JP5819240B2 - Toroidal continuously variable transmission mechanism - Google Patents

Description

  The present invention includes an input disk supported so as not to rotate relative to the input shaft and slidable in the axial direction, an output disk supported relative to the input shaft and slidable in the axial direction, the input disk, and the input disk A pair of power rollers sandwiched between the output disks, urging means for urging the input disk toward the output disk with respect to the input shaft, and the input shaft at the position facing the urging means on the casing The present invention relates to a toroidal-type continuously variable transmission mechanism that includes a first bearing that is rotatably supported and a second bearing that rotatably supports the output disk on the casing.

  A power roller is provided by an input disk 2 supported on the left side of the input shaft 6 so as not to be relatively rotatable and slidable in the axial direction, and an output disk 3 supported on the right side of the input shaft 6 so as to be relatively rotatable and slidable in the axial direction. 5, the input disk 2 is urged to the right side toward the output disk 3 by the urging means (cam roller) 12 provided at the left end of the input shaft 6, and the right end of the input shaft 6 is input to the right side surface of the casing 1. A toroidal-type continuously variable transmission mechanism that is supported via a bearing 13 and that supports the right end of the output disk 3 on the left side surface of the casing 1 via an output bearing 14 is known from Patent Document 1 below.

Japanese Patent Laid-Open No. 10-47448

  By the way, since the input disk and output disk of such a toroidal-type continuously variable transmission mechanism receive a large reaction force from the power roller, the reaction force causes the input disk and the output disk to bend away from each other. There is a risk of loss in power transmission efficiency. To avoid this loss of power transmission efficiency, it is sufficient to increase the rigidity of the input disk and output disk, but this will cause a new problem that the weight of the input disk and output disk will increase. It is desirable to increase the stiffness of the input and output disks while minimizing the increase.

  The present invention has been made in view of the above circumstances, and an object thereof is to increase the rigidity of an input disk and an output disk of a toroidal-type continuously variable transmission mechanism while minimizing an increase in weight.

  In order to achieve the above object, according to the first aspect of the present invention, an input disk supported so as not to be rotatable relative to the input shaft and slidable in the axial direction, and capable of relative rotation to the input shaft and axial direction. An output disk supported slidably, a pair of power rollers sandwiched between the input disk and the output disk, and a biasing means for biasing the input disk toward the output disk with respect to the input shaft A toroidal-type continuously variable transmission mechanism comprising: a first bearing that rotatably supports the input shaft on the casing at a position facing the biasing means; and a second bearing that rotatably supports the output disk on the casing. The first bearing includes a first inner ring, a first intermediate ring, and a first outer ring that are sequentially arranged from the radially inner side to the outer side, the first inner ring, the first outer ring, The intermediate ring and the first outer ring are relatively rotatable via a ball, and the second bearing includes a second inner ring, a second intermediate ring, and a second outer ring that are sequentially arranged from the radially inner side to the outer side, The second inner ring, the second intermediate ring, and the second outer ring are relatively rotatable via a ball, and the first inner ring and the first outer ring are supported by one of the input shaft and the casing, One intermediate wheel is supported by the other of the input shaft and the casing, the second inner ring and the second outer ring are supported by one of the output disk and the casing, and the second intermediate wheel is supported by the output disk and the casing. A toroidal-type continuously variable transmission mechanism that is supported by the other of the two is proposed.

  According to the invention described in claim 2, in addition to the configuration of claim 1, the distance from the axis of the input shaft to the first inner ring and the distance to the second inner ring are the same first distance. And the distance from the axis to the first outer ring and the distance from the second outer ring are the same second distance, and the contact point of the input disk and the output disk when the power roller is tilted A toroidal-type continuously variable transmission mechanism is proposed in which the distance from the axis is larger than the first distance and smaller than the second distance.

  The first thrust bearing 26A of the embodiment corresponds to the first bearing of the present invention, and the second thrust bearing 26B of the embodiment corresponds to the second bearing of the present invention, and the first support member of the embodiment. 45 and the second support member 46 correspond to the casing of the present invention.

