JP2018096429A - Toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a structure of a toroidal type continuously variable transmission that can prevent a shaft-side locking ring constituting a ball spline from falling out from a shaft-side locking groove formed in an input rotary shaft.SOLUTION: A toroidal type continuously variable transmission has an axial distance (α) from a side face on the other end side in an axial direction in an inner diameter-side part 32 of an input-side disk 2c to a side face on the other end side in an axial direction of a shaft-side locking groove 8a that is greater than a maximum displacement amount (β) on one end side in an axial direction relative to an input rotary shaft 1a of the input-side disk 2c based on pressing force that is exerted by a pressing device 17a.SELECTED DRAWING: Figure 2

Description

  The present invention relates to an improvement of a toroidal continuously variable transmission that is used as an automatic transmission device for generators used in, for example, aircrafts, various industrial machines such as pumps, vehicles (automobiles), and construction machines. .

  The use of a toroidal-type continuously variable transmission as a transmission for an automobile is described in publications such as Patent Document 1 and is partially implemented, and is well known. Further, a structure in which the adjustment range of the gear ratio is widened by combining a toroidal type continuously variable transmission and a planetary gear mechanism is described in publications such as Patent Document 2 and has been widely known.

  4 to 5 show a toroidal-type continuously variable transmission having a conventional structure described in Patent Document 3. FIG. In the case of this conventional structure, a pair of input-side disks 2a and 2b are opposed to axially opposite end portions of the input rotary shaft 1 and axial side surfaces (inner side surfaces), each of which is a toroidal curved surface having a circular arc cross section. In this state, it is supported so as to be able to rotate in synchronization with the input rotary shaft 1. Among these, the input side disk 2b shown at the right side in FIG. 4 is spline-engaged with a portion near the one end (tip portion) in the axial direction of the input rotation shaft 1 and the back side thereof is input with the input. By abutting against an outward flange-shaped flange portion 3 provided on the rotary shaft 1, the displacement toward the one end side in the axial direction is made impossible and the rotation synchronized with the input rotary shaft 1 is supported. On the other hand, the input side disk 2a on the other end side in the axial direction shown on the left side of FIG. Further, it is supported so as to be capable of axial displacement and to rotate in synchronization with the input rotary shaft 1.

  As shown in FIG. 5, the ball spline 4 includes a plurality of balls 7, 7, a shaft side locking ring 9, and a disk side locking ring 11. Each of these balls 7 and 7 is freely rollable between a male spline groove 5 formed on the outer peripheral surface of the input rotary shaft 1 and a female spline groove 6 formed on the inner peripheral surface of the input side disk 2a. Has been placed. Further, by locking the shaft side locking ring 9 in a shaft side locking groove 8 formed on the outer peripheral surface of the input rotary shaft 1, the balls 7 and 7 come out to the other end side in the axial direction. Is preventing. Further, by locking the disk-side locking ring 11 in a disk-side locking groove 10 formed on the inner peripheral surface of the input-side disk 2a, the balls 7 and 7 come out to one end in the axial direction. Is preventing.

  Further, an output cylinder 12 is supported around an intermediate portion in the axial direction of the input rotary shaft 1 so as to be able to rotate relative to the input rotary shaft 1. Further, an output gear 13 is fixed to the outer peripheral surface of the output cylinder 12 at the center in the axial direction, and a pair of output side disks 14a and 14b are rotated at both ends in the axial direction in synchronization with the output cylinder 12. I support it. Further, in this state, the axial side surfaces of the output side disks 14a and 14b, each of which is a toroidal curved surface having an arc cross section, are opposed to the axial side surfaces of the input side disks 2a and 2b.

Further, a plurality of power rollers 15 and 15 each having a partially spherical convex surface are sandwiched between the input disks 2a and 2b and the output disks 14a and 14b. These power rollers 15 and 15 are rotatably supported by the trunnions 16 and 16, and rotate with the rotation of the both input side disks 2 a and 2 b, while the both input side disks 2 a and 2 b rotate the both Power is transmitted to the output side disks 14a and 14b.
Or, contrary to the above description, the power of the driving source is input to the inner disks provided at the positions of the output side disks 14a and 14b, and a pair of positions provided at the positions of the input disks 2a and 2b. It can also be configured to extract power from the outer disk.

