JP2000304121A - Toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To minify the size along the axial direction of an input shaft by using only one rolling bearing when an output gear is supported turnably on a casing and miniaturize its device. SOLUTION: A toroidal type continuously variable transmission 30 is provided with a casing 4, an input shaft 1, a pair of input disks 2a, 2b, a pair of output disks 3a, 3b, an output gear 34 and a three point contact ball bearing 41. The input shaft 1 and input disks 2a, 2b are rotated by a drive source E. The output disks 3a, 3b are arranged in the state faced the back surfaces 5a, 5b mutually. The output gear 34 is arranged between the output disks 3a, 3b. The output gear 34 and output disks 3a, 3b are rotated in an interlocked manner. The output gear 34 is supported turnably in the casing 4 by a single three point contact ball bearing 41 provided with an inner ring, outer ring 43, balls 44 and a cage 45. The inner ring is provided with first/second annular members 46, 47.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a toroidal type continuously variable transmission used for transmitting power of a vehicle such as an automobile, a vehicle transmission having the toroidal type continuously variable transmission, and a toroidal type continuously variable transmission. The present invention relates to a rolling bearing used for a step transmission.

[0002]

2. Description of the Related Art Japanese Patent Publication No. 2638 discloses a transmission used for transmitting power of a vehicle such as an automobile.
No. 896 and JP-B-7-96901 are used.

[0003] This type of toroidal-type continuously variable transmission is provided with a casing, an input shaft rotatably driven by a drive source including an engine disposed in the casing, and a support that rotates in conjunction with the input shaft. A pair of input disks, a pair of output disks disposed opposite to each of these input disks, a power roller provided between these input / output disks, and a pair of input / output disks inserted in a direction approaching each other. And a pressing mechanism for pressing at least one of the output disks.

[0004] The pair of input disks are rotationally driven by a drive source including an engine. The pair of output disks are arranged with their backs facing each other.
The output disk transmits power based on the rotation of the input disk via a power roller or the like. The output disk is rotatably supported by the input shaft and rotates in conjunction with the output gear.

The output gear is rotatably supported in the casing by two angular ball bearings. The angular ball bearing is provided along the input shaft along the axis.

[0006] The power roller is swingably provided between the input disk and the output disk, and is in rolling contact with both disks. By changing the inclination angle of the power roller, the reduction ratio of the toroidal-type continuously variable transmission can be changed.

[0007] The pressing mechanism presses the input / output disks in directions approaching each other, and transmits the rotational driving force supplied from the drive source to an output shaft via an input disk, a power roller, an output disk, and the like. .

[0008]

However, the aforementioned Japanese Patent Publication No. 2638896 and Japanese Patent Publication No. 7-96901
In the toroidal-type continuously variable transmission disclosed in Japanese Patent Laid-Open Publication No. H11-207, an output gear is rotatably supported by using two angular ball bearings provided along an axis of an input shaft. For this reason, the dimension tends to increase along the axis of the input shaft.

In particular, when it is used as a transmission for an engine having a relatively large displacement, it is necessary to increase the thickness of each member such as an input / output disk in order to cope with the engine having a large displacement. For this reason, the dimension along the axis has tended to be further increased. For example, it is necessary to increase the thickness of the portion where the thickness along the axis of the output disk becomes thinnest.

Further, in the toroidal-type continuously variable transmission disclosed in Japanese Patent Publication No. 7-96901, a counterbore portion formed concavely from the back surface is formed on one of the pair of output disks. ing. The angular ball bearing supports an output disk and an output gear when inserted in the counterbore. The outer shapes of the pair of output disks are different from each other.

For this reason, the cost of manufacturing these output disks tends to increase. Further, when the pressing mechanism presses the input / output disks in directions approaching each other, a thrust load is applied to the output disk along the axis. When this thrust load is applied, the output disks have different shapes, and these output disks are elastically deformed into different shapes.

In particular, the state of deformation at the place where the output disk and the power roller contact each other is different from each other. For this reason, transmission of power between the cavities arranged along the axis of the input shaft becomes difficult to synchronize,
The behavior of each trunnion in the front and rear cavities becomes unstable, and becomes uncontrollable in the worst case. Also,
When the counterbore portion is formed on the output disk, the durability against the thrust load described above tends to decrease.

