JP2000009200A - Toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the number of part items so as to simplify assembly work and miniaturize and reduce weight by supporting and fixing yokes for supporting pivots of a plurality of power rollers in an oscillatingly displaceable and axially displaceable state, directly to the inner surface of a casing. SOLUTION: During operation of a continuously variable transmission, large thrust load is applied to power rollers 45, 45, and trunnions 27, 27 are elastically deformed in the direction of forming recessed faces on the mutually opposed inner side face side. As a result, the center axes of pivots 29, 29 and the center axes of support holes 31, 31 become slightly discordant. A pair of yokes 54, 55 constituting support means is therefore fixedly connected to the mutually opposed parts in a casing 5, directly to the casing 5, parallel with each other. Since the yokes 54, 55 are not displaced, displacement between the center axes of the pivots 29, 29 and the center axes of the support holes 31, 31 is limited. A support post heretofore required is therefore dispensed with, and height dimension is reduced so as to miniaturize and reduce weight while ensuring durability.

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. 16 to 18 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. 14 to 15) 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. 14 and 15). 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 trunnions 7, 7 are swung in a predetermined direction as a center so that the peripheral surfaces 9a, 9a of the power rollers 9, 9 are located close to 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. 15, 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 angles of the displacement shafts 8 and 8 are set between those in FIGS. 14 and 15, 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. 16 to 18 show a kind 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 side disks 17 and 18 corresponding to the first and second outer disks described in claim 2, respectively, with the ball splines 19 and 18 facing each other with the inner surfaces 2a and 2a facing each other. Support via 19. 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, 21 corresponding to the first and second inner disks described in claim 2,
Support via 2. 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 pair of support walls 24 provided in the casing 5. Rolling bearing 25, 2
5 supports the transmission shaft 16 concentrically and freely rotatable only. The first and second output side disks 2
0 and 21 are thus provided around the intermediate portion of the transmission shaft 16,
Sleeve 22 rotatably supported on transmission shaft 16
Are spline-engaged with both inner side surfaces 4a, 4a facing each other. Therefore,
The first and second output 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 disks 17 and 18, respectively. The first and second input disks 17 and 18 are concentric with the first and second input disks 17 and 18.
8 and is rotatably supported independently.

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. These yokes 26a and 26b correspond to the first and second support means described in the claims, respectively, and are formed by pressing a metal plate such as steel or forging a metal material such as steel. By processing, it is formed in a rectangular frame shape. 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. Circular support holes 31, 31 are provided at the center portions in the width direction (left and right directions in FIGS. 17 and 18) of both ends of the transmission shaft 16 in the axial direction (left and right directions in FIG. 16). Are formed respectively. The pair of yokes 26a and 26b, each having such a shape, is provided on a support post 33 formed on a portion of the inner surface of the casing 5 which faces each other.
a and 33b are slightly displaceably supported. Each of the support posts 33a and 33b is provided between the inner surface 2a of the first input side disk 17 and the inner surface 4a of the first output side disk 20 in the first cavity 34 and the second input side disk 18, respectively. Side 2a and second output disk 2
The second cavity 35 which is a portion between the inner cavity 4a and the inner surface 4a
Are provided in a state of facing each other. Therefore, the yokes 26a and 26b are connected to the support posts 33a and 3b.
3b, these yokes 26a, 26b
Has one end facing the outer periphery of the first cavity 34 and the other end facing the outer periphery of the second cavity 35, respectively.

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. 17, 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 placed 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. Circular holes 39, 39 are formed in the intermediate portion 28, as shown in FIGS. 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. Among these, the respective support shaft portions 42, 42 are rotatably supported inside the respective circular holes 39, 39 via radial needle bearings 44, 44. In addition, first and second power rollers 45 and 46 are rotatably supported around the pivot shafts 43 and 43 via separate radial needle bearings 47 and 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. 17 and 18). 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.
46 is the axial direction of the input shaft 1a and the transmission shaft 16 (FIG. 16).
In the right and left direction (the front and back directions in FIGS. 17 and 18), 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 loads applied to the outer rings 50, 50 of the thrust ball bearings 48, 48 from the first and second power rollers 45, 46 while supporting the pivotal support. The shaft portions 43, 43 and the outer rings 50, 50 are allowed to swing around the support shaft portions 42, 42.

