JP2003074656A - Toroidal-type continuously variable transmission and continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To achieve a construction ensuring torque transmission from a drive shaft 82 to an input shaft 11b of a toroidal type continuously variable transmission 30a and torque transmission from the input shaft 11b to a transmission shaft 34a linked to a planetary gear mechanism 31a, and securing enough durability. SOLUTION: Gear-driving projected parts 84, 84 provided on the side of the driving shaft 82 are engaged with cutouts 83, 83 formed on a collar portion 73 of the input shaft 11. A projected parts 92, 92 formed on the outside surface of an input disc 2b brought into spline engagement with the input shaft 11b are engaged with projections 96, 96 for transmission provided on the side of the transmission shaft 34a. Accordingly the transmission of large torque at each part is enabled by enlarging the diameters of engaging parts for torque transmission.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION A toroidal type continuously variable transmission and a continuously variable transmission according to the present invention are used as a transmission unit constituting an automatic transmission for automobiles or for adjusting the operating speed of various industrial machines such as pumps. Used as a transmission for

[0002]

2. Description of the Related Art As a vehicle transmission, the use of a toroidal type continuously variable transmission as schematically shown in FIGS. 8 to 9 has been studied and partially implemented. This toroidal type continuously variable transmission supports the input side disk 2 concentrically with the input shaft 1 and is arranged concentrically with the input shaft 1, as disclosed in, for example, Japanese Utility Model Laid-Open No. 62-71465. The output disk 4 is fixed to the end of the output shaft 3. Inside the casing 5 (see FIG. 11 to be described later) in which the toroidal type continuously variable transmission is housed, the trunnion 7 swings around the pivot shafts 6, 6 which are in a twisted position with respect to the input shaft 1 and the output shaft 3. ,
7 is provided.

The trunnions 7, 7 are provided with the pivots 6, 6 on the outer surfaces of both ends thereof, concentrically with each trunnion 7, 7 and one pair for each trunnion 7, 7.
The central axes of the pivots 6 and 6 are the discs 2 and 4 described above.
It does not intersect with the central axis of
It exists at a twist position which is almost perpendicular to the direction of the central axis of the No. 4. Further, the base half of the displacement shafts 8, 8 is supported on the central portions of the trunnions 7, 7, and the trunnions 7, 7 are swung about the pivot shafts 6, 6 to displace the displacement shafts 8. , 8 can be freely adjusted. Power rollers 9, 9 are rotatably supported around the first half of the displacement shafts 8, 8 supported by the trunnions 7, 7, respectively. The power rollers 9, 9 are sandwiched between the inner side surfaces 2a, 4a of the input side and output side disks 2, 4.

The inner surfaces 2a, 4a of the input side and output side disks 2 and 4 facing each other are obtained by rotating an arc centered on the pivot 6 or a curve close to such an arc. It has a concave surface with an arcuate cross section. Then, the peripheral surfaces 9a, 9a of the power rollers 9, 9 formed in the spherical convex surface are brought into contact with the inner side surfaces 2a, 4a. Further, a loading cam device 10 is provided between the input shaft 1 and the input side disc 2 and the loading side cam 2 is used by the loading cam device 10.
While being elastically pressed toward the output side disk 4, it can be rotationally driven.

When the toroidal type continuously variable transmission configured as described above is used, the loading cam device 10 causes the input side disk 2 to move to the plurality of power rollers 9 and 9 as the input shaft 1 rotates. Rotate while pressing. And
The rotation of the input side disk 2 is transmitted to the output side disk 4 via the plurality of power rollers 9, 9, and the output shaft 3 fixed to the output side disk 4 rotates.

In the case of changing the rotational speeds of the input shaft 1 and the output shaft 3, first, when decelerating between the input shaft 1 and the output shaft 3, the trunnions 7 with the pivot shafts 6, 6 as the centers, 7 is rocked, and the peripheral surfaces 9a of the power rollers 9, 9 are
9a, as shown in FIG. 8, the inner surface 2a of the input side disk 2
Of the displacement shafts 8 so as to come into contact with the central portion of the output disk 4 and the outer peripheral portion of the inner side surface 4a of the output side disk 4, respectively.
Incline 8

On the other hand, when increasing the speed, the trunnions 7, 7 are swung so that the peripheral surfaces 9a, 9a of the power rollers 9, 9 of the input side disk 2 as shown in FIG. The outer peripheral portion of the inner side surface 2a and the inner side surface 4 of the output side disk 4
The displacement axes 8 and 8 are tilted so that the displacement shafts 8 and 8 come into contact with the central portions of a. If the inclination angle of each of the displacement shafts 8, 8 is set in the middle between FIG. 8 and FIG. 9, an intermediate gear ratio can be obtained between the input shaft 1 and the output shaft 3.

Further, FIGS. 10 to 11 show Japanese Patent Application No. Sho 63-69.
1 shows a more specific toroidal type continuously variable transmission described in a microfilm of No. 293 (Actual Kaihei No. 1-173552). The input side disk 2 and the output side disk 4 are rotatably supported around a circular cylindrical input shaft 11. A loading cam device 10 is provided between the end of the input shaft 11 and the input side disk 2. On the other hand, an output gear 12 is coupled to the output side disk 4 so that the output side disk 4 and the output gear 1
2 and 2 are designed to rotate in synchronization.

Pivots 6, 6 concentrically provided on both ends of the pair of trunnions 7, 7 are provided on the pair of support plates 13, 13.
It is supported so as to be swingable and axially displaceable (front and back directions in FIG. 10, left and right directions in FIG. 11). Then, the base half portions of the displacement shafts 8, 8 are supported by the intermediate portions of the trunnions 7, 7. The displacement shafts 8 and 8 decenter the base half portion and the front half portion from each other. The base half of these is rotatably supported by the middle of the trunnions 7, 7 and the power rollers 9, 9 are rotatably supported by the respective leading halves.

The pair of displacement shafts 8 and 8 are provided 180 degrees opposite to the input shaft 11. or,
The directions in which the base half and the front half of these displacement shafts 8, 8 are eccentric are the same as the rotational directions of the input side and output side disks 2 and 4 (left and right opposite directions in FIG. 11). . Further, the eccentric direction is a direction substantially orthogonal to the disposing direction of the input shaft 11. Therefore, the power rollers 9, 9 are supported so as to be slightly displaceable in the arrangement direction of the input shaft 11.

Further, between the outer side surface of each of the power rollers 9 and 9 and the inner side surface of the intermediate portion of each of the trunnions 7 and 7, in order from the outer surface side of each of the power rollers 9 and 9, thrust ball bearings are provided. 14, 14 and thrust needle bearing 15, 1
And 5 are provided. Of these, thrust ball bearings 14, 1
The reference numeral 4 allows the power rollers 9, 9 to rotate while supporting the load in the thrust direction applied to the power rollers 9, 9. Further, each of the thrust needle bearings 15,
The reference numeral 15 designates a thrust load applied from the respective power rollers 9, 9 to the outer races 16, 16 constituting the respective thrust ball bearings 14, 14 while supporting the first half of the displacement shafts 8, 8 and the outer race 16 respectively. , 16 are allowed to oscillate around the base halves of these displacement shafts 8, 8. Further, the trunnions 7 and 7 are hydraulic actuators 17 and 1, respectively.
7, the axial movements of the pivots 6 and 6 are freely made.

In the case of the toroidal type continuously variable transmission configured as described above, the rotation of the input shaft 11 is transmitted to the input side disk 2 via the loading cam device 10. And
The rotation of the input side disk 2 is transmitted to the output side disk 4 via the pair of power rollers 9, 9, and the rotation of the output side disk 4 is taken out from the output gear 12.

When changing the rotational speed ratio between the input shaft 11 and the output gear 12, the actuators 17 and 1 are used.
7, the pair of trunnions 7 and 7 in opposite directions, for example, the lower power roller 9 of FIG. 11 is on the right side of the figure, the upper power roller 9 of FIG. 11 is on the left side of FIG.
Displace each. As a result, the direction of the tangential force acting on the abutting portions between the peripheral surfaces 9a, 9a of the power rollers 9, 9 and the inner side surfaces 2a, 4a of the input side disk 2 and the output side disk 4 changes. To do. Then, with the change in the direction of the force, the trunnions 7, 7 swing in opposite directions about the pivots 6, 6 pivotally supported by the support plates 13, 13. As a result, as shown in FIGS. 8 to 9 described above, the contact positions of the peripheral surfaces 9a, 9a of the power rollers 9, 9 and the inner side surfaces 2a, 4a change, and the input shaft 11 and The rotation speed ratio with the output gear 12 changes.

