JPH06174035A - Toroidal type continuously variable transmission - Google Patents

Abstract

PURPOSE:To provide a toroidal type continuously variable transmission in which a torque sharing ratio corresponding to the respective transmission capacities of two sets of toroidal change gears can be obtained. CONSTITUTION:Two sets of toroidal change gears 6 and 7 having different transmission capacities are provided oppositely. A differential mechanism 22 composed of a planetary gear mechanism is placed between the first output disk 3 and the second output disk 5 of the toroidal change gears 6 and 7, and an output shaft 20. Since the sun gear 23 of the planetary gear mechanism 22 has been connected to the first output disk 3, a carrier 26 has been connected to the second output disk 5, and a ring gear 27 has been drive-connected to the output shaft 20, a torque sharing ratio corresponding to the transmission capacities of the toroidal change gears 6 and 7 respectively can be obtained by setting the ratio of the teeth of the ring gear 27 and the sun gear 23 adequately.

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. Is transmitted to the output disk via the power roller, and the rotational power is transmitted from the output disk to the output shaft.

In a conventional toroidal type continuously variable transmission, for example, as shown in FIG. 3, an input disc 30, an output disc 31 arranged to face the input disc 30, and a torque from the input disc 30 to the output disc 31 are applied. A first toroidal transmission unit 33 including a power roller 32 capable of tilting transmission, an input disc 34, an output disc 35 and an input disc 3 arranged to face the input disc 34.
Second toroidal speed changer 37 including a tiltable power roller 36 for transmitting torque from the No. 4 to the output disk 35.
It consists of and. 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 parts 33 and 37 are arranged to face each other on an input shaft 38. .

The input disk 30 is supported so as to be rotatable relative to the input shaft 38.
It is drive-coupled to the input shaft 38 via and can rotate integrally with the input shaft 38. On the other hand, the input disk 34 is fixed to the input shaft 38 and can rotate integrally with the input shaft 38. The input shaft 38 is supported so as to be slightly movable in the axial direction with respect to a casing (not shown). The output disks 31 and 35 are arranged to face the input disks 30 and 34, respectively, and are rotatably supported by the input shaft 38. Also, output disc 3
1, 35 are connected to each other by a hollow shaft 40. An output gear 41 is fixed to the hollow shaft 40, and the output gear 41 meshes with a gear 43 of the output shaft 42.

The power roller 32 is disposed between the input disk 30 and the output disk 31, and both the disk 30,
31 is frictionally engaged with the toroidal surface of the power roller 36.
Is disposed between the input disk 34 and the output disk 35 and frictionally engages with the toroidal surfaces of both disks 34, 35. The power rollers 32 and 36 are rotatable about their own rotation axes 44 and 45, respectively, and tilt about the tilt axes 46 and 47 orthogonal to the rotation axes 44 and 45.

The toroidal type continuously variable transmission is constructed so that the power rollers 32 and 36 are synchronously tilted by a link mechanism or the like in order to match the tilt angles of the power rollers 32 and 36. ing. Each power roller 3
When the tilting angles of 2 and 36 change, the frictional engagement points between the power rollers 32 and 36 and the input disks 30 and 34 and the output disks 31 and 35 change accordingly, and continuously variable transmission is performed. The rotational power transmitted from the input discs 30 and 34 to the output discs 31 and 35 via the power rollers 32 and 36 is transmitted by the shearing force of oil under high pressure, that is, the traction force (adhesive friction force). In order to obtain the above traction force, a very large pressing force is required at the contact point between the power rollers 32 and 36 and both disks. This pressing force is generally generated by pressing the input disk 30 toward the output disk 31 with the loading cam 39.

