JP2006022828A - Toroidal continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent a power roller 4 (7) from being excessively tilted. <P>SOLUTION: Projected parts 66 and 66 are formed on stopper members 73 and 73 fixed to both ends of a trunnion 30 (31). Also, recessed parts 67 and 67 are formed in the inner surfaces of end plates 48 and 48 forming a swing frame 21 (22) at positions facing the projected parts 66 and 66. The projected parts 66 and 66 are inserted into the recessed parts 67 and 67 displaceably in the swing direction of the trunnion 30 (31). At the same time, the trunnion 30 (31) is prevented from being swung by a specified amount or more by the contact of the side faces of the projected parts 66 and 66 on the inner faces of the recessed parts 67 and 67 based on the swing of the trunnion 30 (31). <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The toroidal type continuously variable transmission according to the present invention is used as a transmission unit constituting an automatic transmission for a vehicle (automobile), for example.

  Toroidal-type continuously variable transmissions have been studied and partially implemented as transmissions for automobiles. For passenger cars, automatic transmissions for four-wheel drive vehicles incorporating large-sized engines that generate large torque A structure suitable as a transmission unit is described in, for example, Patent Document 1 and is conventionally known. 5 to 8 show a toroidal continuously variable transmission for a four-wheel drive vehicle having a large displacement described in Patent Document 1. FIG. This toroidal continuously variable transmission 1 includes three first power rollers 4, 4 between a first input side disk 2 and a first output side disk 3, and a second input side disk 5 and a second output side. Three second power rollers 7 are provided between the disk 6 and power is transmitted by a total of six power rollers 4 and 7.

  In order to constitute the automatic transmission, a torque converter 8 that is a starting clutch is provided at the most front stage in the power transmission direction, and the toroidal continuously variable transmission 1 is constituted at the output part of the torque converter 8. The front half 9a of the input shaft 9 is incorporated. The front half portion 9a is rotationally driven by the torque converter 8 along with the rotation of a traveling engine (not shown). The rear half 9b of the input shaft 9 is supported on the rear end of the front half 9a concentrically and relatively rotatably.

  And between the front half part 9a and the latter half part 9b, a forward / reverse switching unit 10 for switching between forward and backward is provided in series with respect to the transmission direction of power. This forward / reverse switching unit 10, which is a planetary gear mechanism, switches between a forward state and a reverse state by selecting and connecting a forward clutch 11 and a reverse clutch 12, each of which is a wet multi-plate clutch. .

  The toroidal continuously variable transmission 1 is provided on the rear side of the forward / reverse switching unit 10 as described above with respect to the power transmission direction. And the input part of this toroidal type continuously variable transmission 1, that is, the part connected to the output part of the forward / reverse switching unit 10 and the output part, that is, the part connected to the front wheel drive shaft 13 and the rear wheel drive shaft 14. The gear ratio between is continuously changed. The toroidal continuously variable transmission 1 is provided around the latter half 9b. That is, the first and second input side disks 2 and 5 are arranged concentrically with each other in the state in which the inner side surfaces, which are concave surfaces each having an arcuate cross section, are opposed to each other in the vicinity of both front and rear ends of the rear half portion 9b. Synchronously and freely supported. Therefore, in the illustrated example, the first input side disk 2 provided on the front side (the left side in FIG. 5) is spline-engaged with the base end portion of the carrier 15 constituting the forward / reverse switching unit 10 and also moved forward. Is preventing movement. On the other hand, the second input side disk 5 provided on the rear side (right side in FIG. 5) is supported via a ball spline 16 at the rear end portion of the latter half portion 9b. Then, the second input disk 5 is pressed toward the first input disk 2 by a hydraulic loading device 17 so as to be freely pressed.

  Further, a support cylinder 18 is provided concentrically with the latter half portion 9b around the middle portion of the latter half portion 9b. The support cylinder 18 is supported and fixed at both ends by the inner diameter side ends of the stays 19 and 19. These stays 19 and 19 support and fix their outer diameter side end portions to support rings 20 and 20 which will be described later, and can swing first and second swing frames 21 and 22 which will also be described later. The first and second support frames 23 and 24 are configured to support the above. The rear half 9b is supported inside the support cylinder 18, and the first and second output side disks 3 and 6 are supported around the support cylinder 18 so as to be freely rotatable and axially displaceable. . Further, these output side disks 3 and 6 are capable of rotating relative to each other while supporting an axial load applied between them by a thrust bearing provided therebetween.

