JP3308331B2 - 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 stopper for a roller supporting member of a toroidal type continuously variable transmission.

[0002]

2. Description of the Related Art As a transmission mounted on an automobile, there is known a toroidal type continuously variable transmission capable of continuously changing the rotation of an engine and transmitting the rotation to an output shaft. The toroidal-type continuously variable transmission includes an input disk that is rotated by inputting engine torque, an output disk that is coaxially opposed to the input disk and outputs torque to the drive wheel side, A roller for transmitting torque from the input disk to the output disk in contact therewith. The roller is rotatably supported by a roller supporting member, and the roller tilting angle (or the contact position between the roller and both disks) is changed by vertically displacing the roller supporting member in the axial direction thereof. The gear ratio can be obtained steplessly according to the tilt angle.

The roller supporting member is supported by a connecting member fixed (positioned) to the transmission case via a spherical bush so as to be rotatable about its axis and reciprocally movable in the axial direction. It has become. By moving this roller support member in its axial direction,
As each roller tilts, the roller support member rotates around its axis at a rotation angle corresponding to the tilt angle (for example, Japanese Utility Model Laid-Open No. 1-116246).

[0004] Each roller supporting member is operated by a hydraulic mechanism. However, due to failure of the hydraulic mechanism or other mechanical parts or disturbance of control, the roller supporting member exceeds the normal allowable use range. The roller may rotate, and in such a case, the roller may come off the input disk and the output disk. In order to avoid such a situation, the toroidal type continuously variable transmission is usually provided with a stopper member for preventing the roller support member from rotating beyond a predetermined range.

[0005]

In the conventional toroidal-type continuously variable transmission, the stopper member is fastened to the valve body (partition wall) together with the spherical bush using one fastening bolt. . However, with such a stopper structure, the stopper member easily rotates around the bolt when the stopper member is assembled, and it is difficult to position the stopper member in the rotation direction. Further, when a large force is applied to the stopper member from the roller support member, the stopper member may rotate around the fastening bolt, and may not function sufficiently as a stopper. Further, since the connecting member is sandwiched between the valve body and the stopper, there is a problem that the assembling property is poor.

The present invention has been made to solve the problem of the stopper member of the conventional toroidal type continuously variable transmission, and prevents the roller support member from rotating out of an allowable range. It is another object of the present invention to provide a toroidal-type continuously variable transmission that can improve the assemblability of a stopper member or a connecting member.

[0007]

In order to achieve this object, a toroidal type continuously variable transmission according to the present invention comprises an input disk, an output disk, and a pair of rotary disks which are in rotary contact with both the input disk and the output disk. A roller, a pair of roller support members rotatably supporting the roller and rotatable about a rotation shaft portion, and movable in the direction of the rotation shaft portion; and a roller support member movable in the direction of the rotation shaft portion. A toroidal-type continuously variable transmission having a hydraulic mechanism for moving the roller and a pair of connecting members provided on the valve body side and the other side with the roller interposed therebetween and supporting the roller supporting member. A columnar stopper that defines a tilt limit of the support member is arranged on at least one of the coupling members on the rotation trajectory of each roller support member. That.

A toroidal type continuously variable transmission according to a second aspect of the present invention provides an input disk, an output disk, a plurality of rollers that are in rotational contact with both the input disk and the output disk, and rotatably supports the rollers. A roller support member that is rotatable about the rotation shaft portion and is movable in the direction of the rotation shaft portion, a hydraulic mechanism that moves the roller support member in the direction of the rotation shaft portion, and a valve body that sandwiches the roller. In a toroidal-type continuously variable transmission having a pair of connecting members provided on the other side and supporting a roller supporting member and a wire which is bridged between the rollers and regulates the rotation direction of the roller, A cylindrical stopper that defines a tilt limit is provided on at least one of the connecting members on the rotation trajectory of each roller supporting member, and overlaps the wire in the vertical direction. Characterized in that the placed.

[0009]

As shown in FIG. 2, an automobile transmission TM includes an engine 1 having first to fourth cylinders # 1 to # 4.
Is provided to a transmission output shaft 5 via a torque converter 2, a gear reduction mechanism 3 including a planetary gear mechanism, and a forward / reverse switching mechanism 4. Further, the output torque of the engine 1 is output to the transmission output shaft 5 via the switching clutch 6 and the toroidal type continuously variable transmission C including the first toroidal type transmission mechanism 7 and the second toroidal type transmission mechanism 8. A second transmission unit is provided. When the switching clutch 6 is in the off state, torque is transmitted via the first transmission section, and when it is in the on state, torque is transmitted via the second transmission section.