  In addition, a hydraulic pressing device 17 is assembled between the input side disk 2 a on the other axial end side and the input rotary shaft 1. As a result, the power to be transmitted to the rolling contact portion (traction portion) between the circumferential surface of each of the power rollers 15 and 15 and the axial side surface of each of the input side and output side discs 2a, 2b, 14a and 14b. Appropriate surface pressure is applied.

  A gear-shaped member 18 is spline-engaged with a portion of the outer peripheral surface of the input rotary shaft 1 adjacent to the other end side in the axial direction from a portion where the pressing device 17 is arranged around the periphery. A loading nut 19 is screwed into a portion adjacent to the other end side in the axial direction of the member 18. A rotational force is transmitted from the drive shaft 20 to the input rotary shaft 1 via the gear-shaped member 18. The loading nut 19 supports a pressing reaction force acting on the pressing device 17 and prevents the pressing device 17 from being displaced to the other end side in the axial direction. The pressing force supported by the loading nut 19 is transmitted to the input side disk 2b on the one end side in the axial direction via the input rotary shaft 1. Then, it acts as a pressing force for pressing the input side disk 2b toward the output side disk 14b.

JP 2003-214516 A JP 2004-169719 A JP 2003-139209 A

By the way, when the toroidal continuously variable transmission is operated, the input side disk 2a is placed on the right side of FIGS. 4 and 5 by elastically deforming each part based on the pressing force (pressing reaction force) exerted by the pressing device 17. The input rotary shaft 1 moves to the left in FIGS. However, in the case of the conventional structure, regarding the prevention of the shaft side locking ring 9 from falling off, it is necessary to consider the relative displacement of the input side disk 2a toward the one end in the axial direction with respect to the input rotating shaft 1. It wasn't. For this reason, when the relative displacement amount of the input side disk 2a with respect to the input rotary shaft 1 increases as the pressing force exerted by the pressing device 17 increases during the operation of the toroidal continuously variable transmission, the input side disk There is a possibility that 2a does not exist around the shaft side locking ring 9 (the periphery is not covered), and the shaft side locking ring 9 may be exposed to the outside. As a result, the shaft-side locking ring 9 may drop off from the shaft-side locking groove 8 due to the centrifugal force acting with the rotation of the input rotary shaft 1.
In view of the circumstances as described above, the present invention is to realize a structure of a toroidal continuously variable transmission that can prevent a locking ring constituting a ball spline from falling off from a locking groove formed on a rotating shaft. Invented.

A toroidal continuously variable transmission according to the present invention includes a rotating shaft, a first disk, a second disk, a plurality of power rollers, a pressing device, and a ball spline.
The rotating shaft has a male spline groove and a locking groove on the outer peripheral surface.
The first disk is supported by the rotating shaft and has a female spline groove on the inner peripheral surface.
The second disk is supported by the rotating shaft and is disposed to face the first disk.
The plurality of power rollers are sandwiched between the first disk and the second disk so as to be tiltable.
The pressing device presses the first disk toward one end in the axial direction. The pressing device is fixed on the other end side in the axial direction of the pressing device, for example, on the outer peripheral surface of the rotating shaft, based on the pressing reaction force. It is blocked by the support member.
As such a pressing device, a mechanical pressing device incorporating a loading cam or a hydraulic pressing device including a hydraulic cylinder and a piston can be used. Further, as the support member, a loading nut, a fixed ring (cotter) locked in a fixed groove formed on the outer peripheral surface of the rotating shaft, or the like can be used.
The ball spline is engaged with the plurality of balls disposed between the male spline groove and the female spline groove, and the engagement groove, and is disposed on the other axial end side of the plurality of balls. And a retaining ring.

Particularly in the case of the toroidal type continuously variable transmission according to the present invention, the axial distance from the side surface on the other end side in the axial direction to the side surface on the other end side in the axial direction of the locking groove in the inner diameter side portion of the first disk. Is larger than the maximum displacement amount of the first disk toward the one end side in the axial direction (based on the rotation axis) based on the pressing force exerted by the pressing device.
The inner diameter side portion of the first disk is a portion in which a female spline groove is formed on the inner peripheral surface (the inner diameter dimension of the portion adjacent to the other axial end side of the portion in which the female spline groove is formed is If the inner diameter dimension is substantially the same as the portion where the spline groove is formed, this portion is included).

