JP4923935B2 - Toroidal continuously variable transmission - Google Patents

Description

  The present invention relates to an improvement of a toroidal type continuously variable transmission used as an automatic transmission for an automobile. Specifically, the shift operation is smoothly performed with a light force, the power loss is kept low, and a structure capable of ensuring excellent durability is achieved.

  The use of a toroidal type continuously variable transmission as an automobile transmission is described in many publications such as Patent Documents 1 and 2 and Non-Patent Documents 1 and 2, and has been well-known in some implementations. is there. FIG. 17 shows a basic configuration of a toroidal-type continuously variable transmission currently being implemented. First, this conventional structure will be briefly described. A pair of input-side disks 1a and 1b with respect to the input rotary shaft 2, each of which is a toroidal curved surface (concave arc-shaped concave surface) and corresponding to one axial side surface recited in the claims. In a state where the three are opposed to each other, they are concentrically supported and can freely support synchronized rotation.

  An output cylinder 5 having an output gear 4 fixed to the outer peripheral surface of the intermediate portion is supported around the intermediate portion of the input rotary shaft 2 so as to freely rotate with respect to the input rotary shaft 2. Further, output side disks 6 and 6 are supported at both ends of the output cylinder 5 so as to be rotatable in synchronization with the output cylinder 5 by spline engagement. In this state, the output side surfaces 7 and 7 of the both output side disks 6 and 6, each of which is a toroidal curved surface and corresponding to one axial side surface recited in the claims, Opposite to 3.

  Further, two power rollers 8 and 8 each having a spherical convex surface on each of the peripheral surfaces (cavities) between the input side and output side inner side surfaces 3 and 7 around the input rotation shaft 2 are provided. It is arranged. The power rollers 8 and 8 are respectively connected to the inner surfaces of the trunnions 9 and 9 via support shafts 10 and 10 whose base half and tip half are eccentric and a plurality of rolling bearings. 10 is supported in such a manner that it can be rotated about the front half of the front half and a small amount of swinging about the base half of each of the support shafts 10 and 10.

  The trunnions 9 and 9 are swingable and displaceable around the tilting shafts concentrically provided for the trunnions 9 and 9 at both ends in the length direction (front and back direction in FIG. 17). is there. The operation of swinging (tilting) each of these trunnions 9 and 9 is performed by displacing each of these trunnions 9 and 9 in the axial direction (front and back direction in FIG. 17) of each of the tilting shafts by a hydraulic actuator. . At the time of shifting, the trunnions 9 and 9 are displaced in the axial direction of the tilt shafts by supplying and discharging pressure oil to and from the actuators. As a result, the direction of the force acting in the tangential direction of the contact portion (traction portion) between the peripheral surface of each of the power rollers 8 and 8 and each of the input side and output side inner surfaces 3 and 7 changes (side slip occurs). Therefore, the trunnions 9, 9 are oscillated and displaced about the tilt axes.

  During operation of the toroidal-type continuously variable transmission as described above, one drive side disk 11a (left side in FIG. 17) is rotationally driven via a loading cam type pressing device 12. As a result, the pair of input-side disks 1a and 1b supported at both ends of the input rotation shaft 2 rotate synchronously while being pressed toward each other. Then, this rotation is transmitted to the output side disks 6 and 6 through the power rollers 8 and 8 and is taken out from the output gear 4.

  When the ratio of the rotational speeds of the input rotary shaft 2 and the output gear 4 is changed, and when the deceleration is first performed between the input rotary shaft 2 and the output gear 4, the trunnions 9 and 9 are arranged as shown in FIG. The power rollers 8 and 8 are swung to the positions shown in FIG. 3 and the peripheral surfaces of the input side disks 1a and 1b of the respective input side disks 1a and 1b and the outputs of the output side disks 6 and 6 are output. It is made to contact | abut to the outer periphery side part of the side surfaces 7 and 7, respectively. On the contrary, when the speed is increased, the trunnions 9 and 9 are swung in the direction opposite to that shown in FIG. 17, and the peripheral surfaces of the power rollers 8 and 8 are input to the input disks 1a and 1b. It is made to contact | abut to the outer periphery part of the side surfaces 3 and 3 and the center side part of the output side surfaces 7 and 7 of the said output side discs 6 and 6, respectively. An intermediate speed ratio (transmission ratio) can be obtained between the input rotary shaft 2 and the output gear 4 by setting the swing angles of the trunnions 9 and 9 to an intermediate position.

  During operation of the toroidal type continuously variable transmission as described above, the members used for power transmission, that is, the input side and output side disks 1a, 1b, 6 and the power rollers 8, 8 are It is elastically deformed based on the pressing force (thrust) generated by the pressing device 12. And along with this elastic deformation, each said disk 1a, 1b, 6 is displaced to an axial direction. Further, the pressing force generated by the pressing device 12 increases as the torque transmitted by the toroidal continuously variable transmission increases, and the amount of elastic deformation of each member increases accordingly. Accordingly, in order to properly maintain the contact state between the input and output side surfaces 3 and 7 and the peripheral surfaces of the power rollers 8 and 8 irrespective of the torque fluctuation, 8 is required to displace the disc 8 in the axial direction of the discs 1a, 1b, 6 with respect to the trunnions 9, 9. In the case of the first example of the conventional structure shown in FIG. 17, the first half of each of the support shafts 10 and 10 that support the power rollers 8 and 8 is also oscillated and displaced about the base half as well. Thus, the power rollers 8, 8 are displaced in the axial direction.

  On the other hand, Patent Document 3 discloses a toroidal-type continuously variable transmission in which the change of the gear ratio and the displacement of each power roller in the axial direction of each disk on the input side and output side are performed by completely different mechanisms. The machine is listed. The toroidal type continuously variable transmission of the second example of this conventional structure includes a speed change mechanism as shown in FIGS. In the case of the second example of the conventional structure shown in FIGS. 18 to 19, the swing frame 13 is provided around the input rotation shaft 2 between the input side and output side disks 1, 6. Can be swung around the center. The three trunnions 9a, 9a are rotatably supported between the support plate portions 14, 14 provided at the radially outer end of the swing frame 13 on the inner side surfaces thereof. Is supported so as to be able to swing only about the tilting shafts 15 and 15 provided at both ends. These trunnions 9a and 9a are not displaced in the axial direction of the tilting shafts 15 and 15 with respect to the swinging frame 13, unlike the structure shown in FIG. In this state, the extension lines α and α of the central axes of the power rollers 8 a and 8 a intersect on the central axes β of the disks 1 and 6.

  Of the tilting shafts 15 and 15, the remaining tilting shafts 15 and 15 other than the two tilting shafts 15 and 15 located at the upper end of FIGS. Is fixed. And the sector gears 16 and 16a regarding the trunnions 9a and 9a adjacent in the circumferential direction are meshed | engaged. With this configuration, all trunnions 9a, 9a are inclined at the same angle in the same direction with respect to the direction in which the gear ratio is changed. Further, any one of the sector gears 16 and 16a (lower right part in FIGS. 18 to 19) is connected to a tilt shaft 15 to which the sector gear 16a is fixed by a cam device 17 and an actuator 18. Oscillate around the center.

  The cam device 17 includes a cam follower 19 supported by the one sector gear 16a and a cam member 21 fixed to the inner surface of a housing 20 housing a toroidal-type continuously variable transmission. The cam groove 22 provided in the cam member 21 is engaged with the cam follower 19. The actuator 18 is a hydraulic double-acting type, and the movement of the pin 24 engaged with the long hole provided in the piston 23 is transmitted to the swing frame 13 through the coupling bracket 25, and this swing is performed. The frame 13 is swung around the input rotation shaft 2. As the swing frame 13 swings, the positional relationship between the cam follower 19 supported by the one sector gear 16 a and the cam groove 22 changes, and the sector gear 16 a is centered on the tilt shaft 15. Swing. Further, the movement of the sector gear 16a is transmitted to all trunnions 9a and 9a via the remaining sector gears 16 and 16. As a result, the power rollers 8a and 8a supported on the inner surfaces of the trunnions 9a and 9a have the same direction as to the direction in which the gear ratio between the input and output disks 1 and 6 changes. And the gear ratio is adjusted to a desired value.

