JP4923989B2 - Toroidal continuously variable transmission - Google Patents

Description

  The present invention relates to a toroidal continuously variable transmission that can be used for transmissions of automobiles and various industrial machines.

  For example, a double-cavity toroidal continuously variable transmission used as a transmission for an automobile is configured as shown in FIGS. As shown in FIG. 4, the input shaft 1 is rotatably supported inside the casing 50, and two input side disks 2, 2 and two output side disks 3 are disposed on the outer periphery of the input shaft 1. 3 is attached. An output gear 4 is rotatably supported on the outer periphery of the intermediate portion of the input shaft 1. Output side disks 3 and 3 are connected to cylindrical flange portions 4a and 4a provided at the center of the output gear 4 by spline coupling.

  The input shaft 1 is driven to rotate 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 the drawing. It has become. The output gear 4 is supported on a partition wall (intermediate wall) 13 formed by coupling two members via an angular ball bearing 107 and is supported in the casing 50 via the partition wall 13. Thus, while being able to rotate around the axis O of the input shaft 1, displacement in the direction of the axis O is prevented.

  The output side disks 3 and 3 are supported by needle bearings 5 and 5 interposed between the input shaft 1 so as to be rotatable about the axis O of the input shaft 1. Further, the left input side disk 2 in the figure is supported on the input shaft 1 via a ball spline 6, and the right side input disk 2 in the figure is splined to the input shaft 1. Rotates with the input shaft 1. A power roller is provided between the inner side surfaces (concave surface; also referred to as a traction surface) 2a and 2a of the input side disks 2 and 2 and the inner side surfaces (concave surface; also referred to as a traction surface) 3a and 3a of the output disks 3 and 3. 11 (see FIG. 5) is rotatably held.

  A step 2b is provided on the inner peripheral surface 2c of the input disk 2 located on the right side in FIG. 4, and the step 1b provided on the outer peripheral surface 1a of the input shaft 1 is abutted against the step 2b. At the same time, the back surface (right surface in FIG. 4) 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. Thereby, the 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 a concave surface 2a, 2a, 3a of each disk 2, 2, 3, 3. , 3a and the contact surface between the peripheral surfaces 11a and 11a of the power rollers 11 and 11 are applied with a pressing force.

  As shown in FIG. 5, which is a cross-sectional view taken along the line AA in FIG. The pair of yokes 23A and 23B is supported in the state. The pair of yokes 23A and 23B are formed in a rectangular shape by pressing or forging a metal such as steel. In order to support pivots 14 provided at both ends of the trunnion 15 to be described later in a swingable manner, circular support holes 18 are provided at the four corners of the yokes 23A and 23B, and the width direction of the yokes 23A and 23B. A circular locking hole 19 is provided at the center of the.

  The pair of yokes 23A and 23B is supported by support posts 64 and 68 formed on the inner surface of the casing 50 so as to be able to swing around the support posts 64 and 68 as fulcrums. These support posts 64 and 68 are provided so as to face the first cavity 221 and the second cavity 222, respectively, between the inner side surface 2a of the input side disk 2 and the inner side surface 3a of the output side disk 3. Yes.

  Therefore, the yokes 23 </ b> A and 23 </ b> B are supported by the support posts 64 and 68, and one end thereof faces the outer peripheral portion of the first cavity 221, and the other end faces the outer peripheral portion of the second cavity 222. is doing.

  Since the first and second cavities 221 and 222 have the same structure, only the first cavity 221 will be described below.

  As shown in FIG. 5, inside the casing 50, the first cavity 221 includes a pair of trunnions that swing around a pair of pivots (tilting axes) 14 and 14 that are twisted with respect to the input shaft 1. 15 and 15 are provided. In addition, illustration of the input shaft 1 is abbreviate | omitted in FIG. Each trunnion 15, 15 is a pair of bent portions formed at both ends in the longitudinal direction (vertical direction in FIG. 5) of the support plate portion 16 that is the main body portion in a state of being bent toward the inner side surface of the support plate portion 16. Wall portions 20 and 20 are provided. The bent wall portions 20 and 20 form concave pocket portions P for accommodating the power rollers 11 in the trunnions 15 and 15. Further, the pivot shafts 14 and 14 are concentrically provided on the outer side surfaces of the bent wall portions 20 and 20, respectively.

