JP2001108043A - Toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To offset thrust loads in a transmission unit and to prevent unforeseen change from occurring in the change gear ratio caused by strain or twist in a gearbox casing. SOLUTION: In a toroidal type continuously variable transmission tiltably pivoting a power roller 3 interposed between an input and an output disk 1, 2 by a trunnion 4, mutually connecting the both ends of the trunnion 4 by links 7, 8, oscillatably supporting the links 7, 8 by a link post 10 provided inside a gearbox case 100, and clamping the roller 3 between the input and output disks 1, 2 by a presser force generated by a cam flange 5 arranged in the rear face of the disk 1 according to the drive source, the input and output disks 1, 2 and a loading cam are rotatably supported by a fixed shaft 21 so that thrust loads FK1, FK2 are completely offset in the fixed shaft 21 integrally formed with the post 10 and prevent any load from transmitted to the case 100.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a toroid in which a friction roller interposed between a first disk and a second disk disposed coaxially and opposed to each other is pressed by a pressing force generated by a loading cam according to a driving source. The present invention relates to a type of continuously variable transmission.

[0002]

2. Description of the Related Art A toroidal type continuously variable transmission includes a main shaft, an input disk (first disk) and an output disk (second disk).
The speed change ratio can be continuously changed by a speed change unit including a disc, a loading cam, and a power roller (friction roller). As such a transmission unit, for example, Japanese Patent Application Laid-Open No.
There are FIGS. 5 and 6 described in Japanese Patent No. 47448.

FIG. 5 is a sectional view showing a toroidal type continuously variable transmission attached to the above-mentioned publication, and FIG. 6 is a sectional view taken along the line XX of FIG.

Here, the basic operation of the toroidal-type continuously variable transmission will be described with reference to FIGS. The toroidal-type continuously variable transmission is a single-cavity type in which a pair of input disks 1 and output disks 2 formed in a toroidal shape are arranged coaxially with an input shaft (first rotation shaft) 14. By changing the inclination angle of the pair of power rollers 3 sandwiched and pressed between the disk 1 and the output disk 2, an arbitrary gear ratio is set in a stepless manner.

[0005] The input disk 1 is supplied to the input shaft 1 via a cam roller 6 and a cam flange 5 as urging means for generating an axial propulsion force for pinching and pressing the power rollers 3 and 3.
4, the input shaft 14 is rotatably supported by an input bearing 35 interposed between the input shaft 14 and a bearing support member 100B provided on the inner periphery of the case 100. On the other hand, the output disc 2 has an output gear 9 on the rear side (right side in the figure).
And is rotatably supported relative to the input shaft 14 and is supported by an output bearing 45 interposed between the output gear 9 and the bearing support member 100B. In order to support the thrust load and the radial load for pinching and pressing of No. 3, it is constituted by a tapered roller bearing (roller bearing) or the like.

The power rollers 3, 3 are trunnions 4A, which are roller support members that can be displaced in the axial direction and around the axis.
4B, the trunnions 4A, 4B
Is driven in the axial direction by actuators 60, 60 provided at the ends, and controls the tilt angle of the power rollers 3, 3, that is, the gear ratio.

The trunnions 4A and 4B are driven synchronously in the opposite directions. For example, when the trunnion 4A is driven rightward in FIG. 5, the trunnions 4B are driven leftward in the figure, and the trunnions 4A and 4B are driven. To synchronize
Links 7, 8 for connecting the trunnions 4A, 4B with the power rollers 3, 3 therebetween are provided.

The links 7 and 8 are connected to a swing shaft 7 at the center.
It is swingably supported by a link post 10 connected to the case 100 via A and 8A. As shown in FIG. 6, both ends of the link post 10 are fastened via a bolt B by a link post support member 100A protruding from the inner periphery of the case 100, and act on the pair of links 7, 8. The link post 10 and the input / output bearings 35 and 45 are supported by a case 100.

[0009] A case 10 is provided through the link post 10.
When the force applied to zero is considered based on the conceptual diagram of FIG. 7, the thrust load F1 generated by the cam roller 6 in response to the rotation of the input shaft 14 presses the input disk 1 and the cam flange 5, and The transmitted thrust load F1 is transmitted to the input bearing 35 via the input shaft 14.

Then, the input disk 1 is connected to the power roller 3
Is the component force of the thrust load F1 generated by the cam roller 6, and when the number of the power rollers 3 is n, the component force Fc is expressed by the following equation.

Fc = Fc / (n · sin φ) (1) where φ is the tilt angle of the power roller 3.

The power roller 3 is connected to the output disk 2.
Is pressed by the load Fc, the thrust load F2 which is an axial component of the load acting on the output disk 2 is as follows.

F2 = n · Fc · sin (2θ−φ) (2) where θ is a contact angle between the input / output disks 1 and 2 with respect to the rotation axis of the power roller 3 as shown in FIG.

The thrust load F2 is transmitted to the output bearing 45 via the output gear 9.

Here, the thrust loads F1, F2 acting on the input / output bearings 35, 45 are opposite in the direction of the force.
The load Fk1 acting on the case 100 via the bearing support member 100B is as follows: Fk1 = F1−F2 (3), and the load Fk1 applied to the case 100 is Fk1 = F1−n · Fc · sin (2θ−φ) = F1−n · F1 / (n · sinφ) · sin (2θ−φ) = F1 (1−sin (2θ−φ) / sinφ) = F1 (2cos2θ · sinφ−2sinθ · cosθ · cosφ) / sinφ ... (4) ), The thrust load F1 generated by the cam roller 6 and
The value corresponds to the tilt angle φ of the power roller 3.

