JP2023182111A - Toroidal type continuously variable transmission - Google Patents

Abstract

To provide a toroidal type continuously variable transmission capable of suppressing generation of a high-stress portion in a disc to prevent fatigue failure, without shortage of an oil film on a shaft side.SOLUTION: An oil chamber 50 is provided between an outer diameter surface of an output shaft 1A and an inner diameter surface of an input side disc 2; a bearing 70 is provided in the oil chamber 50; fitting grooves 1g, 1g extending in a circumferential direction of the output shaft 1A are provided on the outer diameter surface of the output shaft 1A so as to be spaced apart in an axial direction; an axial end of the oil chamber 50 is formed in the fitting groove 1g; and a retaining ring 53 is fitted to the fitting groove to restrict movement of an oil chamber forming member 51 in the axial direction against the oil pressure of the oil chamber 50 in contact with the inner diameter surface of the input side disc 2.SELECTED DRAWING: Figure 3

Description

The present invention relates to a toroidal continuously variable transmission that can be used in generators of automobiles, aircraft, transmissions of various industrial machines, and the like.

For example, a double-cavity toroidal continuously variable transmission used as an automobile transmission is configured as shown in FIGS. 6 and 7. As shown in FIG. 6, the input shaft 1 is rotatably supported inside the casing 49, and on the outer periphery of the input shaft 1 are two input side disks 2, 2, two output side disks 3, 3 is attached. Further, an output gear (transmission gear) 4 is rotatably supported on the outer periphery of the intermediate portion of the input shaft 1. Output side disks 3, 3 are connected to cylindrical flanges (sleeves) 4a, 4a provided at the center of the output gear 4 by spline connection.
The input shaft 1 is rotationally driven by a drive shaft 22 via a loading cam type pressing device 12 provided between an input side disk 2 and a cam plate (loading cam) 7 located on the left side in FIG. It looks like this. Further, the output gear 4 is supported within a casing 49 via a partition wall 13 formed by coupling two members, and thus can rotate around the axis O of the input shaft 1 while also being able to rotate around the axis O of the input shaft 1. directional displacement is prevented.

The output side disks 3, 3 are rotatably supported around the axis O of the input shaft 1 by needle bearings 5, 5 interposed between the output side disks 3, 3 and the input shaft 1. In addition, the input side disk 2 on the left side in FIG. 6 is supported by the input shaft 1 via a ball spline 6, and the input side disk 2 on the right side in FIG. 6 is spline-coupled to the input shaft 1. The disk 2 is adapted to rotate together with the input shaft 1. Further, between the inner surfaces (concave surfaces; also referred to as traction surfaces) 2a, 2a of the input side disks 2, 2 and the inner surfaces (concave surfaces; also referred to as traction surfaces) 3a, 3a of the output disks 3, 3, there is a power roller. 11 (see FIG. 7) is rotatably held.

A stepped portion 2b is provided on the inner circumferential surface 2c of the input side disk 2 located on the right side in FIG. 6, and a stepped portion 1b provided on the outer circumferential surface 1a of the input shaft 1 abuts against this stepped portion 2b. At the same time, the back surface (right surface in FIG. 6) of the input side disk 2 is abutted against a loading nut 9 screwed into a threaded portion formed on the outer peripheral surface of the input shaft 1. As a result, displacement of the input side disk 2 in the direction of the axis O with respect to the input shaft 1 is substantially prevented. Further, a disc spring 8 is provided between the cam plate 7 and the flange 1d of the input shaft 1, and this disc spring 8 is connected to the concave surfaces 2a, 2a, 3a of each disc 2, 2, 3, 3. , 3a and the peripheral surfaces 11a, 11a of the power rollers 11, 11 are applied with a pressing force (preload).

FIG. 7 is a cross-sectional view taken along line AA in FIG. 6. As shown in FIG. 7, provided inside the casing 49 are a pair of trunnions 15, 15 that swing about a pair of pivots 14, 14 that are in a twisted position with respect to the input shaft 1. Note that in FIG. 7, illustration of the input shaft 1 is omitted. Each trunnion 15, 15 has a pair of bent walls 20, 20 formed at both ends of the support plate 16 in the longitudinal direction (vertical direction in FIG. have. A concave pocket P for accommodating the power roller 11 is formed in each trunnion 15 by the bent walls 20, 20. Moreover, each pivot shaft 14, 14 is provided concentrically with each other on the outer surface of each bent wall part 20, 20.

A circular hole 21 is formed in the center of the support plate portion 16, and a base end portion 23a of a displacement shaft 23 is supported in the circular hole 21. By swinging each trunnion 15, 15 about each pivot shaft 14, 14, the inclination angle of the displacement shaft 23 supported at the center of each trunnion 15, 15 can be adjusted. Further, each power roller 11 is rotatably supported around the distal end portion 23b of the displacement shaft 23 protruding from the inner surface of each trunnion 15, 15, and each power roller 11, 11 is connected to each input side disk. 2, 2 and each output side disk 3, 3. Note that the base end 23a and the tip end 23b of each displacement shaft 23, 23 are eccentric from each other.