  According to the configuration of the first aspect, when the input disk is urged by the urging means and the power roller is pressed against the output disk so that the power roller does not slip with respect to the input disk and the output disk, the reaction received from the power roller. With force, the input and output disks are biased away from each other. The reaction force received by the input disk from the power roller is transmitted to the casing via the biasing means, the input shaft and the first bearing, and the reaction force received by the output disk from the power roller is transmitted to the casing via the second bearing.

  At this time, the first bearing includes a first inner ring, a first intermediate ring, and a first outer ring that can rotate relative to each other via a ball, and the first inner ring and the first outer ring are supported by one of the input shaft and the casing, Since the first intermediate wheel is supported by the other of the input shaft and the casing, the input disk can uniformly disperse the reaction force received from the power roller in the radial direction and transmit it to the casing, thereby increasing the rigidity. . The second bearing includes a second inner ring, a second intermediate ring, and a second outer ring that can rotate relative to each other via a ball. The second inner ring and the second outer ring are supported by one of the output disk and the casing, Since the intermediate wheel is supported by the other of the output disk and the casing, the output disk can uniformly disperse the reaction force received from the power roller in the radial direction and transmit it to the casing, thereby increasing the rigidity. As a result, only a slight increase in the weight of the first and second bearings can effectively increase the rigidity of the input disk and the output disk and improve the power transmission efficiency with the power roller. Durability can be prevented by preventing an unbalanced load from being applied to the first bearing and the second bearing.

  According to the configuration of claim 2, the distance from the axis of the input shaft to the first inner ring and the distance from the second inner ring are the same first distance, and the distance from the axis of the input shaft to the first outer ring and the first The distance to the two outer rings is the same second distance, and when the power roller is tilted, the distance from the axis of the input shaft at the contact point to the input disk and the output disk is larger than the first distance and from the second distance. Therefore, even if the position of the contact point between the input disk and the output disk changes due to the tilting of the power roller with the change of the gear ratio, the contact point is radially inward of the first and second inner rings. The protrusion of the input disk and the output disk can be more effectively enhanced without protruding or protruding outward in the radial direction from the first and second outer rings.

The skeleton figure of the transmission provided with the toroidal type continuously variable transmission mechanism. (First embodiment) The perspective view of a toroidal type continuously variable transmission mechanism. (First embodiment) FIG. 3 is a sectional view taken along line 3-3 in FIG. 2. (First embodiment) FIG. 4 is a sectional view taken along line 4-4 of FIG. (First embodiment) FIG. 5 is a sectional view taken along line 5-5 of FIG. (First embodiment) The figure corresponding to the said FIG. (Second Embodiment)

First embodiment

  Hereinafter, a first embodiment of the present invention will be described with reference to FIGS.

  As shown in FIG. 1, a single cavity type toroidal continuously variable transmission mechanism T provided in an automobile transmission includes an input shaft 13 connected to a crankshaft 11 of an engine E via a damper 12. A substantially cone-shaped input disk 14 is supported on the input shaft 13 so as not to be relatively rotatable and slidable in the axial direction, and a substantially cone-shaped output disk 15 is supported so as to be relatively rotatable and slidable in the axial direction. A pair of power rollers 18, 18 supported so as to be rotatable about the roller shaft 16 and tilted about the trunnion shafts 17, 17 abut on the input disk 14 and the output disk 15. The opposing surfaces of the input disk 14 and the output disk 15 are formed of toroidal curved surfaces, and when the power rollers 18 and 18 tilt around the trunnion shafts 17 and 17, the power rollers 18 and 18 against the input disk 14 and the output disk 15 The contact point changes.

  A cylinder 19 formed integrally with the outer periphery of the input disk 14, a piston 20 fixed to the outer periphery of the input shaft 13 and slidably fitted to the inner peripheral surface of the cylinder 19, and a partition between the cylinder 19 and the piston 20. The urging means 22 is constituted by the oil chamber 21. Accordingly, by supplying hydraulic pressure to the oil chamber 21 and urging the input disk 14 toward the output disk 15, the power rollers 18 and 18 can be pressed against the input disk 14 and the output disk 15 so as not to slip. it can.