On the other hand, the load F acting on the trunnions 4A and 4B
t is the load applied to the power roller 3,
Ft = 2Fc cos θ (5)

The links 7 and 8 support the trunnions 4A and 4B disposed opposite to each other, and have a power roller axial component F
Of the t, the radial component Fr of the input shaft 14 is the trunnion 4
A and 4B are directed toward the outer peripheral side of each other, and are offset by the links 7 and 8.

However, the axial component Fp of the input shaft 14 of the power roller axial component Ft is the trunnion 4A,
The thrust load Fk2 transmitted from 4B to the case 100 via the links 7, 8 and the link post 10 and applied to the case 100 from the link post 10 is Fp = Ft · sin (θ−φ) (6) Fk2 = n · Fp = n · Ft · sin (θ−φ) = n · 2Fc · cos θ · sin (θ−φ) = n · 2F1 / (n · sinθ) · cosθ · sin (θ−φ) = 2F1 (cosθ · sin (θ−φ)) / sinφ = 2F1 (2sinθ · cosθ · cosφ−2sin2θ · sinφ)) / sinφ (7)

Therefore, the load Fk1 applied to the bearing support member 100B supporting the input / output bearings 35, 45
And the thrust load Fk2 applied to the case 100 from the link post 10 via the link post support member 100A is:
Fk1 + Fk2 = 0, and acts on the case 100 as forces of the same magnitude and opposite directions.

FIG. 8 is a conceptual diagram of FIG. 6, and the same parts as those of FIGS.
As is clear from the above description, points A and C where the case 100 supports the input shaft 14 are located near the transmission unit.
There is a point B where the case 100 supports the link post 10, a load Fk1 occurs at the point A, and the load Fk2 is equally distributed to each of the points B to maintain the balance of the forces.

However, in an actual toroidal-type continuously variable transmission, the case is usually made of a thin aluminum material or the like in order to reduce the size and weight. For example, as shown in FIG. The lower part (thickness t2) of the case has a greater thickness (t1 <t) than the upper part (thickness t1) of 100.
2), the shape of the transmission case 100 may not be uniform.

In such a transmission case 100,
When the driving force from the engine increases, the thrust load F
When k1 and Fk2 cancel each other out in the transmission case 100, the deformation that occurs in the thin case upper portion becomes larger than that in the thick case lower portion. Therefore, as shown in FIG.
It is necessary to consider that distortion or torsion occurs at zero.

In such a case, the supporting points are the areas A, B, C
8 (see FIG. 8), as shown in regions A ', B', and C '(see FIG. 9), and the support state of the transmission unit changes, so that each of the components of the transmission unit is deformed and Causes a tilt. If the symmetry of the input / output disk is lost, the speed ratios of the power rollers are not equivalent, so that the speed ratio may change.

[0024]

The problem to be solved by the present invention has been made in view of the above-mentioned fact, and a toroidal type continuously variable transmission capable of canceling a thrust load in a transmission unit has been developed. The purpose is to provide.

[0025]

To this end, a toroidal-type continuously variable transmission according to the first invention comprises a plurality of friction rollers interposed between a first disk and a second disk which are coaxially opposed to each other. Each of the roller supporting members is pivotally supported so as to be tiltable, the ends of the roller supporting members are connected to each other by link members, and these link members are swingably supported by link posts provided in the transmission case. ,
By urging the first disk in the direction of the second disk by a pressing force corresponding to a driving source generated by a loading cam disposed on the back surface of the first disk, the friction roller is moved to the first disk. And a toroidal-type continuously variable transmission that clamps between the second disk and the first disk and the second disk;
The loading cam is rotatably supported by a fixed shaft fixed to the link post.

A toroidal-type continuously variable transmission according to a second aspect of the present invention, in the first aspect, wherein the fixed shaft is located on the output side of the disk on the input side with respect to the link post. It is characterized in that the shaft diameter in the direction region is increased.

In a toroidal type continuously variable transmission according to a third aspect of the present invention, in the first or second aspect, the fixed shaft is a hollow shaft, and the space at the center portion and the outside penetrate and are supplied to the hollow space. And a through hole for discharging oil to the outside.

A toroidal type continuously variable transmission according to a fourth aspect of the present invention is the toroidal type continuously variable transmission according to any one of the first to third aspects, wherein the loading cam is provided between the loading cam and one end of the fixed shaft. No. supported on fixed shaft
1 A bearing is interposed, the bearing outer ring is attached to the loading cam, the bearing inner ring is attached to the fixed shaft, and the second disk is provided between the second disk and the other end of the fixed shaft. A second bearing supported by the fixed shaft is interposed, and a bearing outer ring is attached to the second disk, and a bearing inner ring is attached to the fixed shaft.

According to a fifth aspect of the present invention, in the toroidal type continuously variable transmission according to the fourth aspect, the first bearing and the second bearing are at least one roller bearing having a tapered roller interposed therebetween, and communicate with the through hole. Further, a communication hole for supplying lubricating oil to a tapered roller interposed between the first bearing and the second bearing is provided.

A toroidal-type continuously variable transmission according to a sixth aspect of the present invention is the first or second aspect of the invention, wherein the fixed shaft is a solid shaft, the first shaft engaging with the back surface of the loading cam.
A shaft and a second shaft engaged with the back surface of the second disk have a cylindrical shape surrounding an end of the fixed shaft, and are provided between a cylindrical end of the first shaft and one end of the fixed shaft. A first bearing for supporting the loading cam on the fixed shaft is interposed, and a bearing outer ring is attached to the loading cam, and a bearing inner ring is attached to the fixed shaft, and a cylindrical end of the second shaft is provided. A second bearing for supporting the second disk on the fixed shaft is interposed between the other end of the fixed shaft and the bearing outer ring is attached to the second disk, and a bearing inner ring is attached to the fixed shaft. It is characterized by being attached.