By the way, the conventional toroidal type continuously variable transmission shown in FIG. 3 (hereinafter, referred to as "conventional example 1") utilizes the loading cam 39 which is driven by the relative rotation of the input disk 30 and the input shaft 38. In addition, the structure is such that a pressing force that is substantially proportional to the torque of the input shaft 38 is generated. In this structure, since the input disc 30 on the loading cam 39 side rotates relative to the input shaft 38 with an increase in torque, a rotational phase difference is generated between the input disc 30 on the opposite side fixed to the input shaft 38. Occurs. This phase difference does not cause a special problem in the steady state, but when the toroidal type continuously variable transmission undergoes a sudden torque change and a rotational phase difference instantaneously occurs between the two input disks 30 and 34, A difference occurs in the rotational speeds of both input disks 30 and 34. Therefore, the equal share of the torque transmitted by the power rollers in the two toroidal transmissions 33 and 37 is broken,
The load on one of the power rollers increases, and slippage occurs between the power roller and the disk on the side where the load increases. In order to prevent this slippage and stabilize the operation, it is necessary to constantly apply a large pressing force to prepare for uneven transmission torque, and as a result, in order to ensure the required durability, a toroidal type continuously variable transmission is used. There is a drawback that the entire machine becomes large.

As a proposal to solve the above problem, for example, a toroidal type continuously variable transmission disclosed in Japanese Unexamined Patent Publication No. 62-233556 (hereinafter referred to as "conventional example 2").
There is). This toroidal type continuously variable transmission includes an input shaft, two annular input disks that are fitted and supported by the input shaft, have their toroidal surfaces opposed to each other, and are relatively unrotatable, and slide in the axial direction between the input disks. Two annular output disks that are movably supported by an input shaft and have their toroidal surfaces facing each other, and a power roller that rotates between the output disks and the input disks by contacting and rotating with both toroidal surfaces. In a toroidal type continuously variable transmission including a supporting member that rotatably supports a power roller, a toroidal type continuously variable transmission is rotatably loosely supported by an input shaft between an output disc and an input shaft,
It is equipped with a connecting member that connects the output discs so that they cannot rotate relative to each other, and an annular loading cam is fitted and arranged between the output discs on the outer periphery of the connecting member in order to apply an axial pressing force to each output disc. is there. According to this toroidal type continuously variable transmission, the axial pressing force generated by the loading cam acts evenly on the two output discs in accordance with the torque, and in particular, a rotational phase difference occurs between the two output discs. Therefore, the transmission torques of the power rollers of the two sets of toroidal transmission units are evenly distributed.

[0009]

By the way, conventionally, when the toroidal type continuously variable transmission is mounted on a vehicle, one of the two sets of toroidal transmissions is arranged in the radial direction more than the other due to layout restrictions and the like. Alternatively, the space may be limited in the axial direction. For example, the diameters of the input disk and the output disk of the first toroidal speed change unit may have to be smaller than the diameters of the input disk and the output disk of the second toroidal speed change unit.

However, in the prior art example 1, since the output disks are connected to each other, the torque sharing ratio of the two sets of toroidal speed change parts is fixed to 1: 1. Since the disks are connected to each other, the torque sharing ratio of the two sets of toroidal transmission units is also fixed at 1: 1. Therefore, in the conventional toroidal type continuously variable transmission, the torque transmission capacity is
The torque transmission capacity of the toroidal speed changer, which has a limited space, is limited to within twice. That is, as explained in the above example, the torque transmission capacity of the toroidal type continuously variable transmission is limited to less than twice the torque transmission capacity of the toroidal transmission unit having the smaller diameter, and a large torque transmission capacity is obtained. There was a problem that I could not.

Therefore, an object of the present invention is to obtain a torque sharing ratio commensurate with the torque transmission capacity of each of the two sets of toroidal transmissions in a double-cavity toroidal type continuously variable transmission. An object of the present invention is to provide a toroidal-type continuously variable transmission that utilizes a differential mechanism to solve the problem, thereby increasing the degree of freedom in layout of the transmission itself.

[0012]

In order to achieve the above object, the present invention is configured as follows. That is,
The present invention is directed to an input disc that rotates integrally with an input shaft, an output disc that is arranged so as to face the input disc and is rotatably supported with respect to the input shaft, and between the input disc and the output disc. A toroidal-type continuously variable transmission that has two sets of toroidal transmissions that are arranged and that include a tiltable power roller that transmits torque from the input disc to the output disc, and an output shaft that is drivingly connected to the output disc. The toroidal transmission has different torque transmission capacities, and the output disks and the output shafts are drive-coupled through a differential mechanism, which relates to a toroidal continuously variable transmission.

