DE19947851A1 - Infinitely variable toroidal drive for motor vehicles etc. has support units for pivot shafts fastened directly to inner surface of drive housing - Google Patents

Abstract

The toroidal drive incorporates support units (54,55) to the side of drive rollers (45), to support pivot shafts (29,30) for a pivot movement and an axial movement. The elements forming the support units are directly fastened to an inner surface of the drive housing (5). The support elements are bridges with ends supporting the pivot shafts, which are located on the ends of several pivot journals (27,28). The bridges are fastened to an inner housing surface. The pivot shafts are displaceable relative to the ends of the bridges via mortise connections (56). Needle bearings (57) in the connections support the shafts.

Description

The invention relates to the field of stepless toroid gearbox, for example as a speed change unit a transmission of a motor vehicle or as a transmission in various industrial machines can be used.

A toroidal type continuously variable transmission, as shown schematically in FIGS . 24 and 25, is used as a motor vehicle transmission. As is known, for example, from JP 62-71465-A (1987), a drive disk 2 is supported coaxially with an input shaft 1 in such a continuously variable toroidal gear, while an output disk 9 is attached to one end of an output shaft 3 arranged coaxially with the input shaft 1 . In a housing (which will be described later in connection with FIGS. 26 to 28), which holds the continuously variable toroidal gear ent, pivot pins 7 are provided, which are about pivot shafts 6 , which are in relation to the drive shaft 1 and the output shaft 3 staggered positions are pivotable.

Therefore, each pivot pin 7 is provided on its two outer end faces with the swivel shafts 6 , which are coaxial to one another, which is why the swivel shafts 6 do not intersect the center lines of the disks 2 , 4 , but run perpendicular to these center lines. Furthermore, support the middle portions of the pivot 7, the near ends of displacement shafts 8 , such that the inclination angle of the displacement shafts 8 can be adjusted by pivoting the pivot 7 about the pivot shafts 6 . To the supported by the pivot 7 Ver shift shafts 8 drive rollers 9 are rotatably supported. The drive rollers 9 are inserted between the drive disc 2 and the driven pulley 4 . The inner surfaces 2a, 4a of the discs 2, 4, which face Einan of which have concave surfaces that are obtained by rotating of circular arcs whose centers are on the pivot shaft 6 to the drive shaft 1 and the output shaft. 3 The circumferential surfaces 9 a of the drive rollers 9, each of which has a spherical convex shape, are located on the inner surfaces 2 a, 4 a of. A press device 10 of the loading cam type is and the output drive disc interposed between the drive pulley 2 9 in such a manner that the driving disc 2 by the pressing device 10 elastically against the driven pulley 4 may be forced. The Preßvor device 10 includes a cam plate 11 which is rotated together with the drive shaft 1 , and a plurality (for example four) rollers 13 which are held by a bracket 12 . A side surface (left side face in FIGS. 24 and 25) of the cam plate 11 is as Noc kenoberfläche 14 is formed which has an unevenness or waviness, the circumferentially he stretches, while an outer surface (right Oberflä surface in Figs. 24 and 25) the drive pulley 2 has a similar cam surface 15 . The plurality of rollers 13 are rotatable about axes which extend radially with respect to the center line of the drive shaft 1 .

When the cam plate 11 is rotated with the drive shaft 1 rotating during the operation of the toroidal continuously variable transmission having the above-described construction, the plurality of rollers 13 are forced by the cam surface 14 against the cam surface 15 formed on the outer surface of the drive pulley 2 . As a result, the drive pulley 2 against the plurality of drive rollers 9 is forced at the same time the driving disc 2 is due to the frictional engagement between the pair Noc kenoberflächen 14, 15 and the plurality of rollers 13 is rotated. The rotation of the drive pulley 2 is transmitted to the driven pulley 4 via the plurality of drive rollers 9 , whereby the driven shaft 3 , which is fastened to the driven pulley 9 , is rotated.

When the speed ratio (gear ratio) to be changed between the driving shaft 1 and the output shaft 3 in the direction of a reduction ratio, the pivot pin 7 including the shift shafts 8 ge about the pivot shafts 6 in predetermined directions are pivots, so that the peripheral surface 9a of the drive rollers 9 at a portion of the inner surface 2 a of the drive pulley 2 in the vicinity of the center or a portion of the inner surface 4 a of the driven pulley 9 in the vicinity of its outer circumference, as shown in Fig. 24. On the other hand, if the speed ratio is to be changed in the direction of a translation, the pivots 7 are pivoted about the pivot shafts 6 in the opposite direction, whereby the displacement shafts 8 are inclined so that the peripheral surface 9 a of the drive shafts 9 on a portion of the inner surface 2 a of the drive pulley 2 in the vicinity of its outer circumference or against a portion of the inner surface 4 a of the driven pulley 4 in the vicinity of the center, as shown in FIG. 25. If an intermediate value is selected between the values shown in FIGS . 24 and 25 for the inclination angle of the displacement waves 8 , an intermediate transmission ratio can be obtained.

It is well known that in a real motor vehicle gearbox, which is formed by a stepless toroidal gear, a stepless toroidal gear of the double-cavity type is provided for this, in which two groups of drive pulleys 2 , driven pulleys 4 and drive rollers 9 are provided, which are parallel in the direction of force transmission are arranged. FIGS. 26 and 27 show an example of such a toroidal continuously variable transmission of the double cavity type which is known from JP-A 8-23386 (1996).

In a housing 5 , a drive shaft 1 a is rotatably supported. A cylindrical transmission shaft 16 is rotatably supported coaxially to the drive shaft 1 a, so that it can rotate relative to the drive shaft 1 a. At the two ends of the transmission shaft 16 first and second drive disks 17 , 18 , which correspond to first and second outer disks, are supported via ball-groove connections 19 , so that the inner surfaces 2 a of these disks face one another. Therefore, the first and two drive pulleys 17 , 18 in the housing 5 are supported coaxially to one another and rotatably synchronously.

First and second driven disks 20 , 21 , which correspond to first and second inner disks, are supported around an intermediate portion of the transmission shaft 16 via a sleeve 22 . On an outer peripheral surface of an intermediate portion of the sleeve 22 , an output gear 23 is formed in one piece, the sleeve having an inner diameter that is larger than the outer diameter of the transmission shaft 16 . The sleeve is rotatably supported by a support wall 24 provided in the housing 5 via a pair of bearings 25 in such a way that the sleeve is arranged axially fixed and rotatable coaxially with the transmission shaft 16 . The first and second output disks 20 , 21 are connected via a keyway connection to both ends of the sleeve 22 , which is rotatably mounted around the intermediate portion of the transmission shaft 16 , the inner surfaces 4 a of the disks 20 , 21 pointing in opposite directions. Consequently, the first and second driven pulleys 20 , 21 are supported coaxially to the first and second drive pulleys 17 , 18 and can be rotated independently of the first and second drive pulleys 17 , 18 , the inner surfaces 4 a corresponding to the inner surfaces 2 a first and second drive disks 17 , 18 are facing.

Furthermore, two pairs of yokes 26 a, 26 b are supported on an inner wall of the housing 5 on both sides of the first and second driven disks 20 , 21 , between which the driven disks 20 , 21 are arranged. The yokes 26 a, 26 b correspond to the yokes that form the first and second sub support devices of the invention, and are each formed as a rectangular frame, which are made by press working a metal plate such as a steel plate or by forging a metal material such as steel. The yokes 26 a, 26 b are provided at their four corners with circular support holes 31 to rotatably support first and second pivot shafts 29 , 30 provided at both ends of first and second pivots 27 , 28 (described later), furthermore, the yokes 26 a, 26 b are provided with circular locking holes 32 which, in the middle sections, of the yokes in the width direction (left-right direction in FIGS. 27, 28) at both ends of the transmission shaft 16 in the axial direction (left-right Direction in Fig. 26) are formed. The pairs of yokes 26 a, 26 b, each having the configuration described above, are supported by support posts 33 a, 33 b, which are formed on opposite sections of the inner wall of the housing 5 , so that they are slightly displaceable. The support posts 33 a, 33 b are opposite each other and are in a first cavity 34 between the inner surface 2 a of the first drive disk 17 and the inner surface 4 a of the first driven pulley 20 or in a second cavity 35 between the inner surface 2 a of the second drive disk 18 and the inner surface 9 a of the second driven pulley 21 are arranged. Therefore, when the yokes 26 a, 26 b are supported by the support posts 33 a, 33 b, one ends of the yokes 26 a, 26 b face the outer peripheral portion of the first cavity 24 , while the other ends face the outer peripheral portion of the second cavity 35 are facing.

Furthermore, a pair of first pivot pins 27 are arranged in the first cavity 34 at diametrically opposite positions of the first drive pulley 17 and the first driven pulley 20 , while a pair of second pivot pins are arranged in the second cavity 35 at diametrically opposite positions of the second drive pulley 18 and the second driven pulley 21 28 is arranged. As shown in Fig. 27, a total of four first pivot shafts 29 of the one end of the yoke pair 26 a, 26 b, which are provided coaxially at the two ends of the pivot pin 27 (two in each pivot pin), for a pivoting movement and an axial Shift supported. This means that the first pivot shafts 29 are supported via radial needle bearings 36 in the support holes 31 , which are formed in one end of the yokes 26 a, 26 b. Each of the radial needle bearings 36 has an outer race 37 with a spherical, convex, outer peripheral surface and a cylindrical, inner peripheral surface, as well as a plurality of needles 38 . Therefore, the first pivot shafts 29 are supported on both axial sides at one end of the yokes 26 a, 26 b so that they can perform a reversible swivel movement and a reversible axial displacement. As shown in FIG. 28, in the second cavity 35, in the same manner as the first pivot shafts 29 provided on the first pivot 27 , there are a total of four second pivot shafts 30 attached to both ends of the second pivot 28 (a pair on each Pivot) are provided coaxially supported.

The first and second pivots 27 , 28 , which are supported in the housing 5 for pivoting movements and displacements in the axial direction of the first and second pivot shafts 29 , 30 , are cut at their Zwischenab with circular holes 39 , as shown in Figs. 27 and 28 are shown. The first and second displacement shafts 40 , 41 are supported in these circular holes 39 . The first and second displacement shafts 40 , 41 have support shaft portions 92 that are parallel and eccentric, and pivot shaft portions 43 . The support shaft sections 42 are rotatably supported in the circular holes 39 via radial needle bearings 44 . Furthermore, the first and second drive rollers 45 , 46 are rotatably supported about the pivot shaft sections 93 via further radial needle bearings 47 .