A toroidal-type continuously variable transmission according to a seventh aspect of the present invention, in any one of the first to sixth aspects, is characterized in that a flange-shaped portion is provided near an end of the fixed shaft. Things.

The toroidal-type continuously variable transmission according to an eighth invention is characterized in that, in the seventh invention, at least one of the flange-shaped portions provided near the end of the fixed shaft is constituted by a nut. is there.

In the toroidal type continuously variable transmission according to the ninth invention, a plurality of friction rollers interposed between the first disk and the second disk coaxially opposed to each other are supported by a roller support member so as to be tiltable. The ends of these roller support members are interconnected by link members, and these link members are swingably supported by link posts provided in the transmission case, and are disposed on the back surface of the first disk. By urging the first disk in the direction of the second disk by a pressing force generated by a loading cam and corresponding to a driving source, the friction roller is pressed between the first disk and the second disk. In the toroidal-type continuously variable transmission, a fixed shaft fixed to the link post extends in a direction in which the second disk is arranged,
A back surface of the second disk is rotatably supported by an inner edge of a second disk side end of the fixed shaft via a second bearing, and an intermediate shaft rotatably supports the first disk and the loading cam. Extends through the fixed shaft in the direction in which the second disk is arranged, and the extending end is rotatably supported by an outer edge of the second disk side end of the fixed shaft via a first bearing. It is characterized by being performed.

In a toroidal type continuously variable transmission according to a tenth aspect of the present invention, in the ninth aspect of the present invention, in the first bearing, the bearing outer ring is mounted on the fixed shaft, the bearing inner ring is mounted on the intermediate shaft, and the second bearing is mounted on the second shaft. The bearing has the bearing outer ring attached to the fixed shaft and the bearing inner ring attached to the second shaft.
It is characterized by being attached to a disk.

The toroidal type continuously variable transmission according to the eleventh invention is characterized in that in the ninth and tenth inventions, a flange-shaped portion is provided near an end of the intermediate shaft.

A toroidal-type continuously variable transmission according to a twelfth invention is characterized in that, in the eleventh invention, a flange-shaped portion provided near the loading cam side end of the intermediate shaft is formed of a nut. It is.

[0037]

In the toroidal type continuously variable transmission according to the first invention, the first disk and the second disk constituting the transmission unit and the loading cam are fixed to the link posts provided in the transmission case. Since it is rotatably supported by the fixed shaft, a thrust load Fk1 generated by the thrust load F1 generated by the loading cam and the thrust load F2 acting on the second disk, and a thrust applied to the transmission case from the link post. The load, that is, the thrust load Fk2 generated from the friction roller is offset as the internal force of the fixed shaft. That is, the thrust loads Fk1 and Fk2 generated when the first disk is urged in the direction of the second disk by the pressing force from the loading cam are all offset in the fixed shaft, and the transmission unit is stored. Do not transfer any load to the existing transmission case.

Therefore, according to the first aspect, the thrust load is canceled by the fixed shaft fixed to the link post, so that the transmission case can be prevented from being deformed due to the thrust load. In this case, it is possible to prevent the gear ratio from fluctuating due to the deformation of the transmission case.

When the thrust load is canceled by the fixed shaft, a tensile stress acts on the fixed shaft. This tensile stress acts on the portion of the fixed shaft from the link post to the output disk when the transmission ratio is large, and acts on the input disk from the link post to the input disk when the transmission ratio is small. Further, the tensile stress increases as the transmission ratio increases. For this reason, in the toroidal-type continuously variable transmission according to the second invention, the fixed shaft has a link post as a boundary, and has a shaft diameter in an axial region of the disk on the output side more than an axial region of the disk on the input side. Since the tensile stress generated in the fixed shaft is offset by increasing the value, the strength and durability of the fixed shaft are improved.

In the toroidal-type continuously variable transmission according to the third aspect of the invention, the fixed shaft is a hollow shaft, and the space at the center portion and the outside penetrate, and the oil supplied to the hollow space is discharged to the outside. With the provision of the through-hole, the oil pumped into the hollow space of the fixed shaft is supplied to the transmission unit via the through-hole, so that the respective parts of the transmission unit can be lubricated in one system. . In addition, since the fixed shaft does not rotate, it is easy to easily pump oil into the hollow space. Therefore, according to the third aspect, each part of the transmission unit can be easily lubricated with a simple structure.

Considering the stress generated in the transmission unit of the toroidal-type continuously variable transmission, a bending moment acts on the loading cam and the second disk in a direction opposite to that of the friction roller to cause distortion. It is known that Therefore, in the toroidal type continuously variable transmission according to the fourth invention, the outer ring of the first bearing is fixed to the loading cam, the outer ring of the second bearing is attached to the second disk, and the first bearing and the second bearing are mounted. By attaching the inner ring to the fixed shaft, the supporting diameter of the loading cam and the supporting diameter of the second disk are increased, so that the stress acting on the loading cam and the second disk is reduced, and distortion due to bending moment is reduced. Can be reduced. In this case, the distortion due to the bending moment can be reduced as the supporting diameter of the loading cam and the second disk increases.

In the toroidal-type continuously variable transmission according to the fifth invention, when the first bearing and the second bearing are roller bearings having tapered rollers, at least one of the bearings communicates with the through hole. Since it has a communication hole for supplying lubricating oil to the tapered roller, it is possible to effectively lubricate the sliding contact surface between the side surface of the rolling groove provided on the outer and inner rings of the bearing and the side surface of the tapered roller. it can. Therefore, according to the present invention, power loss due to friction between the side surface of the rolling groove provided on the outer and inner races of the bearing and the side surface of the tapered roller can be effectively reduced.

