JPH0634009A - Toroidal type continuously variable transmission - Google Patents

Abstract

(57) [Abstract] [Purpose] An object of the present invention is to reliably fix a wire and a roller support member in a toroidal type continuously variable transmission in which a wire is sprinkled around the outer circumference of each trunnion. [Structure] A first wire 91 is wound around the outer circumferences of the first to fourth trunnions 59a to 59d, and the first and second trunnions 5 are connected.
The second wire 92 is stretched between the 9a and 59b, and the third wire 9 is interposed between the third and fourth trunnions 59c and 59d.
Three are crossed over. First wire 91
Is wound around the second and third trunnions 59b and 59c once, and the fixing members 96f and 9f are secured by the inner portions 95f and 95r.
It is fixed to the second and third trunnions 59b and 59c via 6r, the circumferential lengths of the fixing members 96f and 96r are sufficiently secured, and the first wire 91 and the second and third trunnions 59b and 5r are formed.
9c is securely fixed. Therefore, even if the hydraulic mechanism fails, the rollers are prevented from being out of sync.

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 continuously variable transmission for an automobile, an input disk to which torque is input from the engine side and an output disk to output torque to the drive wheels are arranged coaxially with each other. Two rollers are provided which come into contact with both discs and transmit torque between both discs, so that a gear ratio corresponding to the tilt angle (tilt angle) of the rollers can be obtained. Where input / output disk,
If the torque load on each member such as the roller is too large, there arises a problem that the durability of each member decreases. Therefore, for example, two toroidal transmission units including input / output discs, rollers, etc. are provided, and torque is transmitted in parallel by both transmission units to reduce the torque load on each member. The transmission is often used.

In a toroidal type continuously variable transmission including two sets of such transmission units, roller support members for rotatably supporting the respective rollers are provided, and these roller support members are provided. Are collectively supported by a connecting member fixed to the transmission case so as to be rotatable about the axis and reciprocally movable in the axis direction. Then, when each roller support member is moved in the axial direction, each roller is tilted and the roller support member is rotated about its axis at a rotation angle corresponding to the tilt angle.

Here, the respective rollers are synchronized with each other by a hydraulic mechanism. However, when the hydraulic mechanism is broken or a strong impact force is applied from the outside, the synchronization of the rollers may be lost. is there. And
If the synchronization of the rollers is lost in this way, the behavior of the vehicle may change suddenly, or the transmission unit may be damaged. Therefore, a wire is wound around each roller supporting member, the wire is fixed to each roller supporting member, and the rotation of each roller supporting member is synchronized by this wire to back up the synchronization of the tilting of the roller, and the hydraulic pressure is adjusted. Even if the mechanism breaks down,
A toroidal type continuously variable transmission in which synchronous dislocations do not occur in each roller has been proposed.

Specifically, in a toroidal type continuously variable transmission in which the first transmission unit is provided with the first and second roller support members and the second transmission unit is provided with the third and fourth roller support members. , Wire between the first and second roller support members, between the second and third roller support members, between the third and fourth roller support members, and between the fourth and first roller support members, respectively. Another toroidal type continuously variable transmission has been proposed (see, for example, Japanese Utility Model Laid-Open No. 1-116246). In this case, since the roller supporting members connected by the wires are rotated in the opposite directions, the wires are used as a plow. However, in this case, since four wires are required, there is a problem that the number of parts is considerably increased.

Therefore, between the first and second roller support members,
A toroidal type stepless structure in which the wires are wound around the third to fourth roller support members respectively by piling and the wires are wound around the outer circumference of all the roller support members to reduce the number of parts by using three wires. Gearboxes have been proposed.
In this case, of the four roller support members, the two roller support members that rotate in a predetermined direction (for example, the first and third roller support members) are fixed to the wire, but rotate in the opposite direction. The remaining two roller support members (eg, the second,
The fourth roller support member) is adapted to be slidably engaged with the wire.

[0007]

However, in the toroidal type continuously variable transmission in which the wires are wound around the outer circumferences of the four roller supporting members as described above, the wires and the roller supporting members (the one fixed) are There is a problem that the fixation between them is insufficient.