Further, the first and second trunnions 27,
Drive rods 51 and 51 are connected to one end (lower end in FIGS. 17 and 18) of each of the drive rods 5.
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 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 the first input side disk 17 and the second input side disk 17 are rotated. The two input side disks 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. The rotation of the first and second output disks 20, 21 is transmitted to the first and second output disks 20, 21 via the output gear 23.
Taken out. 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. Drive piston 52, 52
Is displaced in the opposite direction by the same distance for each of the cavities 34 and 35.

With the displacement of the drive pistons 52, 52, a total of four trunnions 27, 28 are paired.
Are displaced in the 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. 14 and 15, the peripheral surfaces 9a and 9a of the first and second power rollers 45 and 46 and the disks 1 and
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.

[0019]

In the case of the conventional structure shown in FIGS. 16 to 18, the first and second trunnions 27 and 28 are placed inside the casing 5 and the support posts 33a and 3n respectively.
3b and the yokes 26a, 26b.
For this reason, parts production, parts management,
Not only does the assembling work become complicated, but also the height of the toroidal-type continuously variable transmission in the vertical direction in FIGS. 16 to 18 increases, making it difficult to reduce the size and weight. Further, if the size and the weight are forcibly reduced to enable installation in a limited space, the strength of each part is insufficient, and sufficient durability cannot be secured.
The toroidal-type continuously variable transmission of the present invention has been invented in view of such circumstances.

[0020]

SUMMARY OF THE INVENTION Among the toroidal-type continuously variable transmissions of the present invention, the toroidal-type continuously variable transmission according to the first aspect is similar to the conventionally known toroidal-type continuously variable transmission. The casing, the input side and the output side discs which are rotatably supported concentrically and independently of each other inside the casing, and intersecting the center axis of the discs at a portion between these discs. However, there are an even number of concentric or parallel pivots, which are present at a twist position perpendicular to the direction of the central axis, and a plurality of trunnions swinging about each of these pivots. Displacement shafts protruding from the inner surface of each trunnion, and a plurality of shafts sandwiched between the inner surfaces of the input side and output side disks while being rotatably supported around the respective displacement shafts. It comprises a power roller, provided on a side of the power rollers and a support means for supporting freely displaceable across the respective pivot the swing displacement and axial direction.
The toroidal-type continuously variable transmission according to the second aspect of the present invention has a casing and an inner side of the casing, like the conventional double-cavity toroidal-type continuously variable transmission shown in FIGS. In a state where the inner surfaces of the first and second outer disks are rotatably supported concentrically and synchronized with each other in a state where the inner surfaces of the first and second outer disks are opposed to each other, the inner surface thereof is opposed to the inner surface of the first outer disk. A first inner disk rotatably supported concentrically with the first and second outer disks and independent of the first and second outer disks, and having an inner surface facing an inner surface of the second outer disk. In a state in which the first inner disk is concentric with the first inner disk, and a second inner disk rotatably supported in synchronization with the first inner disk, at 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 located at a twisted position perpendicular to the direction of the center axis, and have four concentric or parallel first pivots, and A pair of first trunnions that swing about a pivot, a first displacement shaft protruding from the inner surface of each of the first trunnions, and a state in which the first trunnions are rotatably supported around these first displacement axes. A pair 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, Four second concentric or parallel second pivots which do not intersect with the center axis of each disk but exist at a twist position perpendicular to the direction of the center axis, and each of these second pivots Pair of second tigers swinging around ON, 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 a second inner surface in a state of being rotatably supported around each of the second displacement shafts. A pair of second power rollers sandwiched between the inner side surfaces of the disks, and a pair of first and second inner disks arranged on both sides of the first and second inner disks, with both inner disks being sandwiched from both sides, and one end portion of the first and second inner disks. A first portion provided substantially parallel to each other, with the other end positioned between the outer disk and the first inner disk, and the other end positioned between the second outer disk and the second inner disk. Second support means, wherein the first support means comprises two first pivots of the four first pivots and two second pivots of the four second pivots. And swingably and freely displaceable in their respective axial directions. , The second supporting means swings the remaining two first axes of the four first pivots and the second two pivots of the four second pivots as well as the respective axes. It is supported so that it can be displaced in any direction. In particular, in the toroidal-type continuously variable transmission of the present invention, the members constituting the support means or the first and second support means are directly supported and fixed to the inner surface of the casing.

