JP2006017144A - Toroidal continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To easily adjust an assembly position of displacement shafts 33 and 33 for supporting power rollers 4 and 7 with respect to axial directions of disks 2, 5, 3 and 6. In addition, it is possible to realize a structure that can prevent a poor synchronization of the transmission gear ratio and instability of the transmission gear ratio control and secure sufficient durability at a low cost.
A thrust needle bearing 51, between axial end surfaces of support cylinders 49 and 49 of the swing frames 21 and 22 and side surfaces of support rings 20 and 20 constituting the support frames 23 and 24, respectively. 51 is installed. By adjusting the thickness dimension of the thrust traces 52, 52 constituting the thrust needle bearings 51, 51 for each of the swing frames 21, 22, the axial direction of the disks 2, 5, 3, 6 The displacement of the displacement shafts 33, 33 is suppressed to a regulation value or less.
[Selection] Figure 1

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. 3 to 6 show a toroidal continuously variable transmission for a four-wheel drive vehicle with a large displacement described in Patent Document 1. 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 concentrically arranged in the vicinity of the front and rear end portions of the rear half portion 9b with the inner side surfaces that are concave surfaces each having an arcuate cross section facing each other. It is supported so that it can rotate in synchronization with each other. Therefore, in the illustrated example, the first input side disk 2 provided on the front side (the left side in FIG. 3) 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. 3) is supported by a rear end portion of the latter half portion 9b via a ball spline 16. 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 freely rotatable relative to each other while supporting an axial load (thrust load) applied between them by a thrust bearing 25 provided therebetween. In the illustrated example, a thrust needle bearing is used as the thrust bearing 25.

  Further, a front wheel output gear 26 is fixed to the outer surface side of the first output side disk 3, and the front wheel output gear 26 and the front wheel drive shaft 13 are coupled via a front wheel driven gear 27. 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 28. On the other hand, a rear wheel output gear 29 is fixed to the outer surface side of the second output side disk 6, and the rear wheel output gear 29 and the rear wheel drive shaft 14 are connected to a rear wheel driven gear 30. Thus, the rear wheel drive shaft 14 is rotatably driven 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 inner surfaces of the first and second trunnions 31 and 32, respectively, around the displacement shafts 33 and 33 provided in a state of protruding from the inner surface. It is supported rotatably. The centers of the displacement shafts 33 and 33 and the centers of the power rollers 4 and 7 are offset from each other in a direction substantially perpendicular to the axial direction of the disks 2, 5, 3, and 6 (offset). is doing. This is because, as is well known in the field of toroidal-type continuously variable transmissions, the elastic deformation of each member that occurs during operation is absorbed. The first and second trunnions 31 and 32 do not intersect the central axes of the disks 2, 5, 3, and 6 provided concentrically with each other at both ends. Centering on the first and second pivots 34 and 34 (the second pivot is not shown) existing at a twisted position that is perpendicular or nearly perpendicular to the direction of the central axes of 5, 3, and 6. Swing. The first and second trunnions 31 and 32 are swingably supported at both ends of the first and second swing frames 21 and 22, respectively.

  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 35 and 35 are provided so as to be swingable and displaceable about the support shafts 35 and 35 provided in a direction parallel to or near the parallel to the central axes 5, 3, and 6. Each of the first and second support frames 23 and 24 has a pair of support rings 20 and 20 arranged in parallel with each other, on the outer diameter side of the three support columns 36 and 36 constituting the stay 19. Combining with each other through the end. The support shafts 35 and 35 constitute the first and second support frames 23 and 24 at intermediate positions of the support columns 36 and 36 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 36 and 36 adjacent in the circumferential direction.

  Further, the first and second swing frames 21 and 22 are swung by hydraulic cylinders 37a and 37b 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 37a and 37b is provided at a position aligned with both ends of each of the swing frames 21 and 22 at a part of each of the support rings 20 and 20, respectively. On the other hand, rods 38a and 38b are arranged at both ends of the first and second swing frames 21 and 22 so as to be aligned with the hydraulic cylinders 37a and 37b in parallel with the support shafts 35 and 35, respectively. The first and second swing frames 21 and 22 are supported and fixed so as to penetrate both end portions. The pistons 39a, 39b fitted to the hydraulic cylinders 37a, 37b are engaged with the rods 38a, 38b.

