JP2002349658A - Toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a toroidal type continuously variable transmission, which is easy to process fueling hole of a thrust-type rolling bearing and can surely supply lubricating oil to a pocket, in which a rolling element is stored through a fueling hole, without causing a low efficiency of transmission. SOLUTION: A straight line fueling hole 84, which passes through a center of each pocket 62 for penetrating from the inner to the outer periphery of a main body 83 toward the radial direction of the main body 83 is formed in the main body 83 of a holder 81. Also an annular recess groove 86 along the circumference direction is formed in a center of the inner periphery of the main body 83, and the inner opening of a fueling hole 84 is equipped in this recess groove 86.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a toroidal type continuously variable transmission used for an automobile or various industrial machines.

[0002]

2. Description of the Related Art As a transmission for an automobile, for example, a toroidal type continuously variable transmission as shown in FIGS. 8 and 9 is known. In this toroidal type continuously variable transmission, an input side disk 2 is provided so as to have the same central axis as the input shaft 1, and an output shaft 3 which is arranged so as to have the same central axis as the input shaft 1.
The output side disk 4 is fixed to the end of. Inside the casing containing the toroidal type continuously variable transmission, there are a plurality (two in this example) swinging about the pivots 5,5.
Trunnions 6 are provided. That is, each of the pivots 5, 5 is provided on both the input side and output side discs 2, 4, respectively.
8 and FIG. 9, a central axis of the two disks 2, 4 in a direction perpendicular to the axial direction of the two disks 2, 4 The trunnions 6 are provided on the outer surfaces of both ends of the respective trunnions 6.

[0003] In the middle of each trunnion 6, 6,
The base ends of the displacement shafts 7, 7 are supported, and the respective pivots 5, 5
By swinging the trunnions 6 around the center, the inclination angles of the displacement shafts 7 are changed. Each of the displacement shafts 7, 7 has a power roller 8,
8 is rotatably supported. These power rollers 8, 8 are sandwiched between the input side and output side disks 2, 4. In other words, the inner surfaces 2a and 4a of the input and output disks 2 and 4 facing each other are formed by rotating an arc around the pivot 5 around the input shaft 1 and the output shaft 3, respectively. Formed on the resulting concave surface,
The peripheral surfaces 8a, 8a of the power rollers 8, 8, which are formed as spherical convex surfaces, are in contact with the inner side surfaces 2a, 4a.

[0004] As for the question of the input shaft 1 and the input side disk 2,
A loading cam type pressing device 9 is provided, and the input side disk 2 is connected to the output side disk 4 by the pressing device 9.
Pressed toward. The pressing device 9 includes the input shaft 1
And a plurality of (for example, four) rollers 12 held by a holder 11. On one side surface (left side surface in FIGS. 8 and 9) of the cam plate 10, a cam surface 13 which is an uneven surface extending in the circumferential direction is formed, and an outer side surface of the input side disk 2 (right side in FIGS. 8 and 9). Surface), a similar cam surface 14 is formed, between which a plurality of rollers 12 are rotatably supported about a radial axis with respect to the center of the input shaft 1. .

In the toroidal type continuously variable transmission configured as described above, when the cam plate 10 rotates with the rotation of the input shaft 1, the cam surface 13 causes the plurality of rollers 12 to move to the outer surface of the input side disk 2. To the cam surface 14. As a result, the input side disk 2 is pressed by the two power rollers 8, 8, and based on the pressing force between the pair of cam surfaces 13, 14 and the plurality of mouth rollers 12.
Rotates. Then, the rotation of the input side disk 2 is
The power is transmitted to the output-side disk 4 via the two power ports 8, 8, and the output shaft 3 fixed to the output-side disk 4 rotates.

When the rotational speed ratio (speed change ratio) between the input shaft 1 and the output shaft 3 is changed, and when deceleration is performed between the input shaft 1 and the output shaft 3, the pivots 5, 5 As shown in FIG. 8, each of the trunnions 6 is swung so that the peripheral surfaces 8 a of the power rollers 8 are closer to the center of the inner side surface 2 a of the input side disk 2 and the output side disk 4. Each of the displacement shafts 7 is inclined so as to abut against the outer peripheral portion of the inner side surface 4a. On the other hand, when increasing speed,
Each trunnion 6, 6 is swung about the pivot 5, 5, and as shown in FIG.
The displacement shafts 7, 7 are inclined so that a, 8a abut on the outer peripheral portion of the inner surface 2a of the input disk 2 and the central portion of the inner surface 4a of the output disk 4, respectively. If the inclination angle of each of the displacement shafts 7 is in the middle between FIGS. 8 and 9, an intermediate speed ratio can be obtained between the input shaft 1 and the output shaft 3.