In the toroidal type continuously variable transmission, the differential mechanism is a planetary gear mechanism.

Further, in this toroidal type continuously variable transmission, the planetary gear mechanism includes a sun gear connected to one of the output discs, a carrier connected to the other output disc, and a gear meshing with the sun gear. A first pinion gear rotatably supported, a second pinion gear meshed with the first pinion gear and rotatably supported by the carrier, and a ring gear meshed with the second pinion gear and drive-connected to the output shaft Is.

In the toroidal type continuously variable transmission, the planetary gear mechanism includes a sun gear connected to one of the output disks, a ring gear connected to the other output disk, and a first pinion gear meshing with the sun gear. There is provided a second pinion gear that meshes with the first pinion gear and meshes with the ring gear, and a carrier that rotatably supports the first pinion gear and the second pinion gear and that is drive-connected to the output shaft.

[0016]

Since the present invention is constructed as described above, it operates as follows. That is, in this toroidal type continuously variable transmission, the two output disks are connected via the differential mechanism, so that even if the torque transmission capacities of the two sets of toroidal transmission parts are different, the one having a smaller torque transmission capacity is used. Is larger than twice the torque transmission capacity of the toroidal speed changer. Therefore, this toroidal-type continuously variable transmission can obtain a torque sharing ratio corresponding to the torque transmission capacity of each of the two sets of toroidal transmissions.

In the toroidal type continuously variable transmission, the operation when the differential mechanism is composed of a planetary gear mechanism will be described. For a toroidal type continuously variable transmission in which a sun gear is connected to one output disk and a carrier is connected to the other output disk, when the speed ratios of the two toroidal transmission parts are the same, the two output disks are Since they are rotating at the same rotation speed, the sun gear connected to one output disk and the carrier connected to the other output disk rotate at the same rotation speed. Therefore, the pinion gear is
Revolves around the input shaft without rotating. However, when the speed ratios of the two sets of toroidal speed change units do not match, the two output disks have different rotational speeds, and therefore either the sun gear or the carrier has a higher rotational speed. As a result, the first pinion gear and the second pinion gear revolve around the input shaft while rotating.

In this toroidal type continuously variable transmission, torque is transmitted from one output disc to the sun gear, from the other output disc to the ring gear, and further from the ring gear to the output shaft. At this time, if the torque of one output disk is T ₁ , the torque of the other output disk is T ₂ , the number of teeth of the ring gear is Z _R , and the number of teeth of the sun gear is Z _S , the torque of each output disk is The sharing ratio is as follows. T ₁ : T ₂ = 1: (Z _R / Z _S -1) Therefore, the torque sharing ratio of the two sets of toroidal speed change parts is determined by the ratio of the number of teeth of the ring gear and the sun gear of the planetary gear mechanism (Z _R /
Z _S ) makes it possible to set a value commensurate with the transmission capacity of each toroidal transmission unit.

[0019]

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
This is a double-cavity toroidal-type continuously variable transmission in which two sets of toroidal transmission units 6 and 7 are coaxially opposed to each other. The first toroidal transmission unit 6 includes the first input disk 2
A first output disc 3 arranged to face the first input disc 2 and a first output disc 3 arranged between the first input disc 2 and the first output disc 3 for frictionally engaging the toroidal surfaces of both discs. It is composed of one power roller 8. Second
Similarly to the first toroidal transmission unit 6, the 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 output. The second power roller 9 is disposed between the disk 5 and frictionally engages with the toroidal surfaces of both disks. However, due to space limitations, the first toroidal transmission unit 6 is smaller than the second toroidal transmission unit 7. The first toroidal transmission unit 6 has a smaller torque transmission capacity than the second toroidal transmission unit 7. Each of the toroidal transmissions 6 and 7 is provided with two power rollers. First power roller 8 and second
Each of the power rollers 9 is rotatable about its own rotation axis 10 and tilts about a tilt axis 11 orthogonal to the rotation axis 10.

