JP3280707B2 - Toroidal type continuously variable transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a toroidal type continuously variable transmission.

[0002]

2. Description of the Related Art Generally, in a toroidal type continuously variable transmission, which is one of continuously variable transmissions for automobiles, an input disk for inputting torque from an engine side and an output disk for outputting torque to driving wheel sides. Are arranged coaxially, and a roller is provided that contacts the two disks and transmits torque between the two disks, so that a gear ratio according to the tilt angle (tilt angle) of the rollers is obtained. .

More specifically, as shown in FIG. 9, for example, two sets of continuously variable transmission mechanisms comprising an input disk, an output disk and rollers are provided coaxially, and torque is transmitted in parallel by each continuously variable transmission mechanism. There has been proposed a toroidal type continuously variable transmission. In the toroidal type continuously variable transmission shown in FIG.
When viewed in the front-rear direction (the left-right direction in FIG. 9), the input disks 101f and 101r are arranged at the center side, while the output disks 102f and 102r are arranged at the end sides. Between the first and second
Rollers 103a and 103b are arranged, and third and fourth rollers 103c and 103d are arranged between the rear input disk 101r and output disk 102r. Although not shown, the first to fourth rollers 103a to 103d are
Each of the first to first extending in the vertical direction (direction perpendicular to the paper surface)
It is rotatably supported by a fourth roller support member.

Here, first to fourth rollers 103a to 103a-10
A force Fx in the left-right direction acts on 3d as a reaction force of the pressing force to the disk side, while the roller is tilted (tilted).
A force Fy acts in the front-rear direction. As a result, the resultant forces F1 to F4 of Fx and Fy act on the _first to _fourth rollers 103a to 103d, respectively. Here, since the resultant force of F _{1 to} F ₄ is almost 0, in such a toroidal-type continuously variable transmission, a connecting member (link member) for generally supporting and positioning the first to fourth roller supporting members collectively. And F ₁
So that together they cancel each other ~F _4.

[0005] Usually, one connecting member is disposed on each of the lower side and the upper side of the roller, and both connecting members are respectively mounted on a transmission case. As such a connecting member, specifically, for example, a member having a lower connecting member 110 as shown in FIG. 10 and an upper connecting member 114 as shown in FIG. 11 has been proposed (Japanese Patent Laid-Open No. 2-283949). Reference). As apparent from FIGS. 10 and 11, the lower connecting member 110 is a single plate member, while the upper connecting member 114 is
15 and 116, and two small plates 117f and 117r connected to both rods 115 and 116, respectively.

Here, the lower connecting member 110 has first to
Four shaft holes 111a-1 supporting the fourth roller supporting member
11d, and two fitting holes 112f and 112r for attaching the lower connecting member 110 to the transmission case. Also, the first to fourth connection members 114
Four shaft holes 118a to 118d supporting the roller supporting member
And two fitting holes 119f and 119r for attaching the upper connecting member 114 to the transmission case.

[0007]

Generally, in such connecting members, in order to absorb an assembling error or an arrangement error of a roller supporting member or the like engaged with the connecting members, an error is required.
It is necessary to allow some relative displacement between the lower connecting member and the upper connecting member.

In the conventional connecting member shown in FIGS. 10 and 11, the upper connecting member 114 is
Since the divided structure is used, the flexible structure is relatively easy to bend, so that a slight relative displacement between the two connecting members 110 and 114 is possible. And fitting holes 119f, 1
The 19r is provided with a predetermined clearance in the Ay direction (left-right direction) between the mounting member (hatched portion) inserted therein, so that the roller support member can be displaced in the Ay direction by the clearance. Etc. can be absorbed. In FIGS. 10 and 11, the connecting members 110 and 114 can hardly be displaced in the direction of the double arrow marked with a cross. However, FIG. 10 and FIG.
In the conventional connecting members 110 and 114 shown in FIG. 1, although a certain degree of assembly error can be absorbed, there is a problem that the number of parts increases due to the divided structure, resulting in an increase in cost.