The pair of first and second displacement shafts 40 , 41 , which are provided for each of the first and second cavities 34 , 35 , are in relation to the drive shaft 1 a and the transmission shaft 16 for each of the first and second cavities 34 , 35 in opposite directions ( diametrically opposed). Furthermore, the directions along which the pivot shaft portions 43 of the first and second displacement shafts 40 , 41 are offset (eccentric) with respect to the support shaft portions 42 are with respect to the direction of rotation of the first and second input and output disks 17 , 18 , 20 , 21 equal (opposite up-down directions in Figs. 27 and 28). Furthermore, the eccentricity directions to the installation direction of the drive shaft 1 a are substantially perpendicular. Therefore, the first and second drive rollers 45 , 46 are supported for a slight displacement in the installation direction of the drive shaft 1 a and the transmission shaft 16 (slight axial displacement). If the first and second drive rollers 45 , 46 due to the change in the amount of elastic deformation of the structural parts, which is caused by a fluctuation in the torque to be transmitted by the toroidal continuously variable transmission, to a displacement in the axial direction of the drive shaft 1 a and the transmission shaft 16 ( tend left-right direction in Fig. 26 and the direction perpendicular to the planes of Figs. 27 and 28), such displacement can be absorbed without any übermä ssige stress is exerted on the construction parts.

Further, between the outer surfaces of the first and second drive rollers 45 , 46 and the inner surfaces of the intermediate portions of the first and second pivots 27 , 28 in order from the outer surfaces of the first and second drive rollers 45 , 46 are thrust ball bearings 48 and thrust bearings 49 such as Plain bearings or needle bearings provided. The thrust ball bearings 48 serve to support the drawer load acting on the first and second drive rollers 45 , 46 and to permit rotations of the first and second drive rollers 45 , 46 . Furthermore, the drawer bearings 49 serve to support drawer loads which act on the outer races 50 of the thrust ball bearings 98 , and to permit pivoting movements of the pivot shaft sections 43 and the outer races 50 around the support shaft sections 42 .

Furthermore, drive rods 51 of the first and second pivots 27 , 28 are connected to one end (the lower end in FIGS. 27 and 28); further, 51 drive pistons 52 are attached to the outer surfaces of the intermediate portions of the drive rods. The Antriebskol ben 52 are slidably mounted oil-tight in drive cylinders 53 . The drive pistons 52 and the drive cylinder 53 form actuators for displacing the first and second pivots 27 , 28 in the axial direction of the first and second pivot shafts 29 , 30 . In response to a switching operation of a control valve (not shown), pressurized oil can be supplied to the drive cylinders 53 .

Between the drive shaft 1 a and the first drive disk 17 , a pressing device 10 of the type of loading noc is arranged. The pressing device 10 contains a cam plate 11 , which is connected to the intermediate portion of the drive shaft 1 a via a keyway connection, so that it can be rotated together with the drive shaft 1 a, but can not be moved in the axial direction, and a plurality of rollers 13 , which are rotatably supported by a bracket 12 . When the drive shaft 1 a is rotated, the pressing device 10 serves to rotate the first drive disk 17 and thereby force it against the second drive disk 18 .

If the toroidal continuously variable transmission is driven with the construction described above, the rotation of the drive shaft 1 a is transmitted via the pressing device 10 to the first drive pulley 17 , so that the first and second drive pulleys 17 , 18 are rotated synchronously. The rotation of the first and second drive pulleys 17 , 18 is transmitted to the first and second driven pulleys 20 , 21 via the pairs of first and second drive rollers 45 , 46 which are arranged in the first and second cavities 34 , 35, respectively. The rotation of the first and second driven disks 20 , 21 is absorbed by the driven gear 23 . If the speed ratio between the drive shaft 1 a and the output gear 23 is changed by a switching operation of the control valve, the pair of drive pistons 52 , which correspond to the first and second cavities 34 , 35 , in opposite directions for the cavities 34 , 35 by the same distance postponed.

When the drive piston 52 are shifted, two pairs (a total of four) pivots 27 , 28 are shifted in opposite directions, so that, for example, the first and second drive rollers 45 , 46 on the right side in FIGS. 27 and 28 are shifted downward ( Figs. 27 and 28) and the first and second driving rollers 45 , 46 on the left side of Figs. 27 and 28 are shifted upward ( Figs. 27 and 28). As a result, the directions of the tangential forces on the contact areas between the peripheral surfaces 9 a of the first and second drive rollers 45 , 46 and on the inner surfaces 2 a, 4 a of the first and second drive disks 17 , 18 and on the first and second Output disks 20 , 21 act, changed. If the directions of the forces are changed, the first and second pivots 27 , 28 are pivoted in opposite directions about the first and second pivot shafts 29 , 30 , which are supported by the yokes 26 a, 26 b. As a result, the contact areas between the peripheral surfaces 9 a of the first and second drive rollers 45 , 46 and the inner surfaces 2 a, 4 a of the disks 17 , 18 , 20 , 21 are changed as shown in FIGS. 24 and 25. where is changed by the speed ratio between the input shaft 1 a and the output gear 23 .

In the conventional arrangement shown in FIGS. 26 to 28, the first and second pivots 27 , 28 in the housing are supported by the support posts 33 a, 33 b and the yokes 26 a, 26 b. Thus, since the number of parts is high, not only are the manufacture, control and assembly of the parts difficult, but the toroidal continuously variable transmission has a great height in the up-down direction in FIGS . 26 to 28, so that the Gearbox can hardly get a compact size and light weight. On the other hand, if the transmission is to be made compact and light in weight to allow installation of the transmission in a limited space, the strength of the parts is reduced, thereby deteriorating the life.

From JP 10-274300-A (1998) an arrangement is known in which is the swivel shafts that are on both ends of the pivot of the toroidal continuously variable transmission are provided by Support elements that are directly supported are attached to an inner surface of a housing. Because the number of parts is reduced in this arrangement is, the gearbox can be compact and lightweight be formed. With the toroidal continuously variable transmission, disclosed in this document, however, are Support elements to support the on the two Independent ends of the pivot shafts provided gig provided for each pivot.

Therefore, in the arrangement disclosed in JP 10 ^-27 4300-A, loads acting on the trunnions when the toroidal type continuously variable transmission is driven directly act on the housing. This means that in the case of a driven, continuously variable toroidal transmission, due to the high pressure acting on the contact areas between the inner surfaces of the drive and driven disks and the peripheral surfaces of the drive rollers, the drive rollers are subject to large thrust loads. These drawers act on the support sections for the pivot shafts provided at the two ends of the pivots via these pivots. In the arrangement disclosed in the above-mentioned document, the large loads acting on the pivot shafts act unchanged on the housing. Since in many cases the housing of the gearbox is made of a light alloy such as an aluminum alloy in order to reduce the weight, it is necessary to prevent displacement of the pivot shafts and to ensure a sufficient service life of the housing regardless of the large loads, to increase the wall thickness of the housing, with the result that the gearbox is difficult to be compact and lightweight.

Furthermore, when the toroidal continuously variable transmission is driven the pivots are due to the drive rollers elastic loads acting on them deformed so that the inner surfaces become concave. The result is parallelism between the Mittelach sen the swivel shafts that at the ends of the pivot are provided, and the central axes of the circular Holes made in the inner surfaces of the casing attached support elements are formed, more or less lost. In the in the above Document disclosed arrangement is not taken into account that the pivots can be moved evenly, without damaging any parts, even if such a condition exists.

The invention is therefore based on the object stepless toroidal gear to create the above mentioned disadvantages of conventional, stepless toroids does not possess shoots.

This task is solved by a stepless toroid gears according to one of claims 1 to 4, 7 and 8. Next Formations of the invention are in the dependent claims specified.

In the stepless toroidal gears according to claim 1 or 2 is a torque between the drive pulley or the first and second outer disks and the output disc or the first and second inner discs transferred, the speed ratio between the  Drive pulley or the first and second outer Disks and the driven disk or the first and second inner washers as in the conventional one stepless toroidal gear can be changed.

Since in particular in the stepless according to the invention Toroidal gear that the support device or the first and second support structures Elements directly from the inner surface of the case supported and attached to this, the number of the parts are reduced, reducing the manufacture of the Control and the assembly of the parts easier and reduce the height of the toroidal continuously variable transmission Is gert, so that the transmission while maintaining the Service life compact dimensions and light weight owns.

Since in the toroidal continuously variable transmission according to claim 3 or 4 the support facility or the first and second support structures forming yokes directly through the inner surface of the case underneath supports and attached to this, the number of Parts are reduced, reducing the manufacturing process Control and the assembly of the parts easier is reduced and the height of the toroidal continuously variable transmission Is gert, so that while maintaining the life has compact dimensions and low weight.

Furthermore, since the yokes at the ends of the several revolutions can support provided pivot shafts all or part of the on the multiple pivot we forces are absorbed in the yokes. Since therefore no heavy load on the housing supporting the yokes acts, the wall thickness of the housing does not have to increase who to a shift in the support sections for the swivel shafts and a shortening of the service life  to prevent the housing.

Furthermore, since the groove connections and the needle bearings between the swivel shafts and the yokes are provided the displacement of the pivots with respect to the yokes done evenly and correctly.

In the toroidal continuously variable transmission according to claim 7, 8 or 9 is the torque between the drive pulley and the Driven pulley or between the first and second outer washers and the first and second inner ones Transfer discs, furthermore the speed ratio between the panes by changing the angle of inclination Pivots can be changed.

Since, in particular, in the continuously variable toroidal gear Invention the displacement movements of the pivot in axial direction of the swivel shafts by mechanical synchronized actuators take place, the Nei agree angle of rotation of the pivots even then exactly match when a rapid speed ratio change operation is carried out.

Further features and advantages of the invention will become clear Lich preferred when reading the following description Versions referring to the drawing; it demonstrate:

Fig. 1 is a sectional view corresponding to a sectional view taken along the line AA in Fig. 26, a first embodiment of the invention;

FIG. 2 shows a sectional view along the line BB in FIG. 1;

Fig. 3 is an enlarged sectional view showing the right portion of Fig. 1;

Fig. 4 is a view corresponding to a section C in Fig. 1 and showing the state in which the assembly is carried out;

Fig. 5 is a view corresponding to a section C in Fig. 1 and shows the state in which the assembly is completed;

Fig. 6 is a view showing a state in which forces act on yokes constituting a double cavity type toroidal continuously variable transmission, as viewed from above in Fig. 1;

Fig. 7 is a partial sectional view corresponding to a right upper portion of Fig. 1 and shows on an enlarged scale the state of a pivot deformed during operation;

Fig. 8A, B are views similar to that of Figure 6, showing a state act in the forces on the yoke, forming a toroidal continuously variable transmission of the single cavity type.