Further, the pivot shafts 14, 14 of the respective trunnions 15, 15 are respectively supported to be swingable and displaceable in the axial direction (vertical direction in FIG. 7) relative to the pair of yokes 23A, 23B. 23B restricts the horizontal movement of the trunnions 15, 15. Each of the yokes 23A and 23B is formed into a rectangular shape by pressing or forging metal such as steel. Four circular support holes 18 are provided at the four corners of each yoke 23A, 23B, and in each of these support holes 18, a pivot shaft 14 provided at both ends of a trunnion 15 swings via a radial needle bearing 30. freely supported. Further, a circular locking hole 19 is provided at the center in the width direction (horizontal direction in FIG. 7) of the yokes 23A, 23B. 64 and 68 are fitted inside. That is, the upper yoke 23A is swingably supported by a spherical post 64 supported by the casing 49 via a fixing member 52, and the lower yoke 23B is supported by a spherical post 68 and a drive supporting it. The cylinder 31 is swingably supported by an upper cylinder body 56.

Note that the displacement shafts 23, 23 provided on the respective trunnions 15, 15 are provided at positions 180 degrees opposite to each other with respect to the input shaft 1. Furthermore, the direction in which the tip end 23b of each of these displacement shafts 23, 23 is eccentric with respect to the base end 23a is the same direction with respect to the rotational direction of both disks 2, 2, 3, 3 (up and down in FIG. (in the opposite direction). Further, the eccentric direction is substantially orthogonal to the direction in which the input shaft 1 is disposed. Therefore, each power roller 11, 11 is supported such that it can be slightly displaced in the longitudinal direction of the input shaft 1. As a result, even if each power roller 11, 11 tends to be displaced in the axial direction of the input shaft 1 due to elastic deformation of each component based on the thrust load generated by the pressing device 12, each component This displacement is absorbed without applying excessive force to the member.

Further, between the outer surface of the power roller 11 and the inner surface of the support plate portion 16 of the trunnion 15, a thrust ball bearing (thrust bearing) 24, which is a thrust rolling bearing, is arranged in order from the outer surface of the power roller 11. , a thrust needle bearing 25 are provided. Among these, the thrust ball bearing 24 supports the load in the thrust direction applied to each power roller 11 and allows each power roller 11 to rotate. Each of these thrust ball bearings 24 includes a plurality of balls (hereinafter referred to as rolling elements) 26, 26, an annular cage 27 that holds each of these rolling elements 26, 26 so as to be able to roll freely, and a circular retainer 27. It is composed of an annular outer ring 28. Further, the inner raceway of each thrust ball bearing 24 is formed on the outer surface (large end surface) of each power roller 11, and the outer raceway is formed on the inner surface of each outer ring 28.

Further, the thrust needle bearing 25 is held between the inner surface of the support plate portion 16 of the trunnion 15 and the outer surface of the outer ring 28. Such a thrust needle bearing 25 supports the thrust load applied from the power roller 11 to each outer ring 28, while also preventing the power roller 11 and outer ring 28 from swinging about the base end 23a of each displacement shaft 23. Allow.

Furthermore, drive rods (trunnion shafts) 29, 29 are provided at one end of each trunnion 15 (lower end in FIG. 7), respectively, and a drive piston ( Hydraulic pistons) 33, 33 are fixedly installed. Each of the drive pistons 33, 33 is fitted oil-tightly into the drive cylinder 31, which is constituted by an upper cylinder body 56 and a lower cylinder body 57. These drive pistons 33, 33 and drive cylinder 31 constitute a drive device 32 that displaces each trunnion 15, 15 in the axial direction of the pivot shafts 14, 14 of these trunnions 15, 15.

In the case of the toroidal continuously variable transmission configured in this way, the rotation of the input shaft 1 is transmitted to each input side disk 2, 2 via the pressing device 12. The rotation of these input side disks 2, 2 is transmitted to each output side disk 3, 3 via a pair of power rollers 11, 11, and furthermore, the rotation of each of these output side disks 3, 3 is transmitted to an output gear 4. taken out from

When changing the rotational speed ratio between the input shaft 1 and the output gear 4, the pair of drive pistons 33, 33 are displaced in opposite directions. As the driving pistons 33, 33 are displaced, the pair of trunnions 15, 15 are displaced in opposite directions. For example, the power roller 11 on the left side of FIG. 7 is displaced to the lower side of the figure, and the power roller 11 on the right side of the figure is displaced to the upper side of the figure.
As a result, the force acts on the contact portions between the circumferential surfaces 11a, 11a of these power rollers 11, 11 and the inner surfaces 2a, 2a, 3a, 3a of each input side disk 2, 2 and each output side disk 3, 3. The direction of the tangential force changes. As the direction of this force changes, each trunnion 15, 15 swings (tilts) in opposite directions about the pivot shafts 14, 14 pivotally supported by the yokes 23A, 23B.