  Further, a front wheel output gear 25 is fixed to the outer surface side of the first output side disk 3, and the front wheel output gear 25 and the front wheel drive shaft 13 are engaged via a front wheel driven gear 26. Thus, the front output shaft 13 can be driven to rotate by the first output side disk 3. The rotation of the front wheel drive shaft 13 can be transmitted to a front wheel (not shown) via a front wheel differential gear 27. On the other hand, a rear wheel output gear 28 is fixed to the outer surface side of the second output side disk 6, and the rear wheel output gear 28 and the rear wheel drive shaft 14 are connected to a rear wheel driven gear 29. The rear output shaft 14 can be driven to rotate by the second output side disk 6. Further, the rotation of the rear wheel drive shaft 14 can be transmitted to a rear wheel (not shown) via a rear wheel differential gear (not shown).

  Further, the three first power rollers 4, 4 are arranged between the inner side surface of the first input side disk 2 and the inner side surface of the first output side disk 3. The three second power rollers 7 are respectively sandwiched between the side surface and the inner side surface of the second output side disk 6. These first and second power rollers 4 and 7 are the inner surfaces of the first and second trunnions 30 and 31, respectively, around the displacement shafts 32 and 32 provided in a state of protruding from the inner surface. It is supported rotatably. The first and second trunnions 30 and 31 do not intersect the central axes of the disks 2, 5, 3, and 6 provided concentrically with each other. Oscillates around the first and second pivots 33 (the second pivot is not shown) that exists in a twisted position that is perpendicular or nearly perpendicular to the direction of the central axes of 5, 3, and 6. To do. The first and second trunnions 30 and 31 are supported at both end portions of the first and second swing frames 21 and 22 so as to be swingably displaceable.

  The intermediate portions of the first and second swing frames 21 and 22 are arranged between the support rings 20 and 20 constituting the first and second support frames 23 and 24, respectively, The support shafts 34 and 34 are provided so as to be swingable and displaceable around the support shafts 34 and 34 provided in a direction parallel to or near the parallel to the center axes of the fifth, third and sixth axes. Each of the first and second support frames 23 and 24 has a pair of support rings 20 and 20 arranged in parallel to each other on the outer diameter side of the three support columns 35 and 35 constituting the stay 19. Combining with each other through the end. The support shafts 34 and 34 constitute the first and second support frames 23 and 24 at intermediate positions of the support columns 35 and 35 with respect to the circumferential direction of the support rings 20 and 20. A pair of support rings 20, 20 are spanned between each other. Accordingly, the first and second swing frames 21 and 22 are swingably supported between the column portions 35 and 35 adjacent to each other in the circumferential direction.

  Further, the first and second swing frames 21 and 22 are swung by hydraulic cylinders 36a and 36b provided between both ends of the swing frames 21 and 22 and the support rings 20 and 20, respectively. It can be moved freely. Each of these hydraulic cylinders 36a, 36b is provided at a position where it is aligned with both ends of each of the swing frames 21, 22 at a part of each of the support rings 20, 20. On the other hand, rods 37a and 37b are arranged at both ends of the first and second swing frames 21 and 22 so as to be aligned with the hydraulic cylinders 36a and 36b in parallel with the support shafts 34 and 34, respectively. The first and second swing frames 21 and 22 are supported and fixed so as to penetrate both end portions. The pistons 38a and 38b fitted to the hydraulic cylinders 36a and 36b are engaged with the rods 37a and 37b. Of the hydraulic cylinders 36a, 36b provided at the time of shifting, two pairs are provided for each of the swing frames 21, 22 (four for each swing frame, a total of 24 toroidal-type continuously variable transmissions 1 as a whole). The one hydraulic cylinder 36a (36b) provided on one end side in the longitudinal direction of each swing frame 21, 22 is extended and the other hydraulic cylinder 36b (36a) is contracted, so that each swing frame 21, 22 is oscillated and displaced by a predetermined amount in a predetermined direction.