Fig. 9 is a sectional view corresponding to a sectional view taken along the line AA in Fig. 26 and showing a second embodiment of the invention;

FIG. 10 is an enlarged view of a section D in FIG. 9, a region above a line a showing a sectional view along the line EOF in FIG. 11 and a region below the line a a sectional view along the line EOG in FIG. 11 shows;

Fig. 11 is a top view of Figure 10 with Wegge left housing.

Fig. 12 is a view similar to Fig. 3, but showing a third embodiment of the invention;

Fig. 13 is a sectional view corresponding to a sectional view taken along the line AA in Fig. 26 and showing a fourth embodiment of the invention;

Fig. 14 is a view corresponding to a section I in Fig. 13;

Fig. 15 is a sectional view corresponding to a sectional view taken along the line AA in Fig. 26 and showing a fifth embodiment of the invention;

Fig. 16 is an enlarged view showing a portion J in Fig. 15;

17 is a perspective view of a female part.

Fig. 18 is a bottom view in Fig. 15 showing a mechanism for synchronizing the axial displacement movements of drive rods;

FIG. 19 is a view from the direction shown by the arrow K in FIG. 15;

Fig. 20 is a bottom view in Fig. 15 showing a gear transmission mechanism;

Fig. 21 is a plan view of a toroidal continuously variable drive for explaining a measured portion in a test which is carried out to confirm an effect of the invention;

Fig. 22A, B graphs showing the displacement states of pivots that form the stepless toroidal drives of the invention;

FIG. 23A, B are graphs showing the displacement pin states of rotation, which form a conventional, step-less toroidal transmission;

Fig. 24 is a side view of the basic structure of a conventional toroidal continuously variable transmission in the maximum reduction state;

FIG. 25 is a side view similar to Figure 29 in a state with maximum translation.

Fig. 26 is a sectional view of an example of a conventional concrete construction;

Fig. 27 is a sectional view taken along the line AA in Fig. 26;

Fig. 28 is a sectional view taken along the line HH in Fig. 26;

FIG. 29 is a sectional view of a first example of a conventional Synchronisationsmechanis mechanism which uses a rope; and

Fig. 30 is a sectional view of a second example of a conventional Synchronisationsmechanis mechanism which uses a rope.

First run

Figs. 1 to 7 show a first embodiment of the dung OF INVENTION. This embodiment contains a construction of parts for supporting first pivot shafts 29 , which are provided at both ends of first pivot pins 27 , on a housing 5, and a construction for accurately synchronizing the angles of inclination of the pivot pins 27 . Since the other constructions and functions are the same as those in the conventional transmission shown in FIGS . 26 to 28, the illustration and explanation thereof are omitted or mentioned only briefly, while the focus of the explanation is placed on the former construction features. Furthermore, the second pivot shafts 30 ( FIG. 28), which are provided at both ends of the second pivot pins 28 , are also supported on the housing 5 and the inclination angles of the second pivot pins 28 are synchronized by the same construction as those with respect to the first pivot shafts 29 . In the following explanation, usually only the first pivot 27 are described, with the exception of cases in which the second pivot 28 and the associated parts must be explained.

A pair of yokes 54 , 55 forming the first and second support means are arranged in parallel to each other and directly attached to opposite portions of the housing 5 . The positional accuracy of the yokes 59 , 55 with respect to the housing 5 is precisely adjusted by a grip between knocking pins which protrude from one of the yokes the housing with locking holes which are formed in the other of the yokes and in the housing. Circular support holes 31 are formed at four corners of the yokes 54 , 55 at engagement positions. In the support holes 31 , which are formed in one end of the yokes 59 , 55 , the first pivot shafts 29 are supported via ball-groove connections 56 and radial needle bearings 57 for axial displacement and pivoting movement.

Ball-groove connection outer raceways 58 , which form the ball-groove connections 56 , are fitted into open half sides of the support holes 31 such that the outer raceways can be pivoted slightly and the axial displacement of the raceways is limited. For this purpose, the open half sides of the support holes 31 are provided with sections 59 with a small diameter, the front diameter of which is smaller than the rear diameter. The ball-groove connection outer raceways 58 , which form the ball-groove connections 56 , are fitted into the sections 59 with a smaller diameter. The outer peripheral surfaces of the intermediate portions of the ball-groove connection outer raceways 58 are formed as a partially spherical convex surfaces 60 . The radius of curvature of each convex surface 60 is substantially equal to half the inner diameter of each support hole 31 .

Are in the outer peripheral surfaces of each of the one axial ends of the ball-and-groove connection outer raceways 58 are formed outwardly directed peripheral flanges 61 while order fangsverriegelungsnuten 62 formed on the outer peripheral surfaces of the other axial ends of the ball-and-groove connection outer raceways 58 . This ball-groove connection outer raceways 58 are assembled in such a way that the flanges 61 are positioned on the rear sides of the support holes 61 and the sections 59 with a smaller diameter from both sides between the flanges 61 and stop rings 63 , which are in the locking grooves 62 are locked, are sandwiched. A distance between each flange 61 and the corresponding stop ring 63 is chosen so that it is greater than the axial length of the corre sponding section 59 with a smaller diameter. Consequently, the ball-groove connection outer raceways 58 are supported in the support holes 31 so that they can perform a slight pivoting movement.

On inner raceways 65 (which act as outer raceways of the radial needle bearings 57 ), which are arranged within the ball-groove connection outer raceways 58 coaxially with the radial needle bearings 57 , a plurality of outer raceway-side ball grooves 64 are formed, which extend axially (upward - Downward direction in Fig. 1 and in Figs. 3 to 5). In sections of the outer circumferential surfaces of the ball-groove connection inner raceways 65 , ball grooves 66 on the inner raceway side are formed, which extend axially and lie opposite the ball grooves 64 on the outer raceway side. Between the respective inner race track grooves 66 and the respective outer race track grooves 64 , a plurality of balls 67 are arranged, whereby the ball-groove connections are created.

Cylindrical outer raceway tracks 68 for the radial needle bearing 57 are provided on inner circumferential surfaces of the ball-groove connection inner raceways 65 . A plurality of needles 70 are arranged between the respective outer raceway tracks 68 and corresponding cylindrical inner raceway tracks 69 , which are formed on the outer circumferential surfaces of the first pivot shaft 29 , which in turn are provided on the two ends of the first pivot pins 27 , whereby the radial needle bearings 57 are formed . Of the first pivot shafts 29 , which are provided at both ends of the first pivot pins 27 , tip end sections of the first pivot shaft 29 , which are connected to the drive rods 51 on one side (lower end face in FIGS. 1 and 3), have pinions 72 ( which form a gear transmission mechanism 71 ( described later) attached thereto. On the other hand, a circular hold-down plate 73 is attached to the tip ends of the first pivot shaft 29 on the other side remote from the drive rods 51 (upper end face in FIGS. 1 and 3) by threaded rods 74 provided on central portions of the hold-down plates in FIG Threaded bores 75 are screwed, which are formed in the central portions of the first pivot shaft 29 . These pinions 72 and hold-down plates 73 serve to prevent an axial displacement movement of the ball-groove connection inner raceways 65 and prevent the balls 67 from falling out. The falling out of the balls 67 in the opposite direction is prevented by stop rings 85 , which are locked on the outer peripheral surfaces of the near end (ends near the axial Mittelab sections of the first pivot 27 ) of the ball-groove connection inner raceways 65 .

In this embodiment, the ball-groove connection 56 and the radial needle bearing 57 are joined together as follows. As shown in FIG. 4, the radial needle bearing 57 containing the ball-groove connection inner race 65 is first attached to the first pivot shaft 29 provided at the other end of the first pivot pin 27 and prevented from falling by means of a washer 76 and a stop ring 77 . Further, as shown in FIG. 4, the ball-groove connection outer race 58 is preliminarily installed in the support hole 31 formed in the yoke 54 . In this state, the plurality of balls 67 , which form the ball-groove connection 56 , between the inner raceway-side ball groove 66 , which is formed in the outer circumferential surface of the ball-groove-connection inner raceway 65 , and the corresponding outer raceway-side ball grooves 64 , which are formed in the inner circumferential surface of the ball-groove connection outer race 58 , through the hole 86 formed in a section of the housing 5 , which is aligned with the support hole 31 , used. After insertion, as shown in Fig. 5, the holding plate 73 is attached, whereupon the through hole 87 is closed by a cover plate 87 .

In the toroidal continuously variable transmission of the invention having a structure according to the embodiment shown, the yokes 59 , 55 have no functions for matching the inclination angles of the pair of opposing first drive rollers 45 with each other due to the fact that they are not displaced. That is, although these angles of inclination are set by axial amounts of displacement of the drive rods 51 , which are controlled by supplying or discharging pressurized oil to the drive cylinders 53 , it is difficult to change the angles of inclination of the pair of first drive rollers 45 to bring such axial displacement amounts into exact agreement. Therefore, in the conventional arrangements, the angles of inclination of the pair of first drive rollers 45 have been brought into exact agreement by allowing displacement of the yokes 26a and in that the first drive rollers 45 are supported in a so-called floating manner. In the toroidal continuously variable transmission of the invention, however, the inclination angles of the pair of first drive rollers 95 cannot be matched by the displacement of the yokes 54 , 55 .

Therefore, in the embodiment shown, the two opposite first pivots 57 are connected to one another via the gear transmission mechanism 71 , so that the two first drive rollers 45 , which are supported by the first pivots 27 , can be brought into exact correspondence with one another. In order to install the gear transmission mechanism 71 , one of the yokes (the lower one ( 55 ) in FIGS. 1 to 3) is provided with a recessed portion 78 . In a state in which the yoke 55 and a cylinder housing 79 overlap with each other, a space 80 containing the gear transmission mechanism 71 is defined between these elements 55 , 79 . The gear transmission mechanism 71 contained in this space 80 includes a pair of pinions 72 with the same configuration and the same number of teeth, and a rack 81 with toothed portions provided at the two end portions and having the same pitch. The pinion 72 are at non-cylindrical portions formed at the upper ends of the first pivot shafts 29 , which are provided at the ends of the first pivot 27 , is introduced and attached. Therefore, the first pivots 27 are rotated in synchronism with the pinions 72 . If the speed ratio is changed, the first pivot pin 27 are moved in the axial direction of the first pivot shaft 29 . Therefore, by providing a small backlash (a size that does not create a problem with the coincidence of the inclination angles) in the engagement areas between the pinions 72 and the rack 81, a relative displacement between the pinions 72 and the rack 81 is allowed.