  An output shaft 23 integrally connected to the output disk 15 is fitted to the outer periphery of the input shaft 13 so as to be relatively rotatable, and a first gear 24 and an output shaft 23 supported on the outer periphery of the input shaft 13 so as to be relatively rotatable. Can be coupled via the clutch 25. The shaft end of the input shaft 13 is supported via a first thrust bearing 26A made of an angular ball bearing, and the output disk 15 is supported via a second thrust bearing 26B made of an angular ball bearing and fixed to the intermediate shaft 27. The second gear 28 meshes with the first gear 24, and the final drive gear 29 fixed to the intermediate shaft 27 meshes with a final driven gear 31 provided in the case of the differential gear 30. Drive wheels W are connected to drive shafts 32 extending from the differential gear 30 to the left and right.

  Next, the structure of the toroidal type continuously variable transmission mechanism T will be described in more detail with reference to FIGS.

  The toroidal-type continuously variable transmission mechanism T includes an upper valve plate 42 and a lower valve plate 43 that are vertically overlapped to form the base member 41, and the lower end of the link post 44 is located at the center of the upper valve plate 42. While being fixed by press-fitting, the lower ends of the first support member 45 and the second support member 46 are fixed so as to sandwich the link post 44. That is, a pair of lower fixing portions 45a, 45a are formed at the lower end of the first support member 45, and bolts 47, 47 penetrating the lower fixing portions 45a, 45a in the horizontal direction project on the upper valve plate 42. The first support member 45 is fixed to the upper valve plate 42 by being screwed into the fixing portions 42 a and 42 a provided. A pair of lower fixing portions 46a, 46a are formed at the lower end of the second support member 46, and bolts 48, 48 penetrating the base member 41 from below to above are screwed into the lower fixing portions 46a, 46a. Thus, the second support member 46 is fixed to the upper valve plate 42.

  A plate-like connecting member 49 is horizontally disposed above the base member 41, and is connected to the link post 44 by screwing a bolt 50 penetrating from the top to the bottom with the upper end of the link post 44. The member 49 is fixed. The connecting member 49 includes a pair of cylindrical fixing portions 49a and 49a. The pair of upper fixing portions 45b and 45b provided on the first support member 45 and the pair of upper fixing portions provided on the second support member 46. The portions 46b and 46b are fixed to both ends of the pair of fixing portions 49a and 49a of the connecting member 49 with bolts 51 and 51 and bolts 52 and 52, respectively. Accordingly, the base member 41, the first support member 45, the second support member 46, the link post 44, and the connecting member 49 constitute a strong box-shaped frame.

  Circular openings 45c and 46c are respectively formed in the central portions of the first support member 45 and the second support member 46, and the input shaft 13 is disposed so as to penetrate these openings 45c and 46c. The large-diameter portion 13a on one end side of the input shaft 13 is rotatably supported by the opening 45c of the first support member 45 by the first thrust bearing 26A. The disc-shaped piston 20 is press-fitted to the outer periphery of the input shaft 13 so as to abut on the large-diameter portion 13a, and is supported on the input shaft 13 by a ball spline 53 so as not to be relatively rotatable and to be slidable in the axial direction. The cylinder 19 formed integrally with the outer periphery of the input disk 14 is slidably fitted to the outer periphery of the piston 20.

  On the other hand, the output disk 15 is supported on the outer periphery of the input shaft 13 via a needle bearing 54 so as to be relatively rotatable and slidable in the axial direction, and the cylindrical shaft portion 15a of the output disk 15 is supported by the second thrust bearing. It is rotatably supported by the opening 46c of the second support member 46 through 26B. The cylindrical output shaft 23 is fitted to the outer periphery of the input shaft 13 projecting outward from the second support member 46 so as to be relatively rotatable, and is splined to the shaft portion 15 a of the output disk 15.

  The input shaft 13 sandwiched between the input disk 14 and the output disk 15 passes through an opening 44 a formed at the center of the link post 44, and a thrust bearing 72 is disposed between the opening 44 a and the output disk 15. .