FIGS. 10 and 11 show a more specific toroidal type continuously variable transmission. In this toroidal-type continuously variable transmission, the input side disk 2 and the output side disk 4 are each provided with a needle bearing 1 on the outer peripheral portion of the input shaft 15.
It is supported in a rotating white space via 6 and 16. Further, the cam plate 10 is located at the end of the input shaft 15 (the left end in FIG. 10).
Is spline-engaged with the outer peripheral surface of the input side disk 2, and is prevented from moving in a direction away from the input side disk 2 by the flange portion 17. The cam plate 10 and the rollers 12, 12 constitute a loading cam type pressing device 9 for rotating the input disk 2 while pressing the input disk 2 toward the output disk 4 based on the rotation of the input shaft 15. are doing. An output gear 18 is connected to the output disk 4 by keys 19, 19, so that the output disk 4 and the output gear 18 rotate integrally. The output gear 18 and a gear (not shown) meshed with the output gear 18 constitute a power take-out means for taking out the rotation of the output side disk 4.

The pivots 5, 5 provided at both ends of the pair of trunnions 6, 6 are swingably and axially (front and back in FIG. 10, and left and right in FIG. 11) on the pair of support posts 20, 20, respectively. It is displaceably supported. The pair of support posts 20 and 20 are formed in a plate shape having sufficient rigidity, and circular holes 21 and 21 formed in the center portions of the support posts 20 and 20 are respectively formed on the inner surface of the casing 22 and the casing 22. By being externally fitted to support pins 24a, 24b fixed to the side surface of a cylinder case 23 provided therein, the support is provided inside the casing 22 so as to be free to swing and to be displaceable in the axial direction of each of the pivots 5, 5. Have been. Further, circular support holes 25 are formed at both ends of the support posts 20, respectively, and these support holes 25 are respectively provided at both ends of the trunnions 6. The pivots 5,5 are supported by radial needle bearings 27,27 with outer rings 26,26. With these configurations, each trunnion 6, 6
5 is supported in the casing 22 so as to be freely swingable around the center 5 and displaceable in the axial direction of each of the pivots 5.

[0009] Displacement shafts 7, 7 are supported in circular holes 40, 40 formed in the intermediate portions of the trunnions 6, 6, respectively. Each displacement shaft 7 includes a support shaft 28 and a pivot shaft 29 which are parallel and eccentric to each other. Each support shaft 2
8 is a radial needle bearing 30 inside each circular hole 40.
And is swingably supported via the. A power roller 8 is supported on the outer peripheral portion of each pivot shaft portion 29 in a rotating white space via a radial needle bearing 31.

The pair of displacement shafts 7, 7 are arranged so as to be located symmetrically with respect to the input shaft 15 (a position on the opposite side by 180 degrees). In addition, the respective pivot shaft portions 29, 29 of the respective displacement shafts 7, 7 are connected to the respective support shaft portions 28, 2
The direction eccentric with respect to 8 is the same direction (left and right opposite directions in FIG. 11) with respect to the rotation direction of the input side and output side disks 2 and 4. The axial direction of each pivot shaft portion 29, 29 is a direction substantially orthogonal to the axial direction of the input shaft 15 (the left-right direction in FIG. 10 and the front and back direction in FIG. 11). Therefore, each power roller 8, 8
The input shaft 15 is supported while allowing a slight displacement in the axial direction. As a result, even if the respective power rollers 8, 8 are slightly displaced in the axial direction of the input shaft 15 due to variations in the dimensional accuracy of the constituent parts, elastic deformation during power transmission, or the like, this displacement is reduced. It can be absorbed and no excessive force is applied to each component.