  A control valve 39 for controlling supply and discharge of pressure oil to and from the hydraulic cylinders 36a and 36b is supported by the support rings 20 and 20, respectively. When the swing frames 21 and 22 are swung and displaced by the supply and discharge of pressure oil to and from the hydraulic cylinders 36a and 36b, they are provided on the outer surfaces of the trunnions 30 and 31 supported by the swing frames 21 and 22, respectively. The cam surface 40 displaces the spool 42 of the control valve 39 via the plunger 41 attached to the control valve 39 to switch the control valve 39. The sleeve 43 that constitutes the control valve 39 together with the spool 42 is displaced to a predetermined position by the control motor 44 so that a desired gear ratio can be realized at the time of shifting. Such a control valve 39 and a control motor 44 are provided on the first cavity 45 side including the first input side disk 2 and the first output side disk 3, and the second input side disk 5 and the second input disk 5. One is provided on the second cavity 46 side including the output side disk 6, and two are provided in the entire toroidal type continuously variable transmission 1. A control valve 39 on the first cavity 45 side is provided by the control motor 44 on the first cavity 45 side, a control valve 39 on the second cavity 46 side is provided by the control motor 44 on the second cavity 46 side, and a microcomputer is incorporated. Based on a command signal from a controller (not shown), the control is performed in synchronization with each other (in a straight traveling state) or independently of each other (in a turning state).

  Because of this configuration, at the time of shifting, the first and second swing frames 21 and 22 are configured to move the support shafts 34 and 34 based on the supply and discharge of the pressure oil to and from the hydraulic cylinders 36a and 36b. The center is oscillated and displaced by a predetermined amount in a predetermined direction. As a result, the first and second trunnions 30 and 31 supported by the swing frames 21 and 22 perform an arc motion (swivel motion) around the support shafts 34 and 34, respectively. Then, due to the displacement of the first and second trunnions 30 and 31 in the axial direction of the first and second pivot shafts 33 based on the arc motion, the peripheral surfaces of the power rollers 4 and 7 and the disks 2 and The direction of the tangential force acting on the rolling contact portion (traction portion) with the inner surfaces of 5, 3, 6 changes. The first and second trunnions 30 and 31 are pivotally supported by the first and second swing frames 21 and 22 with the change in the direction of the force. And the first and second input sides are changed by changing the contact positions of the peripheral surfaces of the first and second power rollers 4 and 7 and the inner side surfaces. The rotational speed ratio between the disks 2 and 5 and the first and second output disks 3 and 6 changes.

  During operation of the conventional toroidal-type continuously variable transmission 1 configured as described above, the first and second input side disks 2 and 5 that rotate in synchronization with the rear half 9b of the input shaft 9 The front wheel drive shaft 13 is rotationally driven by the power transmitted from the one input side disk 2 to the first output side disk 3 via the first power rollers 4 and 4. Further, the rear wheel drive shaft 14 is rotationally driven by the power transmitted from the second input disk 5 to the second output disk 6 via the second power rollers 7.

  By the way, in the case of the toroidal type continuously variable transmission as described above, when the torque passing through the toroidal type continuously variable transmission suddenly fluctuates or when the gear ratio fluctuates rapidly, the gear ratio is a predetermined value. There is a possibility that an overshoot will occur that converges to a predetermined value after going too far. When such overshoot occurs when the first and second power rollers 4 and 7 are greatly inclined (the transmission gear ratio of the toroidal continuously variable transmission is greatly deviated from 1), The power rollers 4 and 7 may be excessively inclined, and the peripheral surfaces of the power rollers 4 and 7 may easily reach the edges of the first, second input side, and output side disks 2, 5, 3, and 6. There is sex. That is, a contact ellipse formed on a rolling contact portion (traction portion) between the peripheral surface of each of the power rollers 4 and 7 and the inner surface of each of the disks 2, 5, 3, 6 is the disc 2, 5, It becomes easy to get on the edge of 3 and 6, and it becomes easy to produce the damage based on an edge load to each of these power rollers 4 and 7 and each disk 2, 5, 3, and 6. Such damage is not preferable because the durability of the power rollers 4 and 7 and the disks 2, 5, 3, and 6 is lowered.

