JPH06174036A - Toroidal type continuously variable transmission - Google Patents

Abstract

PURPOSE:To reduce the loading frequency of a reversing mechanism and to realize small size of gear used for the reversing mechanism. CONSTITUTION:In the advancing condition, a clutch 14 for advance is connected, and a clutch 28 for backing is disconnected, the rotations of output disks 3 and 5 are transmitted to an output gear 13 from a connecting member 12 through the clutch 14 for advance, and the rotating direction of the output gear 13 is reversed by a reversing mechanism 16, and transmitted to an output shaft 15. In this case, the rotating direction of the output shaft 15 is made same as the rotating direction of an input shaft 1. And in the backing condition, the clutch 14 for advance is disconnected, and the rotations of the output disks 3 and 5 are not transmitted to the reversing mechanism 16. And the clutch 28 for backing is connected, and the rotation in the direction reverse to the rotation of the input shaft 1 is transmitted to the output shaft 15 through a planetary gear mechanism 22.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a toroidal type continuously variable transmission applied to an automobile or the like, and more particularly to a double cavity type toroidal type continuously variable transmission in which two sets of toroidal transmission parts are coaxially arranged. .

[0002]

2. Description of the Related Art Generally, a toroidal type continuously variable transmission is provided with a toroidal speed change portion composed of an input disk, an output disk and a power roller arranged between the disks, and an input disk driven by an input shaft. It is configured to transmit the rotational power of the power disc to the output disc via the power roller, and to transmit the rotational power from the output disc to the output shaft. By changing the inclination of the power roller, the gear ratio can be continuously changed. It is possible.

In a conventional toroidal type continuously variable transmission, for example, as shown in FIG. 2, an input disk 2, an output disk 3 arranged to face the input disk 2, and a torque from the input disk 2 to the output disk 3 are applied. A first toroidal transmission unit 6 including a tiltable power roller 8 for transmitting, an input disc 4, an output disc 5 arranged to face the input disc 4, and a tilt for transmitting torque from the input disc 4 to the output disc 5. Second, consisting of a rollable power roller 9
The toroidal transmission unit 7 is included. This toroidal type continuously variable transmission is referred to as a double-cavity toroidal type continuously variable transmission, in which these two sets of toroidal transmission units 6 and 7 are arranged to face each other on the input shaft 1. .

The input disk 2 is supported so as to be rotatable relative to the input shaft 1. However, the input disk 2 is drivingly connected to the input shaft 1 via a loading cam (not shown) and can rotate integrally with the input shaft 1. The input disk 4 is also supported so as to be rotatable relative to the input shaft 1, but can be drivingly connected to the input shaft 1 via another loading cam (not shown) and can rotate integrally with the input shaft 1. The output disks 3 and 5 are arranged to face the input disks 2 and 4, respectively, and are rotatably supported with respect to the input shaft 1. The two output disks 3, 5 are connected to each other by a connecting member 12
Since they are connected with each other, they can rotate together. The output gear 13 fixed to this connecting member 12 is
It is drivingly connected to the output shaft 15 via a reversing mechanism 16. The reversing mechanism 16 has a counter shaft 17 arranged parallel to the input shaft 1. The counter shaft 17 has one end fixed with a gear 18 meshing with the output gear 13 and the other end fixed with a gear 19 meshing with an intermediate gear 20. The intermediate gear 20 meshes with the gear 21 of the output shaft 15.

The power roller 8 is arranged between the input disk 2 and the output disk 3 and frictionally engages with the toroidal surfaces of the two disks 2 and 3, and the power roller 9 is arranged between the input disk 4 and the output disk 5. Placed on both discs 4,
5 frictionally engages the toroidal surface of 5. Power rollers 8, 9
Are respectively rotatable about their own rotation axis 10 and tilt about a tilt axis 11 orthogonal to the rotation axis 10.

In this toroidal type continuously variable transmission, in order to make the tilt angles of the power rollers 8 and 9 coincide with each other, the power rollers 8 and 9 are synchronously tilted by a link mechanism or the like. ing. When the tilt angles of the power rollers 8 and 9 change, the power rollers 8 and 9 are changed accordingly.
The frictional engagement points of the input disks 2, 4 and the output disks 3, 5 change, and continuously variable transmission is performed.

