JP2000320634A - Toroidal continuous variable transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress slippage at a traction part by strictly making axial displacement of trunnions agree with each other from an initial state at the time of transmission operation. SOLUTION: Base ends of drive rods 51, 51 are fixed to pivot shafts 29, 29 of trunnions 27, 27, while receiving pieces 72, 72 are formed on the fronts of the drive rods 51, 51. Both ends of an oscillation arm 80 whose center is pivoted to a second pivot shaft 78 are engaged with the receiving pieces 72, 72. With such a setup, the trunnions 27, 27 are displaced by same lengths in opposite directions to each other in axial directions of the pivot shafts 29, 29.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The toroidal-type continuously variable transmission according to the present invention is used, for example, as a transmission unit of a transmission for an automobile or as a transmission for various industrial machines.

[0002]

2. Description of the Related Art The use of a toroidal type continuously variable transmission as schematically shown in FIGS. This toroidal-type continuously variable transmission is disclosed in, for example, Japanese Utility Model Laid-Open No. 62-71465.
An input disk 2 is supported concentrically with the input shaft 1, and an output disk 4 is fixed to an end of an output shaft 3 arranged concentrically with the input shaft 1. Inside the casing 5 (FIGS. 12 to 14 to be described later) containing the toroidal type continuously variable transmission, it swings around the pivots 6, 6 which are twisted with respect to the input shaft 1 and the output shaft 3. Trunnions 7 and 7 are provided.

That is, each of the trunnions 7, 7 has the above-mentioned pivots 6, 6 concentrically provided on the outer surfaces of both ends. Therefore, these pivots 6, 6 do not intersect with the central axes of the discs 2, 4, but are provided at right angles to the direction of the central axes. At the center of these trunnions 7, 7, the base ends of the displacement shafts 8, 8 are supported, and the trunnions 7, 8 around the pivots 6, 6 are centered.
The tilt angle of each of the displacement shafts 8, 8 can be freely adjusted by swinging the shaft 7. Power rollers 9, 9 are rotatably supported around displacement shafts 8, 8 supported by the trunnions 7, 7, respectively. These power rollers 9, 9 are sandwiched between the input side and output side disks 2, 4. The inner surfaces 2a and 4a of the input and output disks 2 and 4 facing each other have a cross section obtained by rotating an arc centered on the pivot 6 about the input shaft 1 and the output shaft 3. It has a concave surface. Then, the peripheral surfaces 9a, 9a of the power rollers 9, 9, which are formed as spherical convex surfaces, are brought into contact with the inner side surfaces 2a, 4a.

[0004] A loading device 10 of a loading cam type is provided between the input shaft 1 and the input disk 2, and the input disk 2 is directed toward the output disk 4 by the pressing device 10 so as to be elastic. It can be pressed freely. The pressing device 10 includes a cam plate 11 that rotates together with the input shaft 1,
It is composed of a plurality of (for example, four) rollers 13, 13 held by a holder 12. On one side surface (the left side surface in FIGS. 10 to 11) of the cam plate 11, a cam surface 14 which is an uneven surface extending in the circumferential direction is formed.
A similar cam surface 15 is also formed on the outer side surface (the right side surface in FIGS. 10 to 11). And the plurality of rollers 1
3 and 13 are supported rotatably about an axis in a radial direction with respect to the center of the input shaft 1.

When the cam plate 11 rotates with the rotation of the input shaft 1 during use of the toroidal type continuously variable transmission configured as described above, a plurality of rollers 13
Is pressed against a cam surface 15 formed on the outer surface of the input side disk 2. As a result, at the same time that the input side disk 2 is pressed by the power rollers 9, 9, based on the pressing of the pair of cam surfaces 14, 15 and the rollers 13, 13, The input side disk 2 rotates. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 via the plurality of power rollers 9, 9, and the output shaft 3 fixed to the output side disk 4 rotates.

In the case where the rotational speed ratio (speed change ratio) between the input shaft 1 and the output shaft 3 is changed, and when the deceleration is first performed between the input shaft 1 and the output shaft 3, each of the pivots 6 The respective trunnions 7, 7 are swung in a predetermined direction as a center, and the peripheral surfaces 9a, 9a of the respective power rollers 9, 9 are shifted toward the center of the inner surface 2a of the input side disk 2 as shown in FIG. The displacement shafts 8 are inclined so as to abut against the outer peripheral portion of the inner surface 4a of the output side disk 4, respectively. Conversely, when increasing the speed, the trunnions 7, 7 are swung in opposite directions about the respective pivots 6, 6,
As shown in FIG. 11, the peripheral surfaces 9a, 9a of the power rollers 9, 9 are respectively disposed on the inner surface 2a of the input disk 2 near the outer periphery and the inner surface 4a of the output disk 4 near the center. The displacement shafts 8, 8 are tilted so as to be in contact with each other. If the inclination angle of each of the displacement shafts 8, 8 is set between those in FIGS. 10 and 11, an intermediate speed ratio can be obtained between the input shaft 1 and the output shaft 3.

When an actual automobile transmission is constituted by the toroidal-type continuously variable transmission as described above, the input disk 2, the output disk 4, and the power rollers 9, 9 are connected to each other.
A so-called double-cavity toroidal-type continuously variable transmission in which two sets of the input-side disc 2, the output-side disc 4, and the power rollers 9, 9 are arranged in parallel to each other in the power transmission direction is also provided. Has been widely known.
FIGS. 12 to 14 show a type of such a double-cavity toroidal-type continuously variable transmission which is described in Japanese Patent Publication No. 8-23386 and is conventionally known.