For example, as described in Patent Document 2, in the case of a structure in which a trunnion that supports a power roller is supported by a support plate supported by a casing, the trunnion is excessively swung on the support plate or the like. By providing an abutting member for limiting, it is possible to prevent the trunnion and thus the power roller supported by the trunnion from being excessively inclined. However, as shown in FIGS. 5 to 8 described above, the first and second trunnions 30 and 31 are supported at both ends of the first and second swing frames 21 and 22 so as to be swingably displaceable. In such a case, each trunnion is not supported by the support plate as in the structure described in Patent Document 2 above. In the case of the structure shown in FIGS. 5 to 8 described above, the structure described in Patent Document 2 cannot be adopted as it is, for example, the space for providing the abutting member as described above is limited.
Further, when the torque passing through the toroidal-type continuously variable transmission fluctuates as described above, hunting that causes the gear ratio not to converge to a predetermined value may occur with overshoot. Such hunting is not preferable because it reduces transmission efficiency, increases vibration, and reduces drivability (running stability).

JP 2001-165262 A Japanese Utility Model Publication No. 6-43404

  The toroidal type continuously variable transmission of the present invention has been invented to realize a structure having excellent durability by preventing the power roller from being excessively inclined in view of the above-described circumstances.

The toroidal continuously variable transmission of the present invention includes an input side disk and an output side disk, a plurality of trunnions, and a plurality of power rollers.
Of these, the input-side disk and the output-side disk are supported so as to be concentric with each other and rotatable independently of each other, with the inner surfaces of the concave surfaces having arcuate cross sections facing each other.
Each trunnion swings about a pivot that is twisted with respect to the central axis of the input side disk and output side disk.
Each of the power rollers has a spherical convex surface, and is sandwiched between the input side disk and the output side disk while being supported by the trunnions.
Further, the same number of swing frames as the respective trunnions, in which the respective intermediate portions are pivotally supported by support shafts provided on the support frames provided around the respective trunnions, are freely swingable and displaceable by an actuator. At the same time, the pivots provided at both end portions of the trunnions are swingably supported at both end portions of the swing frames.
In particular, in the toroidal-type continuously variable transmission according to the present invention, there is provided swing limiting means for preventing the trunnions from swinging more than a predetermined distance between the swing frames and the trunnions. Provided.

  According to the toroidal type continuously variable transmission of the present invention configured as described above, each trunnion is extended and supported by each trunnion by the swing limiting means provided between each swing frame and each trunnion. Each power roller can be prevented from tilting excessively. That is, in the state where each of these power rollers is largely inclined (the transmission ratio of the toroidal type continuously variable transmission is greatly deviated from 1), the transmission ratio exceeds the predetermined value and then converges to the predetermined value. Even if the chute tends to occur, the trunnions that support the power rollers are prevented from excessively swinging by the swing limiter. For this reason, the contact ellipse formed in the rolling contact portion (traction portion) between the peripheral surface of each power roller supported by each trunnion and the inner surface of each disc does not run on the edge of each disc. The durability of each power roller and each disk can be ensured.

In the case of carrying out the present invention, preferably, as described in claim 2, the swing restriction means is constituted by a convex portion and a concave portion. These convex portions and concave portions are respectively provided on the end surfaces of the pivots provided at both ends of each trunnion and the inner surfaces of the swing frames facing the respective end surfaces (among the end surfaces of the pivot shaft and the inner surfaces of the swing frames). It does not matter which of these is provided with a convex portion or a concave portion). And the said convex part is combined with the said recessed part in the state which inserted the displacement (relative displacement) regarding the rocking | fluctuation direction of each of these trunnions. Then, by causing the side surfaces of the convex portions and the inner surface of the concave portions to come into contact with each other based on the swing of each trunnion, the trunnions are prevented from swinging more than a predetermined amount.
If comprised in this way, the structure which can prevent that each power roller supported by each said trunnion and each these trunnions inclines too much is simple and can be implement | achieved, without increasing installation space.

Further, when carrying out the invention described in claim 2, preferably, as described in claim 3, between the side surface of the convex portion and the inner surface of the concave portion, a resistance means that provides resistance to trunnion oscillation, In other words, resistance means (damper means) for applying a vibration damping force (damping force) to the trunnion is provided. For example, as described in claim 4, the lubricating oil introduced into the space constituted by the side surface of the convex portion and the inner surface of the concave portion is moved in and out of this space based on the displacement of the convex portion. It shall have the composition to make it. Alternatively, as described in claim 5, the resistance means is configured by holding an elastic member between the side surface of the convex portion and the inner surface of the concave portion facing each other.
By providing such resistance means (damper means), it is possible to prevent the respective trunnions and thus the respective power rollers supported by these trunnions from excessively tilting (unnecessarily vibrating). That is, even if there is a tendency for hunting that the gear ratio does not converge to a predetermined value due to sudden torque fluctuations, the trunnions that support the power rollers constitute the resistance means, Excessive rocking is prevented by an object (lubricant, elastic member) that resists the rocking of the trunnion. For this reason, it is difficult for such hunting to occur, and it is possible to prevent a decrease in transmission efficiency, an increase in vibration, and a decrease in running stability.