During power transmission by the toroidal type continuously variable transmission, the power rollers 9, 9 are displaced in the axial direction of the input shaft 11 due to elastic deformation of the respective constituent parts. Then, the displacement shafts 8, 8 supporting the power rollers 9, 9 slightly rotate about their respective base halves. As a result of this rotation, the thrust ball bearings 14 and 1
4, the outer surface of the outer ring 16, 16 and the trunnions 7, 7
Relative to the inner surface of the. Since the thrust needle bearings 15, 15 are present between the outer side surface and the inner side surface, the force required for this relative displacement is small.

In the case of the toroidal type continuously variable transmission constructed and operated as described above, the input shaft 11 and the output gear 12 are provided.
The power transmission between the two is performed by two power rollers 9, 9. Therefore, the peripheral surface 9 of each power roller 9, 9
a, 9a and the inner side surface 2 of both the input side and output side disks 2 and 4
The force per unit area transmitted between a and 4a becomes large, and the power that can be transmitted is limited. In view of such circumstances, it has been conventionally considered to increase the number of power rollers 9 in order to increase the power that can be transmitted by the toroidal type continuously variable transmission.

As a first example of the structure for increasing the number of the power rollers 9 and 9 for such a purpose, three power rollers 9 are provided between one set of the input side disk 2 and the output side disk 4.
It is conventionally known to dispose 9 and to transmit power by these three power rollers 9, 9 as disclosed in, for example, Japanese Patent Laid-Open No. 3-74667. In the case of the structure described in this publication, as shown in FIG. 12, the support pieces 19 and 1, which are bent at 120 degrees, are provided at three positions on the fixed frame 18 at equal intervals in the circumferential direction.
It supports the middle part of 9. And the adjacent support pieces 1
The trunnions 7 and 7 are supported between 9 and 19 so as to freely swing and be displaced in the axial direction.

Each of the trunnions 7 and 7 is freely movable in the axial direction of a pivot 6 which is concentrically provided at both ends thereof by hydraulic actuators 17 and 17, respectively. The hydraulic cylinders 20, 20 forming the actuators 17, 17 communicate with the discharge port of the pump 22, which is a hydraulic pressure source, via the control valve 21. The control valve 21 includes a sleeve 23 and a spool 24, each of which is axially displaceable (left and right in FIG. 12).

When changing the inclination angle of the power rollers 9, 9 pivotally supported by the displacement shafts 8, 8 to the trunnions 7, 7, the sleeve 23 is axially moved by the control motor 25 (see FIG. 12). Left and right).
As a result, the pressure oil discharged from the pump 22 is sent to each of the hydraulic cylinders 20, 20 through the hydraulic pipe. The drive pistons 26, 26 fitted in the hydraulic cylinders 20, 20 for displacing the trunnions 7, 7 in the axial direction of the pivot shaft are provided with the input side disc 2 and the output side disc 4 (FIG. 8). (Refer to 9)). In addition, each drive piston 2
With the displacement of 6, 26, the hydraulic cylinders 20, 20
The hydraulic oil extruded from is returned to the oil sump 27 through a hydraulic pipe (not partly shown) which also includes the control valve 21.

On the other hand, the displacement of the drive piston 26 due to the feeding of the pressure oil is transmitted to the spool 24 via the recess cam 28 and the link 29, and the spool 24 is displaced in the axial direction. As a result, the drive piston 26
Is displaced by a predetermined amount, the flow path of the control valve 21 is closed, and the supply and discharge of the pressure oil to and from the hydraulic cylinders 20, 20 are stopped. Therefore, the amount of displacement of the trunnions 7, 7 in the axial direction only corresponds to the amount of displacement of the sleeve 23 by the control motor 25.

Further, as a second example of the structure for increasing the number of power rollers 9 in order to increase the power that can be transmitted by the toroidal type continuously variable transmission, as shown in FIG. Two input-side disks 2A, 2B and two output-side disks 4, 4 are provided around the input-side disks 2A, 2B and two output-side disks 4, 4 arranged in parallel in the power transmission direction. A so-called double cavity type structure for arranging is also conventionally known. In the structure shown in FIG. 13, the output gear 12a is supported around the intermediate portion of the input shaft 11a so as to be freely rotatable with respect to the input shaft 11a, and both ends of a cylindrical portion provided at the center of the output gear 12a are supported. The output side disks 4 and 4 are spline-engaged with each other. In addition, each input side disk 2
A and 2B are rotatably supported together with the input shaft 11a at both ends of the input shaft 11a. This input shaft 11
a is a loading cam device 10 driven by the drive shaft 100.
It is rotationally driven via. In the case of such a double cavity type toroidal type continuously variable transmission, the transmission of power from the input shaft 11a to the output gear 12a is performed between one input side disk 2A and the output side disk 4 and the other. Since it is divided into two systems, that is, between the input side disk 2B and the output side disk 4, large power can be transmitted.

When a toroidal type continuously variable transmission constructed and operated as described above is incorporated in an actual continuously variable transmission for an automobile, it is possible to construct a continuously variable transmission by combining it with a planetary gear mechanism. -169169 gazette, the same 1-312.
No. 266, No. 10-196759, No. 11-
It has been conventionally proposed as described in Japanese Patent No. 63146. That is, the torque applied to the toroidal type continuously variable transmission during high speed traveling is transmitted by transmitting the engine driving force only by the toroidal type continuously variable transmission during low speed traveling and by transmitting the above driving force by the planetary gear mechanism during high speed traveling. Is being reduced. By configuring in this way,
The durability of each member constituting the toroidal type continuously variable transmission can be improved.

FIG. 14 shows Japanese Unexamined Patent Publication (Kokai) No. Hei 11
6 shows a continuously variable transmission described in Japanese Patent Laid-Open No. 63146. This continuously variable transmission comprises a double cavity toroidal type continuously variable transmission 30 and a planetary gear mechanism 31 in combination. The power is transmitted only by the toroidal type continuously variable transmission 30 during low speed traveling, and the power is mainly transmitted by the planetary gear mechanism 31 during high speed traveling, and the gear ratio by the planetary gear mechanism 31 is changed by the toroidal type continuously variable transmission 30. It is adjustable by changing the gear ratio of the continuously variable transmission 30.

For this reason, the toroidal type continuously variable transmission 3 is used.
A pair of input-side disks 2 that penetrate the center of 0 and are located at both ends.
A ring gear 3 that constitutes the planetary gear mechanism 31 and the tip portion (the right end portion in FIG. 14) of the input shaft 11a supporting A and 2B.
The transmission shaft 34 fixed to the center of the support plate 33 supporting the 2
And are connected via a high speed clutch 35. still,
Of the pair of input side disks 2A and 2B, the input side disk 2B on the tip side (right side in FIG. 14) is the input shaft 1
1a, for example, in the same manner as in the case of the conventional structure shown in FIG. 13 described above, supporting in a state in which rotation in synchronization with the input shaft 11a and substantial movement in the axial direction of the input shaft 11a are blocked. There is. On the other hand, the proximal side (Fig. 1
The input side disk 2A (on the left side of 4) with respect to the input shaft 11a relates to the rotation in synchronization with the input shaft 11a and the axial direction of the input shaft 11a in the same manner as in the conventional structure shown in FIG. It is movably supported. In any case, the configuration of the toroidal type continuously variable transmission 30 is the same as that shown in FIG. 1 except for the pressing device 36 described below.
This is substantially the same as the case of the conventional structure shown in FIG.

The output side end of the crankshaft 38 of the engine 37, which is the drive source (right end in FIG. 14), and the input side end of the input shaft 11a (= base end = left end in FIG. 14).
A starting clutch 39 and a hydraulic pressing device 36 are provided between and in series with each other in the power transmission direction.
The pressing device 36 can generate a pressing force corresponding to the magnitude (torque) of the power transmitted from the crankshaft 38 to the toroidal continuously variable transmission 30 based on a signal from a controller (not shown). The hydraulic pressure is freely introduced.

Further, the output shaft 40 for taking out the power based on the rotation of the input shaft 11a is arranged concentrically with the input shaft 11a. The planetary gear mechanism 31 is provided around the output shaft 40. This planetary gear mechanism 31
The sun gear 41 constituting the above is fixed to the input side end portion (the left end portion in FIG. 14) of the output shaft 40. Therefore, the output shaft 40 rotates with the rotation of the sun gear 41.
Around the sun gear 41, the ring gear 32 is rotatably supported concentrically with the sun gear 41. A plurality of planetary gear sets 43, 43 are provided between the inner peripheral surface of the ring gear 32 and the outer peripheral surface of the sun gear 41, each pair of planetary gears 42a, 42b being combined. There is. The pair of planetary gears 42a and 42b mesh with each other, and the planetary gear 42a arranged on the outer diameter side meshes with the ring gear 32.
A planetary gear 42b arranged on the inner diameter side meshes with the sun gear 41. Such planetary gear sets 43, 43 are rotatably supported on one side surface (left side surface in FIG. 14) of the carrier 44. The carrier 44 is rotatably supported on the intermediate portion of the output shaft 40.

