JPH10141462A - Troidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the durability of a ball bearing by supplying oil from a cage of the ball bearing which supports a power roller into a rolling groove smoothly. SOLUTION: This troidal type continuously variable transmission is provided with a power roller 22 which is nipped and held by input and output discs and is inserted into an eccentric shaft, an outer ring 4 arranged on a trunnion side which opposes to the power roller 22 through a plurality of ball bearings 3, rolling grooves 5, 23 formed in the outer ring 4 and the power roller 22, respectively, annular cages 7a, 7b which specify a relative position of the plurality of ball bearings 3, and an oil supply port which supplies oil to the ball bearings 3 from an eccentric shaft side, and the cage 7a on an inner peripheral side forms inclined faces 70, 71 which guide oil toward the rolling grooves 5, 23 of the outer ring 4 and the power roller 22.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improved bearing for supporting a power roller in a toroidal type continuously variable transmission used for a vehicle or the like.

[0002]

2. Description of the Related Art As a structure for supporting a power roller of a toroidal-type continuously variable transmission, one disclosed in Japanese Patent Application Laid-Open No. H8-4868 is known.

[0003] To explain this, FIG. 8 and FIG.
A pair of toroidal input disk 18 and output disk 20 are arranged coaxially with the input shaft 14, and the tilt angles of the pair of power rollers 22, 22 pressed against the input disk 18 and output disk 20 ( 1 shows a single-cavity toroidal-type continuously variable transmission that can set an arbitrary speed ratio in a stepless manner by changing an inclination angle.

A disc spring 70 provided on the base end side of the input shaft 14
And the pressure generated by the cam roller 79 provided on the left end side of the input shaft 14, the input disk 18 and the output disk 2
The power roller 22 sandwiched between the output disk 20 transmits torque from the input disk 18 to the output disk 20 and drives an output shaft (not shown) via an output gear 26 that rotates integrally with the output disk 20.

The power roller 22 is supported on an eccentric shaft 2 projecting toward an input shaft 14 from a trunnion 1 which can be displaced in a penetrating direction of the drawing and swings around an axis in the penetrating direction. Then, the gear ratio is changed by changing the inclination angle while rotating according to the axial displacement of the trunnion 1 and changing the contact radius between the input disk 18 and the output disk 20. The eccentric shaft 2 is constituted by a predetermined eccentric shaft in order to incline the power roller 22 in accordance with the displacement of the trunnion 1 in the penetrating direction of the drawing.

Since the power roller 22 needs to rotate at a high speed while receiving a large pressure (for example, several tons) due to the holding of the input / output disk, the thrust of the eccentric shaft 2 between the trunnion 1 and the power roller 22 is required. The thrust load of the eccentric shaft 2 accompanying the holding and pressing is supported by interposing a ball bearing 3 that supports the load in the directional direction.

[0007] As shown in FIG.
Is disposed between the outer ring 4 provided on the trunnion 1 and the power roller 22, and has an annular rolling groove 5 formed on the outer ring 4, and an inner ring side facing the rolling groove 5. A plurality of ball bearings 3 are sandwiched between annular rolling grooves 23 formed on a power roller 22 constituting the rolling rollers 5 and 2.
Revolves around the eccentric shaft 2 along 3.

In such a ball bearing 3, the force and speed acting on each ball bearing 3 differ depending on the manufacturing accuracy of the balls and the rolling grooves 5, 23 or the unevenness of the applied load.

Therefore, the ball bearings 3 are engaged at the inner circumference and the outer circumference (the side facing the eccentric shaft 2 is the inner circumference, and the opposite side is the outer circumference).
Annular retainers 17a, 17b for defining the relative positions of each other
Are arranged coaxially with the eccentric shaft 2 (the revolving shaft of the ball), and the uneven force acting on each ball bearing 3 is dispersed and supported by the retainers 17a and 17b in which substantially plate-shaped members are formed in an annular shape. Thus, the ball bearing 3 is correctly rotated.

Note that the roller bearing 16 interposed between the power roller 22 and the eccentric shaft 2 is
In the radial direction.

As described above, since a large thrust force is applied to the power roller 22, the oil supply port 6 for injecting oil from the side surface of the eccentric shaft 2 toward the inner periphery of the ball bearing 3.
To lubricate and cool the ball bearing 3 and the rolling grooves 5 and 23.

Japanese Patent Publication No. 38-17507 discloses a method for smoothly lubricating such a bearing.