  1 to 3 show Embodiment 1 of the present invention corresponding to claims 1 to 4. The feature of the present invention is that the (first, second) power roller 4 (7) supported by the (first, second) trunnion 30 (31) is prevented from being inclined excessively. The first and second) are to ensure the durability of the power roller 4 (7) and the (first and second) input side and output side disks 2, 5, 3, 6 (see FIG. 5). Since the structure and operation of other parts are the same as those of the conventional structure shown in FIGS. 5 to 8 described above, overlapping illustrations and explanations are omitted or simplified, and the structure and parts of parts shown in FIGS. The operation will be described. In the following description, “first” and “second” of the first and second members indicating that the cavities are different will be omitted.

  Each swing frame 21 (22) supported by the support frame 23 (24) via a support shaft 34 (see FIGS. 5 to 8) has a pair of end plates 48 on both end faces of a substantially U-shaped main body 47, 48 is connected and fixed by screws 49 and 49. A pivot shaft provided concentrically at both ends of each trunnion 30 (31) inside a circular hole 51, 51 formed concentrically with a pair of support walls 50, 50 provided at both ends of the main body 47. 33 and 33 are supported only in a swingable manner in a state in which axial displacement is prevented. For this reason, in the case of the present embodiment, the radial needle bearings 52, 52 and the thrust needle bearings 53, 53 are provided between the inner peripheral surfaces of the circular holes 51, 51 and the outer peripheral surfaces of the pivots 33, 33. Is provided.

  And in order to arrange these needle bearings 52 and 53 concentrically, the outer peripheral surface of the outer rings 54 and 54 of these needle bearings 52 and 53, and a spacer 55 fitted and fixed to each of the circular holes 51 and 51, The inner peripheral surface of 55 is spherically fitted. The both needle bearings 52 and 53 are respectively arranged between the outer rings 54 and 54 which are aligned in this way and the inner rings 76 and 76 which are externally fitted to the outer peripheral surfaces of the pivots 33 and 33, respectively. It is configured by arranging a plurality of needles.

  As described above, each of the trunnions 30 (31) is supported by the respective swing frames 21 (22) so that only the swing displacement about the pivots 33 and 33 is freely displaced. The base half portion of the shaft 32a is supported so as to be swingable and displaceable. For this purpose, a circular hole 56 is formed in the intermediate portion of each trunnion 30 (31) so as to penetrate both the inner and outer peripheral surfaces of each trunnion 30 (31). Each of the circular holes 56 has a stepped shape in which a large-diameter portion 57 on the inner surface side and a small-diameter portion 58 on the outer surface side of each trunnion 30 (31) are continuously connected by a step portion 59. In the circular hole 56, the displacement shaft 32a formed integrally with the outer ring 61 constituting the angular thrust ball bearing 60 is rotatably supported by a radial needle bearing 62. Further, a thrust needle bearing 63 is provided between the outer side surface of the outer ring 61 and the inner side surface of each trunnion 30 (31), and the outer ring 61 and the power roller 4 (7) around the displacement shaft 32a. Displacement can be performed smoothly. The thrust roller bearing 60 and another radial needle bearing 64 support the power roller 4 (7) rotatably around the front half of the displacement shaft 32a.

  Further, in the case of the present embodiment, between the swing frames 21 (22) and the trunnions 30 (31), the trunnions 30 (31) are prevented from swinging more than a predetermined amount. Swing restricting means 65 and 65 are provided. In the case of the present embodiment, each of the swing limiting means 65 and 65 is constituted by a pair of convex portions 66 and 66 and a pair of concave portions 67 and 67, respectively. That is, the end surfaces of the pivots 33, 33 provided at both end portions of the trunnions 30 (31) on the inner side surfaces of the end plates 48, 48 coupled and fixed to both end portions of the swing frames 21 (22). The bottomed concave holes 68 and 68 are provided in a state of being recessed from the inner side surface in a portion facing the surface. And the said recessed part 67, 67 whose opening part is fan-shaped is provided in the radial direction 2 place position of these recessed hole parts 68 and 68, respectively.