  A pair of trunnions 55 and 55 that respectively support the pair of power rollers 18 and 18 are arranged so as to sandwich the input shaft 13, and piston rods 57 and 57 of left and right hydraulic actuators 56 and 56 provided on the base member 41 are arranged. The trunnions 55 are formed integrally with the lower ends of the 55, respectively. The hydraulic actuator 56 is a cylinder 58 formed between the upper valve plate 42 and the lower valve plate 43 of the base member 41, and is slidably fitted to the cylinder 58 and fitted to the outer periphery of the piston rod 57 so as to be relatively rotatable. The piston 59 is composed of an upper oil chamber 60 defined on the upper side of the piston 59, and a lower oil chamber 61 defined on the lower side of the piston 59.

  The central portion of the lower link plate 63 is pivotally supported by a lower portion of the link post 44 via a spherical joint 62, and both end portions of the lower link plate 63 are connected to the lower portions of the pair of trunnions 55, 55 by spherical joints 64, 64. It is pivoted through. Further, the central portion of the upper link plate 66 is pivotally supported on the upper portion of the link post 44 via the spherical joint 65, and both end portions of the upper link plate 66 are connected to the upper portions of the pair of trunnions 55, 55. It is pivoted through.

  A pivot shaft 68 that supports the power roller 18 on the trunnion 55 supports a trunnion support portion 68a that is rotatably supported by the trunnion 55 via a needle bearing 69, and a power roller 18 that rotatably supports the needle roller 70. A power roller support portion 68b. One pivot shaft 68 is eccentric to the lower side of the trunnion support portion 68a with respect to the power roller support portion 68b, and the other pivot shaft 68 is a trunnion with respect to the power roller support portion 68b. The support portion 68a is eccentric upward. A ball bearing 71 is disposed between the power roller 18 and the trunnion 55 to allow smooth relative movement of the power roller 18 with respect to the trunnion 55.

  Next, the structure of the first thrust bearing 26A and the second thrust bearing 26B will be further described with reference to FIG.

  The first thrust bearing 26A is formed by integrating two thrust bearings, and is disposed between the first inner ring 81A, the first intermediate ring 82A, the first outer ring 83A, and the first inner ring 81A and the first intermediate ring 82A. And a plurality of balls 85 arranged between the first intermediate ring 82A and the first outer ring 83A. The first inner ring 81A is locked to a step portion 13b formed on the large-diameter portion 13a of the input shaft 13, and the first outer ring 83A is locked to a step portion 20a formed on the outer peripheral portion of the piston 20, and the first intermediate ring 82A. Is locked to a step 45d formed near the opening 45c of the first support member 45. Since the input shaft 13 and the piston 20 which is a part of the input shaft 13 are integrally coupled, the first inner ring 81A and the first outer ring 83A are integrally rotated relative to the first intermediate ring 82A.

  The second thrust bearing 26B has the same structure as the first thrust bearing 26A. Between the second inner ring 81B, the second intermediate ring 82B, the second outer ring 83B, the second inner ring 81B, and the second intermediate ring 82B. And a plurality of balls 85 arranged between the second intermediate wheel 82B and the second outer ring 83B. The second inner ring 81B is locked to a step portion 15b formed at the base of the shaft portion 15a of the output disk 15, and the second outer ring 83B is locked to a step portion 15c formed on the outer periphery of the output disk 15, The ring 82B is locked to a step 46d formed in the vicinity of the opening 46c of the second support member 46. The second inner ring 81B and the second outer ring 83B that are both locked to the output disk 15 are integrally rotated relative to the second intermediate ring 82B.

  A first distance d1 from the axis L of the input shaft 13 to the first inner ring 81A of the first thrust bearing 26A and a first distance from the axis L of the input shaft 13 to the second inner ring 81B of the second thrust bearing 26B. The distance d1 is the same, and the second distance d2 from the axis L of the input shaft 13 to the first outer ring 83A of the first thrust bearing 26A and the second thrust bearing 26B measured from the axis L of the input shaft 13 are the same. The second distance d2 to the second inner ring 81B is the same.