The rack 81 can only be moved in the axial direction (direction perpendicular to the planes of FIGS. 1 and 3) of the drive shaft 1 a and is supported in space 80 . For this purpose, in the embodiment shown, the rack 81 is supported by translation roller bearings (linear bearings) 82 for a parallel displacement movement with respect to the yoke 55 . That is, in a section from (opposite to the rack 81 ) a lower surface of the yoke 55 , which is fixed to the inner surface of the housing 5 , recessed Guide sections 83 are formed, which extend in the direction of displacement of the rack 81 .

Furthermore, an intermediate part of the tooth are portions of rod 81 guide flanges 84 (which are aligned with the recessed guide portions 83) is formed. The thickness of each guide flange 84 is selected to be smaller than the width of each recessed guide section 83 so that the guide flanges 89 are loosely inserted into the recessed guide sections 83 . The roller bearings 82 are arranged between respective surfaces of the flanges 84 and respective inner surfaces of the recessed guide portions 83 . These bearings 82 are located at positions where they sandwich the flanges 84 provided on the rack 82 from both sides (or, contrary to the illustration, at positions where the flanges 84 sandwich the bearings 82 from both sides well).

Thus, the rack 81 can be smoothly moved with respect to the yoke 55 with a small force without inclination to the recessed guide portions 83 . If a force acts perpendicularly to the direction of displacement on the rack 81 , either of the two roller bearings 82 of the rack 81 absorbs this force, which enables the rack 81 to move smoothly.

The pinion 72 and the rack 81 supported in this manner are assembled so that the teeth formed on the outer peripheral edges of the pinion 72 engage with the toothed portions formed on both end portions of the rack 81 , thereby forming the gear transmission mechanism becomes. The gear transmission mechanism 71 serves to minimize the play and increase the pitch circle diameter of the pinion 72 to a certain extent (within a range that can prevent interference with other elements). Therefore, the angle of inclination of the first pivot pin 27 to which the pinions 72 are attached can be brought into exact agreement with the angle of inclination of the first drive rollers 95 , which are supported by the first pivot pin 27 . Although not shown, another gear transmission mechanism having the same construction as the mechanism 71 is provided between the first pivot 27 and the second pivot 28 ( FIG. 28) to pivot the inclination angle of the first pivot 27 with the inclination angle of the second pivot 28 to bring in line.

As mentioned above, in the toroidal type continuously variable transmission according to the invention, the yokes 54 , 55 constituting first and second support means are directly supported by and fixed to an inner surface of the housing 5 . Thus, the posts 33 a, 33 b ( Fig. 26 to 28), which are required in the above-mentioned conventional arrangement, omitted sen, so that the number of parts is reduced and thus the manufacture, control and assembly the parts are facilitated and also the height of the toroidal continuously variable transmission is reduced, so that the transmission has compact dimensions and a low weight while maintaining a service life.

According to the invention, the yokes 54 , 55 support at their four corners the first and second pivot shafts 29 , 30 , which are seen at the ends a total of four pivots 27 , 28 (two first pivots 27 and two second pivots 28 ). All the forces acting on the first and second pivots 27 , 28 can thus be absorbed in the yokes 54 , 55 . This will now be described with reference to FIG. 6. As mentioned above, large drawbar loads act on the first and second driving rollers 45 , 46 along the directions shown by the arrows (α) in Fig. 6 on the first and second pivot pins 27 , 28 when the toroidal type continuously variable transmission is driven . Each drawer load can be in a force component shown by the arrow (β) in Fig. 6, which acts in the diametrical direction of the first and second cavities 39 or 35 ( Fig. 1), and in a force component shown by the arrow (γ ) is shown in Fig. 6 and acts in the axial direction of the drive shaft 1 a, disassembled.

As is apparent from Fig. 6, which shows the directions of the forces, the force components (β) in the diametrical direction of the first and second cavities 34 , 35 on the arranged in the same cavity first and second pivot pins 27 , 28 have the same size and opposite Directions. Furthermore, the force components (γ) in the axial direction of the drive shaft 1 a on the first and second pivots 27 , 28 , which are arranged in adjacent cavities, have the same size and opposite directions. Therefore, all the forces acting on the first and second pivots 27 , 28 are received in the yokes 54 , 55 , with the result that these forces do not act on the housing 5 which supports the yokes 54 , 55 . Thus, since the housing 5 is not subjected to a large load, displacement of the support sections of the first and second pivot shafts 29 , 30 can be prevented even if the wall thickness of the housing 5 is not increased greatly, and the life of the housing 5 is not deteriorated.

Furthermore, since the ball-groove connections 56 and the radial needle bearings 57 are arranged between the first pivot shaft 29 and the yokes 54 , 55 , the first pivot pin 27 can be moved evenly and correctly with respect to the yokes 54 , 55 . That is, as is apparent from the above explanation, during the speed ratio change of the stepless. Toroidal gear the first pivot 27 are displaced in the axial direction of the first pivot shaft 29 , with the result that the first pivot about the first pivot shafts 29 are pivotally displaced. In the embodiment shown, the axial displacement through these ball-groove connection 56 is carried out uniformly from these displacements; furthermore, the pivotal displacement is carried out smoothly by the radial needle bearing 57 , with the result that the speed ratio changing operation of the toroidal continuously variable transmission can be carried out quickly and correctly based on these displacements.

Further, since the outer circumferential surfaces of the ball-groove connection Ver outer raceways 58 are formed as a semi-spherical, convex surfaces 60 , regardless of the elastic deformation of the first pivot 27 can be prevented that the contact areas between the rolling surfaces of the needles 70 , the the radial needle bearing 57 form, and the outer raceway track 68 and the inner raceway track 69 acts on an edge load. That is, when the toroidal continuously variable transmission is driven, the large drawer loads act on the first drive rollers 45 , the first pivots 27 being elastically deformed due to this sliding block, so that the inner surfaces lying opposite become concave, as shown in FIG. 7 in enlarged form Scale is shown. Because of this elastic deformation, the central axes of the first pivot shafts 29 deviate slightly from the central axes of the support holes 31 . In order to eliminate this problem, the ball-groove connection outer raceways 58 are pivotally displaced in the support holes 31 . The central axes of the ball-groove connection outer raceways 58 and the center axes of the ball-groove connection inner raceways 65 (which also act as outer raceways of the radial needle bearing 57 ), which are arranged in the ball-groove connection outer raceways kept aligned. In the arrangement according to the embodiment shown, misalignment between the central axes of the first pivot shaft 29 and the central axes of the support holes 31 is thus compensated for, so that the edge loads are prevented from being exerted. Since in the embodiment shown, the inclination angle of the first drive rollers 45 are brought into agreement by the gear transmission mechanism 71 , it can be prevented that at the contact areas between the peripheral surfaces 9 a of the first drive rollers 45 and the inner surfaces 2 a, 4 a of the disks 17th , 20 a large slip occurs so that the efficiency of the toroidal continuously variable transmission is well ensured.

Although the gear transmission mechanism 71 causes the inclination angles of the first drive rollers 45 to exactly match each other and the inclination angles of the first drive rollers 45 and the inclination angles of the second drive rollers 46 ( FIG. 28) to match, in the practice of the invention a synchronization mechanism is that which Tilt angle of the first drive rollers len 45 and the inclination angle of the second drive rollers 96 matches, not limited to the gear transmission mechanism 71 shown. A rope type synchronization mechanism, well known in the art and shown in Figures 29 and 30, can also be used.

The invention, when applied to a double cavity type toroidal continuously variable transmission, also acts in that the loads acting on the yokes can be substantially absorbed in the yokes and that a large load can be prevented from being applied to the housing supporting the yokes works. However, as shown in Figs. 24 and 25, an effect can be expected to some extent even with a single cavity type toroidal type continuously variable transmission in which a single drive pulley 2 and a single driven pulley 4 are provided. However, when the invention is applied to the single cavity type toroidal type continuously variable transmission as shown in Figs. 8A and 8B, depending on the driving state, part of the loads acting on the trunnions 7 from the driving rollers 9 may act on the housing on which the Yoke 88 is attached.

Thus, if the speed of the drive pulley 2 coincides with the speed of the driven pulley 4 (speed ratio = 1), as shown in FIG. 8A, loads of the same size and in opposite directions act on the pivot pin 7 . Therefore, the loads acting on the trunnions 7 are substantially absorbed in the yoke 88 , with the result that no load acts on the housing supporting the yoke 88 . On the other hand, if the speed of the drive pulley 2 is different from the speed of the driven pulley 4 (speed ratio ≠ 4), as shown in Fig. 8B, of the loads acting on the trunnions 7, a load component acting in the axial direction of the drive pulley 2 and the driven pulley 4 not be compensated so that this load component acts on the housing. Since the load component acting on the housing is smaller than the loads acting on the pivot pins 7 , the yoke 88 is produced when the yoke 88 is fastened to the housing in several places, as is known from JP 10-274300-A, in contrast to the arrangement in which the loads acting on the trunnions are transmitted unchanged to the housing with respect to preventing the deformation of the housing and ensuring the life of the housing is not a practical problem.

Second execution

FIGS. 9 to 11 show a second embodiment of the invention. The second embodiment differs from the first embodiment in the arrangement of the support of the first pivot shaft 29 from the drive rods 51 (of the provided at the two ends of the first pivot pin 27 first pivot shafts 29) on the housing. 5 That is, in the second embodiment, when the ball-and-groove connections 56 for supporting the first pivot shafts 29 are joined together by the drive rods 51 on the yoke 54 , the through hole 86 used in the first embodiment ( FIGS. 4 and 5) is omitted and the cover plate 87 ( FIG. 5) for closing the through hole 86 is also omitted, whereby the costs are reduced and the strength of the housing 5 is improved.

For this purpose, in the second embodiment, notches 89 which are recessed in the diametrical direction of the support hole 31 are formed at diametrically opposite positions (two positions) of the section 59 of smaller diameter formed in the half section of the open section of the support hole 31 of the yoke 54 . Further, protrusions 90 , which may pass through the notches 89 , are formed at diametrically opposite positions (two positions) of the outer peripheral surface of the near end (upper end in FIGS . 9 and 10) of the ball-groove connection outer race 58 . In a central portion of an outer peripheral edge of one of the protrusions 90 (protrusion on the right side in FIG. 10 and right and above in FIG. 11), a locking notch 91 is formed. Corresponding to the section 59 with a smaller diameter in the yoke 54 formed under the support hole 31 , a threaded bore 92 is formed in a section aligned with the locking notch 91 between the notches 89 , and is also with the locking notch 91 a pointed end of a screwed into the threaded bore 92 set screw 93rd in one handle.