  A circular hole 21 is formed in the center portion of the support plate portion 16, and a base end portion (first shaft portion) 23 a of the displacement shaft 23 is supported in the circular hole 21. Then, by swinging each trunnion 15, 15 about each pivot 14, 14, the inclination angle of the displacement shaft 23 supported at the center of each trunnion 15, 15 can be adjusted. In addition, each power roller 11 is rotatably supported around the tip end portion (second shaft portion) 23b of the displacement shaft 23 protruding from the inner surface of each trunnion 15, 15. 11 is sandwiched between the input disks 2 and 2 and the output disks 3 and 3. In addition, the base end part 23a and the front-end | tip part 23b of each displacement shaft 23 and 23 are mutually eccentric.

  As described above, the pivot shafts 14 and 14 of the trunnions 15 and 15 are supported so as to be swingable with respect to the pair of yokes 23A and 23B and displaceable in the axial direction (vertical direction in FIG. 5). The trunnions 15 and 15 are restricted from moving in the horizontal direction by the yokes 23A and 23B. As described above, four circular support holes 18 are provided at the four corners of each of the yokes 23A and 23B, and the pivot shafts 14 provided at both ends of the trunnion 15 are respectively provided in the support holes 18 with radial needle bearings ( A tilting bearing 30 is supported so as to be swingable (tiltable). Further, as described above, the circular locking hole 19 is provided in the central portion of the yokes 23A and 23B in the width direction (left and right direction in FIG. 5), and the inner peripheral surface of the locking hole 19 is cylindrical. Support posts 64 and 68 are internally fitted as surfaces. That is, the upper yoke 23A is swingably supported by the spherical post 64 supported by the casing 50 via the fixing member 52, and the lower yoke 23B is supported by the spherical post 68 and the drive for supporting the same. The upper cylinder body 61 of the cylinder 31 is swingably supported.

  The displacement shafts 23 and 23 provided in the trunnions 15 and 15 are provided at positions 180 degrees opposite to the input shaft 1. Further, the direction in which the distal end portion 23b of each of the displacement shafts 23, 23 is eccentric with respect to the base end portion 23a is the same direction as the rotational direction of both the disks 2, 2, 3, 3 (in FIG. (Reverse direction). Further, the eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 1 is disposed. Accordingly, the power rollers 11 and 11 are supported so that they 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 member based on the thrust load generated by the pressing device 12, each component This displacement is absorbed without applying an 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 24 that is a thrust rolling bearing, and a thrust needle bearing, in order from the outer surface side of the power roller 11. 25. Among these, the thrust ball bearing 24 supports the rotation of each power roller 11 while supporting the load in the thrust direction applied to each power roller 11. Each of the thrust ball bearings 24 is composed of a plurality of balls 26, 26, an annular retainer 27 for holding the balls 26, 26 in a freely rolling manner, and an annular outer ring 28. ing. Further, the inner ring raceway of each thrust ball bearing 24 is formed on the outer side surface (large end surface) of each power roller 11, and the outer ring raceway is formed on the inner side surface of each outer ring 28.

  The thrust needle bearing 25 is sandwiched 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 to each outer ring 28 from the power roller 11, while the power roller 11 and the outer ring 28 swing around the base end portion 23 a of each displacement shaft 23. Allow.

  Further, drive rods (shaft portions extending from the pivot shaft) 29 and 29 are provided at one end portions (lower end portions in FIG. 5) of the trunnions 15 and 15, respectively, and outer peripheral surfaces of intermediate portions of the drive rods 29 and 29 are provided. The drive pistons (hydraulic pistons) 33, 33 are fixedly provided. Each of these drive pistons 33 and 33 is oil-tightly fitted in a drive cylinder 31 constituted by an upper cylinder body 61 and a lower cylinder body 62. The drive pistons 33 and 33 and the drive cylinder 31 constitute a drive device 32 that displaces the trunnions 15 and 15 in the axial direction of the pivots 14 and 14 of the trunnions 15 and 15.