Further, a load in the thrust direction acts on the output gear from a gear meshing with the output gear, and a moment generated by the thrust load acts on the output gear. When such a moment acts, the ball of the angular ball bearing that supports the output gear rotates in the circumferential direction while slightly moving along the axis.

For this reason, the cage for holding the rolling element of the angular ball bearing may collide with the rolling element, and the cage may be damaged. In addition, since the rolling element rotates along the circumferential direction while slightly moving along the axis, the retainer restrains the movement of the rolling element, causing slip when the rolling element rolls, and The life tends to be short.

Accordingly, a first object of the present invention is to provide a toroidal-type continuously variable transmission that can be reduced in size, and an automobile transmission including the toroidal-type continuously variable transmission. A second object is to provide a rolling bearing that can suppress a reduction in life when used in a toroidal-type continuously variable transmission.

[0016]

In order to solve the above-mentioned problems and to achieve the first object, a toroidal-type continuously variable transmission according to the present invention according to claim 1 is provided with a casing and a casing. An input shaft that is rotationally driven from a drive source,
A pair of output disks rotatably supported on the input shaft with the rotational driving force transmitted from the drive source transmitted and the back surfaces facing each other, and a pair of output disks arranged between the back surfaces of the pair of output disks. An output gear that works with
And a rolling bearing that rotatably supports the output gear in the casing around the axis of the input shaft, wherein the rolling bearings are in contact with each other and are provided along the axis. A rolling element having a first ring member and a second ring member and being fixed to the output gear, an outer ring fixed to a casing, and a rolling element rotatably provided between the inner ring and the outer ring; And a retainer for holding the rolling element between an inner ring and an outer ring, wherein the output gear is rotatably supported using only one of the rolling bearings.

Similarly, in order to achieve the first and second objects, a toroidal-type continuously variable transmission according to a second aspect of the present invention is the toroidal-type continuously variable transmission according to the first aspect. At least one of end surfaces of the inner ring of the bearing, the first ring member and the second ring member, which are in contact with each other, is formed to be concave from these end surfaces and guides the lubricant between the inner ring and the outer ring. , And a second lubricant introduction passage formed in the output gear and supplying the lubricant into the first concave groove.

Similarly, in order to achieve the first and second objects, a toroidal-type continuously variable transmission according to a third aspect of the present invention is the toroidal-type continuously variable transmission according to the second aspect, wherein The retainer of the bearing is provided with a pocket for rotatably holding the rolling element, and the pocket is formed in an elongated hole along the axis.

According to another aspect of the present invention, there is provided a toroidal-type continuously variable transmission according to the present invention, wherein the inner race of the rolling bearing is provided. A first race member and a second race member, respectively, comprising a first race groove and a second race groove which are opposed to each other when they are arranged in contact with each other, and The first track groove of the ring member and the first track groove of the second ring member have different curvature radii from each other.

In the toroidal type continuously variable transmission according to the first aspect, only one rolling bearing is used when the output gear is rotatably supported with respect to the casing, so that the output gear runs along the axial direction of the input shaft. An increase in size can be suppressed.
Further, the inner ring of the rolling bearing includes a first ring member and a second ring member which are in contact with each other and are provided side by side along the axis. For this reason, the rolling bearing is a three-point contact ball bearing in which the inner ring is divided into two along a plane perpendicular to the axis.

Therefore, even if a load is applied along the axis of the input shaft via the output gear or the like, the rolling bearing can support the load in the thrust direction, and positions and supports the output gear at a predetermined position. be able to.

In the toroidal-type continuously variable transmission according to the second aspect, at least one of the first ring member and the second ring member constituting the inner ring guides the lubricant between the inner ring and the outer ring. The output gear includes a first groove and a second groove for guiding the lubricant into the first groove. For this reason, the lubricant can be reliably guided between the inner ring and the outer ring, so that the rolling bearing can be prevented from seizing and the life can be prevented from being shortened.

In the toroidal-type continuously variable transmission according to the third aspect, the pocket of the cage of the rolling bearing is formed in an elongated hole along the axis. For this reason, even when a thrust load is applied via an output gear or the like and the rolling element is slightly displaced along the axis when rolling along the circumferential direction, the displacement along the axis of the rolling element is reduced. Do not hinder. For this reason, it is suppressed that a cage and a rolling element contact each other and a cage is damaged. Therefore, it is possible to suppress a decrease in the life of the cage and the rolling bearing.

