JP4055562B2 - Toroidal continuously variable transmission - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention belongs to the technical field of a toroidal type continuously variable transmission applied as a transmission of a vehicle.
[0002]
[Prior art]
A power roller of a conventional toroidal-type continuously variable transmission includes an inner ring, an outer ring, a thrust ball bearing, a radial needle bearing, and a shaft supported by the outer ring. A snap ring is attached in the vicinity of the tip of the shaft, and this snap ring is in contact with the retainer of the radial needle bearing, and restricts the movement of the radial needle bearing in the axial direction (see, for example, Patent Document 1). .
[0003]
[Patent Document 1]
JP-A-11-210854 (FIG. 10).
[0004]
[Problems to be solved by the invention]
However, in the conventional toroidal-type continuously variable transmission, it is necessary to form a groove in the shaft in order to attach the snap ring, resulting in an increase in processing steps. In addition, an increase in the number of parts of the snap ring itself and an attaching operation are added, which causes an increase in cost.
[0005]
The present invention has been made paying attention to the above-mentioned problems, and eliminates the need for the groove processing of the snap ring and the shaft to which the snap ring is attached, and can reduce the cost while realizing the movement restriction in the axial direction of the radial bearing. It aims at providing a type continuously variable transmission.
[0006]
[Means for Solving the Problems]
In order to achieve the above object, in the present invention,
The power roller has an inner ring, an outer ring, a radial support shaft, a thrust bearing, and a radial bearing, and the radial bearing includes a plurality of rolling elements and a cage that supports the rolling elements. In a continuously variable transmission,
One end of said retainer, a rib which projects radially,
Axial movement was restricted by engagement of two of the inner ring, outer ring, and radial support shaft with the rib.
[0007]
【The invention's effect】
Therefore, in the toroidal type continuously variable transmission according to the present invention, it is not necessary to process the groove of the snap ring and the shaft to which the snap ring is attached, and the axial movement restriction of the radial bearing can be realized while reducing the cost. .
[0008]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, an embodiment for realizing a toroidal continuously variable transmission according to the present invention will be described with reference to the drawings.
[0009]
(First embodiment)
First, the configuration will be described.
FIG. 1 is a schematic diagram showing a transmission mechanism of a toroidal-type continuously variable transmission according to a first embodiment. A rotational driving force from an engine is input to an input shaft 1 via a torque converter and a forward / reverse switching mechanism (not shown). The
[0010]
A torque transmission shaft 2 is arranged coaxially with the input shaft 1, and the first input disk 3 and the second input disk 4 are spline-coupled to the positions of both ends of the torque transmission shaft 2 so as to be movable in the axial direction. ing.
[0011]
Between the back surface of the first input disk 3 and the input shaft 1, a loading cam mechanism 5 that generates axial thrust according to the input torque is interposed.
[0012]
Between the back surface of the second input disk 4 and the nut 6 screwed into the end of the torque transmission shaft 2, a disc spring 7 for applying preload to both the input disks 3 and 4 is interposed.
[0013]
An output disk 8 mounted on the torque transmission shaft 2 is disposed at an intermediate position between the input disks 3 and 4. The output disk 8 is formed by integrally joining the back surfaces of two output disks together, and an output gear 9 is formed on the outer periphery of the output disk 8.
[0014]
Toroidal grooves 3 a and 4 a are formed on the output disk 8 facing surface of the first input disk 3 and the output disk 8 facing surface of the second input disk 4. Similarly, toroidal grooves 8a and 8b are formed on the opposing surface of the output disk 8 facing the input disks 3 and 4.
[0015]
Between the toroidal groove 3a and the toroidal groove 8a, two first power rollers 10, 10 arranged at the left and right positions are sandwiched so as to be able to deliver power by friction. Similarly, between the toroidal groove 4a and the toroidal groove 8b, two second power rollers 11, 11 arranged at the left and right positions are sandwiched so as to be able to deliver power by friction.
[0016]
The first input disk 3, the output disk 8 (toroidal groove 8 a), and the first power rollers 10, 10 constitute a first toroidal transmission unit 12. The second input disk 4, the output disk 8 (toroidal groove 8 b), and the second power rollers 11 and 11 constitute a second toroidal transmission unit 13.
[0017]
In the above speed change mechanism, each of the power rollers 10, 10, 11, 11 is tilted so as to obtain a tilt angle corresponding to the target speed ratio by an operation described later. That is, the input rotation of both the input disks 3, 4 is transmitted steplessly (continuously) to the output disk 8 via the power rollers 10, 10, 11, 11.
