 95 is fixed to the trunnion 17a by press-fitting, and the outer race of the power roller in which the raceway groove requiring special heat treatment and surface finishing is formed separately from the power roller shaft 95 and the trunnion 17a. 94, the respective parts 94, 95, 17
Workability such as heat treatment and surface finishing can be improved.

The power roller shaft 95 and the trunnion 17a may be connected to each other by any other method such as press-fitting, nut fastening, and integral molding.

(Second Embodiment) In this second embodiment, as shown in FIGS. 5 and 6, a power roller outer ring portion 95b is formed integrally with a power roller shaft 95, and a trunnion 17 is formed.
FIG. 7A shows an example in which a hole for fixing the power roller shaft 95 is eliminated.

Since the other construction is the same as that of the first embodiment, the corresponding parts are denoted by the same reference numerals and description thereof is omitted.
The operation is also the same as that of the first embodiment, and the description is omitted.

Next, the effects will be described.

The toroidal type continuously variable transmission of the second embodiment has the following effects in addition to the effects (1) and (2) of the first embodiment.

(4) When the power roller shaft 95 and the power roller outer ring 94 are separate bodies, both are mainly lathe processing. However, since the power roller outer ring portion 95b is formed integrally with the power roller shaft 95, The number of parts can be reduced without increasing the number of processing steps, and the cost can be reduced.

(5) Since the trunnion 17a has no hole for fixing the power roller shaft 95, the rigidity of the trunnion 17a can be improved.
It is possible to reduce the size and weight of the toroidal type continuously variable transmission.

The power roller shaft 95 and the power roller outer ring 94 may be joined by press-fitting,
Other methods such as nut fastening may be used.

(Third Embodiment) In this third embodiment, as shown in FIGS. 7 and 8, the power roller bearing which receives the thrust force of the power roller inner ring 93 is a taper roller type thrust bearing 99, and An example in which the roller-type thrust bearing 99 has a flat bearing support surface 99a on the power roller outer ring side, and the power roller outer ring 94 is omitted and the trunnion 17a is also used as the power roller outer ring 94 when compared with the first embodiment. It is.

Since the other construction is the same as that of the first embodiment, the corresponding parts are denoted by the same reference numerals and description thereof will be omitted.
The operation is also the same as that of the first embodiment, and the description is omitted.

Next, the effects will be described.

The toroidal-type continuously variable transmission of the third embodiment has the following effects in addition to the effects (1) and (2) of the first embodiment.

(6) Since the power roller bearing which receives the thrust force of the power roller inner ring 93 is a taper roller type thrust bearing 99, the spinning at the bearing portion is different from the first and second embodiments using the ball bearing 92. And the efficiency of the unit can be improved.

(7) Since the bearing support surface 99a on the power roller outer ring side of the tapered roller type thrust bearing 99 is made flat, when the power roller inner ring 93 slides, the displacement of the power roller inner and outer rings 93, 94 is reduced by the power roller outer ring side. The bearing support surface 99a is absorbed by the displacement and the bearing durability can be improved.

In the third embodiment, the power roller outer ring 94 is omitted, and the power roller outer ring 9 is attached to the trunnion 17a.
4, the trunnion 17a and the power roller outer ring 94 may be provided separately. The power roller shaft 95 and the power roller outer ring 94, or
The method of connecting the power roller shaft 95 and the trunnion 17a may be any method, such as integral molding, press fitting, and nut fastening.

(Fourth Embodiment) In the fourth embodiment, as shown in FIGS. 9 and 10, the power roller bearing which receives the thrust force of the power roller inner ring 93 is a taper roller type thrust bearing 99, and this taper roller This is an example in which the bearing support surface 99b of the roller type thrust bearing 99 on the power roller inner ring 93 side is a flat surface.

Since the other construction is the same as that of the first embodiment, the corresponding parts are denoted by the same reference numerals and description thereof will be omitted.
The operation is also the same as that of the first embodiment, and the description is omitted.

Next, the effects will be described.

In the toroidal type continuously variable transmission according to the fourth embodiment, (1) and (2) in the first embodiment and (6) in the third embodiment.
In addition to the effects described above, the following effects can be obtained.

(8) Bearing support surface 99 of taper roller type thrust bearing 99 on the side of power roller inner ring 93
Since b is a flat surface, the cost of the power roller inner ring 93 is reduced, and even if the power roller inner ring 93 is deformed by the pressing force from the input / output disks 18a and 18b, there is no flange portion. The friction of the part does not increase.

