JPH07243493A - Toroidal type continuously variable transmission - Google Patents

Abstract

PURPOSE:To improve durability of a thrust needle bearing by exerting a uniform thrust load on a plurality of needles of which the thrust needle bearing consists. CONSTITUTION:The diameters of needles 33 and 33 are changed taking resilient deformation of a trunnion 6 during operation into consideration. The diameters of the needles 33 and 33 are decreased in two end positions in the direction of length wherein a distance between the inside surface of the trunnion 6 and a mating surface is decreased, and increased in a central position.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION The toroidal type continuously variable transmission according to the present invention is used, for example, as a transmission for automobiles 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. 3 and 4 has been studied as a transmission for an automobile. This toroidal type continuously variable transmission supports the input side disk 2 concentrically with the input shaft 1 and is arranged concentrically with the input shaft 1, as disclosed in, for example, Japanese Utility Model Laid-Open No. 62-71465. The output disk 4 is fixed to the end of the output shaft 3. Inside the casing in which the toroidal type continuously variable transmission is housed, there are provided trunnions 6 and 6 which swing around a pivot shaft 5 and 5 which are twisted with respect to the input shaft 1 and the output shaft 3. .

The trunnions 6, 6 are provided with the pivots 5, 5 on the outer surfaces of both ends. Further, the base ends of the displacement shafts 7, 7 are supported on the central portions of the trunnions 6, 6 and the trunnions 6, 6 are swung about the pivot shafts 5, 5, so that the displacement shafts 7, 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, 8 are sandwiched between the input side and output side disks 2, 4.

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

A loading cam type pressing device 9 is provided between the input shaft 1 and the input side disk 2, and the pressing device 9 causes the input side disk 2 to face the output side disk 4 and elastically moves. Pressing. This pressing device 9
Is a cam plate 10 that rotates together with the input shaft 1, and a retainer 11.
A plurality of (for example, four) rollers 12 held by
It is composed of 12 and. On one side surface (left side surface of FIGS. 3 to 4) of the cam plate 10, a cam surface 13 which is an uneven surface extending in the circumferential direction is formed, and the outer side surface of the input side disk 2 (right side of FIGS. 3 to 4). The same cam surface 14 is also formed on the surface). Then, the plurality of rollers 12, 12 are rotatably supported about a shaft in the radial direction with respect to the center of the input shaft 1.

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

When the rotational speeds of the input shaft 1 and the output shaft 3 are changed, and when deceleration is first performed between the input shaft 1 and the output shaft 3, the trunnions 6, 6 centering on the pivot shafts 5, 5 are used.
3, the peripheral surfaces 8a, 8a of the power rollers 8, 8 are located near the center of the inner side surface 2a of the input side disk 2 and near the outer peripheral side of the inner side surface 4a of the output side disk 4, as shown in FIG. The displacement shafts 7, 7 are tilted so as to abut with and respectively.

On the other hand, when increasing the speed, the trunnions 6, 6 are swung so that the peripheral surfaces 8a, 8a of the power rollers 8, 8 are located inside the input side disk 2 as shown in FIG. The outer peripheral portion of the side surface 2a and the inner side surface 4a of the output side disk 4
The displacement shafts 7, 7 are tilted so that they are brought into contact with the central portions of the displacement shafts 7, 7, respectively. The inclination angles of the displacement axes 7, 7 are shown in FIG.
4 and FIG. 4, an intermediate gear ratio can be obtained between the input shaft 1 and the output shaft 3.

Further, FIGS. 5 to 8 show the Japanese Patent Application No. 63-6929.
3 shows a more specific toroidal-type continuously variable transmission described in the microfilm of No. 3 (Actual Kaihei No. 1-173552). Input side disk 2 and output side disk 4
Is rotatably supported around a cylindrical input shaft 15 via needle bearings 16 and 16, respectively. The cam plate 10 is spline-engaged with the outer peripheral surface of the end portion (the left end portion in FIG. 5) of the input shaft 15 and is prevented from moving in the direction away from the input side disk 2 by the collar portion 17. Then, the cam plate 10 and the rollers 12 and 12 cause the input side disk 2 to rotate based on the rotation of the input shaft 15.
Is rotated while being pressed toward the output side disk 4,
A loading cam type pressing device 9 is configured. An output gear 18 is provided on the output side disk 4 with keys 19, 19
And the output side disk 4 and the output gear 18
It is designed so that and rotate in synchronization.