  For this reason, in the case of the present embodiment, the partition members 69, 69 are fitted in the respective recessed hole portions 68, 68 in a state in which the rotation in the respective recessed portions 68, 68 is prevented. Each of the recesses 67 and 67 is constituted by a portion surrounded by the side surface 69 and the inner surfaces (inner peripheral surface and bottom surface) of the recessed hole portions 68 and 68. The partition members 69 and 69 are displaced in the circumferential direction of the concave hole portions 68 and 68 in a state of being engaged with the engaging concave portions 70 and 70 provided on the bottom surfaces of the concave hole portions 68 and 68. Is prevented. Further, the outer peripheral surfaces of the partition members 69 and 69 are fitted to the inner peripheral surfaces of the concave holes 68 and 68, so that the partition members 69 and 69 are related to the radial direction of the concave holes 68 and 68. Displacement is prevented. Further, a first oil passage for supplying lubricating oil to the portions of the partition members 68 and 68 that require cooling and lubrication, such as the thrust ball bearing 60 and the radial needle bearings 62 and 64. 71 is provided, and second oil passages 72 and 72 for supplying and discharging the lubricating oil in the recesses 67 and 67 are provided on the radially outer side of the first oil passage 71.

  On the other hand, at the end faces of the pivots 33, 33 provided at both ends of each trunnion 30 (31), at positions facing the respective recessed holes 68, 68 provided on the inner surfaces of the end plates 48, 48. An annular stopper member 73 is fixed. As shown in detail in FIG. 3, the stopper member 73 projects the projections 66 and 66 and the locking projections 75 and 75 on both side surfaces in the axial direction of the disc portion 74 from the respective side surfaces in the axial direction. Each is provided in a state. Each of the convex portions 66, 66 is a radially outward portion of one side surface of the disk portion 74 (the lower side surface of FIG. 3A, the upper side surface of FIG. 3B, and the outer side surface of FIG. 1). These are provided at two positions on the opposite side of the disk portion 74 in the radial direction. Each of the locking projections 75, 75 is located radially inward of the other side surface of the disk portion 74 (the upper side surface of FIG. 3A, the lower side surface of FIG. 3B, the inner side surface of FIG. 1). In the portion, the circular plate portion 74 is provided at a position shifted by 90 degrees from the convex portions 66 and 66 with respect to the circumferential direction of the disk portion 74.

  Then, the stopper members 73 are engaged with the engaging recesses (not shown) formed on the end surfaces of the pivots 33, 33 by engaging the engaging projections 75, 75 with the stopper members 73 at both ends of the trunnions 30 (31). Further, it is fixed in a state in which relative rotation with respect to the trunnion 30 (31) is prevented. In this state, the convex portions 66 and 66 are inserted into the concave portions 67 and 67 so as to be able to be displaced in the swing direction of the trunnions 30 (31). At the same time, the side surfaces of the convex portions 66 and 66 abut the side surfaces of the partition members 69 and 69 on the inner surfaces of the concave portions 67 and 67 based on the swing of the trunnions 30 (31). These trunnions 30 (31) are prevented from swinging more than a predetermined amount. In other words, the convex portions 66 and 66 are displaced in the swing direction of the trunnion 30 (31) in a state where the convex portions 66 and 66 are inserted into the concave portions 67 and 67, and the side surfaces of the convex portions 66 and 66 are the concave portions. It is allowed as long as it does not contact the inner surfaces of 67 and 67. Accordingly, the side surfaces of the convex portions 66 and 66 are contacted based on the distance between the side surfaces of the convex portions 66 and 66 and the inner surface of the concave portions 67 and 67 based on the swing of the trunnions 30 (31). By appropriately restricting the positional relationship of the contacting portions with respect to the swinging direction of the respective trunnions 30 (31), the respective trunnions 30 (31), and further each of the trunnions 30 (31) supported by the respective trunnions 30 (31) The inclination angle of the power roller 4 (7) can be regulated within a desired range.

