JPH08145136A - Troidal type continuously variable transmission - Google Patents

Abstract

PURPOSE: To prevent enlargement of the outside diameter because of existence of a cable for fool proof. CONSTITUTION: Drive cylinders 38, 38 and drive pistons 37, 37 to constitute an actuator for displacing trunnions 6, 6 are installed in the middle between driving rods 36, 36. Pulleys 48a, 48a are secured to the tips of these driving rods 36, 36. Between adjoining cavities, cables 40c, 40c are set over the pulleys 48a, 48a in the form of crossing diagonally.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION The toroidal type continuously variable transmission according to the present invention is used, for example, as a transmission for automobiles or as a transmission for various industrial machines.

[0002]

2. Description of the Related Art As a transmission for an automobile, the use of a toroidal type continuously variable transmission as schematically shown in FIGS. This toroidal type continuously variable transmission supports an input side disk (first disk) 2 concentrically with the input shaft 1 as disclosed in, for example, Japanese Utility Model Laid-Open No. 62-71465, and An output side disk (second disk) 4 is fixed to the end of the output shaft 3 arranged concentrically. Inside the casing containing the toroidal type continuously variable transmission,
There are provided trunnions 6, 6 swinging around pivots 5, 5 in a twisted position with respect to the input shaft 1 and the output shaft 3.

The trunnions 6, 6 are provided with the pivots 5, 5 on the outer surfaces of both ends. Further, the base ends of the displacement shafts 7, 7 are supported by the central portions of the trunnions 6, 6, and the trunnions 6, 6 are swung about the pivot shafts 5, 5, so that the displacement shafts 7, The inclination angle of 7 can be freely adjusted. Power rollers 8, 8 are rotatably supported around displacement shafts 7, 7 supported by the trunnions 6, 6, respectively. The power rollers 8, 8 are sandwiched between the input side and output side disks 2, 4.

The inner surfaces 2a, 4a of the input-side and output-side disks 2, 4 facing each other have a cross-section of a concave surface obtained by rotating an arc about the pivot 5. The peripheral surfaces 8a, 8a of the power rollers 8, 8 formed in the spherical convex surface are in contact with the inner side surfaces 2a, 4a.

A loading cam type pressing device 9 is provided between the input shaft 1 and the input side disk 2, and the pressing device 9 causes the input side disk 2 to face the output side disk 4 and elastically moves. Pressing. This pressing device 9
Is a cam plate 10 that rotates together with the input shaft 1, and a retainer 11.
A plurality of (for example, four) rollers 12 held by
It is composed of 12 and. On one side surface (right side surface of FIGS. 4 to 5) of the cam plate 10, there is formed a cam surface 13 which is an uneven surface extending in the circumferential direction, and an outer side surface of the input side disk 2 (left side of FIGS. 4 to 5). The same cam surface 14 is also formed on the surface). Then, the plurality of rollers 12, 12 are rotatably supported about a shaft in the radial direction with respect to the center of the input shaft 1.

When the toroidal type continuously variable transmission constructed as described above is used, when the cam plate 10 rotates as the input shaft 1 rotates, the cam surface 13 causes the plurality of rollers 12, 1 to rotate.
2 is pressed against the cam surface 14 on the outer surface of the input side disk 2. As a result, the input side disk 2 is pressed by the plurality of power rollers 8, 8 and at the same time, based on the meshing between the pair of cam surfaces 13, 14 and the plurality of rollers 12, 12. The input side disk 2 rotates. And
The rotation of the input side disk 2 is transmitted to the output side disk 4 through the plurality of power rollers 8 and the output shaft 3 fixed to the output side disk 4 rotates.

When the rotational speed ratio (gear ratio) between the input shaft 1 and the output shaft 3 is changed, first, when deceleration is performed between the input shaft 1 and the output shaft 3, the pivot shafts 5 and 5 are centered. As shown in FIG. 4, the respective trunnions 6, 6 are swung so that the peripheral surfaces 8a, 8a of the respective power rollers 8, 8 are near the center of the inner side surface 2a of the input side disk 2 and the inner side surface of the output side disk 4. 4a
The displacement shafts 7, 7 are tilted so as to contact the outer peripheral portions of the displacement shafts 7, 7, respectively.