By the way, in this type of toroidal type continuously variable transmission, the torque output from the engine is input to the toroidal type continuously variable transmission via the input shaft 1, and further the toroidal type continuously variable transmission outputs from the toroidal type continuously variable transmission. It is arranged so as to be transmitted to the differential device via. And
A forward / reverse switching device is usually provided in the middle of the torque transmission path so that the vehicle can be selectively switched between forward and reverse.

Various forward / reverse switching devices have been disclosed in the past. For example, in the toroidal type continuously variable transmission (hereinafter referred to as A type) shown in FIG.
A double pinion type planetary gear mechanism 30 and two sets of clutches 31, 32 are provided between the engine and the toroidal transmission units 6, 7.
Is provided, and the direction of input rotation to the toroidal speed change units 6 and 7 is switched by a combination of connection and disconnection of these clutches 31 and 32.

The arrangement structure of the planetary gear mechanism 30 and the clutches 31 and 32 will be specifically described. The input shaft 1 is connected to a ring gear 33 of the planetary gear mechanism 30 via a forward clutch 31. The ring gear 33 is connected to the casing 34 via the reverse clutch 32. On the other hand, the input shaft 1 is the carrier 35 of the planetary gear mechanism 30.
Are linked to. The carrier 35 rotatably supports a first pinion gear 37 that meshes with the sun gear 36 and a second pinion gear 38 that meshes with the first pinion gear 37 and the ring gear 33. The sun gear 36 is connected to the input disk 2. An example of this type A forward / reverse switching device is disclosed in Japanese Patent Application Laid-Open No. 61-99761.

The A-type forward / reverse switching device has the above-mentioned structure, and when the vehicle is moving forward, the forward clutch 31 is used.
Is operated and the reverse clutch 32 is disengaged.
In this case, as the input shaft 1 rotates, the planetary gear mechanism 30
Rotate integrally with each other in the same direction as the rotation direction of the input shaft 1, and the torque is transmitted to the input disk 2. On the other hand, in reverse, the forward clutch 31 is disengaged and the reverse clutch 32 is engaged. In this case, since the ring gear 33 is fixed to the casing 34, the carrier 35 integrally rotates in the same direction as the input shaft 1 as the input shaft 1 rotates. Then, the ring gear 33
The second pinion gear 38 that meshes with the first pinion gear 37 rotates in the opposite direction, the first pinion gear 37 that meshes with the second pinion gear 38 rotates in the positive direction, and the sun gear 36 that meshes with the first pinion gear 37 rotates in the opposite direction. So
Rotation in the opposite direction is transmitted to the input disk 2.

In the toroidal type continuously variable transmission (hereinafter referred to as B type) shown in FIG. 3, two sets of gears 13 and 39 are provided on a connecting member 12 that connects the output disks 3 and 5 of the toroidal transmissions 6 and 7. The clutches 40 and 41 are provided, and the direction of output rotation from the toroidal type continuously variable transmission is switched by a combination of connection and disconnection of these clutches 40 and 41.

Two sets of gears 13, 39 and clutches 40, 4
The arrangement structure of 1 will be specifically described. The connecting member 1
Two output gears 13 and 39 are fixed to the second gear 13. One output gear 13 is drivingly connected to the forward clutch 40, but the other output gear 39 meshes with the intermediate gear 42, and the intermediate gear 42 It is drivingly connected to the reverse clutch 41 via. The forward clutch 40 and the reverse clutch 41 are provided on the counter shaft 17, and the counter shaft 17 is drivingly connected to the output shaft 15 via the intermediate gear 20. An example of the B type forward / reverse switching device is disclosed in Japanese Patent Application Laid-Open No. 61-96258.

The B type forward / reverse switching device has the above-described structure, and when the vehicle is moving forward, the forward clutch 40 is used.
Is operated and the reverse clutch 41 is disengaged.
In this case, the gear 43 rotates in the opposite direction with the rotation of the output gear 13, the rotation of the gear 43 is transmitted to the counter shaft 17 via the forward clutch 40, and further the gear 19, the intermediate gear 20, and the gear 21. And is transmitted to the output shaft 15. Since the output shaft 15 rotates in the direction opposite to the rotation direction of the output gear 13, it eventually rotates in the same direction as the input shaft 1.
On the other hand, when moving backward, the forward clutch 40 is disengaged and the reverse clutch 41 is engaged. In this case, the intermediate gear 42 reversely rotates in accordance with the rotation of the output gear 39, and the counter shaft 1 is further transmitted through the reverse clutch 41.
7 rotates forward. The counter shaft 17 is rotated by the intermediate gear 20.
Since it is transmitted to the output shaft 15 via, the output shaft 15 rotates in the same direction as the output gear 39.