  In the structure described in Patent Document 3 as described above, the power rollers 8a and 8a only swing in the front and back direction in FIG. 19 with respect to the relative positional relationship with the swing frame 13 at the time of shifting. . In other words, the power rollers 8a and 8a are displaced with respect to the swing frame 13 (along with the swing frame 13 in the rotational direction or the counter-rotation direction of the input rotary shaft 2 for the speed change operation). Even so, the tilting shafts 15 and 15 are not displaced in the axial direction (perpendicular to the extension lines α and α). The swing frame 13 is supported at a position between the input side and output side disks 1 and 6 so as to be swingable and displaceable by an angle required for shifting. There is no displacement in the axial direction of 1 and 6 (front and back direction in FIG. 19). Therefore, the trunnions 9a and 9a are not displaced in the axial direction of the disks 1 and 6.

  On the other hand, during operation of the toroidal continuously variable transmission, the surface pressure of the rolling contact portion (traction portion) between the inner side surfaces 3, 7 of the disks 1, 6 and the peripheral surfaces of the power rollers 8a, 8a is secured. The members 1, 6, 8a are elastically deformed by the force applied for this purpose. And each of these power rollers 8a and 8a is displaced in the front and back direction of FIG. In the case of the structure shown in FIG. 17, the power rollers 8 and 8 are supported by the support shafts (eccentric shafts) 10 and 10 in which the base half and the front half are eccentric with respect to the trunnions 9 and 9, respectively. By supporting the swingable displacement, the power rollers 8 and 8 can be displaced in accordance with the elastic deformation of the constituent members. However, in the case of the structure shown in FIGS. 18 to 19, it is not possible to employ a structure that only allows the rocking displacement of the power rollers 8a and 8a by the eccentric shaft.

  The reason for this is that, in the structure in which each of the power rollers 8a and 8a is simply swung by the eccentric shaft, each of the power rollers 8a and 8a is tilted on the basis of the arc motion having the eccentric amount as the rotation radius. This is because although the shafts 15 and 15 are displaced slightly in the axial direction (perpendicular to the extension lines α and α). As described in the structure shown in FIG. 17, when the power rollers 8a and 8a are displaced in the axial direction of the tilt shafts 15 and 15, side slips are generated in the traction portions, The trunnions 9a and 9a are applied with force in the direction of swinging around the tilt shafts 15 and 15 (directions for changing the gear ratio) via the power rollers 8a and 8a. Such a force is generated even when the displacement is about 0.1 to 0.2 mm. Naturally, it is not preferable to continue the operation of the toroidal type continuously variable transmission in a state where the side slip as described above occurs and the force as described above is applied. Specifically, the side slip is associated with a decrease in transmission efficiency and durability, and the force is associated with an increase in force that is actually required when changing the gear ratio.

For this reason, in the structure described in Patent Document 3, each of the power rollers 8a, 8a among the members 1, 6, 8a is elastically deformed by the structure as shown in FIGS. Is displaced only in the axial direction (front and back direction in FIG. 19) of both the input and output side disks 1 and 6. The support shaft 10a used in this structure for rotatably supporting the power roller 8a with respect to the trunnion 9a includes a base portion 26 and a support shaft portion 27 that are eccentric to each other. On the other hand, a circular recess 28 is formed in the middle portion of the inner surface of the trunnion 9a. A circular (thick disk-shaped) crank member 29 is rotatably fitted in the circular recess 28. A circular hole 30 is formed in a part of the crank member 29 at a position deviated from the center of the crank member 29. Eccentricity [delta] ₂ of the central axis X ₃₀ of the central axis X ₂₉ and the circular hole 30 of the outer peripheral surface of the crank member 29, the eccentricity of the central axis X ₂₇ of the central axis X ₂₆ and the support shaft portion 27 of the base 26 It is equal to the quantity δ ₁ (δ ₂ = δ ₁ ). The base portion 26 is fitted in the circular hole 30 so as not to rattle and swingable. Therefore, consistent with one another and the central axis X ₂₆ and the central axis X ₃₀ of the circular hole 30 of the base 26.

  Further, a long hole 31 extending in the axial direction of the tilting shafts 15 and 15 is formed in a part of the trunnion 9a aligned with the bottom corner of the circular recess 28, and the bottom surface of the circular recess 28 and the trunnion It forms in the state which communicates with the outer surface of 9a. A guide rod 32 projecting from one corner of the base end surface {the right end surface of FIG. 21B) of the base portion 26 of the support shaft 10a is formed in the long hole 31, and the length of the long hole 31 is set. A displacement in the direction (the axial direction of the tilting axes 15 and 15, the vertical direction in FIG. 21) is supported.

In the case of the structure described in Patent Document 3, the input side and output side inner side surfaces 3 and 7, which are axial side surfaces of the input side and output side discs 1 and 6, are configured as described above. Accompanying the axial displacement, the power roller 8a is displaced only in the axial direction as shown by an arrow a in FIG. When the power roller 8a is displaced in the direction of the arrow a, the guide rod 32 is moved to the tilt shafts 15 and 15 on the inner side of the long hole 31 as shown by an arrow b in FIG. Displacement in the axial direction. At this time, the arcuate movement based on the amount of eccentricity [delta] ₂ of the central axis X ₃₀ of the circular hole 30 around the center axis X ₂₉ of the outer peripheral surface of the crank member 29, the central axis X ₂₆ of the base 26 of the support shaft portion 27 The arc motion based on the eccentric amount δ ₁ with respect to the central axis X ₂₇ is canceled out, and the support shaft portion 27 is caused to linearly move.

  In the case of the first example of the conventional structure shown in FIG. 17 described above, it is necessary to provide an actuator for changing the gear ratio for each trunnion 9, 9. For this reason, if the number of power rollers 8 and 8 and trunnions 9 and 9 for supporting each of the power rollers 8 and 8 is increased in order to transmit large power, the number of actuators required increases, and the toroidal type It becomes difficult to reduce the size of the continuously variable transmission. On the other hand, in the second example of the conventional structure shown in FIGS. 18 to 19, a plurality of (three in the illustrated example) trunnions 9a and 9a are oscillated and displaced by one actuator 18. Therefore, it is advantageous in terms of increasing the number of power rollers 8a and 8a while preventing an increase in size.

  However, even in the second example of the conventional structure shown in FIGS. 18 to 19 described above, from the aspect of highly parallelizing downsizing and weight reduction, improving transmission efficiency, ensuring quickness of shifting operation, and suppressing fatigue of the traction surface, There is room for improvement. The reason for this is as follows. The speed change operation according to the second example of the conventional structure described above is a rolling contact portion (traction portion) between the peripheral surface of each power roller 8a, 8a and the input side surface 3 of the input side disc 1 and the output side surface 7 of the output side disc 6. Regardless of the magnitude and direction of the force acting on, the trunnions 9a, 9a are forcibly tilted so as to be inclined. For this reason, the force required to incline each of these trunnions 9a, 9a increases, and a large actuator 18 is required as a power source for the inclining operation. When a large actuator 18 is used, not only is it difficult to reduce the size and weight of the toroidal-type continuously variable transmission, but also the power loss increases due to the pump for supplying pressure oil to the actuator 18, The transmission efficiency of the toroidal continuously variable transmission is substantially reduced.

  Further, since the trunnions 9a and 9a are inclined regardless of the magnitude and direction of the force acting on the traction portion at the time of shifting, an unreasonable force is applied to the traction portion when a quick shifting operation is performed. There is a possibility that each of the surfaces constituting the traction portion may be damaged (these surfaces are fatigued early). On the other hand, if the above speed change operation is performed slowly so as not to damage each of these surfaces, a quick speed change operation, which is one of the advantages of the toroidal-type continuously variable transmission, cannot be performed.

  Furthermore, regardless of whether the first example of the conventional structure shown in FIG. 17 or the second example of the conventional structure shown in FIGS. 1, 1 a, 1 b, 6 and the peripheral surfaces of the power rollers 8, 8 are properly maintained, the power rollers 8, 8 a are displaced in the axial direction of the disks 1, 1 a, 1 b, 6. The structure for making it complex is complicated. For this reason, it is inevitable that the production of parts, the management of parts, and the assembly work of this structural part are complicated, and the cost is increased. In Patent Document 4, a linear motion type rolling bearing is provided between an inner surface of a trunnion and an outer ring of a thrust ball bearing for rotatably supporting the power roller, whereby the shaft of each disk of the power roller is provided. A structure that allows directional displacement is described. Even the structure described in Patent Document 4 has the same problem.