On the other hand, when increasing the speed, the trunnions 6, 6 are swung about the pivots 5, 5, and the peripheral surfaces 8a, 8a of the power rollers 8, 8 are shown in FIG. In the same manner, in the outer peripheral portion of the inner side surface 2a of the input side disk 2 and the central portion of the inner side surface 4a of the output side disk 4,
The displacement shafts 7, 7 are tilted so that they come into contact with each other.
If the inclination angles of the displacement shafts 7, 7 are set in the middle between FIG. 4 and FIG. 5, an intermediate gear ratio can be obtained between the input shaft 1 and the output shaft 3.

Further, FIGS. 6 to 7 show Japanese Patent Application No. 63-6929.
3 shows a more specific toroidal-type continuously variable transmission described in the microfilm of No. 3 (Actual Kaihei No. 1-173552). Input side disk 2 and output side disk 4
Is rotatably supported around a cylindrical input shaft 15 via needle bearings 16 and 16, respectively. The cam plate 10 is spline-engaged with the outer peripheral surface of the end portion (the left end portion in FIG. 6) of the input shaft 15, and is prevented from moving in the direction away from the input side disk 2 by the collar portion 17. Then, the cam plate 10 and the rollers 12 and 12 cause the input side disk 2 to rotate based on the rotation of the input shaft 15.
Constitutes a loading cam type pressing device 9 for rotating the disk while pressing it toward the output side disk 4. An output gear 18 is connected to the output side disk 4 by keys 19 and 19 so that the output side disk 4 and the output gear 18 rotate in synchronization with each other.

Both ends of the pair of trunnions 6, 6 are supported by the pair of support plates 20, 20 so as to be swingable and displaceable in the axial direction (front and back directions in FIG. 6, left and right directions in FIG. 7). There is.
The displacement shafts 7, 7 are supported in the circular holes 23, 23 formed in the intermediate portions of the trunnions 6, 6. The displacement shafts 7, 7 are parallel to each other and eccentric to the support shaft portion 2.
1 and 21 and pivots 22 and 22, respectively.
Each of the support shafts 21, 21 is connected to each of the circular holes 23, 2
It is rotatably supported on the inside of 3 via radial needle bearings 24, 24. Also, each of the pivot shafts 2
Power rollers 8, 8 are rotatably supported around 2, 22 via radial needle bearings 25, 25.

The pair of displacement shafts 7, 7 are provided at positions opposite to the input shaft 15 by 180 degrees. or,
The direction in which the pivot shafts 22, 22 of the displacement shafts 7, 7 are eccentric with respect to the support shafts 21, 21 is the same as the rotation direction of the input side and output side disks 2, 4. In FIG. 7, the left and right directions are reversed. Further, the eccentric direction is a direction substantially orthogonal to the arrangement direction of the input shaft 15. Therefore, each of the power rollers 8 and 8 is supported so as to be slightly displaceable in the arrangement direction of the input shaft 15. As a result, the power rollers 8, 8 tend to be displaced in the axial direction of the input shaft 15 (left and right direction in FIG. 6, front and back direction in FIG. 7) due to dimensional accuracy of each component. Even in this case, this displacement can be absorbed without applying excessive force to each component.

Between the outer surface of each of the power rollers 8 and 8 and the inner surface of the intermediate portion of each of the trunnions 6, 6 in this order from the outer surface of the power rollers 8, 8. Thrust ball bearings 26 for bearing 8
26 and thrust needle bearings 27, 27 that support the thrust load applied to the outer rings 30, 30 described below. The thrust ball bearings 26, 26 support the loads in the thrust direction applied to the power rollers 8, 8 and allow the power rollers 8, 8 to rotate. Such thrust ball bearings 26, 26 are each a plurality of balls 29, 29, annular retainers 28, 28 for rotatably holding the balls 29, 29, and a circle which is a thrust bearing ring. It is composed of an annular outer ring 30, 30. The inner ring raceways of the thrust ball bearings 26, 26 are formed on the outer side surfaces of the power rollers 8, 8 and the outer ring raceways are formed on the inner side surfaces of the outer races 30, 30 respectively.