  Of the hydraulic cylinders 37a and 37b provided at the time of shifting, two pairs are provided for each of the swinging frames 21 and 22 (four for each swinging frame, a total of 24 toroidal-type continuously variable transmissions 1 as a whole). Then, one hydraulic cylinder 37a (37b) provided on one end side in the length direction of each swing frame 21, 22 is extended and the other hydraulic cylinder 37b (37a) is contracted, so that each swing frame 21, 22 is oscillated and displaced by a predetermined amount in a predetermined direction.

  A control valve 40 for controlling the supply and discharge of pressure oil to and from the hydraulic cylinders 37a and 37b 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 37a and 37b, the first and second trunnions 31 supported by the swing frames 21 and 22, A cam surface 41 provided on the outer surface of 32 displaces the spool 43 of the control valve 40 via a plunger 42 attached to the control valve 40 to switch the control valve 40. The sleeve 44 that constitutes the control valve 40 together with the spool 43 is displaced to a predetermined position by a control motor 45 so that a desired gear ratio can be realized at the time of shifting. One such control valve 40 and control motor 45 are provided on the first cavity 46 side including the first input side disk 2 and the first output side disk 3, the second input side disk 5 and the second input disk 5. One is provided on the second cavity 47 side including the output side disk 6, and two are provided in the entire toroidal type continuously variable transmission 1. A control motor 40 on the first cavity 46 side is provided by the control motor 45 on the first cavity 46 side, a control valve 40 on the second cavity 47 side is provided by the control motor 45 on the second cavity 47 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).

  Due to such a configuration, at the time of shifting, the first and second swing frames 21 and 22 are connected to the support shafts 35 and 35 based on the supply and discharge of the pressure oil to and from the hydraulic cylinders 37a and 37b. The center is oscillated and displaced by a predetermined amount in a predetermined direction. As a result, the first and second trunnions 31 and 32 supported by the swing frames 21 and 22 perform an arc motion (swivel motion) about the support shafts 35 and 35, respectively. Then, due to the displacement of the first and second trunnions 31 and 32 in the axial direction of the first and second pivots 34 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 31 and 32 are pivotally supported by the first and second swing frames 21 and 22 with the change in the direction of the force. And the contact positions of the peripheral surfaces of the first and second power rollers 4 and 7 and the inner surfaces of the disks 2, 5, 3 and 6 are changed. The rotational speed ratio between the first and second input 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 disk 2 to the first output disk 3 via the first power rollers 4 and 4. 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.

  In order to ensure the efficiency and durability of the toroidal-type continuously variable transmission as described above, the positional relationship between the constituent components must be regulated with high accuracy. In particular, as shown in FIGS. 3 to 6 described above, in the case of a structure in which the transmission gear ratio is changed by moving the first and second swing frames 21 and 22 in an arc, as described in Patent Document 2 and the like. Compared to a structure in which the gear ratio is changed by directly displacing the trunnion with an actuator in the axial direction of the pivot axis, a slight deviation between the above components causes synchronization of the gear ratios of the first and second power rollers 4 and 7. It is easy to be connected with defect. Then, based on such a gear ratio synchronization failure, the gear ratio control may become unstable, and the efficiency and durability may be reduced.

  For example, the positions of the displacement shafts 33 and 33 with respect to the axial direction of each of the disks 2, 5, 3 and 6 (left and right direction in FIG. 3) , 7 in order to synchronize the transmission ratios between the input disks 2 and 5 and the output disks 3 and 6 with each other. In particular, the base half of the displacement shafts 33, 33 that rotatably support the power rollers 4, 4 (or 7) existing in the same cavity 46 (or 47) around the respective front half, If the positions of the disks 2, 5, 3, 6 in the axial direction are deviated, the transmission efficiency and durability are remarkably lowered. That is, in such a case, the rolling contact between the peripheral surface of each of the power rollers 4, 4 (or 7) and the inner surface of the input side disk 2 (or 5) and the output side disk 3 (or 6). Excessive slip occurs in the section (traction section), and transmission efficiency and durability are significantly reduced. Also, the gear ratio control becomes unstable. In other words, in order to ensure transmission efficiency and durability and to stabilize gear ratio control, the axial directions of the disks 2, 5, 3, 6 in the base half of the displacement shafts 33, 33 are described. It is necessary to match the position with respect to.