JP-A-3-74667 JP 2001-165262 A German Patent Application Publication No. 10246432 (DE10246432A1) JP 2003-294099 A Motoo Aoyama, “Bessed Best Car Red Badge Series 245 / A book that understands the latest mechanics of cars”, Sangensha Co., Ltd./Kodansha Co., Ltd., December 20, 2001, p. 92-93 Hirohisa Tanaka, “Toroidal CVT”, Corona Inc., July 13, 2000

  In view of the circumstances as described above, the present invention realizes a toroidal continuously variable transmission that can at least highly reduce the size and weight, improve the transmission efficiency, ensure the speed of shifting operation, and suppress fatigue on the traction surface. It is an object. Furthermore, if necessary, each power roller is displaced in the axial direction of each disk, and the contact state between the peripheral surface of each power roller and each disk is changed regardless of the change in the amount of elastic deformation of each constituent member. It is intended to make it possible to construct a structure that can be properly maintained at a low cost.

The toroidal continuously variable transmission according to the present invention includes at least one pair of discs, a plurality of trunnions, and the same number of power rollers as each of the trunnions, as in the previously known toroidal continuously variable transmissions. , Synchronization means and displacement drive means.
Each of these disks is supported concentrically and freely in relative rotation with the axial one side surfaces facing each other, each of which is a toroidal curved surface having an arcuate cross section.
Further, each trunnion is provided concentrically with each other at both ends in a plurality of locations in the axial direction between the one side surfaces of the respective discs with respect to the rotational direction of the respective discs. Oscillating displacement about the tilting axis that is twisted with respect to the central axis is freely provided.
Each of the power rollers is rotatably supported on a radially inner portion of each of the discs at an intermediate portion of each of the trunnions via a thrust rolling bearing. The disc is in contact with one side surface in the axial direction.
The synchronizing means is for mechanically synchronizing the swing angles of the trunnions.
Further, the displacement driving means is for oscillating and displacing at least one trunnion of the trunnions around the tilting shafts provided at both ends of the trunnion.
Each thrust rolling bearing includes an inner ring raceway provided on an end face of each power roller in an axial direction and an outer ring shaft supported by an intermediate part of each trunnion. A plurality of rolling elements are provided between the outer ring raceways provided on the end faces on the radial inner side of the respective disks among the both end faces in the direction.
In particular, in the toroidal type continuously variable transmission according to the present invention, the outer ring constituting each thrust rolling bearing is provided on each trunnion, and the direction of each tilt shaft provided at both ends of each trunnion is 5. Oscillating displacement about an inclination axis arranged in a direction inclined by ˜15 degrees is freely supported. And each said power roller is supported with respect to each said trunnion freely by the rocking displacement centering on the said inclination axis .
In other words, the oscillation center axis of each power roller is provided with a caster angle of 5 to 15 degrees with respect to the oscillation center axis of each trunnion.

When implementing the toroidal type continuously variable transmission of the present invention as described above, preferably, the tilting means provided with the synchronizing means at the end of each trunnion as in the invention described in claim 2. The shaft is configured to include a sector gear that is freely fixed to a tilt synchronized with the tilt shaft. Then, the sector gears provided at the ends of the trunnions adjacent to each other in the rotation direction of the disks are meshed with each other.

When implementing the toroidal type continuously variable transmission of the present invention as described above, preferably, as in the invention described in claim 3 , a support shaft is provided at the center of the inner surface of the outer ring constituting each thrust rolling bearing. Project. Each power roller is rotatably supported by a radial needle bearing around the support shaft.
When the invention described in claim 3 is carried out, preferably, as described in claim 4 , the inclined shafts are provided on the outer surface portions of the outer rings constituting the thrust rolling bearings. These outer rings are supported and fixed in the diameter direction. Then, each of these inclined shafts is elastically supported so as to be capable of axial displacement based on a thrust load commensurate with the power transmitted by each of the power rollers to each of the trunnions. In this case, even when the maximum transmission power (maximum transmission torque) is applied to each of the power rollers (even when a thrust load corresponding to the maximum transmission power is applied to each inclined shaft), each of the inclined shafts is displaced in the axial direction. Do not cut all the way out {Make sure that the elastic material for elastic support (for example, a plate spring) does not break due to elastic deformation}. In addition, when each inclined shaft (and thus each power roller) is elastically supported in this way, for example, when a difference occurs in the torque transmitted by each power roller based on, for example, displacement of the mounting position (initial position). Further, the tilt axis is displaced in the axial direction according to the difference in the thrust load based on the difference in torque. Then, each power roller is tilted (shifted) in a direction in which the difference in torque is reduced (a direction in which transmission torque shared by each power roller is equalized, a direction in which the displacement of the mounting position is reduced).

Further, preferably, when the above-described present invention is carried out, each trunnion is provided with a pair of tilting shafts and a supporting beam portion as in the invention described in claim 5 .
These two tilting shafts are provided concentrically with each other at both ends of each trunnion.
The support beam portion exists between the two tilting axes. Then, at least the inner side surface in the radial direction of each disc is parallel to the central axis of these two tilting shafts, and the central axis existing outside the central direction of these two tilting shafts in the radial direction of each of these discs. It has a cylindrical convex surface.
Further, a swing block is disposed between the support beam portion of each trunnion and the outer ring constituting each thrust rolling bearing.
This rocking block rocks the trunnions in the axial direction of the respective discs with respect to the respective trunnions by engaging the concave portions having a partial cylindrical surface provided on the outer surface with the cylindrical convex surfaces of the supporting beam portions. Support displacement possible.
In this case, for example , as in the sixth aspect of the present invention , the inclined shaft and the recess provided on the outer surface of the swing block are engaged via a radial needle bearing.

When the present invention is implemented, preferably, as in the invention described in claim 7 , the virtual center line of the tilt axis of each trunnion and the virtual center line of the tilt axis provided in each trunnion are intersected. Let In other words, both these virtual center lines are located on the same virtual plane (not in a torsional relationship). Further, the virtual center of the tilt axis of each trunnion and the virtual center of the tilt axis are always matched.

Further, when the present invention is carried out, for example, as in the invention described in claim 8 , two discs that are supported concentrically with each other in such a manner that one side surfaces in the axial direction are opposed to each other can be freely rotated. Provide a pair. Of these two to four discs, two outer discs arranged at both ends in the axial direction can be freely combined with each other through a rotating shaft in synchronization with each other. Similarly, two inner disks arranged in the central portion in the axial direction are provided around the rotating shaft so as to freely rotate in synchronization with each other and rotate relative to the rotating shaft. Further, a displacement driving means for swinging and displacing any one of the plurality of trunnions arranged between the outer disk and the inner disk of one pair about the tilt axis, and the other pair of trunnions Displacement drive means for oscillating and displacing any one of the trunnions arranged between the outer disk and the inner disk around the tilt axis is synchronized with each other.

When carrying out the invention described in claim 8 as described above, for example, as in the invention described in claim 9 , the pair of displacement drive means includes a feed screw rod, a rotation drive means, and a first drive The feed nut, the second feed nut, and the transmission mechanism are provided.
Of these, the feed screw 杆 is arranged in parallel with the central axis of each of the disks, and a forward screw is provided in one half of the axial direction, and a reverse screw is provided in the other half of the axial direction. .
The rotational driving means rotationally drives the feed screw 杆 in both directions.
The first feed nut is screwed to one half of the axial direction of the feed screw rod, and the second feed nut is screwed to the other half of the axial direction.
Further, the transmission mechanism has a function of transmitting the movements of the two feed nuts in the axial direction of the feed screw rod to the respective trunnions.
Then, each trunnion is oscillated and displaced about the tilt axis based on the rotation of the feed screw 杆.
When the inventions described in the above eighth to ninth aspects are carried out, the two inner discs may be combined with each other, but the shafts as in the invention described in the tenth aspect may be combined. It is also possible to make an integrated disc having toroidal curved surfaces on both sides.

  When changing the gear ratio of the toroidal continuously variable transmission of the present invention configured as described above, any trunnion is swung by the displacement drive means, and the inclination of the trunnion about each tilting axis The angle is an angle commensurate with the target gear ratio. At the same time, the inclination angle of the other trunnions is set to an angle corresponding to the target gear ratio by the action of the synchronizing means. At this time, the inclination angle of each trunnion is immediately changed to an angle commensurate with the target gear ratio. On the other hand, each power roller tends to stay in its position while swinging with respect to each trunnion about the tilt axis. With such swinging displacement of the power rollers and the trunnions around the tilt axis, the power rollers are displaced with respect to the rotation direction of the disks.