An input shaft 1a is supported inside the casing 5 so as to be rotatable only. A circular transmission shaft 16 is supported around the input shaft 1a concentrically with the input shaft 1a and freely rotates relative to the input shaft 1a. In the portion of the transmission shaft 16 near both ends of the intermediate portion,
The first and second input disks 17 and 18 corresponding to the first and second outer disks described in the claims are respectively ball splines 19 and 19 with the inner surfaces 2a and 2a facing each other. Support through. Therefore, the first and second input side disks 17 and 18 are rotatably supported inside the casing 5 concentrically and synchronously with each other.

Around the intermediate portion of the transmission shaft 16,
The first and second output disks 20 and 21 corresponding to the first and second inner disks described in the claims are connected to a sleeve 22.
Support through. The sleeve 22 has an output gear 23 integrally provided on the outer peripheral surface of the intermediate portion, has an inner diameter larger than the outer diameter of the transmission shaft 16, and has a casing 5.
A pair of rolling bearings 25, 25 is provided on a support wall 24 provided therein.
Thus, the transmission shaft 16 is supported concentrically with the transmission shaft 16 so as to be rotatable only. The first and second output side disks 20,
Reference numeral 21 denotes a state in which the respective inner side surfaces 4a and 4a are opposed to each other around the intermediate portion of the transmission shaft 16 and at both ends of the sleeve 22 rotatably supported with respect to the transmission shaft 16. The spline is engaged. Therefore, the first and second output side disks 20 and 21 have their inner surfaces 4a and 4a opposed to the inner surfaces 2a and 2a of the first and second input side disks 17 and 18, respectively. In this state, the first and second input disks 17 and 18 are concentric with the first and second input disks 17 and 18.
It is supported rotatably independent of.

Further, the first,
At the side positions of the second output disks 20 and 21, the output disks 20 and 21 are sandwiched from both sides.
The pair of yokes 26a and 26b are supported. Each of the yokes 26a and 26b is formed in a rectangular frame by pressing a metal plate such as steel or by forging a metal material such as steel. These yokes 26a and 26b swingably support first and second pivots 29 and 30 provided at both ends of first and second trunnions 27 and 28 described later at the four corners, respectively. The circular support holes 31, 31 are provided at the center portions in the width direction (left and right directions in FIGS. 13 and 14) of both ends of the transmission shaft 16 in the axial direction (left and right directions in FIG. 12). Are formed respectively. The above 1 each having such a shape
The pair of yokes 26a, 26b are formed on support posts 33a, 3
3b, it is supported to be slightly displaceable. These support posts 33a and 33b are respectively connected to the inner surface 2a of the first input disk 17 and the inner surface 4 of the first output disk 20.
a, and a second cavity 35 between the inner side surface 2a of the second input side disk 18 and the inner side surface 4a of the second output side disk 21, respectively. Provided. Therefore, in a state where the yokes 26a, 26b are supported by the support posts 33a, 33b, one end of each of the yokes 26a, 26b is on the outer peripheral portion of the first cavity 34, and the other end is on the second cavity. The outer peripheral portion 35 is opposed to each other.

A pair of first trunnions 27, 27 are provided in the first cavity 34 at diametrically opposite positions of the first input side disk 17 and the first output side disk 20 in the second cavity 35. A pair of second trunnions 28, 28 are arranged at diametrically opposite positions of the second input side disk 18 and the second output side disk 21, respectively. The first trunnions 27 are provided concentrically at both ends of the first trunnions 27.
As shown in FIG. 13, a total of four first pivots 29, 29 are attached to one end of the pair of yokes 26a, 26b, respectively.
It is supported so that it can swing and displace in the axial direction. That is, the first pivots 29, 29 are provided inside the support holes 31, 31 formed at one end of each of the yokes 26a, 26b.
Are supported by radial needle bearings 36, 36. Each of these radial needle bearings 36 includes an outer ring 37 whose outer peripheral surface is a spherical convex surface and whose inner peripheral surface is a cylindrical surface, and a plurality of needles 38, 38. Therefore, the first pivots 29, 29 are connected to the yokes 26a, 2
6b is supported at both ends in the width direction at one end thereof so as to be swingable in each direction and displaceable in the axial direction. Also, a pair of second pivots 30, 30 provided concentrically at both ends of each of the second trunnions 28, 28 are housed in the second cavity 35 as shown in FIG. , 27
Are supported by the same structure as each of the first pivots 29, 29 provided above.

As described above, the first and second trunnions 27 are supported inside the casing 5 so as to be able to swing and displace in the axial direction of the first and second pivots 29 and 30. As shown in FIGS. 13 and 14, circular holes 39, 39 are formed in the intermediate portion 28, respectively. The first and second displacement shafts 40, 4 are respectively formed in these circular holes 39, 39.
Supports 1. These first and second displacement axes 40, 4
1 is a support shaft 4 which is parallel and eccentric to each other
2 and 42 and pivot shafts 43 and 43, respectively.
Each of the support shaft portions 42, 42 is inserted into each of the circular holes 39, 3
9 is rotatably supported through radial needle bearings 44, 44. Also, each of the pivot shaft portions 4
First and second power rollers 45, 46 around
Are rotatably supported via other radial needle bearings 47, 47.