That is, for example, as shown in FIG. 7, in the fixing portion 103 of the wire 100 and the roller supporting member 102, the fixing member 104 crimped to the wire 100 is fixed.
Are fitted into the notches 101 formed in the roller support member 102. In this case, the contact angle between the wire 100 and the roller support member 102 is about 90 °, but if the maximum rotation angle of the roller support member 102 is θ, the fixing member 104 does not separate from the notch 101. In order to obtain, the fixing member 104 must be set within the range of the angle α ′ (= 90 ° −2θ). Therefore, the fixing member 10
4 cannot be sufficiently secured and the wire 100
Caulking between the fixing member 104 and the fixing member 104 becomes insufficient, and the fixing becomes insufficient.

The present invention has been made to solve the above-mentioned conventional problems, and in a toroidal type continuously variable transmission in which a wire is wound around the outer periphery of each roller supporting member, the wire and the roller are provided. An object of the present invention is to provide a toroidal type continuously variable transmission that can be reliably fixed to a support member.

[0010]

In order to achieve the above object, the first invention of the present invention includes an input disk, an output disk arranged so that curved surfaces face the input disk, and an input disk. Two rollers for contacting the output disc and transmitting torque from one disc to the other disc at a gear ratio according to the tilt angle;
In a toroidal type continuously variable transmission in which two second transmission units are arranged in the direction of the output shaft axis, the rollers of the first and second transmission units are rotatably supported by the respective rollers. , A roller support member that rotates around its axis in conjunction with the tilting of the roller, and
A winding member that is wound around the outer periphery of one roller supporting member is provided, and the winding member is arranged in the same direction as one of the roller supporting members on the first speed change unit side and the roller supporting member. The winding member is fixed to the rotating roller supporting member on the side of the second speed change unit, and slidably engaged with the other two roller supporting members rotating in the opposite direction. In the two roller supporting members for fixing the roller supporting member, the winding member is wound around the roller supporting member once, and the fixing portion for fixing the winding member is formed at a position inside the outer circumference of the roller supporting member. A toroidal-type continuously variable transmission characterized by being provided.

A second invention is, in the toroidal type continuously variable transmission according to the first invention, a second winding member which is stretched over two roller supporting members of the first transmission unit, and a second winding member. A toroidal type continuously variable transmission characterized in that a second winding member, which is stretched around two roller supporting members of the second transmission unit, is provided.

[0012]

EXAMPLES Examples of the present invention will be specifically described below.
As shown in FIG. 5, in the transmission TM of the automobile,
The output torque of the engine 1 including the fourth cylinders # 1 to # 4 is transmitted to the transmission output shaft 5 via the torque converter 2 (torque converter 2), the gear reduction mechanism 3 including the planetary gear system, and the forward / reverse switching mechanism 4. A first transmission unit for outputting to is provided. Furthermore, the output torque of the engine 1 is
Switching clutch 6 and toroidal first speed change unit 7
And a toroidal type continuously variable transmission C having a second transmission unit 8 and a second transmission unit for outputting to the transmission output shaft 5. When the switching clutch 6 is in the off state, torque is transmitted via the first speed change portion, and when it is in the on state, the torque is transmitted via the second speed change portion.

Since the torque converter 2 has a strong torque increasing function, the first speed change portion is mainly used when a relatively large speed change ratio (torque ratio) is required at the time of starting or accelerating. The speed changer is mainly used when driving is performed at a relatively small speed change ratio such as during high speed running.

The specific structure of the transmission TM will be described below. First, the first transmission unit will be described. The torque converter 2 substantially includes a pump impeller 12, a turbine liner 13, and a stator 14. The pump impeller 12 is mounted on the engine output shaft 1 via the pump cover 15.
1 and is configured to rotate 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 portion (right end portion 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). Further, 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 the oil discharged from the pump impeller 12, rectifies the oil repelled by 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 substantially includes 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. Further, the first and second pinions 26 and 28 are rotatably supported by the carrier 30. The carrier 30 is
It is fixed to the second hollow shaft 21 fixed to the transmission case 22.