Further, between the outer surface of each power roller 8 and the inner surface of the intermediate portion of each trunnion 6,
A thrust rolling bearing 32, 32 such as a thrust ball bearing, and a thrust bearing 34, 34 such as a thrust needle bearing for supporting a thrust load applied to the outer races 33, 33, which will be described later, in order from the outer surface side of the power rollers 8, 8. Is provided. Of these, the thrust rolling bearings 32, 32
The rotation of each of the power rollers 8, 8 is allowed while supporting the load in the thrust direction applied to each of the power rollers 8, 8. Further, each thrust bearing 34, 34 is connected to the outer ring 3 of each thrust rolling bearing 32, 32 from each power roller 8, 8.
The pivot shafts 29, 29 and the outer rings 33, 33 are supported by the support shafts 28, 28 while supporting the thrust load applied to the shafts 3, 33.
Swinging around the center.

Further, one end of each trunnion 6, 6 (FIG. 1)
1, the driving rods 35, 3
The driving piston 36 is fixed to the outer peripheral surface of the intermediate portion of each of the driving rods 35. Each of the drive pistons 36, 36 is oil-tightly fitted in a drive cylinder 37, 37 provided in the cylinder case 23, respectively. Further, between the support wall 38 provided in the casing 22 and the input shaft 15, a pair of rolling bearings 39 is provided, and the input shaft 15 is rotatably supported in the casing 22.

In 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. The rotation of the input disk 2 is transmitted to the output disk 4 via the pair of power rollers 8, 8, and the rotation of the output disk 4 is extracted from the output gear 18. When changing the rotation speed ratio between the input shaft 15 and the output gear 18, the pair of drive pistons 36, 36 are displaced in opposite directions. Then, each of these drive pistons 36,
The pair of trunnions 6, 6 are displaced in opposite directions with the displacement of. For example, in FIG. 11, the lower power roller 8 is displaced to the right in FIG. 11 and the upper power roller 8 is displaced to the left in FIG. as a result,
The peripheral surfaces 8a, 8a of these power rollers 8, 8 and the inner surfaces 2a, 4a of the input side disk 2 and the output side disk 4
The direction of the tangential force acting on the abutting portion changes. Then, with the change in the direction of the force, each trunnion 6, 6 is pivotally supported by the support post 20, 20,
10 around the center 5 in the opposite directions. As a result, as shown in FIGS. 8 and 9 described above,
The peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner surfaces 2
a, 4a, and the rotational speed ratio between the input shaft 15 and the output gear 18 changes.

When the power rollers 8, 8 are displaced in the axial direction of the input shaft 15 as a result of elastic deformation of the components at the time of power transmission, each of the displacement shafts pivotally supporting the power rollers 8, 8 is displaced. 7, 7 slightly swing about the respective support shafts 28, 28. As a result of this swing, the outer surfaces of the outer rings 33, 33 of the thrust rolling bearings 32, 32 and the inner surfaces of the trunnions 6, 6 are relatively displaced. Since the thrust bearings 34, 34 exist between the outer surface and the inner surface, the force required for the relative displacement is small. Therefore, as described above, the force for changing the inclination angle of each of the displacement shafts 7 can be small.

In the case of a toroidal type continuously variable transmission constructed and operated as described above, each of the trunnions 6 and 6 and each of the trunnions 6 and 6 such as a radial needle bearing 31 and a thrust rolling bearing 32 for supporting the power rollers 8 and 8 are provided. It is necessary to feed the lubricating oil to each bearing part existing in the combination part of the displacement shafts 7, 7 and the respective power rollers 8, 8. because,
Power rollers 8, 8 during operation of the toroidal type continuously variable transmission
Rotates at high speed while receiving a large load. Therefore,
Radial needle bearing 31 and thrust rolling bearing 3
In order to ensure the durability of the bearings such as
This is because it is necessary to feed a sufficient amount of lubricating oil into each bearing portion including the first and second bearings.

For this purpose, in the case of the structure shown in FIGS. 10 and 11, continuous lubrication holes 38a and 38b are formed inside the trunnions 6 and 6, respectively. Then, the hydraulic oil present in each of the drive cylinders 37, 37 is supplied from the low pressure chamber side of each of the drive cylinders 37, 37 to oil supply holes 38a, 38.
The lubricating oil is fed into b. The supplied lubricating oil is discharged from the downstream end of the oil supply hole 38b and is fed between the inner surface of the trunnion 6 and the outer surface of the outer ring 33 of the thrust rolling bearing 32.