The toroidal type continuously variable transmission (hereinafter referred to as the C type) shown in FIG. 4 includes a pair of reverse gears 44 and a clutch 4 between the engine and the toroidal transmissions 6 and 7.
5 is provided, and one set of gears 13 for forward movement and a clutch 46 are provided between the toroidal speed change parts 6, 7 and the output shaft 15, and a set of connection and disconnection of these clutches 45, 46 is provided. The direction of output rotation from the toroidal type continuously variable transmission is switched according to the adjustment.

A set of gears 44 and a clutch 45 for reverse travel,
Further, the arrangement structure of the forward gear set 13 and the clutch 46 will be specifically described. The input shaft 1 is connected to the output gear 44 through the reverse clutch 45. Also,
An output gear 13 is connected to a connecting member 12 that connects the output disks 3 and 5 via a forward clutch 46. Further, the respective output gears 44 and 13 are connected to the input shaft 1
Is connected in parallel to a count shaft 17, which is connected to an output shaft 15 via an intermediate gear 20.

The C type forward / reverse switching device has the above-mentioned structure, and when the vehicle is moving forward, the forward clutch 46 is used.
Is connected and the reverse clutch 45 is disengaged.
In this case, when the input shaft 1 rotates, the forward clutch 46
The output gear 13 rotates in the opposite direction via the
The gear 48 that meshes with the input shaft 1 rotates in the same direction as the input shaft 1, and the counter shaft 17 rotates accordingly.
The output shaft 15 rotates in the same direction as the input shaft 1 via 0. On the other hand, when moving backward, the forward clutch 46 is disengaged, and the reverse clutch 45 is engaged.
In this case, when the input shaft 1 rotates, the reverse clutch 45
The output gear 44 rotates via the gear, and the counter shaft 17 rotates in the opposite direction via the gear 47 meshing with the output gear 44,
Along with this, the rotation of the counter shaft 17 is transmitted to the output shaft 15 via the intermediate gear 20, and the output shaft 15 rotates in the opposite direction to the input shaft 1.

[0017]

However, in the A type, between the engine and the toroidal speed change parts 6 and 7,
Since the double pinion type planetary gear mechanism 30 is arranged, the rotational directions of the toroidal speed change units 6 and 7 are reversed between forward and reverse, so that the speed change control of the toroidal speed change units 6 and 7 becomes complicated. Further, since the clutches 31 and 32 are arranged on the engine side of the toroidal transmissions 6 and 7, when the wheels are locked, such as when the brakes are suddenly applied while running on a snowy road, the toroidal type The continuously variable transmission is locked at the shift position at that time, and when the toroidal transmission unit is locked at a shift position other than the maximum reduction ratio, the power becomes insufficient and the vehicle cannot start again. Therefore, if the gear can be shifted to the maximum deceleration position, the power shortage can be solved, but since the gear cannot be changed without the output shaft rotating, there is a problem that the vehicle cannot be started.

In the B type, since the clutches 40, 41 are provided in the power transmission path from the toroidal transmissions 6, 7 to the differential device, the toroidal transmission can rotate together with the engine during idling. Therefore, even if the toroidal type continuously variable transmission is locked at a position other than the maximum deceleration position, the vehicle can start again by promptly shifting to the maximum deceleration position during idling. Therefore, with the B type, the problem of the A type is solved. However,
In the B type, since the clutches 40 and 41 are arranged not on the input shaft 1 but on the counter shaft 17, there is a problem that the entire device becomes large in the width direction.

The C type has the same advantage as the B type in that it can solve the problem of the A type, and has the advantage that the size of the reverse clutch can be reduced. However, in this C type, in order to be applied to a rear-wheel drive transmission (T / M for FR), the counter shaft 17 becomes long, and the output gear 44 and the reverse clutch 45 are arranged in series in the axial direction. However, there is a problem that the entire device becomes large.

It can be said that the type A, type B and type C are commonly used. However, since the reverse rotation mechanism 16 is used for transmitting torque to the output shaft 15 in both forward and reverse movements, the reverse rotation mechanism is used. The load frequency of each gear of 16 is high,
There is a problem that the life of those gears is shortened. Further, in order to obtain a predetermined life, it is necessary to take measures such as enlarging each gear, which leads to an increase in size of the entire device.