  As a result, as in the case of the conventional structure shown in FIG. 17, the force acting in the tangential direction of the contact portion (traction portion) between the peripheral surface of each power roller and one axial side surface of each disk is determined. The direction changes (side slip occurs), and the power rollers are oscillated and displaced about the inclined axes. Such oscillating displacement of the power rollers about the tilt axes is performed until the tilt angle of the power rollers reaches an angle corresponding to the target gear ratio (target shift speed). Swing to an angle commensurate with the ratio and then stop). When the power rollers are stopped in this manner, the positional relationship between the power rollers and the trunnions is in a neutral state, which is the same as before the shift operation is started. In short, when a speed change operation is performed by the toroidal type continuously variable transmission of the present invention, first, the inclination angle of each trunnion changes to an angle corresponding to the target speed ratio. Next, the power rollers are oscillated and displaced so as to follow the oscillating displacements of the trunnions, and the inclination angles of the power rollers become angles suitable for the target gear ratio.

  As described above, the toroidal continuously variable transmission according to the present invention starts the shift operation by setting the tilt angle of the trunnion to an angle that matches the target gear ratio, and the operation of changing the tilt angle of the trunnion is as follows. It is just a trigger for changing the gear ratio. That is, unlike the above-described second example of the conventional structure shown in FIGS. 18 to 19, the power rollers are inclined according to the speed change operation regardless of the magnitude and direction of the force acting on the traction portion. There is nothing to do. Therefore, the output of the displacement driving means for inclining each trunnion is small, and the toroidal continuously variable transmission including the displacement driving means can be reduced in size and weight. In addition, since less energy is required to swing and displace each trunnion by the displacement driving means, the transmission efficiency can be improved when the entire toroidal continuously variable transmission system is considered.

  Further, in order to realize the target gear ratio, the force for changing the inclination angle of each power roller is applied to the traction portion as in the first example of the conventional structure shown in FIG. Use the side slip that occurs. The speed change operation utilizing the side slip is performed without difficulty unlike the second example of the conventional structure. Therefore, even if the speed change operation is performed quickly, harmful force hardly acts on each surface constituting the traction portion. For this reason, it is possible to achieve a high level of both promptness of speed change operation and suppression of fatigue on the traction surface.

  Note that the speed of the speed change operation by the toroidal type continuously variable transmission of the present invention can be arbitrarily adjusted by changing the speed at which the inclination angle of any of the trunnions is changed by the displacement driving means. That is, as is well known in the first example of the conventional structure shown in FIG. 17, the side slip generated in the traction portion increases as the amount of shifting the power roller in the rotational direction of each disk increases. The speed of On the other hand, in the case of the toroidal continuously variable transmission according to the present invention, the rotation direction of each disk is proportional to the amount of swing displacement between each trunnion and each power roller, with the tilt axis as the center. The amount of deviation of each of these power rollers increases. Therefore, when a fast shifting operation is necessary, the speed for changing the inclination angle of each trunnion is increased by the displacement driving means, and when the shifting operation is delayed, the changing speed of the inclination angle is decreased. When a large gear ratio change is performed by a slow speed change operation, if the inclination angle of each trunnion is changed slowly by the displacement driving means and the synchronization means, the power rollers slightly delay the movement of each trunnion. Swing and displace as if chasing in the state.

In the case of the toroidal type continuously variable transmission according to the present invention, the power rollers are supported by thrust rolling bearings, and the outer rings constituting the thrust rolling bearings are oscillated and displaced around the inclined shaft. Since the power rollers are supported as possible, the power rollers can be smoothly rotated and displaced.
When the present invention is implemented, if the synchronizing means includes a sector gear as in the invention described in claim 2, the synchronizing means can be made small and light .

Further, when carrying out the present invention, as in the invention described in claim 3 , the power rollers are arranged around the support shaft protruding from the center of the inner surface of the outer ring constituting the thrust rolling bearing. If it is supported rotatably by a radial needle bearing, the radial load applied to each of these power rollers as power is transmitted can be efficiently supported.
When carrying out the invention described in such claim 3, as in the invention described in claim 4, if the respective tilt axis by the elastic support to the trunnions, associated with the direction of rotation of the respective disc Even when the mounting positions of the power rollers are slightly deviated, this deviation can be absorbed to some extent. And it can prevent that some power rollers transmit excessive motive power and the durability of the said power roller is impaired.

Further, when the above-described present invention is carried out, if each trunnion having a pair of tilting shafts and supporting beam portions is used as in the invention described in claim 5 , each of the power rollers The structure in which the contact state between the peripheral surface of each power roller and each disk can be properly maintained regardless of the change in the amount of elastic deformation of each constituent member by simply displacing the disk in the axial direction of each disk. Cost can be configured.
That is, when it is necessary to displace the power rollers in the axial direction of the disks based on the elastic deformation of the disks and the power rollers during the operation of the toroidal continuously variable transmission, The outer ring of each thrust rolling bearing that rotatably supports the roller swings around the engaging portion between the concave portion of the cylindrical surface provided on the outer surface of the swing block and the cylindrical convex surface of the support beam. Displace. Based on this swing displacement, the portion of the peripheral surface of each power roller that is in rolling contact with one axial side surface of each disk is displaced in the axial direction of each disk, and the contact state is maintained appropriately. To do. The central axis of the cylindrical convex surface is present on the outer side in the radial direction of each disk with respect to the central axis of the tilting axis that becomes the center of oscillation of each trunnion during the shifting operation. Therefore, the rocking radius of the rocking displacement centered on the central axis of the cylindrical convex surface is larger than the rocking radius at the time of the speed change operation, and has little influence on the change in the gear ratio between the disks. (It can be ignored or easily corrected.)

As described above, it is easy to process the concave portion and the cylindrical convex surface, which are required to maintain the contact state properly, and no special parts are required. For this reason, it can be configured simply and at low cost.
Further, as in the invention described in claim 6 , if the inclined shaft and the concave portion provided on the outer surface of the rocking block are engaged via the radial needle bearing, the above-described aspect of the present invention is achieved. The speed change operation by the structure can be performed more smoothly. In this case, the radial needle bearing reduces the resistance against the rocking displacement between the rocking block and the tilt shaft, so that the force required for shifting can be reduced. For example, each trunnion is swung around the tilt shaft. It is possible to reduce the size of the displacement driving means, rotational driving means, and synchronizing means {for example, sector gears, feed screws (ball screws), actuators (electric motors), etc.} for moving them.

When the present invention is implemented, the virtual center line of the tilt axis of each trunnion and the virtual center line of the tilt axis provided in each trunnion can be crossed as in the invention described in claim 7. For example, during the speed change operation, the peripheral surface of each power roller can be displaced substantially along one axial side surface of each disk. For this reason, the speed change operation can be stabilized by smoothly displacing the traction portion, which is a rolling contact portion between the peripheral surface of each power roller and one axial side surface of each disk.

Further, when the present invention is implemented, if two pairs of disks are provided (double cavity type) and a pair of displacement drive means are synchronized with each other as in the invention described in claim 8 , a large amount of power can be obtained. Can transmit a smooth shift operation.
When carrying out the invention described in claim 8 as described above, for example, as in the invention described in claim 9 , the pair of displacement driving means is divided into a feed screw rod, a rotation driving means, a first and a second. If the structure is provided with a feed nut and a transmission mechanism, the structure can be configured simply, small and light, and the oscillation displacement of each power roller provided in each cavity can be reliably synchronized.
When the structure of the invention described in claims 8 to 9 described above is carried out, if the two inner disks are integrated as in the invention shown in claim 10 , a double cavity type The structure can be reduced in size and weight.

  1 to 16 show an example of an embodiment of the present invention corresponding to all claims. As shown in FIGS. 1 and 2, the toroidal type continuously variable transmission of this example includes a pair of input side disks 1a and 1b at both ends of the input rotary shaft 2, and an input side surface 3 each of which is a toroidal curved surface. 3 are arranged concentrically with each other facing each other. One of the input side discs 1a and 1b (left side in FIGS. 1 and 2) is spline-engaged with one end portion of the input rotary shaft 2, and this input rotation is performed by a holding screw cylinder 33. It is intended to prevent the shaft 2 from coming off. On the other hand, the other input side disk 1b (on the right side in FIGS. 1 and 2) is supported on the other end portion of the input rotary shaft 2 via a ball spline 34, and also by a hydraulic pressing device 12a. The one input side disk 1a can be pressed freely. Further, an input gear 35 is provided concentrically with the input side disk 1a on the outer surface of the one input side disk 1a. During operation of the toroidal-type continuously variable transmission, the input gear 35 and the input rotary shaft 2 are introduced while introducing hydraulic pressure to the pressing device 12a to apply a force in the direction toward the input disks 1a and 1b. These two input-side disks 1a and 1b are rotated in synchronization with each other.