The construction of the embodiment described and shown above is assembled as follows. The radial needle bearing 57 and the ball-groove connection 56 are previously attached to the end of the first pivot shaft 29 . A forth failure of the plurality of balls 67 forming the ball-groove connection 56 is prevented by the stop ring which is on the inner peripheral surface of the end of the ball-groove connection outer race 58 or the outer peripheral surface of the end of the ball- Groove connection inner raceway 65 is locked. Provided that the notches are aligned with the projections 90 89, the protrusions are inserted into the support hole 31 90th Then the ball-groove connection outer race 58 is rotated through 90 ° in order to align the locking notch 91 with the threaded bore 92 . Then the set screw 93 is screwed into the threaded bore 92 to insert the pointed end of the set screw 93 into the locking notch 91 . As a result, the notches 89 deviate from the projections 90 and the ball-groove connection outer raceway 58 can be held in the support hole 31 . Since the rest of the construction and functions are the same as those of the first embodiment, the same elements are denoted by the same reference numerals, and the explanation is omitted.

Third execution

Fig. 12 shows a third embodiment of the invention. In the third embodiment, between the outer raceway-side ball grooves 64 , which are formed in the inner circumferential surface of the ball-groove connection outer race 58 , and the inner raceway-side ball grooves 66 , which are in the outer circumferential surface of the ball-groove connection Inner raceway 65 are formed, rollers 94 are arranged. Therefore, the radial load capacity of the keyway connecting portion can be increased. The rollers 94 do not roll when the first pivot shafts 29 are moved in the axial direction. Therefore, although in the third embodiment, the force required to displace the first pivot shaft 29 becomes larger than that in the first and second embodiments, an adequate practical responsiveness can be obtained because the axial displacement movement of the first pivot shaft 29 by the drive cylinders 53 ( is Fig. 1 and 9) causes a high force as long as the diameter and the oil pressure of the drive cylinder 53 are maintained. The other constructions and functions are the same as in the first version.

Fourth execution

A fourth embodiment of the invention will now be explained with reference to FIGS. 13 and 14. The explanation of the same elements as those in the previous embodiments is omitted.

In the fourth embodiment, first pivot shafts 129 are supported in the support holes 131 formed at one ends of the yokes 154 , 155 by radial needle bearings 136 in such a way that they can perform a pivoting movement and an axial displacement. The outer peripheral surfaces of the outer raceways 137 , which form the Radialna dellager 136 , are formed as spherical, convex upper surfaces, so that edges are prevented from contact areas between the rolling surface of the needles 138 , which form the radial needle bearings 136 , and the associated surfaces act independently of the elastic deformation of the first pivot 127's .

Thus, when the toroidal continuously variable transmission is driven, large drawer loads act on the first drive roller 145 , so that the first pivot pins 127 are elastically deformed, so that inner running surfaces thereof become concave through the drawer loads. Due to the elastic deformation, the central loads of the first pivot shafts 129 slightly from the central axes of the support holes 131 from. In this case, the deviation is compensated for by pivoting the outer raceways 137 in the support holes 131 , thereby preventing an edge load from being exerted.

In the case of the toroidal continuously variable transmission according to the invention with a construction according to this embodiment, however, in contrast to the conventional construction shown in FIGS. 26 to 28, due to the fact that the yokes 154 are not displaced, the deviation between the central axes of the first pivot shaft 129 and the central axes of the support holes 131 . That is, in the conventional construction, the angle of inclination of the pair of opposing first drive rollers 145 due to the support of the yokes 126 a, 126 b by means of the support posts 133 a, 133 b in such a manner that they have a slight displacement with respect to the housing 105 can perform. Therefore, when the toroidal type continuously variable transmission is driven, the central axes of the first pivot shafts 129 deviate from the central axes of the support holes 131 not only by the elastic deformation of the first pivot pins 127 , but also by the displacement of the yokes 126 a, 126 b. Therefore, in the conventional construction, it is inevitable that the radial needle bearings 136 are provided with the outer raceways 137 with spherical, convex outer peripheral surfaces. In contrast, as mentioned above, the deviation between the center axes of the first pivot shafts 129 and the center axes of the support holes 131 is limited because the yokes 154 , 155 are not shifted. Therefore, as long as the occurrence of an edge load can be prevented, for example, by the formation of "crowns" on the needles 138 as shown in FIG. 14, the outer raceways 137 can be omitted from the radial needle bearings 136 .

As mentioned above, the invention, the yokes have in the toroidal continuous variable transmission with the construction according to this embodiment has a function for establishing a correspondence the inclination angle of the pair of opposed first drive rollers 145, because the yokes 154 are not moved 155th That is, although the angles of inclination are adjusted by axial displacement amounts of the drive rods 151 , which are controlled by supplying or discharging pressurized oil to or from the drive cylinders 153 , it is difficult to adjust the angles of inclination of the pair of first drive rollers 145 by such axial displacement amounts to match exactly Thus, the exact match of the inclination angles of the pair of first drive rollers 145 in the conventional construction has been achieved by allowing the yokes 126 a to be displaced and supporting the first drive rollers 145 in a so-called floating manner. In the stepless toroidal transmission according to the invention, however, the angle of inclination of the first two drive rollers 145 cannot be brought into agreement by displacement of the yokes 154 , 155 . Therefore, in the embodiment shown, the inclination angles of the pair of first drive rollers 145 , which are supported by the first pivot 127 , are brought into exact agreement by connecting the pair of opposed first pivot 127 through a gear transmission mechanism 156 .

For the installation of the gear transmission mechanism 156 , one (the lower one ( 155 ) in FIG. 13) of the yokes is provided with a recessed portion 157 . Therefore, when the recessed portion 157 and a cylindrical housing 158 overlap with each other, a space 159 for receiving the gear transmission mechanism 156 is defined between these elements 155 , 158 . The gear transmission mechanism 156 contained in this space 159 includes a pair of pinions 160 having the same configuration and the same number of teeth, a rack 161 having toothed portions provided at the two end portions and having the same pitch. The pinions 160 are attached to and non-cylindrical portions formed at the tip ends of the first pivot shafts 129 , which in turn are provided at the ends of the first pivots 127 or are supported by ball-and-groove connections and the like for axial movement without relative rotation attached. Therefore, the first pivots 127 are rotated in synchronism with the pinions 160 .

The rack 161 can only be moved in the axial direction (the direction perpendicular to the plane of FIG. 13) of a drive shaft 101 a and is supported in the space 159 . For this purpose, in the embodiment shown, a projecting guide section 162 , which is formed on one side surface of the toothed rack 161 , engages with a guide groove 163 formed in the bottom of the recessed section 157 . Further, on the other side surface of the rack 161, a protruding sliding section 166 is formed, which slides with respect to the cylinder housing 158 , thereby preventing the rack 161 from being shifted to fall.

The structure for supporting the rack 161 for parallel displacement movement in one direction only is not limited to the structure shown; rather, many different structures known in the art can be used. For example, in the rack 161 a in the direction 13, slot extending perpendicular to the plane of FIG. Be formed, wherein a plurality of guide pins, in the direction perpendicular to the plane of FIG. Are mounted in the space 159 13, with the elongated hole in engagement could be.

The pinion 160 and the rack 161 supported in this manner are assembled so that the teeth formed on the outer peripheral edges of the pinion 160 mesh with the toothed portions provided on the two end portions of the rack 161 , thereby the gear transmission mechanism 156 is formed. The gear transmission mechanism 156 serves to minimize the play and increase the pitch circle diameter of the pinion 160 to some extent (within a range that can prevent interference with other elements). Therefore, the angles of inclination of the first pivots 127 to which the pinions 160 are attached can be closely matched to the angles of inclination of the first drive rollers 145 supported by the first pivots 157 . Although not shown, another gear transmission mechanism having the same construction as the mechanism 156 is provided between the first pivot 127 and the second pivot 128 (see reference numeral 28 in FIG. 28) to adjust the inclination angles of the first pivot 127 with the inclination angles of the second pivot 128 to match.

Further, a stop plate 164 provided at an upper middle portion in Fig. 13 serves to prevent the inclination angle of the first pivot 127 from becoming too large, the stop plate 164 being arranged around a nozzle 165 which is in contact areas between the peripheral surfaces 109 a of the first drive rollers 145 and the inner peripheral surfaces 102 a of a first drive pulley 117 and the inner peripheral surface 104 a ( FIG. 26) of a first driven pulley 120 supplies lubricating oil. In the above explanation, the example has been described in which the invention is applied to a double-cavity type continuously variable toroidal gear. The invention can have a significant effect when applied to such a double cavity type toroidal continuously variable transmission; however, it can also be applied to a single cavity type toroidal type continuously variable transmission as shown in Figs. 24 and 25.

As mentioned above, in the toroidal continuously variable transmission of the invention, the yokes 154 , 155 constituting the first and second support means are directly supported by and fixed to the inner surface of the housing 105 . Thus, the post 133 a, 133 b, which were required in d 27802 00070 552 00004 001000280000000200012000285912769100040 0002019947851 27683er above-described conventional arrangement, can be omitted; furthermore, the outer raceways 137 forming the radial needle bearings 136 can be omitted, so that the number of parts is reduced and the manufacture, the control and the assembly of the parts is facilitated; furthermore, the height of the toroidal continuously variable transmission is reduced, so that the transmission has compact dimensions and a low weight while maintaining the service life. Since in the illustrated embodiment, the inclination angle of the first driving rollers are brought 145 via the Zahnradübertragungsmechanis mechanism 156 in accordance, a significant slippage can in the areas of contact between the peripheral surfaces 109a of the first driving rollers 145 and the inner surfaces 102 a, 104 a of the discs prevents who the so that the efficiency of the stepless toroid drive is ensured.

Since the invention the arrangement described above and the has the functions described above, a stepless ses toroidal gear can be created that inexpensively can be manufactured and compact dimensions and a has low weight and is also excellent has transmission efficiency.

Fifth version

A fifth embodiment of the invention will now be described. The gear transmission mechanism 71 (or 156 ) described above has been designed in view of the fact that the angles of inclination of the trunnions and therefore of the drive rollers are determined by the axial. Displacement of the drive rods 51 (or 151 ) caused to be brought into line with each other; however, it is not intended to synchronize the axial displacements of the drive rods 51 themselves. The axial displacements of the drive rods 51 are synchronized by control of the oil pressure introduced into the drive cylinder 53 . Thus, in the transition state immediately after the start of the speed ratio operation change operation, the angle of inclination of the pivots 27 , 28 slightly different from each other, so that, if necessary, in the contact areas between the peripheral surfaces 9 a of the drive rollers 45 , 46 and the inner surfaces 2 a, 4 a Slices 2 , 4 , 17 , 18 , 20 , 21 a slip can occur.