In the fourth embodiment, the example in which the power roller outer ring 94 and the trunnion 17a are separate bodies has been described.
This may be integrated. The power roller shaft 95 and the power roller outer ring 94, or the power roller shaft 95 and the trunnion 17a may be connected by any method, such as integral molding, press fitting, and nut fastening.

(Other Embodiments) The toroidal-type continuously variable transmission according to the present invention has been described based on the first to fourth embodiments. However, the specific structure is limited to these embodiments. However, changes and additions of the design are permitted without departing from the gist of the present invention described in each claim of the claims.

For example, in the first to fourth embodiments, an example of a slide fitting structure having a two-sided width using a collar member has been described as the sliding structure. If the slide structure is provided between the slide rollers and supports the power roller inner ring so as to be relatively movable only in a direction perpendicular to the tilt axis of the trunnion and the rotation axis of the power roller with respect to the power roller shaft, the slide fitting shown in the embodiment is applicable. It is not limited to the combined structure.

[Brief description of the drawings]

FIG. 1 is an overall system diagram showing a toroidal type continuously variable transmission according to a first embodiment.

FIG. 2 is a transmission control system diagram showing the toroidal type continuously variable transmission according to the first embodiment;

FIG. 3 is a cross-sectional view showing a power roller support structure in the toroidal type continuously variable transmission according to the first embodiment.

FIG. 4 is a sectional view taken along line AA of FIG. 3 and a sectional view taken along line BB of FIG. 3 in the power roller supporting structure of the first embodiment.

FIG. 5 is a sectional view showing a power roller support structure in a toroidal type continuously variable transmission according to a second embodiment.

FIG. 6 is a sectional view taken along line AA of FIG. 5 and a sectional view taken along line BB of FIG. 5 in the power roller supporting structure of the second embodiment.

FIG. 7 is a sectional view showing a power roller support structure in a toroidal type continuously variable transmission according to a third embodiment.

8 is a sectional view taken along line AA of FIG. 7 and a sectional view taken along line BB of FIG. 7 in the power roller supporting structure of the third embodiment.

FIG. 9 is a sectional view showing a power roller supporting structure in a toroidal type continuously variable transmission according to a fourth embodiment.

FIG. 10 is a sectional view taken along line AA of FIG. 9 and a sectional view taken along line BB of FIG. 9 in the power roller supporting structure of the fourth embodiment.

FIG. 11 is a sectional view showing a power roller support structure in a conventional toroidal type continuously variable transmission.

[Explanation of symbols]

15a Power roller rotating shaft 17a Trunnion 18a Input disk 18b Output disk 18c Power roller 19a Tilting shaft 92 Ball bearing (Power roller bearing) 93 Power roller inner ring 93a Shaft hole 94 Power roller outer ring 95 Power roller shaft 95a Width across flat 96 Color Member 96a Width across flats 97 Needle bearing t Allowable gap 98 E-ring 99 Tapered roller type thrust bearing (power roller bearing) 99a, 99b Bearing support surface

Claims (5)

[Claims] An input disk and an output disk coaxially opposed to each other; a power roller sandwiched between the input and output disks so as to transmit power; and a power roller mounted on a transmission case so as to be tiltable, A power roller inner ring that frictionally contacts an input / output disk, a power roller outer ring provided with relative movement restricted with respect to the trunnion, and the power roller. A power roller bearing interposed between an inner ring and a power roller outer ring, wherein the power roller shaft rotatably supports the power roller inner ring on the power roller. And a power roller inner ring is provided between the power roller shaft and the power roller inner ring. Toroidal type continuously variable transmission, characterized in that a tilt axis and power roller rotation axis direction perpendicular only to the slide structure of relatively movable support trunnion relative bets. 2. The toroidal-type continuously variable transmission according to claim 1, wherein a collar member is provided between the power roller shaft and a power roller inner ring, and the slide structure includes a collar member and a power roller shaft; A toroidal characterized in that the two parallel surfaces in the up-down direction, which is the direction of the tilt axis of the trunnion, are in contact with each other, and have a two-sided width-shaped slide fitting structure in which a sliding allowable gap is interposed in the left-right direction. Type continuously variable transmission. 3. The toroidal continuously variable transmission according to claim 1, wherein a power roller bearing of the power roller is a tapered roller type thrust bearing. . 4. The toroidal type continuously variable transmission according to claim 3, wherein the tapered roller type thrust bearing has a flat bearing support surface on a power roller outer ring side. . 5. The toroidal-type continuously variable transmission according to claim 3, wherein the tapered roller-type thrust bearing has a flat bearing support surface on a power roller inner ring side. .