The first and second cavities 34, 3
The first and second displacement shafts 40 provided one by one for every 5
41 is, for each of the first and second cavities 34, 35,
It is provided at a position opposite to the input shaft 1a and the transmission shaft 16 by 180 degrees. In addition, these first and second displacement axes 4
Each of the pivot shaft portions 43, 43 of the support shaft portions 0, 41
The directions eccentric to 2 are the first and second input sides,
The rotation direction of each of the output-side disks 17, 18, 20, 21 is the same direction (upside-down direction in FIGS. 13 and 14). The eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 1a is provided. Accordingly, the first and second power rollers 45 and 46 are supported so as to be slightly displaceable in the direction in which the input shaft 1a and the transmission shaft 16 are arranged. As a result, the first and second power rollers 45 and 45 are caused by a change in the amount of elastic deformation of each component based on a change in torque transmitted by the toroidal-type continuously variable transmission.
Reference numeral 46 denotes the axial direction of the input shaft 1a and the transmission shaft 16 (FIG. 12).
(In the left-right direction of FIG. 13 and the front-back direction in FIGS. 13 and 14), this displacement can be absorbed without applying excessive force to the constituent members.

Each of the first and second power rollers 4
5, 46 and the first and second trunnions 27,
28, a thrust ball bearing 48, 48 and a thrust bearing 49 such as a slide bearing or a needle bearing, in order from the outer surface side of the first and second power rollers 45, 46. 49 are provided. Of these, the thrust ball bearings 48 are provided with the first and second power rollers 4 respectively.
The first and second power rollers 45 and 46 are allowed to rotate while supporting the thrust load applied to the first and second power rollers 5 and 46. Further, the thrust bearings 49, 49 support the thrust load applied to the outer races 50, 50 of the thrust ball bearings 48, 48 from the first and second power rollers 45, 46, respectively, while supporting the pivot shaft. The parts 43, 43 and the outer races 50, 50 are allowed to swing about the support shaft parts 42, 42.

Further, the first and second trunnions 27,
Drive rods 51, 51 are respectively connected to one end of the drive rod 28 (the lower end in FIGS. 13 and 14).
Driving pistons 52, 52 are fixedly provided on the outer peripheral surface of the intermediate portion of the first and the 51. Each of these drive pistons 52, 52
Are oil-tightly fitted in the drive cylinders 53, 53, respectively. These drive pistons 52, 52 and drive cylinders 53, 53 displace the first and second trunnions 27, 28 in the axial direction of the first and second pivots 29, 30, respectively. Configure the actuator. or,
Pressure oil can be freely supplied and discharged into and from each of the drive cylinders 53 based on switching of a control valve (not shown).

Further, a loading device 10 of the loading cam type is provided between the input shaft 1a and the first input side disk 17. The pressing device 10 includes the input shaft 1
The cam plate 11 is spline-engaged with an intermediate portion of the shaft a and is supported in a state where displacement in the axial direction is prevented, and rotates with the input shaft 1a. And a roller 13. Then, based on the rotation of the input shaft 1a, the first input side disk 17 is rotated while being pressed against the second input side disk 18.

During operation of the toroidal type continuously variable transmission of the double cavity type configured as described above, the rotation of the input shaft 1a is transmitted to the first input side disk 17 via the pressing device 10, and this first input The side disk 17 and the second input side disk 18 rotate in synchronization with each other. The rotation of the first and second input-side disks 17 and 18 causes the first and second power rollers 45 and 46 provided in the first and second cavities 34 and 35 respectively to form a pair. Via the first and second output side disks 20 and 21 via the first and second output side disks 20 and 21.
Is taken out of the output gear 23. When the rotational speed ratio between the input shaft 1a and the output gear 23 is changed, one pair is provided for each of the first and second cavities 34 and 35 based on the switching of the control valve. The driving pistons 52, 52 are connected to the respective cavities 34, 3
Every five steps are displaced in the opposite direction by the same distance.

With the displacement of the drive pistons 52, 52, a total of four trunnions 27, 28 are paired.
Are displaced in opposite directions, for example, the first and second power rollers 45 and 46 on the right side of FIGS. Roller 4
5, 46 are respectively displaced to the upper side of each figure. As a result, the peripheral surfaces 9a, 9a of the first and second power rollers 45, 46 and the first and second input side disks 17,
18 and the direction of the tangential force acting on the contact portions of the first and second output side disks 20, 21 with the inner side surfaces 2a, 4a are changed. The first and second trunnions 27 and 28 are moved by the yoke 26 with the change in the direction of the force.
The first and second pivots 29 and 30 pivotally supported by a and 26b swing in opposite directions. As a result, as shown in FIGS. 10 to 11, the peripheral surfaces 9a, 9a of the first and second power rollers 45, 46 and the disks 1
The contact position between the inner shafts 2a, 4a of the 7, 18, 20, 21 changes, and the rotation speed ratio between the input shaft 1a and the output gear 23 changes.

In the toroidal type continuously variable transmission as described above,
The drive rods 51, 51, drive pistons 52, 52,
When the hydraulic drive device including the drive cylinders 53, 53 and the like fails, the first and second trunnions 27,
A mechanism for synchronizing the rocking motions of each other is incorporated. Even when the hydraulic drive device fails, excessive frictional force acts between the inner surfaces 2a, 4a of the disks 17, 18, 20, 21 and the peripheral surfaces 9a, 9a of the power rollers 45, 46. To prevent catastrophic damage to the toroidal-type continuously variable transmission, and to ensure minimum power transmission.

Conventionally, such a mechanism is disclosed in
-67458, JP-A-4-327051,
Japanese Unexamined Utility Model Publication No. 62-200852 and the like are known. FIGS. 15 and 16 show Japanese Unexamined Patent Publication No.
2 shows two examples of the structure described in Japanese Patent No. 327051. 15 and 16, a mechanism for synchronizing the swinging of the first and second trunnions 27 and 28 in the double-cavity toroidal type continuously variable transmission will be described.