  Further, an integrated output side disk 6 a is provided around the intermediate portion of the input rotary shaft 2 so as to be freely rotatable relative to the input rotary shaft 2. The output side disk 6a has both side surfaces in the axial direction as output side surfaces 7 and 7 each having a toroidal curved surface, and the intermediate portion of the input rotary shaft 2 is loosely inserted into the center hole 36. Further, an output gear 37 is provided on the outer peripheral edge of the output side disk 6a so that power can be taken out from the output side disk 6a during operation of the toroidal type continuously variable transmission. Such an output side disk 6a is rotatably supported by a pair of thrust rolling bearings 39, 39 on a support frame 38 as shown in its entirety in FIG. These thrust rolling bearings 39 and 39 are thrust angular ball bearings or the like that can support a radial load in addition to a thrust load. Further, the input rotary shaft 2 is rotatably supported with respect to the support frame 38 by radial needle bearings 40, 40 provided at two positions of the intermediate portion of the input rotary shaft 2.

  The portions between the input side surfaces 3 and 3 of both the input side disks 1a and 1b and the output side surfaces 7 and 7 of the output side disk 6a (a pair of cavity portions) are shown in FIGS. A plurality of such power roller units 41 and 41 are arranged for each cavity (three in the illustrated example, a total of six). Each of these power roller units 41, 41 includes a trunnion 9b, a swing block 42, a thrust rolling bearing 43, and a power roller 8b.

  Of these, the trunnion 9b includes a pair of tilting shafts 15 and 15 provided concentrically at both ends, and a support beam portion 44 existing between the two tilting shafts 15 and 15. As shown in FIGS. 11 to 14, the support beam portion 44 has at least an inner side (for example, a vertical direction in FIGS. 3, 4, and 6 to 14) in the radial direction of the input side and output side disks 1 a, 1 b, and 6 a ( For example, the cylindrical convex surface 45 is formed on the side surfaces of the upper side of FIGS. 7, 9, 11, and 13 and the lower side of FIGS. As shown in FIG. 7, the central axis A of the cylindrical convex surface 45 is parallel to the central axes B of the two tilting axes 15, 15, and more than the central axes B of the tilting axes 15, 15. It exists outside (for example, the lower side of FIGS. 7, 9, 11, 13 and the upper side of FIGS. 8, 10, 12, 14) in the radial direction of the disks 1a, 1b, 6a.

  Further, as shown in FIGS. 11 to 14, for example, a concave portion 46 having a partial cylindrical surface is provided on the outer surface of the rocking block 42 so as to cross the outer surface in the radial direction. Then, by engaging this concave portion 46 with the cylindrical convex surface 45 of the support beam portion 44, the rocking block 42 is moved to the trunnion 9b so that the input side and output side disks 1a, 1b, 6a The swing displacement in the axial direction is supported. In the case of this example, the curvature radii of the cross-sectional shape of both end portions in the axial direction of the concave portion 46 and the curvature radii of the cross-sectional shape of the cylindrical convex surface 45 are made to coincide with each other. The cylindrical convex surface 45 is brought into direct contact as shown in FIGS. During operation of the toroidal continuously variable transmission, a large thrust load is applied to the swing block 42 from the power roller 8b via the thrust rolling bearing 43. Therefore, the rocking block 42 is not rocked and displaced with a light force with respect to the support beam portion 44, but is rocked and displaced when a certain large force is applied. In the illustrated example, the radius of curvature of the cross-sectional shape of the central portion in the axial direction of the concave portion 46 is made larger than the radius of curvature of the cross-sectional shape of the cylindrical convex surface 45. Accordingly, a semi-cylindrical gap space 47 exists between the axial central portion of the cylindrical convex surface 45 and the axial central portion of the concave portion 46 as shown in FIGS. The gap space 47 serves as a lubricating oil passage for continuously supplying the lubricating oil from the trunnion 9b to the thrust rolling bearing 43 side regardless of the rocking displacement of the trunnion 9b and the rocking block 42. Have.

  The power roller 8 b is rotatably supported by the thrust rolling bearing 43 on the inner surface of the swing block 42. Further, the outer ring 48 constituting the thrust rolling bearing 43 is arranged on an inner surface of the swing block 42 (a radially inner side surface of each of the disks 1a, 1b, 6a), as shown in FIGS. The rocking displacement centering on 49 is supported freely. Therefore, the power roller 8b is supported on the inner surface of the swing block 42 so as to be swingable and rotatable. In the illustrated example, the thrust rolling bearing 43 is an angular ball bearing. As shown in FIGS. 7 to 14, the outer surface of the power roller 8b (the side surface on the radially outer side of each of the disks 1a, 1b, 6a). Between the inner ring raceway 50 provided on the outer ring 48 and the outer ring raceway 51 provided on the inner side surface of the outer ring 48, a plurality of balls 52, 52, each of which is a rolling element, are provided with contact angles deviating from 90 degrees. It is provided in the state. Further, as shown in FIGS. 7 to 12, a support shaft 53 protrudes from the center of the inner surface of the outer ring 48, and the power roller 8 b can be rotated around the support shaft 53 by a radial needle bearing 54. I support it. With this configuration, the power roller 8b is rotatably supported with respect to the outer ring 48 in a state where a large rigidity is ensured in the thrust, radial, and both directions.

As shown in FIGS. 7 to 14, the inclined shaft 49 is inclined on the outer surface of the outer ring 48 in the radial direction of the outer ring 48 and with respect to the central axis B of the both inclined shafts 15, 15. It is arranged with. That is, the inclined shaft 49 is fitted and fixed to a recess 55 formed on the outer surface of the outer ring 48. As shown in FIGS. 7 to 12, an arch-shaped restraining portion 56 is formed at the central portion of the outer surface of the outer ring 48 so as to straddle the concave portion 55. The inclined shaft 49 has its inner half fitted in the recess 55 and its axial intermediate portion is fitted between the recess 55 and the holding portion 56 so that the outer surface of the outer ring 48 is fitted. It is fixed to support. In this state, the oil supply pipe 57 is inserted into the holding portion 56, the inclined shaft 49 and the outer ring 48 so that the inclined shaft 49 does not come out of the recess 55. In this manner, with the inclined shaft 49 coupled and fixed to the outer ring 48, the central axis C of the inclined shaft 49 is aligned with the central axes B of the two inclined shafts 15 and 15, as shown in FIG. On the other hand, it is inclined by a predetermined angle α (5 to 15 degrees, 10 degrees in the illustrated example). Note that the center axis B of the two tilt axes 15 and 15 and the center axis C of the tilt axis 49 are located on the same virtual plane (the center axes B and C intersect each other).

The distance between the inner surface of the rocking block 42 and the outer surface of the outer ring 48 is, as is apparent from FIGS. 11 to 14, the axial center portion of the inclined shaft 49 shown in FIGS. 11 to 12 and FIGS. Any part of both axial ends shown in FIG. 6 becomes wider as the distance from the inclined shaft 49 increases. Further, both end portions in the axial direction of the inclined shaft 49 and concave portions 58 and 58 having a semicircular cross section formed in the inner surface of the swing block 42 at portions facing the both end portions in the axial direction of the inclined shaft 49, The radial needle bearings 59 and 59 are engaged with each other. With this configuration, the outer ring 48 is supported with respect to the swing block 42 so as to be able to swing and displace with a light force around the inclined shaft 49 provided in the intermediate portion of the trunnion 9b. In the case of this example, with such a configuration, the outer ring 48 is easily oscillated and displaced with respect to the inclined shaft 49. Therefore, the resistance against the displacement of the swing block 42 relative to the support beam portion 44 is far greater than the resistance against the displacement of the outer ring 48 and the power roller 8b relative to the swing block 42. Big. However, even if these resistances are the same, the same speed change operation as in this example can be performed. This is because the center of the tilt shafts 15 and 15 of the trunnion 9b coincides with the center of the tilt shaft 49 (concentric), and the trunnion 9b is swung around the tilt shafts 15 and 15. In this case, a moment for swinging and displacing the swing block 42, the outer ring 48 and the power roller 8b is compared with a moment for swinging and shifting the support beam portion 44 and the swing block 42. This is because of the increase.