A lower connecting member 1 as shown in FIG.
20 and an upper connecting member 124 as shown in FIG. 13 have also been proposed. As is clear from FIGS. 12 and 13, the lower connecting member 120 has first to fourth
Four shaft holes 121a to 121d supporting the roller supporting member
And two fitting holes 122f and 122r for attaching the lower connecting member 120 to the transmission case. The upper connecting member 124 also has four shaft holes 125a to 125d for supporting the first to fourth roller supporting members, and two fitting holes 127f and 127r for attaching the upper connecting member 124 to the transmission case. Are formed.

In the connecting member shown in FIGS. 12 and 13, the rear fitting hole 122r of the lower connecting member 120 is a large-diameter hole having a predetermined clearance with respect to the mounting member (shaded portion). And the front fitting hole 1 of the upper connecting member 124
27f is a large-diameter hole having a predetermined clearance with respect to the mounting member (hatched portion). Therefore, the lower connecting member 120 can be displaced in the rear side by the clearance in the Ay direction, and the upper connecting member 124 can be displaced in the front side by the clearance in the Ay direction.
20 and 124 can be displaced relative to each other to some extent,
An error in assembling the roller support member and the like is absorbed. In FIGS. 12 and 13, both connecting members 120 and 124 can hardly be displaced in the direction of the double arrow marked with “X”.

However, the conventional connecting members 120 and 124 shown in FIGS. 12 and 13 can absorb a certain amount of assembly error and have a simple structure, but the rear side of the lower connecting member 120 is Ay. In this case, the rear roller support member may be swung in the Ay direction. In this case, there is a problem that the roller support member interferes with the speed change piston (see paragraph [0040] described later). Occurs. The lower the roller support member is, the more easily it swings.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned conventional problems, and is a toroidal-type continuously variable transmission provided with a pair of upper and lower connecting members for supporting a plurality of roller supporting members collectively. It is possible to allow the relative displacement between the two connecting members to a certain extent with a simple structure without causing troubles such as occurrence of interference between the roller support member and the shifting piston (see paragraph [0040] below). It is an object of the present invention to provide a toroidal-type continuously variable transmission that can be used.

[0013]

In order to achieve the above object, the present invention provides: (i) an input disk, and an output disk arranged such that curved surfaces face the input disk. And two rollers that contact the input disk and the output disk and transmit torque from one disk to the other disk at a speed ratio according to a tilt angle,
In a toroidal-type continuously variable transmission in which first and second two toroidal-type transmission mechanisms are arranged in the axial direction of the output shaft,
(Ii) a roller supporting member for rotatably supporting the rollers of the first and second toroidal transmission mechanisms, and a piston for changing the tilt angle of the rollers via the roller supporting members. (Iii) the first and second two connecting members for connecting these roller supporting members are arranged in a positional relationship such that all the rollers are sandwiched therebetween, and the first connecting member Is disposed on the side on which the piston is disposed, the second connecting member is disposed on the side on which the piston is not disposed, and (iv) allowing the first connecting member to penetrate the insertion member fixed to the fixing portion. Forming two positioning holes for positioning the first connecting member,
One of the positioning holes has a shape that does not allow displacement in the output axis direction and a direction perpendicular to the output axis direction in the spread plane of the first connecting member, and the other positioning hole has (V) two positioning holes for positioning the second connecting member by inserting an insertion member fixed to the fixing portion into the second connecting member. Are formed, and one of the positioning holes is a large-diameter hole having a predetermined clearance with the insertion member, and the other positioning hole has a length that is long in a direction perpendicular to the axis direction of the output shaft. Provided is a toroidal type continuously variable transmission characterized by having holes.