Further, the carrier 44 and a pair of output side disks 4 constituting the toroidal type continuously variable transmission 30,
4 are connected to each other by a first power transmission mechanism 45 so that the rotational force can be transmitted. The first power transmission mechanism 45 includes a transmission shaft 46 parallel to the input shaft 11a and the output shaft 40, a sprocket 47a fixed to one end portion (the left end portion in FIG. 14) of the transmission shaft 46, and each of the above-mentioned components. The sprocket 47b fixed to the output side disks 4 and 4, the chain 48 hung between the two sprockets 47a and 47b, the other end of the transmission shaft 46 (right end in FIG. 14) and the carrier 44, respectively. The first and second gears 49 and 50 are fixed and meshed with each other.
Therefore, the carrier 44 includes the output disks 4,
Along with the rotation of 4, the output-side disks 4 and 4 rotate in the opposite direction at a speed corresponding to the number of teeth of the first and second gears 49 and 50. This is a case where the pair of sprockets 47a and 47b have the same number of teeth.

On the other hand, the input shaft 11a and the ring gear 32 can be freely connected to each other via the transmission shaft 34 arranged concentrically with the input shaft 11a so that the rotational force can be transmitted. The high speed clutch 35 is provided between the transmission shaft 34 and the input shaft 11a.
It is provided in series with 11a. Therefore, in the case of this example, the transmission shaft 34 constitutes the second power transmission mechanism 53 described in the claims. Then, the high speed clutch 3
When connecting 5, the transmission shaft 34 rotates in the same direction as the input shaft 11a at the same speed as the input shaft 11a rotates.

Further, the continuously variable transmission is provided with a clutch mechanism which constitutes the mode switching means described in the claims. This clutch mechanism includes a high speed clutch 35, and a low speed clutch 51 provided between an outer peripheral edge portion of the carrier 44 and one axial end portion (right end portion in FIG. 14) of the ring gear 32.
And a reverse clutch 52 provided between the ring gear 32 and a fixed portion such as a housing (not shown) of the continuously variable transmission. When any one of the clutches 35, 51 and 52 is connected, the remaining two clutches are disconnected.

In the continuously variable transmission constructed as described above, at the time of low speed traveling, first, the low speed clutch 51 is connected and the high speed clutch 35 and the reverse clutch 52 are disconnected. When the starting clutch 39 is connected and the input shaft 11a is rotated in this state, only the toroidal type continuously variable transmission 30 transmits power from the input shaft 11a to the output shaft 40. When driving at low speed like this,
The gear ratio between each pair of the input side disks 2A, 2B and the output side disks 4, 4 is adjusted in the same manner as in the case of the toroidal type continuously variable transmission alone shown in FIG.

On the other hand, during high speed running, the high speed clutch 35 is connected and the low speed clutch 51 and the reverse clutch 52 are disconnected. When the starting clutch 39 is connected and the input shaft 11a is rotated in this state, the transmission shaft 34 and the planetary gear mechanism 31 transmit power from the input shaft 11a to the output shaft 40. That is, the input shaft 11a during high speed traveling
When is rotated, this rotation is transmitted to the ring gear 32 via the high speed clutch 35 and the transmission shaft 34. And
The rotation of the ring gear 32 causes a plurality of planetary gear sets 43, 4
3 is transmitted to the sun gear 41, and the output shaft 40 to which the sun gear 41 is fixed is rotated. In this state, if the revolution speed of each of the planetary gear sets 43, 43 is changed by changing the gear ratio of the toroidal continuously variable transmission 30, the gear ratio of the whole continuously variable transmission can be adjusted.

That is, the planetary gear sets 43, 43 revolve in the same direction as the ring gear 32 during the high speed running. Then, the slower the revolution speed of each planetary gear set 43, 43, the faster the rotation speed of the output shaft 40 to which the sun gear 41 is fixed. For example, when the revolution speed and the rotation speed of the ring gear 32 (both are angular velocities) are the same, the rotation speeds of the ring gear 32 and the output shaft 40 are the same.
On the other hand, if the revolution speed is slower than the rotation speed of the ring gear 32, the rotation speed of the output shaft 40 becomes faster than the rotation speed of the ring gear 32. On the contrary, if the revolution speed is higher than the rotation speed of the ring gear 32, the rotation speed of the output shaft 40 becomes slower than the rotation speed of the ring gear 32.

Therefore, when the vehicle is traveling at high speed, as the gear ratio of the toroidal type continuously variable transmission 30 is changed to the deceleration side, the gear ratio of the entire continuously variable transmission is changed to the speed increasing side. In such a state at the time of high-speed running, the toroidal type continuously variable transmission 30 is not connected to the input side disks 2A, 2B but
Torque is applied from the output side disk 4 (negative torque is applied when the torque applied at low speed is positive torque). That is, when the high speed clutch 35 is connected, the torque transmitted from the engine 37 to the input shaft 11 a is transmitted to the ring gear 32 of the planetary gear mechanism 31 via the transmission shaft 34. Therefore, the torque transmitted from the input shaft 11a side to the input side disks 2A, 2B is almost eliminated.

On the other hand, a part of the torque transmitted to the ring gear 32 of the planetary gear mechanism 31 via the second power transmission device 53 is transmitted from the planetary gear sets 43, 43 to the carrier 44 and the first gear. Is transmitted to each of the output side disks 4, 4 via the power transmission mechanism 45. As described above, the torque applied to the toroidal type continuously variable transmission 30 from the output side disks 4 and 4 changes the gear ratio of the toroidal type continuously variable transmission 30 in order to change the gear ratio of the entire continuously variable transmission to the speed increasing side. Becomes smaller as is changed to the deceleration side. As a result, the torque input to the toroidal type continuously variable transmission 30 during high-speed traveling can be reduced, and the durability of the components of the toroidal type continuously variable transmission 30 can be improved.

Further, when the output shaft 40 is reversely rotated in order to move the vehicle backward, both the low speed clutch 51 and the high speed clutch 51 are disconnected, and the reverse clutch 52 is connected. As a result, the ring gear 32 is fixed, and the planetary gear sets 43, 43 revolve around the sun gear 41 while meshing with the ring gear 32 and the sun gear 41. And this sun gear 4
The output shaft 40 to which 1 and this sun gear 41 are fixed rotates in the opposite direction to the above-described low speed running and the above high speed running.

The continuously variable transmission described above is of a so-called power split type for the purpose of reducing the torque passing through the toroidal type continuously variable transmission 30 during high speed traveling. In the case of this type of continuously variable transmission,
Since the output shaft 40 cannot be stopped while the input shaft 11a is rotating, the starting clutch 39 is required. On the other hand, by devising the specifications of the planetary gear mechanism and the combination of this planetary gear mechanism and the toroidal type continuously variable transmission, the output shaft can be stopped while the input shaft is rotating, the so-called geared neutral type. A continuously variable transmission referred to as is also described in, for example, Japanese Patent Application Laid-Open No. 11-63148 and British Patent Publication GB2 256 015 A. In the case of this geared neutral type continuously variable transmission, the starting clutch can be omitted instead of increasing the torque passing through the toroidal type continuously variable transmission when the output shaft is stopped or rotates at a low speed.

[0036]

Among the above-mentioned prior arts, the continuously variable transmission shown in FIG. 14 is excellent in that it can transmit a large torque while ensuring durability. Considering that a larger torque can be transmitted while ensuring sufficient durability, there is a possibility that simply combining the conventional techniques may not be sufficient. That is, in consideration of realizing the structure for transmitting a large torque with the structure shown in FIG. 14, between the output portion of the starting clutch 39 and the input shaft 11a, and between the input shaft 11a and the high speed clutch 35. Therefore, it becomes necessary to transmit a large amount of power to each. On the other hand, hitherto, no practical structure has been known in which a large torque can be transmitted in each of these parts. For example, in Japanese Patent Laid-Open No. 11-303961,
Although a structure is described in which the outer surface inner diameter portion of the output side disk and the end portion of the sleeve are engaged in a concavo-convex manner, a large torque cannot always be transmitted because the diameter of the torque transmitting portion is small. The continuously variable transmission of the present invention was invented in view of such circumstances.