  When the gear ratio is between LOW and OD and the power roller 18 is not tilted, the contact point between the power roller 18 and the input disk 14 is a1, and the contact point between the power roller 18 and the output disk 15 is When b1, the contact points a1 and b1 move to a2 and b2, respectively, when the speed ratio is LOW, and the contact points a1 and b1 move to a3 and b3, respectively, when the speed ratio is OD. That is, the contact point of the input disk 14 changes between a2 and a3, and the contact point of the output disk 15 changes between b2 and b3, but these contact points a2, a3; b2, b3 are the first distance. It is within the range of d1 and the second distance d2, and does not protrude inside the first distance d1 or protrude outside the second distance d2.

  Next, the operation of the embodiment of the present invention having the above configuration will be described.

  Of the pair of hydraulic actuators 56, 56, when the lower oil chamber 61 of one hydraulic actuator 56 is at a high pressure relative to the upper oil chamber 60, the upper oil chamber 60 of the other hydraulic actuator 56 is relative to the lower oil chamber 61. Because of the high pressure, the pair of piston rods 57 and 57 are driven in opposite directions. When one of the pair of trunnions 55 and 55 moves up along the trunnion shaft 17, the other moves along the trunnion shaft 17. Move down. At this time, the vertical movement of the left and right trunnions 55, 55 can be synchronized by the action of the lower link plate 63 and the upper link plate 66. When the pair of trunnions 55 and 55 move in the opposite directions, the power rollers 18 and 18 together with the trunnions 55 and 55 are rotated around the trunnion shafts 17 and 17 by the reaction force received from the input disk 14 and the output disk 15 in FIG. , B.

  For example, when the power rollers 18 and 18 tilt in the direction of arrow a, the contact point with the input disk 14 moves radially outward with respect to the input shaft 13, and the contact point with the output disk 15 moves to the input shaft 13. On the other hand, since it moves radially inward, the rotation of the input disk 14 is accelerated and transmitted to the output disk 15, and the ratio of the toroidal continuously variable transmission mechanism T continuously changes to the OD side. On the other hand, when the power rollers 18 and 18 tilt in the direction of arrow b, the contact point with the input disk 14 moves radially inward with respect to the input shaft 13, and the contact point with the output disk 15 moves to the input shaft 13. On the other hand, since it moves radially outward, the rotation of the input disk 14 is decelerated and transmitted to the output disk 15, and the ratio of the toroidal continuously variable transmission mechanism T continuously changes to the LOW side. The rotation of the output disk 15 follows the path of the output shaft 23 → the clutch 25 → the first gear 24 → the second gear 28 → the intermediate shaft 27 → the final drive gear 29 → the final driven gear 31 → the differential gear 30 → the drive shafts 32 and 32. It is transmitted to the drive wheels W, W.

  As apparent from FIGS. 4 and 5, when hydraulic pressure is supplied to the oil chamber 21 of the urging means 22 so that the power rollers 18 and 18 do not slip with respect to the input disk 14 and the output disk 15, they are fixed to the input shaft 13. The input disk 14 is urged to the left side in the drawing with respect to the piston 20 thus pressed, and the power rollers 18 and 18 are pressed against the output disk 15. In other words, the output disk 15 is urged to the left in the figure by the reaction force received from the power rollers 18 and 18, and the input disk 14 is urged to the right in the figure by the reaction force received from the power rollers 18 and 18. As a result, when the input disk 14 and the output disk 15 are deformed away from each other by the reaction force received from the power rollers 18 and 18, an eccentric load is applied to the first thrust bearing 26A and the second thrust bearing 26B, and the durability thereof is increased. May be adversely affected or power transmission efficiency may be reduced.

  However, according to the present embodiment, the above problem is solved by the special structure of the first thrust bearing 26A and the second thrust bearing 26B. That is, when the gear ratio changes to the LOW side, the contact point of the input disk 14 moves to the a2 side, but the first intermediate wheel 82A is moved from the first inner ring 81A located radially inward of the first thrust bearing 26A. After that, when a load is transmitted to the first support member 45 and the gear ratio changes to the LOW side, the contact point of the output disk 15 moves to the b2 side, but is positioned on the radially outer side of the second thrust bearing 26B. Since the load is transmitted from the second outer ring 83B to the second support member 46 via the second intermediate ring 82B, not only is the load applied to the first thrust bearing 26A and the second thrust bearing 26B prevented, The bending of the input disk 14 and the output disk 15 is effectively prevented.