In order to constitute a synchronization mechanism, the axial direction of the first and second trunnions 27 and 28 (the front and back directions in FIGS. 15 and 16).
Pulleys 54, 54 are fixed to the ends. The outer peripheral surface of each of these pulleys 54, 54 is
14) and a concentric arc surface. Then, a part of the cable 55, 55a, 55b is bridged so as to be fitted in a concave groove formed on the outer peripheral surface of each of the pulleys 54, 54. The two trunnions 27 and 28 are rocked synchronously. That is, in any structure, a pair of first,
The cables 55, 55 are connected between a pair of pulleys 54, 54 fixed to the ends of the second trunnions 27, 28,
It is crossed over. Therefore, each pair of first and second trunnions 27 and 28 (each existing in the same cavity) constituting each set are rotatable in the opposite direction by the same angle and exist at diagonal positions (different positions). Pulley 5 which is located in the cavity on the opposite side of the input shaft 1a in the circumferential direction)
4, 54 are rotatable in the same direction by the same angle.

For this reason, in the structure of the first example shown in FIG. 15, the cable 55a is passed only between the pulleys 54, 54 located at the diagonal positions, and the stoppers 56, 5
6, the cable 55a is connected to the pulleys 54, 54 located at the diagonal positions. On the other hand, FIG.
In the structure of the second example shown in FIG. 6, instead of extending the cable 55b over all the pulleys 54, 54, the stoppers 56, 5
6, the cable 55b is connected. A sliding plate 5 is provided between the remaining pulleys 54, 54 and the cable 55b.
The movement of the cable 55b is prevented from being transmitted to the remaining pulleys 54, 54 by interposing the cables 7, 57.
The structure shown in FIG. 16 is such that the cable 55b includes the first and second output side disks 20, 21 and the large-diameter output gear 23.
It is adopted to prevent interference with other members constituting the toroidal type continuously variable transmission. Incidentally, also in the case of a so-called single cavity type toroidal type continuously variable transmission in which one input side disk and one output side disk are provided, by providing the cross cable 55 shown in FIGS. The swing of the plurality of trunnions is synchronized. Also, although not shown in the drawings, the actual fairness 4-5251
No. 2, JP-A-6-117515, JP-A-7-24
Japanese Patent No. 3496 describes a technique in which a mechanism for synchronizing the inclination angles of a plurality of trunnions is constituted by a gear transmission mechanism.

[0023]

All of the conventional synchronous mechanisms take into account the fact that the inclination angles of the trunnions 7, 27, 28 resulting from the axial displacement of the drive rods 51, 51 coincide with one another. However, the axial displacements of the drive rods 51 are not synchronized. Further, the synchronization mechanism itself is only an emergency one, and the inclination angles of the trunnions 7, 27, 28 are strictly matched on the basis of the elongation of the cables 55, 55a, 55b and the existence of gear backlash. Was not something that could be done. Synchronizing the axial displacement of the drive rods 51, 51 is performed by the drive cylinders 53, 53.
This is done by controlling the hydraulic pressure introduced into the inside. Therefore, in the transition period immediately after the start of the shifting operation, the inclination angles of the trunnions 7, 27, 28 are slightly different, and the peripheral surfaces 9a, 9a of the power rollers 9, 45, 46 and the disks 2, 4, There is a possibility that slippage may occur in the abutment portions of the 17, 17, 20, 21 with the inner side surfaces 2a, 4a.

The slip generated at the abutting portion between the surfaces due to the above-mentioned causes causes the trunnions 7, 27, and 28 to move faster in the axial direction of the pivots 6, 29, and 30 in order to perform a quick shift operation. When moved, it tends to be significant. When the slippage occurs, not only is the power transmission efficiency deteriorated, but also the rolling fatigue life of each surface is reduced, which is not preferable. Therefore, in order to perform a quick shift operation while preventing the transmission efficiency from being deteriorated and the rolling fatigue life from being shortened, a structure in which the axial displacements of the drive rods 51 and 51 are strictly synchronized is realized. There is a need to. The toroidal type continuously variable transmission of the present invention has been invented in view of the above-described circumstances.

[0025]

Means for Solving the Problems Among the toroidal type continuously variable transmissions of the present invention, the toroidal type continuously variable transmission according to the first aspect is the same as the conventionally known toroidal type continuously variable transmission. A casing, an input-side disc and an output-side disc concentrically and independently rotatably supported in a state in which the inner surfaces face each other inside the casing; and the input-side disc and the output-side disc. In the portion between the discs and the disc, the disc does not intersect with the center axis of each disc, but exists at a twisted position perpendicular to the direction of the center axis.
An even number of pivots, a plurality of trunnions swinging about these pivots, displacement axes protruding from the inner surface of each trunnion, and a state supported rotatably around these displacement axes The same number of power rollers as the respective trunnions sandwiched between the inner surface of the input side disk and the inner side surface of the output side disk, and these trunnions are displaced in the axial direction of the pivots. And the same number of actuators as the trunnions.