In the toroidal-type continuously variable transmission according to a fourth aspect, the radius of curvature of the first raceway groove of the first wheel member and the radius of curvature of the second raceway groove of the second wheel member are different from each other. .
At this time, of the first and second wheel members, the radius of curvature of the raceway groove of the wheel member that supports the thrust load acting from the output gear or the like less frequently is increased, and the aforementioned thrust load is reduced. It is desirable to reduce the radius of curvature of the raceway groove of the ring member that is less frequently supported.

In this case, the contact area with the ball in the raceway groove of the ring member that supports the thrust load less frequently is reduced, and the contact area with the ball in the raceway groove of the ring member that supports the thrust load more frequently is reduced. Becomes larger. Therefore, the pressure generated between the raceway groove and the ball when the first ring member supports the thrust load, and the pressure generated between the raceway groove and the ball when the second ring member supports the thrust load. Since the pressures approach each other, it is possible to suppress power loss in the rolling bearing.

[0026]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to FIG.
A description will be given with reference to FIG.

FIG. 1 shows a double-cavity half-toroidal continuously variable transmission 3 as a toroidal continuously variable transmission.
FIG. 2 is a cross-sectional view showing a part of a vehicle transmission 31 provided with a zero.

The automobile transmission 31 is shown in FIG.
As shown in FIG. 1, a double-cavity half-toroidal continuously variable transmission 30 is provided. As shown in FIG. 1, a double-cavity half-toroidal-type continuously variable transmission 30 includes a casing 4, an input shaft 1 rotated by a drive source E including an engine and the like, and a pair of input disks 2
a, 2b, a pair of output disks 3a, 3b, a plurality of power rollers 10, and a loading cam mechanism 6 as a pressing mechanism.

The casing 4 accommodates therein a toroidal-type continuously variable transmission 30 and the like. In FIG. 1, only a part of the casing 4 is shown. Input shaft 1 is
It is housed in the casing 4. The input shaft 1 is formed in a tubular shape. The input shaft 1 has one end 1a at its inner periphery.
Is supplied with a lubricant.

The input disks 2a and 2b are connected to the input shaft 1,
The input shafts 1 are arranged at intervals along the axis P of the input shaft 1. The input disks 2a and 2b are supported so as to face each other. The input disks 2a, 2b are arranged coaxially with each other.

The input disks 2a, 2b are arranged coaxially with the input shaft 1. The input disks 2a and 2b are attached to the input shaft 1 by ball spline engagement portions, and rotate in conjunction with the input shaft 1. Input disk 2a,
2b is provided slidably along the axis P of the input shaft 1.

The output disks 3a and 3b are provided between the pair of input disks 2a and 2b.
They are provided facing each other. Output disk 3
a, 3b are arranged with their back surfaces 5a, 5b facing each other. The output disks 3a and 3b are supported in a state of being loosely fitted to the input shaft 1. Output disk 3
a, 3b are arranged coaxially with each other and rotate synchronously with each other.

The back surface 5 of these output disks 3a, 3b
An output gear 34 is arranged between a and 5b. The output gear 34 is arranged coaxially with the output disks 3a and 3b and in a state of being loosely fitted to the input shaft 1. The output gear 34 includes a cylindrical portion 35 that loosely fits on the input shaft 1, and a tooth portion 37 protruding from the cylindrical portion 35 toward the outer periphery and having teeth 36. The output gear 34 is connected to the output disks 3a and 3b by spline engagement.
The output disks 3a and 3b and the output gear 34 rotate in conjunction with each other.

The output gear 34 is rotatably supported around the axis P of the input shaft 1 by a three-point contact ball bearing 41 as a rolling bearing in the casing 4. Output gear 34
Is rotatably supported by one three-point contact ball bearing 41. The three-point contact ball bearing 41 includes an annular inner ring 42, an annular outer ring 43 having an inner diameter larger than the outer diameter of the inner ring 42, and a ball 44 as a rolling element.
, A retainer 45 and the like.