The first transmission section is used mainly when the torque converter 2 has a strong torque increasing function and thus requires a relatively large speed ratio, such as when starting or accelerating, and the second transmission section. Is mainly used when the operation is performed at a relatively small gear ratio, such as during high-speed running. Hereinafter, a specific structure of the transmission TM will be described. [First Transmission Section] The torque converter 2 includes a pump impeller 12, a turbine liner 13, and a stator 14. The pump impeller 12 includes the pump cover 1.
5, and is connected to the engine output shaft 11 so as to rotate integrally with the engine output shaft 11. further,
A first hollow shaft 16 is coaxially connected to the pump impeller 12, and a rear end portion of the first hollow shaft 16 (see FIG. 2).
(The right end) is connected to the oil pump 17. 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 the one-way clutch 19. This second hollow shaft 21
Are fixed to the transmission case 22.

The torque converter 2 includes a pump impeller 1
The process of rotating the turbine liner 13 with the oil discharged from the turbine liner 2, rectifying the oil rebounding from the turbine liner 13 with the stator 14, and increasing the rotation of the pump impeller 12 with the rectified oil, is repeated. At 18, a torque larger than the torque of the engine output shaft 11 is output.

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

The sun gear 25 and the front portion of the first pinion 26 mesh with each other, and the first pinion 26 and the reverse ring gear 27 mesh with each other, which constitute a planetary gear mechanism having a reverse rotation reduction function. In this planetary gear mechanism, a reverse rotation torque larger than the torque input to the sun gear 25 is output from the reverse ring gear 27.

The rear portion of the first pinion 26 meshing with the sun gear 25 meshes with the second pinion 28,
Further, the second pinion 28 meshes with the forward ring gear 29, and these form a planetary gear mechanism having a forward rotation reduction function. In this planetary gear mechanism, 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 includes a reverse clutch 3
1, clutch case 32, 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 below. When reverse clutch 31 is engaged, reverse ring gear 27 and clutch case 32 are connected, and torque of reverse ring gear 27 is transmitted to 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. [Second Transmission Section] The second transmission section is a toroidal type including a switching clutch 6 for intermittently inputting torque to the second transmission section, and first and second toroidal type transmission mechanisms 7 and 8. It comprises a continuously variable transmission C and a gear mechanism 35 for transmitting torque from the switching clutch 6 to the toroidal type continuously variable transmission C.

When the switching clutch 6 is engaged, the gear mechanism 35 sequentially engages the torque of the first hollow shaft 16, ie, the torque of the engine output shaft 11, with the driving gear 37, the idle gear 38, and the driven gear. 39
, 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. I have.

The toroidal type continuously variable transmission C is disposed on the front side (left side in FIG. 2) of the vehicle so as to surround the transmission output shaft 5 and on the rear side. A second toroidal transmission mechanism 8.
Although the first and second toroidal transmission mechanisms 7 and 8 are arranged symmetrically in the front-rear direction, since the configurations and functions of both are the same, in each figure, corresponding members are denoted by the same reference numerals. 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, two members (for example, rollers) provided in each of the toroidal transmission mechanisms 7 and 8 are arranged on the left and right sides of the first toroidal transmission mechanism 7 instead of the suffixes f and r. Each member is given a suffix a, b, and the second toroidal transmission mechanism 8
Are assigned subscripts c and d, respectively. Therefore, in the following description, the description given for a member also applies to other members having the same numbers and different subscripts.

A first input disk 43f loosely fitted around the transmission output shaft 5 is attached to the first toroidal transmission mechanism 7;
First output disk 44f fixed to transmission output shaft 5
The first roller 45a and the second roller 4 for transmitting the torque of the first input disk 43f to the first output disk 44f.
5b is provided. The first input disk 43f is engaged with an input cam 48 to which the driven gear 42 is attached via a first cam roller 49f. As the input torque to the first input disk 43f increases, the input cam 48 It is configured to be strongly pressed against one input disk 43f.

Each of the first roller 45a and the second roller 45b is formed so as to be rotatable around an axis Y, and its peripheral surface is formed between the curved surface of the first input disk 43f and the curved surface of the first output disk 44f. Abutting. As a result, the torque of the first input disk 43f is reduced by the first and second rollers 4f.
The signal is transmitted to the first output disk 44f via the first and second output disks 44a and 45b. Here, the first input disk 43
f in the torque transmission from the first output disk 44f to the first output disk 44f is determined by the radius R ₂ 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.
Once 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 roller 45a and the second roller 45b and the disks 43f, 44f is determined by the tilt angle of the first roller 45a and the second roller 45b, as described later. . The gear ratio can be arbitrarily set within a predetermined range by changing the tilt angle with a hydraulic mechanism described later. The structure of the second toroidal transmission mechanism 8 is basically the same as that of the first toroidal transmission mechanism 7.