As a result, the contact positions between the circumferential surfaces 11a, 11a of the power rollers 11, 11 and the inner surfaces 2a, 3a change, and the rotational speed ratio between the input shaft 1 and the output gear 4 changes. Furthermore, when the torque transmitted between the input shaft 1 and the output gear 4 changes and the amount of elastic deformation of each component changes, each power roller 11, 11 and the outer ring attached to each power roller 11, 11 change. 28, 28 rotate slightly around the base end portions 23a, 23a of the respective displacement shafts 23, 23. Thrust needle bearings 25, 25 are present between the outer surfaces of the outer rings 28, 28 and the inner surfaces of the support plate portions 16 constituting the trunnions 15, 15, respectively, so that the rotation is performed smoothly. be exposed. Therefore, as described above, only a small force is required to change the inclination angle of each displacement shaft 23, 23.

Japanese Patent Application Publication No. 2004-347047 Japanese Patent Application Publication No. 2003-166609

By the way, in a toroidal type continuously variable transmission, a roller bearing or a cage and roller is interposed between a disk (input side disk or output side disk) and the shaft, so that the disk is rotatably supported by the shaft. The directions of rotation of the disk and shaft are opposite, and a bearing between the two must support the relative rotation. In toroidal continuously variable transmissions for aircraft that are used at high speeds, the relative rotational speed of the bearing is approximately 30,000 rpm at most, and the bearing retainer and mating parts to support the axial position (for example, stops) are required. If there is contact with the ring), there is a risk of seizing or retainer wear, which may ultimately lead to retainer damage or retaining ring damage.
If the bearing retainer is damaged, the supporting disks and shafts will run out, which may cause the toroidal continuously variable transmission to become unsynchronized, making it impossible to transmit power. Furthermore, when the cage is damaged, it may cause impact to surrounding parts and cause cracks in the disk or shaft.
Furthermore, if the retaining ring of the bearing is damaged, the bearing will move in the axial direction, causing the rollers of the bearing to roll at a location other than the original raceway surface, which may lead to early damage to the bearing.
As mentioned above, the retaining ring rotates at high speed, so centrifugal force is generated. In order to prevent the retaining ring from coming off even if it is deformed by centrifugal force, it is advantageous in design to provide the retaining ring on the hole side, that is, on the inner diameter side of the disk. On the other hand, if a retaining ring groove (fitting groove) for fitting a retaining ring is provided on the inner diameter surface of the disk, the retaining ring groove of the disk becomes a high stress area, and there is a concern that the disk may crack.

For example, in the prior art shown in FIG. 8, a retainer 72 of a bearing 70 is supported in the axial direction by a splined stepped portion (axial end surface of the spline portion) 2d of the disk 2, a shim 73, and a retaining ring 74. There is. On the other hand, since the disk inner diameter surface 2c is deformed inward due to the influence of the normal force from the power roller 11, the retaining ring groove 2e provided in the disk inner diameter surface 2c becomes highly stressed. The disk 2 for aircraft rotates at approximately 20,000 rpm (300 Hz or more), and this deformation occurs twice per rotation of the disk, so there is a concern about fatigue failure of the disk (disk cracking).

Therefore, a configuration in which a retaining ring is provided on the shaft 1A side can be considered, but since the oil moves radially outward due to centrifugal force due to high-speed rotation, oil shortage easily occurs on the radially inner side, that is, on the shaft side. There may be no oil in the contact area between the side retaining ring and the shim (the part between the cage & roller and the retaining ring). As a result, wear of the retaining ring and shim progresses due to lack of oil film, and there is a concern that the retaining ring may be damaged.
In the toroidal continuously variable transmission for aircraft, a shaft indicated by reference numeral 1A is an output shaft, and the input side disk 2 is rotatably supported by this output shaft 1A via a bearing 70.

The present invention has been made in view of the above-mentioned circumstances, and is a toroidal continuously variable transmission that does not run out of oil film on the shaft side, suppresses the occurrence of high stress areas on the disk, and prevents fatigue failure of the disk. The purpose is to provide an opportunity.

In order to achieve the above object, the toroidal continuously variable transmission of the present invention has a shaft and a shaft that can rotate concentrically and integrally with the shaft with their inner surfaces facing each other. A toroidal continuously variable transmission comprising a first disk provided on the shaft, a second disk rotatably provided on the shaft, and a power roller sandwiched between the two disks,
An oil chamber is provided between the outer diameter surface of the shaft and the inner diameter surface of the second disk, and forms an end of the oil chamber in the axial direction of the shaft, and the inner diameter surface of the second disk. A seal body is provided in contact with the
A bearing rotatably supporting the second disk and the shaft is provided in the oil chamber,
Fitting grooves extending in the circumferential direction of the shaft are provided on the outer diameter surface of the shaft, and are spaced apart in the axial direction,
A retaining ring that restricts movement of the seal body in the axial direction and in a direction away from the bearing is fitted into the fitting groove.