The inner ring 42 includes a first ring member 46 and a second ring member 47 each formed in an annular shape. The inner and outer diameters of the first ring member 46 and the second ring member 47 are substantially the same. As shown in FIG. 2, the first ring member 46 and the second ring member 47 are arranged such that the end faces 46 a and 47 a are in contact with each other and fitted on the outer periphery of the cylindrical portion 35 of the output gear 34. .

When the end surfaces 46a and 47a are brought into contact with each other, the first ring member 46 and the second ring member 47 form a first raceway groove 48 and a second raceway groove 49 which are opposed to each other.
And The first raceway groove 48 extends over the outer peripheral surface of the first ring member 46 and the end surface 46a.
6 is formed over the entire circumference. First track groove 48
Are formed in an arc-shaped cross section.

The second raceway groove 49 is formed over the entire outer periphery of the second ring member 47 over the outer peripheral surface and the end surface 47a of the second ring member 47. The second raceway groove 49 is formed in an arc-shaped cross section.

In the illustrated example, of the first and second wheel members 46 and 47, the first wheel member 46 close to the drive source E is provided.
Is a front wheel member, and the second wheel member 47 located on the side remote from the drive source E is a rear wheel member.

The outer ring 43 is disposed so as to fit in the casing 4. The outer race 43 is provided with a raceway groove 50 having an arc-shaped cross section on its inner peripheral surface. The ball 44 is rotatably arranged between the inner ring 42 and the outer ring 43. The ball 44 is rotatable in the first and second raceway grooves 48 and 49 of the inner race 42 and the raceway groove 50 of the outer race 43.

The retainer 45 is formed in an annular shape.
The ball 44 is rotatably held between the inner ring 42 and the outer ring 43. As shown in FIG. 3, the retainer 45 has pockets 51 arranged at equal intervals along the circumferential direction. The pocket 51 penetrates the retainer 45. Pocket 51
Holds the ball 44 on its inner periphery in a freely rolling manner. The pocket 51 is formed in an elongated hole along the axis P of the input shaft 1, as shown in FIG.

In the case shown in FIG.
1 is formed as an elongated hole including a parallel portion 52 along the axis P and arc portions 53 provided at both ends of the parallel portion 52. In the case shown in FIG.
Is formed in a long hole of an elliptical shape whose longitudinal direction is along the axis P. With the above-described configuration, the ball 44 is held in the pocket 51 so as to be movable along the axis P.

Further, an end surface 46a of the first ring member 46,
At least one of the end surfaces 47a of the second ring member 47 has, as shown in FIG.
A concave groove 54 formed to be concave from FIG. In the illustrated example, the concave groove 54 is formed on both the end surfaces 46a and 47a. These concave grooves 54 are formed on the end surfaces 46a,
When the members 47a come into contact with each other, they oppose each other. These concave grooves 54 can guide the lubricant between the inner ring 42 and the outer ring 43. The concave groove 54 forms a first lubricant introduction path.

The output gear 34 and the input shaft 1 are provided with a second lubricant introduction passage 55 and the like. The second lubricant introduction passage 55 is located 3 m from the inner peripheral surface of the input shaft 1.
The lubricant is led over the groove 52 of the inner ring 42 of the point contact ball bearing 41.

A driven gear 38 is engaged with the teeth 36 of the teeth 37 of the output gear 34. The driven gear 38 is supported on an output shaft 39 arranged in parallel with the input shaft 1. The output shaft 39 extracts a rotational driving force based on the input shaft 1. The driven gear 38 and the output shaft 39 are fixed to each other by spline engagement or the like. The driven gear 38 and the output shaft 39 rotate in conjunction with each other. With the above-described configuration, the output gear 34 rotates in conjunction with the output shaft 39.

The output gear 34 and the driven gear 38 are helical gears. Therefore, the output gear 3
When the gear 4 and the driven gear 38 mesh with each other and rotate in association with each other, thrust loads T1 and T2 along the axis P and in opposite directions are applied.

In the illustrated example, a thrust load is applied to the output gear 34 in a direction away from the drive source E along the arrow T1 in the figure. A thrust load is applied to the driven gear 48 in a direction approaching the drive source E along the arrow T2 in the drawing.