Hereinafter, a specific structure of the toroidal type continuously variable transmission C will be described. As shown in FIG. 3, in the first toroidal transmission mechanism 7, the first output disk 44f is spline-coupled 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. Have been. The second output disk 44r of the second toroidal type transmission mechanism 8 is provided between the enlarged diameter portion 5g formed integrally with the transmission output shaft 5 and the transmission case 22, and the transmission output shaft 44r is provided. 5 is rotatably supported by a second bearing 47r.

Between the first output disk 44f and the second output disk 44r, there are first and second input disks 43f, 43f.
The input cams 43r are arranged close to each other with their backs facing each other, and an input cam 48 rotatable relative to the input disks 43f and 43r is arranged between the input disks 43f and 43r. Then, between the input cam 48 and the first and second input disks 43f and 43r, the first and second cam rollers 4 are respectively provided.
9f and 49r are interposed. 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 relatively,
The first and second input disks 43f and 43r are respectively connected to the first and second input disks 43f and 43r.
It has a function of generating a pressing force for pressing against the second output disks 44f, 44r, and the larger the input torque to the first and second input disks 43f, 43r, the larger the first and second cam rollers 49f, 49r. , The pressing force on the first and second input disks 43f and 43r is increased.

The first and second input disks 43f and 43r are loosely fitted to the transmission output shaft 5 and both ends are in contact with the rear surfaces of the first and second input disks 43f and 43r, respectively. An engagement member 50 is spline-fitted to the first and second input disks 43f, 43r. A disc spring 51 is interposed between the engagement 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 away from each other. It has become so. The disc spring 51 abuts against the back 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 43r via the engaging member 50. 43f to the first output disk 44f side,
Between the first input disk 43f and the first output disk 44f, and between the second input disk 43r and the second output disk 4f.
A predetermined preload is applied to the preload 4r.

Next, a hydraulic mechanism for tilting the first to fourth rollers 45a to 45d will be described. FIG.
As shown in (1), the first toroidal type speed change mechanism 7 is provided with first and second roller support members 59a and 59b that rotatably support the first and second rollers 45a and 45b, respectively. Then, the first and second roller support members 59a, 5
9b, the first and second eccentric shafts 60a, 60b, respectively.
(Only 60b is shown) through the first and second rollers 45
a and 45b are rotatably supported. Also,
First and second shaft members 61a and 61b are attached to the second roller support members 59a and 59b, respectively, and extend to extend downward (in a direction perpendicular to the transmission output shaft 5). .

Slightly above the first and second rollers 45a and 45b, the transmission case 22
2 are installed. On the other hand, the first and second rollers 45
A lower connecting member 63 is attached to a valve body (partition wall) 53 fixed to the transmission case 22 below a and 45b. Then, the upper connecting member 62
The first and second roller support members 5 are respectively provided by first and second shaft holes 65a and 65b (only 65b is shown) formed in
Upper ends of 9a and 59b are rotatably supported via first and second upper spherical bushes 64a and 64b (only 64b is shown). On the other hand, the first and second shaft holes 67a and 67b formed in the lower connecting member 63 allow the first and second shaft holes 67a and 67b to be respectively provided.
The lower ends of the second roller support members 59a, 59b are
It is rotatably supported via the second lower spherical bushes 66a, 66b. In addition, the first and second shaft members 61a,
The lower portion of 61b penetrates through the opening 55g of the upper housing 55 attached to the lower surface of the partition wall portion 53, and a bearing (not shown) in the concave portion 56g of the lower housing 56 attached to the lower surface of the upper housing 55.
It is rotatably supported via.

The upper connecting member 62 and the lower connecting member 63 are connected by a plurality of coil springs 97 and are urged in a direction in which they are attracted to each other. It is prevented from occurring. In the valve body (partition wall portion) 53, first and second hydraulic cylinders 76a and 76b are provided for operating the first and second roller support members 59a and 59b, respectively. Two hydraulic cylinders 76a, 76b
Are partition walls 53g each forming a part of the valve body 53.
It is divided up and down by. The first and second upper pistons 77a and 77b are fitted in the upper halves 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. For this reason, the first and second upper pistons 77a, 77b
And the first and second upper hydraulic chambers 7 by the
The first and second lower pistons 78a and 78b and the partition wall 53g define first and second lower hydraulic chambers 80a and 80b, respectively.