According to a sixth aspect of the present invention, in the toroidal-type continuously variable transmission, the first rotating shaft engaged with the back surface of the loading cam and the second rotating shaft engaged with the back surface of the second disk are connected to the end of the fixed shaft. The outer ring of the first bearing is fixed to the loading cam, the outer ring of the second bearing is attached to the second disk, and the inner rings of the first bearing and the second bearing are fixed to the fixed shaft. In this case, the supporting diameter of the loading cam and the supporting diameter of the second disk are increased, so that the stress acting on the loading cam and the second disk is reduced, and the distortion due to the bending moment can be reduced. . In this case, the distortion due to the bending moment can be reduced as the supporting diameter of the loading cam and the second disk increases. In addition, in the sixth invention, since the fixed shaft is a solid shaft, the loading cam, the first and second disks constituting the transmission unit, and the fixed shaft that rotatably supports these are formed. Increases rigidity.

In the toroidal-type continuously variable transmission according to the seventh aspect of the present invention, since the flange-shaped portion is provided near the end of the fixed shaft, the first disk is connected to the second disk by the pressing force from the loading cam. The thrust load generated when urging in the direction can be efficiently absorbed.

In the toroidal-type continuously variable transmission according to the eighth invention, since at least one of the flange-shaped portions provided near the end of the fixed shaft is formed of a nut, operations such as assembly and disassembly are easy.

In a toroidal type continuously variable transmission according to a ninth aspect of the present invention, a fixed shaft fixed to a link post provided in a transmission case extends in a direction in which the second disk is disposed. The inner surface of the disk-side end supports the back surface of the second disk rotatably via a second bearing, and the outer periphery of the second disk-side end of the fixed shaft connects the first disk and the loading cam. Since the second disk side extending end of the rotatably supported intermediate shaft is rotatably supported via a first bearing, a thrust load F1 generated by the loading cam and a thrust load F2 acting on the second disk. And a thrust load applied to the transmission case from the link post, that is, a thrust load F generated from the friction roller. k2 is the second on the fixed shaft
Canceled at the end on the disk side. In other words, the thrust load generated when the first disk is urged in the direction of the second disk by the pressing force from the loading cam is all offset in the fixed shaft, and the transmission case in which the transmission unit is accommodated. Do not transmit any load to

Therefore, according to the ninth aspect, since the thrust load is canceled by the fixed shaft fixed to the link post, deformation of the transmission case due to the thrust load can be prevented. In this case, it is possible to prevent the gear ratio from fluctuating due to the deformation of the transmission case.

In a toroidal type continuously variable transmission according to a tenth aspect of the present invention, in the first bearing, the bearing outer ring is attached to the fixed shaft, and the bearing inner ring is attached to the intermediate shaft which rotatably supports the loading cam. , The second
In the bearing, since the bearing outer ring is attached to the fixed shaft and the bearing inner ring is attached to the second disk, the supporting diameter of the intermediate shaft and the supporting diameter of the second disk are increased. The stress acting on the second disk is reduced, and the distortion due to the bending moment can be reduced. in this case,
As the support diameter of the intermediate shaft and the second disk increases, distortion due to bending moment can be reduced.

In the toroidal type continuously variable transmission according to the eleventh aspect of the present invention, since the flange-shaped portion is provided near the end of the intermediate shaft, the first disk is moved in the direction of the second disk by the pressing force from the loading cam. It is possible to efficiently absorb a thrust load generated at the time of urging.

In the toroidal type continuously variable transmission according to the twelfth aspect, the flange-shaped portion provided near the loading cam side end of the intermediate shaft is formed of a nut, so that operations such as assembly and disassembly are easy.

[0051]

Embodiments of the present invention will be described below in detail with reference to the drawings. In the toroidal-type continuously variable transmission to which the present invention can be applied, two friction rollers are arranged at equal intervals around the axis of the input / output disk. In the description of the present embodiment, the same elements as those in FIGS.

FIG. 1 is a sectional view conceptually showing a side view of a first embodiment of a toroidal type continuously variable transmission according to the present invention, wherein a first disk (an input disk in this embodiment) is disposed on an axis O1. 1) and a second disk (referred to as an output disk in this embodiment) 2 are opposed to each other, and two friction rollers (hereinafter referred to as power rollers) 3 are interposed between the input / output disks 1 and 2. The power roller 3 is supported by roller supporting members (hereinafter referred to as trunnions) 4A and 4B, respectively.
B is a link member (hereinafter referred to as a link)
The links 7 and 8 are connected to each other at 8 and supported by a link post 10 attached to the transmission case 100 so as to be swingable.

One end of the input shaft 11 has a cylindrical shape surrounding the end of the input shaft 11 and engages with the rear surface of the cam flange 5. The cam flange 5 is in contact with the rear surface of the input disk 1 via a cam roller 6 to form a loading cam. As a result, the loading cam generates a pressing force on the input disk 1 according to the drive source.

The input shaft 11 passes through a fixed shaft 21 formed integrally with the link post 10. Fixed shaft 21
The (link post 10) is connected to the link 7 via the pin P.
(8) and is attached to the inner wall of the transmission case 100. The fixed shaft 21 rotatably supports the loading cam, the input disk 1 and the output disk 2, and forms a flange-shaped portion by attaching nuts 50 and 51 to external thread portions 21s formed near both ends thereof. .