Therefore, when the above-described thrust load T1 acts on the output gear 34, the output gear 34 tries to slide together with the inner ring 42 in a direction away from the drive source E along the thrust load T1. Then, the raceway groove 48 of the first ring member 46 of the first ring member 46 and the second ring member 47 constituting the inner ring 42 mainly comes into contact with the ball 44, thereby reducing the thrust load T1 described above. Will support.
Therefore, the first raceway groove 48 of the first ring member 46 mainly supports the thrust load T1, and positions and supports the output gear 34 at a predetermined position.

Therefore, in the illustrated example, the first ring member 4
Of the 6 and the second ring members 47, the frequency of the first ring member 46 contacting the ball 44 is higher. Second ring member 47
The frequency of contact with the ball 44 decreases.

The power roller 10 includes the input disks 2a, 2
b and between the output disks 3a and 3b. The power roller 10 is in rolling contact with both disks 2a, 2b, 3a, 3b. The power roller 10 includes a traction portion 10a that comes into contact with the input disks 2a and 2b and the output disks 3a and 3b, respectively.

The input disks 2a and 2b and the output disk 3
The trunnions 8 are provided between the trunnions 8a and 3b, respectively. The trunnion 8 can swing about the pivot 7 in the direction indicated by the arrow R in FIG. Trunnion 8
Is provided with a displacement shaft 9 at the center thereof. A power roller 10 is rotatably supported on each of the displacement shafts 9. These power rollers 10 change the inclination angle between the input disks 2a, 2b and the output disks 3a, 3b according to the speed ratio of the toroidal-type continuously variable transmission 30.

A thrust ball bearing 1 functioning as a power roller bearing is provided between the trunnion 8 and the power roller 10.
1 is provided. The thrust ball bearing 11 supports a load in the thrust direction applied to the power roller 10 from the input disks 2a and 2b and the output disks 3a and 3b, and allows the power roller 10 to rotate. Thrust ball bearing 11
Are held by an annular holder 14. The retainer 14 is provided between the annular outer ring 13 provided on the trunnion 8 and the power roller 10 as a rotating unit.

As shown in FIG. 1, the loading cam mechanism 6 is provided on the back surface 15a side of one of the input disks 2a and 2b.

The loading cam mechanism 6 is connected to the input shaft 1.
A loading cam 21 and a cam roller 22 are supported. Loading cam 21
Is provided on the back surface 15a side of the input disk 2a. The surface of the loading cam 21 facing the input disk 2a has a cam surface 2 formed with irregularities along the circumferential direction.
3 are formed. The loading cam 21 rotates in conjunction with the driving source E. The loading cam 21 is rotatably supported on the input shaft 1 by a ball bearing 24.

The cam roller 22 includes a loading cam 21.
And the input disk 2a. The cam roller 22 is provided so as to be rotatable around an axis Q along the radial direction with respect to the axis P of the input shaft 1. Cam roller 22
Are arranged around the axis P of the input shaft 1.

With the above-described configuration, when the loading cam 21 rotates in conjunction with the driving source E including the engine, the loading cam mechanism 6 rotates.
One cam surface 23 presses the plurality of cam rollers 22 toward the input disk 2a. And the input / output disk 2
The input disk 2a is pressed via the cam roller 22 in a direction in which the input disks 2a, 2b, 3a, 3b approach each other.

According to the configuration described above, the double-cavity half-toroidal continuously variable transmission 30 of the present embodiment is used.
The output gear 34 is driven by one three-point contact ball bearing 41.
Are rotatably supported in the casing 4. Therefore, an increase in the dimension of the input shaft 1 along the axis P is suppressed. In addition, the three-point contact ball bearing 41 is
Therefore, the thrust load T1 generated by the engagement between the output gear 34 and the driven gear 38 can be reliably supported.

Further, between the inner ring 42 and the outer ring 43 of the three-point contact ball bearing 41, the lubricant supplied from one end 1 a of the input shaft 1 passes through the second lubricant introduction path 55 and the concave groove 54. Led. Therefore, seizure of the three-point contact ball bearing 41 can be suppressed, and a reduction in the life of the three-point contact ball bearing 41 can be suppressed.