A part of the lubricating oil sent between the inner surface of the trunnion 6 and the outer surface of the outer ring of the thrust rolling bearing 32 is, as shown in FIG.
9 and is discharged from the downstream ends of the branch nozzle holes 73a and 73b branched from the oil supply hole 73 and sent to the inner diameter sides of the thrust rolling bearing 32 and the radial needle bearing 31, respectively. .

The thrust rolling bearing (thrust ball bearing) 32 includes a power roller 8 as an inner ring,
A plurality of rolling elements (balls) 32a, and these rolling elements 32a
And the outer ring 33. The inner raceway of the thrust rolling bearing 32 is
An outer raceway is formed on the outer surface of the power roller 8, and an outer raceway is formed on the inner surface of the outer race 33.

As the retainer 61, a retainer described in JP-A-7-174146 is conventionally known. As shown in FIG. 13, the retainer 61 is provided with a plurality of pockets 62 at equal intervals in the circumferential direction in a main body 63 having an annular plate shape.
Are formed, and the rolling elements 32a are held in the respective pockets 62. The main body 63 has oil supply holes 64 formed between its outer peripheral surface and the inner peripheral surface of each pocket 62. Each of these oil supply holes 64 has a tapered hole whose inner end is opened on the inner peripheral surface of the pocket 62 and whose outer end is opened on the outer peripheral surface of the main body 63, and whose inner diameter gradually decreases from the outer end to the inner end. Have been. In addition, each oil supply hole 64
Is inclined by an angle φ with respect to the radial direction of the main body 63. The inclination direction is such that each of the oil supply holes 64,
The outer end of the opening 64 opens forward in the rotation direction.

Further, as shown in FIG.
A holder 61a as another example is described. In the retainer 61a, an oil supply hole 65 is formed between the inner peripheral surface of each pocket 62 and the inner peripheral surface of the main body 63a in the radial direction of the main body 63a. In the retainer 61a, during operation of the thrust rolling bearing, the lubricating oil present inside the main body 63a in the radial direction is sucked into each oil supply hole 65 and fed into each pocket 62 based on the centrifugal force accompanying rotation. It is.
The publication also describes that the oil supply hole 64 and the oil supply hole 65 are mainly formed in combination.

[0021]

However, using the conventional retainers 61 and 61a has the following problems.
That is, in the retainer 61 in which the oil supply hole 64 is formed on the outer peripheral side of the pocket 62, a centrifugal force is generated with the rotation of the retainer 61. Therefore, a sufficient amount of lubricating oil is supplied to each pocket against the centrifugal force. It is difficult to send to 62. on the other hand,
In the retainer 61a in which the oil supply hole 65 is formed on the inner peripheral side of the pocket 62, the processing for forming the oil supply hole 65 is difficult. Further, in the retainer 61 and the retainer 61a,
When the lubricating oil is supplied to the lubrication holes 64 and 65, the lubricating oil is not circulated and accumulates without lubricating oil because the lubricating oil discharge port is not provided. Therefore, stirring resistance increases and dynamic torque increases. As a result, the efficiency may be reduced. Further, in the retainer in which the oil supply hole 64 and the oil supply hole 65 are mainly formed, there is a problem that the processing of the oil supply hole 65 on the inner peripheral side is difficult.

The present invention has been made in view of the above circumstances, and relates to a cage for a thrust rolling bearing, which facilitates machining of an oil supply hole of the cage and does not cause a reduction in efficiency of a transmission. It is another object of the present invention to provide a toroidal-type continuously variable transmission that can reliably supply lubricating oil to a pocket in which a rolling element is stored through an oil supply hole.

[0023]

According to a first aspect of the present invention, there is provided a toroidal-type continuously variable transmission having an input shaft rotatably supported and an input side rotatable with the input shaft. A disk, an output disk arranged in the same central axis as the input disk, and supported rotatably with respect to the input disk;
It is arranged in the middle of the two discs in the axial direction of the two discs on the output side, in a direction perpendicular to the axial direction of the two discs, and at a twisted position with respect to the central axis of the two discs, and swings at this position. A plurality of trunnions, a plurality of power rollers which are supported in rotation white on a displacement shaft supported by each of the trunnions, and are sandwiched between both input side and output side disks, and an outer surface of each of these power rollers. A thrust rolling bearing provided between the inner surface of each of the trunnions and supporting the thrust load of the power roller, and allowing rotation of the power roller, an input side;
The inner surfaces of both the output side disks facing each other are concave surfaces having a circular cross section, the peripheral surfaces of the power rollers are spherical convex surfaces, and the peripheral surface and the inner surface are brought into contact with each other. In the toroidal type continuously variable transmission, the thrust rolling bearing has a plurality of pockets for accommodating rolling elements formed in a circumferential direction of an annular main body, and an oil supply hole for supplying lubricating oil to the pockets. In the toroidal-type continuously variable transmission including a retainer formed in the main body, the oil supply hole of the retainer is configured such that at least a part of the plurality of pockets is provided with the pocket. It is characterized by being formed in a straight line so as to penetrate from the inner peripheral surface to the outer peripheral surface of the main body.