  In the case of the present embodiment configured as described above, the swing restricting means 65, 65 provided between each swing frame 21 (22) and each trunnion 30 (31), that is, each projection 66 described above. , 66 and the recesses 67, 67 can prevent the trunnions 30 (31) and the power rollers 4 (7) supported by the trunnions 30 (31) from being excessively inclined. That is, in a state in which each of these power rollers 4 (7) is greatly inclined (a state in which the transmission ratio of the toroidal continuously variable transmission is greatly deviated from 1), a predetermined value is exceeded after the transmission ratio exceeds a predetermined value. The trunnions 30 (31) that support the power rollers 4 (7) have the side surfaces of the convex portions 66 and 66 of the concave portions 67 and 67. Further contact with the side surfaces of the partition members 69 and 69, which are the inner surfaces, is prevented from further swinging. Therefore, a rolling contact portion (traction) between the peripheral surface of each power roller 4 (7) supported by each trunnion 30 (31) and the inner surface of each of the input side and output side disks 2, 5 (3, 6). Contact ellipse formed on the edge of each of the disks 2, 5 (3, 6), and the power roller 4 (7) and each of the disks 2, 5 (3, 6). Durability can be secured.

  In the case of the present embodiment, the second passage is formed in a space (a portion indicated by a diagonal lattice in FIG. 2) formed by the side surfaces of the convex portions 66 and 66 and the inner surfaces of the concave portions 67 and 67. Lubricating oil is fed through the oil passages 72, 72. And the resistance means used as the resistance with respect to rocking | fluctuation of each said trunnion 30 (31) is comprised by filling lubricating oil in the said space. That is, by filling the space with the lubricating oil in this way, when the projections 66 and 66 are displaced as the trunnions 30 (31) swing, the lubrication is applied to the projections 66 and 66. Force to scrape oil (force to send the lubricating oil back into the second oil passages 72, 72, lubricating oil to the inner peripheral side of the convex portions 66, 66, the outer peripheral side peripheral surfaces, and the concave portions 67, 67 Force to pass through the gap between the inner surface).

Such a force prevents the trunnions 30 (31) from vibrating unnecessarily to the trunnions 30 (31) via the stopper members 73 and 73 provided with the convex portions 66 and 66. As power (damping force, damping force) For this reason, it is possible to prevent each of the trunnions 30 (31) and the respective power rollers 4 (7) supported by the respective trunnions 30 (31) from excessively tilting (unnecessarily vibrating). That is, even if there is a tendency for hunting that the gear ratio does not converge to a predetermined value due to a sudden torque fluctuation or the like, each trunnion 30 (31) supporting each power roller 4 (7) Excessive rocking based on force is prevented. For this reason, it is difficult for such hunting to occur, and it is possible to prevent a decrease in transmission efficiency, an increase in vibration, and a decrease in running stability.
As described above, the force (damping force, damping force) applied to each trunnion 30 (31) via each convex portion 66, 66 is the inner diameter of each of the second oil passages 72, 72 and each convex portion. By adjusting the dimensions of the gaps between the inner and outer diameter side surfaces of the portions 67 and 67 and the inner surfaces of the recesses 67 and 67, it can be regulated to a desired value.

