JP2008261469A - Toroidal continuously variable transmission - Google Patents

Abstract

[PROBLEMS] To secure sufficient strength at a pivotal and bent wall portion of trunnions and their connecting portions at a low cost without increasing the size of trunnions, without inhibiting the rotation of tilting bearings, and reducing stress. A toroidal continuously variable transmission capable of achieving the above is provided.
In this toroidal continuously variable transmission, a collar member 200 is inserted in a fitted state so as to cover these connecting portions from a pivot 14 of a trunnion 15 to a bent wall portion 20. The collar member 200 is preferably set to have a surface hardness of HRC 55 or more, and a first extension portion 200a extending on the pivot 14 of the trunnion 15 and a second extension portion extending on the bent wall portion 20. Extending portion 200b.
[Selection] Figure 1

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. 6, an 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. 7) is rotatably held.

  A step 2b is provided on the inner peripheral surface 2c of the input side disk 2 located on the right side in FIG. 6, 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. 6) of the input side disk 2 is abutted against a loading nut 9 screwed into a screw 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. 7 which is a cross-sectional view taken along the line AA in FIG. 6, both the disks 3 and 3 are sandwiched from both sides inside the casing 50 and laterally to the output side disks 3 and 3. 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. 7, inside the casing 50, the first cavity 221 includes a pair of trunnions that swing about a pair of pivots 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 in a state in which the trunnions 15, 15 are bent at the inner side of the support plate 16 at both ends in the longitudinal direction (vertical direction in FIG. 7) of the support plate 16. Wall portions 20 and 20 are provided. Then, the trunnions 15 and 15 form a pocket portion P that is a concave accommodation space for accommodating the power roller 11 by the bent wall portions 20 and 20. 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 central portion of the support plate portion 16, and a base end portion (first shaft portion) 23 a of a displacement shaft 23 as a support shaft 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.

  Further, 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. 7). 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 part of the yokes 23A and 23B in the width direction (left and right direction in FIG. 6), 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 such thrust ball bearings 24 includes a plurality of balls (rolling elements) 26, 26, an annular retainer 27 that holds the balls 26, 26 in a freely rolling manner, and an annular outer ring 28. It consists of and. 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, driving rods (shaft portions extending from the pivot shaft) 29 and 29 are respectively provided at one end portions (lower end portions in FIG. 7) of the trunnions 15 and 15, and outer peripheral surfaces of intermediate portions of the driving rods 29 and 29. 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 of FIG. 7 is displaced downward in the figure, and the power roller 11 on the right side of FIG. 7 is displaced upward 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 positions of the peripheral surfaces (traction surfaces) 11a and 11a of the power rollers 11 and 11 and the inner surfaces 2a and 3a change, and the rotational speed ratio between the input shaft 1 and the output gear 4 is changed. Change. 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.

  As described above, the toroidal-type continuously variable transmission transmits power by the power roller 11 sandwiched between the input side disk 2 and the output side disk 3. A large pressing force is required at the contact point with the power roller 11. Therefore, a large load also acts on the trunnion 15 that supports the power roller 11, and due to the load, the trunnion 15 is supported at two upper and lower points (portions supported by the upper and lower tilt bearings 30). For this reason, the portion that holds the power roller 11 is bent. As described above, the toroidal-type continuously variable transmission often moves the trunnion 15 up and down for shifting the position of the contact point. Therefore, if the trunnion 15 is bent, the power roller 11 and the disks 2 and 3 As a result, the rigidity of the trunnion 15 affects the controllability of the shift control.

  In relation to this, Patent Document 1 proposes forming the trunnion 15 in a specific shape that can ensure sufficient rigidity (so that the trunnin 15 does not bend).

  Further, as described above, since the trunnion 15 is supported at two points, the connection between the pivot shaft 14 of the trunnion 15 (corresponding to the neck portion of the trunnion 15) and the bent wall portion 20 (corresponding to the shoulder portion of the trunnion 15). The part (R-shaped part) becomes a high stress part. Therefore, in patent document 2, stress relaxation is aimed at by devising the connection shape of this connection part.