Here, the first and second upper hydraulic chambers 79a, 79
When the hydraulic pressure is applied to the first and second roller supporting members 59a and 59b, the first and second upper pistons 77a and 77b displace the first and second roller supporting members 59a and 59b upward.
When hydraulic pressure is applied to the second lower hydraulic chambers 80a and 80b, the first and second roller support members 59a and 59b are displaced downward by the first and second lower pistons 78a and 78b. ing. When the first and second roller supporting members 59a and 59b are vertically displaced in this manner, the first and second rollers 45a and 45b are tilted in accordance with the amount of displacement, and the first toroidal member is displaced. The gear ratio of the mold transmission mechanism 7 changes. Accordingly, the first and second roller support members 59a, 59b
Is adapted to rotate about its axis.

A wire 58 is wound around the outer periphery of the first to fourth roller supporting members 59a to 59d slightly above the upper end surface of the lower connecting member 63. This wire 5
Reference numeral 8 denotes a first and second roller support member 59 when the hydraulic mechanism fails.
This is for preventing the occurrence of synchronization loss of the rotation of the a and 59b. Hydraulic pressure is supplied from the hydraulic valve V to the first and second upper hydraulic chambers 79a and 79b and the first and second lower hydraulic chambers 80a and 80b according to the operation state. Although the hydraulic valve V is not a feature of the present invention and will not be described in detail,
A sleeve 83 and a spool 8 are provided in the valve housing 82.
4, a hydraulic valve return spring 85 and the rod 86 or the like is disposed, is controlled by a stepping motor 88 which operates in accordance with signals from a control unit (not shown), while the line pressure is introduced into the P ₁ port , predetermined hydraulic pressure chamber 79a and a P ₂ ports and P ₃ port, 79b, 80a, so as to supply the hydraulic pressure to 80b.

The lower connecting member 63 has a lower positioning hole 68f formed at an intermediate portion between the first shaft hole 67a and the second shaft hole 67b (only 67b is shown). This lower positioning hole 6
A supporting portion 69f is inserted through the lower lubrication member 8f via a lower spherical bearing 73f.
0f is attached. This roller lubricating member 70f
A pair of oil outlets 72 are provided at the tip of
Lubricating oil is supplied from the oil outlet 72 toward a tilting surface between the rollers 45a and 45b and the input and output disks. At the same time, the lower connecting member 63
Is fixed or positioned with respect to the valve body 53 by the lower spherical bearing 73f.

As described above, when the hydraulic pressure is supplied from the hydraulic valve V to the predetermined hydraulic chambers 79a, 79b, 80a, 80b and the first and second roller support members 59a, 59b are displaced in the vertical direction, the first and second roller support members 59a, 59b are displaced vertically. As the second rollers 45a and 45b tilt, the first and second roller support members 59
a and 59b are axes 59a1 and 59b1 (see FIG. 4).
Rotate around. The first and second roller support members 5
Four stopper members 100f are attached to the upper surface of the lower connecting member 63 by fastening bolts 101, respectively, in order to prevent the rotation of the 9a and 59b outside the normal use range.

The four stopper members 100f are provided so as to have a height that overlaps the wire 58 in the vertical direction. That is, the stopper member 100
f is arranged in a space (dead space) generated by arranging the wire 58, and the space of the toroidal type continuously variable transmission is effectively used. As shown in FIG. 4, the stopper member 100f has a columnar shape, and has a space 102 (see FIG. 1) large enough to embed the entire fastening bolt 101 in the axial direction. The fastening bolt 101 is attached so as to be embedded in the space 102. Therefore, the fastening bolt 101 is not exposed outside the stopper member 100f.

The stopper member 100f includes a lower spherical bearing 73.
f are disposed on both sides of the lower positioning holes 68f and 68r for supporting f. Notches 90a to 90d of a predetermined angle are formed on the outer periphery of the roller support members 59a to 59d. The cylindrical stopper member 100f has an outer peripheral surface on the locus of the roller support members 59a to 59d.
It is arranged at a position such that it contacts the notches 90a to 90d. With this arrangement, the roller support members 59a to 59d are prevented from rotating out of the allowable rotation range due to the notches 90a to 90d contacting the stopper member 100f.