[0014]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be specifically described below.
As shown in FIG. 5, the transmission TM of the automobile includes first to first transmissions.
An output torque of the engine 1 having the fourth cylinders # 1 to # 4 is transmitted to a transmission output shaft 5 via a torque converter 2 (torque converter 2), a gear reduction mechanism 3 including a planetary gear system, and a forward / reverse switching mechanism 4. Is provided. Further, the output torque of the engine 1 is
A second transmission unit is provided for outputting to the transmission output shaft 5 via a switching clutch 6 and a toroidal-type continuously variable transmission C including a first toroidal transmission mechanism 7 and a second toroidal transmission mechanism 8. ing. When the switching clutch 6 is in the off state, the torque is transmitted through the first transmission section, and when the switching clutch 6 is in the on state, the torque is transmitted through the second transmission section.

The first transmission portion is used when the torque converter 2 has a strong torque increasing function, and is required mainly when a relatively large speed ratio (torque ratio) is required at the time of starting, acceleration, or the like. The transmission section is mainly used when the operation is performed at a relatively small speed ratio such as during high-speed running.

Hereinafter, a specific structure of the transmission TM will be described. First, the first transmission unit will be described. The torque converter 2 is substantially composed of a pump impeller 12, a turbine liner 13, and a stator 14. The pump impeller 12 is connected to the engine output shaft 1 via a pump cover 15.
1 and rotates integrally with the engine output shaft 11. Further, the pump impeller 12 has a first
A hollow shaft 16 is coaxially connected, and an oil pump 17 is provided at a rear end (right end in FIG. 5) of the first hollow shaft 16.
Are connected. The turbine liner 13 is coaxially connected to a torque converter output shaft 18 (turbine shaft). The stator 14 is connected to the second hollow shaft 21 via a one-way clutch 19. The second hollow shaft 21 is fixed to the transmission case 22.

The torque converter 2 rotationally drives the turbine liner 13 with oil discharged from the pump impeller 12, rectifies the oil rebounding from the turbine liner 13 with the stator 14, and increases the rotation of the pump impeller 12 with the rectified oil. By repeating the above process, a torque larger than the torque of the engine output shaft 11 is output to the torque converter output shaft 18.

The gear reduction mechanism 3 is substantially composed of the sun gear 2
5, a first pinion 26, a reverse ring gear 27, a second pinion 28, a forward ring gear 29, and a carrier 30. Here, the torque of the torque converter output shaft 18 is input to the sun gear 25. The first and second pinions 26 and 28 are rotatably supported by a carrier 30. Note that the carrier 30 is
It is fixed to a second hollow shaft 21 fixed to a transmission case 22.

The sun gear 25 and the first pinion 26
And the first pinion 26 and the reverse ring gear 27 mesh with each other to form a planetary gear system having a reverse rotation reduction function. In this planetary gear system, a reverse torque larger than the torque input to the sun gear 25 is output from the reverse ring gear 27.

The first gear meshing with the sun gear 25
The rear portion of the pinion 26 meshes with the second pinion 28,
Further, the second pinion 28 and the forward ring gear 29 mesh with each other, and these form a planetary gear system having a forward rotation reducing function. In this planetary gear system, a forward rotation torque larger than the torque input to the sun gear 25 is output from the forward ring gear 29.

The forward / reverse switching mechanism 4 is substantially composed of a reverse clutch 31, a clutch case 32, a forward clutch 33, and a one-way clutch 34.
The clutch case 32 is connected to the transmission output shaft 5 via an output disk 44f of the first toroidal transmission mechanism 7 described later. Here, when the reverse clutch 31 is engaged, the reverse ring gear 27
And the clutch case 32 are connected, and the torque of the reverse ring gear 27 is transmitted to the transmission output shaft 5. On the other hand, when the forward clutch 33 is engaged, the torque of the forward ring gear 29 is transmitted to the transmission output shaft 5.
It should be noted that the one-way clutch 34 runs idle when the rotation speed of the transmission output shaft 5 is higher than the rotation speed of the forward ring gear 29 to prevent the forward ring gear 29 from being reversely driven by the transmission output shaft 5. It is provided in.