  On the contrary, when the gear ratio changes to the OD side, the contact point of the input disk 14 moves to the a3 side, but from the first outer wheel 83A located on the radially outer side of the first thrust bearing 26A to the first intermediate wheel 82A. When the load is transmitted to the first support member 45 and the gear ratio changes to the OD side, the contact point of the output disk 15 moves to the b3 side, but is positioned radially inward of the second thrust bearing 26B. Since the load is transmitted from the second inner ring 81B to the second support member 46 via the second intermediate ring 82B, not only an unbalanced load is prevented from being applied to the first thrust bearing 26A and the second thrust bearing 26B. The bending of the input disk 14 and the output disk 15 is effectively prevented.

  As a result, it is possible to achieve both power transmission efficiency and durability while using small capacities for the first thrust bearing 26A and the second thrust bearing 26B. That is, in general, when the ball bearing ball and the ball groove holding the ball are in point contact, there is an advantage that the power transmission efficiency is improved because both of them are in rolling contact with each other. There is a problem that the surface pressure increases and durability decreases. On the other hand, if the ball and the ball groove are in surface contact with each other in a predetermined area, there is a problem that the power transmission efficiency is lowered because both of them are in sliding contact with each other at the contact portion. There is an advantage of improving the performance.

  According to the present embodiment, since the first thrust bearing 26A and the second thrust bearing 26B are less likely to receive an unbalanced load, not only the capacity can be afforded, but also the surface pressure per ball decreases (ball rolling) The ratio of (groove radius) / (ball diameter) can be increased, and the contact area of the ball rolling groove can be reduced. As a result, the power transmission efficiency can be improved, so that both the durability of the first thrust bearing 26A and the second thrust bearing 26B and the power transmission efficiency can be improved.

  Moreover, even if the speed change ratio becomes LOW and the contact points a1 and b1 move to a2 and b2, respectively, or the speed change ratio becomes OD and the contact points move to a3 and b3, respectively, the contact points after the movement a2 a3; b2 and b3 are within the range of the first distance d1 and the second distance d2, and do not protrude inside the first distance d1 or outside the second distance d2. Further, deformation of the output disk 15 can be prevented more reliably.

Second embodiment

  Next, a second embodiment of the present invention will be described with reference to FIG.

  In the first embodiment, the first thrust bearing 26A includes a first inner ring 81A, a first intermediate ring 82A, and a first outer ring 83A, and the second thrust bearing 26B includes a second inner ring 81B, a second intermediate ring 82B, and a second In the second embodiment, the first and second thrust bearings 26A and 26B are each provided with two thrust bearings that are stacked inward and outward in the radial direction.

  For example, each thrust bearing constituting the first thrust bearing 26A includes a first race 86 that is locked to the input shaft 13 or the piston 20, a second race 87 that is locked to the first support member 45, and a first race. And a plurality of balls 88 sandwiched between the second races 86 and 87, and an annular retainer 89 disposed so as to surround the outer periphery of the balls 88. The inner surfaces 86a and 87a of the first and second races 86 and 87 that face each other are tapered such that the distance between the inner surfaces 86a and 87a decreases inward in the radial direction, and the inner surfaces 86a and 87a are in contact with the balls 88. The tangent lines of the surfaces intersect on the axis L of the input shaft 14.

  Each thrust bearing constituting the second thrust bearing 26B has the same structure as each thrust bearing constituting the first thrust bearing 26A described above, and the first race 86 is locked to the output disk 15, and the second The race 87 is locked to the second support member 46.