Therefore, an object of the present invention is to solve the above-mentioned problems, and in a double-cavity toroidal type continuously variable transmission in which a clutch is arranged between the toroidal transmission unit and the output shaft, a reverse rotation mechanism is provided. The problem is to reduce the frequency of torque transmission and to arrange the clutch on the input shaft.By solving this problem, the gear of the reversing mechanism is downsized, the entire device is downsized, and the rear wheel drive is A double cavity toroidal type continuously variable transmission that can be applied as a transmission for a vehicle.

[0022]

In order to achieve the above object, the present invention is configured as follows. That is,
The present invention relates to an input shaft, a pair of input disks that rotate integrally with the input shaft, a pair of output disks that are arranged to face each of the input disks and that are rotatably supported with respect to the input shaft, A tiltable power roller disposed between the input disk and the output disk and transmitting torque from the input disk to the output disk, a connecting member connecting the output disks to each other, and rotatable to the connecting member. An output gear supported on the output gear, a forward clutch that connects and disconnects the output gear and the connecting member, an output shaft arranged on the same shaft as the input shaft, and the rotation of the output gear is reversed to be transmitted to the output shaft. A reverse rotation mechanism, a planetary gear mechanism that is arranged between the input shaft and the output shaft, reverses the rotation of the input shaft and transmits the rotation to the output shaft, and the planetary gear mechanism. About the toroidal type continuously variable transmission having a reverse clutch for switching the rolling state or a torque transmission state.

In this toroidal type continuously variable transmission, the planetary gear mechanism includes a sun gear that rotates integrally with the input shaft, a pinion gear that meshes with the sun gear, a carrier that rotatably supports the pinion gear, and the pinion gear. The reverse clutch has a ring gear that meshes with and is connected to the output shaft, and connects and disconnects the carrier to and from the casing.

Further, in this toroidal type continuously variable transmission, the reversing mechanism is a counter shaft arranged in parallel with the input shaft, a first gear fixed to one end of the counter shaft and meshing with the output gear, It has a second gear fixed to the other end of the counter shaft, an intermediate gear meshing with the second gear, and a gear meshing with the intermediate gear and fixed to the output shaft.

[0025]

Since the present invention is constructed as described above, it operates as follows. That is, in the toroidal continuously variable transmission according to the present invention, the forward clutch is a clutch that connects and disconnects the connecting member that connects the two output disks and the output gear rotatably supported by the connecting member. Further, the reverse clutch is a clutch that switches a planetary gear mechanism arranged on the same shaft as the input shaft to an idle state or a transmission state. Therefore, both of the clutches are arranged on the same shaft as the input shaft, and the width of the device can be reduced.

Further, in the toroidal type continuously variable transmission according to the present invention, the torque transmitted from the input shaft to the input discs of the respective toroidal transmission units is transmitted to the output discs via the power rollers. At this time, the rotation direction of the output disk is opposite to the rotation direction of the input shaft. When moving forward, the forward clutch is connected and the reverse clutch is disengaged. At this time, the rotation of the output disc is transmitted from the connecting member to the output gear through the forward clutch,
Since the rotation direction of the output gear is reversed by the reverse rotation mechanism and transmitted to the output shaft, the rotation direction of the output shaft eventually becomes the same as the rotation direction of the input shaft. On the other hand, when moving backward, the forward clutch is disengaged, so that the rotation of the output disk is not transmitted to the reverse mechanism. However, since the reverse clutch is connected, the rotation of the input shaft is reversed and transmitted to the output shaft via the planetary gear mechanism. Therefore, the torque is transmitted to the reverse rotation mechanism only when moving forward, and the torque is not transmitted to the reverse rotation mechanism when moving backward, so that the load frequency of the reverse rotation mechanism is reduced.