According to the first aspect of the present invention, since the oil supply hole of the retainer is formed in a straight line penetrating from the inner peripheral surface to the outer peripheral surface of the main body across the pocket, the processing of the oil supply hole is very difficult. Since it becomes easy, the processing cost can be reduced. Further, since the lubricating oil supplied from the inner opening of the oil supply hole is discharged from the outer opening along with the centrifugal force of the cage, there is no possibility that the lubricating oil remains inside the thrust rolling bearing and increases the stirring resistance. Therefore, the transmission efficiency does not decrease. In particular, the effect is great when traction oil having high clay is used as lubricating oil. Further, since the lubricating oil circulates without remaining inside the thrust rolling shaft, there is an effect that the heat of the bearing is released.

According to a second aspect of the present invention, in the toroidal-type continuously variable transmission according to the first aspect, an inner opening of the oil supply hole of the retainer has a lubricating oil supply port formed on the displacement shaft. , And is arranged to face.

According to the second aspect of the present invention, since the inner opening of the oil supply hole is arranged to face the lubricating oil supply port formed on the displacement shaft, the lubricating oil ejected from the supply port of the displacement shaft is provided. Surely enters the oil supply hole from the inside opening of the oil supply hole, so that the lubricating oil can be reliably sent to the pocket.
Therefore, lubricating oil can be fed to the rolling surface of the rolling element, and wear and seizure of the thrust rolling bearing can be prevented.

According to a third aspect of the invention, there is provided a toroidal-type continuously variable transmission according to the second aspect, wherein an inner opening of the oil supply hole of the retainer is formed in a circumferential direction formed on an inner peripheral surface of the main body. It is characterized by being arranged in an annular recessed groove along.

According to the third aspect of the present invention, the lubricating oil ejected from the supply port of the displacement shaft surely enters the recess groove, and enters the lubrication hole from the inside opening of the lubrication hole. Can be sent to your pocket.

[0029]

Embodiments of the present invention will be described below with reference to the drawings. In each drawing, the same components as those in FIGS. 10 to 13 are denoted by the same reference numerals, and description thereof will be simplified. 1 to 3 are diagrams according to a first embodiment of the present invention, and FIG. 1 is a cross-sectional view and a diagram illustrating a portion of a thrust rolling bearing of a toroidal-type continuously variable transmission according to the embodiment. 2 is a plan view of the cage, and FIG. 3 is a cross-sectional view along the line ZZ in FIG.

The thrust rolling bearing (thrust ball bearing) 32A of the present embodiment has a power roller 8 as an inner ring.
And a plurality of rolling elements (balls) 32a and these rolling elements 3
It comprises a retainer 81 for rotatably holding 2 a and an outer ring 33. The inner raceway of the thrust rolling bearing 32A is on the outer surface of the power roller 8, and the outer raceway is the outer race 33.
Are formed on the inner surfaces of the respective members.

In the retainer 81, a plurality of pockets 62 are formed at equal intervals in the circumferential direction in a main body 83 of an annular plate, and the rolling elements 32a are held in each pocket 62. In the main body 83, across the center of each pocket 62,
A straight oil supply hole 84 is formed from the inner peripheral surface to the outer peripheral surface of the main body 83 in a radial direction of the main body 83. Oil supply hole 8
The inside opening 4 is disposed at a position facing the supply port at the downstream end of the branch nozzle hole 73a formed in the pivot shaft 29 of the displacement shaft 7 described above. An annular recess groove 86 extending in the circumferential direction is formed at the center of the inner peripheral surface of the main body 83, and an inside opening of the oil supply hole 84 is arranged in the recess groove 86. Therefore, the opening side of the recess groove 86 faces the supply port at the downstream end of the branch nozzle hole 73a. The cross section of the recess groove 86 along the thickness direction of the main body 83 is formed in an arc shape (a semicircular shape in this example).