[0021]

With the toroidal-type continuously variable transmission of the present invention configured as described above, the input side disk or the first and second outer disks are connected to the output side disk or the first and second inner disks. In addition to transmitting the rotational force, the operation when changing the speed ratio between the input side disk or the first and second outer disks and the output side disk or the first and second inner disks is conventionally known. It is the same as a known toroidal-type continuously variable transmission. In particular, in the case of the toroidal type continuously variable transmission of the present invention, the members constituting the support means or the first and second support means are directly supported and fixed to the inner surface of the casing, so that the number of parts is reduced. As a result, parts production, parts management, and assembling work can be simplified, and at the same time, height and size can be reduced to ensure durability and to reduce size and weight.

[0022]

FIG. 1 shows a first embodiment of the present invention corresponding to claims 2 and 3. The features of the present embodiment are the structure of a portion for supporting the first pivots 29, 29 provided at both ends of the first trunnions 27, 27 with respect to the casing 5, and the inclination angles of the first trunnions 27, 27. There is a structure for reliably synchronizing. Since the structure and operation of the other parts are the same as those of the conventional structure shown in FIGS. 16 to 18, 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. . Further, the second pivots 30, 30 (FIG. 18) provided at both ends of the second trunnions 28, 28 are also supported on the casing 5 by the same structure as the first pivots 29, 29. Thus, the inclination angles of the second trunnions 28, 28 are reliably synchronized. The following description is based on each of the first trunnions 27, 2
Perform only for step 7.

A pair of yokes 54 and 55, which are members constituting first and second support means, are directly connected and fixed to the casing 5 in parallel with each other at portions facing each other in the casing 5. ing. The positioning accuracy of each of the yokes 54 and 55 with respect to the casing 5 is strictly regulated by the engagement between a knock pin protruding on one side and a locking hole formed on the other side (both are not shown). Circular support holes 31, 31 are formed at positions where the four yokes 54, 55 are aligned with each other at the four corners.
And among these support holes 31, 31, the first pivots 29, 29 are provided inside the support holes 31, 31 formed at one end side of the yokes 54, 55 by radial needle bearings 36, 36, respectively. , Swinging and displaceable in the axial direction. The outer peripheral surfaces of the outer races 37, 37 constituting the radial needle bearings 36, 36 are spherical convex surfaces, respectively, and
Irrespective of the elastic deformation of the radial needle bearings 7, 27, the edge load is prevented from being applied to the contact portions between the rolling surfaces of the needles 38, 38 constituting the radial needle bearings 36, 36 and the mating surfaces.

That is, a large thrust load is applied to the first power rollers 45, 45 during operation of the toroidal type continuously variable transmission, and the first trunnions 27, 27 oppose each other based on the thrust load. It is elastically deformed in the direction in which the side surface becomes concave. Then, based on this elastic deformation, the center axis of each of the first pivots 29, 29 and the center axis of each of the support holes 31, 31 become slightly inconsistent.
Therefore, in such a case, the mismatch is compensated for by oscillating the outer races 37 in the support holes 31 to prevent the edge load from being applied.

However, in the case of the toroidal type continuously variable transmission of the present invention including the structure of this embodiment, unlike the conventional structure shown in FIGS.
Is not displaced, so that the deviation between the central axes of the first pivots 29, 29 and the central axes of the support holes 31, 31 is limited. That is, in the case of the above-mentioned conventional structure, the yokes 26a and 26b are respectively connected to the support posts 33a and
By supporting the casing 5 with a slight displacement via the bracket 33b, the inclination angles of the pair of first power rollers 45, 45 provided opposite to each other are made to coincide with each other. Therefore, during operation of the toroidal type continuously variable transmission, the center axes of the first pivots 29, 29 and the support holes 31,
The center axis of the yoke 26 is not only shifted from the center axis of the first trunnions 27, 27 due to the elastic deformation of the first trunnions 27, 27, but also
a, 26b. Therefore, in the conventional structure, the radial needle bearings 36
It is indispensable to provide the outer rings 37, 37 whose outer peripheral surfaces have spherical convex surfaces. On the other hand, in the case of the present example, since the yokes 54 and 55 are not displaced, the center axes of the first pivots 29 and the support holes 31 The deviation from the central axis is limited. Therefore, if the edge load can be prevented by crowning each of the needles 38, 38, the outer rings 37, 37 must be removed from the radial needle bearings 36, 36 as shown in FIG. Can also.