Moreover, since the pivot 14 of the trunnion 15 serves as a transfer surface of the tilt bearing 30, sufficient hardness is required. For this reason, Patent Document 2 and Patent Document 3 propose to form the trunnion 15 with a predetermined hardness. Furthermore, in the technique disclosed in Patent Document 4, the connecting portion forms a continuous metal flow during forging in order to prevent the strength of the connecting portion from decreasing. It is also known to quench the pivot 14 in order to ensure the strength of the pivot 14 of the trunnion 15.

  Further, the bent wall portion 20 of the trunnion generally has a structure in which the yokes 23A and 23B are in contact with each other. For this reason, attempts have been made to reduce the friction during tilting by providing protrusions on the yoke 23A to reduce the contact surface with the trunnion 15 (see, for example, Patent Document 5). In addition, in order to secure the strength of the contact surface with the yoke 23A, it has been proposed to quench the contact surface to reduce wear due to friction (see Patent Document 6). Further, in order to avoid direct contact between the trunnion 15 and the yoke 23A, a structure is proposed in which a plate is inserted between the trunnion 15 and the tilt bearing 30 so that the plate and the yoke 23A are in contact with each other. (See Patent Document 7).

  Conventionally, as disclosed in Patent Document 8, it is proposed to press-fit a collar into the pivot 14 of the trunnion 15 made of a lightweight alloy in order to ensure wear resistance while reducing the weight of the trunnion 15. Has been.

JP-A-7-229546 JP-A-11-201250 Japanese Patent No. 3733713 JP 2000-230615 A JP 7-174201 A JP 2004-286053 A JP 2005-121045 A Japanese Utility Model Publication No. 2-60753

  However, as disclosed in Patent Document 1 and Patent Document 2, if the trunnion 15 is processed into a predetermined shape in order to prevent the trunnion 15 from being bent or to relieve stress, there arises a problem that the processing cost increases. In addition, special processing as disclosed in Patent Documents 2 to 4 results in an increase in manufacturing cost.

  Further, if the pivot 14 is quenched in order to ensure the strength of the pivot 14, grinding must be performed after quenching, in which case the pivot 14 (neck) and the bent wall 20 (shoulder) There is a possibility that a step is generated in the vicinity of the R-shaped portion of the connecting portion between the two, and R (the radius of curvature of the connecting portion) is reduced. Therefore, it is necessary to increase the margin value in order to prevent the R-shaped portion (arc-shaped portion) having a small curvature radius with such a step from being damaged. However, if the margin value is increased in this way, the trunnion itself inevitably increases in size. Moreover, when induction hardening is performed, the cost increases.

  Further, as disclosed in Patent Document 5, if a projection is provided on the yoke 23A in order to reduce the contact area between the yoke 23A and the trunnion 15, the processing cost increases and the yoke 23A becomes expensive. . Furthermore, if the contact surface is quenched as disclosed in Patent Document 6 in order to ensure the strength of the contact surface with the yoke 23A, a finishing process or the like is required, resulting in further cost increase. Further, as disclosed in Patent Document 7, in the structure in which the plate is inserted between the trunnion 15 and the tilt bearing 30, the position of the plate with respect to the trunnion 15 is not determined. Therefore, when the yoke 23A does not hit the plate, the plate may move, and the rolling of the tilt bearing 30 may be hindered. Further, even when the plate and the yoke 23A are brought into contact with each other, resistance becomes large when the contact area is large, so that it is necessary to provide a protrusion on the yoke 23A.

  Further, in the structure disclosed in Patent Document 8, since the collar is press-fitted only into the pivot 14 of the trunnion 15 and the connecting portion between the pivot 14 and the bent wall portion 20 is substantially perpendicular, the stress at the connecting portion. Reduction cannot be achieved.

  The present invention has been made in view of the above circumstances, and without increasing the size of the trunnion, without inhibiting the rotation of the tilt bearing, and at a low cost, the pivot shaft and the bent wall portion of the trunnion and their connection. It is an object of the present invention to provide a toroidal continuously variable transmission that can secure sufficient strength at a portion and can reduce stress.