  In the case of the toroidal continuously variable transmission configured as described above, the rotation of the drive shaft 22 is transmitted to the input side disks 2 and 2 and the input shaft 1 via the pressing device 12. Then, the rotation of the input side disks 2 and 2 is transmitted to the output side disks 3 and 3 via the pair of power rollers 11 and 11, and the rotation of the output side disks 3 and 3 is further transmitted to the output gear 4. It is taken out more.

  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 drive pistons 33 and 33 are displaced, the pair of trunnions 15 and 15 are displaced (offset) in opposite directions. For example, the power roller 11 on the left side in FIG. 5 is displaced to the lower side in the figure, and the power roller 11 on the right side in the figure is displaced to the upper side in the figure. As a result, the peripheral surfaces 11a and 11a of the power rollers 11 and 11 act on contact portions of the input side disks 2 and 2 and the inner side surfaces 2a, 2a, 3a and 3a of the output side disks 3 and 3, respectively. The direction of the tangential force changes. As the force changes, the trunnions 15 and 15 swing (tilt) in opposite directions around the pivots 14 and 14 pivotally supported by the yokes 23A and 23B.

  As a result, the contact position between the peripheral surfaces 11a and 11a of the power rollers 11 and 11 and the inner surfaces 2a and 3a changes, and the rotational speed ratio between the input shaft 1 and the output gear 4 changes. Further, when the torque transmitted between the input shaft 1 and the output gear 4 fluctuates and the amount of elastic deformation of each component changes, the power rollers 11 and 11 and the outer rings attached to the power rollers 11 and 11 will be described. 28 and 28 slightly rotate around the base end portions 23a and 23a of the displacement shafts 23 and 23, respectively. Since the thrust needle bearings 25 and 25 exist between the outer side surfaces of the outer rings 28 and 28 and the inner side surfaces of the support plate portions 16 constituting the trunnions 15 and 15, respectively, the rotation is performed smoothly. Is called. Therefore, as described above, the force for changing the inclination angle of each displacement shaft 23, 23 can be small.

  By the way, in the toroidal-type continuously variable transmission having the above-described configuration, the yokes 23A and 23B for supporting the pivot shaft 14 of the trunnion 15 so as to be swingable and displaceable in the axial direction have been conventionally known in various structural forms. In general, however, when the gear is shifted, it oscillates around the spherical posts 64 and 68 so that, for example, one trunnion 15 (for example, the right trunnion 15 in FIG. 5) is displaced upward. Accordingly, the other trunnions 15 (for example, the left trunnion 15 in FIG. 5) are displaced downward so that the movements of the pair of trunnions 15 facing each other in the same cavity are synchronized like a seesaw. It has a function of displacing in the reverse direction.

  For example, when the left drive piston 33 in FIG. 5 is displaced downward in the figure and the right drive piston 33 is displaced upward in the figure, the trunnions 15 and 15 coupled to these drive pistons 33 are mutually connected. Displacement is performed in the opposite direction (the left trunnion 15 is displaced downward and the right trunnion 15 is displaced upward), whereby the upper yoke 23A is inclined in the direction in which the right side is up. Similarly, the lower yoke 23B is inclined in the same direction as the upper yoke 23A. Conversely, when the left drive piston 33 in FIG. 5 is displaced upward in the figure and the right drive piston 33 is displaced downward in the figure, the upper yoke 23A is inclined in a direction in which the left side is upward. Similarly, the lower yoke 23B is also inclined in the same direction as the upper yoke 23A.

  The problem here is that depending on the hydraulic control of the drive piston 33, the end surface 33a of the drive piston 33 and the end surface 61a of the drive cylinder 31 (61) may come into contact with each other at the time of the above shift. That is, the drive piston 33 tilts together with the trunnion 15 and the power roller 11 while being in contact with each other. When such a situation occurs, there is a concern that the contact portion between the end faces 33a and 61a may be worn, or that a bolt for fixing the drive piston 33 may be loosened due to frictional resistance due to contact. Therefore, for example, Patent Document 1 proposes that a separate displacement regulating member that regulates displacement of the yokes 23 </ b> A and 23 </ b> B in the tilt axis direction is attached to the end of the trunnion 15.