A first bearing 31 for supporting the cam flange 5 on the fixed shaft 21 is interposed between the cam flange 5 and one end (nut) 50 of the fixed shaft 21.
1a is attached to the nut 50 and the inner ring 31b is attached to the back of the cam flange 5. Further, between the output disk 2 and the other end of the fixed shaft 21,
A second bearing 41 for supporting the output disk 2 on the fixed shaft 21 is interposed. An outer ring 41a of the bearing 41 is attached to a nut 51, and an inner ring 41b is attached to the back surface of the output disk 2. The first bearing 31 and the second bearing 41 are ball bearings, and a ball member 31r or 41r is interposed between the bearing outer ring and the inner ring, respectively.

The input disk 1, the loading cam and the first
The assembling with the bearing 31 is performed by sequentially fitting these from the input side (the left side in the drawing) of the fixed shaft 21 and then fixing them with the nut 50. The output disk 2 and the second bearing 41 are assembled by sequentially fitting them from the output side (the right side in the drawing) of the fixed shaft 21 and then fixing them with the nuts 51.

Next, the operation of the first embodiment will be described.

The power transmission in this embodiment is almost the same as that of the prior art, and the input roller 1 is urged in the direction of the output disk 2 by a pressing force corresponding to the driving force from the engine, so that the power roller 3 is driven. Power is transmitted from the input shaft 11 to the input disk 1 by being pressed between the input disk 1 and the output disk 2. The power transmitted to the input disk 1 is taken out as a shift output from an output gear 9 attached to the back of the output disk 2 via the power roller 3.

In this case, the input disk 1 and the output disk 2 are not fixed to the transmission case 100,
Since it is supported only by the fixed shaft 21 via the first bearing 31 and the second bearing 41, a thrust load Fk1 (= F1−) generated by the thrust load F1 generated by the cam roller 6 and the thrust load F2 applied to the output disk 2 F2) and the thrust load applied to the transmission case 100 from the link post 10, that is, the thrust load Fk2 generated from the power roller 3 is offset as the internal force of the fixed shaft 21. That is, the thrust loads Fk1 and Fk2 generated when the input disk 1 is urged in the direction of the output disk 2 by the pressing force from the loading cam are all offset in the fixed shaft 21 formed integrally with the link post. And does not transmit any load to the transmission case 100.

Therefore, according to the first embodiment, since the thrust load is canceled by the fixed shaft 21 fixed to the link post 10, the transmission case 100 caused by the thrust load is provided.
Deformation can be prevented. In this case, it is possible to prevent the gear ratio from fluctuating due to the deformation of the transmission case 100.

When the thrust loads Fk1 and Fk2 are offset by the fixed shaft 21, the fixed loads 21 apply the loads F1 and F2 to the fixed shaft 21.
Acts as a tensile stress. This tensile stress F
1 and F2 act on the portion of the fixed shaft 21 from the link post 10 to the output disk 2 when the gear ratio is large, and act on the portion from the link post 10 to the input disk 1 when the gear ratio is small. Further, the tensile stresses F1, F2 increase as the speed ratio increases. For this reason, in the first embodiment, the fixed shaft 21 is set so that the shaft diameter dimension φ2 in the axial direction area of the output disk 2 is larger than the shaft diameter dimension φ1 in the axial direction area of the input disk 1 at the link post. .

In this case, the first bearing 31 and the second bearing 4
The relationship between the loads F1 and F2 acting on 1 is as follows from Japanese Patent Application Laid-Open No. Hei 10-47448 described in the background art: F2 = F1 · sin (2θ−φ) / sinφ (2) When θ is small, that is, when the reduction ratio is large, F2> F1, and F2 becomes larger as the maximum value of the load.
Since the diameter .phi.2 of the output disk 2 in the axial direction region is increased, the tensile stresses become equal. Accordingly, the tensile stresses F1 and F2 generated in the fixed shaft 21 are canceled, and the strength and durability of the fixed shaft 21 are improved.

In this embodiment, a flange-shaped portion is provided near both ends of the fixed shaft 21. Therefore, the thrust loads Fk1 and Fk2 generated when the input disk 1 is urged in the direction of the output disk 2 by the pressing force from the loading cam mechanism can be efficiently absorbed. , 51
, It is easy to assemble and disassemble.

FIG. 2 is a sectional view conceptually showing a side view of a toroidal type continuously variable transmission according to a second embodiment of the present invention, and the same parts as those in FIG.

As in the first embodiment, one end of the input shaft 11 has a cylindrical shape surrounding the periphery of the end and engages with the rear surface of the cam flange 5. The input shaft 11 penetrates a fixed shaft 22 described later, and the vicinity of the loading cam side end is sealed by a seal member S such as an O-ring.

The fixed shaft 22 is separate from the link post 10 attached to the transmission case 100. The fixed shaft 22 is separated from the link post 10 by an output disk larger than the shaft diameter dimension φ1 in the axial direction area of the input disk 1. The shaft diameter dimension φ2 in the axial region 2 is set large. In this case, the fixed shaft 22 penetrates the link post 10 and the fitting portion 22n
, And the link post 10 is fixed with the nut 53. Further, similarly to the first embodiment, the fixed shaft 22 rotatably supports the loading cam, the input disk 1 and the output disk 2, and attaches a nut 50 to a male screw portion 22s formed near one end thereof to form a flange. A flange-shaped portion 22f is provided integrally with the fixed shaft 22 near the other end while constituting a shaped portion.

Next, the operation of the second embodiment will be described.

The power transmission in this embodiment is almost the same as in the prior art. Also in this case, the input disk 1 and the output disk 2 are supported by the fixed shaft 22 via the first bearing 32 and the second bearing 42 without being fixed to the transmission case 100. Similarly to the above, the thrust loads Fk1 and Fk2 generated when the input disk 1 is urged toward the output disk 2 by the pressing force from the loading cam are all offset in the fixed shaft 22, so that
No load is transmitted to the transmission case 100.