The toroidal-type continuously variable transmission according to the second aspect of the invention has a casing and an inner side of the casing inside each other, similarly to a conventionally known double-cavity toroidal-type continuously variable transmission. The first and second outer disks, which are rotatably supported concentrically and synchronously with each other in a state where the side surfaces are opposed to each other, and these first and second outer disks are arranged such that their inner surfaces face the inner surface of the first outer disk. A first inner disk supported concentrically with the second and outer disks and independently rotatable independently of the first and second outer disks, and an inner surface thereof is opposed to an inner surface of the second outer disk. In the state, the second inner disk concentrically with the first inner disk, and rotatably supported in synchronization with the first inner disk, and a portion between the first outer disk and the first inner disk, These discs do not intersect with the center axis of each disk, but are present at four or more concentric or parallel and even-numbered first pivots existing at a twist position perpendicular to the direction of the center axis. A plurality of first trunnions swinging about each of the first pivots, a first displacement axis protruding from an inner surface of each of the first trunnions, and rotatably supported around each of the first displacement axes. A plurality of first power rollers sandwiched between the inner surface of the first outer disk and the inner surface of the first inner disk, and a portion between the second outer disk and the second inner disk. Although it does not intersect with the center axis of each of these discs, four or more concentric or parallel and even-numbered second pivots are present at twisted positions that are perpendicular to the direction of the center axis. And around each of these second axes A plurality of second trunnions that swing and swing, a second displacement shaft protruding from the inner surface of each of the second trunnions, and the second outer shaft in a state rotatably supported around each of the second displacement shafts. A plurality of second power rollers sandwiched between the inner surface of the disk and the inner surface of the second inner disk; and the same number of trunnions as displacing the respective trunnions in the axial direction of the respective pivots. Actuator.

In particular, the toroidal type continuously variable transmission of the present invention is provided with a synchronization mechanism for mechanically synchronizing the displacement of the trunnions in the axial direction of the pivots by the actuators. As such a synchronizing mechanism, for example, a driving rod for connecting and fixing a base end to each end of each trunnion and displacing each trunnion axially by an actuator to displace each trunnion in the axial direction of the pivot axis. The receiving piece fixed to the tip of the disk and the end of the receiving piece are freely engaged with these receiving pieces only for swinging displacement, and the central part is provided in the fixed part in parallel with the rotation center of each disk. And a swing arm pivotally supported on the second pivot.

[0028]

The toroidal-type continuously variable transmission of the present invention configured as described above has a function similar to that of the above-mentioned conventional toroidal-type continuously variable transmission, and is provided between the input side disk and the output side disk, or Rotational force is transmitted between the first and second outer disks and the first and second inner disks, and the rotation speed ratio of these two disks is changed by changing the inclination angle of the trunnion. In particular, in the case of the toroidal-type continuously variable transmission of the present invention, since the displacement of each trunnion in the axial direction of each pivot axis by each actuator is mechanically synchronized, even when a quick shifting operation is performed, The inclination angle of the trunnion can be exactly matched.

[0029]

1 to 6 show an example of an embodiment of the present invention corresponding to claims 2 and 3. FIG. It should be noted that the features of the structure of the present example are a structure for surely synchronizing the inclination angles of the first trunnions 27 and 27 and the second trunnions 28 and 28 (see FIG. 14), and the first trunnions 27 and 27, The first pivots 29, 29 provided at both ends of the second trunnion 28, and the second pivots 30, 30 (see FIG. 14) provided at both ends of the second trunnions 28, 28 are configured to support the casing 5. is there. Since the structure and operation of the other parts are the same as those of the conventional structure shown in FIGS. 12 to 14, the illustration and description of the equivalent parts are omitted or simplified, and the following description will focus on the characteristic parts of this example. .

A pair of yokes 58 and 59 are directly connected to and fixed to the casing 5 in parallel with each other at portions facing each other in the casing 5. Circular support holes 31, 31 are formed at positions where the yokes 58, 59 are aligned with each other at the four corners. And
The first pivots 2 are provided inside the support holes 31.
9 and 29 are supported by ball splines 60 and 60 and radial needle bearings 61 and 61, respectively, so as to be displaceable and swingable in the axial direction.

Of these, the ball spline outer races 62, which constitute the ball splines 60, 60, are fitted and supported inside the support holes 31, 31 while limiting the displacement in the axial direction. . A plurality of outer ring side ball spline grooves 63 are formed on the inner peripheral surface of each of the outer races 62 for ball splines in the axial direction (vertical direction in FIGS. 1 and 2). On the inner diameter side of each of the outer races 62, 62 for ball splines, inner races 64, 64 for ball splines, which are also outer races of the radial needle bearings 61, 61, are concentric with the respective radial needle bearings 61, 61. Has been placed. On the outer peripheral surface of each of the ball spline inner rings 64, 64, the inner ring-side ball spline grooves 65, 65 are respectively provided at portions facing the outer ring-side ball spline grooves 63, 63.
Each is formed in the axial direction. A plurality of balls 66, 66 are arranged between the inner ring-side ball spline grooves 65, 65 and the outer ring-side ball spline grooves 63, 63, respectively. Make up. The ball spline outer ring 62 is prevented from rattling by an elastic material such as a disc spring 90.

Also, the inner race 64 for each ball spline described above,
64, the radial needle bearings 61,
A cylindrical outer raceway 67 for 67 is provided. Then, these outer raceways 67, 67 and the first pivots 2 provided at both ends of the first trunnions 27, 27 are provided.
A cylindrical inner raceway 68 formed on the outer peripheral surface of each of 9 and 29;
68, a plurality of needles 69, 6
9 and the radial needle bearings 61, 61
Is composed.