[0027]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT An embodiment of a toroidal type continuously variable transmission according to the present invention will be described below with reference to the drawings. FIG. 1 is a schematic structural diagram showing an embodiment of a toroidal type continuously variable transmission according to the present invention. This toroidal-type continuously variable transmission is a double-cavity toroidal-type continuously variable transmission in which two sets of toroidal transmissions 6 and 7 are coaxially opposed to each other. The first toroidal transmission unit 6 is disposed between the first input disc 2, the first output disc 3 arranged to face the first input disc 2, and the first input disc 2 and the first output disc 3. The first power roller 8 frictionally engages with the toroidal surfaces of both disks. Similarly to the first toroidal transmission unit 6, the second toroidal transmission unit 7 also has a second input disk 4, a second output disk 5 arranged to face the second input disk 4, a second input disk 4, and a second input disk 4. The second power roller 9 is disposed between the two output disks 5 and frictionally engages with the toroidal surfaces of both disks. Each of the toroidal transmissions 6 and 7 is provided with two power rollers. Each of the first power roller 8 and the second power roller 9 is rotatable about its own rotation axis line 10, and this rotation axis line 10 is also rotatable.
Tilting movement is performed around a tilting axis 11 that is orthogonal to.

The input shaft 1 is rotatably supported by a casing (not shown), and the engine torque is input to the input shaft 1 via a torque converter (not shown). Although the first input disk 2 is rotatably supported with respect to the input shaft 1, it can be driven and connected to the input shaft 1 via a loading cam (not shown) and can rotate integrally with the input shaft 1. The first, which is arranged to face the first input disk 2,
The output disk 3 is rotatably supported with respect to the input shaft 1. The second input disk 4 is rotatably supported with respect to the input shaft 1, but is drivingly connected to the input shaft 1 via another loading cam (not shown).
It can rotate together with. The second output disk 5 arranged so as to face the second input disk 4 is rotatably supported on the input shaft 1.

First output disk 3 and second output disk 5
Are connected to each other by connecting members 12 at their back surfaces, and can rotate integrally around the input shaft 1. The output gear 13 is rotatably supported by the connecting member 12. The connecting member 12 and the output gear 13 are connected by a forward clutch 14, and the forward clutch 14 is arranged on the same axis as the input shaft 1. Forward clutch 1
4 is connected during forward movement and can transmit torque from the connecting member 12 to the output gear 13. When moving backward, the forward clutch 14 is disengaged, so that torque is not transmitted from the connecting member 12 to the output gear 13.

The output shaft 15 is arranged on the same axis as the input shaft 1, and a reverse rotation mechanism 16 is arranged between the output gear 13 and the output shaft 15. The reverse rotation mechanism 16 includes a counter shaft 17 arranged parallel to the input shaft 1 and the counter shaft 17
The first gear 18 fixed to one end of the counter gear 17 and meshing with the output gear 13 and the second gear 1 fixed to the other end of the counter shaft 17.
9, an intermediate gear 20 that meshes with the second gear 19, and a gear 21 that meshes with the intermediate gear 20 and is fixed to the output shaft 15.
It consists of and. Due to the action of the reversing mechanism 16, the rotation of the output gear 13 turns in the opposite direction and the output shaft 15 rotates.
Be transmitted to.

The counter shaft 17 of the reversing mechanism 16 is
Since the length is almost equal to the distance from the output gear 13 to the gear 21, the counter shaft 17 is shorter than the B type shown in FIG. 3 or the C type shown in FIG. Further, only two bearings are required to support the counter shaft 17. B
In the type, a bearing for supporting the forward clutch and the reverse clutch is also required in addition to the bearing for supporting the counter shaft. In the C type, since the counter shaft is long and there are three sets of gear transmissions, three sets of bearings are required. Therefore, the toroidal type continuously variable transmission according to the present invention can reduce the number of bearings used as compared with the B type and C type.

A planetary gear mechanism 22 is arranged between the input shaft 1 and the output shaft 15. The planetary gear mechanism 22 has a function of reversing the rotation of the input shaft 1 and transmitting it to the output shaft 15. The planetary gear mechanism 22 includes a sun gear 23 fixed to the tip of the input shaft 1 and rotating integrally with the input shaft 1, and a sun gear 23.
The pinion gear 24 meshes with the pinion gear 24, the carrier 25 that rotatably supports the pinion gear 24, and the ring gear 26 that meshes with the pinion gear 24 and is connected to the output shaft 15. A reverse clutch 28 is provided between the carrier 25 and the casing 27.
When the reverse clutch 28 is engaged, the carrier 25
Is fixed to the casing 27, and the torque can be transmitted from the input shaft 1 to the output shaft 15. On the contrary, when the reverse clutch is disengaged, the carrier 25 becomes rotatable, so that the input shaft 1 becomes idle with respect to the output shaft 15, and the torque is transmitted from the input shaft 1 to the output shaft 15. Disappear.