The slippage generated in the contact areas can thus occur when the pivots 27 , 28 are quickly displaced in the axial direction of the pivot shafts 29 , 30 in order to perform a speed ratio change operation quickly. If the slip is generated, this occurrence of the slip is not desirable because not only is the power transmission efficiency deteriorated, but the life of each surface is shortened due to the rolling fatigue. In order to allow a rapid speed ratio change operation while avoiding deterioration in transmission efficiency and shortening of life due to rolling fatigue, a structure must be realized in which the axial displacements of the drive rods 51 themselves are precisely synchronized with each other.

A continuously variable toroidal gear according to the fifth version tion has been developed in the light of these circumstances.

Figs. 15 to 20 show the fifth embodiment of the invention. This embodiment is characterized in that it has a specific construction for accurate synchronization of the angles of inclination of the first pivots 227 with the angles of inclination of the second pivots 228 (see reference numeral 28 in FIG. 28) and also a specific construction for supporting the first pivot shafts 229 , which are provided at both ends of the first pivot 227 , and the second pivot shafts 230 (see reference numeral 30 in Fig. 28), which are provided at the two ends of the second pivot 228 . Since the other constructions and functions are the same as in the conventional device shown in Figs. 26 to 28, the explanation and illustration of similar elements are omitted or simplified, the main focus of the explanation being on the characteristics of the embodiment of the invention.

A pair of yokes 258 , 259 are attached directly to opposite portions of the housing 205 . Circular support holes 231 are formed at the four corners of the yokes 258 , 259 in areas aligned with one another. The first swivel shafts 229 are supported in the support holes 231 via ball-groove connections 260 and via radial needle bearings 261 for axial displacement and swivel movement.

The keyway outer treads 262 which form the ball-groove connections 260 are fitted into the support holes 231 , thereby limiting the axial displacement of the raceways. In the inner peripheral surfaces of the ball-groove connection outer raceways 262 , a plurality of outer raceway-side ball grooves 263 are formed, which extend in the axial direction (up-down direction in FIGS. 15 and 16). The ball-groove connection inner raceways 264 (which also act as outer raceways of the radial needle bearings 261 ) are arranged within the ball-groove connection outer raceways 282 coaxially with the radial dial needle bearings 261 . The inner raceway-side ball grooves 265 , which extend in the axial direction, are formed in sections of the outer circumferential surfaces of the ball-groove-connection inner raceways 264 , which are opposite to the outer raceway-side ball grooves 263 . A plurality of balls 266 are arranged between the ball grooves 265 on the inner raceway side and the ball grooves 263 on the outer raceway side, as a result of which the ball-groove connections 260 are formed. Any play of the ball-groove connection outer raceways 262 is prevented by elastic elements such as conical disc springs 290 .

On the inner circumferential surfaces of the ball-groove connection inner raceways 264 , cylindrical outer raceway tracks 267 for the radial needle bearings 261 are provided. A plurality of needles 269 are arranged between the respective outer raceway tracks 267 and the corresponding cylindrical inner raceway tracks 268 formed on the outer peripheral surfaces of the first pivot shafts 229 provided on both ends of the first pivot pins 227 , thereby forming the radial needle bearings 261 .

Drive rods 251 , the proximal ends (upper ends in FIG. 15) of which one end of the lower first pivot shafts 229 , which are provided at the two ends of the first pivot pin 227 , extend through through holes 271 , which in a on the housing 205 BEFE Stigt valve body 270 are formed. Receiving parts 272 as shown in FIG. 17 are attached to the tip ends (lower ends in FIG. 15) of the drive rods 251, protrude from an outer surface (lower surface in FIG. 15) of the valve body 270 . The receiving portions 272 are defined by circumferential portions of peripheral edges of a pair of parallel annular portions 273 a, 273 b via a partially cylindrical connecting portion 274 det gebil, further, an opening portion is defi ned by deviating from the connecting portion 274 portions 275th Of the ring sections 273 a, 273 b, the inner diameter of a ring section (upper ring section in FIGS. 15 and 17) is relatively small, so that only an external thread section, which is formed on the drive rod 251 , can run through such a ring section. On the other hand, the inner diameter of the other ring portion 272 b (lower ring portion in FIGS. 15 and 17) is relatively large, so that a nut 276 can be screwed onto the external thread portion and a tool for tightening the nut 276 can run through such a ring portion.

Swivel brackets 279 having second swivel shafts 278 are provided on fastening substrate plates 277 which are fastened to the outer surface of the valve body 270 . The second pivot shafts 278 extend parallel to the axes of rotation of the first and second drive disks 217 and first and second driven disks 220 , 221 ( FIG. 12) and are arranged in positions opposite the sides of the first and second cavities 234 , 235 ( FIG. 12). The second pivot shafts 278 support widthwise (left-right direction in Fig. 18) pivotable middle portions of the two longitudinal (up-down direction in Fig. 18) ends of a swing arm 280 which is formed as a substantially square frame is as shown in Fig. 18. Therefore, the two ends of the swing arm 280 are shifted in the width direction in opposite directions by the same amount with respect to the axial direction of the drive rods 251 .

The two longitudinal ends of the two ends in the width direction of the swing arm 280 are with the opening portion 275 between the pair of ring portions 273 a, 273 b, which form the receiving parts 272 , so that no play is generated even when the swing arm around the second pivot shaft 278 is pivoted. For this purpose, in the embodiment shown, small projections 281 are formed on regions of both surfaces of the two longitudinal ends of the two ends in the width direction of the swivel arm 280 , which are opposite to the ring sections 273 a, 273 b, the pointed ends of the small projections 281 on opposite surfaces of the ring sections Cast on 273 a, 273 b. Therefore, axial displacements (in the axial directions of the first and second pivot shafts 229 , 230 ) of the receiving parts 272 and the first and second pivots 227 , 228 , which are firmly connected to the receiving parts 272 via the drive rods 25 a, mechanically exactly synchronized. A precession cam is attached to any trunnion or to the drive rod, which is fixedly connected to any of the trunnions, so that a feedback control for the activation of a control valve for supplying or discharging pressurized oil to or from the drive cylinders 253 the precession cam is executed.

In the embodiment shown, the first and second pivots 227 , 228 are connected together by a gear transmission mechanism 282 . For the installation of the gear transmission mechanism 282 , one of the yokes (lower yoke ( 259 ) Fig. 15) is provided with a recessed portion 284 . Therefore, when the yoke 259 and a cylinder housing 285 overlap with each other, a space 289 is defined between these elements 259 , 285 , which contains the gear transmission mechanism 282 . The gear transmission mechanism 282 contained in this space 289 includes a pair of pinions 283 with the same configuration and the same number of teeth, and four racks 287 a, 287 b with toothed portions, which are provided at the two end portions and have the same pitch. The pinions 283 are drier on non-cylindrical. Portions formed at the tip ends of the first and second pivot shafts 229 , 230 , which in turn are provided at the ends of the first and second pivots 227 , 228 , are attached and fixed. Therefore, the first and second pivots 227 , 228 are rotated synchronously with the pinions 283 . When the speed ratio is changed, the first and second pivots 227 , 228 are shifted in the axial directions of the first and second pivot shafts 229 , 230 . Therefore, by providing a moderate backlash (with an amount that does not create any problem with respect to the coincidence of the inclination angles) with respect to the engagement areas between the pinions 283 and the racks 287 a, 287 b, a relative displacement between the pinions 283 and the racks 287 a, 287 b approved.

The racks 287 a, 287 b can only be in the axial direction (the direction perpendicular to the plane of FIG. 15 or the left-right direction in FIG. 15; the left-right direction or the up-down direction in FIG . 20) the drive shaft 1 a are moved and are supported in room 289 . For this purpose, the toothed racks 287 a, 287 b are supported in the embodiment shown by pairs of translational rolling bearings (linear bearings) 288 for a parallel displacement movement with respect to the yokes 295 . Therefore, the racks 287 a, 287 b can be pushed evenly with a small force without inclination ver. Further, if a force which is oriented perpendicular to the displacement direction, on the racks 287 a, 287 b acts, accepts any one of the two bearings 288 of the rack gears 287 a, 287 that force b, whereby a uniform displacement of the racks 287 a, 287 b is made possible.

The thus supported pinion 283 and rack 287 a, 287 b are mounted in such a way that the teeth formed on the outer peripheral edges of the pinion 283 come into engagement with the teeth on the two end portions of the racks 287 a, 287 b are provided, whereby the gear transmission mechanism 282 is formed. The gear transmission mechanism 282 serves to minimize the play and increase the pitch circle diameters of the pinions 283 to a certain extent (within a range that can prevent interference with other elements). Therefore, the angles of inclination of the first and second pivots 227 , 228 to which the pinions 283 are attached can exactly match the angles of inclination of the first and second drive rollers 245 , 246 supported by the first and second pivots 227 , 228 to be brought.

As mentioned above, in the toroidal type continuously variable transmission of the invention, the displacements of the first and second pivots 227 , 228 in the axial directions of the first and second pivot shafts 229 , 230 are mechanically exactly synchronized with each other by the pivot arm 280 . During the speed ratio change operation, the amounts of displacement of the first and second pivots 227 , 228 quickly and exactly match, so that during the speed ratio change operation, the generation of any slip in the contact areas between the inner surfaces 202 a, 204 a ( Fig. 26) of the first and second drive pulleys 217 , 218 and the first and second driven pulleys 220 , 221 and the peripheral surfaces 209 a (FIGS . 15, 27 and 28) of the first and second drive pulleys 245 , 246 can be prevented.

Results of tests performed to confirm the effect of the invention in this connection will now be explained with reference to FIGS. 22A to 23B. The tests were carried out using the double cavity type toroidal continuously variable transmission in which a pair of drive rollers are provided for each of the cavities, as shown in FIG . In the tests, four pivot pins 227 , 228 , the front right (FR) and front left (FL) drive rollers near the press device 210, and rear right (RR) and rear left (RL) drive rollers were supported away from the press device (ie, support a total of four drive rollers 245 , 246 ), during the speed ratio change operation, the axial displacement amounts and pivot angles of the pivots 227 , 228 that were generated after a predetermined amount of pressurized oil was introduced into the drive cylinders, depending on measured by time. FIG. 22A and 22B show a test result for the continuously variable gear Toroidge the invention, wherein Fig. 22A shift amounts, the axial Ver the pivot pin, and Fig. 22B shows the pivot angle of the pivot. FIG. 23A and 23B show the case in which the displacements of the trunnions were adjusted merely by adjusting the oil pressure, Fig. 23A shows the axial displacement amounts of the trunnions and Fig. 23B shows the pivot angle of the pivot. As shown in FIGS. 22A to 23B showing the test results, according to the present invention, the displacements of the pivots can be precisely synchronized with each other even when performing a rapid speed ratio change operation.