Further, among the first pivots 29, 29 provided at both ends of the first trunnions 27, 27, the respective drive shafts have their base ends (upper end in FIG. 1) connected and fixed to one end. The rods 51, 51 pass through through holes 71, 71 formed in a valve body 70 fixed in the casing 5. Then, a receiving piece 72 as shown in FIG. 72 are fixedly connected. Each of these receiving pieces 72,
72 is a pair of annular portions 73a, 7
The circumferential portions of the peripheral portions 3b are connected to each other by a partially cylindrical connecting portion 74.
The portion deviating from 4 is an opening 75. Further, one of the above-mentioned circular ring portions 73a and 73b (upper portion of FIGS. 1 and 3).
The inner diameter of the circular ring portion 73a is relatively small so that only the male screw portion formed at the end of the drive rod 51 can be inserted. On the other hand, the inner diameter of the other annular part 73b (the lower part in FIGS. 1 and 3) is made relatively large, and a nut 76 screwed to the male screw part and a tool for tightening the nut 76 can be inserted. And

The second pivots 7 are attached to mounting substrates 77, 77 fixed to the outer surface of the valve body 70, respectively.
A pivot bracket 79, 79 having 8, 78 is provided. These second pivots 78, 78 are parallel to the rotation centers of the first and second input disks 17, 17 and the first and second output disks 20, 21 (see FIG. 12), and , The second cavities 34 and 35 (see FIG. 12). The second pivots 78, 78 are arranged in a substantially rectangular frame shape as shown in FIG. 4 in the length direction (vertical direction in FIG. 4) of the swing arm 80. 4 in the left-right direction) and pivotally pivotally support the central portion. Therefore, both ends in the width direction of the swing arm 80 are displaced by the same distance in the directions opposite to each other with respect to the axial direction of the drive rods 51, 51.

Then, both ends in the length direction of the swing arm 80 in the width direction are connected to the receiving pieces 72, 72.
The opening 75 between the pair of ring portions 73a, 73b is engaged without play irrespective of the swing displacement about the second pivots 78, 78. For this reason, in the case of the present example, small projections 81, 81 are respectively provided on both sides of the both ends in the width direction of the swing arm 80 in the lengthwise direction opposite ends to the respective annular portions 73a, 73b. Are formed, and the tips of the small projections 81, 81 are brought into contact with the surfaces of the annular portions 73a, 73b facing each other. Accordingly, the first and second pivots of the first and second trunnions 27 and 28 fixedly connected to the receiving pieces 72 and 72 via the receiving pieces 72 and 72 and the driving rods 51 and 51, respectively. The displacements in the axial direction of 29, 30 are tightly mechanically synchronized. Note that feedback control is performed by fixing a precess cam to any trunnion or a drive rod coupled and fixed to any trunnion, and moving a control valve for supplying and discharging pressurized oil to and from the drive cylinders 53 and 53 by this precess cam. I do it.

Further, in this embodiment, the first and second trunnions 27 and 28 are connected to each other by a gear transmission mechanism 82. In order to provide the gear transmission mechanism 82, a concave portion 84 is provided in one yoke 59 (the lower part in FIG. 1). Therefore, in a state where the yoke 59 and the cylinder case 85 are overlapped, a space 89 for accommodating the gear transmission mechanism 82 is formed between the two members 59 and 85. The gear transmission mechanism 82 accommodated in the space 89 includes a pair of pinions 83, 83 having the same shape and the same number of teeth, and four racks 87a having teeth at both ends formed with the same pitch. 87b. Each of the pinions 83, 83 is externally fitted to a non-cylindrical portion formed at the end of the first and second pivots 29, 30 provided at the end of the first and second trunnions 27, 28, respectively. It is fixed. Therefore, the first and second trunnions 27, 2
8 rotates in synchronization with each of the pinions 83,83.
When changing the gear ratio, the first and second trunnions 2 are used.
7, 28 are the first and second pivots 29, 30, respectively.
Displace in the axial direction of. Therefore, each of the pinions 83, 8
The meshing portion between the rack 3 and the racks 87a and 87b has an appropriate degree (a degree that does not cause a problem when the inclination angles are matched).
A backlash is provided to enable relative displacement between the pinions 83, 83 and the racks 87a, 87b.

The racks 87a and 87b allow only the displacement in the axial direction of the input shaft 1a (the front-back direction or the left-right direction in FIG. 1, the left-right direction or the up-down direction in FIG. 6) to allow free space 89. Support within. For this reason, in the example shown,
The racks 87a, 87b are supported on the yoke 59 by a pair of linearly-acting rolling bearings (linear bearings) 88, 88 so as to be movable in parallel.
Therefore, the racks 87a and 87b can be smoothly displaced by a light force without tilting. When a force in a direction perpendicular to the direction of displacement is applied to the racks 87a, 87b, one of the pair of rolling bearings 88, 88 attached to the racks 87a, 87b. Supports the above-mentioned force, and the racks 87a, 87
Compensate for the smooth displacement of b.

Each of the pinions 8 supported as described above
3, 83 and the racks 87a, 87b are formed by teeth formed on the outer peripheral edge of each of the pinions 83, 83 and the racks 87a, 8b.
The gear transmission mechanism 82 is formed by combining the teeth formed on both side edges of the gear 7b with each other in a state of being meshed with each other. The gear transmission mechanism 82 suppresses backlash as much as possible and increases the pitch circle diameter of each of the pinions 83, 83 to some extent (within a range where interference with other members can be prevented). Therefore, each of these pinions 83, 8
The inclination angles of the first and second trunnions 27 and 28 to which the fixing member 3 is fixed and the first and second power rollers 45 and 46 supported by the first and second trunnions 27 and 28 can be made to coincide with each other. .