The input shaft 1 is rotatably supported by a casing (not shown), and 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.

A differential mechanism 22 is provided between the first output disc 3 and the second output disc 5 and the output shaft 20. The differential mechanism 22 is composed of a planetary gear mechanism, and has a sun gear 23 connected to the first output disk 3, a carrier 26 connected to the second output disk 5, and a sun gear 23 meshingly rotatably with respect to the carrier 26. A first pinion gear 24 supported, a second pinion gear 25 meshing with the first pinion gear 24 and rotatably supported by a carrier 26, and a ring gear 27 meshing with the second pinion gear 25 and drivingly connected to the output shaft 20. Is.

Further, one end of a first hollow shaft 12 through which the input shaft 1 is inserted is fixed to the back surface of the first output disk 3, and a sun gear 23 is fixed to the other end of the first hollow shaft 12. Further, one end of the second hollow shaft 14 through which the input shaft 1 is inserted is fixed to the back surface of the second output disk 5, and the carrier 26 is fixed to the other end of the second hollow shaft 14. The carrier 26 rotatably supports the pinion gear. The pinion gears are the first pinion gear 24 and the second pinion gear 2
It consists of 5. The first pinion gear 24 meshes with the sun gear 23, and the second pinion gear 25 meshes with both the first pinion gear 24 and the ring gear 27. The output gear 19 is fixed to the ring gear 27. The output gear 19 meshes with the gear 21 of the output shaft 20.

Next, the operation of the toroidal type continuously variable transmission according to the present invention will be described. First, the operation of the toroidal type continuously variable transmission shown in FIG. 1 will be described. When a torque is input to the input shaft 1 as the engine operates, the torque is transferred to the first input disk 2 via the loading cam.
Be transmitted to. At the same time, the torque is transmitted from the input shaft 1 to the second input disk 4 via another loading cam. When torque is transmitted to the first input disk 2, the first
The input disk 2 rotates, the rotation of which rotates the first power roller 8, and the rotation is transmitted to the first output disk 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 of the first output disk 3 is performed by the sun gear 23.
And the rotation of the second output disk 5 is transmitted to the carrier 26.
Be transmitted to. In the normal state, that is, when the speed ratios of the two toroidal speed change parts are the same, the rotation speed of the first output disk 3 and the rotation speed of the second output disk 5 are the same, so the sun gear 23 and the carrier 26 are the same. Rotate at the same speed. Therefore, the first pinion gear 24 and the second pinion gear 25 do not rotate, but the sun gear 23, the first pinion gear 24, the second pinion gear 25, the carrier 26, the ring gear 27, and the output gear 19 are integrated around the input shaft 1. Revolve around. The rotation of the output gear 19 is transmitted to the output shaft 20 via the gear 21 that meshes with the output gear 19.

When the transmission ratios of the toroidal transmissions 6 and 7 do not match due to the twist of the input shaft 1 or the deformation of the support member of the power roller, the first output disc 3 and the second output disc 3 are
There is a difference in rotation speed between the output disk 5 and the output disk 5. For example, the first
When the rotation speed of the output disk 3 becomes higher than the rotation speed of the second output disk 5, the sun gear 23 to which the first output disk 3 is connected is the second output disk 5
Will rotate faster than the carrier 26 to which they are connected. As a result, the first pinion gear 24 rotates, and along with that, the second pinion gear 25 also rotates, and the difference in rotation between the output disks 3 and 5 is absorbed. Therefore, even if the transmission ratios of the toroidal transmissions 6 and 7 do not match, the differential mechanism 22 provided between the output disks does not cause slippage at the traction contact portions of the toroidal transmissions 6 and 7. .