[0013]

However, in the toroidal type continuously variable transmission as described above, the retainers 17a and 17b also rotate about the eccentric shaft 2 in accordance with the rolling of the ball bearing 3, and the eccentric shaft 2 As shown in FIG. 9, the oil supplied from the oil supply port 6 from the upper and lower ends of the retainer 17 a on the inner peripheral side formed of a substantially plate-like member and the gap between the power roller 22 and the outer ring 4 Bearing 3 and rolling groove 5,
23, but flows out from the gap between the outer retainer 17b, the power roller 22, and the outer ring 4 to the outside due to the centrifugal force as shown by the arrow in the figure, and the rolling grooves 5, 23 which receive a high load. Since sufficient oil is not supplied to the bearings, the lubrication and cooling of the rolling grooves 5 and 23 cannot be sufficiently performed, and the durability of the ball bearing 3 and the rolling grooves 5 and 23 deteriorates. Even if the retainer is provided with an oil supply hole as in the prior art, the rolling element (ball bearing)
However, there is a problem that the oil supply to the rolling grooves is insufficient as described above.

SUMMARY OF THE INVENTION The present invention has been made in view of the above problems, and improves the durability of a ball bearing by smoothly supplying oil from a cage of a ball bearing supporting a power roller to a rolling groove. The purpose is to:

[0015]

According to a first aspect of the present invention, there is provided an input disk connected to an input shaft, an output disk connected to an output shaft, and a rotating shaft provided at a predetermined position facing the input / output disk. A protruding trunnion, and a power roller that is sandwiched between toroidal grooves formed on opposing surfaces of the input / output disk and inserted through the rotating shaft,
An outer ring disposed on the trunnion side facing the power roller via a plurality of rolling elements, a rolling groove formed on each of the outer ring and the power roller to guide the rolling element, and An annular retainer that defines a relative position, and a toroidal-type continuously variable transmission that includes an oil supply unit that supplies oil from the rotation shaft side to the rolling elements,
A guide surface that guides oil supplied from the rotating shaft toward at least one of the rolling grooves formed in the outer ring or the power roller on an inner peripheral side portion of the annular retainer. Form.

According to a second aspect of the present invention, in the first aspect, the guide surface is formed by inclining the thickness of the annular retainer so as to increase from the inner circumference to the outer circumference.

According to a third aspect of the present invention, there is provided an input disk coupled to an input shaft, an output disk coupled to an output shaft, and a trunnion having a rotating shaft protruding at a predetermined position facing the input / output disk. While being sandwiched between toroidal grooves formed on the opposing surfaces of the input / output disk,
A power roller inserted through the rotating shaft, an outer ring disposed on a trunnion side facing the power roller via a plurality of rolling elements, and rolling elements formed on the outer ring and the power roller to guide the rolling elements. A toroidal-type continuously variable transmission including a dynamic groove, an annular retainer that defines a relative position between the plurality of rolling elements, and an oil supply unit that supplies oil from the rotating shaft side to the rolling elements. On the inner peripheral side portion of the annular retainer, a notch formed substantially in the circumferential direction is formed, and the notch is formed on the outer ring or the power roller in a direction opposed to the revolving direction of the rolling element. The oil supplied from the rotating shaft is guided toward at least one of the rolling grooves.

In a fourth aspect based on the third aspect, the notch is formed in accordance with the forward and reverse directions of the retainer.

[0019]

Accordingly, in the first invention, the oil supplied from the oil supply means is guided in the radial direction from the rotating shaft side to the rolling groove by the guide surface formed on the inner peripheral side of the annular cage. It can flow in, can reliably lubricate and cool the inner circumference of the rolling groove that comes into contact with the rolling element, and can improve the durability of the bearing of the power roller that receives a large thrust load in the axial direction of the rotating shaft. It is possible to greatly improve compared to the conventional example.

According to a second aspect of the present invention, the annular retainer has an inclined guide surface whose thickness increases from the inner periphery toward the outer periphery, and is supplied from the oil supply means on the rotating shaft side to the guide surface. Oil is guided to the rolling grooves in the radial direction by the inclination of the guide surface, and the inner circumference of the rolling grooves that come into contact with the rolling elements can be reliably lubricated and cooled, and the durability of the power roller bearings is improved. Can be greatly improved as compared with the conventional example.