  In order to achieve the above object, the toroidal continuously variable transmission according to claim 1 is characterized in that an input side disk and an output that are supported concentrically and rotatably with their respective inner surfaces facing each other. A side disk, a power roller sandwiched between the input side disk and the output side disk, a twisted position with respect to the rotation center axis of the input side disk and the output side disk, and concentrically with each other A trunnion that swings about a pair of pivots provided and rotatably supports the power rollers, and the trunnion is supported at both ends in the longitudinal direction of a support plate that is a main body of the trunnion. A pair of bent wall portions formed in a state of being bent on the inner surface side of the plate portion, and a concave shape for accommodating the power roller by these bent wall portions In the toroidal continuously variable transmission in which the accommodation space is formed and the pair of pivots are provided concentrically with each other on the outer surface of each bent wall, the trunnion extends from the pivot to the bent wall. It is provided with the collar member inserted in the covering state so that a connection part may be covered.

  In the invention described in claim 1, since the collar member is inserted in a fitted state so as to cover these connecting portions from the pivot shaft of the trunnion to the bent wall portion, the pivot shaft and the bent wall portion of the trunnion and these It is possible to secure a sufficient strength at the connecting portion and to reduce the stress. Therefore, it is not necessary to perform heat treatment on the trunnion body, and therefore the cost can be reduced. In addition, since it is not necessary to perform a grinding process in accordance with the elimination of the heat treatment, it is possible to eliminate the collapse of the curvature shape of the connecting portion and the step in the vicinity thereof. Therefore, it is not necessary to consider a design value (margin value) considering such a shape, and as a result, the trunnion can be downsized. Further, since it is not necessary to adopt a structure in which a plate is inserted between the trunnion and its tilting bearing as in the prior art, there is no possibility of inhibiting the rotation of the tilting bearing.

  According to a second aspect of the present invention, in the invention described in the first aspect, the surface hardness of the collar member is HRC55 or more.

  In the invention described in claim 2, since the hardness of the collar member is increased, a further sufficient strength can be secured at the pivot shaft and the bent wall portion of the trunnion and the connecting portions thereof.

  According to a third aspect of the present invention, there is provided the toroidal continuously variable transmission according to the first or second aspect, wherein the collar member extends on a pivot of the trunnion. And a second extension part extending on the bent wall part, and the second extension part comes into contact with a yoke for swingably supporting the pivot shaft, and a second extension part. A projecting portion that forms a predetermined gap is formed between the extending portion and the yoke.

  In the invention described in claim 3, since the contact between the yoke and the trunnion is prevented by the protruding portion of the collar member, it is not necessary to newly form the protruding portion on the yoke, and an inexpensive yoke is provided. Can do. In addition, since it is not necessary to increase the height of the protrusion more than necessary, the continuously variable transmission can be reduced in size.

  According to a fourth aspect of the present invention, in the invention described in the third aspect, the protruding portion is formed by bending the collar member.

  In the invention described in claim 4, the collar member itself can be manufactured at low cost by forming the protruding portion by bending.

  According to a fifth aspect of the present invention, in the invention described in any one of the first to fourth aspects, the collar member is press-fitted into the trunnion. .

  In the invention described in claim 5, since the collar member is press-fitted into the trunnion, the rotation of the collar member with respect to the trunnion is prevented, and the position of the collar member with respect to the trunnion can be clearly defined.

  According to a sixth aspect of the present invention, there is provided the toroidal continuously variable transmission according to any one of the first to fourth aspects, wherein the collar member includes a locking portion that is locked to the trunnion. It is characterized by having.

  In the invention described in claim 6, the collar member is positioned with respect to the trunnion by the engaging portion, and the rotation of the collar member with respect to the trunnion can be prevented.

  According to a seventh aspect of the present invention, in the invention described in the sixth aspect, the locking portion functions as a stopper for restricting the tilting of the pivot within a predetermined range. It is characterized by that.