[0037]

Of the toroidal type continuously variable transmission and the continuously variable transmission of the present invention, the toroidal type continuously variable transmission described in claims 1 and 2 is known from the above-mentioned prior art. Similar to the toroidal type continuously variable transmission, the input side disc, the output side disc which is arranged concentrically with the input side disc and is rotatable independently of the input shaft, and the input side disc and the output side disc. A plurality of trunnions that are provided between the discs and swing around a pivot that is in a twisted position with respect to the central axes of these discs;
Displacement shafts projecting from the inner side surfaces of the trunnions, one for each trunnion, and the inner side surfaces of the input side disc and the output side disc in a state of being rotatably supported by these displacement shafts. One power roller is provided for each of the trunnions sandwiched between the power rollers.

Particularly, in the toroidal type continuously variable transmission according to the first aspect, at least a part of the outer side surface of at least one of the input side disk and the output side disk has a radial direction. Engages a plurality of protrusions projecting in a half portion closer to the outer diameter than the central portion of the outer side surface and the tip of a transmission projection provided on a transmission member for transmitting torque between the disc By doing so, it is possible to transmit torque between the disc and the transmission member.

Further, in the toroidal type continuously variable transmission according to a second aspect of the invention, the first rotation is freely rotatable in synchronization with one of the input side disk and the output side disk. Between a plurality of notches formed in the outer peripheral edge portion of the outward flange-shaped collar portion provided on the outer peripheral surface of the end portion of the shaft, and the first rotation shaft arranged concentrically with the first rotation shaft. By engaging a driving convex portion formed at the end of the second rotary shaft that transmits torque by means of the torque transmission between the second rotary shaft and the first rotary shaft, It is possible.

Further, the continuously variable transmission according to claim 3 is
An input shaft, an output shaft, a toroidal type continuously variable transmission, a planetary gear mechanism, a first power transmission mechanism, and a second power transmission mechanism. Of these, the input shaft is connected to a drive source and is rotationally driven by this drive source. The output shaft is for taking out power based on the rotation of the input shaft. Further, the toroidal type continuously variable transmission is
A pair of input side disks supported by both ends of the input shaft and rotating with the rotation of the input shaft, and the input shaft in a state where the inner side surfaces of the input side disks face the inner side surfaces of the respective input side disks. A pair of output disks which are arranged concentrically with the respective input disks around the middle part of the disk and which are rotatable independently of the respective input disks and in synchronization with each other; A plurality of trunnions for each pair of the input side disc and the output side disc, which are provided between the output side discs and swing around a pivot shaft in a twisted position with respect to the center axes of the respective discs. , One displacement shaft protruding from the inner surface of each of these trunnions, one displacement shaft for each of these trunnions, and each input side disk and each output side while being rotatably supported by these displacement shafts. One power roller for each trunnion sandwiched between the inner surfaces of the disk and each disk, and each input side disk and each output side disk sandwiches each power roller based on hydraulic pressure. A force is applied in correspondence with the magnitude of the force transmitted between each of the input side discs and each of the output side discs, parallel to the input shaft with respect to the power transmission direction, and around the input shaft. And a pressing device provided. The planetary gear mechanism is rotatably supported by a carrier which is provided between a sun gear and a ring gear arranged around the sun gear and is concentrically and rotatably supported by the sun gear. Is formed by meshing with the sun gear and the ring gear, and the power transmitted through the first power transmission mechanism and the power transmitted through the second power transmission mechanism are the sun gear and the ring. It can be transmitted to two members of the gear and the carrier, and the remaining one of the sun gear, the ring gear, and the carrier can be transmitted.
The output shaft is connected to each member. The first power transmission mechanism transmits the power input to the input shaft via the toroidal type continuously variable transmission.
The second power transmission mechanism transmits the power input to the input shaft without passing through the toroidal type continuously variable transmission, has a transmission shaft, and is supported at one end of the input shaft. A part of the outer side surface of one of the input side discs, which is provided with a plurality of convex portions projecting in a half portion closer to the outer diameter than the central portion of the outer side surface in the radial direction, and the radial direction from the end of the transmission shaft. By engaging the tip of the outwardly extending transmission projection piece, the rotational force can be freely transmitted from the one input side disk to the transmission shaft.

Further, as described in claim 4, preferably, an outer flange portion of the input shaft is provided with an outward flange-shaped flange portion, and a plurality of notches formed in an outer peripheral edge portion of the flange portion. By engaging the driving convex portion formed at the tip of the drive shaft with the drive shaft, the drive shaft can be rotationally driven by the drive shaft. Furthermore, when a large torque is required at a low speed or the rotation direction needs to be reversed at the time of low speed, such as when it is used as a transmission unit constituting an automatic transmission for automobiles, the input as described in claim 5. Mode switching means is provided for switching the state in which the power input to the shaft is sent to the planetary gear mechanism through the first power transmission mechanism and the second power transmission mechanism. The mode switching means transmits the power by the first mode in which the power is transmitted only by the first power transmission mechanism, and the power is transmitted by both the first power transmission mechanism and the second power transmission mechanism. And a third mode in which power is transmitted only by the first power transmission mechanism and the rotation direction of the output shaft is opposite to those in the first and second modes. Is switched.

[0042]

In the toroidal type continuously variable transmission and continuously variable transmission of the present invention configured as described above, power is transmitted between the input side disk and the output side disk or between the input shaft and the output shaft. In addition, the basic operation when changing the gear ratio between the two disks or between the two shafts is as follows. This is the same as in the case of a transmission or a continuously variable transmission.
In particular, in the case of the toroidal type continuously variable transmission or continuously variable transmission of the present invention, it is provided on a plurality of convex portions formed on a half portion of the outer surface of the disk near the outer diameter and a transmission member for transmitting torque. By engaging with the tip of the transmission projection, or by engaging the plurality of notches formed on the outer peripheral edge of the flange formed on the rotary shaft or the input shaft with the tip of the driving projection. , A large torque can be easily transmitted by each power transmission unit.

[0043]

1 to 7 show an example of an embodiment of the present invention. The illustrated example shows a case where a continuously variable transmission is configured by combining the toroidal type continuously variable transmission 30a and the planetary gear mechanism 31a. This continuously variable transmission includes an input shaft 11b, an output shaft 40a, the toroidal type continuously variable transmission 30a, the planetary gear mechanism 31a, a first power transmission mechanism 45a, and a second power transmission mechanism 53. With. Of these, the input shaft 11b is connected to a drive source such as the engine 37 (see FIG. 14) and is rotationally driven by this drive source. Also, the output shaft 40a
Is for extracting power based on the rotation of the input shaft 11b, and is also connected to a wheel drive shaft (not shown) via a differential gear (not shown).

Further, the toroidal type continuously variable transmission 30a.
Is a double-cavity type as shown in FIGS. 13 to 14 described above, and three trunnions 7, 7 and three power rollers 9, 9 are provided in each cavity, six in total. In order to configure such a toroidal type continuously variable transmission 30a, a pair of input side disks 2A, 2B are provided at both ends of the input shaft 11b with their inner side surfaces 2a, 2a facing each other. It is rotatably supported in synchronization with the input shaft 11b. Of these, the base end side (on the drive source side,
The input side disk 2A (on the left side of) is attached to the input shaft 11b,
It is supported via a ball spline 54 so as to be displaceable in the axial direction. On the other hand, the input side disk 2B on the tip side (the side far from the drive source, the right side in FIGS. 1 and 2) has the back surface thereof loaded with the loading nut 55 in a state of being spline-engaged with the tip portion of the input shaft 11b. By suppressing
It is fixed to the input shaft 11b.

Around the middle portion of the input shaft 11b, one portion is provided between the pair of input side disks 2A and 2B.
The pair of output disks 4 and 4 are connected to inner surfaces 4a,
4a is the inner side surface 2a of each of the input side disks 2A, 2B,
In the state of being opposed to 2a, they are rotatably supported in synchronization with each other. Then, the input side disks 2A, 2B
The power rollers 9 and 9 rotatably supported on the inner side surfaces of the trunnions 7 and 7 are sandwiched between the inner side surfaces 2a and 4a of the output side disks 4 and 4, respectively.

In order to support each of the trunnions 7, 7, a frame 57 is inserted into a mounting portion 56 provided on the inner surface of the casing 5a, and the mounting holes 58, 58 at three outer diameter side end portions of the frame 57 are inserted. Studs 59, 59 and nuts 60, 60 screwed to the studs 59, 59.
Fixed by combining with. In the illustrated example, the gear housing 61 is provided between the mounting portion 56 and the frame 57 by the studs 59, 59 and the nuts 60, 60.
Is fixed. On the inner diameter side of the gear housing 61, an output sleeve 62 in which the pair of output side disks 4 and 4 are engaged in concave and convex at both ends thereof is formed a pair of rolling bearings 6.
The output gear 12b rotatably supported by 3, 63 and provided on the outer peripheral surface of the intermediate portion of the output sleeve 62 is
It is housed inside the gear housing 61.