  When implementing the present invention as described above, for example, the amount of movement from the assembly completion position of the first disk to the one end side in the axial direction during the assembly operation of the locking ring is expressed as the locking groove. And the axial distance from the side surface on the other end side in the axial direction in the inner diameter side portion of the first disc to the side surface on the other end side in the axial direction of the locking groove. I can do things.

According to the toroidal type continuously variable transmission of the present invention having the above-described configuration, it is possible to prevent the locking ring constituting the ball spline from dropping off from the locking groove formed on the rotating shaft.
That is, in the case of the present invention, the axial distance from the side surface on the other end side in the axial direction to the side surface on the other end side in the axial direction of the locking groove in the inner diameter side portion of the first disk is the pressing device. Is larger than the maximum amount of displacement of the first disk toward the one end side in the axial direction with respect to the rotating shaft based on the pressing force exerted by the. For this reason, in the case of the present invention, when the toroidal type continuously variable transmission is operated, the pressing force exerted by the pressing device is maximized, so that the first disk is relatively relative to one end side in the axial direction with respect to the rotating shaft. Even when the amount of displacement becomes maximum, it is possible to maintain a state in which the inner diameter side portion constituting the first disk exists around (covers the periphery of) the locking ring. For this reason, this locking ring can be prevented from being exposed to the outside. Therefore, according to the present invention, it is possible to prevent the locking ring from dropping even when a centrifugal force is applied as the rotation shaft rotates.

  Further, the amount of movement of the first disk from the assembly completion position to one end in the axial direction at the time of assembling the locking ring is determined by the axial width dimension of the locking groove and the inner diameter of the first disk. When it is larger than the sum of the axial distance from the side surface on the other end side in the axial direction in the side portion to the side surface on the other end side in the axial direction of the locking groove, during assembly work of the locking ring, The entire locking groove can be exposed to the outside. Therefore, it is possible to improve the working efficiency of the work of assembling the locking ring.

Sectional drawing of the toroidal type continuously variable transmission which shows an example of embodiment of this invention. The A section enlarged view of FIG. 1 similarly. The schematic diagram similarly shown in order to demonstrate the assembly procedure of a ball spline. Sectional drawing which shows the toroidal type continuously variable transmission of conventional structure. The enlarged view corresponding to FIG. 2 similarly.

[Example of Embodiment]
1 to 3 show an example of an embodiment of the present invention. The toroidal-type continuously variable transmission 21 of this example is a transmission used, for example, for an aircraft generator, and includes an input rotary shaft 1a corresponding to the rotary shaft described in the claims, and the claims. An input side disk 2c corresponding to the described first disk, another input side disk 2d, an output side disk 14c corresponding to the second disk described in the claims, a plurality of power rollers 15, 15; A plurality of trunnions (not shown), a hydraulic pressing device (loading device) 17a, and a ball spline 4a are provided.

The input rotary shaft 1a is supported on the upper side of the actuator case 22 through a pair of support columns 23 and 23 and the output side disk 14c so as to be rotatable only. Specifically, the input rotary shaft 1a is supported on the output side disk 14c rotatably supported by thrust angular ball bearings 24 and 24 on support ring portions provided at intermediate portions of the both columns 23 and 23, respectively. Is supported rotatably by a pair of radial needle bearings 25, 25.
In the present specification and claims, the “axial direction” refers to the axial direction of the input rotary shaft 1a unless otherwise specified, and refers to the horizontal direction of FIGS. Moreover, in the case of this example, the right side of FIGS. 1-3 which is the front end side of the said input rotating shaft 1a is equivalent to the axial direction one end side of a claim.

  The two input-side disks 2c and 2d are disposed at portions close to both ends in the axial direction of the input rotation shaft 1a in a state where the axial side surfaces (inner side surfaces) of the toroidal curved surfaces each having a circular arc cross section are opposed to each other. The rotation is synchronized with the input rotation shaft 1a, and is supported so as to be movable in the near and far directions.