In the toroidal continuously variable transmission of this embodiment, the yokes 258 , 259 , which form the first and second support devices, are directly supported by the inner surface of the housing 205 and attached to it. Thus, the support posts 233 a, 233 b (see the reference numerals 33 a, 33 b in Figs. 27 and 28), which are required in the conventional arrangement, can be omitted, so that the number of parts is reduced by the Manufacturing, the control and assembly of the parts to facilitate, and the height of the toroidal continuously variable transmission is reduced, so that the transmission has compact dimensions and light weight while maintaining the service life.

Furthermore, since the ball-groove connections 260 and the radial needle bearings 261 are arranged between the pivot shafts 229 and the yokes 258 , 259 , the displacements of the first and second pivots 227 , 228 with respect to the yokes 258 , 259 can be evenly and correctly be carried out. That is, as is apparent from the above-mentioned explanations, that during the speed ratio operation of the toroidal continuously variable transmission, the first and second pivots 227 , 228 are displaced in the axial directions of the first and second pivot shafts 229 , 230 , with the result that the pivots are rotated the first and second pivot shafts 229 , 230 are pivotally displaced due to the axial displacements. In the embodiment shown, the axial displacements by the ball-groove connections 260 are carried out uniformly from these displacements and the pivot displacements are carried out uniformly by the radial needle bearing 261 , so that the speed ratio change operation of the toroidal continuously variable transmission based on these displacements is quick and correct can be executed.

Since the gear transmission mechanism 282 is provided in the illustrated embodiment, the inclination angles of the first and second drive rollers 245 can be brought into agreement with each other even when an oil pressure supply line to the drive cylinders 252 is damaged. Therefore, even in the event of a malfunction, serious slippage in the contact areas between the peripheral surfaces 209 a of the first and second drive rollers 245 and the inner surfaces 202 a, 204 a of the disks 217 , 218 , 220 , 221 can be prevented, thereby damaging the stepless Toroidal gear can be avoided.

Since the invention has the above-mentioned construction and has the above-mentioned functions, can be quick Speed ratio change operation while maintaining the life span, which makes the possibility the application of the stepless toroidal gear high-performance vehicles such as sports vehicles increased becomes. Therefore, the invention is of practical use stepless toroidal gear.

When the invention is carried out, a mechanism for achieving matching of the tilt angle of the trunnions is not limited to the gear transmission mechanisms 282 , 71 or 156 , but a mechanism using a rope as shown in Figs. 29 and 30 is shown.

A conventional synchronization mechanism using a rope will now be described with reference to FIGS . 29 and 30.

Such mechanisms are well known and are disclosed, for example, in JP 63-67458-A (1988), JP 4-327051-A (1992) and JP 62-200852-A (1987). Figures 29 and 30 show two examples disclosed in JP 4-327051-A. Now, based on these figures, a mechanism for synchronizing the pivotal movements of the first and second pivots 227 , 228 in the double cavity type stepless toroidal drive will be explained.

In the construction of the synchronization mechanisms , pulleys 354 are attached to the axial ends (at the ends in the direction perpendicular to the planes of FIGS. 29 and 30) of the first and second pivots 227 , 228 . The peripheral surfaces of the pulleys 354 are formed as curved surfaces which are coaxial with the pivot shafts 329 , 330 (see reference numerals 29 , 30 in FIGS. 27 and 28). Rope sections 355 , 355 a, 355 b are inserted and wound around the grooves formed in the peripheral surfaces of the pulleys 354 , so that a total of four first and second pivots 227 , 228 are pivoted synchronously. That is, in any of the arrangements of each rope 355, only the two sheaves 354 , which are attached to the ends of the first and second pivots 227 , 228 , are wound cross-wise through each pair. Therefore, the pair of first and second pivots 227 , 228 (located in the same cavity) can be rotated through the same angle in opposite directions, with the pulleys 354 arranged along a diagonal line (and located in different cavities and on are arranged diametrically opposite positions with respect to the drive shaft 301 a) can be rotated in the same direction by the same amount.

For this purpose, in the arrangement according to the first example shown in FIG. 29, the rope 355 a is only placed between the rope sheaves 354 arranged along the diagonal line, the rope 355 being attached to the rope sheaves 354 arranged along the diagonal line BEFE stigungseinrichtung 356 is attached. On the other hand, the cable 355 b in the arrangement according to the second example shown in FIG. 30 is wound around all the pulleys 354 , the cable 355 b being fastened to the two pulleys 354 fastening devices 356 which are arranged along the diagonal line. Any slip can be generated between the remaining sheaves 354 and the rope 355 b, so that the movement of the rope 355 b is not transmitted to the remaining sheaves 354 . The arrangement shown in Fig. 30 is det USAGE to interference between the cable 355 b, and countries other, the toroidal continuously variable transmission forming elements such as the first and second driven pulleys 320, 321 and the output gear having a large diameter to verhin. Also in the stepless toroidal gear of the so-called single cavity type, in which a single drive pulley and a single driven pulley are provided, the pivotal movements of the plurality of pivots can be synchronized with each other by providing the cross winding type cable 355 as shown in Figs. 29 and 30. Although not shown, JP 4-52512-A (1992), JP 6-117515-A (1994) and JP 7-243496-A (1995) disclose techniques in which a mechanism for synchronizing tilt angles of multiple pivots is formed by a gear transmission mechanism is.

There can be many very different versions of the Invention can be constructed without the inventive concept and depart from the scope of the invention. Of course Lich, the invention is not limited to those described above specific designs, but only by the scope of the appended claims.

Claims (11)