As described above, in the case of the toroidal type continuously variable transmission of the present invention, the first and second trunnions 2 are used.
The displacement of the first and second pivots 29 and 30 in the axial direction of the first and second pivots 28 and 28 is mechanically and strictly synchronized by the swing arm 80. Therefore, the amount of displacement of the first and second trunnions 27 and 28 is quickly and strictly matched during the shifting operation, and the first and second input side disks 1 are shifted during the shifting operation.
7, 18 and the inner surfaces 2a, 4a of the first and second output side disks 20, 21 (see FIG. 12) and the peripheral surfaces 9a, 9a of the first and second power rollers 45, 46 (FIGS. 1, 13). , 14
) Can be suppressed.

This point will be described with reference to FIGS. 8 and 9 showing the results of an experiment conducted to confirm the effects of the present invention. The experiment was performed using a double-cavity toroidal type continuously variable transmission having a pair of power rollers for each cavity as shown in FIG. In the experiment, the front right side (FR) close to the pressing device 10 and the left side (F
L), on each of the four trunnions 27 and 28 supporting a total of four power rollers 45 and 46 on the rear right side (RR) and also on the left side (RL) far from the pressing device. The axial displacement and swing angle of each of the trunnions 27 and 28 after the introduction of a predetermined pressure oil into the drive cylinder were measured together with the elapsed time. FIG. 8 shows a case of the toroidal type continuously variable transmission of the present invention,
(A) shows the axial displacement of each trunnion, and (B) shows the swing angle. FIG. 9 shows a case where the displacement of the trunnion is adjusted only by adjusting the hydraulic pressure. FIG. 9A shows the axial displacement of each trunnion, and FIG. 9B shows the swing angle. As is clear from FIGS. 8 and 9 showing the results of such an experiment, according to the present invention, it is possible to reliably synchronize the displacements of the trunnions even if a quick shift operation is performed.

Further, in the case of the toroidal type continuously variable transmission of this embodiment, the yokes 58 and 59, which are members constituting the first and second support means, are directly supported and fixed to the inner surface of the casing 5. are doing. Therefore, the support posts 33a and 33b required in the above-described conventional structure (FIGS. 13 and 14).
This makes it possible to simplify the production of parts, the management of parts, and the assembling work by reducing the number of parts, and at the same time, it is possible to reduce the height dimension, secure durability, and reduce the size and weight.

Each of the first pivots 29, 29 and the yoke 5
8 and 59, the ball spline 60 and the radial needle bearing 61 are provided.
8, 59, the first and second trunnions 27, 2
8 can be performed smoothly and accurately. That is, as is apparent from the above description, the first and second trunnions 27 and 28 are displaced in the axial direction of the first and second pivots 29 and 30 during the shifting operation of the toroidal-type continuously variable transmission. Then, based on the axial displacement, the first and second pivots 29, 3
Oscillating displacement occurs around 0. In the case of this example, the axial displacement of these displacements is smoothly performed by the ball spline 60 and the oscillating displacement by the radial needle bearing 61, and the toroidal stepless step is performed based on these displacements. The speed change operation of the transmission can be performed quickly and accurately.

Further, as shown in the illustrated example, the gear transmission mechanism 82
Is provided, the inclination angles of the first and second power rollers 45, 45 can be matched with each other even when the hydraulic pressure supply circuit to the drive cylinders 52, 52 described above breaks down. Therefore, even in the event of a failure, the peripheral surfaces 9a, 9a of the first and second power rollers 45, 45 and the disks 17, 1
It is possible to prevent the occurrence of significant slippage at the contact portions between the inner surfaces 2a, 4a of the 8, 20, 21 and prevent the toroidal type continuously variable transmission from being damaged. When the present invention is carried out, the mechanism for matching the inclination angles of the trunnions is not limited to the gear transmission mechanism 82, but may be any of the above-described FIGS.
As shown in FIG. 6, a cable may be used.

[0044]

The present invention is constructed and operated as described above, so that it is possible to perform a quick shift operation while ensuring durability, and to provide a high-performance vehicle mainly for sports cars. Can contribute to the practical use of toroidal-type continuously variable transmissions, for example, by expanding the possibility of mounting the same.

[Brief description of the drawings]

FIG. 1A illustrates one example of an embodiment of the present invention.
FIG.

FIG. 2 is an enlarged view of a portion B in FIG.

FIG. 3 is a perspective view of a receiving piece.

FIG. 4 is a view from below of FIG. 1 showing a mechanism for synchronizing the axial displacement of the drive rod.

FIG. 5 is a view taken in the direction of arrow C in FIG. 1;

FIG. 6 is a view of the gear transmission mechanism taken out from below in FIG. 1;

FIG. 7 is a schematic plan view of a toroidal-type continuously variable transmission for explaining measurement sites in an experiment performed to confirm the effects of the present invention.

FIG. 8 is a diagram showing a displacement state of each trunnion constituting the toroidal type continuously variable transmission according to the present invention.

FIG. 9 is a diagram showing a displacement state of each trunnion constituting the conventional toroidal type continuously variable transmission.

FIG. 10 is a side view showing a basic configuration of a conventionally known toroidal-type continuously variable transmission in a state of maximum deceleration.

FIG. 11 is a side view showing a state at the time of maximum speed increase.

FIG. 12 is a sectional view showing an example of a conventional specific structure.

FIG. 13 is a sectional view taken along line AA of FIG. 11;

FIG. 14 is a sectional view taken along the line DD in FIG.