In the toroidal type continuously variable transmission configured as described above, at the time of operation, the lubricating oil squirted from the supply port of the branch nozzle hole 73a enters the recess groove 86, and further from the inner opening of the oil supply hole 84. The oil enters the oil supply hole 84, is supplied into the pocket 62 through the oil supply hole 84, and is discharged from the outer opening of the oil supply hole 84 through the oil supply hole 84 outside the pocket 62 by the centrifugal force of the retainer 81. .

In this toroidal type continuously variable transmission,
Since the oil supply hole 84 of the retainer 81 is formed in the main body 83 by a straight through hole crossing the pocket 62, the processing becomes very easy, so that the processing cost can be reduced. Further, since the lubricating oil supplied from the inner opening of the oil supply hole 84 is discharged from the outer opening along with the centrifugal force of the retainer 81, the lubricating oil may remain inside the thrust rolling bearing 32A and increase the stirring resistance. As a result, the efficiency of the transmission is not reduced. In a toroidal-type continuously variable transmission, the thrust rolling bearing 32A is normally lubricated with traction oil, unlike a general bearing. Since the traction oil enters between the peripheral surface 8a of the power roller 8 and the inner surfaces 2a, 4a of the input-side disk 2 and the output-side disk 4, the traction oil is high in clay. For this reason, stirring resistance is likely to occur, and thus the oil supply hole 84 having the above structure is particularly effective. Further, in the thrust rolling bearing 32A, since the power is transmitted by the power roller 8 as the inner ring, heat is easily generated. However, as described above, since the lubricating oil circulates without remaining in the thrust rolling bearing 32A, This has the effect of releasing the heat of the bearing 32A.
Further, the inside opening of the oil supply hole 84 is arranged at a position facing the supply port at the downstream end of the branch nozzle hole 73a.
An annular recess groove 86 is formed on the inner peripheral surface of the nozzle 3, and the inside opening of the oil supply hole 84 is arranged in the recess groove 86, so that the lubricating oil ejected from the supply port of the branch nozzle hole 73 a can be reliably recessed. Since the lubricating oil enters the groove 86 and enters the lubricating hole 84 from the inside opening of the lubricating hole 84, the lubricating oil can be reliably sent to the pocket 62, and therefore, the lubricating oil can be sent to the rolling surface of the rolling element 32a. it can. This allows
Wear and seizure of the thrust rolling bearing 32A can be prevented.

FIGS. 4, 5, and 6 are views showing modified examples of the first embodiment, and are partial cross-sectional views of the retainer. These retainers differ from the first embodiment only in the shape of the recess grooves. That is, in the retainer 81a of FIG. 4, the recess groove 86a is formed such that the cross-sectional shape along the thickness direction of the main body 83a is a part of an ellipse (a semi-ellipse in this example). Also, the retainer 81 of FIG.
In b, the recess groove 86b has a rectangular cross section along the thickness direction of the main body 83b. Further, in the retainer 81c of FIG. 6, the recess groove 86c is formed such that the cross-sectional shape along the thickness direction of the main body 83c is rounded at both corners of the square, thereby forming the recess groove 86b of FIG. In contrast, stress concentration is less likely to occur at both corners of the groove.

FIG. 7 is a plan view of a cage according to the second embodiment of the present invention. In the retainer 81d of the present embodiment, a straight oil supply hole 84a penetrating from the inner peripheral surface to the outer peripheral surface of the main body 83d across the center of each pocket 62,
The main body 83d is formed to be inclined at an angle φ with respect to the radial direction. Even with this toroidal type continuously variable transmission, the first
The same effect as that of the embodiment can be obtained.

When the thrust rolling bearing according to the present invention is formed, the oil supply holes 84 and 84a do not necessarily need to be provided in all the pockets 62. If the oil supply holes 84 and 84a are provided only in some of the pockets 62, lubricating oil is supplied to the inner ring raceway and the outer ring raceway through the rolling elements 32a held in the part pockets 62, and the oil supply holes 8 are formed.
Rolling element 32 in pocket 62 not provided with 4, 84a
The lubrication between the rolling surface a and both raceway surfaces is also performed. Further, the recess grooves 86, 86a, 86b, 86c are not necessarily provided. Further, as the thrust rolling bearing, a thrust taper roller bearing can be used in addition to the thrust ball bearing.