As described above, in the case of the toroidal type continuously variable transmission of the present invention including the structure of this embodiment, the yokes 54 and 55 are not displaced.
4 and 55 do not have the function of making the inclination angles of the pair of first power rollers 45 and 45 provided opposite to each other coincide with each other. That is, the inclination angle is determined by the drive cylinders 53, 5
3 is adjusted by the amount of axial displacement of the driving rods 51, 51 based on the supply and discharge of the pressure oil to and from the pressure oil.
It is difficult to exactly match the inclination angles of the pair of first power rollers 45, 45. Therefore, in the case of the conventional structure, the yokes 26a, 26a can be freely displaced, and the first power rollers 45, 45 are floating-supported, so-called floating angles of the pair of power rollers 45, 45. Was exactly matched. In contrast, in the case of the toroidal-type continuously variable transmission of the present invention, the pair of power rollers 4
The inclination angles of 5, 45 cannot be matched with each other.
Therefore, in the case of this example, a pair of first trunnions 27, 27 provided to face each other are connected to each other by a gear transmission mechanism 56, so that the first trunnions 27, 27 are supported by the first trunnions 27, 27. Power roller pair 45, 45
Are exactly matched to each other.

In order to provide the gear transmission mechanism 56, a recess 57 is provided in one yoke 55 (the lower part in FIG. 1). Therefore, a space 59 for accommodating the gear transmission mechanism 56 is formed between the two members 55 and 58 in a state where the recess 57 and the cylinder case 58 are overlapped. Gear transmission mechanism 5 housed in this space 59
6 includes a pair of pinions 60, 60 having the same shape and the same number of teeth as one another, and one rack 61 having teeth of the same pitch formed at both end edges. Each of the pinions 60 is connected to the first trunnion 27, 27, respectively.
Non-cylindrical portions formed at the distal ends of the first pivots 29, 29 provided at the ends of the first shafts 29 are externally fixed or supported by ball splines or the like so that they cannot rotate relative to each other and can move freely in the axial direction as necessary. Accordingly, each of the first trunnions 27,
Reference numeral 27 rotates in synchronization with the pinions 60, 60. When changing the gear ratio, each of the first trunnions 2
7, 27 are displaced in the axial direction of the first pivots 29, 29, respectively. Therefore, when each of the pinions 60, 60 is externally fitted and fixed to the non-cylindrical portion, each of the pinions 6
A suitable backlash is provided at a meshing portion between the racks 61 and 60 so as not to cause a problem in matching the inclination angles, and the relative displacement between the pinions 60 and 60 and the rack 61 is adjusted. Enable. Each pinion 6 above
If the non-cylindrical parts 0 and 60 are supported movably in the axial direction, such considerations are unnecessary.

The rack 61 is supported in the space 59 so that only the displacement in the axial direction of the input shaft 1a (the front and back direction in FIG. 1) is free. For this reason, in the illustrated example, the guide protrusions 62 formed on the side surfaces of the rack 61 and the guide grooves 63 formed on the bottom surface of the recess 57 are engaged. Further, a sliding convex portion 66 is formed on the other side surface of the rack 61, and the sliding convex portion 66 is slid in contact with the cylinder case 58 to prevent the rack 61 from being displaced in the falling direction. ing. The structure for supporting the rack 61 so as to be able to move in parallel in only one direction is not limited to the structure shown in the figure, and various structures conventionally known can be adopted. For example, a long hole is formed in the rack 61 in the front and back direction in FIG. 1, and a plurality of guide pins fixed in the space 59 in the space 59 in the front and back direction in FIG. 1 are engaged with the long hole. You can do it.

Each of the pinions 6 supported as described above
0, 60 and the rack 61, these pinions 60, 6
The gear transmission mechanism 56 is configured by combining the teeth formed on the outer peripheral edge of the No. 0 with the teeth formed on both side edges of the rack 61 in a mutually meshed state. This gear transmission mechanism 56
In addition to minimizing backlash, each pinion 6
The diameters of the pitch circles 0 and 60 are increased to some extent (within the range where interference with other members can be prevented). Accordingly, the first trunnions 27, 27 to which the respective pinions 60, 60 are fixed, and the respective first trunnions 2
The inclination angles of the first power rollers 45, 45 supported by 7, 27 can be made to exactly match each other. Although not shown, a gear transmission mechanism having the same structure is provided between each of the first trunnions 27, 27 and the second trunnions 28, 28 (FIG. 18).
The inclination angle between 7, 27 and the second trunnions 28, 28
They try to match each other.