FIG. 15 is a cross-sectional view showing a first example of a conventionally known mechanism that matches the inclination angle of a trunnion with a cable.

FIG. 16 is a sectional view showing the second example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1, 1a Input shaft 2 Input side disk 2a Inner surface 3 Output shaft 4 Output side disk 4a Inner surface 5 Casing 6 Pivot 7 Trunnion 8 Displacement shaft 9 Power roller 9a Peripheral surface 10 Pressing device 11 Cam plate 12 Cage 13 Roller 14 Cam Surface 15 Cam surface 16 Transmission shaft 17 First input side disk 18 Second input side disk 19 Ball spline 20 First output side disk 21 Second output side disk 22 Sleeve 23 Output gear 24 Support wall 25 Rolling bearing 26a, 26b Yoke 27 First trunnion 28 Second trunnion 29 First pivot 30 Second pivot 31 Support hole 32 Locking hole 33a, 33b Support post 34 First cavity 35 Second cavity 36 Radial needle bearing 37 Outer ring 38 Needle 39 Circular hole 40 First displacement Axis 41 Second displacement axis 42 Shaft portion 43 pivot shaft portion 44 radial needle bearing 45 first power roller 46 second power roller 47 radial needle bearing 48 thrust ball bearing 49 thrust bearing 50 outer ring 51 drive rod 52 drive piston 53 drive cylinder 54 pulley 55, 55a, 55b Cable 56 Stopper 57 Slip plate 58 Yoke 59 Yoke 60 Ball spline 61 Radial needle bearing 62 Outer ring for ball spline 63 Outer ring side ball spline groove 64 Inner ring for ball spline 65 Inner ring side ball spline groove 66 Ball 67 Outer ring raceway 68 Inner ring raceway 69 Needle 70 Valve body 71 Through hole 72 Receptacle 73a, 73b Ring part 74 Connection part 75 Opening 76 Nut 77 Mounting board 78 Second pivot 79 Pivot bracket 80 Swing arm 81 Small Projection 82 Gear transmission mechanism 83 Pinion 84 Recess 85 Cylinder case 86 Space 87a, 87b Rack 88 Rolling bearing 89 Space 90 Disc spring

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Takashi Machida 1-5-50 Kugenuma Shinmei, Fujisawa-shi, Kanagawa F-term in NSK Ltd. (Reference) 3J051 AA03 BA03 BB01 BD02 BE09 CA03 CB06 DA01 FA02

Claims (3)

[Claims] 1. A casing, an input disk and an output disk which are rotatably supported concentrically and independently of each other with their inner surfaces facing each other inside the casing. The portion between the disk and the output side disk does not intersect with the center axis of each of these disks, but exists at a twisted position perpendicular to the direction of the center axis and is concentric with or parallel to each other. An even number of pivots, a plurality of trunnions swinging about these pivots, displacement axes protruding from the inner surface of each trunnion, and a state supported rotatably around these displacement axes The same number of power rollers as the trunnions sandwiched between the inner surface of the input disk and the inner surface of the output disk, and these trunnions are connected to the respective pivots. In the toroidal type continuously variable transmission having the same number of actuators as the trunnions, the displacement of the trunnions in the axial direction of the pivots by the respective actuators is mechanically displaced. A toroidal-type continuously variable transmission characterized by having a synchronizing mechanism for synchronizing with each other. 2. A casing, first and second outer disks rotatably supported concentrically and synchronously with each other in a state in which the inner surfaces face each other inside the casing, and inner surfaces thereof. A first inner disk concentric with the first and second outer disks in a state where the first inner disk is opposed to the inner surface of the first outer disk, and a first inner disk rotatably supported independently of the first and second outer disks. A second inner disk rotatably supported concentrically with the first inner disk with its inner surface facing the inner surface of the second outer disk, and synchronously with the first inner disk; The portion between the outer disk and the first inner disk does not intersect with the center axis of each of these disks, but exists at a twisted position perpendicular to the direction of the center axis. I Or four or more parallel first and second even axes, a plurality of first trunnions swinging about these first axes, and first displacement axes protruding from the inner surface of each of the first trunnions. A plurality of first power rollers sandwiched between the inner surface of the first outer disk and the inner surface of the first inner disk while being rotatably supported around each of the first displacement axes. The portion between the second outer disk and the second inner disk does not intersect with the central axis of each of these disks, but exists at a twist position perpendicular to the direction of the central axis. Four or more even numbered second axes that are concentric or parallel to each other, and a plurality of second trunnions that swing about each of these second axes,
A second displacement shaft protruding from the inner surface of each of the second trunnions, and an inner surface of the second outer disk and an inner surface of the second inner disk in a state of being rotatably supported around each of the second displacement shafts. A toroidal-type continuously variable transmission comprising a plurality of second power rollers sandwiched between the side surfaces and the same number of actuators as the respective trunnions for displacing the respective trunnions in the axial direction of the respective pivots. A toroidal-type continuously variable transmission, wherein a synchronization mechanism for mechanically synchronizing the displacement of each trunnion in the axial direction of each of the pivots by each of the actuators is provided. 3. A synchronizing mechanism comprising: a drive rod having a base end connected and fixed to an end of each trunnion, each being axially displaced by an actuator to displace each trunnion in the axial direction of a pivot. The receiving piece fixed to the tip of the disk and the end of the receiving piece are freely engaged with these receiving pieces only for swinging displacement, and the central part is provided in the fixed part in parallel with the rotation center of each disk. And a swing arm pivotally supported by a second pivot.
The toroidal-type continuously variable transmission according to any one of the above.