Further, the frame 57 is formed in a star shape as a whole, and its radial middle portion or outer diameter side portion is bifurcated so that the three holding portions 64, 64 are circumferentially or the like. Formed at intervals. Then, each of these holding portions 64, 6
The intermediate portions of the support pieces 19a, 19a are pivotally supported by the second pivots 65, 65 at the radial intermediate portions of 4, respectively.
Each of these support pieces 19a, 19a has a second pivot 6
It is composed of a cylindrical mounting portion 66 arranged around the 5, 5 and a pair of support plate portions 67, 67 projecting radially outward from the outer peripheral surface of the mounting portion 66. The intersecting angle between the pair of support plate portions 67, 67 is 120 degrees. Therefore,
Support pieces 6a of support pieces 19a, 19a adjacent to each other in the circumferential direction
7, 67 are parallel to each other.

Circular holes 68, 68 are formed in the respective support plate portions 67, 67 as described above. Each supporting piece 19
When a and 19a are in a neutral state, the circular holes 68 and 68 formed in the support plate portions 67 and 67 of the support pieces 19a and 19a adjacent to each other in the circumferential direction are concentric with each other. Then, in the circular holes 68, 68, the pivots 6, 6 provided at both ends of the trunnions 7, 7 are attached to the radial needle bearings 69, 6 respectively.
It is supported by 9. The outer peripheral surfaces of the outer rings 70, 70 constituting the radial needle bearings 69, 69 are spherical convex surfaces. Such outer rings 70, 70 are fitted in the respective circular holes 68, 68 so as to be swingably displaceable without rattling. In addition, in a part of each of the support plate portions 67, 67, an arc-shaped elongated hole 71, which is concentric with the circular holes 68, 68,
71, and the studs 72 projecting from the end faces (shoulders) of the trunnions 7, 7 in the long holes 71, 71.
72 is loosely engaged to form a stopper mechanism for limiting the inclination angle of each trunnion 7, 7 about each pivot 6, 6.

In this way, on the inner side surfaces of the trunnions 7, 7 supported in the casing 5a, the power rollers 9, 9 via the displacement shaft 8 as in the conventional structure described above.
I support you. And these power rollers 9, 9
The peripheral surfaces 9a, 9a of the disk and the inner side surfaces 2a, 4a of the disks 2A, 2B, 4 are in contact with each other. Further, a hydraulic pressing device 36a is assembled between the input side disk 2A on the base end side and the input shaft 11b, and the above-mentioned surfaces 9a, 2a,
The surface pressure of the contact part (traction part) between the 4a is secured,
The power transmission by the toroidal type continuously variable transmission 30a can be efficiently performed.

In order to configure the pressing device 36a, an outward flange-shaped collar portion 73 is fixed to the outer peripheral surface of the input shaft 11b near the base end, and the input side disk 2A on the base end side is fixed. The cylinder cylinder 74 is connected to the input side disk 2
The outer surface of A (left surface of FIGS. 1 and 2) is oil-tightly fitted and supported in a state of protruding in the axial direction. The inner diameter of the cylinder cylinder 74 is small at the intermediate portion in the axial direction and is large at both end portions, and the input side disk 2A is oil-tightly and axially displaceable in the large diameter portion on the tip side thereof. Has been fitted inside. Further, an inward flange-shaped partition plate portion 75 is provided on the inner peripheral surface of the intermediate portion of the cylinder cylinder 74. Further, a first piston member 76 is provided between the inner peripheral surface of the cylinder cylinder 74 and the outer peripheral surface of the input shaft 11b.

The first piston member 76 has an outward flange-shaped partition plate 78 formed on the outer peripheral surface of the intermediate portion of a support cylinder 77 that can be externally fitted to the input shaft 11b. The peripheral edge is in sliding contact with the small diameter portion of the intermediate portion of the inner peripheral surface of the cylinder cylinder 74 so as to be oil-tight and axially displaceable. Further, in this state, the inner peripheral edge of the partition plate portion 75 is brought into sliding contact with the outer peripheral surface of the support tubular portion 77 in an oiltight manner so as to be displaceable in the axial direction. Furthermore, a circular ring-shaped second piston member 79 is provided between the outer peripheral surface of the base end portion of the support cylinder 77 and the inner peripheral surface of the base end portion of the cylinder cylinder 74. The second piston member 79 has a base end side surface on which the collar portion 7 is formed.
3 is prevented from axially displacing, and oil-tightness is maintained between the inner and outer peripheral edges and the outer peripheral surface of the base end portion of the support cylinder 77 and the inner peripheral surface of the base end of the cylinder cylinder 74. is doing.

Further, the cylinder cylinder 74 provided with the partition plate portion 75 is provided with a preload spring such as a disc leaf spring 80 provided between the partition plate portion 75 and the second piston member 79 so as to perform the input. It is pressed toward the side disk 2A. Therefore, the input side disk 2A is pressed by at least the pressing force commensurate with the resilience of the disc leaf spring 80 (even when the pressure oil is not introduced into the pressing device 36a), and the surfaces 9a, 2a, 4a are connected to each other. A surface pressure commensurate with this elasticity is applied to the contact portion of. Therefore, this elasticity causes slippage (excluding unavoidable spin) at each abutting portion between the surfaces 9a, 2a, 4a when the tiny power is transmitted by the toroidal type continuously variable transmission 30a. Regulate to the extent that no

Further, a central hole of the input shaft 11b is provided in hydraulic chambers existing between the second piston member 79 and the partition plate portion 75 and between the partition plate 78 and the input side disk 2A. The hydraulic pressure can be freely introduced via 81. The center hole 81 communicates with a hydraulic pressure source such as a pressurizing pump, which is also not shown, via a hydraulic pressure adjusting valve (not shown). During operation of the continuously variable transmission including the toroidal type continuously variable transmission 30a, the hydraulic pressure adjusted by the hydraulic pressure adjusting valve according to the magnitude of the power to be transmitted is introduced into each of the hydraulic chambers, and the input side is provided. Press the disk 2A,
A surface pressure commensurate with the magnitude of the power is applied to each contact portion between the surfaces 9a, 2a, 4a.

At this time, the surface pressure applied to each contact portion is the sum of the hydraulic pressure and the disc spring 80. Therefore, the hydraulic pressure required to prevent slippage at each of the abutting portions at the time of power transmission is low by the elasticity of the disc spring 80, and the hydraulic pressure is increased by the provision of the disc spring 80. The loss (pump loss) due to the drive of the source can be kept low. In the illustrated example, the pressing device 36a
Since it is a double piston type, the pressure receiving area is secured without increasing the diameter, and the hydraulic pressure for securing the required pressing force is kept low, so pump loss can be kept low from this aspect as well. In addition to the magnitude of the power to be transmitted, the factors to be considered when adjusting the hydraulic pressure are various factors that affect the operation of the toroidal continuously variable transmission 30a, such as the gear ratio and the temperature of the traction oil. You can incorporate elements.

Further, the rotational force is transmitted from the drive shaft 82 to the input shaft 11b via the collar portion 73. For this reason, at a plurality of outer peripheral edge portions of the collar portion 73,
The notches 83, 83 as shown in FIGS. 6 to 7 are formed, and the notches 83, 83 are engaged with the drive projections 84, 84 formed at the end of the drive shaft 82. There is. Therefore, in the case of this example, an outward flange-shaped connecting portion 85 is provided at the end portion of the drive shaft 82, and the driving convex portions 84, 84 are provided at the end portions of the connecting portion 85 on the one-side outer diameter side. Is protruding.

Further, hydraulic actuators 17a and 17b are provided on the trunnions 7 and 7, and the trunnions 7 and 7 are provided on both ends of the pivot shafts 6 and 6, respectively.
Displacement can be freely driven in the axial direction. Of these, the trunnion 7 in the lower center portion of FIG. 3 is a single-acting type (only a force in the pushing direction is obtained), and is leveraged by a pair of actuators 17a and 17a whose pushing directions are opposite to each other. Through the arms 86, 86, the shafts 6, 6 provided at both ends can be displaced and driven in the axial direction. When displacing the trunnion 7, pressure oil is sent only to the hydraulic chamber of one of the actuators 17a, and the hydraulic chamber of the other actuator 17a is released. On the other hand, the trunnions 7 and 7 on both upper sides of FIG. 3 are driven by the double-acting actuators 17b and 17b (which can obtain the force in the pushing direction or the pulling direction based on the switching of the pressure oil supply / discharge direction). , And can be displaced and driven in the axial direction of the pivots 6, 6 provided at both ends thereof.