According to a third aspect of the present invention, the notch provided in the circumferential direction on the inner peripheral side of the annular retainer is supplied from the inner peripheral rotating shaft side in a direction opposite to the revolving direction of the rolling element. Since the oil is guided, the oil can be reliably and efficiently supplied between the rolling grooves and the rolling elements, and the lubrication and cooling of the rolling grooves and the rolling elements can be performed more efficiently. Thus, the durability of the toroidal-type continuously variable transmission can be improved.

According to the fourth aspect of the present invention, even if the annular cage rotates in either direction, the rolling grooves and the rolling elements can be surely lubricated, and therefore, stable regardless of the mounting direction of the cage. Lubrication and cooling performance can be ensured, and there is no distinction between the front and back sides of the cage, simplifying the work during the assembly process, preventing incorrect assembly, and ensuring the durability of the toroidal type continuously variable transmission. Performance and reliability can be improved.

[0023]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to the accompanying drawings.

FIGS. 1 and 2 show a case where the present invention is applied to the toroidal type continuously variable transmission shown in FIGS. 8 and 9 of the conventional example, and guides a plurality of ball bearings 3 as rolling elements. The cages 17a and 17b of the conventional example are replaced with the cage 7
The other parts are the same as those of the conventional example described above, and the same parts are denoted by the same reference numerals and description thereof will be omitted.

A retainer 7a having a substantially triangular cross section is engaged on the inner periphery of the ball bearing 3 as a rolling element, and a substantially plate-like retainer 7b is engaged on the outer periphery. The bearing 3 has a relative position defined by the retainers 7 a and 7 b, and rolls in the rolling groove 23 of the power roller 22 and the rolling groove 5 of the outer ring 4, and the eccentric shaft 2 (rotating shaft) applied to the power roller 22. ) Direction thrust force.

The retainer 7b for guiding the outer periphery of the ball bearing 3 is formed of an annular member having a substantially plate-shaped cross section, as in the conventional example. vessel 7a is unlike the conventional example, the inclined surfaces 70, each toward the apex 7x provided on the inner periphery of the rotary shaft O ₂ side of the power rollers 22 to the grooves 5 and 23 side is inclined at a predetermined angle θ , 71 and an annular member having an isosceles triangular cross section, and the thickness of the retainer 7a on the inner periphery gradually increases from the inner periphery to the outer periphery.

The vertex 7x of the holder 7a is, as shown in FIG.
The inclination angle θ of the inclined surfaces 70 and 71 serving as guide surfaces is arranged on a revolution radius r ₁ connecting the center of revolution O ₁ of the ball bearing 3 and the center of rotation O of the ball bearing 3. , That is, the center of revolution O ₁
And the inclination with respect to the line connecting the rotation center O. The rotation axis of the revolution shaft and the power rollers 22 of the ball bearing 3 is consistent with O _2.

The inclination angle θ is obtained by calculating the apex 7x and the outermost peripheral point 5b of the rolling groove 5 from the extension of the inclined surface 70 connecting the vertex 7x and the innermost peripheral point 5a of the rolling groove 5 of the outer ring 4. It is set to be placed between the connecting extension lines. Similarly, on the power roller 22 side as well, from the extension line (θ = θa) connecting the vertex 7x and the innermost peripheral point 23a of the rolling groove 23 of the power roller 22, the vertex 7x and the outermost peripheral point 23b of the rolling groove 23 are obtained. Are set between the extension lines (θ = θb) connecting.

The thickness of the cages 7a and 7b (Z in FIG. 2)
The length of the retainer 7a on the inner peripheral side is set smaller than the thickness of the retainer 7b on the outer peripheral side.

The operation will be described below.

When the ball bearing 3 rotates along the rolling grooves 5 and 23 with the rotation of the power roller 22, the retainers 7a and 7b rotate with the revolution of the ball bearing 3.

At the same time, as shown in FIG. 9, oil is injected from an oil supply port 6 as an oil supply means opened on the side surface of the eccentric shaft 2, and is supplied to a retainer 7 a facing the eccentric shaft 2. .

Here, since the retainer 7a has an isosceles triangular cross section, the oil supplied from the inner peripheral side flows toward the rolling groove 5 by the inclined surfaces 70 and 71 extending from the vertex 7x, and The flow toward the moving groove 23 is divided into two flows and moves toward the outer periphery.