1. Stepless toroidal gear, with:
a housing ( 5 ),
Input and output disks ( 2 , 4 ) which are supported coaxially in the housing ( 5 ) and can be rotated independently of one another,
an even number of swivel shafts ( 29 , 30 ) which are arranged coaxially or parallel to one another between the disks ben ( 2 , 4 ) at offset positions at which the swivel shafts ( 29 , 30 ) do not have the central axis of the disks ( 2 , 4 ) intersect, but extend in directions perpendicular to the central axis,
a plurality of pivots ( 27 , 28 ) which can be pivoted about the pivoting shafts ( 29 , 30 ),
Displacement shafts ( 40 , 41 ) projecting from the inner surfaces of the trunnions ( 27 , 28 ),
a plurality of drive rollers ( 45 ) which are rotatably supported about the displacement shafts and are inserted between the inner surfaces of the drive and driven disks ( 2 , 4 ), and
Support devices ( 54 , 55 ) which are provided on the sides of the drive rollers ( 45 ) and are designed such that they support the pivot shafts ( 29 , 30 ) for a pivoting movement and an axial movement, characterized in that the elements ( 54 , 55 ), which form the support devices, are supported and attached directly to an inner surface of the housing ( 5 ). 2. Stepless toroidal gear, with:
a housing ( 5 ),
first and second outer disks ( 220 , 221 ), which are supported coaxially to one another in the housing ( 5 ) and can be rotated synchronously with one another, the inner surfaces of the disks ( 220 , 221 ) being opposite one another,
a first inner washer ( 217 ) supported coaxially with the first and second outer washers ( 220 , 221 ), can be rotated independently of the first and second outer washers ( 220 , 221 ) and has an inner surface that corresponds to the inner Opposite surface of the first outer disc ( 217 ),
a second inner washer ( 218 ) supported coaxially with the first inner washer ( 217 ) and rotatable in synchronism with the first inner washer ( 217 ) and having an inner surface opposite the inner surface of the second outer washer ( 221 ) ,
four first pivot shafts ( 229 ) which are arranged coaxially or parallel to one another between the first outer disk ( 220 ) and the first inner disk ( 217 ) at offset positions at which the pivot shafts ( 229 ) do not intersect the central axis of the disks, but rather intersect extend in directions perpendicular to the central axis,
a pair of first pivots ( 227 ) which are pivotable about the first pivot shafts ( 229 ),
first displacement shafts ( 240 , 241 ) protruding from the inner surfaces of the first pivots ( 227 ),
a pair of first drive rollers ( 245 ) rotatably supported about the first displacement shafts ( 240 , 241 ) and interposed between the inner surface of the first outer plate ( 220 ) and the inner surface of the first inner plate ( 217 ),
four second swivel shafts ( 278 ) which are arranged coaxially or parallel to one another between the second outer disk ( 221 ) and the second inner disk ( 218 ) at offset positions, the swivel shafts ( 278 ) not cutting the central axis of the disks, but rather extend in directions perpendicular to the central axis,
a pair of second pivots ( 228 ) which are pivotable about the second pivot shafts ( 278 ),
second displacement shafts ( 242 , 243 ) protruding from the inner surfaces of the second pivots ( 228 ),
a pair of second drive rollers ( 246 ) rotatably supported about the second displacement shafts ( 242 , 243 ) and interposed between the inner surface of the second outer disc ( 221 ) and the inner surface of the second inner disc ( 218 ), and
first and second support means (258, 259) which are substantially parallel to each other on the sides of first and second inner plates (217, 218) are provided, wherein the first and second hold ren discs (217, 218) is inserted in such a manner are that the one ends of the first and second support devices ( 258 , 259 ) between the first outer plate ( 220 ) and the first inner plate ( 217 ) are arranged and the other ends between the second outer plate ( 221 ) and the second inner Disc ( 218 ) are arranged, wherein
the first support device ( 258 ) supports two of the four first pivot shafts ( 229 ) and two of the four second pivot shafts ( 278 ) for a pivoting movement and an axial displacement, and
the second support device ( 259 ) supports the other two of the four first swivel shafts ( 258 ) and the other two of the four second swivel shafts ( 278 ) for swivel movement and axial displacement, characterized in that the elements ( 258 , 259 ) which the form first and second support devices, are directly supported and attached to an inner surface of the housing ( 5 ). 3. Stepless toroidal gear, with:
a housing ( 5 ),
Input and output disks ( 2 , 4 ) which are supported coaxially in the housing ( 5 ) and can be rotated independently of one another,
an even number of swivel shafts ( 29 , 30 ) which are arranged coaxially or parallel to one another between the disks ben ( 2 , 4 ) at offset positions at which the swivel shafts ( 29 , 30 ) do not have the central axis of the disks ( 2 , 4 ) intersect, but extend in directions perpendicular to the central axis,
a plurality of pivots ( 27 , 28 ) which can be pivoted about the pivoting shafts ( 29 , 30 ),
Displacement shafts ( 40 , 41 ) projecting from the inner surfaces of the trunnions ( 27 , 28 ),
a plurality of drive rollers ( 45 ) which are rotatably supported about the displacement shafts and are inserted between the inner surfaces of the drive and driven disks ( 2 , 4 ), and
Support devices ( 54 , 55 ) which are provided on the sides of the drive rollers ( 45 ) and are designed such that they support the pivot shafts ( 29 , 30 ) for a pivoting movement and an axial movement, characterized in that
Yokes ( 54 , 55 ) forming part of the support means and having ends that support the pivot shafts ( 29 , 30 ) provided at the ends of the plurality of pivots ( 27 , 28 ) on an inner surface of the housing ( 5 ) are directly supported and attached under
the swivel shafts ( 29 , 30 ) can be pushed by means of groove connections ( 56 ) with respect to the ends of the yokes ( 54 , 55 ) and needle bearings ( 57 ) are provided within the groove connections ( 56 ) which provide the swivel shaft ( 29 , 30 ) pivotally support. 4. Stepless toroidal gear, with:
a housing ( 5 ),
first and second outer disks ( 220 , 221 ), which are supported coaxially to one another in the housing ( 5 ) and can be rotated synchronously with one another, the inner surfaces of the disks ( 220 , 221 ) being opposite one another,
a first inner washer ( 217 ) supported coaxially with the first and second outer washers ( 220 , 221 ), can be rotated independently of the first and second outer washers ( 220 , 221 ) and has an inner surface that corresponds to the inner Opposite surface of the first outer disc ( 217 ),
a second inner washer ( 218 ) supported coaxially with the first inner washer ( 217 ) and rotatable in synchronism with the first inner washer ( 217 ) and having an inner surface opposite the inner surface of the second outer washer ( 221 ) ,
four first pivot shafts ( 229 ) which are arranged coaxially or parallel to one another between the first outer disk ( 220 ) and the first inner disk ( 217 ) at offset positions at which the pivot shafts ( 229 ) do not intersect the central axis of the disks, but rather intersect extend in directions perpendicular to the central axis,
a pair of first pivots ( 227 ) which are pivotable about the first pivot shafts ( 229 ),
first displacement shafts ( 240 , 241 ) protruding from the inner surfaces of the first pivots ( 227 ),
a pair of first drive rollers ( 245 ) rotatably supported about the first displacement shafts ( 240 , 241 ) and interposed between the inner surface of the first outer plate ( 220 ) and the inner surface of the first inner plate ( 217 ),
four second pivot shafts ( 278 ) which are arranged coaxially or parallel to one another between the second outer disc ( 221 ) and the second inner disc ( 218 ) at offset positions, the pivot shafts ( 278 ) not intersecting the central axis of the discs, but instead extend in directions perpendicular to the central axis,
a pair of second pivots ( 228 ) which are pivotable about the second pivot shafts ( 278 ),
second displacement shafts ( 242 , 243 ) protruding from the inner surfaces of the second pivots ( 228 ),
a pair of second drive rollers ( 246 ) rotatably supported about the second displacement shafts ( 242 , 243 ) and interposed between the inner surface of the second outer disc ( 221 ) and the inner surface of the second inner disc ( 218 ), and
first and second support means (258, 259) which are substantially parallel to each other on the sides of first and second inner plates (217, 218) are provided, wherein the first and second hold ren discs (217, 218) is inserted in such a manner are that the one ends of the first and second support devices ( 258 , 259 ) between the first outer plate ( 220 ) and the first inner plate ( 217 ) are arranged and the other ends between the second outer plate ( 221 ) and the second inner Disc ( 218 ) are arranged, wherein
the first support device ( 258 ) supports two of the four first pivot shafts ( 229 ) and two of the four second pivot shafts ( 278 ) for a pivoting movement and an axial displacement, and
the second support device ( 259 ) supports the other two of the first four pivot shafts ( 258 ) and the other two of the four second pivot shafts ( 278 ) for pivoting movement and axial displacement, characterized in that
Yokes ( 258 , 259 ) forming the first and second support means and four corners for supporting the pivot shafts ( 229 , 278 ) provided at the ends of the plurality of pivots ( 227 , 228 ) on an inner surface of the housing ( 5 ) are directly supported and attached, and
the swivel shafts ( 229 , 278 ) can be moved axially by means of groove connections ( 260 ) with respect to the four corners of the yokes ( 258 , 259 ) and in the groove connections ( 260 ) needle bearings ( 261 ) for pivotable support of the swivel shafts ( 229 , 278 ) are provided. 5. Continuously variable toroidal gear according to one of claims 3 or 4, characterized in that:
the groove connections are ball-groove connections ( 260 ) and
outer circumferential surfaces of outer raceways, which are formed in inner circumferential surfaces of the ball grooves forming the ball-groove connections, are designed as semispherical, convex surfaces which are pivotally received in circular holes formed in the yokes ( 258 , 259 ). 6. Toroidal continuously variable transmission according to any one of claims 1 to 4, characterized in that a gear drive mechanism ( 71 , 156 , 282 ) between the plurality of pivots ( 27 , 28 , 227 , 228 ) is provided, which the inclination movements of the pivots ( 27 , 28th , 227 , 228 ). 7. Stepless toroidal gear, with:
a housing ( 5 ),
Drive and driven pulleys (2, 4) which are coaxially supported in the housing (5) to each other and can rotate independently of each other, wherein the inner surfaces of the disks (2, 4) opposed to each other,
four or a higher even number of swivel shafts ( 29 , 30 ) which are arranged coaxially or parallel to each other between the drive pulley ( 2 ) and the driven pulley ( 4 ) at offset positions at which the swivel shafts ( 29 , 30 ) the central axis the slices do not cut, but extend in directions perpendicular to the central axis,
several pivots ( 27 , 28 ) which can pivot about the pivoting shafts ( 29 , 30 ),
Displacement shafts ( 40 , 41 ) protruding from the inner surface of the trunnions ( 27 , 28 ),
a plurality of drive rollers ( 45 ) which are rotatably supported about the displacement shafts ( 40 , 41 ) and between the inner surface of the drive pulley ( 2 ) and the inner surface of the driven pulley ( 4 ) are inserted, and
several actuators ( 53 ) in the same number as the pivots ( 27 , 28 ), which are designed so that they can move the pivots ( 27 , 28 ) in the axial direction of the pivot shafts ( 29 , 30 ), characterized by a synchronization mechanism ( 71 ) which mechanically synchronizes the displacement movements of the pivots ( 27 , 28 ) in the axial direction of the pivot shafts ( 29 , 30 ), which are caused by the actuators ( 53 ). 8. Stepless toroidal gear, with:
a housing ( 5 ),
first and second outer disks ( 220 , 221 ), which are supported coaxially to one another in the housing ( 5 ) and can be rotated synchronously, the inner surfaces of the disks ( 220 , 221 ) lying opposite one another,
a first inner washer ( 217 ) supported coaxially with the first and second outer washers ( 220 , 221 ), can be rotated independently of the first and second outer washers ( 220 , 221 ) and has an inner surface that corresponds to the inner Opposite surface of the first outer disc ( 220 ),
a second inner disc ( 218 ) supported coaxially with the first inner disc ( 217 ) and rotatable in synchronism with the first inner disc ( 217 ) and having an inner surface opposite the inner surface of the second outer disc ( 221 ) ,
four or more even number of first pivot shafts ( 229 ) coaxially or parallel to each other between the first outer disc ( 220 ) and the first inner disc ( 217 ) at offset positions where the pivot shafts ( 229 ) are the center axis of the discs do not cut, but extend in directions perpendicular to the central axis,
a plurality of first pivots ( 227 ) which can pivot about the first pivot shafts ( 229 ),
first displacement waves projecting from inner surfaces of the first pivots ( 227 ),
a plurality of first drive rollers ( 245 ) which are rotatably supported about the first displacement shafts and are inserted between the inner surface of the first outer disk ( 220 ) and the inner surface of the first inner disk ( 217 ),
four or a higher even number of second pivot shafts ( 278 ), which are arranged coaxially or parallel to one another between the second outer disk ( 221 ) and the second inner disk ( 218 ) at offset positions, at which the pivot shafts ( 278 ) are the means Do not cut the axis of the disks, but extend in directions perpendicular to the central axis,
a plurality of second pivots ( 228 ) which can be pivoted about the second pivot shafts ( 278 ),
second displacement shafts protruding from inner surfaces of the second pivots ( 228 ),
a plurality of second drive rollers ( 246 ), which are rotatably supported around the second displacement shafts and are inserted between the inner surface of the second outer disk ( 221 ) and the inner surface of the second inner disk ( 218 ), and
a plurality of actuators ( 53 ), which are present in the same number as the pivots ( 227 , 228 ) and are designed such that they can move the pivots ( 227 , 228 ) in the axial direction of the pivot shafts ( 229 , 278 ), characterized by a synchronization mechanism ( 282 ), the displacement movements of the pivots ( 227 , 228 ) in the axial direction of the pivot shafts ( 229 , 278 ), which are caused by the actuators ( 53 ), mechanically synchronized. 9. stepless toroidal gear according to claim 7 or 8, characterized in that the synchronization mechanism ( 71 , 282 ) contains:
Receiving parts ( 272 ) which have near ends which are fastened to the ends of the pivots ( 227 , 228 ) and which are attached to the tip ends of drive rods ( 51 ) which can move axially through the actuators ( 53 ), to move the pivots ( 27 , 28 , 227 , 228 ) in the axial direction of the pivot shafts ( 29 , 30 , 229 , 278 ), and
a swing arm ( 280 ) which has ends which are engaged with the receiving parts ( 278 ) to be pivoted only single, its middle portion by a second pivot shaft which forms a fixed section from parallel to a rotational center line of the disks is arranged, is pivotally supported. 10. Continuous toroidal transmission according to claim 5, 7 or 8, characterized in that between the plurality of pivots ( 27 , 28 , 227 , 228 ) a gear transmission mechanism ( 71 , 156 , 282 ) is provided, which the inclination movements of the pivots ( 27 , 28th , 227 , 228 ). 11. Toroidal continuously variable transmission according to claim 9, characterized in that between the plurality of pivots ( 27 , 28 , 227 , 228 ) a gear transmission mechanism ( 71 , 156 , 282 ) is provided, which the inclination movements of the pivots ( 27 , 28 , 227 , 228 ) synchronized.