  In the case of this example, as described above, the inclined shaft 49 is assembled on the outer surface of the outer ring 48 while the radial displacement of the outer ring 48 is prevented by the oil supply pipe 57. When a large force is applied to the inner surface of the trunnion 9b, the tilt shaft 49 is supported so that the tilt shafts 15 and 15 can be displaced in the axial direction. Therefore, in the case of this example, the inner surfaces of the bent portions 60, 60 that make the support beam portion 44 and the pair of tilting shafts 15, 15 continuous in a part of the trunnion 9b, and the inclined surfaces. Steel balls 61 and 61 and disc springs 62 and 62 are provided in series with each other in order from the inner surface side between both axial end surfaces of the shaft 49. The elasticity of the disc springs 62, 62 is applied to the trunnion 9b from the side surfaces 3, 7 of the discs 1a, 1b, 6a via the power rollers 8b during operation of the toroidal continuously variable transmission. It is sufficiently large so that it is not bent even by a force called 2Ft. In other words, the inclined shaft 49 is displaced in the axial direction according to the force applied to the outer ring 48, that is, the thrust load corresponding to the power transmitted by the power roller 8b. The contact surfaces between the steel balls 61 and 61 and the bent portions 60 and 60 are preferably located on an extension line of the central axis of the inclined shaft 49.

  A plurality of sets (six sets in the illustrated example) of the power roller units 41 and 41, each configured as described above, are provided on the support frame 38 as shown in FIG. Only the rocking displacement about the tilting shafts 15 and 15 is supported freely. That is, when the toroidal continuously variable transmission is assembled, the two tilting shafts 15 and 15 rotate (oscillate and displace) via the radial rolling bearings 64 and 64, respectively, to the support ring portions 63 and 63 of the support frame 38. The toroidal-type continuously variable transmission shown in FIGS. In the case of this example, by using a self-aligning roller bearing as each of the radial rolling bearings 64, 64, a load capacity is ensured, and at the time of elastic deformation of the trunnion 9b, each of the radial rolling bearings. The edge load is prevented from occurring at the rolling contact portions existing in 64 and 64.

While the power roller units 41 and 41 are supported by the support frame 38 only in a swingable manner, the swinging angles of the trunnions 9b and 9b are mechanically synchronized by the synchronizing means 65 described below. The displacement driving means 66, which will be described later, is configured to be displaced by a desired angle.
In the case of this example, in order to constitute the synchronization means 65, as in the second example of the conventional structure shown in FIGS. 18 to 19, the trunnions 9b and 9b are connected as shown in FIGS. Sector gears 16 and 16 are fixed to the tilt shafts 15 and 15 provided at the ends, respectively. And, as shown in FIG. 1, sector gears 16, 16 provided on the respective tilting shafts 15, 15 at the ends of the trunnions 9b, 9b adjacent to each other with respect to the rotation direction of the respective disks 1a, 1b, 6a, Meshed with each other. With this configuration, the synchronizing means 65 is configured to swing and displace three trunnions 9b, 9b existing in the same cavity in the same direction and at the same angle.

  On the other hand, the displacement driving means 66 is one of the three trunnions 9b, 9b existing in mutually different cavities and existing in a portion where the phases of the respective disks 1a, 1b, 6a coincide with each other. Each of the two trunnions 9b, 9b is configured to be oscillated and displaced in synchronism with each other at the same angle in the reverse direction (the same direction with respect to the change direction of the gear ratio). Therefore, in the case of this example, as shown in FIG. 1, the discs 1a, 1b, 6a are slightly deviated from the lateral sides of the discs 1a, 1b, 6a. The feed screw rod 67 is arranged in a state in which only the rotation is supported in parallel with the central axis of each of the disks 1a, 1b, 6a. This feed screw rod 67 is provided with a forward screw in one half of the axial direction and a reverse screw in the other half of the axial direction at the same pitch, and a driven gear 68 fixed to the end. In addition, a drive gear that is rotationally driven by a rotational drive means such as an electric motor that can rotate forward and reverse is meshed so that it can be rotationally driven by a desired angle (including 360 degrees or more) in a desired direction.

Also, a first feed nut 69 is attached to a forward screw formed on one half of the axial direction of the feed screw rod 67, and a second feed nut 70 is attached to a reverse screw formed on the other half of the axial direction. They are screwed together. A part of these feed nuts 69 and 70 that is opposed to the base of a pair of sector gears 16 and 16 fixed to the ends of the tilt shafts 15 and 15 at the ends of the two trunnions 9b and 9b. Are formed with holding portions 71, 71 opened on both sector gears 16, 16 side, and locking notches 72, 72 are formed at the edges of both holding portions 71, 71. On the other hand, as shown in FIGS. 3, 4, 7, and 8, swing arm portions 73 projecting toward the both holding portions 71 and 71 are formed at the base portions of the sector gears 16 and 16. An intermediate portion of the locking pin 74 is fitted and fixed to the distal end portions of both the swing arm portions 73 and 73. Then, both end portions of both the locking pins 74 are engaged with the respective locking notches 72, 72 as shown in FIG. The said holding | maintenance parts 71 and 71, these each latching notches 72 and 72, both said rocking | swiveling arm parts 73, and both said latching pins 74 and 74 comprise the transmission mechanism described in Claim 9. Then, the movement of the first and second feed nuts 69 and 70 in the axial direction of the feed screw rod 67 is transmitted to the trunnions 9b and 9b.

  When changing the gear ratio of the toroidal continuously variable transmission of the present invention configured as described above, the two trunnions 9b, 9b installed in different cavities are reversed by the displacement driving means 66 in the reverse direction ( In the same direction with respect to the direction of change of the gear ratio, they are swung and displaced in synchronism with each other by the same angle. In the case of this example, if the feed screw rod 67 is rotated by a desired angle in a desired direction by the rotation driving means, the first and second feed nuts 69 and 70 move in opposite directions (perspective movement). Then, both the trunnions 9b and 9b are oscillated and displaced about the tilting shafts 15 and 15 provided at both ends. At the same time, the remaining two trunnions 9b and 9b are provided for each of the cavities by the synchronizing means 65, and the remaining four trunnions 9b and 9b are also reversed in the opposite direction between the cavities (in the same direction with respect to the direction of change of the gear ratio) Oscillate and displace by the same angle in synchronization with each other. In this way, the inclination angles of the six trunnions 9b, 9b in total are set to angles suitable for the target gear ratio.

  At the start of the shifting operation performed in this manner, the inclination angles of the six trunnions 9b, 9b are immediately changed to an angle corresponding to the target gear ratio. At the same time, the inclination angle of each rocking block 42 is also changed to an angle corresponding to the target gear ratio in synchronism with each trunnion 9b, 9b. That is, during the operation of the toroidal continuously variable transmission, the cylindrical convex surface 45 of the support beam portion 44 of each trunnion 9b, 9b and the axial end portions of the concave portion 46 of each swing block 42 Due to the thrust load applied from the rolling contact portion (traction portion) between the side surfaces 3 and 7 of 1a, 1b and 6a and the peripheral surfaces of the power rollers 8b and 8b, they are in strong contact (with a large contact pressure). For this reason, at the time of the speed change operation, the rocking blocks 42 are caught by the trunnions 9b and 9b and are rocked and displaced by the same angle as the trunnions 9b and 9b.

  On the other hand, the outer ring 48 supported by the swing block 42 via the radial needle bearings 59 and 59 and the inclined shaft 49 swings with respect to the swing block 42 with a light force. Further, the inclination angle of each of the power rollers 8b and 8b rotatably supported by the thrust rolling bearing 43 including the outer ring 48 and the radial needle bearing 54 changes immediately due to the resistance acting on the traction portions. There is nothing. For this reason, the thrust rolling bearing 43 including the outer ring 48 and the power rollers 8 b and 8 b are inclined with respect to the swing blocks 42 around the inclined shaft 49. And with this inclination, each of these power rollers 8b, 8b is displaced in the direction of each said inclination axis | shaft 15,15. As a result of this displacement, a side slip is generated in the traction section, and the power rollers 8b and 8b, together with the thrust rolling bearing 43 including the outer ring 48, are oscillated and displaced toward an angle corresponding to a target gear ratio. To do.