The inclined surfaces 70 and 71 have a predetermined inclination angle θ with respect to the revolution radius r ₁ of the ball bearing 3.
And the inclination angle θ is set between the vertex 7x and the innermost peripheral points 5a, 23a of the rolling grooves 5, 23 to the outermost peripheral points 5b, 2b.
3b, the oil diverted by the retainer 7a flows along the inclination angle θ of the inclined surfaces 70, 71.
Each of the rolling grooves 5 and 23 can flow into the rolling grooves 5 and 23, and the inner circumferences of the rolling grooves 5 and 23 on which the ball bearing 3 rolls can be reliably lubricated and cooled. The durability of the bearing of the power roller 22 that receives a large thrust load can be greatly improved as compared with the conventional example.

In the above embodiment, the retainer 7a
Is an isosceles triangular cross section, and the inclination angles θ of the inclined surfaces 70 and 71 are set to be equal. However, the inclination angle θ of the inclined surfaces 70 and 71 is not limited to θ as described above.
The angle may be in the range of a to θb, and the inclined surface may be formed on only one of them.

Further, the position of the apex 7x of the cage 7a, is not limited on the revolution radius r ₁ of the ball bearing 3, it is suitably changed in accordance with the direction of injection position and the oil filler opening 6 it can.

Since the thickness of the cage 7a is set smaller than the thickness of the cage 7b on the outer circumference, the thickness of the cage 7a on the outer circumference is smaller than the gap between the outer ring 4 and the power roller 22 on the inner circumference. The gap between the retainer 7b, the outer ring 4 and the power roller 22 can be set relatively small, and the oil injected from the eccentric shaft 2 can be smoothly guided into the rolling grooves 5, 23, while the rolling grooves 5, It is possible to further reduce the outflow of oil from 23 to the outer periphery, and to further improve the lubrication and cooling performance of the ball bearing 3.

FIGS. 3 to 6 show a second embodiment in which the retainer 7a of the first embodiment is changed to a retainer 27a having a notch 8, and the other structure is the same as that of the first embodiment. This is the same as the embodiment.

The retainer 27 for guiding the inner peripheral side of the ball bearing 3 has a notch for guiding oil to an annular plate-shaped member instead of using the retainer 7a having a triangular cross section as in the first embodiment. 8 from the inner peripheral side surface 27a to the end surface 27.
c and 27b. The end surface 27b of the retainer 27 is an end surface facing the outer ring 4, and the end surface 27c is a surface facing the power roller 22.

The notch 8 is formed on the inner peripheral side surface 27 of the retainer 27.
a to the end face 27b or 27c so as to gradually expand to the outer peripheral side. Further, as shown in FIGS. Alternatively, an inclined surface similar to that of the first embodiment is provided so as to be guided to the rolling grooves 5 and 23 of the power roller 22.

The notches 8 are formed at predetermined intervals in the circumferential direction of the cage 27 so as to correspond to the respective ball bearings 3. As shown in FIG.
The holder 27 is disposed at a predetermined angle with respect to the rotation direction.

That is, it is inclined at a predetermined angle α in the tangential direction with respect to the revolution radius r ₁ of the ball bearing 3 on the front side in the rotation direction of the cage 27 with respect to the ball bearing 3 for supplying oil (see FIG. 3). ).

With the rotation of the power roller 22, the holder 7
a and 27 also rotate, so that the notch 8 provided corresponding to each ball bearing 3 allows the oil supply port 6 of the eccentric shaft 2 to be opened.
The rotational force of the retainer 27 is applied to the oil supplied from the oil supply device, and the oil is reliably supplied into the two rolling grooves 5 and 23 as shown by the broken line in FIG. Is supplied toward the front surface facing the revolving direction of the ball bearing 3, so that lubrication and cooling between the rolling grooves 5, 23 and the ball bearing 3 can be performed more efficiently, and the toroidal stepless The durability of the transmission can be improved.

FIG. 7 shows a third embodiment in which a notch 8 'for reverse rotation is added to the retainer 27 in addition to the notch 8 of the second embodiment. This is the same as the second embodiment.

The retainer 27 that guides the inner periphery of the ball bearing 3 is provided with a rotation when the retainer 27 rotates forward (counterclockwise in FIG.
At the time of UCW), notches 8 for supplying oil to the rolling grooves 5 and 23 and the front surface of the ball bearing 3 are formed at predetermined intervals in the circumferential direction. And a predetermined angle α in the tangential direction with respect to the revolution radius r ₁ of the ball bearing 3 on the side of the retainer 27 in the normal rotation direction.