Therefore, according to the second embodiment, since the thrust load is canceled by the fixed shaft 22 fixed to the link post 10, the transmission case 100 caused by the thrust load is provided.
Deformation can be prevented. In this case, it is possible to prevent the gear ratio from fluctuating due to the deformation of the transmission case 100.

In the second embodiment, the fixed shaft 22 is a hollow shaft, and the input disk side end is sealed by a seal member S while the output disk side end is opened to the outside. It has through holes r1 to r5 for discharging oil supplied to the hollow space 22c to the outside. in this case,
The oil pressure-fed from the output disk side (right side in the drawing) to the hollow space 22c of the fixed shaft 22 is supplied to the transmission unit via each of the through holes r1 to r5, so that each unit of the transmission unit is lubricated by one system. be able to. In addition, since the fixed shaft 22 does not rotate, it is easy to easily pump oil into the hollow space 22c. Therefore, according to the second embodiment, each part of the transmission unit can be easily lubricated with a simple structure.

A first bearing 32 for supporting the cam flange 5 on the fixed shaft 22 is interposed between the cam flange 5 and one end (nut) 50 of the fixed shaft 22. The bearing 32 is a roller bearing with a tapered roller 32 r interposed. The bearing outer ring 32 a is attached to the back surface of the cam flange 5, and the bearing inner ring 32 b is attached to a nut 50. Further, a second bearing 42 that supports the output disk 2 on the fixed shaft 22 is interposed between the output disk 2 and the other end of the fixed shaft 22. This bearing 42 is also a roller bearing with a tapered roller 42r interposed.
2a is attached to the back of the output disk 2 and a bearing inner ring 42b is attached to the fixed shaft 22.

Here, considering the stress generated in the transmission unit of the toroidal-type continuously variable transmission, a bending moment acts on the loading cam and the output disk 2 in the direction opposite to that of the power roller 3 so as to be distorted. It is known to Therefore, the second embodiment is directed to the first bearing 3
The second outer ring 32a is fixed to the cam flange 5 and the second
The outer ring 42a of the bearing 42 is attached to the output disk 2, and the inner ring 42 of the first bearing 32 and the second bearing 42
By attaching b to the fixed shaft 22, the support diameter of the cam flange 5 (referred to as a support radius D1 in this embodiment) and the support diameter of the output disk 2 (support radius D in the present embodiment)
2), the stress acting on the loading cam and the output disk 2 is reduced, and the distortion due to the bending moment can be reduced. In this case, the distortion caused by the bending moment can be reduced as the supporting radius D1 of the loading cam and the supporting radius D2 of the output disk 2 increase.

In particular, in the second embodiment, the first bearing 32 and the second bearing 42 are roller bearings with tapered rollers 32r, 42r interposed therebetween.
Since there are communication holes ra and rb communicating with the through holes r1 to r5 provided in the fixed shaft 22 and supplying the lubricating oil to the tapered rollers 32r and 42r, the outer rings (inner rings) of the bearings 32 and 42 are provided.
It is possible to effectively lubricate the sliding contact surfaces between the side surfaces of the rolling grooves provided in 32a and 42a (32b and 42b) and the side surfaces of the tapered rollers 32r and 42r. Therefore, the outer rings (inner rings) 32a, 42a (32b, 4) of the bearings 32, 42
2b) and the side surfaces of the rolling grooves and the tapered rollers 32r,
Power loss due to friction with the side surface of the 42r can be effectively reduced.

FIG. 3 is a sectional view conceptually showing a side view of a third embodiment of the toroidal type continuously variable transmission according to the present invention, and the same parts as those in FIG.

The fixed shaft 23 is a solid shaft integrally formed with the link post, and rotatably supports the loading cam, the input disk 1 and the output disk 2 as in the first embodiment. Male thread 2 formed near
The flanges are formed by attaching the nuts 50 and 51 to 3s.

A first rotating shaft (hereinafter referred to as an input shaft) 12 engaging with the back surface of the cam flange 5 and a second rotating shaft (hereinafter referred to as the output shaft) 13 engaging with the back surface of the output disk 2.
Each has a cylindrical shape surrounding the end of the fixed shaft 23.

A first bearing 33 for supporting the loading cam on the fixed shaft 23 is interposed between the inner peripheral surface of the cylindrical end of the input shaft 12 and the outer peripheral surface of the end of the fixed shaft 23.
Is mounted on the back surface of the cam flange 5, and the bearing inner ring 33b is mounted on the fixed shaft 33. The inner peripheral surface of the cylindrical end of the output shaft 13 and the fixed shaft 2
The output disk 2 is fixed between the outer peripheral surface of
A second bearing 43 supported by the bearing 3 is provided. An outer ring 43 a of the bearing 43 is attached to the back surface of the output disk 2, and a bearing inner ring 43 b is attached to the fixed shaft 33. Note that the first bearing 33 and the second bearing 43 are ball bearings, and a ball member 33 is provided between the outer ring and the inner ring of the bearing.
r or 43r intervenes.

When the bearings 33 and 34 are arranged as in the present embodiment, similarly to the second embodiment, the support diameter of the cam flange 5 (in this embodiment, the support radius is D1) and the support diameter of the output disk 2 ( In this embodiment, the support radius is D2.)
Is increased, the stress acting on the loading cam and the output disk 2 is reduced, and the distortion due to the bending moment can be reduced. In this case, as the supporting radii D1 and D2 of the loading cam and the output disk 2 increase, the distortion due to the bending moment can be reduced.