  However, the positions of the displacement shafts 33 and 33 are easily displaced in the axial direction of the disks 2, 5, 3, and 6 due to the shape error, dimensional error, and assembly error of many members. And when it shifted | deviated, the gear ratio between the said input side disk 2 (or 5) and the said output side disk 3 (or 6) was rotatably supported by each said displacement shaft 33,33, respectively. The power rollers 4, 4 (or 7) are slightly different. In such a state, not only the transmission efficiency and durability of the toroidal-type continuously variable transmission are remarkably lowered but also the gear ratio control is unstable due to the excessive slip generated in each traction section as described above. become.

  In order to eliminate such an inconvenience, it is necessary to match the assembly positions of the displacement shafts 33 and 33 with respect to the axial directions of the disks 2, 5, 3, and 6. Because of the accumulation of the above errors, it is difficult. In particular, the arrangement directions of the central axes of the pivots 34, 34 provided at both ends of each trunnion 31 (or 32) shown by the chain line α in FIG. In the case where the directions of the central axes of 3 and 6 are not perpendicular to each other, it is difficult to adjust the assembly position. That is, as shown in FIG. 7, in the case of a structure in which the trunnion 31 (or 32) is supported with a so-called caster angle with respect to the swing frame 21 (or 22), Adjustment work for matching the installation positions of the shafts 33 and 33 is difficult.

JP 2001-165262 A JP 11-153203 A

  In view of the circumstances as described above, the toroidal-type continuously variable transmission of the present invention is capable of easily adjusting the assembly position of the displacement shaft for supporting each power roller in the axial direction of each disk. The present invention has been invented to realize a structure that can prevent a poor synchronization of the transmission ratio and instability of the transmission ratio control and can secure sufficient durability at a low cost.

The toroidal type continuously variable transmission of the present invention includes an input side disk, an output side disk, a plurality of trunnions, and the like, as in the conventional toroidal type continuously variable transmission described in Patent Document 1 and the like. And a plurality of displacement shafts 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 axes of the input and output disks.
The displacement shafts are supported by the trunnions so that their base halves are swingable.
Further, each of the power rollers is sandwiched between the input-side disk and the output-side disk in a state of being rotatably supported around the front half of each of the displacement shafts. Convex surface.
And each said trunnion pivotally supports each said pivot provided in each both ends at the both ends of the same number of rocking | fluctuation frames as each of these trunnions.
In addition, each of these swing frames is inserted into a support cylinder portion provided at each intermediate portion through a support shaft installed on a support frame provided around each trunnion, and an actuator provided between the support frames. It can be swung freely.
In particular, in the toroidal-type continuously variable transmission according to the present invention, each axially opposite end surface of the support tube portion of each swing frame and the support frame are each between a pair of thrust traces. A thrust needle bearing comprising a plurality of needles is provided. Then, by adjusting the axial dimension of each thrust needle bearing for each swing frame, the displacement of the position of each displacement shaft with respect to the axial direction of each disk is suppressed to a regulation value or less.

  According to the toroidal-type continuously variable transmission of the present invention configured as described above, it is possible to easily adjust the assembly position of each displacement shaft for supporting each power roller in the axial direction of each disk. That is, if the axial dimension of each thrust needle bearing provided between the axially opposite end faces of the support cylinder portion of each swing frame and the support frame is changed, the assembly position of each displacement shaft with respect to the axial direction of each disk is changed. Can be adjusted easily. In addition, it is possible to realize a structure capable of preventing the transmission ratio from being poorly synchronized and the transmission ratio control from becoming unstable and ensuring sufficient durability at a low cost.