Further, the thrust needle bearings 27, 27
Is composed of a race 31, a retainer 32, and needles 33, 33. Of these, the race 31 and the cage 32 are combined so as to be slightly displaceable in the rotational direction. Such thrust needle bearings 27, 27 are provided between the inner surfaces of the trunnions 6 and 6 and the outer surfaces of the outer rings 30, 30 in a state where the races 31, 31 are in contact with the inner surfaces of the trunnions 6, 6. It is sandwiched. The thrust needle bearings 27, 27 as described above support the thrust load applied to the outer rings 30, 30 from the power rollers 8, 8 while the pivot shafts 22, 22 and the outer rings 30, 30 are in contact with each other. It is allowed to swing around the support shaft portions 21, 21.

Further, drive rods 36, 36 are connected to one end portions (the left end portions in FIG. 7) of the trunnions 6, 6 respectively, and drive pistons 37, 37 are provided on the outer peripheral surfaces of the intermediate portions of the drive rods 36, 36. Is fixed. Then, the drive pistons 37, 37 are respectively connected to the drive cylinder 3
8 and 38 are oil-tightly fitted. The drive pistons 37, 37 and the drive cylinders 38, 38 constitute actuators for displacing the trunnions 6, 6 in the axial directions of the pivots 5, 5, respectively.

During operation of the toroidal type continuously variable transmission configured as described above, the rotation of the input shaft 15 is transmitted to the input side disk 2 via the pressing device 9. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 via the pair of power rollers 8, 8 and the rotation of the output side disk 4 is taken out from the output gear 18.

When changing the rotational speed ratio between the input shaft 15 and the output gear 18, the pair of drive pistons 37,
37 is displaced in opposite directions. As the drive pistons 37, 37 are displaced, the pair of trunnions 6,
6 are displaced in opposite directions, for example, the lower power roller 8 in FIG. 7 is displaced to the right side in FIG. 7, and the upper power roller 8 in FIG. 7 is displaced to the left side in FIG. As a result, the peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner side surfaces 2a, 4a of the input side disk 2 and the output side disk 4 are described.
The direction of the tangential force acting on the contact portion with and changes. The trunnions 6, 6 are pivotally supported by the support plates 20, 20 according to the change in the direction of the force.
It swings in directions opposite to each other with 5 as the center. As a result,
As shown in FIGS. 4 to 5, the power rollers 8,
The abutting positions of the peripheral surfaces 8a, 8a of 8 and the respective inner side surfaces 2a, 4a change, and the rotation speed ratio between the input shaft 15 and the output gear 18 changes.

In this way, the input shaft 15 and the output gear 1 are as described above.
When changing the inclination angle of the displacement shafts 7, 7 in order to change the rotation speed ratio between the displacement shafts 7, 8, the displacement shafts 7, 7 are slightly moved around the support shaft portions 21, 21. Rotate. As a result of this rotation, each thrust ball bearing 2
The outer side surfaces of the outer races 30, 30 of 6, 26 and the inner side surfaces of the trunnions 6, 6 are relatively displaced. The thrust needle bearings 27, 27 are provided between the outer side surface and the inner side surface.
, The force required for this relative displacement is small.