  The behavior of each part at this time will be described in more detail with reference to FIG. When performing a speed change operation, first, the trunnion 9b and the swing block 42 are moved to a desired angle (a gear ratio to be changed) in the direction of the arrow α in FIG. Oscillating and shifting by an angle suitable for the size of As described above, immediately after the swing displacement of the trunnion 9b and the swing block 42, the outer ring 48 and the power roller 8b tend to remain in the same position without being displaced. Therefore, the power roller 8b is oscillated and displaced with respect to the oscillating block 42 in the direction of arrow β in FIG. In actuality, the power roller 8b is not oscillated and displaced, but the oscillating block 42 is oscillated and displaced with respect to the power roller 8b. From the viewpoint of explaining the movement of the power roller 8b, the same applies. Conceivable.

As a result of the swinging displacement of the power roller 8b in the direction of the arrow β, the center of the power roller 8b is displaced with respect to the rotational direction of the disks 1a (1b) and 6a. That is, the center of the power roller 8b with the swinging displacement of the arrow β direction is displaced as indicated by arrow γ in FIG. 16. The direction of the arrow γ is a direction perpendicular to the central axis of the inclined shaft 49 and is inclined with respect to the direction of the central axis of each of the disks 1a (1b) and 6a. Accordingly, the center of the power roller 8b is displaced with respect to the rotational direction of each of the disks 1a (1b) and 6a (for example, δ in FIG. 16) in accordance with the displacement in the arrow γ direction in FIG.

  As a result, as in the case of the conventional structure shown in FIG. 17, the contact portion (traction portion) between the peripheral surface of each power roller 8b and the axial one side surface 3, 7 of each disk 1a, 1b, 6a. ) Changes in the direction of the force acting in the tangential direction (side slip occurs), and the power rollers 8b swing and displace about the inclined shafts 49. The direction of the oscillating displacement based on such side slip is a direction that cancels the displacement in the directions of arrows β and γ at the start of the shifting operation (the direction opposite to the directions of arrows β and γ at the start of the shifting operation). The same displacement). Then, the swinging displacement in the direction opposite to the arrows β and γ at the start of the speed change operation of the power roller 8b centering on the tilt shaft 49 is the tilt angle of the power roller 8b. The process is performed until the angle matches the target gear ratio. In other words, the thrust roller bearing 43 including the power roller 8b and the outer ring 48 stops swinging in a state where the power roller 8b swings to an angle commensurate with a target gear ratio. Thus, in a state where the oscillation of the power roller 8b and the thrust rolling bearing 43 is stopped, the positional relationship between the power roller 8b and the trunnion 9b is as shown in FIGS. Same neutral state. However, in this state, the positional relationship of the trunnion 9b (and the power roller 8b supported by the trunnion 9b) with respect to the support frame 38 (with respect to the disks 1a, 1b, and 6a) is different from that before the start of the shifting operation. (The tilt angle is changed to match the gear ratio).

  In short, when performing the speed change operation by the toroidal type continuously variable transmission of this example, first, the displacement drive means 66 and the synchronization means 65, three for each of the two cavities, a total of six trunnions 9b, The inclination angle of 9b is changed to an angle commensurate with the target gear ratio. In this state, the power rollers 8b, 8b supported by the trunnions 9b, 9b are displaced in the rotational direction of the disks 1a, 1b, 6a while swinging with respect to the trunnions 9b, 9b. Causes side slip. The side slip causes the power rollers 8b and 8b to swing and follow the swing displacement of the trunnions 9b and 9b, and the inclination angles of the power rollers 8b and 8b The angle is suitable for the gear ratio to be used.

  As described above, the toroidal-type continuously variable transmission of this example starts the shifting operation by setting the inclination angle of each trunnion 9b, 9b to an angle corresponding to the target gear ratio, but each trunnion 9b, The operation of changing the inclination angle of 9b is only a trigger for changing the gear ratio. That is, unlike the second example of the conventional structure shown in FIGS. 18 to 19 described above, the magnitude and direction of the force acting on the traction portion is caused to move the power rollers 8b and 8b with the start of the speed change operation. Regardless, do not tilt. Accordingly, the output of the rotational drive means constituting the displacement drive means 66 for inclining the two trunnions 9b, 9b, one for each of the cavities, can be small, and the toroidal type including the displacement drive means 66 is included. The continuously variable transmission can be reduced in size and weight. Further, since the energy required to displace all six rocking displacements via the two trunnions 9b and 9b by the displacement driving means 66 is reduced, the entire toroidal type continuously variable transmission system is considered. The transmission efficiency can be improved. In particular, if the rotational drive means is an electric motor, the loss due to energy for changing the gear ratio can be suppressed to a minimum.

Furthermore, according to the toroidal type continuously variable transmission of this example, the power rollers 8b are displaced in the axial direction of the disks 1a, 1b, 6a, regardless of changes in the elastic deformation amounts of the constituent members. A structure that can appropriately maintain the contact state between the peripheral surfaces of the power rollers 8b and 8b and the disks 1a, 1b, and 6a can be configured easily and at low cost.
That is, during operation of the toroidal-type continuously variable transmission, the disks 1a, 1b, 6a and the power rollers 8b, 8b are elastically deformed. When the magnitude of torque transmitted by the toroidal continuously variable transmission varies, the amount of elastic deformation also changes. Therefore, in order to properly maintain the surface pressure of each traction section, it is necessary to displace the power rollers 8b and 8b in the axial direction of the disks 1a, 1b and 6a in accordance with the fluctuation of the torque. is there.

  In the case of this example, if it is necessary to displace the power rollers 8b, 8b in the axial direction of the disks 1a, 1b, 6a for the reasons described above, the power rollers 8b are rotatably supported. The oscillating block 42 slidingly slides the contact surface between the concave portion 46 of the partial cylindrical surface provided on the outer surface and the cylindrical convex surface 45 of the support beam portion 44, and the center of the cylindrical convex surface 45. It swings and displaces around the axis A (see FIG. 7). Along with the elastic deformation, the force for displacing the power rollers 8b, 8b in the axial direction of the disks 1a, 1b, 6a is large. For this reason, as described above, the rocking block regardless of the relatively large frictional force acting between the concave portion 46 and the cylindrical convex surface 45 based on the thrust load applied from the power rollers 8a and 8b. 42 is reliably oscillated and displaced.

Based on the swing displacement, the portions of the peripheral surfaces of the power rollers 8b and 8b that are in rolling contact with the axial one side surface of the disks 1a, 1b, and 6a are the disks 1a, 1b, 6a is displaced in the axial direction to maintain the above contact state properly. As described above, the central axis A of the cylindrical convex surface 45 is greater than the central axes B of the tilting shafts 15 and 15 that become the swing center of the trunnions 9b during the shifting operation. It exists outside in the radial direction. Therefore, the rocking radius of the rocking displacement centered on the engaging portion is larger than the rocking radius in the shifting operation, and the gear ratio between the input side disks 1a and 1b and the output side disk 6a. Has little impact on the fluctuations (it can be neglected or easily corrected).
In this manner, the processing of the concave portion 46 and the cylindrical convex surface 45, which are required to maintain the contact state properly, is easy, and no special parts are required. For this reason, it can be configured simply and at low cost.

  Further, in the case of this example, the steel balls 61 and 61 and the dish plate are respectively disposed between the mutually facing inner surfaces of the bent portions 60 and 60 of the trunnions 9b and the both axial end surfaces of the inclined shaft 49. Since the springs 62 and 62 are provided, even if the mounting positions of the power rollers 8b and 8b with respect to the rotational direction of the disks 1a, 1b and 6a are slightly deviated, this deviation can be absorbed to some extent. . That is, the elasticity of the disc springs 62 and 62 is applied to the power rollers 8b and 8b and the power rollers 8b and 8b from the side surfaces 3 and 7 of the discs 1a, 1b, and 6a in a normal operation state of the toroidal continuously variable transmission. It is large enough not to bend by a so-called 2Ft force applied to each trunnion 9b through the outer ring 48 of the thrust rolling bearing 43. Then, by bending according to 2Ft, the mounting positions of the power rollers 8b and 8b are allowed to change with respect to the rotation direction of the disks 1a, 1b and 6a. When the mounting positions of the power rollers 8b and 8b are deviated, the thrust rolling supporting the other power roller 8b is supported on the outer ring 48 of the thrust rolling bearing 43 supporting the power roller 8b from a part of the power rollers 8b. There is a possibility that a larger force than the outer ring 48 of the bearing 43 is applied. In this case, the outer ring 48 supporting the power roller 8b is moved in the rotational direction of the disks 1a, 1b, 6a with respect to the trunnion 9b. Displacement is made so that the power roller 8b does not transmit excessive power, thereby preventing the durability of the power roller 8b from being impaired.