Both ends of the pair of trunnions 6, 6 are supported by the pair of support plates 20, 20 so as to be swingable and displaceable in the axial direction (front and back directions in FIG. 5, left and right directions in FIG. 6). There is.
The displacement shafts 7, 7 are supported in the circular holes 23, 23 formed in the intermediate portions of the trunnions 6, 6. The displacement shafts 7, 7 are parallel to each other and eccentric to the support shaft portion 2.
1 and 21 and pivots 22 and 22, respectively.
Of these, the support shaft portions 21 and 21 are attached to the circular holes 23 and 23, respectively.
Is rotatably supported on the inner side of the bearing via needle bearings 24, 24. In addition, the power rollers 8 and 8 are provided around the pivot shafts 22 and 22 and the needle rollers 25 and 25 are provided separately.
It is rotatably supported via.

The pair of displacement shafts 7, 7 are provided at positions opposite to the input shaft 15 by 180 degrees. or,
The direction in which the pivot shafts 22, 22 of the displacement shafts 7, 7 are eccentric to the support shafts 21, 21 is the input side,
The rotation directions of the output side disks 2 and 4 are the same (left and right opposite directions in FIG. 6). Further, the eccentric direction is set to be a direction substantially orthogonal to the disposing direction of the output shaft 15. Therefore, the power rollers 8 and 8 are connected to the input shaft 1.
5 is supported so as to be slightly displaceable in the arrangement direction. As a result, even if the power rollers 8, 8 tend to be displaced in the axial direction of the input shaft 15 due to the dimensional accuracy of the components, etc., without applying an unreasonable force to the components, This displacement can be absorbed.

A thrust rolling bearing is provided between the outer surface of each of the power rollers 8 and 8 and the inner surface of the intermediate portion of each of the trunnions 6 in order from the outer surface of the power rollers 8, 8. Thrust ball bearings 26, 26 and thrust needle bearings 27, 27 are provided. The thrust ball bearings 26, 26 support the loads in the thrust direction applied to the power rollers 8, 8 and allow the power rollers 8, 8 to rotate. Each of such thrust ball bearings 26, 26 has a plurality of balls 2.
9, 29, annular retainers 28, 28 that hold the balls 29, 29 rotatably, and annular outer rings 30, 30. The inner ring raceways of the thrust ball bearings 26, 26 are formed on the outer side surfaces of the power rollers 8, 8 and the outer ring raceways are formed on the inner side surfaces of the outer races 30, 30 respectively.

Further, the thrust needle bearings 27, 27
Is composed of a race 31, a retainer 32, and needles 33, 33 as shown in FIGS. Race 3 of these
1 and the retainer 32 are combined so as to be slightly displaceable in the rotation direction. Also, these races 31 and cage 3
2 is an annular portion 34a whose center is the pivot shaft portion 22;
34b, and protrusions 35a and 35b that protrude diametrically outward from the partial outer peripheral edge of each annular portion 34a and 34b.

Such thrust needle bearings 27, 27
With the races 31 and 31 in contact with the inner side surfaces of the trunnions 6 and 6, the inner side surfaces and the outer ring 3 are
It is sandwiched between the outer surface of 0 and 30. The arrangement direction of each of the protrusions 35a and 35b is the same as that of the support shaft portion 21,
The eccentric directions of the pivot shaft portions 22, 22 with respect to 21 are matched. Such thrust needle bearings 27, 27 are
While supporting the thrust load applied to the outer rings 30, 30 from the power rollers 8, 8, the pivot shaft portion 22,
22 and the outer rings 30, 30 are the support shaft portions 21, 21.
Allows swinging around.

Further, drive rods 36, 36 are connected to one end portions (lower end portions in FIG. 6) of the trunnions 6, 6 respectively, and drive pistons 37, 37 are provided on outer peripheral surfaces of intermediate portions of the drive rods 36, 36. Is fixed. Then, the drive pistons 37, 37 are respectively connected to the drive cylinder 3
8 and 38 are oil-tightly fitted.