  FIG. 4 shows a second embodiment of the present invention corresponding to claims 1 to 5. In the case of the present embodiment, the side surfaces of the convex portions 66, 66 provided on the stopper member 73, and the inner surfaces of the concave portions 67, 67 provided on the end plate 48 constituting the swing frame 21 (see FIG. 1) By providing the elastic members 77 and 77 between them, a resistance means is provided that provides resistance to the swing of the trunnion 30 (see FIG. 1). That is, by sandwiching the elastic members 77 and 77 such as compression coil springs between the side surfaces of the convex portions 66 and 66 facing each other and the inner surfaces of the concave portions 67 and 67, the convex portions 66 are provided. , 66 and the inner surfaces of the recesses 67, 67 are applied with forces in directions away from each other. Such a force is applied to each trunnion 30 via the stopper member 73 provided with the convex portions 66 and 66 in a direction that prevents the trunnions 30 from vibrating unnecessarily (damping force). , Damping force). In the case of the present embodiment, since the elastic members 77 and 77 as described above are provided, the lubricating oil is filled in the space formed by the side surfaces of the convex portions 66 and 66 and the inner surfaces of the concave portions 67 and 67. Absent. For this reason, the second oil passages 72 and 72 (see FIG. 2) are not provided in the partition member 69 constituting the recesses 67 and 67. Other configurations and operations are the same as those of the first embodiment described above, and thus redundant description is omitted.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cross-sectional view of an essential part showing Embodiment 1 of the present invention. The A arrow view which abbreviate | omits and shows a part. 4A is a perspective view showing a stopper member, with (A) having a surface facing the end surface of the trunnion facing upward and (B) having a surface facing the inner surface of the end plate facing upward. The figure similar to FIG. 2 which shows Example 2 of this invention. Sectional drawing which shows an example of a conventional structure. BB sectional drawing of FIG. CC sectional drawing. FIG. 8 is a cross-sectional view showing a portion substantially the same as FIG. 7 cut along a plane including the central axis of the first pivot provided at both ends of the first trunnion.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Toroidal type continuously variable transmission 2 1st input side disk 3 1st output side disk 4 1st power roller 5 2nd input side disk 6 2nd output side disk 7 2nd power roller 8 Torque converter 9 Input shaft 9a Front half 9b Second half 10 Forward / reverse switching unit 11 Forward clutch 12 Reverse clutch 13 Front wheel drive shaft 14 Rear wheel drive wheel 15 Carrier 16 Ball spline 17 Loading device 18 Support cylinder 19 Stay 20 Support ring 21 First swing frame 22 Second swing frame 23 First support frame 24 Second support frame 25 Front wheel output gear 26 Front wheel driven gear 27 Front wheel differential gear 28 Rear wheel output gear 29 Rear wheel driven gear 30 First trunnion 31 Second trunnion 32, 32a Displacement shaft 33 First pivot 34 Support 35 Columns 36a, 36b Hydraulic cylinders 37a, 37b Rods 38a, 38b Piston 39 Control valve 40 Cam surface 41 Plunger 42 Spool 43 Sleeve 44 Control motor 45 First cavity 46 Second cavity 47 Main body 48 End plate 49 Screw 50 Support wall 51 circular hole 52 radial needle bearing 53 thrust needle bearing 54 outer ring 55 spacer 56 circular hole 57 large diameter part 58 small diameter part 59 step part 60 thrust ball bearing 61 outer ring 62 radial needle bearing 63 thrust needle bearing 64 radial needle bearing 65 rocking Limiting means 66 Convex part 67 Concave part 68 Concave hole part 69 Partition member 70 Engaging concave part 71 First oil passage 72 Second oil passage 73 Stopper member 74 Disk part 75 Locking convex part 76 Inner ring 77 Elastic member

Claims (5)

  An input side disk and an output side disk that are supported concentrically and independently of each other in a state where the inner side surfaces of the concave surfaces each having an arcuate cross section are opposed to each other, and the centers of these two disks A plurality of trunnions that swing around a pivot that is twisted with respect to the shaft, and a plurality of trunnions that are sandwiched between the two disks while being supported by each trunnion and that have a circumferential convex surface. A power frame, and a support frame provided around each trunnion, with the same number of swing frames as each trunnion pivotally supported by a support shaft. In the toroidal continuously variable transmission in which the pivots provided at both ends of the trunnions are swingably supported at both ends of the swing frames, Serial between each oscillating frame and the trunnions, the toroidal type continuously variable transmission, characterized in that the trunnions are provided with a swinging limiting means for blocking to predetermined or rocking.   The swing limiting means is constituted by a convex portion and a concave portion provided on the end surfaces of the pivots provided at both ends of each trunnion and the inner surfaces of the respective swing frames facing the respective end surfaces. Is combined with a state in which the displacement in the swing direction of each trunnion is inserted into the recess, and the side surface of the projection and the inner surface of the recess are brought into contact with each other based on the swing of each trunnion, The toroidal continuously variable transmission according to claim 1, wherein each trunnion is prevented from swinging more than a predetermined amount.   The toroidal-type continuously variable transmission according to claim 2, wherein a resistance means is provided between the side surface of the convex portion and the inner surface of the concave portion to provide resistance to trunnion oscillation.   The resistance means has a configuration in which lubricating oil introduced into a space constituted by the side surface of the convex portion and the inner surface of the concave portion is made to enter and exit from this space based on the displacement of the convex portion. The toroidal continuously variable transmission described. The toroidal type continuously variable transmission according to claim 3, wherein the resistance means is configured by sandwiching an elastic member between a side surface of the convex portion and an inner surface of the concave portion facing each other.

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