Further, the aforementioned thrust load T1 acts on the output gear 34, and the output gear 34
1 is positioned. For this reason, FIG.
As shown in FIG. 5, the tooth portion 37 of the output gear 34 located on the side where the driven gear 38 meshes is urged in the direction away from the drive source E, and the tooth portion located on the side of the output gear 34 remote from the driven gear 38. The portion 37 is urged in a direction approaching the drive source E, and the bending moment along the arrow M in the figure is output.
Act on.

Then, as shown in FIG. 4 (B), the ball 44 of the three-point contact ball bearing 41 is aligned with the center line of the first and second raceway grooves 48 and 49 or the raceway groove 50 of the outer race 43 which are opposed to each other. While displacing along the axis P from C, the above-described raceway groove 4
Roll inside 8,49,50. At this time, since the pocket 51 of the retainer 45 is formed in a long hole along the axis P, it is possible to suppress the displacement of the ball 44 along the axis P. In addition, contact between the inner periphery of the pocket 51 and the ball 44 is also suppressed. Therefore, breakage of the retainer 45 is suppressed, and a reduction in the life of the three-point contact ball bearing 41 is suppressed.

In this embodiment, as shown in FIG. 5, a first raceway groove 48 of a first ring member 46 of the inner ring 42 is provided.
It is desirable that the radius of curvature Rif of the second ring member 47 and the radius of curvature Rir of the second raceway groove 49 of the second ring member 47 be different from each other. In this case, of the curvature radii Rif and Rir of the raceway grooves 48 and 49, the thrust load T generated by the engagement between the output gear 34 and the driven gear 38 described above.
It is desirable to support 1 and to form the one with less frequency of contact with the ball 44 larger, and to form the one with higher frequency relatively smaller. Then, the ball 44 of the raceway grooves 48 and 49 is
The contact area with the ball 44 increases as the frequency of contact with the ball 44 increases, and the contact area with the ball 44 decreases as the frequency of contact with the ball 44 decreases.

In the illustrated example, the first raceway groove 48 of the first wheel member 46 as the front wheel member is the ball 44.
Contact with the second ring member 47,
Of the raceway groove 49 of the first ring member 46 is formed to be larger than the radius of curvature Rif of the raceway groove 48 of the first ring member 46.
For this reason, the radius of curvature Rir of the second raceway groove 49 and the radius of curvature Rif of the first raceway groove 47 satisfy Expression 1 below.

Rir> Rif Equation 1 As described above, of the raceway grooves 48 and 49, the one that contacts the ball 44 more frequently has a larger contact area with the ball 44 and makes contact with the ball 44. Since the smaller the frequency, the smaller the contact area with the ball 44, the pressure generated when the ball 44 contacts the ball 44 with the higher frequency and the smaller ball 44 contacted with the ball 44 less frequently. And the pressure generated when it comes into contact with the object. Therefore, of the ring members 46, 47 of the inner ring 42, the one having a higher frequency of contact with the ball 44 can suppress the amount of heat generated, and the three-point contact ball bearing 41.
The calorific value generated as a whole can also be suppressed. Three-point contact ball bearing 41
Can be more reliably suppressed from being shortened.

In the present invention, it is conceivable to use a deep groove ball bearing in place of the three-point contact ball bearing 41 described above. However, this deep groove ball bearing is large along the axis P of the input shaft 1. Therefore, in the toroidal-type continuously variable transmission 30, the torque input from the input shaft 1 such as the engine brake changes abruptly to change the output gear 3.
In a situation where the input is made from the fourth side, the direction of the thrust force generated in the output gear 34 and the driven gear 28 changes rapidly.

For this reason, the output disks 3a and 3b move along the axis P of the input shaft 1. When these output disks 3a and 3b move, the stability of the toroidal-type continuously variable transmission 30 may be lost, leading to an unstable control. Therefore, when a deep groove ball bearing is used, it is necessary to perform the speed change control of the toroidal-type continuously variable transmission 30 in consideration of the occurrence of this unstable control situation.

[0065]

According to the toroidal type continuously variable transmission described in claim 1, only one rolling bearing is used when the output gear is rotatably supported with respect to the casing.
It is possible to suppress an increase in the dimension of the input shaft along the axial direction.

Further, since the rolling bearing is a three-point contact ball bearing, it is possible to support a thrust load acting from the output gear, and to reliably support the output gear by positioning it at a predetermined position.