In the case of the toroidal type continuously variable transmission configured as described above, the rotation of the input shaft 15 is transmitted to the input side disk 2 via the pressing device 9. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 via the pair of power rollers 8, 8 and the rotation of the output side disk 4 is taken out from the output gear 18.

When changing the rotational speed ratio between the input shaft 15 and the output gear 18, the pair of drive pistons 37,
37 is displaced in opposite directions. As the drive pistons 37, 37 are displaced, the pair of trunnions 6,
6 are displaced in the opposite directions, for example, the power roller 8 on the right side of FIG. 6 is displaced to the upper side of the figure, and the power roller 8 on the left side of the figure is displaced to the lower side of the figure. As a result, the peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner side surfaces 2a, 4a of the input side disk 2 and the output side disk 4 are described.
The direction of the tangential force acting on the contact portion with and changes. The trunnions 6, 6 are pivotally supported by the support plates 20, 20 according to the change in the direction of the force.
It swings in directions opposite to each other with 5 as the center.

As a result, as shown in FIGS.
The contact position between the peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner side surfaces 2a, 4a changes, and the input shaft 15
The rotational speed ratio between the output gear 18 and the output gear 18 changes.

In order to change the rotational speed ratio between the input shaft 15 and the output gear 18 in this manner, the displacement shafts 7, 7
When changing the inclination angle of each of the displacement axes 7, 7,
Rotates slightly about each of the support shafts 21, 21. As a result of this rotation, the thrust ball bearings 26, 26 are
The outer surfaces of the outer rings 30, 30 and the inner surfaces of the trunnions 6, 6 are relatively displaced. Since the thrust needle bearings 27, 27 are present between the outer side surface and the inner side surface, the force required for this relative displacement is small. Therefore, as described above, a small force is required to change the inclination angles of the displacement shafts 7, 7.

Although not described in publications or the like, the present inventors previously considered a thrust needle bearing as shown in FIG. 9 as a thrust needle bearing conforming to the structure of FIG. This thrust needle bearing has an annular main cage 3
9 and arc-shaped sub-retainers 40a and 40b, and a plurality of needles 33 and 33 are rotatably held in the retainers 39, 40a and 40b, respectively. Of these, the main retainer 39 is arranged around the support shaft portion 21 constituting the displacement shaft 7, and the sub-retainers 40a and 40b are aligned with the eccentric direction of the pivot shaft portion 22 with respect to the support shaft portion 21, It is arranged on the outer portion of the main cage 39. In any case, in the case of the conventional thrust needle bearing, a plurality of needles 3
As the materials 33 and 33, those having the same outer diameter and the same length were used.

[0021]

However, in the case of the toroidal type continuously variable transmission configured and operating as described above, there are the following points to be solved. That is, the thrust needle bearing 2 provided between the outer side surface of the outer ring 30, 30 of the thrust ball bearing 26, 26 and the inner side surface of each trunnion 6, 6.
The thrust load applied to 7 becomes uneven over the surface direction. Such non-uniformity of thrust load is caused by elastic deformation of the trunnions 6, 6 based on the thrust load applied to the power rollers 8, 8.

That is, during operation of the toroidal type continuously variable transmission, the trunnions 6, 6 are elastically deformed in the lengthwise direction based on the thrust load. Then, the distance between the inner side surface of each trunnion 6, 6 and the outer side surface of the outer ring of each outer ring 30, 30 becomes non-uniform. The trunnions 6, 6 are elastically deformed in an arc shape over the length direction based on the thrust load applied to the lengthwise intermediate portion through the power rollers 8, 8. Therefore, the distance between the inner side surface and the outer side surface is large at the central portion in the length direction and small at both end portions.

Thus, the thrust needle bearings 27, 27
Although the distance between the two surfaces to be supported becomes uneven due to the conventional structure, in the case of the conventional structure, the thrust needle bearing 2
As the plurality of needles 33, 33 constituting 7, 27, those having the same outer diameter and length were used. Therefore,
The thrust load is not uniformly applied to all the needles 33, 33, but is largely applied to some of the needles 33, 33.
For example, in the case of the structure shown in FIG. 9, a large thrust load acts on the needles 33, 33 arranged at both ends in the longitudinal direction (vertical direction in FIG. 9) of the inner surface of the trunnion 6,
Only a small thrust load acts on the needles 33, 33 arranged in the central portion in the length direction.