Next, the second transmission section will be described. The second transmission section substantially includes a switching clutch 6 for connecting / disconnecting the input of torque to the second transmission section, and a toroidal type transmission mechanism including first and second toroidal type transmission mechanisms 7 and 8. The transmission includes a step transmission C and a gear mechanism 35 that transmits torque from the switching clutch 6 to the toroidal-type continuously variable transmission C. Here, when the switching clutch 6 is engaged, the gear mechanism 35 transmits the torque of the first hollow shaft 16, that is, the torque of the engine output shaft 11 to the drive gear 37, the idle gear 38, and the driven gear 39, which are sequentially meshed. , And the torque of the bypass shaft 40 is transmitted to the toroidal-type continuously variable transmission C via the driving gear 41 and the driven gear 42 meshing with each other.

The toroidal type continuously variable transmission C includes a first toroidal type transmission mechanism 7 disposed on the front side (left side in FIG. 5) so as to surround the transmission output shaft 5 and a second toroidal transmission mechanism 7 disposed on the rear side. And a toroidal transmission mechanism 8. Here, the first and second toroidal transmission mechanisms 7 and 8 are arranged so as to be symmetrical in the front-rear direction, but since the configuration and function of both are basically the same, corresponding members are The same numbers are given, and in principle, each member of the first toroidal transmission mechanism 7 is given a suffix f, and each member of the second toroidal transmission mechanism 8 is given a suffix r. However, since two members, such as rollers, provided in each of the toroidal transmission mechanisms 7 and 8 cannot be distinguished only by the suffixes f and r, each of the members disposed on the left and right of the first toroidal transmission mechanism 7 can be distinguished. The members are provided with subscripts a and b, respectively, and the members disposed on the left and right of the second toroidal transmission mechanism 8 are provided with subscripts c and d, respectively. Therefore, in the following, the description given for a member will, in principle, also apply to other members having the same number and different subscripts.

The first toroidal transmission mechanism 7 has a first input disk 43f loosely fitted around the transmission output shaft 5.
And a first output disk 44 fixed to the transmission output shaft 5
f, and first and second rollers 45a and 45b for transmitting the torque of the first input disk 43f to the first output disk 44f. The first input disk 43f includes an input cam 48 to which the driven gear 42 is attached,
The input cam 48 engages via the first cam roller 49f, and the input torque to the first input disk 43f is increased as the input torque to the first input disk 43f is increased.

The first and second rollers 45a and 45b are rotatable about an axis Y, respectively, and their peripheral surfaces are formed by the curved surface of the first input disk 43f and the first output disk 4b.
4f is in contact with the curved surface. For this reason, the torque (rotation) of the first input disk 43f is reduced by the first and second rollers 45f.
The signal is transmitted to the first output disk 44f via the first and second output disks 45a and 45b. Here, the gear ratio in the torque transmission from the first input disk 43f to the first output disk 44f
(Torque ratio) is the radius R of the first output disk 44f at the position where the first output disk 44f is in contact with the first and second rollers 45a and 45b.
_2, is determined by the ratio R ₂ / R ₁ of the radius R ₁ of the first input disc 43f.

The contact position between the first and second rollers 45a and 45b and the disks 43f and 44f is determined by the tilt angle (tilt angle) of the first and second rollers 45a and 45b, as described later. ), And by changing this tilt angle by a hydraulic mechanism described later,
The gear ratio can be arbitrarily set within a predetermined range. The second toroidal transmission mechanism 8 is, of course, basically the same as the first toroidal transmission mechanism 7.

Hereinafter, a specific structure of the toroidal transmission mechanism C will be described. As shown in FIGS. 1 to 4, in the first toroidal transmission mechanism 7, the first output disk 44 f
Are spline-fitted to the transmission output shaft 5. Further, the first output disk 44f is rotatably supported by the transmission case 22 via the first bearing 47f while being positioned by the ring-shaped positioning member 46 fitted to the transmission output shaft 5. I have. The second
The second output disk 44r of the toroidal transmission mechanism 8 is
The transmission output shaft 5 is positioned by a second bearing 47r provided between the enlarged diameter portion 5g formed integrally with the transmission output shaft 5 and the transmission case 22 and rotatably supporting the transmission output shaft 5.