A stopper plate 64 provided at the upper center of FIG. 1 is for preventing the inclination angle of each of the first trunnions 27, 27 from becoming excessive. 45 around the nozzle piece 65 for spraying the lubricating oil to the contact portions between the peripheral surfaces 9a, 9a of the first 45 and the inner surface 2a of the first input disk 17 and the inner surface 4a of the first output disk 20 (FIG. 16). I support it. The yoke 5
The mounting position accuracy of the nozzle piece 65 with respect to 4 does not need to be particularly strict, and does not cause an increase in cost. If the stopper plate 64 is supported so as to be slightly displaceable with respect to the nozzle piece 65, a practically sufficient function can be exhibited. The above explanation is
The present invention was applied to a case where the present invention was applied to a double-cavity toroidal type continuously variable transmission. The present invention can exert a remarkable effect when applied to a double cavity type toroidal type continuously variable transmission, but is also applicable to a single cavity type toroidal type continuously variable transmission as shown in FIGS. it can.

As described above, in the case of the toroidal-type continuously variable transmission of the present invention, the yokes 54 and 55, which are members constituting the first and second support means, are attached to the inner surface of the casing 5. It is directly supported and fixed. This eliminates the need for the support posts 33a and 33b required in the above-described conventional structure, thereby simplifying component production, component management, and assembly work by reducing the number of components, and at the same time, reducing the height dimension. In addition, miniaturization and weight reduction can be achieved while ensuring durability.
In addition, as shown in the example of the drawing, the peripheral surfaces 9 of the first power rollers 45, 45 are made to match the inclination angles of the first power rollers 45, 45 by the gear transmission mechanism 56.
It is possible to prevent the occurrence of remarkable slippage at the contact portions between the a, 9a and the inner surfaces 2a, 4a of the disks 17, 20, and to sufficiently secure the efficiency of the toroidal type continuously variable transmission.

Next, FIG. 3 corresponds to claims 2-3.
9 shows a second example of the embodiment of the present invention. In the case of the present example, the first pivots 29, 29 provided at both ends of the first trunnions 27, 27 are respectively provided in the support holes 31, 31 formed in the yokes 54, 55 with the radial needle bearing 36 and the ball spline. By 67 and 67, it supports so that rocking displacement and axial displacement are possible. By adopting such a structure, in the case of this example, compared to the case of the above-described first example,
Each of the first trunnions 27, 27 is connected to each of the first pivots 2
It can be smoothly displaced in the axial directions of 9 and 29.
Since the configuration and operation of the other parts are the same as those in the first example described above, the same parts are denoted by the same reference numerals, and redundant description will be omitted.

Next, FIGS. 4 to 11 show a third embodiment of the present invention corresponding to claims 2 to 4. FIG. In the case of this example, the gear transmission mechanism 56a for synchronizing the swing displacements of the first trunnions 27, 27 employs a structure that operates smoothly, and the yokes 54a, 55a include first and second yokes 54a, 55a. A disk having a shape capable of preventing interference with the two input disks 17, 18 and the first and second output disks 20, 21 (FIG. 16) is employed to smooth the differential of the toroidal type continuously variable transmission. And a reduction in size and weight.

The above-mentioned gear transmission mechanism 56a is constituted, and each is disposed between adjacent pinions 60, 60.
A total of four racks 61a and 61b are
Linear motion rolling bearing (linear bearing) for a
By 68a and 68b, it supports so that translation is possible.
That is, a total of eight guide recesses 69a and 69b, two for each of the racks 61a and 61b, are provided on the lower surface of the yoke 55a fixed to the inner surface of the casing 5 so as to face the racks 61a and 61b, respectively. Rack 61a,
61b.

Guide flanges 71a, 71b are formed at portions of the intermediate portions of the connecting portions 70a, 70b provided at the intermediate portions of the racks 61a, 61b, respectively, at the portions matching the guide recesses 69a, 69b. are doing. The thickness of each of the guide flanges 71a and 71b is the same as that of the guide recess 69.
a, 69b, and each of these guide flanges 71a, 71b is formed with each of these guide recesses 69a, 69b.
Inside, loosely inserted. And each of these flanges 71
a, 71b and each of these guide recesses 69a, 69
b, between each of the rolling bearings 68a,
68b are provided. Each of these rolling bearings 68a, 68
Each of b includes a race made of a hard metal plate, a plurality of needles, and a retainer.