As a result, the load on the needles 33, 33 arranged at both ends in the longitudinal direction of the inner side surface of the trunnion 6 and the raceway surface facing the rolling surfaces of the needles 33, 33 becomes large, and these surfaces Sufficient durability cannot be secured, such as shortening the fatigue life of. Further, the balls 29, 29 of the thrust ball bearing 26, which is a rolling element of the thrust rolling bearing, and the outer ring 3
Since the contact load of 0 becomes large near both ends of the trunnion 6 in the lengthwise direction, the fatigue life of the thrust ball bearing 26, which is the thrust rolling bearing, also becomes short. The toroidal type continuously variable transmission of the present invention was invented in view of the above circumstances.

[0025]

All of the toroidal type continuously variable transmissions of the present invention are concentric with each other, with their inner side surfaces facing each other, like the conventional toroidal type continuously variable transmission described above. And rotatably supported first and second discs, and a trunnion that swings about a pivot that is in a twisted position with respect to the central axes of the first and second discs and is parallel to each other and An eccentric support shaft portion and a pivot shaft portion, a displacement shaft rotatably supported by the support shaft portion of the trunnion, the pivot shaft portion is projected from the inner surface of the trunnion, In a state of being rotatably supported around the pivot shaft portion, the power roller sandwiched between the first and second disks, and provided on the outer side surface of the power roller, Thrust direction added to this power roller A thrust rolling bearing that allows the power roller to rotate while supporting the weight, and is provided between the outer surface of the outer ring that constitutes the thrust rolling bearing and the inner surface of the trunnion, and from the power roller to the outer ring. A thrust needle bearing that allows the pivot shaft portion and the outer ring to swing around the support shaft portion while supporting the applied thrust load, wherein the inner surfaces of the first and second disks are Each of the sections has an arcuate concave surface, and the peripheral surface of the power roller is a spherical convex surface, and the peripheral surface and the inner side surface are in contact with each other.

Particularly, in the case of the toroidal type continuously variable transmission described in claim 1, the following conditions are satisfied. The outer diameters of the plurality of needles forming the thrust needle bearing are slightly different depending on the arrangement position of the needles. The outer diameter of each needle is larger at the central portion of the trunnion in the lengthwise direction and smaller at the portions closer to both ends in the longitudinal direction.

Further, in the case of the toroidal type continuously variable transmission described in claim 2, the following condition is satisfied. The lengths of the plurality of needles forming the thrust needle bearing differ depending on the arrangement position of the needles. The needle used is long as long as the end of the needle does not interfere with other members.

[0028]

The toroidal type continuously variable transmission of the present invention constructed as described above is based on the same action as that of the above-described conventional toroidal type continuously variable transmission, and is based on the operation between the first disk and the second disk. By transmitting the rotational force with, and changing the inclination angle of the trunnion, the rotational speed ratio of these two disks is changed.

Particularly, in the case of the toroidal type continuously variable transmission of the present invention, the thrust needle bearing provided between the inner surface of the trunnion and the outer surface of the outer ring forming the thrust rolling bearing covers substantially the entire surface thereof. And even thrust load is applied.

First, in the case of the toroidal type continuously variable transmission according to the first aspect of the present invention, the needles are adjusted in accordance with the uneven distance between the inner side surface and the outer side surface due to elastic deformation of the trunnion. Changing the diameter of. Therefore, only some of the needles are not stretched between these two surfaces, and the thrust load applied to the plurality of needles is made uniform. Further, the contact load between the rolling element of the thrust rolling bearing and the outer ring can be made uniform.

Further, in the case of the toroidal type continuously variable transmission according to the second aspect, it is possible to dispose the needle over substantially the entire length between the both surfaces. Therefore, the backup performance of the trunnion by the thrust needle bearing is improved, the trunnion is less likely to be elastically deformed, and the thrust load applied to the plurality of needles is made uniform.
Further, the contact load between the rolling element of the thrust rolling bearing and the outer ring can be made uniform.

