JP3307053B2 - Toroidal type continuously variable transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The toroidal type continuously variable transmission according to the present invention is used, for example, as a transmission for an automobile or as a transmission for various industrial machines.

[0002]

2. Description of the Related Art The use of a toroidal-type continuously variable transmission as schematically shown in FIGS. This toroidal-type continuously variable transmission supports an input disk 2 concentrically with an input shaft 1 and is disposed concentrically with the input shaft 1 as disclosed in, for example, Japanese Utility Model Application Laid-Open No. 62-71465. An output disk 4 is fixed to an end of the output shaft 3. Inside the casing containing the toroidal-type continuously variable transmission, trunnions 6 and 6 that swing about pivots 5 and 5 that are twisted with respect to the input shaft 1 and the output shaft 3 are provided. .

Each of the trunnions 6, 6 has the pivots 5, 5 on the outer surfaces of both ends. The center of each trunnion 6, 6 supports the base end of the displacement shaft 7, 7 and swings each trunnion 6, 6 around the pivot 5, 5, thereby allowing each displacement shaft 7, 6 to swing. The inclination angle of 7 can be freely adjusted. Power rollers 8, 8 are rotatably supported around displacement shafts 7, 7 supported by the trunnions 6, 6, respectively. The power rollers 8 are sandwiched between the input side and output side disks 2, 4.

[0004] The displacement shafts 7, 7 incorporated in an actual toroidal-type continuously variable transmission are composed of a base end and a tip which are eccentric to each other.
6, and the power rollers 8, 8 are pivotally supported at the tip thereof. This is because when the power rollers 8 and 8 tend to be displaced in the left-right direction in FIGS.
A thrust rolling bearing is provided between the inner surface of each of the trunnions 6, 6 and the outer surface of the power rollers 8, 8. However, since these points are not related to the gist of the present invention, illustration and detailed description are omitted.

The inner surfaces 2a and 4a of the input and output disks 2 and 4 facing each other have cross sections each having a concave surface obtained by rotating an arc centered on the pivot 5. The peripheral surfaces 8a, 8a of the power rollers 8, 8 formed on the spherical convex surfaces are in contact with the inner side surfaces 2a, 4a.

[0006] A loading device 9 of a loading cam type is provided between the input shaft 1 and the input disk 2, and the input disk 2 is directed toward the output disk 4 by the pressing device 9 so as to be elastic. Pressing. This pressing device 9
Is a cam plate 10 that rotates together with the input shaft 1 and a retainer 11
(For example, four) rollers 12 held by
12. A cam surface 13 which is an uneven surface extending in the circumferential direction is formed on one side surface (the left side surface in FIGS. 5 to 6) of the cam plate 10, and an outer side surface (the right side in FIGS. Surface) also has a similar cam surface 14 formed thereon. The plurality of rollers 12 are supported rotatably about an axis in a radial direction with respect to the center of the input shaft 1.

When the cam plate 10 rotates with the rotation of the input shaft 1 when using the toroidal type continuously variable transmission configured as described above, the plurality of rollers 12, 1, 1
2 is pressed against the cam surface 14 on the outer surface of the input disk 2. As a result, the input side disk 2 is pressed by the plurality of power rollers 8 and 8 and at the same time, based on the engagement between the pair of cam surfaces 13 and 14 and the plurality of rollers 12, The input side disk 2 rotates. And
The rotation of the input disk 2 is transmitted to the output disk 4 via the plurality of power rollers 8, and the output shaft 3 fixed to the output disk 4 rotates.

When the rotational speed of the input shaft 1 and the output shaft 3 is changed, and when deceleration is first performed between the input shaft 1 and the output shaft 3, each of the trunnions 6, 6 around the pivots 5, 5 is used.
As shown in FIG. 5, the peripheral surfaces 8a, 8a of the power rollers 8, 8 are closer to the center of the inner surface 2a of the input disk 2 and to the outer surface of the inner surface 4a of the output disk 4. And the respective displacement shafts 7, 7 are tilted so as to abut against them.