JP 2003-222217 A

  However, separately providing a displacement regulating member and attaching it to the end of the trunnion 15 causes an increase in the number of parts and assembly man-hours and an increase in weight, which in turn causes an increase in manufacturing cost.

  The present invention has been made in view of the above circumstances, and provides an inexpensive toroidal continuously variable transmission capable of preventing the contact between the piston and the cylinder in the drive device by regulating the axial displacement of the trunnion with a simple configuration. The purpose is to do.

In order to achieve the above object, the toroidal continuously variable transmission according to claim 1 is input via an input side disk to which rotational torque is input and a power roller sandwiched between the input side disk. An output-side disk to which rotational torque is transmitted from the side disk at a predetermined speed ratio, and a pair of pivots that are concentrically provided with respect to a central axis of the input-side disk and the output-side disk And a plurality of trunnions that rotatably support the power rollers, a drive device that displaces the trunnions in the axial direction of the pivots, and tilts the pivots of the trunnions. A pair of yokes that are freely and axially displaceable and that swing with the displacement of the trunnion, and a support member that swingably supports the pair of yokes A toroidal type continuously variable transmission comprising the at least one of the support member and the yoke are regulating means is formed for restricting the swinging of the yoke due to axial displacement of the trunnion, the regulation The means comprises a stopper surface that abuts against the yoke or the support member by swinging of the yoke accompanying axial displacement of the trunnion and restricts further swinging of the yoke .

  In the first aspect of the present invention, since the restricting means for restricting the swing of the yoke accompanying the axial displacement of the trunnion is formed on at least one of the support member and the yoke, the trunnion is controlled by restricting the swing of the yoke. The axial displacement of the drive device can be restricted, thereby preventing contact between the piston and the cylinder of the drive device that displaces the trunnion in the axial direction. Further, since the restricting means is formed on the post itself and / or the yoke itself, it is not necessary to prepare a new part for displacement restriction, and therefore, it can be manufactured at low cost. Further, if the regulating means is provided on the post itself and / or the yoke itself in this way, the regulation displacement can be inspected when they are temporarily assembled outside the casing, so that the reliability of the apparatus can be ensured. .

Further , since the restricting means is formed as a post or yoke surface (stopper surface), it is possible to further simplify the manufacturing and reduce the cost.

  According to the present invention, it is possible to prevent the contact between the piston and the cylinder in the drive device by restricting the axial displacement of the trunnion with a simple and inexpensive configuration.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The feature of the present invention lies in the structure for restricting the displacement of the trunnion in the direction of the tilt axis, and the other configurations and functions are the same as the conventional configurations and functions described above. Only the characteristic part of FIG. 5 will be referred to, and other parts will be simply described with the same reference numerals as those in FIGS.

  As shown in FIGS. 1 to 3, the toroidal continuously variable transmission according to the embodiment of the present invention includes a support member (post member) formed integrally with support posts 64 and 68 of the conventional structure shown in FIG. 5. ) 300, and the support member 300 supports the pair of yokes 23 </ b> A and 23 </ b> B through the bearing 302 so as to be swingable. The support member 300 has a large-diameter main body shaft portion 300a extending between the yokes 23A and 23B, and is formed at both ends of the main body shaft portion 300a, and the circular locking holes 19 of the yokes 23A and 23B via bearings 302. The step portion between the small diameter shaft portion 300b and the main body shaft portion 300a is formed as a restriction means for restricting the swing of the yokes 23A and 23B due to the axial displacement of the trunnion 15. ing. In particular, in the present embodiment, the restricting means is formed as an inclined stopper surface 310 that connects the outer peripheral surface of the small-diameter shaft portion 300b and the outer peripheral surface of the main body shaft portion 300a.