Between the first output disk 44f and the second output disk 44r, there are first and second input disks 43f and 43f.
The input cams r are arranged close to each other such that the back faces each other, and an input cam 48 rotatable relative to the input disks 43f and 43r is disposed between the input disks 43f and 43r. Further, between the input cam 48 and the first and second input disks 43f, 43r, first and second cam rollers 49f, 49r are provided, respectively. Here, the first and second cam rollers 49f and 49r are connected to the input cam 48 and the first and second cam rollers.
When the input disks 43f, 43r are relatively rotated, the first and second input disks 43f, 43r have a function of generating a pressing force for pressing the first and second output disks 44f, 44r, respectively. , The first and second input disks 43f,
The larger the input torque to 43r, the larger the first and second input disks 43f, 43f of the first and second cam rollers 49f and 49r.
The pressing force on 43r increases.

Between the first and second input disks 43f and 43r, the transmission output shaft 5 is loosely fitted, and both ends are first and second, respectively.
An engagement member 50 that is spline-fitted with the first and second input disks 43f and 43r is disposed in a state of being in contact with the rear surfaces of the second input disks 43f and 43r. A disc spring 51 is interposed between the engaging member 50 and the second input disc 43r, and the first input disc 43f and the second input disc 43r are pre-pressed by the disc spring 51 in a direction in which they are separated from each other. It has become so. This disc spring 51
Abuts against the rear surface of the second input disk 43r and urges the second input disk 43r toward the second output disk 44r, while the urging reaction force causes the first input disk 4r via the engaging member 50.
3f is biased toward the first output disk 44f to apply a predetermined preload between the first input disk 43f and the first output disk 44f and between the second input disk 43r and the second output disk 44r. It has become.

Next, a hydraulic mechanism for tilting the first to fourth rollers 45a to 45d will be described. The first and second rollers 45a, 4
First and second trunnions 59 each rotatably supporting 5b.
a, 59b. These trunnions 59a, 59b (59c, 59d) correspond to "roller supporting members" described in the claims. And the first and second
The first and second rollers 45a and 45b are respectively provided by trunnions 59a and 59b via first and second eccentric shafts 60a and 60b, respectively.
Are rotatably supported. Further, the first and second trunnions 59a and 59b are respectively provided with first and second shaft members 61a and 61b extending so as to extend downward (in a direction perpendicular to the transmission output shaft 5). Have been.

An upper connecting member 62 is attached to the transmission case 22 slightly above the first and second rollers 45a and 45b. On the other hand, the first and second rollers 45a, 45
Below 5b, a lower connecting member 63 is attached to a partition wall 53 fixed to the transmission case 22. The lower connecting member 63 and the upper connecting member 62
They respectively correspond to the “first connecting member” and the “second connecting member” described in the claims. And, by the first and second shaft holes 65a and 65b formed in the upper connecting member 62,
Upper ends of the first and second trunnions 59a and 59b are rotatably supported via first and second upper spherical bushes 64a and 64b, respectively. On the other hand, the lower ends of the first and second trunnions 59a and 59b are respectively connected to the first and second lower spherical bushes 66a and 66b by the first and second shaft holes 67a and 67b formed in the lower connecting member 63. It is rotatably supported via 66b. The lower portions of the first and second shaft members 61a and 61b are connected to the upper housing 5 attached to the lower surface of the partition wall 53.
5 through the opening 55g of the upper housing 55
56 of the lower housing 56 attached to the lower surface of the
By g, it is rotatably supported via the first and second support bearings 54a and 54b.