  For this purpose, of the two input side disks 2c and 2d, the input side disk 2d on the one end side in the axial direction shown on the right side in FIG. The back surface (outer side surface) of the input rotary shaft 1a is abutted against an outward flange-shaped flange portion 3a provided at one axial end portion of the input rotary shaft 1a. As a result, the input side disk 2d is supported so that it cannot be displaced toward the one end side in the axial direction with respect to the input rotary shaft 1a, and can rotate in synchronization with the input rotary shaft 1a.

  On the other hand, among the input side disks 2c and 2d, the input side disk 2c on the other end side in the axial direction corresponding to the first disk shown on the left side of FIG. A portion near the other end (proximal end) in the axial direction of the input rotary shaft 1a is supported via a ball spline 4a so as to be able to be displaced in the axial direction and to be synchronized with the input rotary shaft 1a. ing.

  The ball spline 4a includes a plurality of balls 7a, 7a, a shaft side locking ring 9a, and a disk side locking ring 11a. Of these, the balls 7a and 7a are freely rollable between a male spline groove 5a formed on the outer peripheral surface of the input rotary shaft 1a and a female spline groove 6a formed on the inner peripheral surface of the input side disk 2c. Is arranged. Here, a plurality of the male spline grooves 5a are formed on the outer peripheral surface of the input rotating shaft 1a in a state of being spaced apart in the circumferential direction and extending in the axial direction, and the female spline grooves 6a are A plurality (the same number as the male spline grooves 5a) are formed on the inner peripheral surface of the side disk 2c while being spaced apart in the circumferential direction and extended in the axial direction. Further, the male spline groove 5a and the female spline groove 6a are formed at portions where phases in the circumferential direction coincide with each other. The female spline groove 6a is formed on the inner peripheral surface of the input side disk 2c (inner diameter side portion 32 described later) so as to penetrate both sides in the axial direction, and the groove depth extends in the axial direction. It is constant. In contrast, the male spline groove 5a has a groove depth that decreases toward both axial sides.

  In the case of this example, the male spline groove 5a is crossed in the circumferential direction at a portion closer to the other axial end of the portion where the male spline groove 5a is formed on the outer peripheral surface of the input rotary shaft 1a. The shaft side locking groove 8a corresponding to the locking groove described in the claims is formed over the entire circumference. The shaft-side locking groove 8a has a substantially semi-circular cross section, and the groove depth in the radial direction from the outer peripheral surface of the input rotating shaft 1a is smaller than the groove depth in the radial direction of the male spline groove 5a ( About half). Then, by locking the shaft side locking ring 9a corresponding to the locking ring described in the claims in such a shaft side locking groove 8a, each of the balls 7a, 7a is axially or the like. It is prevented from slipping out to the end side (left side in FIGS. 1 to 3). That is, the shaft side locking ring 9a is arranged on the other axial end side of the balls 7a, 7a. In the case of this example, the shaft side locking ring 9a is circular in cross section, and the whole is formed in a circular shape (C shape).

  Further, on the inner peripheral surface of the input-side disk 2c, the disk-side locking is carried out at a portion near the one end in the axial direction of the portion where the female spline groove 6a is formed so as to cross the female spline groove 6a in the circumferential direction. The groove 10a is formed over the entire circumference. The disk-side locking groove 10a has a substantially semicircular cross section, and the groove depth in the radial direction from the inner peripheral surface of the input-side disk 2c is smaller than the groove depth in the radial direction of the female spline groove 6a. (Approximately 1/2). Then, by locking the disk-side locking ring 11a in such a disk-side locking groove 10a, the balls 7a and 7a are prevented from coming out to one end side in the axial direction (the right side in FIGS. 1 to 3). It is preventing. In the case of this example, the disk-side locking ring 11a has a circular cross section, and is configured in a partially circular shape (C shape) as a whole.

  The output side disk 14c is supported around an intermediate portion in the axial direction of the input rotary shaft 1a so as to be able to rotate relative to the input rotary shaft 1a. In this state, both side surfaces (outer surfaces) in the axial direction of the output side disk 14c are opposed to the side surfaces in the axial direction of the both input side disks 2c and 2d. Further, a plurality of power rollers 15 and 15 are sandwiched between the input disks 2c and 2d and the output disk 14c so as to be tiltable. The power rollers 15 and 15 transmit power from the input disks 2c and 2d to the output disk 14c while rotating with the rotation of the input disks 2c and 2d.