In this toroidal type continuously variable transmission, the planetary gear mechanism 22 is used as a mechanism for the reverse movement, and further, the reverse clutch 28 is arranged outside the circumference of the planetary gear mechanism 22. , The mechanism for reverse drive is B
It is shortened in the axial direction as compared with the type and C type. Further, since the reverse clutch 28 is also arranged on the same axis as the input shaft 1 like the forward clutch 14, the width of the entire device, that is, the length in the direction perpendicular to the axial direction is also shortened. Therefore, the entire device is miniaturized. Further, since the planetary gear mechanism 22 is used as the mechanism for the reverse movement, the reaction force of the gear can be canceled internally. Therefore, the conventional B
The radial bearing for supporting the gear, which was necessary for the type C and type C, is no longer required.

The toroidal type continuously variable transmission is constructed as described above. Next, the operation of this toroidal type continuously variable transmission will be described. When torque is input to the input shaft 1 as the engine operates, the torque is transmitted to the first input disk 2 via the loading cam. At the same time, the torque is transmitted from the input shaft 1 to the second input disk 4 via another loading cam. When the torque is transmitted to the first input disc 2, the first input disc 2 rotates, the first power roller 8 rotates with the rotation, and the rotation is transmitted to the first output disc 3. Further, the torque transmitted to the second input disc 4 is transmitted to the second output disc 5 via the second power roller 9. During this transmission, when the power rollers 8 and 9 are synchronized and tilted about the tilt axis 11 by the same angle, the frictional relationship between the power rollers 8 and 9 and the input disks 2 and 4 and the output disks 3 and 5 is increased. The point of change changes, and continuously variable transmission can be performed.

The rotation direction of the output disks 3 and 5 is the input shaft 1
Opposite to the direction of rotation. When moving forward, the forward clutch 14 is connected and the reverse clutch 28 is disengaged. At this time, the output disks 3 and 5 are rotated by the connecting member 12
Is transmitted to the output gear 13 via the forward clutch 14, and the rotation direction of the output gear 12 is reversed by the reverse rotation mechanism 16 and transmitted to the output shaft 15, so that the rotation direction of the output shaft 15 is eventually changed to the input shaft 1 It becomes the same as the rotation direction of. On the other hand, when the vehicle is moving backward, the forward clutch 14 is disengaged, so that the rotation of the output disks 3 and 5 is not transmitted to the reverse rotation mechanism 16.
However, since the reverse clutch 28 is connected, the rotation in the direction opposite to the rotation of the input shaft 1 is transmitted to the output shaft 15 via the planetary gear mechanism 22. Therefore, the torque is transmitted to the reversing mechanism 16 only when moving forward. in this way,
Since the gears that transmit power to the output shaft 15 are independent for forward movement and reverse movement, the load frequency applied to each gear of the reverse rotation mechanism is reduced, and conventional A type, B type, and C type In comparison, the gear can be downsized.

When the output shaft 15 is in a stopped state,
To shift gears, the forward clutch 14 may be disengaged. When the forward clutch 14 is disengaged, the toroidal transmission unit 6,
No load on the output side is applied to 7. In this state, the rotation of the input disks 2 and 4 is transmitted to the output disks 3 and 5 via the power rollers 8 and 9, so that the tilt angle of the power rollers 8 and 9 can be changed. Therefore,
Even when the wheels are locked when the toroidal transmission units 6 and 7 are in the shift positions other than the maximum deceleration position, the vehicle can be started again by shifting to the maximum deceleration position during idling.

In the above embodiment, the gear transmission mechanism is used as the reversing mechanism, but the invention is not limited to this, and other reversing mechanisms such as a transmission mechanism using a chain and a sprocket, or A belt transmission mechanism or the like may be used.

[0038]

Since the present invention is constructed as described above, it has the following effects. That is, in this toroidal type continuously variable transmission, torque is transmitted from the input shaft to the output shaft through the toroidal transmission unit and the reverse rotation mechanism when moving forward, but the torque is not transmitted to the reverse rotation mechanism when moving backward,
Since it is configured to be directly transmitted from the input shaft to the output shaft via the planetary gear mechanism, it is possible to reduce the load frequency applied to each gear of the reverse rotation mechanism, and thus the conventional toroidal type continuously variable transmission. It is possible to reduce the size of the gear compared to.