In the partition wall portion 53, first and second hydraulic cylinders 76a and 76b are provided for operating the first and second trunnions 59a and 59b, respectively, and these first and second hydraulic cylinders are provided. 76a and 76b are vertically separated by a partition wall 53g which forms a part of the partition wall 53, respectively. The first and second upper pistons 77a and 77b are fitted in the upper half of the first and second hydraulic cylinders 76a and 76b, respectively, and the first and second lower pistons 78a and 78b are fitted in the lower half. It is inserted. Therefore, the first and second upper pistons 77a, 77b
And the first and second upper hydraulic chambers 79 by the
a, 79b are defined, while the first and second lower pistons 78a,
First and second lower hydraulic chambers 80a and 80b are defined by the 78b and the partition 53g, respectively.

Here, the first and second upper hydraulic chambers 79a, 79b
When the hydraulic pressure is applied to the first and second trunnions 59a and 59b, the first and second upper pistons 77a and 77b are used.
b is displaced upward, while the first and second lower hydraulic chambers 8 are displaced upward.
When hydraulic pressure is applied to the first and second trunnions 5a and 80b, the first and second lower pistons 78a and 78b cause the first and second trunnions 5 to move.
9a, 59b are displaced downward. When the first and second trunnions 59a and 59b are vertically displaced in this manner, the first and second rollers 45a and 45b are tilted in accordance with the displacement, and the first toroidal transmission mechanism 7 The gear ratio changes. In addition, the first and second trunnions 59a and 59b rotate around their axes. In order to synchronize the rotation of the first and second trunnions 59a, 59b, or to provide backup when one of the trunnions 59a, 59b fails, two interlocking wires 5 are connected to both trunnions 59a, 59b (59c, 59d).
7,58 are wound. The second toroidal transmission mechanism 8 is, of course, basically the same as the first toroidal transmission mechanism 7.

The first to fourth upper hydraulic chambers 79a to 79d and the first to fourth lower hydraulic chambers 80a to 80d are supplied with hydraulic pressure from a hydraulic valve V according to the operation state. I have. Since the hydraulic valve V is not a characteristic part of the present invention, a detailed description thereof will be omitted, but an ordinary hydraulic valve V in which a sleeve 83, a spool 84, a return spring 85, a rod 86, a pin 87, and the like are arranged in a valve housing 82. a valve, while being controlled by a stepping motor 88 which operates in accordance with signals from a control unit (not shown), the line pressure is introduced into the P ₁ port,
And a P ₂ ports and P ₃ port, a predetermined hydraulic pressure chamber 79a~7
The hydraulic pressure can be supplied to 9d and 81a to 80d. The hydraulic valve V is provided with a feedback mechanism 90.

Hereinafter, the two connecting members 62 and 63, which are characteristic parts of the present invention, and their mounting structure will be described. The upper coupling member 62 has a first upper positioning hole 68f formed at an intermediate portion between the first shaft hole 65a and the second shaft hole 65b, and a second upper positioning hole 68f formed at an intermediate portion between the third shaft hole 65c and the fourth shaft hole 65d. A positioning hole 68r is formed. The first support portion 69f formed integrally with the transmission case 22 is inserted into the first upper positioning hole 68f. A first roller lubrication member 70f is attached to the first support portion 69f using a first attachment member 71f. Also, the second upper positioning hole 6
An upper spherical bearing 75r attached to the second support 69r is inserted through 8r. Note that a second roller lubrication member 70r is attached to the second support portion 69r using a second attachment member 71r. Thus, the upper connecting member 62
Is formed by the first support portion 69f and the upper spherical bearing 75r.
It is fixed or positioned with respect to the transmission case 22.

The lower connecting member 63 has a first lower positioning hole 72f formed at an intermediate portion between the first shaft hole 67a and the second shaft hole 67b, and an intermediate portion between the third shaft hole 67c and the fourth shaft hole 67d. Part 2
A lower positioning hole 72r is formed. And the first,
In the second lower positioning holes 72f, 72r, first and second lower spherical bearings 73f, 73r fixed to the upper surface of the partition wall 53 using first and second mounting bolts 74f, 74r, respectively. It has been inserted. Thus, the lower connecting member 63 is fixed or positioned with respect to the partition wall 53 (the transmission case side) by the first and second lower spherical bearings 73f, 73r. The first support portion 69f, the upper spherical bearing 75r,
The first and second lower spherical bearings 73f, 73r correspond to the "insertion member" described in the claims.