Conversely, when increasing the speed, the trunnions 6, 6 are swung so that the peripheral surfaces 8a, 8a of the power rollers 8, 8, as shown in FIG. A portion near the outer periphery of the side surface 2a and an inner side surface 4a of the output side disk 4
The respective displacement shafts 7 are inclined so as to abut against the portion near the center of. FIG. 5 shows the inclination angles of the displacement shafts 7, 7.
6 and FIG. 6, an intermediate speed ratio can be obtained between the input shaft 1 and the output shaft 3.

FIGS. 7 to 10 show an example of a more specific toroidal type continuously variable transmission. Housing 1
5 is made hollow by casting a light metal such as an aluminum alloy, and has an input side wall portion 16 and an output side wall portion 17.
The two wall portions 16 and 17 are formed integrally with the housing 15. Therefore, the operation of inserting each component into the housing 15 is performed by these two wall portions 16 and 1.
7 is carried out through an opening (not shown) provided in the portion between the two. The input shaft 18 is rotatably supported in the housing 15 and rotates together with the drive shaft 19.

The drive shaft 19 is rotatably supported inside a through hole 20 formed in the input side wall portion 16 through a support cylinder 21 and a rolling bearing 22. or,
The drive shaft 19 located inside the housing 15
A support pin 23 is provided at the center of the inner end face of the
Are provided around each of them. on the other hand,
The inner peripheral edge of the cam plate 10a is spline-engaged with the outer peripheral surface of the base end (the left end in FIGS. 7 and 8) of the input shaft 18. The projections 25, 25 formed on the outer surface of the cam plate 10a are engaged with the irregularities formed on the distal end of the engagement cylinder 24. Therefore, the rotation of the drive shaft 19 is transmitted to the input shaft 18 via the engagement cylinder 24, the projections 25, 25, and the cam plate 10a, and rotates the input shaft 18.

The input shaft 18 has a base 26 (left end in FIGS. 7 and 8) formed with a recess 26 having a circular cross section. The support pin 23 is inserted into the recess 26. I have. A bearing 27 such as a needle bearing or a sliding bearing is provided between the outer peripheral surface of the support pin 23 and the inner peripheral surface of the concave hole 26. Therefore, the base end of the input shaft 18 is rotatably supported by the input side wall 16 via the drive shaft 19. A disc spring 29 is provided between the flange 28 formed on the outer peripheral surface of the base end of the input shaft 18 and the cam plate 10a, and a first input-side disk described below is provided on the cam plate 10a. The elasticity toward 2A is given.

A first input-side disc 2A is rotatably supported via a needle bearing 30 at a portion near the base end of the input shaft 18 (near the left end in FIGS. 7 and 8). And
Rollers 12, 12 are provided between a cam surface 14 formed on the outer side surface (left side surface in FIGS. 7 and 8) of the first input side disk 2A and a cam surface 13 formed on the side surface of the cam plate 10a. And a loading device 9 of the loading cam type.
On the other hand, near the tip of the input shaft 18 (rightward in FIGS. 7 and 8).
The inner peripheral edge of the second input side disk 2B is spline-engaged with the portion. A loading nut 31 is screwed onto a portion of the input shaft 18 that protrudes from the outer surface (the right side surface in FIGS. 7 and 8) of the second input-side disk 2B at the distal end. A disc spring 32 is provided between the loading nut 31 and the second input side disk 2B. Therefore, when the drive shaft 19 rotates, these two input side disks 2A, 2B rotate in the same direction while being elastically pressed in the direction approaching each other.

Further, a first portion is provided at an intermediate portion of the input shaft 18.
The second output side disks 4A, 4B are rotatably supported via needle bearings 33, 33, respectively. The output gear 34 is sandwiched between the two output disks 4A and 4B. The output gear 34 engages with the first and second output disks 4A and 4B in an uneven manner, and rotates in synchronization with both the output disks 4A and 4B.

The first input side disk 2A and the first output side disk 4A have their inner side surfaces 2a, 4a facing each other, and the second input side disk 2A
B and the second output side disk 4B are mutually inner surfaces 2
a and 4a are opposed to each other. The power rollers 8, 8 rotatably supported by the trunnions 6, 6, respectively, are sandwiched between the inner surfaces 2a, 4a. The inclination angles of these power rollers 8, 8 are controlled while synchronizing with each other. Therefore, the rotation speeds of the first and second output side disks 4A and 4B are always the same.