  Further, the pressing device 17a is provided between the other axial end portion of the input rotary shaft 1a and the input side disk 2c. The pressing device 17a is a hydraulic pressing device, and presses the input side disk 2c toward the input side disk 2d on one end side in the axial direction with a force corresponding to the magnitude of the hydraulic pressure introduced inside. .

  A fixed ring 28 is fixed to a portion near the other axial end of the input rotary shaft 1a. For this reason, in the case of this example, a fixing groove 29 is provided on the other axial end portion of the outer peripheral surface of the input rotating shaft 1a where the inner diameter side portion of the pressing device 17a is fitted. The fixing ring 28 is locked in the fixing groove 29. In this state, the one end surface in the axial direction of the stationary ring 28 is abutted against the other end surface in the axial direction of the inner diameter side portion of the pressing device 17a, and the pressing device 17a has the other end in the axial direction based on the pressing reaction force. It is prevented from moving to the side (the direction away from the input side disk 2c, the left side in FIG. 1). The fixed ring 28 is formed by combining a plurality of (for example, 2 to 4) partial arc-shaped elements in the circumferential direction. A stationary ring 28 is configured. Further, in order to prevent a plurality of elements constituting the fixing ring 28 from coming out of the fixing groove 29 radially outward, the periphery of each element is covered with a restraining ring 30.

  During operation of the toroidal-type continuously variable transmission 21, the input side disk 2c is rotationally driven by the drive shaft (not shown) via the pressing device 17a. As a result, the pair of input-side disks 2c and 2d supported on the axially opposite ends of the input rotation shaft 1a rotate synchronously while being pressed in a direction approaching each other. This rotation is transmitted to the output side disk 14c via the power rollers 15 and 15. In the illustrated example, a preload spring 31 is disposed on the inner diameter side portion of the pressing device 17a. Thus, even when the pressing device 17a is not in operation (when the drive shaft is stopped), the peripheral surfaces of the power rollers 15 and 15 and the axial side surfaces of the input and output disks 2c, 2d and 14c. The surface pressure of the rolling contact part (traction part) is secured to the minimum necessary.

Particularly in the case of the toroidal-type continuously variable transmission 21 of the present example, the shaft-side locking groove 8a formed on the outer peripheral surface of the input rotating shaft 1a is formed by the shaft-side locking ring 9a constituting the ball spline 4a. In order to prevent it from falling off, the formation position of the shaft side locking groove 8a is regulated as follows.
That is, in the case of this example, in the state before the operation of the toroidal continuously variable transmission 21 (assembled state) as shown in FIGS. A side surface on the other end side in the axial direction of the shaft side locking groove 8a (shaft side locking ring 9a) from a side surface on the other end side in the axial direction in the inner diameter side portion 32 in which the female spline groove 6a is formed on the peripheral surface. Is larger than the maximum displacement amount (β) of the input side disk 2c toward the one end side in the axial direction with respect to the input rotating shaft 1a based on the pressing force exerted by the pressing device 17a during operation. The shaft side locking groove 8a is formed at the position.

  In the case of this example, the inner diameter side portion 32 is provided in a range extending from one end portion in the axial direction to the middle portion on the inner peripheral surface of the input side disk 2c. A spline groove 6a is formed. For this reason, the side surface on the other end side in the axial direction of the inner diameter side portion 32 can also be expressed as the other end surface in the axial direction of the female spline groove 6a. Further, the inner diameter dimension of the inner diameter side portion 32 (the diameter of the inscribed circle of the portion circumferentially removed from the female spline groove 6a) is at least closer to the other end from the other axial end portion of the input rotating shaft 1a. It is larger than the outer diameter in the range of the portion (position where the input side disk 2c is arranged in the assembled state).

  The maximum displacement (β) is based on the pressing force exerted by the pressing device 17a during the operation of the toroidal-type continuously variable transmission 21, and the input side disk 2c is at one end in the axial direction (FIGS. 1 and 2). The input rotation shaft 1a is maximized on the other axial end side (left side in FIGS. 1 and 2) based on the displacement amount (β1) when the displacement is maximally (right side) and the pressing reaction force of the pressing device 17a. This is the sum of the displacement amount (β2) when displaced (β = β1 + β2).