As shown in FIGS. 6 and 7, in the lower connecting member 63, the first lower positioning hole 72f is inserted through the insertion member.
(Shaded portion) is formed in such a shape as to fit almost exactly. On the other hand, the second lower positioning hole 72r is, _{A 2} direction
(Left and right direction) just contact the insertion member (shaded area), A
_{In one} direction (front-back direction), the insertion member is an elongated hole having a predetermined clearance. On the other hand, in the upper connecting member 62, the first upper positioning hole 68f is
(Shaded area) and a large-diameter hole having a predetermined clearance. On the other hand, the second upper positioning hole 68r is, _{A 1}
Direction just in contact with the insertion member (hatched portion) in the (longitudinal direction), the A ₂ direction (lateral direction) is a long hole having a predetermined clearance between the insertion member (hatched portion). In addition,
FIG. 8 shows this elongated hole in an enlarged manner.

According to this configuration, the lower connecting member 63
Are positioned (fixed) in the front-rear direction and the left-right direction around the first lower positioning hole 72f.
Since the positioning around the 2r is performed only in the left-right direction, the lower connecting member 63 as a whole is positioned in the front-rear direction and the left-right direction, and the positioning accuracy is increased. In addition, since the second lower positioning hole 72r has a predetermined clearance in the front-rear direction, the first lower spherical bearing 73f and the second lower spherical bearing 73r fixed to the upper surface of the partition wall 53 are in the front-rear direction. Even when there is an assembly error, the assembly error can be absorbed. Note that, contrary to the present embodiment, the first lower positioning hole 72f may be an elongated hole. In this case, the conventional lower connecting member 1 shown in FIG.
In No. 10, such an assembling error cannot be absorbed, but if the assembling error is to be absorbed, one of the positioning holes must be increased in diameter, and the positioning accuracy is reduced. Further, since the conventional lower connecting member 120 shown in FIG. 12 cannot perform positioning in the left-right direction, the positioning accuracy is reduced.

The upper connecting member 62 is positioned in the front-rear direction around the second upper positioning hole 68r, but is not positioned around the first upper positioning hole 68f. Therefore, the entire upper connecting member 62 is positioned in the front-rear direction, but not in the left-right direction. For this reason, the upper connecting member 62 and the lower connecting member 63 can be relatively displaced to some extent in the left-right direction, and an assembly error or an arrangement error of each member can be effectively absorbed. Contrary to the present embodiment, the first upper positioning hole 68f may be an elongated hole and the second upper positioning hole 68r may be a large diameter hole. The size of the clearance between the first and second upper positioning holes 68f, 68r is preferably set so as to correspond to the maximum inclination generated in the upper connecting member 62.

In the above configuration, when the trunnion moves up and down for shifting, the connecting member can be tilted about the spherical bush. When the position of the roller changes due to an assembly error or a shake of the input / output disk, the trunnion does not shake in the front-rear direction but does shake in the left-right direction. In this case, according to the present invention, since the trunnion oscillates around the lower spherical bush, the trunnion hardly oscillates around the piston. Therefore, interference between the trunnion and the piston does not occur. In addition, since the upper connecting member can be displaced in the left-right direction, the right and left swing of the upper part of the trunnion is absorbed.
Here, "interference between the trunnion and the piston" means the following phenomenon. That is, FIGS.
As is clear from FIG. 5, the shaft members 61a to 61d of the trunnions 59a to 59d
The holes 7a to 77d penetrate. Therefore, when each of the trunnions 59a to 59d swings in the left-right direction, each of the shaft members 6
1a to 61d are inevitably pressed against a part of the inner peripheral surface of each of the holes, and exert excessive forces on each other. In this specification, this phenomenon is referred to as "interference between the trunnion and the piston". As described above, according to the present embodiment, it is possible to accurately position the connecting member with a simple structure, to absorb an assembly error of each member, and to prevent interference between the trunnion and the piston. it can.