Here, during operation of the toroidal type continuously variable transmission, oil is constantly supplied to the oil chamber from, for example, an oil supply hole formed inside the shaft.

In the present invention, the seal body forms the axial end of the oil chamber in the fitting groove provided on the outer diameter surface of the shaft and is spaced apart in the axial direction, and is in contact with the inner diameter surface of the second disk. Since a retaining ring that restricts movement in the axial direction and in the direction away from the bearing is fitted, there is no need to form a retaining ring groove on the inner diameter surface of the second disk, unlike in the past. Therefore, there is no high stress area generated in the second disk, and fatigue failure of the second disk can be prevented.
Further, since an oil chamber can be formed by the outer diameter surface of the shaft, the inner diameter surface of the second disk, and the seal body, there is no oil film breakage on the shaft side. Therefore, an oil film is formed on the bearing provided in the oil chamber, the seal body facing the oil chamber, and the retaining ring that restricts movement of the seal body, so that wear caused by lack of the oil film can be suppressed.

Further, in the configuration of the present invention, the seal body includes a cylindrical member that is externally fitted onto the shaft with a predetermined gap, and is provided on the outer peripheral surface of the cylindrical member, and Equipped with a seal member that is in oil-tight contact with the inner diameter surface,
A surface of the cylindrical member facing toward the retaining ring near the inner diameter may be in contact with the retaining ring.
The above-mentioned "oil-tightly" means "the sealing member (outer diameter surface) fits loosely onto the inner diameter surface of the second disk, and viscous oil is attached to (the outer diameter surface of the sealing member)". This means "to prevent or suppress the passage between the second disk and the inner diameter surface of the second disk", and the same applies in the following description.

Here, if excessive oil is supplied to the oil chamber, the dynamic torque (rotational resistance) of the shaft and second disk will increase, so to prevent this increase from occurring, the gap between the shaft and the cylindrical member must be It is preferable to adjust the leakage (discharge) of oil from the oil chamber depending on the size.

According to this configuration, the seal portion of the seal body is in oil-tight contact with the inner diameter surface of the second disk, and the surface of the cylindrical member facing the retaining ring near the inner diameter is in contact with the retaining ring. The oil supplied to the oil chamber is discharged from the gap between (the inner diameter surface of) the cylindrical member and the shaft, and is supplied to the contact portion between the cylindrical member and the retaining ring. Therefore, wear of the contact portion between the retaining ring and the cylindrical member can be suppressed.

Further, the toroidal continuously variable transmission of the present invention includes a shaft and a first rotatable shaft that is rotatably concentric with each other and integrally with the shaft, with their inner surfaces facing each other. A toroidal continuously variable transmission comprising a disk, a second disk rotatably provided with respect to the shaft, and a power roller sandwiched between these two disks,
An oil chamber is provided between the outer diameter surface of the shaft and the inner diameter surface of the second disk, and forms an end of the oil chamber in the axial direction of the shaft, and the inner diameter surface of the second disk. An annular plate-shaped seal member is provided in oil-tight contact with the
Fitting grooves extending in the circumferential direction of the shaft are provided on the outer diameter surface of the shaft, and are spaced apart in the axial direction,
A sealing member is fitted into the fitting groove,
The shaft and the second disk are rotatably supported by hydraulic pressure in the oil chamber.

Here, during operation of the toroidal type continuously variable transmission, oil is constantly supplied to the oil chamber from, for example, an oil supply hole formed inside the shaft.

In the present invention, an end portion of the oil chamber in the axial direction is formed in a fitting groove provided at a distance in the axial direction on the outer diameter surface of the shaft, and a seal is provided in oil-tight contact with the inner diameter surface of the second disk. Since the member is fitted, there is no need to form a retaining ring groove on the inner diameter surface of the second disk, unlike in the conventional case. Therefore, there is no high stress area generated in the second disk, and fatigue failure of the second disk can be prevented.
Further, since an oil chamber can be formed by the outer diameter surface of the shaft, the inner diameter surface of the second disk, and the seal member, there is no oil film breakage on the shaft side. Therefore, an oil film is formed on the seal member facing the oil chamber, so that wear caused by lack of the oil film can be suppressed.
Furthermore, since the shaft and the two discs are rotatably supported by the oil pressure in the oil chamber, there is no need to provide a bearing between the shaft and the second disc to rotatably support them, reducing the number of parts. can be done.
In addition, since the sealing member is in oil-tight contact with the inner diameter surface of the second disk, the oil filled in the oil chamber will not leak from between the sealing member and the second disk, and the oil pressure in the oil chamber will be reduced. Can be held constant.