Preferably, when carrying out the present invention, as described in claim 2, a plurality of units present in a cavity existing between an inner surface of a pair of input-side disks and an inner surface of an output-side disk facing each other. The regulation value relating to the displacement of the displacement axis is 0.1 mm, more preferably 0.05 mm.
If the displacement of the assembly position of each displacement shaft with respect to the axial direction of each disk is suppressed to 0.1 mm or less, the circumferential surface of each power roller is considered when considering a general toroidal continuously variable transmission for automobiles. At the traction portion between the input side disk and the inner side surface of the output side disk, unnecessary slip that occurs in addition to the inevitable slip associated with the spin of the contact ellipse can be suppressed to a practically acceptable level. In addition, it is possible to prevent the transmission ratio from becoming poorly synchronized and the transmission ratio control from becoming unstable, ensuring the efficiency of the toroidal-type continuously variable transmission and ensuring sufficient durability. If the regulation value is suppressed to 0.05 mm or less, the efficiency and durability can be ensured at a higher level.

Preferably, as described in claim 3, both end portions of each support shaft are supported and fixed to a pair of support rings constituting the support frame, and the inner peripheral surface of each support cylinder portion and each of these support shafts are supported. A radial needle bearing is installed between the outer peripheral surface, and a thrust needle bearing is installed between both axial end surfaces of each of the support cylinders and the side surfaces of the support rings. Then, the position of each displacement shaft in the axial direction of each disk is adjusted by changing the thickness dimension of the thrust trace constituting each thrust needle bearing.
If a radial needle bearing is provided between the inner peripheral surface of each support cylinder and the outer peripheral surface of each support shaft, each swing frame can be swingably supported by the support frame with a light force.
Furthermore, if the installation position of each displacement shaft is adjusted by changing the thickness dimension of the thrust trace, this adjustment operation can be performed easily and reliably at low cost. That is, the axial dimension of each thrust needle bearing can be adjusted by changing the diameter of each needle, but preparing various types of needles having slightly different diameters causes an increase in cost. On the other hand, if it is configured to be adjusted by changing the thickness dimension of the above-mentioned thrust trace, even if multiple types of thrust traces with different thicknesses are prepared, the cost increase can be suppressed and the adjustment work can be suppressed. Can be done easily.

Further, as described in claim 4, it is effective that the present invention is implemented with a structure in which the directions of the central axes of the pivots provided at both ends of each trunnion are not perpendicular to the direction of the central axis of each disk. It is.
As described above, in the case of such a structure, it is difficult to adjust the position of each displacement axis with respect to the axial direction of each disk. Therefore, if the present invention is implemented with such a structure, the effects of the present invention can be obtained effectively.

  1 and 2 show an embodiment of the present invention. The feature of the present invention relates to the axial direction of each of the disks 2, 5, 3, and 6 in order to prevent poor synchronization of the transmission ratio and instability of the transmission ratio control and to ensure sufficient durability. This is to realize a structure capable of easily adjusting the assembly position of the displacement shafts 33 and 33 for supporting the power rollers 4 and 7. Since the structure and operation of the other parts are the same as those of the conventional structure shown in FIGS. 3 to 6 described above, overlapping illustrations and explanations are omitted or simplified. The explanation will be focused on the parts.

  The intermediate portions of the first and second swing frames 21 and 22 are supported by the first and second support frames 23 and 24 so as to be swingable and displaceable about the support shafts 48 and 48, respectively. For this purpose, both ends of each of the support shafts 48, 48 are supported and fixed to the support rings 20, 20 constituting the support frames 23, 24, one pair for each of the support frames 23, 24. ing. Further, support cylinder portions 49 and 49 are provided at intermediate portions of the swing frames 21 and 22, respectively. Further, radial needle bearings 50, 50 are provided between the inner peripheral surfaces of the support cylinder portions 49, 49 and the intermediate outer peripheral surfaces of the support shafts 48, 48. Further, thrust needle bearings 51 and 51 are provided between the axial end surfaces of the support cylinders 49 and 49 and the side surfaces of the support rings 20 and 20, respectively. Each of these thrust needle bearings 51, 51 is formed by arranging a plurality of needles 53, 53 arranged radially by a pair of thrust traces 52, 52.