A transmission shaft 35 disposed in parallel with the input shaft 18 is rotatably supported inside the housing 15. A first transmission gear 36 fixed to one end (the left end in FIG. 8) of the transmission shaft 35 meshes with the output gear 34. A second transmission gear 37 is fixed to the other end of the transmission shaft 35 (the right end in FIG. 8). Further, a third transmission gear 38 (see FIG. 9) meshed with the second transmission gear 37 is meshed with a fourth transmission gear 39. The fourth transmission gear 39 is formed integrally with a base end (left end in FIGS. 7, 8, and 10) of an output shaft 40 described below.

The base end of the output shaft 40 is connected to the output side wall 1.
7 is rotatably supported by a rolling bearing 42 inside the through hole 41 formed therein. That is, the rolling bearing 42 is provided between the outer peripheral surface of the cylindrical portion 43 formed on one side surface (the left side surface in FIGS. 7 and 8) of the fourth transmission gear 39 and the inner peripheral edge of the through hole 41. I have. An auxiliary housing 44 is fixed to the outer side surface of the output side wall portion 17 via a bracket 45. The intermediate portion of the output shaft 40 is supported by a rolling bearing 46 on the inner peripheral edge of the auxiliary housing 44. Like the housing 15, the auxiliary housing 44 and the bracket 45 are made of a light metal such as an aluminum alloy for weight reduction.

Further, the base end face of the output shaft 40 (FIG. 7,
On the left end faces 8 and 10), a concave hole 47 having a circular cross section is formed. A locking shaft portion 48 protruding from the loading nut 31 at the tip of the input shaft 18 is supported inside the concave hole 47 via a needle bearing 49. Therefore, the tip of the input shaft 18 is connected to the output side wall 1.
7 is rotatably supported via the output shaft 40. Supporting the tip of the input shaft 18 on the output side wall portion 17 via the output shaft 40 in the following manner is as follows.
(1) (2) (3).

(1) It is necessary to arrange the input shaft 18 and the output shaft 40 coaxially. For example, in order to efficiently arrange a crankshaft of an engine and a drive shaft for transmitting power to wheels, it is often preferable to arrange the input shaft 18 and the output shaft 40 coaxially.

(2) The disc spring 32 and the loading nut 31 are mounted on the tip of the input shaft 18. That is, even when the input shaft 18 and the output shaft 40 are coaxially arranged for the reason (1), both the members 32 and 31 are connected to the input shaft 18.
Must be attached to the tip of the These two members press the second input side disk 2B toward the power rollers 8 and 8, and immediately after the operation of the pressing device 9 starts, the peripheral surfaces 8a and 8a of the power rollers 8 and 8 and each disk 2A, 4
A, 2B, and 4B function so that the contact pressure with the inner side surfaces 2a, 4a becomes sufficiently high.

Since it is necessary to mount such a disc spring 32 and the loading nut 31 on the distal end of the input shaft 18, a space for inserting the two members 32, 31 is secured on the extension of the distal end. There is a need. Therefore, FIGS.
As shown in FIG. 0, a structure in which the tip of the input shaft 18 is supported on the output side wall 17 via the output shaft 40 is employed.

(3) The structure is to absorb the displacement of the input shaft 18 in the axial direction, and to prevent wear of the aluminum alloy housing 15. That is, during operation of the toroidal type continuously variable transmission, the input shaft 18 is slightly displaced in the axial direction, albeit slightly. Therefore, the distal end of the input shaft 18 is supported by the needle bearing 49 to absorb the displacement, but the needle constituting the needle bearing 49 is also finely displaced in the axial direction. Therefore,
When the outer raceway of the needle bearing 49 is formed on the output side wall portion 17 made of aluminum alloy,
May wear out early, and the tip of the input shaft 18 may rattle.