  In the invention described in claim 7, since the locking portion also has a function as a stopper for restricting the tilting of the pivot within a predetermined range, it is not necessary to newly provide a stopper, It is possible to reduce the number of parts and thus the cost.

  According to the present invention, since the collar member is inserted so as to cover these connecting portions from the pivot axis of the trunnion to the bent wall portion, the rotation of the tilt bearing is inhibited without increasing the size of the trunnion. Therefore, sufficient strength can be ensured and stress can be reduced at the pivot shaft and the bent wall portion of the trunnion and the connecting portions thereof at a low cost.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The feature of the present invention lies in the form of the collar member attached to the trunnion, and other configurations and operations are the same as those of the conventional configuration and operations described above. Therefore, only the features of the present invention will be described below. Reference will be made to the other parts, and the same reference numerals as those in FIGS.

  1 and 2 show a first embodiment of the present invention. As illustrated, in this embodiment, the collar member 200 is inserted in a fitted state on both sides of the trunnion 15 so as to cover these connecting portions from the pivot 14 to the bent wall portion 20. The collar member 200 has a surface hardness set to HRC 55 or more, and extends on the cylindrical first extending portion 200 a extending on the columnar pivot 14 of the trunnion 15 and the bent wall portion 20. The cross section which consists of the 2nd annular extension part 200b which exists and the connection part 200c which has the predetermined curvature radius which connects these smoothly has a substantially L shape. In particular, in this embodiment, the collar member 200 is press-fitted into the trunnion 15, and the second extending portion 200b is inserted between the outer surface 20a of the bent wall portion 20 and the yokes 23A and 23B. In close contact with the outer surface 20a.

  Further, in the present embodiment, the protruding portions 230 that protrude from the outer surface 20a of the bent wall portion 20 are formed on the side surfaces 23Aa and 23Ba of the yokes 23A and 23B that face the bent wall portion 20. The protrusion 230 forms a predetermined gap between the trunnion 15 and the yokes 23 </ b> A and 23 </ b> B to prevent contact between the trunnion 15 and the bent wall portion 20. The protruding portion 230 is in contact with the second extending portion 200 b of the collar member 200.

  As described above, in this embodiment, since the collar member 200 is inserted in a fitted state so as to cover these connecting portions from the pivot 14 of the trunnion 15 to the bent wall portion 20, the pivot 14 and the bent of the trunnion 15 are bent. Sufficient strength can be secured at the wall portion 20 and these connecting portions, and stress can be reduced (particularly at the high stress portion Q of the connecting portion where the connecting portion 200c is located). Therefore, it is not necessary to perform heat treatment on the trunnion body, and therefore the cost can be reduced. In addition, since it is not necessary to perform the grinding process in accordance with the elimination of the heat treatment, it is possible to eliminate the collapse of the curvature shape of the connecting portion and the step in the vicinity thereof. Therefore, it is not necessary to consider a design value (margin value) considering such a shape, and as a result, the trunnion 15 can be downsized. In addition, since it is not necessary to adopt a structure in which a plate is inserted between the trunnion 15 and the tilt bearing 30 as in the prior art, there is no possibility of inhibiting the rotation of the tilt bearing 30.

  Further, in the present embodiment, since the surface hardness of the collar member 200 is set to HRC 55 or higher, it is possible to secure further sufficient strength at the pivot 14 and the bent wall portion 20 of the trunnion 15 and the connecting portions thereof.

  In this embodiment, since the collar member 200 is press-fitted into the trunnion 15, the rotation of the collar member 200 with respect to the trunnion 15 is prevented, and the position of the collar member 200 with respect to the trunnion 15 can be clearly defined.

  FIG. 3 shows a second embodiment of the present invention. In the present embodiment, the protruding portion 200d that contacts the yokes 23A and 23B and forms a predetermined gap between the second extending portion 200b and the yokes 23A and 23B is provided at the tip of the second extending portion 200b. A part is formed by projecting toward the yokes 23A and 23B.