  Further, in the case of this example, not only the position where the shaft side locking groove 8a is formed is determined from the viewpoint of preventing the shaft side locking ring 9a from falling off, but also this shaft side locking ring. It is determined from the viewpoint of improving the assembly workability of 9a. For this reason, in the case of this example, in addition to the first requirement (α> β) as described above, the shaft side locking groove 8a is formed so as to satisfy the following second requirement. Yes. Prior to describing the second requirement, the entire assembly procedure of the toroidal-type continuously variable transmission 21 of this example will be briefly described, and the assembly procedure of the ball spline 4a will be described.

  In order to assemble the toroidal type continuously variable transmission 21 of this example, the input side rotary shaft 1a is arranged around the input rotary shaft 1a in the order of the input side disc 2d, the output side disc 14c, and the input side disc 2c. After assembling from the other end side in the axial direction of 1a, the power rollers 15, 15 are arranged between the input side disk 2d and the output side disk 14c. Next, after the ball spline 4a is assembled between the input side disk 2c and the input rotary shaft 1a, the power rollers 15, 15 are provided between the input side disk 2c and the output side disk 14c. Place. Thereafter, the pressing device 17a is assembled around the input rotary shaft 1a from the other axial end side of the input-side rotary shaft 1a, and the stationary ring 28 is placed near the other axial end of the input-side rotary shaft 1a. The toroidal type continuously variable transmission 21 of this example is obtained by fixing.

Next, the assembly procedure of the ball spline 4a will be described with reference to FIG.
In order to assemble the ball spline 4a, before assembling the power roller 15 between the input side disk 2c and the output side disk 14c on the other axial end side, as shown in FIG. The input side disk 2c is moved to one end side in the axial direction (right side in FIG. 3) rather than the position in the assembly state (state before the start of operation) indicated by the chain line. In the case of this example, in the state before the input rotary shaft 1a is inserted into the input side disk 2c from the other axial end side, the disk side engagement groove 10a is inserted into the disk side engagement groove 10a. The retaining ring 11a is locked.

  Then, as shown in FIG. 5B, the balls 7a and 7a are moved into the male spline groove 5a and the female spline groove 6a while the input side disk 2c is moved to one end in the axial direction. Between the other ends in the axial direction.

  Next, as shown in FIG. 5C, the shaft side locking ring 9a is locked to the shaft side locking groove 8a. More specifically, the shaft side locking ring 9a is incorporated from the other axial end side of the input rotating shaft 1a in an elastically expanded state, and is locked in the shaft side locking groove 8a.

  Next, as shown in FIG. 3D, the input side disk 2c is moved to the other axial end side (left side in FIG. 3). Thereafter, as shown in FIG. 5E, the power roller 15 is disposed between the input side disk 2c and the output side disk 14c, and the pressing device 17a and the fixed ring 28 are assembled. . When the assembly of the toroidal continuously variable transmission 21 is completed, the disk-side locking groove 8a is formed at a position that satisfies the first requirement (α> β).

In the case of this example, the ball spline 4a is assembled through the steps as described above, but from the viewpoint of improving the assembly workability of the shaft side locking ring 9a, the following second requirement is satisfied. The formation position of the shaft side locking groove 8a is restricted.
That is, as shown in FIG. 3A, the movement amount (γ) from the assembly completion position (broken line position) of the input side disk 2c to the one end side in the axial direction is such that the shaft side locking groove 8a The shaft side locking groove 8a is formed at a position larger than the sum (δ + α) of the axial width dimension (δ) and the axial distance (α) (γ> δ + α).
The maximum value of the movement amount (γ) is allowed by the ball spline 4a (until the balls 7a and 7a ride on the portion of the male pipeline groove 5a where the groove depth is shallow), or The amount of movement until the input side disk 2c comes into contact with the output side disk 4c is determined by design.