[0023]

However, in the case of the toroidal type continuously variable transmission configured and operated as described above, the toroidal type continuously variable transmission has a structure in which the tip of the input shaft 18 is supported on the output side wall portion 17 via the output shaft 40. Then, there are the following points to be solved.

That is, the output shaft 40 may vibrate during operation of the toroidal type continuously variable transmission. For example, when the toroidal type continuously variable transmission is operated in a speed increasing state, the output shaft 40 rotates at a high speed, and when the toroidal type continuously variable transmission is operated in a deceleration state, the output shaft 40 is operated with a high load. As a result, the output shaft 40 may vibrate. Further, such vibration of the output shaft 40 is generated by a gear transmission mechanism for transmitting power from the output gear 34 to the output shaft 40, such as a fourth transmission gear 39 fixed to the output shaft 40, so that poor meshing can occur. Etc.

In any case, in the case of the toroidal type continuously variable transmission having the structure shown in FIGS. 7 to 10, the vibration of the output shaft 40 generated in this manner is caused by the needle bearing 49 and the locking shaft portion. The signal is transmitted to the input shaft 18 through the input shaft 48. The vibration transmitted to the input shaft 18 in this manner is
First and second input side disks 2 supported on the outer peripheral surface of
A, 2B, the first and second output side disks 4A, 4B, and further to the respective power rollers 8, 8 via the respective disks 2A, 2B, 4A, 4B. As a result, the inner surface 2a of each of these disks 2A, 2B, 4A, 4B,
This may adversely affect the fatigue life and the like of the contact portion between the power roller 4a and the peripheral surfaces 8a of the power rollers 8, and may impair the durability of the toroidal type continuously variable transmission.

The toroidal type continuously variable transmission of the present invention has been made in view of such circumstances, and the vibration of the output shaft is applied to the input shaft while satisfying the necessary conditions for the configuration of the toroidal type continuously variable transmission. It is intended to prevent transmission and improve durability.

[0027]

A toroidal-type continuously variable transmission according to the present invention has a housing having an input side wall portion and an output side wall portion, and a housing having an input side wall portion, as in the above-described conventional toroidal type continuously variable transmission. An input shaft rotatably supported, an output shaft arranged concentrically with the input shaft, an input disk supported by spline engagement on an outer peripheral surface of an intermediate portion of the input shaft and rotating with the input shaft, An output-side disk rotatably supported on the input shaft on the outer peripheral surface of the input shaft; a power transmission means provided between the output-side disk and the output shaft; A trunnion swinging about a pivot at the position, a displacement shaft having a tip protruding from the inner surface of the trunnion, and the input shaft being rotatably supported around the tip of the displacement shaft. Side, and a power roller interposed between the output side disks. The inner surface of each of the disks is an arc-shaped concave surface in cross section, and the peripheral surface of the power roller is a spherical convex surface, and the peripheral surface and the inner surface are in contact with each other.

In particular, in the toroidal-type continuously variable transmission according to the present invention, an end portion of the input shaft near the output side wall portion.
And the loading nut screwed into the
Disc spring provided between a nut and the input side disk
And the loading provided on the output side wall portion.
It has a through hole having an inner diameter larger than the outer diameter of the nut and the disc spring, and a detachable support bracket inside the through hole. The end portion of the input shaft to the support bracket, independent of the output shaft without passing through the output shaft
It is rotatably supported Te.

[0029]

The toroidal-type continuously variable transmission of the present invention configured as described above transmits the rotational force between the input shaft and the output shaft based on the same operation as the above-mentioned conventional toroidal-type continuously variable transmission. And the rotational speed ratio between these two shafts is changed.

In particular, in the case of the toroidal type continuously variable transmission of the present invention, it is possible to prevent the vibration of the output shaft from being transmitted to the input shaft while satisfying the necessary conditions for the configuration of the toroidal type continuously variable transmission.

[0031]

DETAILED DESCRIPTION FIG. 1 corresponds to claims 1 to 3 show a first embodiment of the present invention. The feature of the present invention is to prevent the vibration of the output shaft 40 from being transmitted to the input shaft 18.
The point is that the structure of the supporting portions of these two shafts 40 and 18 is devised. The structure and operation of the other parts are the same as those of the conventionally known toroidal-type continuously variable transmission. Therefore, description of the same parts as the conventional structure is omitted, and
The following description focuses on the features of the present invention.