Further, arcuate surfaces 39, 39 concentric with the pivots 5, 5 are formed on the outer peripheral surfaces of the ends of the trunnions 6, 6. The cable 40 is hung between the two arcuate surfaces 39, 39. still,
Stoppers 41, 41 are provided on a portion of the cable 40 corresponding to the arc surfaces 39, 39 to prevent the cable 40 and the arc surfaces 39, 39 from slipping. Such a cable 40 is used for both the trunnions 6 and 6 described above.
The tilting movements (the swinging movements about the respective pivots 5, 5) are synchronized with each other. Then, the drive rods 36, 36, drive pistons 37, 37, drive cylinder 3
Even when the actuator (hydraulic drive device) including 8, 38 and the like fails, the trunnions 6, 6 are tilted in synchronization with each other. Therefore, even if the actuator fails, the inclination directions of the plurality of power rollers 8 sandwiched between the pair of the input side disk 2 and the output side disk 4 do not become disjointed. As a result, an excessive frictional force does not act between the inner surfaces 2a and 4a of the disks 2 and 4 and the peripheral surfaces 8a and 8a of the power rollers 8 and 8, and the toroidal type continuously variable transmission is provided. Will not be fatally damaged, and the minimum power transmission can be secured.

Regarding the arrangement structure of the cable 40 which fulfills such a role, the above-mentioned Japanese Utility Model Application No. 63-692 has been conventionally used.
In addition to the structure described in the microfilm of Japanese Patent No. 93 (Japanese Utility Model Laid-Open No. 1-173552), Japanese Patent Laid-Open Nos. 63-67458, 4-327051 and 62-20.
Those described in Japanese Patent No. 0852 and the like are known. 8 to 9 show two examples of the structure described in JP-A-4-327051. 8 to 9, the function of the cable 40 will be further described.

The structures shown in FIGS. 8 to 9 are similar to those shown in FIGS.
7 shows a so-called double cavity structure in which two sets of the input side disks 2 and 2 and the output side disks 4 and 4 are provided in parallel with each other in order to transmit a larger power than that of the structure described in 7. . Each of the input disks 2 and 2 corresponds to the first disk, and each of the output disks 4 and 4 corresponds to the second disk. Between the input side disks 2 and 2 and the output side disks 4 and 4 of each set, there are two power rollers 8 and 8 which are a first power roller and a second power roller, respectively.
A total of four pieces are provided. The power rollers 8 and 8 are rotatably supported on the inner surfaces of the four trunnions 6 and 6, which are the first trunnion and the second trunnion, respectively. Axial direction (left and right direction in Figures 8-9)
The rotational power transmitted from the pair of input-side disks 2 and 2 existing at both ends to the pair of output-side disks 4 and 4 located at the central portion in the axial direction is coupled between the both output-side disks 4 and 4. It is taken out to the output shaft 45 via the large gear 43 that has been formed and the small gear 44 that meshes with the large gear 43.

Then, the pulleys 42, which are the first engaging portion or the second engaging portion, are respectively provided at the axial end (front and back direction in FIGS. 8 to 9) end portions of the trunnions 6 and 6 which constitute such a structure. ,
42 is fixed, and the outer peripheral surfaces of the pulleys 42, 42 are arcuate surfaces concentric with the pivots 5, 5 (see FIG. 7). Then, a part of the cables 40, 40a, 40b are fitted over the groove formed on the outer peripheral surface of each of the pulleys 42, 42 so as to fit over them, and the four trunnions 6, 6 are tilted synchronously. I am doing it. That is, in any structure, the cables 40, 40 are hung between the pair of pulleys 42, 42 fixed to the ends of the pair of trunnions 6, 6 constituting each set. ing. Therefore,
The pair of trunnions 6, 6 forming each set rotate in the opposite direction by the same angle. In addition, the pulley 4 existing in the diagonal position
2, 42 are rotatable in the same direction by the same angle.

For this reason, in the structure of the first example shown in FIG.
The cable 40a is stretched only between the pulleys 42, 42 existing in the diagonal position, and the cable 40a and the pulleys 42, 42 existing in the diagonal position are coupled by the stoppers 46, 46. On the other hand, in the structure of the second example shown in FIG. 9, instead of hanging the cable 40b over all the pulleys 42, 42, the stoppers 46, 46 are provided only for the pair of pulleys 42, 42 existing in the diagonal position. Thus, the cable 40b is connected. Sliding plates 47, 4 are provided between the remaining pulleys 42, 42 and the cable 40b.
7 is interposed so that the movement of the cable 40b is not transmitted to the remaining pulleys 42, 42. In the structure shown in FIG. 9, the cable 40b is connected to the output side disk 4,
4 and the outer periphery of the large gear 43, etc., to prevent interference with other members constituting the toroidal type continuously variable transmission.