As the races, those having an appropriate thickness are selected and used in order to eliminate the backlash of the installation portions of the rolling bearings 68a and 68b. Of course, the other surfaces of the flanges 71a and 71b and the guide recesses 69
A gap is interposed between the a and 69b and the other inner surface to prevent friction between these two surfaces. Such rolling bearings 68a, 68b are connected to the respective racks 61a,
Two sets of each of the flanges 71a and 71b provided on the racks 61a and 61b are sandwiched from both sides by two sets for each of the racks 61a and 61b. At both sides).

Therefore, each of the racks 61a and 61b is connected to each of the guide recesses 69a and 69 with respect to the yoke 55a.
It can be smoothly displaced with a light force without tilting in the direction of b. Also, each of these racks 61a and 61b has
When a force perpendicular to the displacement direction is applied, a pair of rolling bearings 68 attached to the racks 61a and 61b are used.
a, one of the rolling bearings 68a, 68b
8b supports the force and compensates for the smooth displacement of each of the racks 61a, 61b. Further, a part of the yoke 55a which is aligned with the guide recesses 69a, 69b includes:
Oil supply holes 72, 72 are formed. Also, the upper yoke 5
An oil supply hole 73 communicating with the nozzle piece 65 is formed in 4a. During operation of the toroidal-type continuously variable transmission, the lubricant (traction oil) supplied from the oil supply hole 73 is applied to the peripheral surfaces 9a, 9a of the power rollers 45, 46 and the first and second input side disks 17, 18, and First, abutment portions of inner surfaces 2a, 4a of second output side disks 20, 21 (FIG. 16)
To lubricate these contact portions. The lubricating agent that lubricates each of the abutting portions is connected to the lubrication holes 72, 72.
Flows down into each of the guide recesses 69a, 69b to lubricate the rolling bearings 68a, 68b.

With the structure of the present embodiment as described above, the racks 61a and 61b are smoothly displaced, and the four trunnions 27 (28) forming the double cavity type toroidal type continuously variable transmission are formed. The swinging can be performed with a light force while being synchronized. Further, the swing angle of each trunnion 27 (28) can be easily regulated by using each of the guide concave portions 69a, 69b and each of the flange portions 71a, 71b. That is, it is necessary to prevent each of the trunnions 27 (28) from swinging beyond the maximum value. On the other hand, each of the flanges 71a, 71b
Can be displaced only inside the guide recesses 69a, 69b. Therefore, in the case of the present example, as shown in FIG. 11, in a state where the trunnions 27 (28) are oscillated to the maximum extent, the flanges 71a and 71b are connected to the guide recesses 69a and 69b. Displaced to the end.

FIG. 11 shows each of the first trunnions 2.
7 and 27 show the state of being displaced to the maximum speed increasing side.
a, 71b abut against opposite ends of the guide recesses 69a, 69b. Each of the above rolling bearings 68a, 68b
Has a length enough to back up the flanges 71a, 71b even when the flanges 71a, 71b abut against the opposite ends of the guide recesses 69a, 69b.

Further, in the case of this embodiment, as in the case of the second embodiment shown in FIG.
The combination of the ball troughs 36 and the ball splines 67, 67 allows the axial displacement and the oscillating displacement of the first trunnions 27, 27 to be smoothly performed with a light force. The first and second input side disks 17 and 18 and the first and second output side disks 20 and 21 have a shape capable of preventing interference.

First, with respect to the axial direction of the input shaft 1a (vertical direction in FIGS. 5 and 8), a through hole 74 is formed at the center position of the upper yoke 54a. ) A pair of connecting portions 75, 75 sandwiching from both sides are formed. As shown in FIG. 7, the lower surface of each of the connecting portions 75 is in the width direction of the yoke 54a (the left-right direction in FIG. 5).
It inclines in the upward direction as it approaches the center (closer to the through hole 74). Even when the mounting position of the upper yoke 54a is lowered based on the existence of such a through hole 74 and the lower surface shape of each of the connecting portions 75, 75, the yoke 54a and the first and second output side disks 20, 21
And the first and second output side disks 2
Interference with the outer peripheral edge of the support wall 24 for rotatably supporting 0 and 21 can be prevented. Curved portions 77, 77 are provided at both ends of the yoke 54a in the axial direction of the input shaft 1a. Each of the curved surface portions 77, 77 moves toward the center in the width direction of the yoke 54a (the above-described notch portion 7).
6 and 76) are inclined upward (toward the rear surface in FIG. 5). Even when the mounting position of the upper yoke 54a is lowered based on the shape of each curved surface portion 77, 77, the yoke 54a and the outer peripheral edge portions of the first and second input side disks 17, 18 Interference can be prevented. Therefore, the installation position of the yoke 54a can be made closer to the input shaft 1a. In addition, through holes for inserting the bolts 84 constituting the support wall 24 are formed in a part of the upper yoke 54a as necessary.