[0037]

As described above, according to the toroidal type transmission of the present invention, the lubrication hole of the retainer of the thrust rolling bearing can be easily formed and the efficiency of the transmission is not reduced. The lubricating oil can be reliably supplied to the pocket in which the rolling elements are stored through the oil supply hole.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a portion of a thrust rolling bearing of a toroidal type continuously variable transmission according to a first embodiment of the present invention.

FIG. 2 is a plan view showing the retainer according to the first embodiment.

FIG. 3 is a sectional view taken along line ZZ of FIG. 2;

FIG. 4 is a diagram showing a modification of the first embodiment,
It is a fragmentary sectional view of a maintenance machine.

FIG. 5 is a partial sectional view of the retainer.

FIG. 6 is a partial sectional view of the retainer.

FIG. 7 is a plan view showing a retainer according to a second embodiment.

FIG. 8 is a side view showing a basic configuration of the toroidal-type continuously variable transmission in a state of minimum deceleration.

FIG. 9 is a side view similarly showing a state at the time of maximum deceleration.

FIG. 10 is a sectional view of a main part showing an example of a specific structure of a toroidal type continuously variable transmission.

FIG. 11 is a sectional view taken along line XX of FIG. 10;

FIG. 12 is a cross-sectional view showing a part of a conventional thrust rolling bearing.

FIG. 13 is a plan view showing a conventional cage.

FIG. 14 is a plan view showing another conventional cage.

[Explanation of symbols]

 7 Displacement shaft 32A Thrust rolling bearing 32a Rolling element 62 Pocket 73a Branch nozzle hole 81, 81a, 81b, 81c, 81d Cage 83, 83a, 83b, 83c, 83d Main body 84, 84a Oil supply hole 86, 86a, 86b, 86c Recess groove

 ────────────────────────────────────────────────── ─── Continued on the front page F term (reference) 3J051 AA03 BA03 BD02 BE09 CA05 CB07 ED08 FA02 3J063 AA02 AB33 AC03 BA11 CA10 CD02 XD03 XD42 XD62 3J101 AA02 AA32 AA42 AA53 AA62 AA73 BA35 BA44 CA11 FA32 FA32 FA32 FA32 FA32 FA32 FA32 FA32 FA32 FA32 FA32

Claims (3)

[Claims] An input shaft rotatably supported, an input disk rotatable with the input shaft, a central axis arranged with the input disk and rotating with respect to the input disk. A freely supported output side disk and an intermediate portion between the input side and the output side disks with respect to the axial direction of the input side and the output side disks, in a direction perpendicular to the axial direction of the both disks and at the center axis of the both disks. In contrast, a plurality of trunnions arranged at a twist position and swinging at the position, and a plurality of trunnions supported by the displacement shafts supported by the respective trunnions in a rotating white space and sandwiched between the input side and the output side disks. Power rollers, and provided between the outer surface of each power roller and the inner surface of each trunnion to support the thrust load of the power roller. With a thrust rolling bearing that allows rotation, the inner surfaces of the input side and the output side disks facing each other are each concave in cross section, and the peripheral surface of each power roller is a spherical convex surface. A toroidal-type continuously variable transmission in which the peripheral surface and the inner surface are in contact with each other, wherein the thrust rolling bearing has a plurality of pockets for accommodating rolling elements formed in a circumferential direction of an annular main body. And a toroidal-type continuously variable transmission including a retainer in which an oil supply hole for supplying lubricating oil to the pocket is formed in the main body, wherein the oil supply hole of the retainer is provided in the plurality of pockets. A toroidal-type continuously variable transmission, wherein at least some of the pockets are formed in a straight line so as to penetrate from the inner peripheral surface to the outer peripheral surface of the main body across the pockets. 2. An inner opening of the oil supply hole of the retainer,
The toroidal-type continuously variable transmission according to claim 1, wherein the toroidal-type continuously variable transmission is arranged to face a lubricating oil supply port formed on the displacement shaft. 3. An inner opening of the oil supply hole of the retainer,
The toroidal-type continuously variable transmission according to claim 2, wherein the toroidal-type continuously variable transmission is disposed in an annular recess groove formed in an inner peripheral surface of the main body and extending along a circumferential direction.