  When the half toroidal toroidal continuously variable transmission as shown in the figure is operated, the first and second trunnions 31 and 32 are supported by the swing frames 21 and 22 respectively. A thrust load is applied to the power rollers 4 and 7, and this thrust load is applied as a radial load between the support cylinder portions 49 and 49 and the support shafts 48 and 48. Further, each of the discs out of the thrust load applied to each of the power rollers 4 and 7 unless the gear ratio between the input discs 2 and 5 and each of the output discs 3 and 6 is 1 (constant speed transmission). A component force in the axial direction of 2, 3, 5, 6 is applied as a thrust load between the support cylinder portions 49, 49 and the support shafts 48, 48. In the case of the present embodiment, the radial displacements of the swing frames 21 and 22 are caused by the radial needle bearings 50 and 50 and the thrust needle bearings 51 and 51 regardless of the radial load and the thrust load as described above. Can be performed smoothly.

  In the case of the present embodiment, the axial direction of each of the disks 2, 5, 3, 6 is changed by changing the thickness dimension of each of the thrust traces 52, 52 of the thrust needle bearings 51, 51 (see FIG. The positions of the respective displacement shafts 33 and 33 with respect to the left and right direction (1 to 2) are adjusted. Then, the displacement of the displacement shafts 33, 33 with respect to the axial direction of the disks 2, 5, 3, 6 is kept within a range of about 0.05 to 0.1 mm and below a preset regulation value. Yes.

  In the case of this embodiment, it is assumed that it is used as a transmission unit of an automatic transmission for a four-wheel drive vehicle, and the gear ratio between the first input side disk 2 and the first output side disk 3 is assumed. The gear ratio between the second input side disk 5 and the second output side disk 6 does not match except during straight running. That is, the transmission ratio of the first cavity 46 and the transmission ratio of the second cavity 47 are controlled independently of each other. Therefore, it is the displacement existing in the same cavity 46 (or 47) that suppresses the displacement of the displacement shafts 33, 33 with respect to the axial direction of the disks 2, 5, 3, 6 below the regulation value. It may be between the shafts 33. In other words, it is not necessary to suppress the displacement of the positions of the displacement shafts 33 and 33 between the different cavities 46 and 47 below the regulation value. On the other hand, when the present invention is applied to a toroidal-type continuously variable transmission having a plurality of cavities for a general two-wheel drive vehicle, the displacement of each displacement shaft is restricted even between different cavities. Keep it below the value.

  According to the toroidal type continuously variable transmission of the present embodiment configured as described above, the first and second power rollers 4 and 7 in the axial direction of the disks 2, 5, 3, and 6 are supported. It is possible to easily adjust the assembly position of the displacement shafts 33, 33. This adjustment operation is carried out by connecting both end surfaces in the axial direction of the support tube portions 49, 49 provided at the intermediate portions of the first and second swing frames 21, 22 and the first and second support frames 23, 24. This is done by changing the thickness dimension of the thrust traces 52, 52 constituting the thrust needle bearings 51, 51 provided between the supporting rings 20, 20 constituting the thrust rings. For example, in order to move the first swing frame 21 in the same direction in order to move the position of the displacement shaft 33 shown in FIG. 2 to the right in the figure, the right thrust needle bearing 51 in the figure is configured. The (total) thickness dimension of the thrust traces 52, 52 to be reduced is reduced. In accordance with this, the (total) thickness dimension of the thrust traces 52 and 52 constituting the thrust needle bearing 51 on the left side of the figure is increased. Each of the above thrust traces 52, 52 is a simple circular flat plate, and it is easy to prepare and use various types of those having slightly different thickness dimensions. Therefore, it is possible to easily adjust the assembly position of the displacement shafts 33 and 33 in the axial direction of the disks 2, 5, 3 and 6. And, in the adjusted state, it is possible to prevent a gear ratio synchronization failure and a gear ratio control from becoming unstable, and to realize a structure capable of ensuring sufficient durability at a low cost.