On the other hand, also at the center of the lower yoke 55a,
A through-hole 78 and a curved surface portion 79, 79 for preventing interference with the outer peripheral edge portions of the first and second output side disks 20, 21.
Is formed. Similarly, at both ends of the yoke 55a in the axial direction of the input shaft 1a, cutouts 80, 80 at the center in the width direction, and curved surfaces 81, which sandwich these cutouts 80, 80 from both sides in the width direction, 81 are provided. Even when the mounting position of the lower yoke 55a is raised based on the existence of the through holes 78, the respective notches 80, 80, and the respective curved surface portions 79, 81, the yoke 55a and the first, Interference with the outer peripheral edge portions of the second input side disks 17, 18 and the first and second output side disks 20, 21 can be prevented. Therefore, the installation position of the yoke 55a can be made closer to the input shaft 1a. As a result, the distance between the upper yoke 54a and the lower yoke 55a is reduced, and the toroidal-type continuously variable transmission including both the yokes 54a, 55a can be reduced in size and weight.
A plurality of through holes for lubrication or for supplying and discharging traction oil into and from the drive cylinders 53 are formed at both ends in the width direction of the lower yoke 55a. Further, a control valve for controlling the supply and discharge of traction oil into and from the drive cylinders 53, 53 is incorporated in the casing 5 or provided separately.

Next, FIG. 12 shows a fourth embodiment of the present invention corresponding to the second to fourth aspects. In the case of this example, the lubricant is applied to the peripheral surfaces 9a, 9a of the power rollers 45 (46) and the inner surfaces of the first and second input disks 17, 18 and the first and second output disks 20, 21. 2a, 4
Nozzle piece 65 for spraying the contact portion (FIG. 16) with a.
Is provided on the upper surface of the lower yoke 55a. Since the configuration and operation of the other parts are the same as those of the above-described third example, the same parts are denoted by the same reference numerals, and duplicate description will be omitted. The nozzle piece 65 is attached to each yoke 54.
a, 55a, or directly on the inner surface of the casing 5.

Next, FIG. 13 shows a fifth example of the embodiment of the present invention, which also corresponds to claims 2 and 4. In the case of this example, the first trunnions 27, 27,
A mechanism for synchronizing the swing angle between the second trunnions 27, 28 is provided by a cable 23a that is directly or via the pulleys 22, 22 connected to the respective trunnions 27, 28,
23b. Such a cable 2
Synchronization mechanisms using 3a and 23b have been widely known in the past, and detailed illustration and description are omitted. Since the configuration and operation of the other parts are the same as those of the third example described above, the same reference numerals are given to the same parts, and duplicate description will be omitted. When the present embodiment is implemented, in order to make the swing angles of the trunnions 27 and 28 strictly coincide with each other, the cables 23a and 23b are made of a material that is not easily elastically deformed and whose dimensions are precisely regulated. I do.

[0045]

Since the present invention is constructed and operates as described above, it can contribute to the realization of a toroidal type continuously variable transmission which can be manufactured small, light and inexpensive and has excellent transmission efficiency.

[Brief description of the drawings]

FIG. 1 is a view showing a first example of an embodiment of the present invention and corresponding to an AA cross section in FIG. 16;

FIG. 2 is a view showing another structural example and corresponding to a portion B in FIG. 1;

FIG. 3 is a view similar to FIG. 1, showing a second example of the embodiment of the present invention;

FIG. 4 is a view similar to FIG. 1, showing the third example.

FIG. 5 is a view of an upper yoke used in a third example as viewed from below in FIG. 4;

FIG. 6 is a perspective view of the same.

FIG. 7 is a view showing a structure of a third example and corresponding to a CC section of FIG. 16;

FIG. 8 is a view of a lower yoke used in a third example as viewed from above in FIG. 4;

FIG. 9 is a perspective view of the same.

FIG. 10 is a perspective view showing the gear transmission mechanism incorporated in the third example when viewed from above in FIG. 4;

FIG. 11 shows the trunnion in the most inclined position, FIG.
The figure corresponding to the D part of 0.