[0032]

FIG. 1 shows a first embodiment of the present invention, which corresponds to claim 1. The feature of the present invention is that the plurality of needles 33, 33 constituting the thrust needle bearing 27 are arranged.
(See FIG. 9) A thrust load is uniformly applied to the needles 33, 33, members facing the needles 33, 33, and a thrust ball bearing 2 which is a thrust rolling bearing.
In order to improve the durability of No. 6, the diameter of the needles 33, 33 is devised in relation to the arrangement position. The structure and operation of the other parts are similar to those of the conventionally known toroidal type continuously variable transmission as described above. Therefore,
A description of the same parts as those of the conventional structure is omitted, and the characteristic parts of the present invention will be mainly described below.

The plurality of needles 33, 33 constituting the thrust needle bearing 27 are arranged separately in ranges A, B, C, D shown by slanted lattices in FIG. Each range A to D
In the arrangement direction of the needles 33, 33 in the radial direction about the center O of the support shaft portion 21 (see FIG. 6) of the displacement shaft 7 (this radiation coincides with the central axis of the needles 33, 33). Direction).

The outer diameters of the needles 33, 33 arranged in these ranges A to D are different in each range. The diameters of the plurality of needles 33, 33 included in the same range are the same. That is, the needles 3 included in the range C located near the center of the trunnion 6 in the longitudinal direction (vertical direction in FIG. 1).
The diameters of the needles 33 and 33 included in the range B slightly shifted toward the end side are set to be the same as or slightly smaller than the needles of the range C. Further, the range A located at the portions near both ends in the length direction,
The diameter of the needles 33, 33 included in D is small (C ≧ B
> A, D). The extent to which the diameters of the needles 33, 33 are made different in the respective ranges A to D in this way is determined by design depending on the length dimension and rigidity of the trunnion 6, the thrust load applied to the trunnion 6, and the like. However, even between the needles 33, 33 having the largest diameter, the difference (for example, C-
Even in A), it is about several tens to several hundreds of μm.

The thrust needle bearing 27 as described above is
Due to the elastic deformation of the trunnion 6, this trunnion 6
Inner surface of the outer ring 30 of the thrust ball bearing 26 (see FIG. 6)
The diameters of the needles 33, 33 are changed in accordance with the non-uniformity of the distance from the outer surface of the needle. Therefore, only some of the needles 33, 33 are not stretched between the two surfaces, and the thrust load applied to the plurality of needles 33, 33 is made uniform.

Next, FIG. 2 shows a second embodiment of the present invention corresponding to claim 2. Thrust needle bearing 33
The lengths of the plurality of needles 33, 33 (see FIG. 9) that make up the needle 33, 33 are made different in relation to the arrangement position of the needles 33, 33. That is, the needles 33, 33 are long as long as the ends of the needles 33, 33 do not interfere with other members.

That is, relatively short needles 33, 33 are used in the E portion surrounding about 2/3 of the support shaft portion 21 (see FIG. 6) of the displacement shaft 7, and the trunnion 6 in the remaining portion is used.
The longest needle 3 is located in the F part at the center position in the width direction.
I am using 3, 33. Further, needles 33, 33 having an intermediate length dimension are used for G and G portions located on both sides of the F portion (F>G> E).

In this way, by changing the length dimension of the needles 33, 33 according to the installation position, a plurality of needles 3
3, 33 to the inner surface of the trunnion 6 and the thrust ball bearing 2
It is possible to arrange the outer ring 30 of the outer ring 6 (see FIG. 6) over substantially the entire length of the outer ring 30. Therefore, the backup performance of the trunnion 6 by the thrust needle bearing 27 is improved, and the trunnion 6 is less likely to be elastically deformed. As a result, the thrust load applied to the plurality of needles 33, 33 can be made uniform.

[0039]

Since the toroidal type continuously variable transmission of the present invention is constructed and operates as described above, the durability and reliability of the thrust needle bearing portion and the thrust rolling bearing are improved, and the thrust needle bearing is improved. Further, the durability and reliability of the toroidal type continuously variable transmission incorporating the thrust rolling bearing can be improved.