According to the present invention, there is no oil film breakage on the shaft side, and generation of high stress areas on the disk (second disk) can be suppressed, thereby preventing fatigue failure of the disk.

1 is a sectional view schematically showing a toroidal continuously variable transmission according to a first embodiment of the present invention; FIG. It is a sectional view of the main part of the same. FIG. 3 is an enlarged cross-sectional view of a main part in FIG. 2 . FIG. 2 is a perspective view of the bearing. FIG. 3 is a sectional view of a main part of a toroidal continuously variable transmission according to a second embodiment of the present invention. FIG. 2 is a cross-sectional view showing an example of a conventional toroidal continuously variable transmission. 7 is a sectional view taken along line AA in FIG. 6. FIG. 1 is an enlarged sectional view of a main part, showing an example of a conventional toroidal continuously variable transmission for aircraft.

Embodiments of the present invention will be described below with reference to the drawings.
(First embodiment)
The toroidal continuously variable transmission of this embodiment is a transmission used in an aircraft generator, and is a transmission that changes the rotation speed from an aircraft engine to a constant rotation speed to generate a generator. Output to.
FIG. 1 is a cross-sectional view schematically showing the entire toroidal continuously variable transmission according to the first embodiment, FIG. 2 is a cross-sectional view of the main parts thereof, and FIG. 3 is an enlarged cross-sectional view of the main parts in FIG. 2.
In the prior art shown in FIGS. 6 and 7, the case where the output side disk 3 is rotatably supported by the input shaft 1 via the bearing 5 has been explained as an example, but in this embodiment, the input side disk 2 An example will be explained in which the output shaft 1A is rotatably supported via a bearing 70. However, in the toroidal type continuously variable transmission of this embodiment and the conventional toroidal type continuously variable transmission, the power roller 11 sandwiched between the input side disk 2 and the output side disk 3, the input side disk 2 and the output side Other configurations, such as a pressing device 12 that presses one disk 2 (3) of the disks 3 toward the other disk 3 (2), are the same, so a description thereof will be omitted. Moreover, hatching is omitted in FIG.

As mentioned above, the toroidal type continuously variable transmission of this embodiment is a double cavity type half toroidal type continuously variable transmission for aircraft (generators), and the input side disk disposed in one cavity. (second disk) 2 and an output side disk (first disk) 3 are attached around the output shaft (shaft) 1A, and an input side disk (second disk) 2 placed in the other cavity. , an output side disk (first disk) 3 are attached around the output shaft (shaft) 1A.
The output side disk 3 is provided so as to be rotatable integrally with the output shaft 1A, and the input side disk 2 is provided so as to be rotatable with respect to the output shaft 1A via a bearing 70. A power roller 11 is provided between the input side disk 2 and the output side disk 3, and the power roller 11 is sandwiched between both the disks 2 and 3.
Further, in this embodiment, the output side disk 3 is pressed toward the input side disk 2 by the pressing device 12.

As shown in FIGS. 2 to 4, the bearing 70 includes a plurality of cylindrical rollers 71 that can roll between the output shaft 1A and the input side disk 2, and a plurality of cylindrical rollers 71 that can roll between the output shaft 1A and the input side disk 2. It is provided with a cylindrical retainer 72 that holds the output shaft 1A and is attached to the output shaft 1A. The rollers 71 are in rolling contact with the outer diameter surface of the output shaft 1A and the inner diameter surface of the input side disk 2.
A plurality of holding holes 72d are formed in the outer circumferential surface (outer diameter surface) 72a of the cage 72 at predetermined equal angular intervals and open in the radial direction of the cage 72. Each holding hole 72d is capable of holding a roller 71 that rolls between the output shaft 1A and the input side disk 2 in a freely rolling manner.

Such a bearing 70 is provided in an oil chamber 50, which will be described later, provided between the output shaft 1A and the input side disk 2, as shown in FIGS. 2 and 3.
Further, the input side disk 2 has a shaft hole 2A having a circular cross section and extending in the axial direction in the radial center thereof, and the output shaft 1A is inserted through the shaft hole 2A. One end of the shaft hole 2A is opened on the small end surface side of the input side disk 2 (the right side in the axial direction in FIG. 2), and the other end is opened on the large end surface side of the input side disk 2 (on the left side in the axial direction in FIG. 2). ing.

Further, as shown in FIG. 1, an input gear 40 is provided between the pair of input side disks 2, 2. For example, rotational force from a rotating shaft of a turbine of an engine is transmitted to the input gear 40 via a gear or the like.
As shown in FIG. 2, the input gear 40 includes a gear portion 41 disposed on the outer side (axially outer side) of the input side disk 2, and a radially central portion side of this gear portion 41 (output shaft 1A in FIG. 2). cylindrical sleeve 42 provided at the right end of the side). This sleeve 42 is arranged coaxially with the shaft hole 2A of the input side disk 2, and approximately half of the sleeve 42 on the distal end side is inserted into the shaft hole 2A. As shown in FIG. 1, a sleeve 42 similar to the sleeve 42 is symmetrically provided at the left end of the gear portion 41 on the radial center side. It is similarly inserted into the shaft hole 2A of the input side disk 2 provided in the other cavity located on the left side.