  In such a configuration, for example, when the left drive piston 33 shown in FIG. 5 is displaced upward in the figure and the right drive piston 33 is displaced downward in the figure, the pistons are coupled to the drive pistons 33. 1 are displaced (offset) in opposite directions (the left trunnion 15 is displaced upward and the right trunnion 15 is displaced downward), whereby the yokes 23A and 23B are shown in FIG. From the neutral state to the state shown in FIG. That is, the upper yoke 23A is inclined in the direction in which the left side is upward, and similarly, the lower yoke 23B is also inclined in the same direction as the upper yoke 23A. At this time, as shown in an enlarged view in FIG. 3, the stopper surface 310 formed on the support member 300 and the yoke 23A (23B) come into contact with each other, and further swinging of the yoke is restricted (the yoke (Doesn't tilt any more) That is, the trunnion 15 cannot be offset any more. Therefore, if the dimensions of each part are set so that a gap is still formed between the drive piston 33 and the drive cylinder 31 in this restricted state, the contact between the drive piston 33 and the drive cylinder 31 during shifting is prevented. it can.

  As described above, according to the present embodiment, the support member 300 is formed with the restricting means (stopper surface 310) that restricts the swing of the yokes 23A and 23B due to the axial displacement of the trunnion 15. The axial displacement of the trunnion 15 can be restricted by the swing restriction of 23A and 23B, thereby preventing contact between the drive piston 33 and the drive cylinder 31 of the drive device 32 that displaces the trunnion 15 in the axial direction. It becomes possible to do. Further, since the restricting means is formed on the support member 300 itself, it is not necessary to prepare a new part for displacement restriction, and therefore it can be manufactured at low cost. In particular, if the restricting means is formed as a surface (stopper surface) of the support member 300 as in the present embodiment, it is possible to further facilitate the simplification of manufacturing and cost reduction. Further, if the restricting means is provided on the support member 300 as described above, the displacement restriction by the restricting means can be inspected when the variator portion is temporarily assembled outside the casing 50, so that the reliability of the apparatus is ensured. Can do.

  Needless to say, the present invention is not limited to the above-described embodiments, and can be variously modified without departing from the scope of the invention. For example, in the embodiment described above, the restricting means is formed on the support member 300, but the restricting means may be formed on the yokes 23A and 23B, or on both the yokes 23A and 23B and the support member 300. It may be formed. In the above-described embodiment, the restricting means is formed as a surface (stopper surface) of the support member 300. However, the restricting means is not limited to the surface, and contacts the yokes 23A and 23B or the support member 300 so that the yoke is fixed. Other forms such as protrusions may be used as long as the swinging can be restricted.

  The present invention can be applied to various half-toroidal continuously variable transmissions such as a single cavity type and a double cavity type.

It is principal part sectional drawing (at the time of a yoke neutral) of the toroidal type continuously variable transmission which concerns on embodiment of this invention. It is principal part sectional drawing (at the time of yoke swing) of the toroidal type continuously variable transmission which concerns on embodiment of this invention. It is the A section enlarged view of FIG. It is sectional drawing which shows an example of the specific structure of the toroidal type continuously variable transmission conventionally known. It is sectional drawing which follows the AA line of FIG.

Explanation of symbols

2 input side disk 3 output side disk 11 power roller 14 pivot 15 trunnion 23A, 23B yoke 32 drive device 300 support member 310 stopper surface (regulating means)

Claims (1)

An input side disk to which rotational torque is input, an output side disk to which rotational torque is transmitted at a predetermined speed ratio from the input side disk via a power roller sandwiched between the input side disk, and the input side A plurality of trunnions that are twisted with respect to the central axis of the disk and the output-side disk and tilt about a pair of pivots that are concentrically provided to each other and that rotatably support the power rollers; A pair of driving devices for displacing each trunnion in the axial direction of the pivot, and a pair of pivots for supporting the pivots of each trunnion so as to be tiltable and axially displaceable, and swinging by the displacement of the trunnion In a toroidal continuously variable transmission including a yoke and a support member that supports a pair of yokes so as to be swingable,
At least one of the support member and the yoke is formed with a restricting means for restricting the swing of the yoke accompanying the axial displacement of the trunnion .
The restricting means is a toroidal type comprising a stopper surface that abuts against the yoke or the support member and restricts further swinging of the yoke by swinging of the yoke accompanying axial displacement of the trunnion Continuously variable transmission.

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