[0018]
FIG. 2 is a schematic diagram showing a shift control system of the toroidal type continuously variable transmission according to the first embodiment. The first power rollers 10 and 10 are supported by one ends of trunnions 14 and 14, and the power roller rotating shaft 15. , 15 can be rotated around the center. At the other end of the trunnions 14, 14, servos as hydraulic actuators that cause the trunnions 14, 14 to offset move in the direction of the tilt axis L and tilt the power rollers 10, 10 around the tilt axis L. Pistons 16 and 16 are provided.
[0019]
Similarly, the second power rollers 11 and 11 are also supported by one end of a trunnion (not shown), and the trunnions are offset in the direction of the tilting shaft to move the power rollers 11 and 11 around the tilting axis L. A servo piston is provided as a hydraulic actuator for tilting to the right. The four trunnions that support the power rollers 10, 10, 11, and 11 are connected by synchronization wires (not shown) so that they move in synchronization.
[0020]
The servo pistons 16, 16 are defined by high-side oil chambers 16b, 16b and low-side oil chambers 16c, 16c by pistons 16a, 16a. A shift control valve 19 is provided as a hydraulic control system for controlling the operation of the servo pistons 16. The shift control valve 19 and the servo pistons 16 and 16 are connected by a high-side oil passage 17 connected to the high-side oil chambers 16b and 16b and a low-side oil passage 18 connected to the low-side oil chambers 16c and 16c. Has been.
[0021]
The shift control valve 19 has a port 19 a for connecting the high side oil passage 17 and a port 19 b for connecting the low side oil passage 18. The line pressure port 19c of the shift control valve 19 is supplied with a line pressure from a hydraulic source having an oil pump and a relief valve (not shown).
[0022]
The speed change spool 19 d of the speed change control valve 19 is driven to move in the axial direction by a step motor 22 while interlocking with the lever 20 and the recess cam 21. The recess cam 21 is provided at the lower end of one trunnion shaft, detects the tilt axis direction position and tilt angle position of the trunnion 14, and feeds back to the shift control valve 19.
[0023]
A CVT control unit 23 is provided as an electronic control system for driving and controlling the step motor 22. The CVT control unit 23 receives input information from a throttle opening sensor 24, an engine rotation sensor 25, an input disk rotation sensor 26, an output shaft rotation sensor (vehicle speed sensor) 27, an inhibitor switch 28, an oil temperature sensor 29, and the like. It is.
[0024]
FIG. 3 is a sectional view showing the trunnion 14 and the power roller 10 employed in the toroidal type continuously variable transmission of the first embodiment. The power roller 11 has the same structure.
[0025]
The power roller 10 includes an inner ring 30 for transmitting the power of the input disk 3 to the output disk 8, an outer ring 31 supported by the trunnion 14, a radial support shaft 32 coupled to the outer ring 31 by press-fitting, and the like. A thrust ball bearing 33 (thrust bearing) for supporting a working thrust load and a radial needle bearing 34 (radial bearing) for supporting a radial load acting on the inner ring 30 are provided. The radial needle bearing 34 is a plurality of needles 34a. (Rolling element) and a holder 34b that supports the needle 34a.
[0026]
The trunnion 14 has a power roller storage portion 14 a for storing the power roller 10, and the power roller 10 is slid in a direction perpendicular to the tilt axis L via the back bearing 35. A power roller support surface 14b is formed so as to support the power roller. The back bearing 35 includes a plurality of needles 35a, a retainer 35b that supports the needles 35a, and a central oil hole 35c that is opened in the retainer 35b. The trunnion 14 is formed with a trunnion-side oil passage 36 that guides oil from a lubricating oil pressure source (not shown), and the opening 36a of the trunnion-side oil passage 36 rotates the power roller toward the back surface of the outer ring 31. It is opened at the axial center position.
[0027]
The inner ring 30 includes a torque transmission curved surface 30 a that contacts both the disks 3, 8, a central shaft hole 30 b that passes through the central axis, and an inner ring side raceway groove 30 c that guides the rolling element of the thrust ball bearing 33. . A radial needle bearing 34 is interposed between the central shaft hole 30 b and the radial support shaft 32.