Then, the sun gear 25 and the first pinion 26
The front part of the gear meshes with the first pinion 26 and the reverse ring gear 27 meshes with each other to form a planetary gear system having a reverse rotation reduction function. In this planetary gear system, a torque in the reverse rotation direction 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 part of the pinion 26 and the second pinion 28 mesh with each other,
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 deceleration function. In this planetary gear system, the forward rotation direction torque that is 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 disc 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.
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 drive ring gear 29 to prevent the forward drive 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 speed change section is substantially a toroidal type continuously variable speed change gear including a switching clutch 6 for connecting and disconnecting the torque input to the second speed change section, and first and second speed change units 7 and 8. The machine C and the gear mechanism 35 that transmits torque from the switching clutch 6 to the toroidal type continuously variable transmission C. Here, the gear mechanism 35 sequentially engages the torque of the first hollow shaft 16, that is, the torque of the engine output shaft 11 when the switching clutch 6 is engaged, with the drive gear 37, the idle gear 38, and the driven gear 39. Is transmitted to the bypass shaft 40 via the drive gear 4 and the torque of the bypass shaft 40 is meshed with each other.
1 and the driven gear 42 to the toroidal type continuously variable transmission C.

The toroidal type continuously variable transmission C includes a first transmission unit 7 arranged on the front side (left side in FIG. 5) so as to surround the transmission output shaft 5 and a second transmission unit arranged on the rear side. 8 and. Here, the first and second transmission units 7 and 8 are arranged symmetrically in the front and rear, but since the configurations and functions of both are basically the same, the corresponding members have the same reference numerals. In principle, the first
Each member of the speed change unit 7 is given a subscript f, and each member of the second speed change unit 8 is given a subscript r. However, with respect to the members such as rollers, two of which are arranged in each of the speed change units 7 and 8, it is not possible to distinguish only by the subscripts f and r. A and b are attached, and subscripts c and d are attached to the respective members arranged on the left and right of the second transmission unit 8. Therefore,
In the following, the description made for one member will in principle also apply to other members having the same number but different subscripts.

The first transmission unit 7 includes a transmission output shaft 5
A first input disc 43f loosely fitted around, a first output disc 44f fixed to the transmission output shaft 5, and a first output disc 44f.
First and second rollers 45a and 45b for transmitting the torque of the input disk 43f to the first output disk 44f are provided. The first input disk 43f is driven by the driven gear 4
The input cam 48 to which 2 is attached is engaged via the first cam roller 49f, and the input cam 48 is strongly pressed against the first input disc 43f as the input torque to the first input disc 43f is larger. Has become.

The first and second rollers 45a and 45b are rotatable about the axis Y, and their peripheral surfaces are curved surfaces of the first input disk 43f and the first output disk 4 respectively.
It is in contact with the curved surface of 4f. Therefore, the torque (rotation) of the first input disk 43f is equal to that of the first and second rollers 45.
It is adapted to be transmitted to the first output disk 44f via a and 45b. Here, the gear ratio in 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 in contact with the first and second rollers 45a and 45b.
₂ and the ratio R ₂ / R ₁ of the radius R ₁ of the first input disk 43f.

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

The specific structure of the toroidal type continuously variable transmission C will be described below. As shown in FIG. 3, in the first transmission unit 7, the first output disc 44f is spline-fitted to the transmission output shaft 5. Further, the first output disc 44f is positioned by the ring-shaped positioning tool 46 fitted to the transmission output shaft 5,
It is rotatably supported by the transmission case 22 via a bearing 47f. The second output disk 44r of the second transmission unit 8 is provided between the enlarged diameter portion 5g formed integrally with the transmission output shaft 5 and the transmission case 22 to rotate the transmission output shaft 5. It is positioned by a second bearing 47r that supports it freely.

Between the first output disc 44f and the second output disc 44r, there are first and second input discs 43f, 43.
The r's are arranged close to each other so that their rear surfaces face each other, and an input cam 48 which is rotatable relative to the input disks 43f, 43r is arranged between the input disks 43f, 43r. Then, first and second cam rollers 49f and 49r are provided between the input cam 48 and the first and second input disks 43f and 43r, 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 and 43r rotate relative to each other, it has a function of generating a pressing force that presses the first and second input disks 43f and 43r toward the first and second output disks 44f and 44r, respectively. , The first and second input disks 43f,
The greater the input torque to 43r, the first and second input discs 43f, 43f by the first and second cam rollers 49f, 49r.
The pressing force on 43r is designed to increase.