In addition, since the fixed shaft 23 is a solid shaft,
Loading cam and input / output disks 1 and 2 constituting a speed change unit, and a fixed shaft 23 rotatably supporting these.
The rigidity between them increases. Furthermore, in this embodiment, since the input shaft 12 and the output shaft 13 can be arranged on the same axis, the present invention can be applied to FR vehicles (front-engine rear-wheel drive vehicles) and the like.

FIG. 4 is a sectional view conceptually showing a side view of a toroidal type continuously variable transmission according to a fourth embodiment of the present invention, and the same parts as those in FIG.

The fixed shaft 24 is a hollow shaft formed integrally with the link post 10 and extends in the direction in which the output disk 2 is arranged. Near the end on the output disk 2 side, a flange-shaped portion 24f is provided. Is provided. Thus, the back surface of the output disk 2 is rotatably supported by the inner edge 24f2 of the output disk side end via the second bearing 44.

The intermediate shaft 25 penetrates inside the fixed shaft 24. The intermediate shaft 25 rotatably supports the input disk 1 and the cam flange 5 and has a nut 5 attached to a male screw portion 25s formed near the end on the loading cam side.
0 to form a flange-shaped portion, and a flange-shaped portion 2 near the end on the output disk 2 side.
5f is provided. Thus, the intermediate shaft 25 is connected to the outer edge 24f1 of the output disk side end via the first bearing 34.
It is rotatably supported by.

The input shaft 11 passes through the intermediate shaft 25, and one end of the input shaft 11 has a cylindrical shape surrounding the periphery of the end and engages with the rear surface of the cam flange 5.

Next, the operation of the fourth embodiment will be described.

The power transmission in this embodiment is also substantially the same as that of the prior art, and the input roller 1 is urged in the direction of the output disk 2 by a pressing force corresponding to the driving force from the engine, so that the power roller (FIG. (Not shown) 3 is pressed between the input disk 1 and the output disk 2 to transmit the power from the input shaft 11 to the input disk 1. The power transmitted to the input disk 1 is taken out as a shift output from an output gear 9 attached to the back of the output disk 2 via the power roller 3.

In this case, the input disk 1 and the cam flange 5 supported by the intermediate shaft 25 are not fixed to the transmission case 100 but are fixed to the fixed shaft 24 via the first bearing 34.
And the output disk 2 is also not fixed to the transmission case 100,
It is supported by a flange-shaped portion 24f of the fixed shaft 24 via a bearing 44.

Therefore, the thrust load F1 generated by the loading cam and the thrust load F2 acting on the output disk 2
And the thrust load Fk1 generated by the
Thrust load applied to the transmission case 100 from
The thrust load Fk2 generated from the power roller 3 is offset at the end of the fixed shaft 24 on the output disk side (corresponding to the flange-shaped portion 24f in this case). That is, the thrust load F generated when the input disk 1 is urged toward the output disk 2 by the pressing force from the loading cam.
k1 and Fk2 are all offset in the fixed shaft 24 and do not transmit any load to the transmission case 100 in which the transmission unit is housed.

Therefore, according to the fourth embodiment, similarly to the first embodiment, the fixed shaft 24 fixed to the link post 10 is used.
Thus, the transmission case 100 can be prevented from being deformed due to the thrust load. in this case,
It is also possible to prevent the gear ratio from fluctuating due to the deformation of the transmission case 100.

Also in the case of the fourth embodiment, the outer race 34a of the first bearing 34 is mounted on the fixed shaft 24, the inner race 34b is mounted on the intermediate shaft 25 which rotatably supports the loading cam, and the second bearing 34 44 outer ring 44a
Is attached to the fixed shaft 24 and the bearing inner ring 44b is attached to the output disk 2, so that the support diameter of the intermediate shaft 25 (support radius D1 in this embodiment) and the support diameter of the output disk 2 (support diameter in this embodiment) Since the radius D2 is increased, the stress acting on the loading cam and the output disk 2 is reduced, and the distortion due to the bending moment can be reduced. In this case, the intermediate shaft 2
As the support radii D1 and D2 of the output disk 5 and the output disk 2 increase, the distortion due to the bending moment can be reduced.

In the fourth embodiment, flange-shaped portions 25f are provided near both ends of the intermediate shaft 25. Therefore, the thrust loads Fk1 and Fk2 generated when the input disk 1 is urged in the direction of the output disk 2 by the pressing force from the cam flange 5 can be effectively absorbed. When the flange-shaped portion provided near the side end is formed of the nut 50, operations such as assembly and disassembly are easy.

The foregoing merely illustrates preferred embodiments of the present invention, and those skilled in the art will be able to make various modifications within the scope of the appended claims.

[Brief description of the drawings]

FIG. 1 is a first view of a toroidal type continuously variable transmission according to the present invention;
It is sectional drawing which showed embodiment from the side.

FIG. 2 is a sectional view showing a second embodiment of the present invention from the side.

FIG. 3 is a sectional view showing a third embodiment of the present invention from the side.

FIG. 4 is a cross-sectional view showing a fourth embodiment of the present invention from the side.

FIG. 5 is a radial sectional view showing a conventional toroidal-type continuously variable transmission.

FIG. 6 is a sectional view taken along line XX of FIG. 5;

FIG. 7 is a conceptual diagram of a force acting on a toroidal type continuously variable transmission.

FIG. 8 is a conceptual diagram of forces acting on a transmission case of a conventional toroidal-type continuously variable transmission.

FIG. 9 is a conceptual diagram illustrating forces acting on the transmission case in FIG.