When the gear ratios of the toroidal transmission units 6 and 7 do not match, the torque of the first output disc 3 is T ₁ , the torque of the second output disc 5 is T ₂ , and the rotation speed of the first output disc 3 is Is N ₁ , and the rotation speed of the second output disk 5 is N ₂
Then, the torque T and the rotation speed N of the output gear 19 are expressed by the following equations (referred to as equation (1)). _{N = Z S N 1 / Z} R + (Z R -Z S) N 2 / Z R T = Z R (N 1 T 1 + N 2 T 2) / [Z _S N ₁ + (Z _R
-Z _S ) N ₂ ] Here, Z _S represents the number of teeth of the sun gear 23, and Z _R represents the number of teeth of the ring gear 27.

Further, in this toroidal type continuously variable transmission,
The torque is transmitted from the first output disc 3 to the sun gear 23, from the second output disc 5 to the ring gear 27, and then to the output shaft 20. At this time, the torque of the first output disk 3 is T ₁ , the torque of the second output disk 5 is T ₂ , the number of teeth of the ring gear 27 is Z _R , and the sun gear 23.
Assuming that the number of teeth of Z is Z _S , the torque sharing ratio of each of the output disks 3 and 5 is given by the following expression [referred to as expression (2)]. _{T 1: T 2 = 1:} (Z R / Z S -1)

Now, let us consider what the torque transmission capacity T of the toroidal type continuously variable transmission becomes when T ₁ : T ₂ = 1: 2. In Conventional Example 1 and Conventional Example 2, the torque transmission capacity T is represented by T = 2T ₁ .

On the other hand, the torque transmission capacity T of the toroidal type continuously variable transmission according to the present invention is as follows. According to the above equation (2) of the torque sharing ratio, Z _R / Z _S
= 3, the torque transmission capacity T is expressed by the following equation [formula (3)] from the equation (1) of the torque. T = 3 (N ₁ T ₁ + 2N ₂ T ₁ ) / (N ₁ + 2N ₂ ) Therefore, when the two output disks have the same rotation speed, that is, when N ₁ = N ₂ , the above equation (3) is used. , The torque transmission capacity T is expressed by the following equation. T = 3T _{1 When} the two output disks have different rotational speeds, for example, when N ₁ = 2N ₂ , the torque transmission capacity T is expressed by the following equation. T = 3T ₁ Therefore, if the gear ratio Z _R / Z _S satisfies the equation (2), always torque transmission capacity is the sum value of the two sets of torque transmission capacity.

On the other hand, when Z _R / Z _S = 2, the torque transmission capacity T is expressed by the following equation (equation (4)) from the above equation (1). T = 2 (N ₁ T ₁ + 2N ₂ T ₁ ) / (N ₁ + N ₂ ) Therefore, if the two output disks have the same rotational speed, that is, if N ₁ = N ₂ , then from the above equation (4) , The torque transmission capacity T is expressed by the following equation. T = 3T _{1 When} the two output disks have different rotational speeds, for example, when N ₁ = 2N ₂ , the torque transmission capacity T is expressed by the following equation. T = 8T _1/3

Therefore, in the toroidal type continuously variable transmission according to the present invention, the torque transmission capacity T is determined by the tooth number ratio Z _R /
Regardless of whether or not Z _S satisfies the above expression (2), it always becomes larger than those of Conventional Example 1 and Conventional Example 2. Also,
If the tooth number ratio Z _R / Z _S is set so as to satisfy the above formula (2), even if the rotational speeds of the two output disks are different,
The torque transmission capacity is always the sum of the torques of the two output disks, maximizing the torque transmission capacity.

As can be seen from the above description, by appropriately setting the tooth ratio of the ring gear 27 and the sun gear 23 of the planetary gear type differential mechanism 22, a value commensurate with the transmission capacity of each toroidal transmission unit 6, 7 can be obtained. It is possible to set the torque sharing ratio of the two sets of toroidal transmission units 6 and 7. That is, the transmission capacity of the toroidal type continuously variable transmission has conventionally been limited to less than twice the transmission capacity of the first toroidal transmission section 6 having a small diameter. However, if the above gear ratio is appropriately set, Even if the sizes of the two sets of toroidal transmissions are different, the torque transmission capacity is not limited, and a large torque transmission capacity can be obtained. Therefore, the degree of freedom in the layout of the entire device can be increased.