Further, since a planetary gear mechanism is used as a mechanism for reverse, and a clutch for reverse is arranged outside the circumference of the planetary gear mechanism, the mechanism for reverse is B type. It is shortened in the axial direction as compared with the C type. Also, since the reverse clutch is arranged on the same axis as the input shaft, like the forward clutch, the width of the entire device, that is, the length in the direction perpendicular to the axial direction is also reduced. Therefore, the entire device is miniaturized.

The length of the counter shaft of the reversing mechanism is 2
Since the distance from the output gear arranged between two toroidal speed change parts to the gear of the output shaft is almost equal, B type and C type
The length of the counter shaft can be shortened as compared with the type. Therefore, there is an advantage that this toroidal type continuously variable transmission can be easily applied as a rear-wheel drive transmission.

Further, since this toroidal type continuously variable transmission has only two sets of gear transmissions between the input shaft and the counter shaft parallel to the input shaft, the number of bearings is smaller than that of the conventional B type and C type. Can be reduced. Furthermore, since the planetary gear mechanism is used as the mechanism for the reverse movement, the reaction force of the gear can be canceled inside, so that the radial bearing for supporting the gear is not necessary.

Furthermore, since this toroidal type continuously variable transmission is provided with the forward clutch between the toroidal transmission and the output shaft, when the forward clutch is disengaged, when the output shaft is in a stopped state. But you can shift.
Therefore, even if the wheels are locked when the toroidal speed changer is in a shift position other than the maximum deceleration position, it is possible to shift to the maximum deceleration position during idling and start again.

[Brief description of drawings]

FIG. 1 is a schematic structural diagram showing an embodiment of a toroidal type continuously variable transmission according to the present invention.

FIG. 2 is a schematic structural diagram showing an example of a conventional toroidal type continuously variable transmission.

FIG. 3 is a schematic structural diagram showing another example of a conventional toroidal type continuously variable transmission.

FIG. 4 is a schematic structural diagram showing still another example of a conventional toroidal type continuously variable transmission.

[Explanation of symbols]

 1 Input Shaft 2 1st Input Disc 3 1st Output Disc 4 2nd Input Disc 5 2nd Output Disc 6 1st Toroidal Speed Change Part 7 2nd Toroidal Speed Change Part 8 1st Power Roller 9 2nd Power Roller 12 Connecting Member 13 Output Gears 14 Forward clutch 15 Output shaft 16 Reverse rotation mechanism 17 Counter shaft 18 First gear 19 Second gear 20 Intermediate gear 21 Gear 22 Planetary gear mechanism 23 Sun gear 24 Pinion gear 25 Carrier 26 Ring gear 27 Casing 28 Reverse clutch

Claims (3)

[Claims] 1. An input shaft, a pair of input disks that rotate integrally with the input shaft, a pair of output disks that are arranged to face each of the input disks and are rotatably supported with respect to the input shaft. A tiltable power roller that is respectively disposed between the input disk and the output disk that face each other and that transmits torque from the input disk to the output disk, a connecting member that connects the output disks to each other, and a rotation to the connecting member. A freely supported output gear, a forward clutch that connects and disconnects the output gear and the connecting member,
An output shaft arranged on the same axis as the input shaft, a reversing mechanism for reversing the rotation of the output gear and transmitting the rotation to the output shaft, a rotation of the input shaft arranged between the input shaft and the output shaft A toroidal continuously variable transmission having a planetary gear mechanism that reverses and transmits the planetary gear mechanism to the output shaft, and a reverse clutch that switches the planetary gear mechanism to an idle state or a torque transmitting state. 2. The planetary gear mechanism includes a sun gear that rotates integrally with the input shaft, a pinion gear that meshes with the sun gear, a carrier that rotatably supports the pinion gear, and a gear that meshes with the pinion gear and is connected to the output shaft. The toroidal type continuously variable transmission according to claim 1, further comprising a ring gear, wherein the reverse clutch is a clutch that connects and disconnects the carrier with respect to a casing. 3. The reversing mechanism is fixed to a counter shaft arranged parallel to the input shaft, a first gear fixed to one end of the counter shaft and meshing with the output gear, and the other end of the counter shaft. The toroidal type continuously variable transmission according to claim 1 or 2, further comprising a second gear, an intermediate gear that meshes with the second gear, and a gear that meshes with the intermediate gear and is fixed to the output shaft.