The total displacement of the six trunnions 7, 7 provided in the toroidal type continuously variable transmission 30a is controlled by the control valve 21.
(See FIG. 12)
By supplying / discharging an equal amount of pressure oil to 7b, the same length is performed in synchronization with each other. Therefore, the precess cam 28 is fixed to the end of the rod 87 which is displaced together with any one of the trunnions 7 (the upper left side in FIG. 3 in the illustrated example), and the posture of the trunnions 7 is controlled by the link 29 via the link 29. Valve 2
It can be freely transmitted to one spool 24.

The operation of the toroidal type continuously variable transmission 30a configured as described above is as follows. During operation, the input side disk 2A on the base end side is pressed by the pressing device 36a.
While pressing, the input shaft 11b is rotated. As a result, the pair of input-side disks 2A and 2B provided at both ends of the input shaft 11b become the output-side disks 4 and 4, respectively.
It rotates while being pressed toward. This rotation is transmitted to the output disks 4, 4 via the power rollers 9, 9, and the rotations of the output disks 4, 4 are taken out through the output sleeve 62 and the output gear 12b.

In order to change the gear ratio between the input side disks 2A, 2B and the output side disks 4, 4, the trunnions 7, 7 supporting the power rollers 9, 9 are swung and displaced. In this case, the actuators 17a, 17b move the trunnions 7, 7 in the axial direction of the pivots 6, 6 provided at both ends of the trunnions 7, 7 so that the input disks 2A, 2B and the output disks are output. Four, four
With respect to the circumferential direction of, the same stroke is displaced in the same direction. By displacing the trunnions 7 and 7 in this way, the power rollers 9 and 9 supported by the trunnions 7 and 7 are similarly to the case of the conventional structure described above.
Peripheral surfaces 9a, 9a and the input-side and output-side disks 2A,
The direction of the tangential force acting on the abutting portions of the inner surfaces 2a and 4a of the power rollers 2B and 4 changes, and the peripheral surfaces 9a of the power rollers 9 and 9 are changed as shown in FIGS. , 9a and the abutting positions of the inner side surfaces 2a, 4a change, and the gear ratio changes.

On the other hand, each of the actuators 17a, 17
The displacement of the trunnion 7 on the upper left side of FIG. 3 due to the supply and discharge of the pressure oil to and from b is transmitted to the spool 24 via the precess cam 28 and the link 29, and the spool 2
4 is displaced in the axial direction. As a result, the flow path of the control valve 21 is closed and the supply and discharge of the pressure oil to and from the actuators 17a and 17b are stopped while the actuators 17a and 17b have stroked a predetermined amount. Therefore,
The displacement amount of each trunnion 7, 7 in the axial direction of the pivot shafts 6, 6 depends only on the displacement amount of the sleeve 23 (see FIG. 12) by the control motor 25.

The structure and operation of the toroidal type continuously variable transmission 30a are as described above, but the planetary gear mechanism 31 combined with the toroidal type continuously variable transmission 30a is used.
The a includes a sun gear 41, a ring gear 32, and planetary gear sets 43, 43. Of these, the sun gear 41 is fixed to the input side end (the left end in FIG. 1) of the output shaft 40a. Therefore, the output shaft 40a is connected to the sun gear 41.
Rotates with the rotation of. The ring gear 32 is supported around the sun gear 41 concentrically with the sun gear 41 and rotatably. And this ring gear 3
Plural sets of planetary gear sets 43, 43 are provided between the inner peripheral surface of 2 and the outer peripheral surface of the sun gear 41, each pair of planetary gears 42a, 42b being combined.
And, these planetary gears 42a and 42b of each one pair,
The planetary gears 42 meshed with each other and arranged on the outer diameter side.
a is engaged with the ring gear 32, and the planetary gear 42b arranged on the inner diameter side is engaged with the sun gear 41.
Such planetary gear sets 43, 43 are rotatably supported on one side surface (left side surface in FIG. 1) of the carrier 44. Further, the carrier 44 is provided around the intermediate portion of the output shaft 40a.
It is rotatably supported.

Further, the carrier 44 and the pair of output side disks 4 constituting the toroidal type continuously variable transmission 30a,
4 and 4 are connected by the first power transmission mechanism 45a in a state in which the rotational force can be transmitted. In order to configure the first power transmission mechanism 45a, a transmission shaft 46a parallel to the input shaft 11b and the output shaft 40a is provided, and a gear fixed to one end portion (the left end portion in FIG. 1) of the transmission shaft 46a. 88
Are meshed with the output gear 12b. A sleeve 89 is rotatably arranged around the intermediate portion of the output shaft 40a, and a gear 90 supported on the outer peripheral surface of the sleeve 89.
And a gear 91 fixed to the other end (right end in FIG. 1) of the transmission shaft 46a are meshed with each other via an idler gear (not shown). Further, the carrier 44 is supported around the sleeve 89 via a circular coupling bracket 101 so as to be rotatable in synchronism with the sleeve 89. Therefore, the carrier 44 rotates in a direction opposite to the output disks 4, 4 as the output disks 4, 4 rotate, at a speed corresponding to the number of teeth of the gears 12b, 88, 90, 91. Rotate. A low speed clutch 51a is provided between the carrier 44 and the output shaft 40a.

On the other hand, the input shaft 11b and the ring gear 32 are connected via an input side disk 2B supported at the tip of the input shaft 11b and a transmission shaft 34a arranged concentrically with the input shaft 11b. , It can be connected freely to transmit torque. Therefore, the input side disk 2
4 to a part of the outer side surface of B (right side surface of FIGS. 1 and 2), in the radial direction in a half portion of the outer side surface closer to the outer diameter than the central portion.
As shown in FIG. 5, a plurality of convex portions 92, 92 are provided in a protruding manner.
In the case of this example, each of these convex portions 92, 92 is arcuate, and is intermittently and equidistantly arranged on the same arc centered on the central axis of the input side disk 2B. . Then, between the circumferential end faces of the convex portions 92, 92 that are adjacent to each other in the circumferential direction, there are locking notches 93, 93. In other words, the locking notches 93, 93 are formed by removing the short cylindrical portions protruding from the outer surface of the input side disk 2B at equal intervals, and the locking notches 93 adjacent in the circumferential direction are formed. , 93 between the convex portions 92, 9
2

On the other hand, a transmission flange 95 is provided at the base end portion of the transmission shaft 34a, which is the transmission member described in claim 1, via a transmission tubular portion 94 having a conical tubular shape. Then, on the outer peripheral edge of the transmission flange 95, transmission projections 96, 96 are formed at the same number as the locking notches 93, 93 at equal intervals in the circumferential direction. Then, the transmission projections 96, 96 and the locking notches 93, 9 are provided.
3 is engaged with each other to enable torque transmission between the input side disk 2B and the transmission shaft 34a. The transmission projections 96, 96 and the locking notches 93, 9
Since the diameter of the engaging portion with 3 is sufficiently large, a sufficiently large torque can be transmitted between the input side disk 2B and the transmission shaft 34a.

In order to increase the torque that can be transmitted between the input side disk 2B and the transmission shaft 34a as much as possible, the projections 92, 92 are formed on the outer surface of the input side disk 2B. It is preferable to form the end portion (outer peripheral edge portion) near the outer diameter. However, when the respective convex portions 92, 92 are formed on the outer diameter side end portion of the outer side surface of the input side disk 2B,
It becomes difficult to secure the finishing accuracy of the inner side surface 2a of the input side disk 2B. That is, the peripheral surface 9a of the power roller 9
The inner side surface 2a, which transmits the torque based on the rolling contact with, needs to be finished in strict shape and dimensional accuracy. The finishing of the inner side surface 2a is performed by strongly pressing the grindstone against the inner side surface 2a while supporting the outer side surface of the input side disk 2B. At this time, in order to suppress the elastic deformation of the input side disk 2B and finish the shape and dimensional accuracy strictly, it is necessary to support the outer diameter portion of the outer surface.

Therefore, for example, a flat portion 97 having a width W _{97 in the} radial direction of 10 mm or more is formed on the outer peripheral portion of the outer surface located on the outer peripheral surface of each of the convex portions 92, 92. The portion 97 is used to support the outer surface outer diameter portion of the input side disk 2B during the finishing process. Further, the length of each of the transmitting projections 96, 96 in the circumferential direction is as close as possible to the width of each of the locking notches 93, 93 in the circumferential direction, and the locking notches 93, 93 are provided. The transmission projections 96, 96 are adapted to be engaged therein without rattling.

The tip of the transmission shaft 34a (the right end in FIG. 1) is rotatably supported at the center of the sun gear 41. Further, the ring gear 32 is provided around the intermediate portion of the transmission shaft 34a via the annular coupling bracket 98 and the high speed clutch 35a described later.
It is rotatably supported in synchronization with 4a. Therefore, when the high speed clutch 35a is engaged, the ring gear 32 is rotated along with the rotation of the input shaft 11b.
It rotates at the same speed in the same direction as b.