Further, as shown in FIG. 2, on the outer diameter surface of the distal end of the sleeve 42, an uneven shape extending in the circumferential direction (continuously) that is uneven in the radial direction, and a spline extending in the axial direction. A portion 45a is provided.
On the other hand, on the inner diameter surface of the shaft hole 2A of the input side disk 2 that faces the spline portion 45a in the radial direction, an uneven shape that is uneven in the radial direction extends (continuously) along the circumferential direction, and in the axial direction. An inner diameter side spline portion 45b extending from the inner diameter side is provided. The inner diameter spline portion 45b and the spline portion 45a have approximately the same length in the axial direction.
By spline-coupling the inner spline portion 45b and the outer spline portion 45a of the sleeve 42, the rotation of the input gear 40 is transmitted to the input disk 2 via the sleeve 42. The rotation of the disk 2 is transmitted to the output shaft 1A via the power roller 11 and the output side disk 3.

In addition, in this embodiment, as shown in FIGS. 2 and 3, an input is made from the tip of the sleeve 42 between the outer diameter surface of the output shaft 1A and the inner diameter surface of the input side disk (second disk) 2. An oil chamber 50 is provided on the small end surface side of the side disk 2. At both ends of the oil chamber 50 in the axial direction (the axial direction of the output shaft 1A), seal bodies 51, 51 are provided facing each other and spaced apart in the axial direction. Therefore, the area surrounded by the pair of seal bodies 51, 51, the outer diameter surface of the output shaft 1A, and the inner diameter surface of the input side disk 2 forms the oil chamber 50. The bearing 70 is provided in this oil chamber 50.

The seal body 51 includes a cylindrical member 51a made of iron that is fitted onto the output shaft 1A with a predetermined gap S in the radial direction, and is provided on the outer circumferential surface of the cylindrical member 51a so that the inner diameter of the input disk 2 A seal member 51b that is in oil-tight contact with the surface is provided. A groove 51c is formed along the circumferential direction on the outer circumferential surface of the cylindrical member 51a, and the inner circumference of the ring-shaped seal member 51b is fitted into the groove 51c. This seal member 51b is in oil-tight contact with the inner diameter surface of the input side disk 2. Since the input side disk 2 rotates around the output shaft 1A, the seal member 51b is in oil-tight sliding contact with the inner diameter surface of the rotating input side disk 2. The sealing member 51b is formed of, for example, an O-ring or a resin ring-shaped sealing material.

In addition, fitting grooves 1g, 1g extending in the circumferential direction of the output shaft 1A are provided on the outer diameter surface of the output shaft 1A to be spaced apart in the axial direction. The inner circumferential portion of an annular plate-shaped retaining ring 53 is fitted into the fitting groove 1g, and the outer circumferential portion of the retaining ring 53 is radially outward from the outer diameter surface of the output shaft 1A and the inner diameter surface of the cylindrical member 51a. It stands out.
The retaining ring 53 restricts the movement of the seal body 51 in the axial direction and in the direction away from the bearing 70 (in FIG. 3, the right seal body 51 is to the right and the left seal body 51 is to the left). be. That is, the surface of the cylindrical member 51a of the seal body 51 that is closer to the inner diameter and faces the retaining ring 53 is in contact with the retaining ring 53, thereby causing the seal body 51 to move in the axial direction and away from the bearing 70. Movement is restricted. That is, in FIG. 3, the right retaining ring 53 restricts rightward movement of the right seal body 51, and the left retaining ring 53 restricts leftward movement of the left seal body 51.

Further, the output shaft 1A is provided with an oil passage 1e extending in the axial direction in the radial center thereof, and a plurality of oil supply holes 1f extending in the radial direction from the oil passage 1e are arranged at predetermined intervals in the circumferential direction. It is provided.
The oil supply hole 1f opens into the oil chamber 50 on the outer diameter surface of the output shaft 1A. Therefore, oil is constantly supplied to the oil chamber 50 through the oil passage 1e and the oil supply hole 1f during operation of the toroidal continuously variable transmission. As described above, the bearing 70 is provided in the oil chamber 50.
The oil supplied to the oil chamber 50 supplies oil to the bearing 70, the outer diameter surface of the output shaft 1A supported by the bearing 70, and the inner diameter surface of the input side disk 2. Further, since a gap S is provided between the inner diameter surface of the cylindrical member 51a of the seal body 51 and the output shaft 1A, the oil supplied to the oil chamber 50 is discharged through the gap S, and the retaining ring 53 and the contact portion of the seal body 51 with the cylindrical member 51a. Note that such oil flow is shown by arrows in FIG. 3.
When oil is excessively supplied to the oil chamber 50, the dynamic torque (rotational resistance) of the output shaft 1A and the input side disk 2 increases. The leakage (discharge) of oil from the oil chamber 50 is adjusted depending on the size of the gap S between the oil chambers 50 and 50.