[0028]
The outer ring 31 includes an outer ring rear surface 31a that receives the needle 35a of the rear bearing 35, an outer ring side raceway groove 31b that guides a rolling element of the thrust ball bearing 33, and an outer ring front side 31c in which the outer ring side raceway groove 31b is formed. Have.
[0029]
The radial support shaft 32 is formed with an axial oil passage 37 communicating with the opening 36 a and the central oil hole 35 c on the power roller rotating shaft 15, and the branch oil passage 37 a has a diameter from the axial oil passage 37. In the direction.
[0030]
The thrust ball bearing 33 includes a ball 33a as a rolling element mounted on the inner ring side raceway groove 30c and the outer ring side raceway groove 31b, and a cage 33b that holds a plurality of balls 33a .
[0031]
The radial needle bearing 34 is interposed between the inner ring 30 and the radial support shaft 32. As shown in FIG. 4, the retainer 34b is provided with a rib 34c projecting in the radial direction, and the rib 34c is provided with the rib 34c. A notch oil groove 34d for guiding the lubricating oil in the radial direction is provided. In FIG. 4, 34e is a needle insertion hole.
[0032]
Then, as shown in FIG. 3, the ribs 34c of the cage 34b are sandwiched between the back surface 30d of the inner ring 30 and the stepped surface 32a of the radial support shaft 32 through a slight gap. The movement of the cage 34b in the axial direction (power roller rotation axis direction) is restricted to the movement between the both surfaces 30d and 32a while allowing the cage 34b to freely rotate with respect to the radial support shaft 32. ing. When the step surface is formed on the front side of the outer ring 31 instead of the radial support shaft 32, the both surfaces are sandwiched between the back surface of the inner ring and the step surface of the outer ring with a slight gap. Also good.
[0033]
Next, the operation will be described.
[0034]
[Gear ratio control action]
In the toroidal type continuously variable transmission, when the trunnions 14 and 14 are slightly displaced in the direction of the tilt axis L (the vertical direction in FIG. 2), the power rollers 10 and 10 are tilted in accordance with the displacement, thereby changing the gear ratio. change.
[0035]
That is, when the speed change spool 19d is displaced by rotating the step motor 22 in accordance with a drive command for obtaining a target speed ratio from the CVT control unit 23, hydraulic oil is guided to one servo piston chamber of the servo pistons 16 and 16, The hydraulic fluid is discharged from the other servo piston chamber, and the trunnions 14 and 14 are displaced in the direction of the tilt axis L.
[0036]
As a result, the power roller rotating shafts 15 and 15 are offset from the disk rotation center position. Due to the offset, the power rollers 10 and 10 are tilted by the side slip force generated at the contact portion between the power rollers 10 and 10 and the input / output disks 3 and 8.
[0037]
This tilting motion and offset are transmitted to the transmission spool 19d via the recess cam 21 and the lever 20. Therefore, the shift spool 19d stops at a balance position with the step motor 22, and the displacement applied to the trunnions 14 and 14 is returned to the original disk rotation center position at a tilt angle at which the target gear ratio is obtained. Then, the tilting operation of the power rollers 10, 10 is stopped.
[0038]
The power rollers 11 and 11 also exhibit the same gear ratio control action, and the gear ratio is determined by the tilt angle of the stopped power rollers 10, 10, 11, and 11.
[0039]
[Power roller lubrication]
The power roller 10 that receives a large pressing force while rotating due to the speed change action needs to lubricate the bearing portion with a sufficient amount of lubricating oil in order to ensure a smooth rotational operation and suppress a temperature rise due to heat generation. .
[0040]
Lubricating oil is supplied from the trunnion 14 to the power roller 19 from a trunnion-side oil passage 36 formed in the trunnion 14 through an opening 36 a that opens toward the outer ring 31 and a radial support shaft 32. It is guided to an axial center oil passage 37 formed therein. Then, the lubricating oil is supplied from the shaft center oil passage 37 to the radial needle bearing 34 through the branch oil passage 37a, and further, the lubricating oil is supplied to the thrust ball bearing 33 through the notch oil groove 34d.
[0041]
[Axial movement restriction action of radial needle bearing]
Conventionally, as shown in FIG. 5 (b), a snap ring is attached in the vicinity of the tip of the shaft supported by the outer ring, and this snap ring abuts on the retainer of the radial needle bearing, Axial movement is restricted.
[0042]
Therefore, in order to attach the snap ring, it is necessary to form a groove in the shaft, resulting in an increase in processing steps. In addition, an increase in the number of parts of the snap ring itself and an attaching operation are added, which causes an increase in cost.