Further, the continuously variable transmission includes a clutch mechanism which constitutes the mode switching means described in claim 5. This clutch mechanism includes a reverse clutch provided between the high speed clutch 35a, the low speed clutch 51a, and a fixed portion such as the ring gear 32 and a fixed wall 99 provided in the housing of the continuously variable transmission. And a clutch 52a. Each of the clutches 35a, 51a, 52a is a wet multi-plate clutch, and is connected / disconnected based on the supply / discharge of pressure oil into / from the hydraulic cylinders attached to the clutches. Further, when any one clutch is connected, the remaining two clutches are disconnected.

In the continuously variable transmission constructed as described above, at the time of low speed traveling, first, the low speed clutch 51a is connected and the high speed clutch 35a and the reverse clutch 52a are disconnected. In this state, the input shaft 11b
When is rotated, only the toroidal type continuously variable transmission 30a transmits power from the input shaft 11b to the output shaft 40a. That is, in this state, the rotation of the output gear 12b of the toroidal type continuously variable transmission 30a is transmitted to the carrier 44 via the first power transmission mechanism 45a. By connecting the low speed clutch 51a, the rotation of the carrier 44 is transmitted to the output shaft 40a as it is, and the output shaft 40a having the sun gear 41 fixed thereto rotates. During such low-speed running, the toroidal type continuously variable transmission as shown in FIG. 13 is used for the gear ratio between the pair of input side disks 2A, 2B and the pair of output side disks 4, 4 respectively. Adjust as if alone. It should be noted that the low speed clutch may be any clutch as long as it does not allow relative displacement of the gears 32, 41, 42a, 42b constituting the planetary gear mechanism 31a, and is not necessarily between the carrier 44 and the output shaft 40a. There is no need to install it in.

However, in the case of the continuously variable transmission of this example, three powers are provided between each pair of the input side disks 2A, 2B and the output side disks 4, 4 and a total of six powers. Since the rollers 9 and 9 are provided, the power transmitted to each of the power rollers 9 and 9 can be suppressed low. Therefore, the inner side surfaces 2a, 4a of the above-mentioned disks 2A, 2B, 4 are
Even if the surface pressure of the contact portion between the power rollers 9 and 9 and the peripheral surfaces 9a and 9a is lowered, power can be transmitted without causing slippage in the contact portion. The surface pressure of each of the contact portions can be easily and reliably adjusted by adjusting the hydraulic pressure introduced into the hydraulic pressing device 36a. By suppressing the surface pressure of each of the contact portions to be low, the rolling fatigue life of each of the surfaces 2a, 4a, 9a can be improved. On the contrary, when the rolling fatigue life is the same, a larger power can be transmitted.

On the other hand, during high speed running, the high speed clutch 35a is connected and the low speed clutch 51a and the reverse clutch 52a are disconnected. When the input shaft 11b is rotated in this state, the input shaft 1b
1b to the output shaft 40a, the second power transmission mechanism 53 including the transmission shaft 34a, and the planetary gear mechanism 3
1a transmits power. That is, when the input shaft 11a rotates during the high speed running, this rotation causes the transmission shaft 3 to rotate.
4a, the coupling bracket 98, and the high speed clutch 3
5a, and is transmitted to the ring gear 32. The rotation of the ring gear 32 causes the plurality of planetary gear sets 4 to rotate.
It is transmitted to the sun gear 41 via 3, 43 and rotates the output shaft 40a to which the sun gear 41 is fixed. In this state, if the revolution speed of each planetary gear set 43, 43 is changed by changing the gear ratio of the toroidal type continuously variable transmission 30a, the gear ratio of the continuously variable transmission as a whole can be adjusted.

That is, the planetary gear sets 43, 43 revolve in the same direction as the ring gear 32 during the high speed running. Then, the slower the revolution speed of each planetary gear set 43, 43, the faster the rotation speed of the output shaft 40a to which the sun gear 41 is fixed. For example, when the revolution speed and the rotation speed of the ring gear 32 (both are angular velocities) are the same, the rotation speeds of the ring gear 32 and the output shaft 40a are the same. On the other hand, if the revolution speed is slower than the rotation speed of the ring gear 32, the rotation speed of the output shaft 40 becomes faster than the rotation speed of the ring gear 32. On the contrary, if the revolution speed is faster than the rotation speed of the ring gear 32,
The rotation speed of the output shaft 40 becomes slower than the rotation speed of the ring gear 32.

Therefore, at the time of high speed running, as the gear ratio of the toroidal type continuously variable transmission 30a is changed to the deceleration side, the gear ratio of the whole continuously variable transmission is changed to the speed increasing side. In such a high speed running state, torque is applied to the toroidal type continuously variable transmission 30a from the output side disks 4 and 4 instead of from the input side disks 2A and 2B (the torque applied at low speed is regarded as a positive torque). If the negative torque is applied). That is, the high speed clutch 35a
The torque transmitted to the input shaft 11b is connected to the planetary gear mechanism 3 via the transmission shaft 34a.
It is transmitted to the ring gear 32 of 1a. Therefore, input shaft 1
The torque transmitted from the 1b side to the input side disks 2A, 2B is almost eliminated.

On the other hand, a part of the torque transmitted to the ring gear 32 of the planetary gear mechanism 31a via the second power transmission mechanism 53 is transferred from the planetary gear sets 43, 43 to each other.
It is transmitted to the output side disks 4 and 4 via the carrier 44 and the first power transmission mechanism 45a. As described above, the torque applied to the toroidal type continuously variable transmission 30a from the output side disks 4 and 4 changes the gear ratio of the toroidal type continuously variable transmission 30a in order to change the gear ratio of the entire continuously variable transmission to the speed increasing side. Becomes smaller as is changed to the deceleration side. As a result, the torque input to the toroidal type continuously variable transmission 30a during high-speed traveling is reduced, and the toroidal type continuously variable transmission 30a is reduced.
The durability of the component a can be improved. Further, even when traveling at such a high speed, the magnitude of the power passing through the toroidal type continuously variable transmission 30a changes, but by adjusting the hydraulic pressure introduced into the pressing device 36a, the respective surfaces 2a, Four
The surface pressure of the contact portion between a and 9a is set to an appropriate value.

Further, when the output shaft 40a is reversely rotated in order to move the vehicle backward, the low speed clutch 51a and the high speed clutch 51a are disconnected, and the reverse clutch 52a is connected. As a result, the ring gear 32 is fixed, and the planetary gear sets 43, 43 revolve around the sun gear 41 while meshing with the ring gear 32 and the sun gear 41. Then, the sun gear 41 and the output shaft 40a to which the sun gear 41 is fixed rotate in the opposite direction to the above-described low speed running and the above high speed running.

When the continuously variable transmission of the present invention is used as an automatic transmission for automobiles, a torque converter or an electromagnetic clutch is started between the engine which is a drive source and the input shaft 11b. Install a clutch. However, the low speed clutch 51a may be provided with a mechanism as a starting clutch, and an independent starting clutch may be omitted. In this case, when the vehicle is stopped, the high speed clutch 35a and the reverse clutch 52a are disconnected in addition to the low speed clutch 51a. In this state, the toroidal type continuously variable transmission 30a and the first,
The second power transmission mechanisms 45a and 53 run idle, and no power is transmitted to the output shaft 40a. From this state, by gradually connecting the low speed clutch 51a, the stopped vehicle can be started smoothly.

Further, the illustrated example is based on the assumption that the continuously variable transmission of the present invention is used as an automatic transmission for automobiles, and therefore each of the high speed, low speed and reverse clutches 35 is used.
a, 51a, 52a are provided. On the other hand, when the continuously variable transmission of the present invention is used as a transmission for adjusting the operating speed of various industrial machines such as pumps while keeping the operating speed of the drive source constant, It suffices to operate the continuously variable transmission only in the above-described high-speed traveling state. Therefore, when the continuously variable transmission of the present invention is used for such an application, the transmission shaft 34 shown in FIG.
a and the ring gear 32 (the high speed clutch 35a
(Without intervening) to connect and fix in a synchronized and rotatable manner.
Further, the low speed clutch 51a for realizing the locked state of the planetary gear mechanism 31a and the reverse clutch 52 for fixing the ring gear 32 to the casing 5a.
Omit a.

[0078]

Since the present invention is constructed and operates as described above, a structure capable of transmitting a large torque between the constituent members, particularly a toroidal type continuously variable transmission and this toroidal type continuously variable transmission. It is possible to do without increasing the size of the continuously variable transmission incorporating the. Due to these, it is possible to realize a toroidal type continuously variable transmission and a continuously variable transmission that are capable of transmitting a large amount of power, have superior durability, and are small and lightweight.