According to the first embodiment, the seal body 51 that forms the end portion of the oil chamber 50 in the axial direction is provided in the fitting grooves 1g, 1g provided in the outer diameter surface of the output shaft 1A spaced apart in the axial direction. Since the retaining rings 53, 53 that restrict the movement of the output shaft 1A in the axial direction and in the direction away from the bearing 70 are fitted, there is no need to provide a retaining ring groove on the inner diameter surface of the input side disk 2. Therefore, there are no high-stress areas generated on the input side disk 2, and fatigue failure of the input side disk 2 can be prevented.
Further, since the oil chamber 50 can be formed by the outer diameter surface of the output shaft 1A, the inner diameter surface of the input side disk 2, and the seal bodies 51, 51, there is no oil film breakage on the output shaft 1A side. Therefore, an oil film is formed on the bearing 70 provided in the oil chamber 50, the seal body 51 facing the oil chamber 50, and the retaining ring 53 that restricts the movement of the seal body 51, so that wear caused by lack of the oil film can be suppressed.

Further, the seal body 51 includes a cylindrical member 51a that is externally inserted into the output shaft 1A with a predetermined gap S, and is provided on the outer circumferential surface of the cylindrical member 51a to provide oil to the inner diameter surface of the input side disk 2. Since the surface of the cylindrical member 51a that is closer to the inner diameter and faces the retaining ring 53 is in contact with the retaining ring 53, the oil supplied to the oil chamber 50 is supplied to the cylindrical member 51a. is discharged from the gap S between the inner diameter surface of the output shaft 1A and the output shaft 1A, and is supplied to the abutting portion (contact portion) between the cylindrical member 51a and the retaining ring 53. Therefore, wear of the contact portion between the retaining ring 53 and the cylindrical member 51a can be suppressed.

(Second embodiment)
FIG. 5 is a sectional view showing essential parts of a toroidal continuously variable transmission according to the second embodiment. The second embodiment differs from the first embodiment in that, without providing a bearing between the outer diameter surface of the output shaft 1A and the inner diameter surface of the input side disk 2, the input side Since the disk 2 and the output shaft 1A are rotatably supported, this point will be explained below, and the same components as in the first embodiment will be given the same reference numerals and the explanation thereof will be omitted. In some cases.

In the second embodiment, an oil chamber 60 is provided between the outer diameter surface of the output shaft 1A and the input side disk 2 on the small end surface side of the input side disk 2 from the tip of the sleeve 42.
Seal members 61, 61 are provided at both ends of the oil chamber 60 in the axial direction (the axial direction of the output shaft 1A) so as to be opposed to each other in the axial direction. Therefore, the area surrounded by the pair of seal members 61, 61, the outer diameter surface of the output shaft 1A, and the inner diameter surface of the input side disk 2 forms the oil chamber 60.

The sealing member 61 is formed in the shape of an annular plate, and is made of, for example, a ring-shaped sealing material made of resin. This seal member 61 is in oil-tight contact with the inner diameter surface of the input side disk 2. Since the input side disk 2 rotates around the output shaft 1A, the seal member 61 is in oil-tight sliding contact with the inner diameter surface of the rotating input side disk 2.
In addition, fitting grooves 1h, 1h extending in the circumferential direction of the output shaft 1A are provided on the outer diameter surface of the output shaft 1A, spaced apart in the axial direction. An inner peripheral portion of an annular plate-shaped seal member 61 is fitted into the fitting groove 1h. This restricts the movement of the seal member 61 in the axial direction. That is, in FIG. 5, rightward movement of the right sealing member 61 is regulated by the right-hand fitting groove 1h, and leftward movement of the left-hand sealing member 61 is regulated by the left-hand fitting groove 1h. There is.

Further, similarly to the first embodiment, the output shaft 1A is provided with an oil passage 1e extending in the axial direction in the radial center thereof, and an oil supply hole extending in the radial direction from the oil passage 1e. A plurality of 1f are provided at predetermined intervals in the circumferential direction.
The oil supply hole 1f opens into the oil chamber 60 on the outer diameter surface of the output shaft 1A. Therefore, oil is constantly supplied to the oil chamber 60 through the oil passage 1e and the oil supply hole 1f during operation of the toroidal continuously variable transmission.
The input side disk 2 and the output shaft 1A are rotatably supported by the hydraulic pressure of the oil supplied to the oil chamber 60. This suppresses radial movement and resonance of the output shaft 1A.