A through hole 41a is formed in the output side wall portion 17 of the housing 15. The support bracket 50 is mounted inside the through hole 41a. The support bracket 50 has a cylindrical portion 51, a mounting flange 52 provided on an outer peripheral surface of the cylindrical portion 51, and an L-shaped cross section that is bent inward from one end (the right end in FIG. 1) of the cylindrical portion 51. And a supporting flange 53. On the other hand, on the outer side surface (the right side surface in FIG. 1) of the output side wall portion 17, a recess 54 is formed in a portion surrounding the through hole 41 a so that the mounting flange 52 can be fitted outside without rattling. .

When the tip of the input shaft 18 is supported, first, at the tip of the input shaft 18, a portion protruding from the outer side surface (the right side surface in FIG. 1) of the second input side disk 2B is fitted with a disc spring. Then, the loading nut 31 is screwed on. Next, the mounting flange 52 is
To fit inside. At the same time, the locking shaft 48 formed at the tip of the input shaft 18 is inserted into the center hole 55 of the support flange 53. At the same time as this insertion operation, a needle bearing 49 is mounted between the inner peripheral surface of the center hole 55 and the outer peripheral surface of the locking shaft portion 48. Further, the mounting flange 52 and the output side wall portion 17 are screwed to fix the support bracket 50 to the output side wall portion 17. That is, the support bracket 50 is detachable from the output side wall portion 17 by tightening or loosening a screw. As a result of the screwing, the distal end of the input shaft 18 is connected to the output side wall portion 17 via the support bracket 50.
And is rotatably supported.

On the other hand, the output shaft 40 is connected to the output side wall 17.
The roller 45 is rotatably supported by a rolling bearing 42 on an inner peripheral surface of a bracket 45 fixed to an outer surface of the bracket 45. As a result,
The input shaft 18 and the output shaft 40 are connected to the output side wall 17.
Supported independently of each other.

In the case of the toroidal type continuously variable transmission of the present invention configured as described above, the vibration of the output shaft 40 is applied to the input shaft 18 while satisfying the necessary conditions for the configuration of the toroidal type continuously variable transmission. Transmission can be prevented. That is,

(1) As is clear from FIG.
And the output shaft 40 can be arranged coaxially. Therefore, for example, a crankshaft of an engine and a drive shaft for transmitting power to wheels can be efficiently arranged.

(2) Even when the input shaft 18 and the output shaft 40 are coaxially arranged as described above, the disc spring 32 and the loading nut 31 are attached to the tip of the input shaft 18 without particularly troublesome assembling work. And can be attached. That is, before the support bracket 50 is mounted, a space in which the members 32 and 31 can be inserted is secured inside the through hole 41a. Therefore, the mounting work of these two members 32, 31 can be easily performed.

(3) The support bracket 50 is much smaller than the entire housing 15. Therefore, even if the support bracket 50 is made of a hard metal such as steel, the weight increase of the toroidal type continuously variable transmission is extremely small. It will be. Therefore, in order to adopt a structure in which the locking shaft portion 48 at the tip of the input shaft 18 is rotatably supported while absorbing the displacement in the axial direction.
Needle bearings 49 are directly provided on the inner peripheral surface of the support flange 53.
The inner peripheral surface is not significantly worn even when the needle constituting the above is brought into contact.