[0043]
On the other hand, in the first embodiment of the present invention, the conventional snap ring is eliminated, and the radial needle bearing 34 is formed by ribs 34c integrally projecting radially from the cage 34b as shown in FIG. 5 (a). Since the movement in the axial direction is restricted, there is no need to perform grooving.
[0044]
Further, since the rib 34c of the retainer 34b is supported between the inner ring 30 and the radial support shaft 32 with a slight gap, the rib 34c can freely rotate around the radial support shaft 32. The movement in the axial direction is restricted such that only the gap with the stepped surface 32a of the radial support shaft 32 can move in the direction, and only the gap with the back surface 30d of the inner ring 30 can move in the right direction in FIG. The radial needle bearing 34 does not fall out of the power roller 10.
[0045]
Next, the effect will be described.
In the toroidal type continuously variable transmission of the first embodiment, the effects listed below can be obtained.
[0046]
(1) The power roller 10 acts on the inner ring 30 that transmits the power of the input disk 3 to the output disk 8, the outer ring 31 supported by the trunnion 14, the radial support shaft 32 coupled to the outer ring 31, and the inner ring 30. A thrust ball bearing 33 for supporting a thrust load; and a radial needle bearing 34 for supporting a radial load acting on the inner ring 30; the radial needle bearing 34 is held by a plurality of needles 34a and the needle 34a. In the toroidal-type continuously variable transmission constituted by the cage 34b, the retainer 34b is provided with ribs 34c projecting in the radial direction, and two of the inner ring 30, the outer ring 31 and the radial support shaft 32 are engaged with the rib 34c. As a result, the movement in the axial direction is restricted, eliminating the need for groove processing of the snap ring and the shaft to which it is attached, reducing costs. However, the movement restriction of the radial needle bearing 34 in the axial direction can be realized.
[0047]
(2) Since the radial needle bearing 34 is located between the inner ring 30 and the radial support shaft 32 and the rib 34c of the retainer 34b restricts the axial movement of the inner ring 30 and the radial support shaft 32, the retainer 34b The movement of the radial needle bearing 34 in the axial direction can be achieved by the rib 34c protruding in the outer diameter direction.
[0048]
(3) Since the axial center oil passage 37 for supplying the lubricating oil to the inner diameter side from the radial needle bearing 34 is disposed, and the notched oil groove 34d for guiding the lubricating oil in the radial direction is provided in the rib 34c of the retainer 34b. The oil passage is not blocked by the rib 34c, and the lubricating oil with a sufficient amount of oil can be supplied to the radial needle bearing 34 and the thrust ball bearing 33.
[0049]
(Second embodiment)
The second embodiment is an example in which the cage 34 b of the radial needle bearing 34 is restricted in the axial direction by the outer ring 31 and the radial support shaft 32.
[0050]
That is, as shown in FIG. 6, the radial needle bearing 34 is interposed between the inner ring 30 and the radial support shaft 32, and the retainer 34b is provided with a rib 34f protruding in the inner diameter direction, and the rib 34f In addition, a notch oil groove 34d for guiding the lubricating oil in the radial direction is provided.
[0051]
Then, the rib 34f that protrudes in the inner diameter direction from the end of the cage 34b is interposed between the stepped surface 32b of the radial support shaft 32 and the front surface 31c of the outer ring 31 with a slight gap between the both surfaces 32b and 31c. Thus, the movement of the cage 34b in the axial direction is restricted to the movement between the both surfaces 32b and 31c while allowing the cage 34b to freely rotate with respect to the radial support shaft 32. Since other configurations are the same as those of the first embodiment, the corresponding components are denoted by the same reference numerals and description thereof is omitted.
[0052]
Next, the operation will be described. Since the rib 34f of the retainer 34b is supported between the radial support shaft 32 and the outer ring 31 with a slight gap, it can freely rotate around the radial support shaft 32. However, only the gap with the front surface 31c of the outer ring 31 can move in the left direction in FIG. 6, and only the gap with the stepped surface 32b of the radial support shaft 32 can move in the right direction in FIG. The movement in the direction is restricted, and the radial needle bearing 34 does not fall out of the power roller 10. Further, in the lubricating action, lubricating oil is supplied from the axial center oil passage 37 to the radial needle bearing 34 and the thrust ball bearing 33 through the branch oil passage 37a and the notch oil groove 34d. Other operations are the same as in the first embodiment.