Cables 40, 4 which perform the above-mentioned functions.
0a (or 40b) of the trunnions 6 and 6 in a more specific arrangement in the axial direction is as follows.
No. 6246. 10 to 11 show the structure described in this publication. The cables 40, 40 for synchronizing the tilting of the two trunnions 6, 6 (existing in the same cavity) located between the same input side disc 2 and output side disc 4 are the trunnions 6, 6 are engaged with the arcuate surfaces 39, 39 formed at the ends. The cables 40, 40 are arranged between the input side disk 2 and the output side disk 4, respectively.

On the other hand, the cable 40a for synchronizing the tilting movement of the plurality of trunnions 6 (existing in the adjacent cavities) located between the different input side discs 2 and output side discs 4 is provided with the respective trunnions. 6 and 6 are arranged in a portion separated from the main body portion. That is, the pulleys 48, 4 are provided at the intermediate portions of the drive rods 36, 36 for connecting the trunnions 6, 6 with the drive pistons 37, 37, respectively.
By fixing 8 the first and second engaging portions are formed.
The cable 40 is attached to both pulleys 48, 48.
By crossing over a, the tilting motions of the plurality of trunnions 6, 6 existing in the adjacent cavity are synchronized. The drive cylinders 38, 38 fitted with the drive pistons 37, 37 in an oil-tight manner are present on the side opposite to the power rollers 8, 8 with respect to the pulleys 48, 48.

[0025]

In the case of the conventional toroidal type continuously variable transmission configured and operating as described above, it is difficult to design the toroidal type continuously variable transmission while preventing interference between the parts. That is, in the conventional structure as described above, the cable 40a for synchronizing the tilting of the trunnions 6 in the adjacent cavities is provided between the trunnions 6 and 6 and the drive cylinders 38. Therefore, the cable 40a is arranged between the cavities adjacent to each other at a position between the trunnions 6 and 6 and the drive cylinders 38. However, various parts such as gears for taking out power from the output side disks 4 and 4 are provided in the position portion between these. Therefore, depending on the conditions, it may not be possible to dispose the cable 40a in the interposition portion, which may make it difficult to specifically design the toroidal type continuously variable transmission.

In order to prevent the cable 40a from interfering with other parts and to enable the arrangement of the cable 40a in the conventional structure, for example, the distance between the trunnions 6 and 6 and the drive cylinders 38 and 38 is increased. However, it is conceivable to increase the degree of freedom in the space in which the cable 40a can be arranged in the axial direction of the drive rods 36, 36 (vertical direction in FIG. 11). However, if such a structure is adopted, the drive cylinders 38, 38 having a large outer diameter size are arranged at positions distant from the input side and output side disks 2, 4, so that the external dimensions of the toroidal type continuously variable transmission are increased. Will become too large to be installed in a limited space such as under the floor of a car. The toroidal type continuously variable transmission of the present invention was invented in view of such circumstances.

[0027]

The toroidal type continuously variable transmission of the present invention is concentric with each other, with their inner side surfaces facing each other, like the above-described conventional toroidal type continuously variable transmission. A pair of first discs that are rotatably supported in synchronization with each other, and are arranged concentrically with the first discs with their inner faces facing the inner faces of these first discs, and are synchronized with each other. A pair of rotating second disks,
A first trunnion that is provided between the first disc and the second disc on one side and that swings about a first pivot that is in a twisted position with respect to the central axes of these two discs, and this first trunnion. The first displacement shaft protruding from the inner side surface, and in a state of being rotatably supported around the first displacement axis, sandwiched between the inner side surfaces of the first disk and the second disk on the one side. A first power roller, a first actuator for displacing the first trunnion in the axial direction of the first pivot, and a first disk and a second disk on the other side. A second trunnion that swings around a second pivot that is twisted with respect to the center axis of the disc, a second displacement shaft that protrudes from the inner surface of this second trunnion, and rotates around this second displacement shaft. With it being freely supported, A second power roller that is sandwiched between the inner surfaces of the first disk and the second disk on the other side, and a second actuator that displaces the second trunnion in the axial direction of the second pivot. And a first engaging portion fixed to the first trunnion and a second engaging portion fixed to the second trunnion, an intermediate portion of which is coupled to swing the first and second trunnions. And a cable that mutually regulates each other.