[Brief description of drawings]

FIG. 1 is a schematic view of a trunnion inner surface portion showing a first embodiment of the present invention.

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

FIG. 3 is a side view showing a basic configuration of a conventionally known toroidal type continuously variable transmission in a state of maximum deceleration.

FIG. 4 is a side view showing the same state at the time of maximum acceleration.

FIG. 5 is a sectional view showing an example of a conventional specific structure.

6 is a cross-sectional view taken along the line AA of FIG.

FIG. 7 is a view of the thrust needle bearing incorporated in the conventional structure as viewed from the same direction as FIG. 1.

FIG. 8 is an enlarged BB sectional view of FIG.

FIG. 9 is a view similar to FIG. 7, showing a thrust needle bearing manufactured according to a conventional structure.

[Explanation of symbols]

 1 Input Shaft 2 Input Side Disk 2a Inner Side Surface 3 Output Shaft 4 Output Side Disk 4a Inner Side Surface 5 Axis 6 Trunnion 7 Displacement Axis 8 Power Roller 8a Circumferential Surface 9 Pressing Device 10 Cam Plate 11 Cage 12 Roller 13, 14 Cam Surface 15 Input shaft 16 Needle bearing 17 Collar part 18 Output gear 19 Key 20 Support plate 21 Support shaft part 22 Pivot shaft part 23 Circular hole 24, 25 Needle bearing 26 Thrust ball bearing 27 Thrust needle bearing 28 Cage 29 Ball 30 Outer ring 31 Race 32 retainer 33 needles 34a, 34b annular parts 35a, 35b protruding part 36 drive rod 37 drive piston 38 drive cylinder 39, 39A main retainer 40a, 40b sub-retainer 41 pocket

Claims (2)

[Claims] 1. In a state in which the inner surfaces of each other are opposed to each other,
First and second discs that are concentrically and rotatably supported, and a trunnion that swings about a pivot that is in a twisted position with respect to the central axes of these first and second discs and is parallel to each other. And a eccentric support shaft portion and a pivot shaft portion, and the support shaft portion is rotatably supported by the trunnion, and the pivot shaft portion is projected from the inner surface of the trunnion. And a power roller sandwiched between the first and second disks in a state of being rotatably supported around the pivot shaft portion, and provided on the outer side surface of the power roller. Between the outer surface of the outer ring forming the thrust rolling bearing and the inner surface of the trunnion while supporting the load in the thrust direction applied to the power roller and allowing the rotation of the power roller. A thrust needle bearing that allows the pivot shaft portion and the outer ring to swing around the support shaft portion while supporting the thrust load applied to the outer ring from the power roller. The inner surfaces of the first and second disks are concave surfaces each having an arcuate 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, and , A toroidal type continuously variable transmission that satisfies the following conditions. The outer diameters of the plurality of needles forming the thrust needle bearing are slightly different depending on the arrangement position of the needles. The outer diameter of each needle is larger at the central portion of the trunnion in the lengthwise direction and smaller at the portions closer to both ends in the longitudinal direction. 2. In a state in which the inner surfaces of each other are opposed to each other,
First and second discs that are concentrically and rotatably supported, and a trunnion that swings about a pivot that is in a twisted position with respect to the central axes of these first and second discs and is parallel to each other. And a eccentric support shaft portion and a pivot shaft portion, and the support shaft portion is rotatably supported by the trunnion, and the pivot shaft portion is projected from the inner surface of the trunnion. And a power roller sandwiched between the first and second disks in a state of being rotatably supported around the pivot shaft portion, and provided along with an outer surface of the power roller. Between the thrust ball bearing that allows the rotation of the power roller while supporting the load in the thrust direction applied to the power roller, and the outer surface of the outer ring forming the thrust ball bearing and the inner surface of the trunnion. Provided A thrust needle bearing that allows the pivot shaft and the outer ring to swing around the support shaft while supporting the thrust load applied from the power roller to the outer ring; The inner surface of the second disk is a concave surface having an arcuate cross section, 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. A toroidal type continuously variable transmission that satisfies the conditions of. The lengths of the plurality of needles forming the thrust needle bearing differ depending on the arrangement position of the needles. The needle used is long as long as the end of the needle does not interfere with other members.