  When normal angular ball bearings are used as the first and second thrust bearings 26A and 26B, there is a problem that loss due to slippage of the contact portion between the ball and the ball groove increases. When tapered roller bearings are used, the end surfaces of the rollers are There is a problem that the friction loss of the supporting shoulder portion becomes large. However, according to the present embodiment, the inner surfaces 86a, 87a of the first and second races 86, 87 are tapered, so that the balls 88 ... urged radially outward by the compressive load in the direction of the axis L direction. The load is received by the retainer 89, and the contact points of the balls 88 and the retainer 89 are positioned in a plane perpendicular to the axis L and passing through the center of the balls 88, thereby contacting the balls 88 and the retainer 89. Loss can be reduced by eliminating the occurrence of slipping at points.

  Moreover, since the load of the balls 88 urged radially outward is received by a single retainer 89 disposed radially outward of the balls 88, the number of retainers 89 can be reduced to one and the number of parts can be reduced. In addition, since the load is supported by the internal stress of the retainer 89, the structure for holding the retainer 89 can be simplified.

  The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention.

  For example, in the first thrust bearing 26A of the embodiment, the first inner ring 81A and the first outer ring 83A are respectively engaged with the input shaft 13 and the piston 20 that is a part of the input shaft 13, and the first intermediate ring 82A is the first intermediate ring 82A. The first intermediate ring 82A is locked to the input shaft 13 or the piston 20, and the first inner ring 81A and the first outer ring 83A are connected to the first support member. You may latch to 45.

  In the second thrust bearing 26B of the embodiment, the second inner ring 81B and the second outer ring 83B are locked to the output disk 15, and the second intermediate ring 82B is locked to the second support member 46. The relationship may be reversed, and the second intermediate ring 82B may be locked to the output disk 15, and the second inner ring 81B and the second outer ring 83B may be locked to the second support member 46.

13 Input shaft 14 Input disk 15 Output disk 18 Power roller 22 Biasing means 26A First thrust bearing (first bearing)
26B Second thrust bearing (second bearing)
45 First support member (casing)
46 Second support member (casing)
81A First inner ring 81B Second inner ring 82A First intermediate ring 82B Second intermediate ring 83A First outer ring 83B Second outer ring 84 Ball 85 Ball d1 First distance d2 Second distance L Input shaft axis

Claims (2)

An input disk (14) supported on the input shaft (13) so as not to rotate relative to the input shaft and slidable in the axial direction; ), A pair of power rollers (18) sandwiched between the input disk (14) and the output disk (15), and the input disk (14) with respect to the input shaft (13). 15) a biasing means (22) for biasing toward the side, and a first bearing (26A) for rotatably supporting the input shaft (13) on the casing (45) at a position facing the biasing means (22). A toroidal continuously variable transmission mechanism comprising a second bearing (26B) for rotatably supporting the output disk (15) on the casing (46),
The first bearing (26A) includes a first inner ring (81A), a first intermediate ring (82A), and a first outer ring (83A) that are sequentially arranged from the radially inner side toward the outer side, and the first inner ring (81A). ), The first intermediate ring (82A) and the first outer ring (83A) are rotatable relative to each other via balls (84, 85),
The second bearing (26B) includes a second inner ring (81B), a second intermediate ring (82B), and a second outer ring (83B) that are sequentially arranged from the radially inner side toward the outer side, and the second inner ring (81B). ), The second intermediate ring (82B) and the second outer ring (83B) are rotatable relative to each other via balls (84, 85),
The first inner ring (81A) and the first outer ring (83A) are supported by one of the input shaft (13) and the casing (45), and the first intermediate ring (82A) is supported by the input shaft (13) and The second inner ring (81B) and the second outer ring (83B) supported by the other of the casing (45) are supported by one of the output disk (15) and the casing (46), and the second intermediate ring ( 82B) is a toroidal continuously variable transmission mechanism that is supported on the other of the output disk (15) and the casing (46). The distance from the axis (L) of the input shaft (13) to the first inner ring (81A) and the distance from the second inner ring (81B) are the same first distance (d1), and the axis (L) The distance from the first outer ring (83B) to the second outer ring (83B) is the same second distance (d2),
The distance from the axis (L) of the contact point with respect to the input disk (14) and the output disk (15) when the power roller (18) is tilted is larger than the first distance (d1). The toroidal continuously variable transmission mechanism according to claim 1, wherein the toroidal continuously variable transmission mechanism is smaller than the second distance (d2).

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