According to the toroidal type continuously variable transmission 21 of the present example having the above-described configuration, the shaft-side locking ring 9a constituting the ball spline 4a is formed on the outer peripheral surface of the input rotary shaft 1a. It can prevent falling off from the side locking groove 8a.
That is, in this example, as a first requirement, the formation position of the shaft side locking groove 8a with respect to the input rotating shaft 1a is set to the other end in the axial direction in the inner diameter side portion 32 of the input side disk 2c. The input rotational shaft of the input side disk 2c is based on the axial distance (α) from the side surface on the side to the side surface on the other axial end side of the shaft side locking groove 8a based on the pressing force exerted by the pressing device 17a. It is formed at a position larger than the maximum displacement amount (β) toward one end in the axial direction with respect to 1a. For this reason, in the case of this example, when the toroidal type continuously variable transmission 21 is operated, the pressing force exerted by the pressing device 17a is maximized, so that the input side disk 2c with respect to the input rotating shaft 1a. Even when the amount of relative displacement toward one end in the axial direction is maximized, the state where the input side disk 2c (inner diameter side portion 32) is present around (covers) the shaft side locking ring 9a. Can be maintained. For this reason, it is possible to prevent the shaft side locking ring 9a from being exposed to the outside. Therefore, according to the toroidal type continuously variable transmission 21 of this example, it is possible to prevent the shaft side locking ring 9a from dropping even when a centrifugal force is applied as the input rotary shaft 1a rotates.

  Further, in the case of this example, as a second requirement, the formation position of the shaft side locking groove 8a with respect to the input rotating shaft 1a is set to the input side in the assembly operation of the shaft side locking ring 9a. The amount of movement (γ) from the assembly completion position of the disk 2c to one axial end side is determined by the axial width dimension (δ) of the shaft side locking groove 8a and the inner diameter side portion 32 of the input side disk 2c. The position is restricted to a position larger than the sum (δ + α) of the axial distance (α) from the side surface on the other end side in the axial direction to the side surface on the other end side in the axial direction of the shaft side locking ring 9a. Therefore, in the case of this example, as is apparent from FIGS. 3B and 3C, the entire shaft side locking groove 8a is exposed to the outside when the shaft side locking ring 9a is assembled. (Can be in a state not covered by the input side disk 2c). Accordingly, it is possible to improve the work efficiency of the work of assembling the shaft side locking ring 9a.

  The present invention is not limited to the half toroidal type as shown in the figure, and can be implemented by a full toroidal type toroidal continuously variable transmission. Further, when carrying out the present invention, as a support member for restricting the displacement of the pressing device toward the other end in the axial direction, a fixing nut (cotter) as shown in the embodiment, a loading nut, etc. Various members conventionally known can be used. In the above embodiment, the description has been given of the case where the pair of outer disks are input disks for inputting power, and the inner disks are output disks for outputting power. In some cases, on the contrary, the inner disk may be an input side disk for inputting power, and the pair of outer disks may be an output side disk for outputting power.

DESCRIPTION OF SYMBOLS 1, 1a Input rotating shaft 2a, 2b, 2c, 2d Input side disk 3, 3a Gutter 4, 4a Ball spline 5, 5a Male spline groove 6, 6a Female spline groove 7, 7a Ball 8, 8a Shaft side locking groove 9, 9a Shaft side locking ring 10, 10a Disk side locking groove 11, 11a Disk side locking ring 12 Output cylinder 13 Output gears 14a, 14b, 14c Output side disk 15 Power roller 16 Trunnion 17, 17a Pressing device 18 Gear Shaped member 19 Loading nut 20 Drive shaft 21 Toroidal type continuously variable transmission 22 Actuator case 23 Strut 24 Ball bearing 25 Radial needle bearing 28 Fixed ring (cotter)
29 Fixing groove 30 Retaining ring 31 Preload spring 32 Inner diameter side portion

Claims (1)

A rotating shaft having a male spline groove and a locking groove on the outer peripheral surface;
A first disk supported by the rotating shaft and having a female spline groove on the inner peripheral surface;
A second disk supported by the rotating shaft and disposed opposite the first disk;
A plurality of power rollers sandwiched between the first disk and the second disk in a tiltable manner;
A pressing device for pressing the first disk toward one axial end;
A plurality of balls disposed between the male spline groove and the female spline groove; and a locking ring that is locked to the locking groove and that is disposed on the other axial end side of the plurality of balls. A ball spline having
The axial distance from the side surface on the other end side in the axial direction at the inner diameter side portion of the first disk to the side surface on the other end side in the axial direction of the locking groove is based on the pressing force exerted by the pressing device. A toroidal-type continuously variable transmission that is larger than the maximum displacement amount of one disk toward one end in the axial direction with respect to the rotating shaft.

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