  In FIG. 1, intermediate portions of the synchronous cable are connected to a part of the first and second support frames 23, 24 via radial needle bearings 54, 54 different from the radial needle bearings 50, 50. Guide rollers 55 and 55 are installed for guiding. In this synchronous cable, a plurality of trunnions 31 (or 32) existing in the same cavity 46 (or 47) are spanned between the trunnions 31 (or 32), and the swing amount of the plurality of trunnions 31 (or 32) is mechanically increased. To match. Such a synchronous cable structure is well known in the technical field of toroidal type continuously variable transmissions, and therefore detailed illustration and description thereof will be omitted.

The principal part sectional drawing which shows the Example of this invention. The A section enlarged view of FIG. Sectional drawing which shows an example of a conventional structure. BB sectional drawing of FIG. CC sectional drawing. Sectional drawing which shows the state substantially the same as FIG. 5 in the state cut | disconnected by the plane containing the central axis of the 1st pivot provided in the both ends of the 1st trunnion. The figure which took out the trunnion and the rocking | fluctuation frame, and was seen from the radial inside of each disc.

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 Thrust bearing 26 Front wheel output gear 27 Front wheel driven gear 28 Front wheel differential gear 29 Rear wheel output gear 30 Rear wheel driven gear 31 First trunnion 32 Second trunnion 33 Displacement axis 34 First pivot DESCRIPTION OF SYMBOLS 5 Support shaft 36 Support | pillar part 37a, 37b Hydraulic cylinder 38a, 38b Rod 39a, 39b Piston 40 Control valve 41 Cam surface 42 Plunger 43 Spool 44 Sleeve 45 Control motor 46 First cavity 47 Second cavity 48 Support shaft 49 Support cylinder part 50 Radial needle bearing 51 Thrust needle bearing 52 Thrust trace 53 Needle 54 Radial needle bearing 55 Guide roller

Claims (4)

  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, which are concave surfaces each having an arcuate cross section, are opposed to each other, and these input side disks and A plurality of trunnions that swing around a pivot that is twisted with respect to the center axis of the output-side disk, a displacement shaft in which the respective base halves are swingably supported by each trunnion, and each of these displacement axes Each of the trunnions includes a plurality of power rollers that are sandwiched between the input-side disk and the output-side disk in a state of being rotatably supported around the front half of the front half, and whose circumferential surfaces are spherical convex surfaces. The pivots provided at both ends are pivotally supported at both ends of the same number of swing frames as the trunnions, and the swing frames are provided at intermediate portions. In a toroidal type continuously variable transmission in which a support shaft installed on a support frame provided around each trunnion is inserted into a holding cylinder part and is swingably displaceable by an actuator provided between the support frame and the support frame. In addition, a thrust needle bearing is provided between each end face in the axial direction of the support cylinder portion of each swing frame and the support frame, each of which includes a plurality of needles sandwiched between a pair of thrust traces. In addition, by adjusting the axial dimension of each of the thrust needle bearings for each of the swing frames, the displacement of the displacement shafts with respect to the axial direction of the disks is suppressed to a regulation value or less. Toroidal type continuously variable transmission.   The regulation value relating to the displacement of the positions of the plurality of displacement shafts existing in the cavity existing between the inner surface of the pair of input-side disks facing each other and the inner surface of the output-side disk is 0.1 mm. Item 2. A toroidal-type continuously variable transmission according to item 1.   Each support shaft has its both ends supported and fixed to a pair of support rings constituting a support frame, and a radial needle bearing is provided between the inner peripheral surface of each support cylinder and the outer peripheral surface of each support shaft. Thrust needle bearings are respectively installed between the axial end surfaces of the support cylinders and the side surfaces of the support rings, and the positions of the displacement shafts in the axial direction of the discs are determined by the thrust needles. The toroidal continuously variable transmission according to any one of claims 1 to 2, wherein the torsion type continuously variable transmission is adjusted by changing a thickness dimension of a thrust trace constituting the bearing.   The toroidal continuously variable transmission according to any one of claims 1 to 3, wherein the direction of the central axis of the pivot provided at both ends of each trunnion is not perpendicular to the direction of the central axis of each disk.

Images