(4) It becomes difficult for the vibration of the output shaft 40 to be transmitted to the input shaft 18. That is, between the two shafts 18 and 40, a rolling bearing 42 and a
The bracket 45 and the output side wall portion 17 of the housing 15
, A support flange 53 and a needle bearing 49. Of these, the rolling bearing 42, the bracket 45,
Output side wall 17 of housing 15 and support flange 53
Are increased compared to the conventional structure described above. Moreover,
The bracket 45 and the housing 15 made of a light metal such as an aluminum alloy are provided with a needle bearing 4 made of bearing steel.
9 has a larger internal loss and is less likely to transmit vibration. Therefore, as described above, it is difficult for the vibration of the output shaft 40 to be transmitted to the input shaft 18, and the input shaft 18
First and second input side disks 2 supported on the outer peripheral surface of
A, 2B, inner surfaces 2a, 4a of first and second output disks 4A, 4B and peripheral surfaces 8a, 8a of power rollers 8, 8
This has no adverse effect on the fatigue life and the like of the contacting portion. As a result, the durability of the toroidal-type continuously variable transmission can be improved. Further, since no harmful vibration is applied to the contact portion, an improvement in transmission efficiency can be expected.

Next, FIG. 2 corresponds to claims 1 and 4.
7 shows a second embodiment of the present invention. In the case of this embodiment, the cylindrical portion 56 formed at the center of the support bracket 50
Of the input shaft 18 distal locking shaft portion 48 of the inner and supports the needle bearing 49. A cylindrical portion 57 is formed at the base end of the output shaft 40, and a fourth transmission gear 39 is integrally formed on the outer peripheral surface of the cylindrical portion 57. The cylindrical portion 57 is supported around the cylindrical portion 56 by the rolling bearing 42a.

In the case of the present embodiment, the number of members existing between the output shaft 40 and the input shaft 18 is smaller than that of the first embodiment, so that the vibration from the output shaft 40 to the input shaft 18 is small. The effect of preventing transmission is inferior to that of the first embodiment. However, the effect of preventing vibration transmission is superior to that of the conventional structure described above. Other configurations and effects are the same as those of the above-described first embodiment.

Next, FIG. 3 corresponds to claims 1 and 5.
7 shows a third embodiment of the present invention. In the case of this embodiment, the cylindrical bearing 57 formed at the base end of the output shaft 40 is supported by the needle bearing 60 around the cylindrical part 56 formed at the center of the support bracket 50, and the rolling bearing 42.
Thus, it is also supported inside the bracket 45. As a result, in the case of the present embodiment, the support rigidity of the base end of the output shaft 40 is improved. Other configurations and operations are the same as in the above-described second embodiment.

Next, FIG. 4 corresponds to claims 1 and 6.
9 shows a fourth embodiment of the present invention. In the case of the present embodiment, the distal end of the input shaft 18 is provided inside the cylindrical portion 56 formed at the center of the support bracket 50 by a deep groove ball bearing 58 .
We support. To allow the axial displacement of the input shaft 18 in the axial direction, the outer ring 59 of the ball bearing 58
Is fitted inside the inside so as to be displaceable in the axial direction. Other configurations and operations are the same as those of the above-described second and third embodiments.

[0044]

The toroidal type continuously variable transmission according to the present invention is constructed and operates as described above. Therefore, it is possible to prevent the vibration of the output shaft from being transmitted to the input shaft while satisfying the necessary conditions in the construction. Thus, the durability and reliability of the toroidal type continuously variable transmission can be improved.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a first embodiment of the present invention and corresponding to a right portion of FIG.

FIG. 2 is a sectional view similar to FIG. 1, showing a second embodiment of the present invention;

FIG. 3 is a sectional view similar to FIG. 1, showing the third embodiment;

FIG. 4 is a sectional view similar to FIG. 1, showing the fourth embodiment;

FIG. 5 is a side view showing a basic configuration of a conventionally known toroidal type continuously variable transmission in a state of maximum deceleration.

FIG. 6 is a side view showing a state at the time of maximum speed increase.

FIG. 7 is a sectional view showing an example of a conventional specific structure.

FIG. 8 is a sectional view taken along line AA of FIG. 7;

FIG. 9 shows a combined state of second to fourth gears,
A schematic view from the right side of FIG.