[0053]
Next, the effect will be described.
In the toroidal type continuously variable transmission according to the second embodiment, the following effects can be obtained in addition to the effects (1) and (3) of the first embodiment.
[0054]
(4) Since the radial needle bearing 34 is located between the inner ring 30 and the radial support shaft 32 and the rib 34f of the retainer 34b is restricted from moving in the axial direction by the outer ring 31 and the radial support shaft 32, the retainer 34b The movement of the radial needle bearing 34 in the axial direction can be achieved by the rib 34f protruding from the inner diameter direction of the radial needle bearing 34.
[0055]
(Third embodiment)
In the third embodiment, the axial movement of the retainer 34 b of the radial needle bearing 34 is restricted by the inner ring 30 and the outer ring 31.
[0056]
That is, as shown in FIG. 7, the radial needle bearing 34 is interposed between a radial support shaft 32 formed integrally with the inner ring 30 and the outer ring 31, and the retainer 34b has an outer diameter direction. A protruding rib 34g is provided, and a notch oil groove 34d for guiding the lubricating oil in the radial direction is provided in the rib 34g.
[0057]
The rib 34g of the cage 34b is sandwiched between the back surface 30d of the inner ring 30 and the front surface 31c of the outer ring 31 with a slight gap between them, and a radial support shaft of the cage 34b is provided. The movement of the cage 34b in the axial direction is restricted to the movement of the gap between the both surfaces 30d and 31c while allowing free rotation with respect to 32. Since other configurations are the same as those of the first embodiment, description thereof is omitted.
[0058]
Next, the operation will be described. Since the rib 34g of the retainer 34b is supported between the inner ring 30 and the outer ring 31 with a slight gap, it can freely rotate around the radial support shaft 32. The movement in the axial direction is restricted so that only the gap with the front surface 31c of the outer ring 31 can be moved in the left direction of FIG. 7 and only the gap with the back surface 30d of the inner ring 30 can be moved in the right direction of FIG. Thus, the radial needle bearing 34 does not fall out of the power roller 10. In addition, the lubricating oil is supplied from the center oil hole 35c to the radial needle bearing 34 through a gap between the rear bearing 35 and the end face of the radial support shaft 32, and branches from the center oil hole 35c to the shaft center oil passage 37. Lubricating oil is supplied to the thrust ball bearing 33 through the oil passage 37a and the notched oil groove 34d. Other operations are the same as in the first embodiment.
[0059]
Next, the effect will be described.
In the toroidal type continuously variable transmission of the third embodiment, the following effects can be obtained in addition to the effects (1) and (3) of the first embodiment.
[0060]
(5) Since the radial needle bearing 34 is located between the radial support shaft 32 and the outer ring 31, and the rib 34g of the retainer 34b is restricted from moving in the axial direction by the inner ring 30 and the outer ring 31, The movement of the radial needle bearing 34 in the axial direction can be achieved by the rib 34g protruding in the radial direction.
[0061]
In addition, since the inner ring 30 has a structure without a through hole and the radial support shaft 32 is integrally formed, high inner ring strength can be ensured.
[0062]
Further, since the trunnion side end surface of the radial support shaft 32 is disposed on the inner ring side from the back surface 31a of the outer ring 31, a lubricating oil passage is formed by a gap between the both end surfaces, thereby improving the lubricity of the radial needle bearing 34. it can.
[0063]
(Fourth embodiment)
The fourth embodiment is basically the same as the first embodiment, but is an example in which the rib 34c is provided in a part of the circumference.
[0064]
That is, as shown in FIG. 8, the ribs 34c of the cage 34b are formed only at three locations on the circumference. Since other configurations are the same as those of the first embodiment, description thereof is omitted. The operation is also the same as that of the first embodiment, and the description thereof is omitted.
[0065]
Next, the effect will be described.
In the toroidal continuously variable transmission of the fourth embodiment, the following effects can be obtained in addition to the effects (1), (2), and (3) of the first embodiment.
[0066]
(6) Since the ribs 34c of the cage 34b are formed at only three locations on the circumference, the weight can be reduced by the amount of the rib volume reduced compared to the first embodiment.
[0067]
As mentioned above, although the toroidal type continuously variable transmission of this invention has been demonstrated based on 1st Example-4th Example, about a concrete structure, it is not restricted to these Examples, Claims Modifications and additions of the design are permitted without departing from the spirit of the invention according to the claims.