In particular, in the toroidal type continuously variable transmission of the present invention, the first actuator is provided at the intermediate portion of the first rod whose base end is connected to the first pivot, and the tip end portion of the first rod is provided. The first engaging portion, the second actuator is provided at the intermediate portion of the second rod whose base end is coupled to the second pivot, and the second engaging portion is provided at the distal end of the second rod. Are provided respectively.

[0029]

The toroidal type continuously variable transmission of the present invention configured as described above is rotated between the first disk and the second disk based on the same operation as that of the conventional toroidal type continuously variable transmission described above. By transmitting the force and changing the inclination angle of the trunnion, the rotation speed ratio of these two disks is changed. Further, by tilting the plurality of trunnions in synchronization with the cable, a fatal failure does not occur even when the actuator fails, and a minimum power transmission can be secured.

In particular, in the case of the toroidal type continuously variable transmission of the present invention, a cable for synchronizing the tilting of the trunnions supporting the power rollers in the adjacent cavities from the first and second discs is used. Can be placed far apart in the direction. Therefore, this cable is less likely to interfere with other parts, and the design of the toroidal type continuously variable transmission is facilitated. Since the outer diameters of the first and second engaging portions are smaller than the outer diameters of the first and second actuators, these first and second engaging portions are first and second. Even if the toroidal type continuously variable transmission is arranged at a position away from both disks, it is possible to design the external dimensions of the toroidal type continuously variable transmission without increasing.

[0031]

1 and 2 show a first embodiment of the present invention. A pair of input side disks 2 and 2, each of which is a first disk, are provided on both ends of an input shaft 49 that is rotationally driven by the pressing device 9, with their inner side surfaces 2a and 2a facing each other. They are attached via ball splines 50, 50, respectively. Therefore, these two input side disks 2,
The two rotate concentrically with each other and in synchronization with each other.

A sleeve 51 is rotatably supported around the intermediate portion of the input shaft 49 with respect to the input shaft 49. Then, output-side discs 4 and 4, which are second discs, are supported at both ends in the axial direction (the left-right direction in FIG. 1) of the sleeve 51 via spline engagement portions. Therefore, both the output side disks 4 and 4 are arranged concentrically with the respective input side disks 2 and 2. Further, the both output side disks 4 and 4 rotate in synchronization with each other.
Also, the inner side surfaces 4a, 4a of the output side disks 4, 4 are
Faces the inner side surfaces 2a, 2a of the input side disks 2, 2.

As described above, the trunnions 6 and 6 are respectively provided between the input side disks 2 and 2 and the output side disks 4 and 4 which are provided in two sets each in the axial direction (left and right direction in FIG. 2).
Is provided. These trunnions 6 and 6 swing around pivots 5 and 5 which are twisted with respect to the central axes of the disks 2 and 4, respectively. Further, the power rollers 8, 8 rotatably supported around the displacement shafts 7, 7 protruding from the inner side surfaces of the trunnions 6, 6 are provided with inner side surfaces 2a of the input side disk 2 and the output side disk 4, respectively. It is sandwiched between 4a. Further, one ends (upper ends in FIG. 1) of the drive rods 36, 36 are coupled to the ends of the trunnions 6, 6, and a drive piston fixed to an intermediate portion of the drive rods 36, 36. 37, 37 are oil-tightly fitted in the drive cylinders 38, 38.