FIG. 10 is an enlarged sectional view of the right part of FIG. 8;

[Explanation of symbols]

 Reference Signs List 1 input shaft 2 input disk 2A first input disk 2B second input disk 2a inner surface 3 output shaft 4 output disk 4A first output disk 4B second output disk 4a inner surface 5 pivot Reference Signs List 6 trunnion 7 displacement shaft 8 power roller 8a peripheral surface 9 pressing device 10 cam plate 11 retainer 12 roller 13, 14 cam surface 15 housing 16 input side wall portion 17 output side wall portion 18 input shaft 19 drive shaft 20 inlet side through hole 21 support Cylinder 22 Rolling bearing 23 Support pin 24 Engaging cylinder 25 Protrusion 26 Concave hole 27 Bearing 28 Flange 29 Disc spring 30 Needle bearing 31 Loading nut 32 Disc spring 33 Needle bearing 34 Output gear 35 Transmission shaft 36 First transmission gear 37 Second transmission gear 38 Third transmission gear 39 Fourth transmission gear 40 Output shaft 41 41a Through-hole 42, 42a Rolling bearing 43 Cylindrical part 44 Auxiliary housing 45 Bracket 46 Rolling bearing 47 Recessed hole 48 Locking shaft part 49 Needle bearing 50 Support bracket 51 Cylindrical part 52 Mounting flange 53 Support flange 54 Depression 55 Center hole 56, 57 Cylindrical part 58 Ball bearing 59 Outer ring 60 Needle bearing

Claims (6)

(57) [Claims] 1. A housing having an input side wall and an output side wall, an input shaft rotatably supported in the housing, an output shaft disposed concentrically with the input shaft, and an intermediate portion between the input shaft. An input disk supported on the outer peripheral surface by spline engagement and rotating with the input shaft; an output disk rotatably supported on the outer peripheral surface of the input shaft with respect to the input shaft; Power transmission means provided between the output shaft, a trunnion that swings about a pivot that is in a twisted position with respect to the input shaft, and a displacement shaft that has a tip portion protruding from the inner surface of the trunnion. A power roller sandwiched between the input-side and output-side disks in a state rotatably supported around the distal end of the displacement shaft, and the inner surfaces of both the disks are cut off. In the toroidal-type continuously variable transmission in which the surface is an arc-shaped concave surface, the peripheral surface of the power roller is a spherical convex surface, and the peripheral surface and the inner surface are in contact with each other, the input shaft Of which is screwed into the end near the output side wall.
Loaded loading nut and this loading nut
Disc spring provided between the input side disk and
These loading nuts provided on the output side wall section
And a through hole having an inner diameter larger than the outer diameter of the disc spring and
With a removable support bracket inside the through hole,
The end of the input shaft is attached to the support bracket by the output shaft.
A toroidal-type continuously variable transmission characterized in that it is rotatably supported independently of the output shaft without any intervening shaft . 2. The toroidal-type continuously variable transmission according to claim 1, wherein the output shaft is supported on the output side wall by a separate support bracket independently of the input shaft. 3. A supporting shaft portion formed at a tip of the input shaft is supported by a needle bearing on an inner peripheral surface of a support flange provided on the support bracket, and an output shaft is supported on an inner peripheral surface of another support bracket. The toroidal-type continuously variable transmission according to claim 2, wherein the toroidal-type continuously variable transmission is supported by a rolling bearing. 4. A locking shaft formed at the tip of the input shaft is supported by a needle bearing inside a cylindrical portion provided on the support bracket, and another cylindrical portion formed at a base end of the output shaft. The toroidal-type continuously variable transmission according to claim 1, wherein the cylindrical portion is supported by a rolling bearing. 5. A locking shaft formed at a tip of an input shaft is supported by a needle bearing inside a cylindrical portion provided on a support bracket, and another cylindrical portion formed at a base end of an output shaft. The needle member is supported around the cylindrical portion by another needle bearing, and the base end of the output shaft is supported by a rolling bearing with respect to another support bracket fixed to the output side wall portion. 2. The toroidal-type continuously variable transmission according to 1. 6. A tip portion of an input shaft is supported by a deep groove ball bearing inside a cylindrical portion formed at the center of a support bracket, and another cylindrical portion formed at a base end portion of an output shaft is provided. 2. The bearing according to claim 1, wherein the cylindrical portion is supported by a needle bearing, and a base end of the output shaft is supported by a rolling bearing with respect to another support bracket fixed to an output side wall portion. Toroidal type continuously variable transmission.