A transmission output shaft 5 is loosely fitted between the first and second input disks 43f and 43r, and both ends thereof are respectively connected to the first and second input disks 43f and 43r.
An engagement member 50, which is spline-fitted to the first and second input disks 43f and 43r, is arranged in a state of being brought into contact with the back 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 disc spring 51 preloads the first input disc 43f and the second input disc 43r in a direction in which they are separated from each other. It has become so. This disc spring 51
Contacts the back surface of the second input disk 43r and urges the second input disk 43r toward the second output disk 44r, and the urging reaction force of the second input disk 43r causes the first input disk 4r to pass through the engaging member 50.
3f is urged toward the first output disc 44f to apply a predetermined preload between the first input disc 43f and the first output disc 44f and between the second input disc 43r and the second output disc 44r. It is like this.

Next, a hydraulic mechanism for tilting the first to fourth rollers 45a to 45d will be described. As shown in FIG. 4, the first transmission unit 7 is provided with first and second trunnions 59a and 59b that rotatably support the first and second rollers 45a and 45b, respectively. The trunnions 59a, 59b (59c, 59d) correspond to the "roller support member" described in the claims. And
The first and second trunnions 59a and 59b rotatably support the first and second rollers 45a and 45b via the first and second eccentric shafts 60a and 60b, respectively. Also, the first
For the second trunnions 59a and 59b, these should be placed below, respectively.
First and second shaft members 61a and 61b are attached that extend in the direction (perpendicular to the transmission output shaft 5).

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, 4
Below 5b, a lower connecting member 63 is attached to the partition wall portion 53 fixed to the transmission case 22. Then, the first and the second formed on the upper connecting member 62
Due to the shaft holes 65a and 65b, the upper ends of the first and second trunnions 59a and 59b are respectively attached to the first and second upper spherical bushes 6.
It is rotatably supported via 4a and 64b. On the other hand,
First and second shaft holes 67a, 6 formed in the lower connecting member 63
7b, the first and second trunnions 59a and 59b, respectively.
Has a lower end portion rotatably supported via first and second lower spherical bushes 66a and 66b. Further, the lower portions of the first and second shaft members 61a and 61b penetrate the opening 55g of the upper housing 55 attached to the lower surface of the partition wall portion 53 to attach the lower housing to the lower surface of the upper housing 55. It is rotatably supported by the recess 56g of 56 through 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. These first and second hydraulic cylinders are provided. Each of 76a and 76b is vertically partitioned by a partition wall portion 53g that forms a part of the partition wall portion 53. The first and second upper pistons 77a and 77b are fitted in the upper half portions 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 portions. It has been inserted. Therefore, the first and second upper pistons 77a, 77b
The first and second upper hydraulic chambers 79 by the partition wall 53g and the partition wall 53g, respectively.
a and 79b are defined, while the first and second lower pistons 78a,
The first and second lower hydraulic chambers 80a and 80b are defined by 78b and the partition 53g, respectively.

Here, the first and second upper hydraulic chambers 79a, 79b
When hydraulic pressure is applied to the first and second upper pistons 77a and 77b, the first and second trunnions 59a and 59a
b is displaced upward, while the first and second lower hydraulic chambers 8 are
When hydraulic pressure is applied to 0a and 80b, the first and second trunnions 5 are moved by the first and second lower pistons 78a and 78b.
9a and 59b are displaced downward. When the first and second trunnions 59a and 59b are displaced in the vertical direction in this way, the first and second rollers 45a and 45b are tilted according to the displacement amount accordingly, and the first toroidal transmission mechanism 7 is moved. The gear ratio of is changed. Along with this, the first and second trunnions 59a and 59b are adapted to rotate around their axes. Further, in order to back up the synchronization of the rotations of the first and second trunnions 59a and 59b, first to third wires 91 to 93 to be described later are provided for the respective trunnions 59a to 59d. . Although not shown in detail, the second toroidal transmission mechanism 8
Of course, basically, it is basically the same as the first toroidal transmission mechanism 7.