The trunnions 6 and 6, the pivot 5,
5, the displacement shafts 7, 7, and the power rollers 8, 8, each member 6, 5, 7, provided between the input side disk 2 and the output side disk 4 on one side (the left side in FIG. 2). Reference numeral 8 corresponds to “first to” described in the claims, and each member 6, 5, 7 provided between the input side disk 2 and the output side disk 4 on the other side (right side in FIG. 2). , 8 correspond to “second to” described in the claims. Further, the drive rod 36 corresponding to the trunnion 6 on the one side is a first rod, and the drive piston 37 fixed to the drive rod 36 and the drive cylinder 38 fitted with the drive piston 37 are the first actuator. , Respectively. Further, the drive rod 36 corresponding to the trunnion 6 on the other side is the second rod, and the drive piston 37 fixed to the drive rod 36.
And the drive cylinder 38 fitted with the drive piston 37 correspond to the second actuator.

Cables 40, 40 are bridged between the trunnions 6, 6 existing in the same cavity by straddling to synchronize the tilting of each of the trunnions 6, 6. That is, as in the case of the above-described conventional structure, these cables 40, 40 are bridged over the arcuate surfaces 39, 39 formed at the ends of the trunnions 6, 6 so that the trunnions 6, 6 are It is designed to tilt in the opposite direction by the same angle.

Further, at the tip end portions of the drive rods 36, 36, the first projecting portions or the second engaging portions are respectively provided at the portions projecting from the fixed plate portion 52 containing the drive cylinders 38, 38 therein. The pulleys 48a, 48a corresponding to the parts are fixed. The cables 40c, 40c are provided between the pulleys 48a, 48a in the adjacent cavities.
Are crossed over with a cross.

The toroidal type continuously variable transmission of the present invention constructed as described above has a pair of input side disks 2 and 2 each based on the same operation as the above-mentioned conventional toroidal type continuously variable transmission. Rotational force is transmitted between the output side disks 4 and 4. Further, the rotation speed ratio between the two disks 2 and 4 is changed by changing the inclination angles of the trunnions 6 and 6 in synchronization. Further, by tilting the trunnions 6 synchronously with the cables 40 and 40c, even when the actuator fails, a fatal failure does not occur and a minimum power transmission can be secured.

Particularly, in the case of the toroidal type continuously variable transmission of the present invention, the power rollers 8 and 8 in the adjacent cavities.
The cables 40c, 40c for synchronizing the tilting movements of the trunnions 6, 6 for supporting the trunnions 6 can be arranged at a great distance in the diametrical direction from the input side and output side disks 2, 4.
Therefore, the cables 40c and 40c are less likely to interfere with other components, and the design of the toroidal type continuously variable transmission is facilitated. That is, the outer diameters of the pulleys 48a and 48a fixed to the end portions of the drive rods 36 and 36 are provided at the intermediate portions of the pulleys 36 and 36 in order to bridge the intermediate portions of the cables 40c and 40c. Drive cylinder 38,
It is smaller than the outer diameter dimension of 38. Therefore, these pulleys 48a, 48a are connected to both the input side and output side discs 2,
Even if the toroidal type continuously variable transmission is arranged at a position away from the No. 4, it is possible to design the external dimensions of the toroidal type continuously variable transmission without increasing.

Next, FIG. 3 shows a second embodiment of the present invention. In the case of the present embodiment, the present invention is applied to a double cavity type toroidal type continuously variable transmission in which three power rollers 8 and 8 are provided in the same cavity. Therefore, in the case of this structure, the power rollers 8 and 8 and the trunnions 6 and 6 are provided in two sets of three and a total of six. Since the feature of the present invention is the structure for synchronizing the tilting of the trunnions 6, 6 in the adjacent cavities, FIG. 3 shows a mechanism for synchronizing the tilting of the trunnions 6, 6 in the same cavity. Omitted.

Of the three trunnions 6, 6 provided in each cavity, a drive piston 37 and a drive cylinder are provided in the middle of a drive rod 36 having the base ends fixed to any one of the trunnions 6, 6. An actuator composed of 38 and 38 is provided. Then, a pulley 48a is fixed to the tip of the drive rod 36, and a cable 40c is spanned between the pulleys 48a by crossing. Therefore, as in the case of the first embodiment described above, it is possible to design the toroidal type continuously variable transmission without enlarging its outer dimensions.