FIG. 12 is a view similar to FIG. 1, illustrating a fourth example of the embodiment of the present invention;

FIG. 13 is a view similar to FIG. 1, showing the fifth example;

FIG. 14 is a side view showing a basic configuration of a conventionally known toroidal-type continuously variable transmission in a state of maximum deceleration.

FIG. 15 is a side view similarly showing a state at the time of maximum acceleration.

FIG. 16 is a sectional view showing an example of a conventional specific structure.

FIG. 17 is a sectional view taken along the line AA of FIG. 16;

FIG. 18 is a sectional view taken along the line EE in FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1, 1a Input shaft 2 Input side disk 2a Inner side 3 Output shaft 4 Output side disk 4a Inner side 5 Casing 6 Pivot 7 Trunnion 8 Displacement axis 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 Bearing section 43 Pivot shaft section 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, 54a Yoke 55, 55a Yoke 56, 56a Gear transmission mechanism 57 recess 58 cylinder case 59 space 60 pinion 61, 61a, 61b rack 62 guide projection 63 guide groove 64 stopper plate 65 nozzle piece 66 sliding projection 67 ball spline 68a, 68b rolling bearing 69a , 69b Guide concave portions 70a, 70b Connecting portions 71a, 71b Guide flange portion 72 Oil supply hole 73 Oil supply hole 74 Through hole 75 Connecting portion 77 Curved surface portion 78 Through hole 79 Curved surface portion 80 Cutout portion 81 Curved surface portion 82 Pulley 83 , 83b cable 84 volts

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Takashi Imanishi 1-5-50 Kumeinuma Shinmei, Fujisawa-shi, Kanagawa Nippon Seiko Co., Ltd. Nippon Seiko Co., Ltd. (72) Inventor: Satoshi Yamashita

Claims (4)

[Claims] 1. A casing, an input side disk and an output side disk which are rotatably supported concentrically and independently of each other inside the casing, and a central axis of the two disks at a portion between the two disks. Although it does not intersect, there is an even number of concentric or parallel pivots that exist at a twist position that is perpendicular to the direction of this central axis, and a plurality of pivots that swing about each of these pivots. The trunnion, the displacement shaft protruding from the inner surface of each of the trunnions, and the input side and the output side of the disk are sandwiched between the inner surfaces of the two disks in a state of being rotatably supported around the respective displacement axes. A toroidal-type continuously variable transmission comprising a plurality of power rollers and supporting means provided on the side of each of the power rollers to support the pivots so as to be able to swing and displace in the axial direction. A toroidal-type continuously variable transmission, wherein a member constituting the supporting means is directly supported and fixed to an inner surface of the casing. 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 parallel first axes, a pair of first trunnions swinging about these first axes, a first displacement axis projecting from the inner surface of each first trunnion, A pair of first power rollers sandwiched between an inner surface of the first outer disk and an inner surface of the first inner disk while being rotatably supported around the first displacement axis; The portion between the two outer disks and the second 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, concentric with each other, or Four parallel second pivots, a pair of second trunnions swinging about the respective second pivots, a second displacement axis protruding from the inner surface of each of the second trunnions, While being rotatably supported around the displacement axis, A pair of second power rollers sandwiched between the inner surface of the second outer disk and the inner surface of the second inner disk; With one end positioned at the portion between the first outer disk and the first inner disk, and the other end positioned at the portion between the second outer disk and the second inner disk. And first and second support means provided substantially parallel to each other, wherein the first support means comprises two of the four first pivots and the four first pivots. The two pivots of the second pivot are supported so as to swing and be displaceable in their respective axial directions. The second support means includes:
The remaining two first pivots of the four first pivots and the two second pivots of the four second pivots are supported swingably and displaceably in their respective axial directions. In the toroidal-type continuously variable transmission, the members constituting the first and second support means are directly supported and fixed to the inner surface of the casing. 3. A gear transmission mechanism is provided between the plurality of trunnions to synchronize the tilting of each of the trunnions.
A toroidal-type continuously variable transmission according to claim 1. 4. A part of a member constituting the first and second support means, which is opposed to the peripheral portions of the first and second inner disks, is prevented from interfering with the peripheral portions of the two disks. The first and second supporting means have a lubricant passage for supplying lubricant to a contact portion between each disk and each roller. The toroidal-type continuously variable transmission according to any one of claims 2 to 3, which is provided.