On the other hand, when the retainer 27 rotates in the reverse direction (clockwise in the drawing = CW), the rolling grooves 5, 23 and the ball bearing 3
Notch 8 'for supplying oil to the front surface of the retainer 27 in the reverse direction of the ball bearing 3 for supplying oil,
And inclined by a predetermined angle -α tangentially with respect to the revolution radius r ₁ of the ball bearing 3.

Therefore, no matter which direction the cage 27 is rotated, the inner circumferences of the rolling grooves 5 and 23 and the ball bearing 3 can be reliably lubricated, and stable regardless of the mounting direction of the cage 27. Lubrication and cooling performance can be ensured.

In this way, since there is no longer any distinction between the front and back sides of the retainer 27, the operation during the assembly process is simplified,
Incorrect assembling can be prevented, and the durability and reliability of the toroidal-type continuously variable transmission can be improved.

[Brief description of the drawings]

FIG. 1 is a plan view illustrating a ball bearing and a retainer of a power roller according to an embodiment of the present invention.

FIG. 2 is a sectional view taken along the line AA of FIG. 1;

FIG. 3 is a plan view illustrating a ball bearing and a retainer of a power roller according to the second embodiment.

FIG. 4 is a sectional view taken along line BB of FIG. 3; Sectional drawing of the power roller and ball bearing which show the conventional example.

FIG. 5 is a cross-sectional view taken along the line CC of FIG. 3;

FIG. 6 is a perspective view of the retainer as viewed from the inner periphery.

FIG. 7 is a plan view illustrating a ball bearing and a retainer of a power roller according to the third embodiment.

FIG. 8 is a cross-sectional view of a toroidal-type continuously variable transmission showing a conventional example.

FIG. 9 is a sectional view of a main part of a power roller and a ball bearing showing a conventional example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Trunnion 2 Eccentric shaft 3 Ball bearing 4 Outer ring 5, 23 Rolling groove 6 Oil supply port 7a, 7b Retainer 8 Notch 18 Input disk 20 Output disk 22 Power roller 27 Retainer 70, 71 Inclined surface

Claims (4)

[Claims] An input disk coupled to an input shaft; an output disk coupled to an output shaft; a trunnion having a rotating shaft protruding at a predetermined position facing the input / output disk; A power roller inserted into the rotating shaft and an outer ring disposed on the trunnion side facing the power roller via a plurality of rolling elements, while being sandwiched by toroidal grooves formed respectively on the opposing surfaces of the power roller. A rolling groove formed in the outer ring and the power roller to guide the rolling element, an annular retainer that defines a relative position between the plurality of rolling elements, and a rolling element from the rotating shaft side to the rolling element. A toroidal-type continuously variable transmission provided with an oil supply means for supplying oil, wherein at least one of rolling grooves formed in the outer ring or the power roller is formed on an inner peripheral side portion of the annular retainer. A guide surface for guiding the oil supplied from the rotary shaft toward one of the rolling grooves is formed. 2. The toroidal stepless type according to claim 1, wherein the guide surface is formed by inclining the thickness of the annular retainer so as to increase from the inner circumference to the outer circumference. transmission. 3. An input disk coupled to an input shaft, an output disk coupled to an output shaft, a trunnion having a rotating shaft protruding at a predetermined position facing the input / output disk, and the input / output disk. A power roller inserted into the rotating shaft and an outer ring disposed on the trunnion side facing the power roller via a plurality of rolling elements, while being sandwiched by toroidal grooves formed respectively on the opposing surfaces of the power roller. A rolling groove formed in the outer ring and the power roller to guide the rolling element, an annular retainer that defines a relative position between the plurality of rolling elements, and a rolling element from the rotating shaft side to the rolling element. In a toroidal-type continuously variable transmission provided with an oil supply means for supplying oil, a notch disposed substantially in a circumferential direction is formed in an inner peripheral side portion of the annular retainer, and the notch is provided with a rolling element. Public A toroidal type in which oil supplied from the rotating shaft is guided toward at least one of the rolling grooves formed in the outer ring or the power roller in a direction opposite to the rolling direction. Continuously variable transmission. 4. The toroidal-type continuously variable transmission according to claim 3, wherein the notch is formed according to a forward rotation direction and a reverse rotation direction of the retainer, respectively.