[0041]

Since the toroidal type continuously variable transmission of the present invention is constructed and operates as described above, it is possible to increase the degree of freedom in the position of arranging the cables without increasing the external dimensions, and toroidal type. The design of the continuous variable transmission can be facilitated.

[Brief description of drawings]

FIG. 1 is a partial sectional view showing a first embodiment of the present invention.

FIG. 2 is a sectional view taken along line AA of FIG.

FIG. 3 is a sectional view showing a second embodiment of the present invention.

FIG. 4 is a side view showing a basic configuration of a conventionally known toroidal type continuously variable transmission in a state of maximum deceleration.

FIG. 5 is a side view showing the same state at maximum acceleration.

FIG. 6 is a sectional view showing a first example of a conventional specific structure.

7 is a sectional view taken along line BB of FIG.

FIG. 8 is a cross-sectional view showing a first example of a conventionally known arrangement portion of a cable.

FIG. 9 is a sectional view showing the second example.

FIG. 10 is a sectional view showing the third example.

11 is a cross-sectional view taken along line CC of FIG.

[Explanation of symbols]

 1 Input Shaft 2 Input Side Disk (First Disk) 2a Inner Side Surface 3 Output Shaft 4 Output Side Disk (Second Disk) 4a Inner Side Surface 5 Axis 6 Trunnion 7 Displacement Axis 8 Power Roller 8a Circumferential Surface 9 Pressing Device 10 Cam Plate 11 Cage 12 Rollers 13 and 14 Cam surface 15 Input shaft 16 Needle bearing 17 Collar part 18 Output gear 19 Key 20 Support plate 21 Support shaft part 22 Pivot shaft part 23 Circular hole 24, 25 Radial needle bearing 26 Thrust ball bearing 27 Thrust Needle bearing 28 Cage 29 Ball 30 Outer ring 31 Race 32 Cage 33 Needle 36 Drive rod 37 Drive piston 38 Drive cylinder 39 Arc surface 40, 40a, 40b, 40c Cable 41 Stopper 42 Pulley 43 Large gear 44 Small gear 45 Output shaft 46 Stopper 47 Sliding Plate 48, 48a Li 49 input shaft 50 ball spline 51 sleeve 52 fixed plate portion

Claims (1)

[Claims] 1. In a state in which the inner surfaces of each other are opposed to each other,
A pair of first disks that are concentrically and rotatably supported in synchronization with each other, and are arranged concentrically with the first disks with their inner surfaces facing the inner surfaces of these first disks. , A pair of second discs that rotate in synchronization with each other, and a first pivot shaft that is provided between the first disc and the second disc on one side and that is in a twisted position with respect to the central axes of both discs. A first trunnion that swings as a center, a first displacement shaft that projects from the inner surface of the first trunnion, and a first displacement shaft that is rotatably supported around the first displacement shaft. A first power roller sandwiched between the inner surfaces of the disk and the second disk, a first actuator that displaces the first trunnion in the axial direction of the first pivot, and a first actuator on the other side. One disc and second disc A second trunnion that is provided between the two trunnions and swings about a second pivot that is in a twisted position with respect to the central axes of the two disks, a second displacement shaft that protrudes from the inner surface of the second trunnion, The second power roller sandwiched between the inner surfaces of the first disk and the second disk on the other side and the second trunnion in a state of being rotatably supported around the two displacement shafts. A second actuator that displaces in the axial direction of the second pivot, a first engaging portion fixed to the first trunnion, and a second engaging portion fixed to the second trunnion with an intermediate portion therebetween. In a toroidal type continuously variable transmission equipped with a cable for connecting the first and second trunnions to each other and mutually controlling the swing of the first and second trunnions, a first rod of which the base end is connected to the first pivot is connected. The first actuator in the middle part, The first engaging portion is provided at the tip end portion of the first rod, the second actuator is provided at the intermediate portion of the second rod whose base end is connected to the second pivot, and the tip end portion of the second rod. A toroidal type continuously variable transmission characterized in that each of the second engaging portions is provided in each.