  When such a protrusion 200d is provided, contact between the yokes 23A and 23B and the trunnion 15 is prevented by the protrusion 200d. Therefore, a protrusion 230 as in the first embodiment is newly formed on the yokes 23A and 23B. Therefore, the inexpensive yokes 23A and 23B can be provided. In addition, since it is not necessary to increase the height of the protrusion more than necessary, the continuously variable transmission can be reduced in size.

  FIG. 4 shows a third embodiment of the present invention. In the present embodiment, the protruding portion 200d is formed by bending a part of the collar member 200 near the tip of the second extending portion 200b in a ring shape toward the yokes 23A and 23B. Thus, if the protruding portion 200d is formed by being bent, the collar member 200 itself can be manufactured at low cost.

  FIG. 5 shows a fourth embodiment of the present invention. In this embodiment, in addition to the configuration of the third embodiment, the collar member 200 is provided with a locking portion 200e that is locked to the trunnion 15. The locking portion 200e is formed by projecting a part of the tip of the second extending portion 200b of the collar member 200 to the side opposite to the yokes 23A and 23B. In particular, in this embodiment, the locking portion 200e functions as a stopper for restricting the tilt of the pivot 14 within a predetermined range.

  As described above, when the locking member 200e that is locked to the trunnion 15 is provided in the collar member 200, the collar member 200 is positioned with respect to the trunnion 15 by the locking portion 200e, and the rotation of the collar member 200 with respect to the trunnion 15 is prevented. it can. Further, if the locking portion 200e functions as a stopper for restricting the tilting of the pivot 14 within a predetermined range, it is not necessary to newly provide a stopper, thereby reducing the number of parts and thus the cost. Can do.

  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 of the 1st Embodiment of this invention. It is an expanded sectional view which shows the principal part of the structure of FIG. It is principal part sectional drawing of the 2nd Embodiment of this invention. It is principal part sectional drawing of the 3rd Embodiment of this invention. It is principal part sectional drawing of the 4th Embodiment of this invention. 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 Axis 15 Trunnion 20 Bending wall portion 23A, 23B Yoke 200 Collar member 200a First extending portion 200b Second extending portion 200d Protruding portion 200e Locking portion

Claims (7)

An input side disk and an output side disk that are supported concentrically and rotatably with their inner side surfaces facing each other, and a power roller sandwiched between the input side disk and the output side disk And swing about a pair of pivots concentrically with each other at a twisted position with respect to the rotation center axis of the input side disk and the output side disk, and the power rollers can be rotated freely. A trunnion that supports the trunnion, and the trunnion has a pair of bent wall portions formed in a state of being bent toward the inner surface side of the support plate portion at both ends in the longitudinal direction of the support plate portion that is the main body portion, A concave housing space for housing the power roller is formed by these bent wall portions, and the pair of the bent wall portions is formed on the outer surface of each bent wall portion. In the toroidal type continuously variable transmission comprising a shaft is provided concentrically with each other,
A toroidal-type continuously variable transmission comprising a collar member inserted in a fitted state so as to cover these connecting portions from the pivot shaft of the trunnion to the bent wall portion.   The toroidal continuously variable transmission according to claim 1, wherein the surface hardness of the collar member is HRC55 or more.   The collar member has a first extension portion extending on the pivot axis of the trunnion and a second extension portion extending on the bent wall portion, and the second extension portion includes 2. A protruding portion that forms a predetermined gap between the second extending portion and the yoke by being in contact with a yoke that swingably supports the pivot shaft. The toroidal continuously variable transmission according to claim 2.   The toroidal continuously variable transmission according to claim 3, wherein the protrusion is formed by bending the collar member.   The toroidal continuously variable transmission according to any one of claims 1 to 4, wherein the collar member is press-fitted into the trunnion.   The toroidal continuously variable transmission according to any one of claims 1 to 4, wherein the collar member has a locking portion that is locked to the trunnion.   The toroidal continuously variable transmission according to claim 6, wherein the locking portion functions as a stopper for restricting the tilting of the pivot within a predetermined range.

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