The principal part perspective view which shows one example of embodiment of this invention. FIG. 2 is a cross-sectional view taken along the line II in FIG. 1 in an accelerated state. The perspective view which takes out and shows the power roller unit displaced by the displacement drive means. Similarly side view. The figure seen from the lower part of FIG. The same view from the right. FIG. 6 is a cross-sectional view of FIG. The perspective view seen from the reverse direction in the state cut | disconnected in the same position as FIG. FIG. 6 is a cross-sectional view of FIG. The perspective view seen from the reverse direction in the state cut | disconnected in the same position as FIG. FIG. 6 is a sectional view of the knee of FIG. The perspective view seen from the reverse direction in the state cut | disconnected in the same position as FIG. FIG. The perspective view seen from the reverse direction in the state cut | disconnected in the same position as FIG. The perspective view of a support frame. The schematic diagram for demonstrating the condition where a power roller is displaced to the rotation direction of each disk based on the relative displacement of a trunnion and a rocking | fluctuation block. Sectional drawing which shows the 1st example of a conventional structure. The principal part perspective view which shows the 2nd example. The figure which took out a part of FIG. 18 and was seen from the axial direction of each disc. The disassembled perspective view shown in the state which took out the trunnion and the power roller. (A) is the figure seen from the inner surface side of the trunnion, (B) is sectional drawing in the assembled state. (A) is the perspective view seen from the inner surface side of the trunnion in the same state, (B) is the perspective view seen from the outer surface side in the state which cut | disconnected a part.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1, 1a, 1b Input side disk 2 Input rotary shaft 3 Input side side surface 4 Output gear 5 Output cylinder 6, 6a Output side disk 7 Output side side surface 8, 8a, 8b Power roller 9, 9a, 9b Trunnion 10, 10a Support shaft DESCRIPTION OF SYMBOLS 11 Drive shaft 12, 12a Pressing device 13 Oscillating frame 14 Support plate part 15 Tilt shaft 16, 16a Sector gear 17 Cam device 18 Actuator 19 Cam follower 20 Housing 21 Cam member 22 Cam groove 23 Piston 24 Pin 25 Connecting bracket 26 Base 27 Support shaft 28 Circular recess 29 Crank member 30 Circular hole 31 Long hole 32 Guide rod 33 Set screw cylinder 34 Ball spline 35 Input gear 36 Center hole 37 Output gear 38 Support frame 39 Thrust rolling bearing 40 Radial needle bearing 41 Power roller uni 42 Rocking block 43 Thrust rolling bearing 44 Support beam portion 45 Cylindrical convex surface 46 Concave portion 47 Clearance space 48 Outer ring 49 Inclined shaft 50 Inner ring raceway 51 Outer ring raceway 52 Ball 53 Support shaft 54 Radial needle bearing 55 Concave portion 56 Suppressing portion 57 Oil supply Pipe 58 Recess 59 Radial needle bearing 60 Bent portion 61 Steel ball 62 Disc spring 63 Support ring portion 64 Radial rolling bearing 65 Synchronizing means 66 Displacement driving means 67 Feed screw rod 68 Drive gear 69 First feed nut 70 Second feed Nut 71 Holding part 72 Locking notch 73 Swing arm part 74 Locking pin

Claims (10)

At least one pair of discs that are concentrically supported by each other in a state in which one side surfaces in the axial direction, each of which is a toroidal curved surface having an arc-shaped cross section, are opposed to each other and freely rotatable relative to each other, and each of these discs in the axial direction. The tilting shafts which are provided concentrically with each other at both ends of the respective discs at a plurality of positions in the axial direction between the side surfaces of the discs and are twisted with respect to the central axes of the discs. A plurality of trunnions provided with a freely swinging displacement at the center, and at the intermediate portions of each trunnion, supported radially on the radially inner portion of each disk via thrust rolling bearings, The number of power rollers equal to the number of trunnions, and the vibrations of the trunnions, with the respective peripheral surfaces being in contact with one axial side surface of the disks, respectively. And synchronization means for causing mechanically synchronize the angle, and a displacement driving means for swinging displacing at least one of the trunnions about said tilt shaft provided at both end portions of the trunnion, each thrust The rolling bearing includes an inner ring raceway provided on the radially outer end face of each disk among the axial end faces of each power roller, and an axial end face of the outer ring supported by an intermediate portion of each trunnion. In the toroidal-type continuously variable transmission in which a plurality of rolling elements are provided between the outer ring raceway provided on the radially inner end face of each disk , each thrust rolling bearing is configured. The outer ring is freely supported on each trunnion, and swinging displacements centered on the tilt axis disposed in the direction inclined by 5 to 15 degrees with respect to the direction of each tilt axis provided on both ends of each trunnion are freely supported. to be More, the power rollers to the trunnions, the toroidal type continuously variable transmission, characterized in that supported freely swings around the tilt axis.   The synchronizing means includes a sector gear fixed to a tilting shaft provided at an end of each trunnion so that the tilting synchronized with the tilting shaft can be freely performed, and the trunnions adjacent to each other in the rotation direction of each disk. The toroidal-type continuously variable transmission according to claim 1, wherein sector gears provided at the end of each of these are meshed with each other. A support shaft projects from a central portion of an inner surface of an outer ring constituting each thrust rolling bearing, and each power roller is rotatably supported by a radial needle bearing around the support shaft . 2. A toroidal continuously variable transmission according to any one of the above. Each inclined shaft is supported and fixed to the outer surface portion of each outer ring constituting each thrust rolling bearing in the diameter direction of each outer ring, and each of these inclined shafts is thrust corresponding to the power transmitted by each power roller to each trunnion. The toroidal-type continuously variable transmission according to claim 3 , wherein the toroidal continuously variable transmission is elastically supported so as to be capable of axial displacement based on a load. Each trunnion exists between a pair of tilting shafts concentrically provided at both end portions and the two tilting shafts, and at least the inner side surface in the radial direction of each disk has the two tilting shafts. And a support beam portion having a cylindrical convex surface having a central axis that is parallel to the central axis of each of the two tilt axes and is located outside the central axes of the two tilting axes in the radial direction of each disk. A rocking block is arranged between the beam part and the outer ring constituting the thrust rolling bearing. The rocking block has a concave part of a partial cylindrical surface provided on the outer surface and a cylindrical shape of the support beam part. 5. The toroidal type of claim 1 , wherein the trunnion is supported so as to be capable of swinging displacement in the axial direction of each disk by engaging with a convex surface. Step transmission. The toroidal continuously variable transmission according to claim 5 , wherein the inclined shaft and a recess provided on the outer surface of the swing block are engaged via a radial needle bearing. The toroidal continuously variable transmission according to any one of claims 1 to 6 , wherein a virtual center line of a tilt axis of each trunnion intersects a virtual center line of a tilt axis provided in each trunnion. Two pairs of discs that are supported concentrically with each other so that relative rotation is freely possible with one axial side facing each other, and two of these two to four discs arranged at both ends in the axial direction. The outer discs of the two discs can be freely combined with each other via a rotating shaft, and two inner discs arranged at the central portion in the axial direction are also rotated around the rotating shaft and synchronized with each other. Displacement for swinging and displacing any trunnion of a plurality of trunnions arranged between one pair of outer disk and inner disk around the tilt axis. Displacement drive means for oscillating and displacing any one of a plurality of trunnions arranged between the drive means and the other pair of outer disk and inner disk about the tilt axis Make synchronization with each other, the toroidal type continuously variable transmission as set forth in any one of claims 1 to 7. A pair of displacement drive means is arranged in parallel with the central axis of each disk, and a feed screw rod provided with a forward screw in one axial half and a reverse screw in the other axial half, respectively , A rotation driving means for rotationally driving the feed screw 杆 in both directions, a first feed nut screwed to one half of the axial direction of the feed screw 杆, and a second screw screwed to the other half of the axial direction. A feed nut and a transmission mechanism for transmitting the movements of the two feed nuts with respect to the axial direction of the feed screw そ れ ぞ れ to the respective trunnions. The toroidal-type continuously variable transmission according to claim 8 , wherein the toroidal continuously variable transmission is oscillated and displaced as a center. The toroidal-type continuously variable transmission according to any one of claims 8 to 9 , wherein the two inner disks are integrated disks each having a toroidal curved surface on both axial sides.

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