[0041]

According to the present invention, according to the present invention, the first connecting member is connected to the output shaft axial direction (front-rear direction) and the direction perpendicular to this.
(Left-right direction) while the second connecting member is positioned only in the front-back direction and can be displaced in the left-right direction, so that the connecting member can be accurately positioned, and a set of members Attached errors can be absorbed.
In addition, since the run-out of the roller support member on the piston arrangement side is reduced, interference between the trunnion and the piston (see paragraph [0040] above) can be prevented.

[Brief description of the drawings]

FIG. 1 is an elevational side sectional view of a toroidal-type continuously variable transmission according to the present invention.

FIG. 2 is an explanatory plan sectional view of the toroidal-type continuously variable transmission shown in FIG. 1;

FIG. 3 is a sectional view of the toroidal type continuously variable transmission shown in FIG.
It is a line elevation line sectional explanatory drawing.

FIG. 4 is a BB diagram of the toroidal type continuously variable transmission shown in FIG. 1;
It is a line elevation sectional drawing.

FIG. 5 is a system configuration diagram of a transmission including the toroidal-type continuously variable transmission according to the present invention.

FIG. 6 is an explanatory plan view of a lower connecting member.

FIG. 7 is an explanatory plan view of an upper connecting member.

FIG. 8 is a view showing the shape of a long hole.

FIG. 9 is a diagram showing reaction forces acting on four rollers of the toroidal type continuously variable transmission.

FIG. 10 is an explanatory plan view of a conventional lower connection member.

FIG. 11 is an explanatory plan view of a conventional upper connection member.

FIG. 12 is an explanatory plan view of a conventional lower connection member.

FIG. 13 is an explanatory plan view of a conventional upper connection member.

[Explanation of symbols]

 C: Toroidal-type continuously variable transmission 5: Transmission output shaft 7: First toroidal-type transmission mechanism 8: Second toroidal-type transmission mechanism 22: Transmission case 43f, 43r: First and second input disks 44f, 44r First and second output disks 45a to 45d first to fourth rollers 59a to 59d first to fourth trunnions 62 upper connecting member 63 lower connecting members 68f, 68r first and second upper positioning holes 72f, 72r: first and second lower positioning holes 79a to 79d: first to fourth upper hydraulic chambers 80a to 80d: first to fourth lower hydraulic chambers

Claims (1)

(57) [Claims] 1. An input disk, an output disk arranged such that curved surfaces thereof face each other with respect to the input disk, and an input disk and an output disk which are in contact with the output disk and have a speed ratio corresponding to a tilt angle. In a toroidal-type continuously variable transmission in which first and second two toroidal-type transmission mechanisms, each including two rollers for transmitting torque from one disk to the other disk, are arranged in the axial direction of the output shaft. A roller supporting member for rotatably supporting these rollers and a piston for changing a tilt angle of the roller via the roller supporting member are provided for each roller of the first and second toroidal transmission mechanisms, respectively. First and second two connecting members for connecting these roller supporting members are arranged in a positional relationship such that all rollers are sandwiched therebetween, and the first connecting member is provided with a piston. The second connecting member is disposed on the side where the piston is not disposed, and the first connecting member is inserted into the first connecting member by passing the insertion member fixed to the fixing portion. Positioning 2
One positioning hole is formed, and one of the positioning holes has a shape that does not allow displacement in the output axis direction and the direction perpendicular to the output axis direction in the spread plane of the first connecting member. The other positioning hole is an elongated hole that is long in the axial direction of the output shaft, and the second connecting member is positioned by inserting the insertion member fixed to the fixing portion through the second connecting member. 2
One positioning hole is formed as a large-diameter hole having a predetermined clearance with the insertion member, and the other positioning hole is elongated in a direction perpendicular to the output shaft axis direction. A toroidal-type continuously variable transmission characterized by having a long hole.