[0068]
For example, as the radial support shaft, the shaft member coupled to either the inner ring, the outer ring or the trunnion, or the shaft portion integrally formed with either the inner ring, the outer ring or the trunnion is described in the embodiment. It is not limited to.
[0069]
In addition, the rib protruding in the radial direction from the cage can be used in the embodiment as long as it restricts movement in the axial direction by engagement with the rib with respect to the two combined members of the inner ring, the outer ring, and the radial support shaft. It is not limited to what has been described.
[Brief description of the drawings]
FIG. 1 is a schematic view showing a transmission mechanism of a toroidal type continuously variable transmission according to a first embodiment.
FIG. 2 is a schematic diagram showing a shift control system of the toroidal-type continuously variable transmission according to the first embodiment.
FIG. 3 is a longitudinal sectional view showing a trunnion and a power roller employed in the toroidal continuously variable transmission according to the first embodiment.
FIG. 4 is a perspective view showing a radial needle bearing retainer in the toroidal-type continuously variable transmission according to the first embodiment.
FIG. 5 is a diagram for explaining a comparison between a position restricting structure in the radial needle bearing of the first embodiment and a position restricting structure in the radial needle bearing of the conventional example.
FIG. 6 is a longitudinal sectional view showing a trunnion and a power roller employed in a toroidal type continuously variable transmission according to a second embodiment.
FIG. 7 is a longitudinal sectional view showing a trunnion and a power roller employed in a toroidal type continuously variable transmission according to a third embodiment.
FIGS. 8A and 8B are a rear view and a sectional view showing a retainer of a radial needle bearing according to a fourth embodiment. FIGS.
[Explanation of symbols]
3 First input disk 4 Second input disk 8 Output disk 10 First power roller 11 Second power roller 14 Trunnion 14a Power roller storage surface 14b Power roller support surface 15 Power roller rotation axis L Tilt shaft 30 Inner ring 31 Outer ring 32 Radial Support shaft 33 Thrust ball bearing (Thrust bearing)
34 Radial needle bearings (radial bearings)
34a Needle (rolling element)
34b Cage 34c Rib 34d Notch oil groove 34e Needle fitting insertion hole 35 Back bearing 35a Needle 35b Cage 35c Center oil hole 36 Trunnion side oil passage 36a Opening 37 Shaft center oil passage 37a Branch oil passage

Claims (6)

An input disk, an output disk, a plurality of power rollers sandwiched between toroidal grooves formed on the opposing surfaces of these input / output disks, and a trunnion that supports the power rollers in a tiltable manner,
The power roller is coupled to an inner ring for transmitting the power of the input disk to the output disk, an outer ring supported by the trunnion, and either the inner ring, the outer ring or the trunnion, or integrally formed with either the inner ring, the outer ring or the trunnion. A radial support shaft, a thrust bearing that supports a thrust load acting on the inner ring, and a radial bearing that supports the radial load acting on the inner ring,
In the toroidal-type continuously variable transmission, in which the radial bearing includes a plurality of rolling elements and a cage that supports the rolling elements,
One end of said retainer, a rib which projects radially,
A toroidal continuously variable transmission characterized in that axial movement is restricted by engagement of two of the inner ring, outer ring and radial support shaft and the rib. In the toroidal continuously variable transmission according to claim 1,
The radial bearing is between the inner ring and the radial support shaft;
A toroidal continuously variable transmission characterized in that the cage rib restricts axial movement by an inner ring and a radial support shaft . In the toroidal continuously variable transmission according to claim 1,
The radial bearing is between the inner ring and the radial support shaft;
A toroidal continuously variable transmission characterized in that the cage rib restricts axial movement between a radial support shaft and an outer ring. In the toroidal continuously variable transmission according to claim 1,
The radial bearing is between the outer ring and the radial support shaft;
A toroidal-type continuously variable transmission characterized in that the cage rib regulates axial movement between an inner ring and an outer ring. The toroidal continuously variable transmission according to any one of claims 1 to 4,
An oil passage for supplying lubricating oil to the inner diameter side from the radial bearing is disposed,
A toroidal continuously variable transmission, characterized in that a notch oil groove that guides lubricating oil in a radial direction is provided in a rib of the cage. In the toroidal continuously variable transmission according to any one of claims 1 to 5,
A toroidal-type continuously variable transmission characterized in that a rib of the cage is formed in a part of a circumference.

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