According to the toroidal-type continuously variable transmission according to the second aspect, in addition to the effect of the first aspect, the lubricant can be reliably introduced between the inner ring and the outer ring, and the rolling bearing is seized. Can be suppressed, so that a reduction in the life can be suppressed.

According to the toroidal-type continuously variable transmission according to the third aspect, in addition to the effect of the second aspect, the rolling element does not hinder the displacement along the axis when rolling along the circumferential direction. Accordingly, the cage and the rolling elements are prevented from contacting each other and the cage from being damaged. Therefore, it is possible to suppress a decrease in the life of the cage and the rolling bearing.

According to the toroidal-type continuously variable transmission according to the fourth aspect, in addition to the effect of the first aspect, the pressure generated when the first wheel member supports the thrust load and the second wheel member And the pressure generated when supporting the thrust load,
Since they approach each other, it is possible to suppress power loss in the rolling bearing.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing a part of an automotive transmission using a double-cavity half-toroidal-type continuously variable transmission according to an embodiment of the present invention.

FIG. 2 is a perspective view of the toroidal continuously variable transmission shown in FIG.
FIG. 4 is a developed view showing an inner ring of the point contact ball bearing developed in a circumferential direction.

FIG. 3 is a perspective view of the toroidal continuously variable transmission shown in FIG. 1;
FIG. 4 is a development view showing a cage of the point contact ball bearing developed in a circumferential direction.

FIG. 4 is a diagram showing a state in which a bending moment acts on an output gear of the toroidal-type continuously variable transmission shown in FIG. 1;

FIG. 5 is a perspective view of the toroidal-type continuously variable transmission shown in FIG.
Sectional drawing which shows the modification of a point contact ball bearing.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Input shaft 2a, 2b ... Input disk 4 ... Casing 3a, 3b ... Output disk 5a, 5b ... Back side of output disk 30 ... Double cavity type toroidal type continuously variable transmission (Troidal type continuously variable transmission) 34 ... Output gear 41 ... three-point contact ball bearing (rolling bearing) 42 ... inner ring 43 ... outer ring 44 ... ball (rolling element) 45 ... retainer 46 ... first ring member 46a ... end face 47 ... second ring member 47a ... end face 48 ... First track groove 49 ... Second track groove 51 ... Pocket 54 ... Groove (first lubricant introduction path) 55 ... Second lubricant introduction path E ... Drive source

 ────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Takashi Imanishi 1-5-50 Kugenuma Shinmei, Fujisawa-shi, Kanagawa Japan Seiko Co., Ltd. F-term (reference) 3J051 AA03 AA08 BA03 BB02 BE09 CA05 CB07 ED08 FA02

Claims (4)

[Claims] A casing; an input shaft disposed in the casing and driven to rotate by a drive source; and a rotary drive force from the drive source transmitted to the input shaft and rotated by the input shaft in a state in which the back faces each other. A pair of output discs freely supported, an output gear disposed between the back surfaces of the pair of output discs and interlocking with these output discs, and the output gear is rotatably supported in the casing around the axis of the input shaft. A toroidal-type continuously variable transmission, comprising: a first wheel member and a second wheel member that are in contact with each other and are provided side by side along the axis; An inner ring fixed to the gear, an outer ring fixed to the casing, a rolling element rotatably provided between the inner ring and the outer ring, and holding the rolling element between the inner ring and the outer ring. And a retainer, the rolling bearing toroidal type continuously variable transmission, characterized in that for rotatably supporting the output gear with one only. 2. An inner ring of said rolling bearing, wherein at least one of end surfaces of said first and second ring members which are in contact with each other is formed to be concave from said end surfaces, and between said inner and outer rings. And a second lubricant introduction passage formed in the output gear and supplying the lubricant into the first groove. The toroidal-type continuously variable transmission according to claim 1. 3. The rolling bearing cage according to claim 2, further comprising a pocket for rotatably holding the rolling element, wherein the pocket is formed in an elongated hole along the axis. Toroidal continuously variable transmission. 4. The first race member and the second race member of the inner race of the rolling bearing are respectively in contact with each other when the first race member and the second race member are provided in contact with each other. A raceway groove, wherein the first raceway member of the first ring member and the first raceway groove of the second ring member have different radii of curvature. 2. The toroidal-type continuously variable transmission according to 1.