The upper connecting member 62 is provided with a first upper positioning hole 68f at an intermediate portion between the first shaft hole 65a and the second shaft hole 65b, while a third shaft hole and a fourth shaft hole (not shown) are formed. A second upper positioning hole is formed in the middle of the hole. The support portion 69f integrally formed with the transmission case 22 is inserted through the first upper positioning hole 68f. The roller lubrication member 69f is attached to the support portion 69f using the attachment member 71f. Note that the second upper positioning hole side also has substantially the same configuration. in this way,
The upper coupling member 62 is fixed or positioned with respect to the transmission case 22 around the first and second upper positioning holes.

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. A second lower positioning hole is formed in the middle of the four-axis hole. A first lower bearing 73f fixed to the upper surface of the partition wall portion 53 with a mounting bolt 74f is inserted through the first lower positioning hole 72f. The second lower positioning hole side also has the same configuration. As described above, the lower coupling member 63 is fixed or positioned with respect to the partition wall portion 53 (transmission case side) by the first and second lower bearings.

Hereinafter, the first to third wires 91 to 93 which are provided on the first to fourth trunnions 59a to 59d and which are characteristic of the present invention will be described. As shown in FIG. 1 and FIG. 2, the first wire 91 is stretched around the outer peripheral portions near the lower ends of the first to fourth trunnions 59a to 59d. Then, on the slightly upper side of the first wire 91, the second wire 92 is crossed between the first trunnion 59a and the second trunnion 59b, and the third trunnion 59c.
A third wire 93 is laid between the and the fourth trunnion 59d by a cross. The first to third wires 91 to 93 correspond to the "winding member", the "second winding member", and the "third winding member" described in the claims, respectively. .

The first wire 91 has a second trunnion 59b and a third trunnion 5 which rotate in the same direction during gear shifting.
It is wound once around each of 9c and 9c.
And, to the second trunnion 59b of the first wire 91,
A front side fixing member 96f is caulked to the inner side portion 95f of the portion wound only around the circumference, that is, a portion facing the third trunnion 59c. The front side fixing member 96f is formed on the second trunnion 59b. It is fitted in the cutout portion 98f. Also, of the first wire 91,
A rear fixing member 96r is attached by caulking to an inner portion 95r of a portion wound around the third trunnion 59c for one round, that is, a portion facing the second trunnion 59b, and the rear fixing member 96r is 3 trunnions 5
It is fitted in a rear notch 98f formed in 9c.

On the other hand, the first wire 91 is not wound around the first trunnion 59a and the fourth trunnion 59d. Then, slip members 97f and 97r made of a low friction material such as Teflon are attached to the contact portions between the first wire 91 and the first and fourth trunnions 59a and 59d, respectively. Therefore, substantially no frictional force or engaging force acts between the first wire 91 and the first and fourth trunnions 59a and 59d. Therefore, the first wire 91 has a function of synchronizing the rotation only between the second and third trunnions 59b and 59c.

The second wire 92 is provided as a hook because the first and second trunnions 59a and 59b rotate in opposite directions during gear shifting. In addition, the second wire 92 is fixed to the first and second trunnions 59a and 59b, respectively.
It is fixed using 4. Therefore, the synchronization of the first and second trunnions 59a and 59b is backed up by the second wire 92. Similarly, the third wire 93 is also provided as a hook because the third and fourth trunnions 59c and 59d rotate in opposite directions at the time of shifting. The third wire 93 is fixed to the third and fourth trunnions 59c and 59d using fixing members (not shown). Therefore, the synchronization of the third and fourth trunnions 59c and 59d is backed up by the third wire 93.

Therefore, the second and third trunnions 59b,
59c is backed up by the first wire 91 for synchronization, the first and second trunnions 59a, 59b are backed up for synchronization by the second wire 92, and the third and fourth trunnions 59c, 59d are backed up by the third wire 93. Since the synchronization is backed up, eventually the first to fourth trunnions 5
The entire synchronization of 9a-59d is backed up. Therefore, even if the hydraulic mechanism fails, the first to fourth
The synchronization failure between the rollers 45a to 45d does not occur, and the reliability of the toroidal type continuously variable transmission C is improved.

By the way, as described above, the first wire 91
Is wound around the second trunnion 59b and the third trunnion 59c once, and each fixing member 9
6f and 96r are fixed to the second and third trunnions 59b and 59c by the inner portions 95f and 95r. Therefore, the circumferential lengths of the fixing members 96f and 96r can be sufficiently secured, the first wire 91 and both fixing members 96f and 96r can be firmly swaged, and the first wire 91 and the second and the second 3 trunnions 5
The 9b and 59c can be securely fixed.