It should be noted that in FIG.
Reference numerals a and 59b are at the extreme positions of the allowable rotation range, and the rotation is stopped by the stopper member 100f. On the other hand, the roller support members 59c and 59d are located within the allowable rotation range. In this embodiment, the stopper member 100f is attached to the lower connecting member 63, but may be attached to the upper surface of the upper connecting member 62. However, as described above, by attaching to the lower connecting member 63, it is possible to effectively use the dead space generated by the arrangement of the wires 58.

[0034]

As described above, the stopper member in the toroidal type continuously variable transmission according to the present invention can reliably function as a stopper, and the stopper member has a cylindrical shape. The accuracy of the mounting position can be improved as compared with the case where the shape is formed into another shape (for example, a rectangular shape or a polygonal shape).
That is, when the stopper member is formed in, for example, a rectangular shape, the flat portion of the rectangular stopper member and the flat portion of the roller support member (for example, the notch 9 in this embodiment).
0a to 90d), the processing accuracy of the flat portion of the stopper member must be increased. On the contrary,
It is relatively easy to precisely process the columnar member so that the radius of the columnar member becomes a predetermined radius than to process a member having another shape (for example, a rectangular shape or a polygon) to a correct size. Therefore, even if the processing accuracy is slightly reduced, the positional accuracy when the stopper member is attached is higher than in the case of other shapes.

The conventional stopper member has a drawback that it can easily rotate around the mounting bolt at the time of assembling. However, in the stopper member according to the present invention, for example, it rotates around the fastening bolt at the time of assembling the stopper member. Even if it does, the position of the stopper member does not shift. Further, even if a large force acts on the stopper member from the roller support member and the stopper member rotates around the fastening bolt, unlike the conventional stopper member, there is no influence on the function as the stopper member.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of an embodiment of a toroidal type continuously variable transmission according to the present invention.

FIG. 2 is a schematic configuration diagram of a transmission including a toroidal-type continuously variable transmission according to the present invention.

FIG. 3 is a plan sectional view of the toroidal-type continuously variable transmission according to the present invention.

FIG. 4 is a plan view of a connecting member to which a stopper member is attached.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Engine 2 Torque converter 5 Transmission output shaft 7 First toroidal type transmission mechanism 8 Second toroidal type transmission mechanism 43f, 43r Input disk 44f, 44r Output disk 45a, 45b, 45c, 45d Roller 53 Valve body 59a, 59b, 59c , 59d Roller support member 62 Upper connection member 63 Lower connection member 68f, 68r Lower positioning hole 73f Spherical bush 90a, 90b, 90c, 90d Notch 100f Stopper member 101 Fastening bolt

──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Haruo Sakamoto 3-1 Shinchi, Fuchu-cho, Aki-gun, Hiroshima Prefecture Inside Mazda Corporation (72) Inventor Hidenao Taketomi 3-1 Shinchi, Fuchu-cho, Aki-gun, Hiroshima Mazda (56) References JP-A-57-47060 (JP, A) JP-A-62-37562 (JP, A) JP-A-5-60198 (JP, A) Jpn. U) Japanese Utility Model Sho 61-20882 (JP, U) Japanese Utility Model Application Hei 3-90784 (JP, U) (58) Fields investigated (Int. Cl. ⁷ , DB name) F16H 15/38

Claims (2)

(57) [Claims] An input disk, an output disk, a pair of rollers that come into rotational contact with both the input disk and the output disk, the rollers being rotatably supported and rotatable about a rotation shaft. A pair of roller support members movable in the direction of the rotating shaft, a hydraulic mechanism for moving the roller supporting member in the direction of the rotating shaft, and a valve body and the other side with the roller interposed therebetween. A toroidal-type continuously variable transmission having a pair of connecting members that support the roller supporting member, wherein a cylindrical stopper that defines a tilt limit of the roller supporting member is provided on at least one of the connecting members. A toroidal-type continuously variable transmission, wherein the toroidal-type continuously variable transmission is disposed on a rotation locus of a support member. 2. An input disk, an output disk, a plurality of rollers that are in rotational contact with both the input disk and the output disk, and the rollers are rotatably supported and rotatable about a rotation shaft. A roller supporting member movable in the direction of the rotating shaft, a hydraulic mechanism for moving the roller supporting member in the direction of the rotating shaft, and a valve body provided on the other side with the roller interposed therebetween; In a toroidal-type continuously variable transmission having a pair of connecting members that support a roller supporting member and a wire that is bridged between the rollers and regulates a rotation direction of the roller, a tilt limit of the roller supporting member is defined. The cylindrical stopper is formed on at least one of the connecting members on the rotation locus of each roller supporting member, and overlaps the wire in the vertical direction. Toroidal type continuously variable transmission, characterized in that arranged in.