[Explanation of symbols]

 Reference Signs List 1 input disk (first disk) 2 output disk (second disk) 3 power roller (friction roller) 4 trunnion (roller support member) 5 cam flange 6 cam roller 7, 8 link (link member) 9 output gear 10 link post 11 , 12,14 Input shaft (first rotating shaft) 13 Output shaft (second rotating shaft) 21 Hollow fixed shaft 22 Hollow fixed shaft 22f Flange shape portion 24 Hollow fixed shaft 24f Flange shape portion 25 Intermediate shaft 25f Flange shape portion 23 Medium Actual fixed shaft 31,33 First bearing (ball bearing) 31a, 33a Bearing outer ring 31b, 33b Bearing inner ring 31r, 33r Ball member 32 First bearing (roller bearing) 32a Bearing outer ring 32b Bearing inner ring 32r Tapered roller 41,43 Second Bearing (ball bearing) 41a, 43a Bearing outer ring 41b, 43b Bearing inner ring 41r, 43r Ball member 42 Second bearing (roller bearing) 42a Bearing outer ring 42b Bearing inner ring 42r Taper roller 50, 51, 52, 53 Nut 100 transmission case

Claims (12)

[Claims] A plurality of friction rollers interposed between a first disk and a second disk coaxially opposed to each other are supported by a roller support member so as to be tiltable, and the ends of the roller support members are connected to each other. The link members are connected to each other by a link member, and these link members are swingably supported by link posts provided in the transmission case, and correspond to a driving source generated by a loading cam disposed on the back surface of the first disk. In the toroidal-type continuously variable transmission in which the friction roller is pressed between the first disk and the second disk by urging the first disk in the direction of the second disk by a pressing force, The disk and the second disk and the loading cam are rotatably supported by a fixed shaft fixed to the link post. Toroidal type continuously variable transmission. 2. The fixed shaft has a larger shaft diameter in an axial area of a disk on an output side than an axial area of a disk on an input side with respect to the link post. Item 2. A toroidal-type continuously variable transmission according to item 1. 3. The fixed shaft is a hollow shaft, and has a through hole through which a space at a center portion and the outside penetrate, and discharges oil supplied to the hollow space to the outside. The toroidal-type continuously variable transmission according to claim 1. 4. A first bearing for supporting the loading cam on the fixed shaft is interposed between the loading cam and one end of the fixed shaft, and a bearing outer ring is attached to the loading cam. A bearing inner ring is attached to the fixed shaft, and a second bearing for supporting the second disk on the fixed shaft is interposed between the second disk and the other end of the fixed shaft. The bearing inner ring is attached to the fixed shaft while being attached to the second disk.
The toroidal-type continuously variable transmission according to any one of claims 3 to 3. 5. The first bearing and the second bearing are roller bearings having a tapered roller interposed therebetween, wherein the first bearing and the second bearing communicate with the through hole, and at least one of the tapered rollers interposed in the first bearing or the second bearing. The toroidal-type continuously variable transmission according to claim 4, further comprising a communication hole for supplying lubricating oil to the roller. 6. The fixed shaft is a solid shaft, and a first rotating shaft engaged with a back surface of the loading cam and a second rotating shaft engaged with a back surface of the second disk are formed of the fixed shaft. A first bearing that supports the loading cam on the fixed shaft is interposed between the cylindrical end of the first rotating shaft and one end of the fixed shaft, and has a cylindrical shape surrounding the end. The bearing outer ring is attached to the loading cam, the bearing inner ring is attached to the fixed shaft, and the second disk is provided between the cylindrical end of the second rotating shaft and the other end of the fixed shaft. 3. A toroidal mold according to claim 1, wherein a second bearing supported by the fixed shaft is interposed, and a bearing outer ring is mounted on the second disk and a bearing inner ring is mounted on the fixed shaft. Step transmission. 7. A flange-shaped portion is provided near an end of the fixed shaft.
7. The toroidal-type continuously variable transmission according to any one of claims 6 to 6. 8. The toroidal-type continuously variable transmission according to claim 7, wherein at least one of the flange-shaped portions provided near an end of the fixed shaft is formed of a nut. 9. A plurality of friction rollers interposed between a first disk and a second disk coaxially opposed to each other are supported by a roller supporting member so as to be tiltable, and the ends of the roller supporting members are connected to each other. The link members are connected to each other by a link member, and these link members are swingably supported by link posts provided in the transmission case, and correspond to a driving source generated by a loading cam disposed on the back surface of the first disk. In the toroidal-type continuously variable transmission, which presses the friction roller between the first disk and the second disk by urging the first disk in the direction of the second disk by a pressing force, A fixed shaft fixed to a post extends in a direction in which the second disk is disposed, and a back surface of the second disk is connected to the fixed shaft via a second bearing. An intermediate shaft rotatably supported by the inner edge of the two-disk-side end portion and rotatably supporting the first disk and the loading cam extends through the fixed shaft in the direction in which the second disk is disposed. The toroidal-type continuously variable transmission is characterized in that the extending end is rotatably supported by an outer edge of the second disk-side end of the fixed shaft via a first bearing. 10. The first bearing has a bearing outer ring attached to the fixed shaft and a bearing inner ring attached to the intermediate shaft. The second bearing has a bearing outer ring attached to the fixed shaft and a bearing. The toroidal-type continuously variable transmission according to claim 9, wherein an inner ring is attached to the second disk. 11. The toroidal-type continuously variable transmission according to claim 9, wherein a flange-shaped portion is provided near an end of the intermediate shaft. 12. The toroidal-type continuously variable transmission according to claim 11, wherein the flange-shaped portion provided near the loading cam side end of the intermediate shaft is formed of a nut.