That is, as shown in FIG. 6, in the second trunnion 59b, the front fixing member 96f does not interfere with the portion of the first wire 91 extending in the first trunnion direction or the fourth trunnion direction. Within range (almost 1
It can be rotated by 80 °. Therefore, if the maximum rotation angle of the second trunnion 59b is θ, the front side fixing member 96f can be arbitrarily set within the range of a relatively large angle α (= 180 ° −2θ). In the example shown in FIG. 6, β is set to be smaller than α. For this reason,
It is possible to secure a sufficient circumferential length of the front side fixing member 96f. As described above, according to this embodiment, the first
The wire 91 and the second and third trunnions 59b, 59c can be securely fixed, and even if the hydraulic mechanism fails, the synchronous collapse of the first to fourth rollers 45a to 45d is surely prevented. be able to.

[0041]

According to the first aspect of the invention, the winding member is wound around the predetermined roller supporting member once, and the fixing portion between the winding member and the roller supporting member is arranged inside. Therefore, the circumferential length of the fixed portion can be increased. For this reason, the winding member and the roller supporting member can be reliably fixed, and even if the hydraulic mechanism fails, it is possible to reliably prevent the synchronous collapse of the rollers.

According to the second invention, basically, the same operation and effect as those of the first invention can be obtained. Further, the second winding member backs up the synchronization between the two roller supporting members of the first transmission unit, and the third winding member backs up the synchronization between the two roller supporting members of the second transmission unit. Therefore, in the event of a hydraulic mechanism failure or the like, it is possible to more effectively prevent the synchronous collapse of each roller.

[Brief description of drawings]

FIG. 1 is a front elevation cross-sectional explanatory view around a second trunnion of a toroidal type continuously variable transmission according to the present invention.

FIG. 2 shows a first of the toroidal type continuously variable transmission shown in FIG.
It is a plane cross-sectional explanatory view seen from the lower side near the wire.

3 is a plan cross-sectional explanatory view of the toroidal type continuously variable transmission shown in FIG. 1 as viewed from above.

FIG. 4 is a front elevation cross-sectional explanatory view of the toroidal type continuously variable transmission according to the present invention.

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

FIG. 6 is a schematic view of an engaging portion between a first wire and a second trunnion.

FIG. 7 is a schematic view of an engaging portion of a wire and a roller supporting member of a conventional toroidal type continuously variable transmission.

[Explanation of symbols]

 C ... Toroidal type continuously variable transmission 5 ... Transmission output shaft 7 ... First transmission unit 8 ... Second transmission unit 43f, 43r ... First and second input disks 44f, 44r ... First and second output disks 45a- 45d ... 1st-4th roller 59a-59d ... 1st-4th trunnion 91-93 ... 1st-3rd wire 96f ... Front side fixing member 96r ... Rear side fixing member

Claims (2)

[Claims] 1. An input disc, an output disc arranged such that curved surfaces face each other with respect to the input disc, and a gear ratio according to a tilt angle by contacting the input disc and the output disc. A toroidal-type continuously variable transmission in which two first and second transmission units having two rollers for transmitting torque from one disc to the other disc are arranged in an output shaft axial direction, A roller supporting member that rotatably supports the rollers of the second speed change unit and that rotates about the axis thereof in conjunction with tilting of the rollers, and these four roller supporting members. And a winding member that is wound around the outer periphery of the roller, and the winding member rotates in the same direction as one of the roller supporting members on the first speed change unit side While being fixed to the roller supporting member on the side of the second speed changing unit, it is slidably engaged with the other two roller supporting members that rotate in the opposite direction, and fixes the winding member. In the two roller support members that
The winding member is wound around the roller supporting member once, and the fixing portion for fixing the winding member is formed at a position inside the outer periphery of the roller supporting member. Gearbox. 2. The toroidal type continuously variable transmission according to claim 1, wherein a second winding member that is stretched over the two roller supporting members of the first speed change unit, and a second speed change gear. A toroidal type continuously variable transmission characterized in that a third winding member that is stretched over the two roller supporting members of the unit is provided.