According to the second embodiment, the ends of the oil chamber 60 in the axial direction are formed in the fitting grooves 1h, 1h provided in the outer diameter surface of the output shaft 1A at a distance in the axial direction, and the ends of the oil chamber 60 are formed on the input side. Since the seal members 61, 61 in oil-tight contact with the inner diameter surface of the disk 2 are fitted, there is no need to provide a retaining ring groove on the inner diameter surface of the input side disk 2. Therefore, there are no high-stress areas generated on the input side disk 2, and fatigue failure of the input side disk 2 can be prevented.
Further, since the oil chamber 60 can be formed by the outer diameter surface of the output shaft 1A, the inner diameter surface of the input side disk 2, and the seal members 61, 61, there is no oil film breakage on the output shaft 1A side. Therefore, an oil film is formed on the seal members 61, 61 facing the oil chamber 60, so that there is no oil film breakage, and wear caused by the oil film breakage can be suppressed.

Further, the sealing member 61 is formed in the shape of an annular plate, and the inner peripheral part is fitted into the fitting groove 1h, and the outer peripheral part is in oil-tight contact with the inner diameter surface of the input side disk 2, so that the seal member 61 is not connected to the oil chamber 60. The filled oil does not leak from between the seal member 61 and the input side disk 2, and the oil pressure in the oil chamber 60 can be kept constant.

In the first and second embodiments, the present invention has been described with reference to a toroidal continuously variable transmission for aircraft, but the present invention can also be applied to other uses (for example, for automobile transmissions).
Further, in the first and second embodiments, the present invention has been described taking as an example a case where the present invention is applied to a double cavity type half-toroidal continuously variable transmission, but the present invention is not limited to this. It can also be applied to a full toroidal continuously variable transmission, a single cavity half toroidal continuously variable transmission, and a single cavity full toroidal continuously variable transmission.

Furthermore, in the first and second embodiments, the case where the output side disk 3 is pressed by the pressing device 12 has been explained as an example, but in a toroidal continuously variable transmission, the input/output relationship between the input side disk and the output side disk is Sometimes it is reversed. Therefore, the present invention can also be applied to the case where the input side disk 2 is pressed by the pressing device 12. In other words, as shown in FIGS. 6 and 7, there is an input shaft 1, an input disk 2 that is spline-coupled to the input shaft 1 by a ball spline and rotates integrally with the input shaft 1, and an input disk 2 that faces the input shaft 1. , and an output side disk 3 rotatably provided with respect to the input shaft 1. The present invention can also be applied to a toroidal continuously variable transmission.

1A output shaft (shaft)
1g, 1h Fitting groove 2 Input side disk (second disk)
3 Output side disk (first disk)
11 Power roller 50, 60 Oil chamber 51 Seal body 51a Cylindrical member 51b Seal member 53 Retaining ring 61 Seal member 70 Bearing 72 Cage

Claims (3)

a first disk rotatably provided on the shaft concentrically and integrally with the shaft with their inner surfaces facing each other; and a first disk rotatably provided on the shaft so as to be rotatable with respect to the shaft. In a toroidal continuously variable transmission including a second disk and a power roller sandwiched between these two disks,
An oil chamber is provided between the outer diameter surface of the shaft and the inner diameter surface of the second disk, and forms an end of the oil chamber in the axial direction of the shaft, and the inner diameter surface of the second disk. A seal body is provided in contact with the
A bearing rotatably supporting the second disk and the shaft is provided in the oil chamber,
Fitting grooves extending in the circumferential direction of the shaft are provided on the outer diameter surface of the shaft, and are spaced apart in the axial direction,
A toroidal continuously variable transmission characterized in that a retaining ring that restricts movement of the seal body in the axial direction and in a direction away from the bearing is fitted into the fitting groove. The seal body includes a cylindrical member fitted onto the shaft with a predetermined gap, and a seal member provided on the outer peripheral surface of the cylindrical member and in oil-tight contact with the inner diameter surface of the second disk. and
2. The toroidal continuously variable transmission according to claim 1, wherein a surface of the cylindrical member facing toward the retaining ring near the inner diameter is in contact with the retaining ring. a first disk rotatably provided on the shaft concentrically and integrally with the shaft with their inner surfaces facing each other; and a first disk rotatably provided on the shaft so as to be rotatable with respect to the shaft. In a toroidal continuously variable transmission including a second disk and a power roller sandwiched between these two disks,
An oil chamber is provided between the outer diameter surface of the shaft and the inner diameter surface of the second disk, and forms an end of the oil chamber in the axial direction of the shaft, and the inner diameter surface of the second disk. An annular plate-shaped seal member is provided in oil-tight contact with the
Fitting grooves extending in the circumferential direction of the shaft are provided on the outer diameter surface of the shaft, and are spaced apart in the axial direction,
A sealing member is fitted into the fitting groove,
A toroidal continuously variable transmission, wherein the shaft and the second disk are rotatably supported by hydraulic pressure in the oil chamber.

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