[Brief description of drawings]

FIG. 1 is a sectional view of an essential part showing an example of an embodiment of the present invention.

FIG. 2 is an enlarged view of the left half of FIG.

3 is a sectional view taken along line AA of FIG.

FIG. 4 is a cross-sectional view of the input side disk that transmits torque between the transmission shaft and the drive shaft, taken out from the same direction as FIG.

FIG. 5 is a view seen from the right side of FIG.

6 is a side view of the input shaft taken out and viewed from the same direction as FIG. 1. FIG.

FIG. 7 is a view seen from the left side of FIG.

FIG. 8 is a side view showing a basic configuration of a conventionally known toroidal type continuously variable transmission in a state of maximum deceleration.

FIG. 9 is a side view showing the same state at the time of maximum acceleration.

FIG. 10 is a sectional view showing an example of a conventional specific structure.

11 is a sectional view taken along line BB of FIG.

FIG. 12 is a front view of relevant parts showing a first example of a conventionally known structure for increasing the power that can be transmitted, with a part thereof being cut away.

FIG. 13 is a partial cross-sectional view showing the second example.

FIG. 14 is a schematic cross-sectional view showing an example of a continuously variable transmission in which a toroidal type continuously variable transmission and a planetary gear mechanism are combined.

[Explanation of symbols]

1 input axis 2, 2A, 2B Input side disc 2a Inside surface 3 output axes 4 Output side disc 4a inner surface 5, 5a casing 6 Axis 7 trunnions 8 displacement axes 9 power rollers 9a peripheral surface 10 Loading cam device 11, 11a, 11b Input shaft 12, 12a, 12b Output gear 13 Support plate 14 Thrust ball bearing 15 Thrust needle bearing 16 outer ring 17, 17a, 17b Actuator 18 frames 19, 19a Support piece 20 hydraulic cylinder 21 Control valve 22 pumps 23 Sleeve 24 spools 25 control motor 26 Drive piston 27 oil sump 28 Precessum 29 links 30, 30a toroidal type continuously variable transmission 31, 31a Planetary gear mechanism 32 ring gear 33 Support plate 34, 34a Transmission shaft 35, 35a High speed clutch 36, 36a Pressing device 37 engine 38 crankshaft 39 Starting clutch 40, 40a Output shaft 41 sun gear 42a, 42b planetary gears 43 Planetary gear set 44 career 45, 45a First power transmission mechanism 46, 46a Transmission shaft 47a, 47b sprockets 48 chains 49 first gear 50 second gear 51, 51a Low speed clutch 52, 52a Reverse clutch 53 Second power transmission mechanism 54 ball spline 55 loading nut 56 Mounting part 57 frames 58 mounting holes 59 Stud 60 nuts 61 gear housing 62 Output sleeve 63 Rolling bearing 64 holding part 65 Second Axis 66 Mounting part 67 Support plate 68 circular holes 69 radial needle bearing 70 outer ring 71 long hole 72 Stud 73 Tsubabe 74 cylinder 75 Partition plate 76 First piston member 77 Support tube 78 Partition plate 79 Second piston member 80 Disc leaf spring 81 Center hole 82 Drive shaft 83 Notches 84 Drive projection 85 Connection 86 arms 87 rod 88 gears 89 sleeve 90 gears 91 gears 92 convex 93 Locking notch 94 Transmission tube 95 Transmission flange 96 Transmission projection 97 Flat part 98 coupling bracket 99 fixed wall 100 drive shaft 101 coupling bracket

Claims (5)

[Claims] 1. An input side disc, an output side disc which is arranged concentrically with the input side disc and is rotatable independently of the input shaft, and between the input side disc and the output side disc. A plurality of trunnions that are provided and swing around a pivot that is in a twisted position with respect to the center axis of each of these disks, and one displacement axis that projects from the inner surface of each of these trunnions And one power roller for each trunnion sandwiched between the inner surfaces of the input side disc and the output side disc while being rotatably supported by the respective displacement shafts. In the toroidal type continuously variable transmission, a part of the outer side surface of at least one of the input side disk and the output side disk, which is the central portion of the outer side surface in the radial direction. By engaging a plurality of protrusions protruding on the half portion closer to the outer diameter with the tip of a transmission projection provided on a transmission member for transmitting torque between the disc, A toroidal-type continuously variable transmission characterized by enabling torque transmission between a disc and a transmission member. 2. An input side disk, an output side disk which is arranged concentrically with the input side disk and is rotatable independently of the input shaft, and between the input side disk and the output side disk. A plurality of trunnions that are provided and swing around a pivot that is in a twisted position with respect to the center axis of each of these disks, and one displacement axis that projects from the inner surface of each of these trunnions And one power roller for each trunnion sandwiched between the inner surfaces of the input side disc and the output side disc while being rotatably supported by each of these displacement shafts, and A first rotary shaft that is freely rotatable in synchronization with one of the input-side disc and the output-side disc; and the first rotary shaft that is arranged concentrically with the first rotary shaft. while In a toroidal type continuously variable transmission having a second rotary shaft for transmitting torque by means of an outer peripheral edge portion of an outward flange-shaped flange portion provided on an outer peripheral surface of an end portion of the first rotary shaft. By engaging a plurality of notches formed in the, and the drive projection formed at the end of the second rotating shaft, between the second rotating shaft and the first rotating shaft A toroidal type continuously variable transmission characterized by enabling the transmission of torque. 3. An input shaft connected to a drive source and driven to rotate by the drive source, an output shaft for extracting power based on the rotation of the input shaft, a toroidal type continuously variable transmission,
A planetary gear mechanism, a first power transmission mechanism that transmits the power input to the input shaft via the toroidal type continuously variable transmission, and the power input to the input shaft to the toroidal type continuously variable transmission. And a second power transmission mechanism that transmits without passing through the toroidal type continuously variable transmission. The toroidal type continuously variable transmission is supported by both ends of the input shaft and rotates with the rotation of the input shaft. Discs are arranged concentrically with the respective input side discs around the intermediate portion of the input shaft in a state where the inner side faces of the respective input side discs face the inner side faces of these respective input side discs, and are independent of these respective input side discs. And a pair of output side disks which are rotatable in synchronism with each other, and a pivot shaft which is provided between the input side disks and the output side disks and is in a twisted position with respect to the center axis of each of the disks. Inside A plurality of trunnions for each of the pair of input side discs and output side discs, and a displacement shaft protruding from the inner surface of each of these trunnions, one for each trunnion, and each of these displacements. In a state of being rotatably supported by the shaft, it was sandwiched between the inner surfaces of the input side disks and the output side disks,
One power roller for each trunnion, and a force for sandwiching each power roller between each input side disk and each output side disk on the basis of hydraulic pressure is applied to each input side disk and each output side disk. A pressure device provided in parallel to the input shaft with respect to the power transmission direction, which is applied corresponding to the magnitude of the force transmitted between the input shaft, and a pressing device provided around the input shaft, The planetary gear mechanism is a planetary gear rotatably supported by a carrier which is provided between a sun gear and a ring gear arranged around the sun gear and is concentrically and rotatably supported by the sun gear, The sun gear and the ring gear are meshed with each other, and the power transmitted through the first power transmission mechanism and the power transmitted through the second power transmission mechanism are the sun gear. The output shaft is connected to two members of the ring gear and the carrier, and the output shaft is connected to the remaining one member of the sun gear, the ring gear, and the carrier. The second power transmission mechanism has a transmission shaft and is a part of the outer surface of one input side disk supported by one end of the input shaft, and has an outer diameter in the radial direction that is larger than the central portion of the outer surface. By engaging a plurality of convex portions projecting on the side half with the tip of a transmission projection extending radially outward from the end of the transmission shaft, the transmission from the one input side disk A continuously variable transmission that freely transmits rotational force to the shaft. 4. An outer peripheral surface of the other end portion of the input shaft is provided with an outward flange-shaped flange portion, and a plurality of notches formed in the outer peripheral edge portion of the flange portion and a driving convex portion formed at the tip end portion of the drive shaft. The continuously variable transmission according to claim 3, wherein the input shaft is rotatably driven by the drive shaft by engaging with and. 5. Mode switching means for switching the state in which the power input to the input shaft is sent to the planetary gear mechanism through the first power transmission mechanism and the second power transmission mechanism is provided, and this mode switching means is provided. A first mode in which power is transmitted only by the first power transmission mechanism, and a second mode in which power is transmitted by both the first power transmission mechanism and the second power transmission mechanism. , The power is transmitted only by the first power transmission mechanism, and the rotation direction of the output shaft is switched to the third mode which is opposite to the first and second modes. The continuously variable transmission according to any one of claims 3 to 4.