Next, another embodiment of the toroidal type continuously variable transmission according to the present invention will be described with reference to FIG. In FIG. 2, the same parts as those shown in FIG. 1 are designated by the same reference numerals. In the above embodiment, the case where the sun gear 23 is connected to the first output disk 3 and the carrier 26 is connected to the second output disk 5 has been described. However, in this embodiment, the sun gear 23 is connected to the first output disk 3. The ring gear 27 is connected to the second output disk 5. In this case, the torque sharing ratio of the output disks 3 and 5 is as follows. T ₁ : T ₂ = 1: Z _R / Z _S

In any of the embodiments, the torque sharing ratio of the two sets of toroidal transmissions 6 and 7 is determined by the gear ratio of the ring gear 27 of the planetary gear type differential mechanism 22 and the sun gear 23.
It is possible to set a value corresponding to the transmission capacity of each toroidal transmission unit 6, 7.

Further, also in the case of a belt type toroidal speed change unit, when two sets of belts are used, they can be similarly applied and the same effect can be obtained.

[0036]

Since the present invention is constructed as described above, it has the following effects. That is, in this toroidal type continuously variable transmission, the torque distribution ratio of the two sets of toroidal transmission units is adjusted to the transmission capacity of each toroidal transmission unit by the gear ratio of the ring gear and the sun gear of the planetary gear mechanism, which is a differential mechanism. It is possible to set to different values. Therefore, it is possible to obtain a sufficient torque transmission capacity even if the sizes of the two sets of toroidal speed change parts are different, so that it is possible to increase the degree of freedom in the layout of the entire device.

In this toroidal type continuously variable transmission, since the two output disks are connected through the differential mechanism, even if there is a difference in the gear ratio of the two sets of toroidal transmission parts, the efficiency of the entire device is reduced and Without heat generation of the traction contact part,
It is possible to absorb this difference in gear ratio. In particular, when the power roller support member is deformed or a difference occurs in both toroidal speed change parts with respect to the tilt angle of the power roller, the difference in the gear ratio between the two toroidal speed change parts is the same as the conventional toroidal type continuously variable transmission. I couldn't absorb it, but
The toroidal type continuously variable transmission according to the present invention makes this possible for the first time.

Further, in this toroidal type continuously variable transmission,
Even if the transmission ratios of the two sets of toroidal transmissions do not match, the planetary gear type differential mechanism absorbs the difference of the transmission ratios. There is no need for strict synchronization in the toroidal transmission,
There is an advantage that the shift control of the two sets of toroidal shift units is simplified.

Further, the conventional toroidal type continuously variable transmission is
In order to prevent slippage between the power roller and the input / output disc and to stabilize the operation, it was necessary to constantly apply a large pressing force by the loading cam, so there was the problem that the entire toroidal type continuously variable transmission became large. However, in the toroidal type continuously variable transmission according to the present invention, since slippage and heat are not generated at the traction contact portion, it is not necessary to apply a large pressing force. Therefore, the overall size of the toroidal type continuously variable transmission can be reduced.

[Brief description of drawings]

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

FIG. 2 is a structural view showing another embodiment of the toroidal type continuously variable transmission according to the present invention.

FIG. 3 is a schematic structural diagram showing an 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 19 Output Gear 20 Output Axis 22 Differential mechanism 23 Sun gear 24 First pinion gear 25 Second pinion gear 26 Carrier 27 Ring gear

Claims (4)

[Claims] 1. An input disk which rotates integrally with an input shaft,
An output disc disposed to face the input disc and rotatably supported with respect to the input shaft; a torque disposed between the input disc and the output disc and transmitted from the input disc to the output disc In a toroidal type continuously variable transmission having two sets of toroidal speed change parts including a tiltable power roller and an output shaft drivingly connected to the output disk, the toroidal speed change parts have different torque transmission capacities, A toroidal type continuously variable transmission characterized in that each output disk and the output shaft are drivingly connected via a differential mechanism. 2. The toroidal type continuously variable transmission according to claim 1, wherein the differential mechanism comprises a planetary gear mechanism. 3. The planetary gear mechanism includes a sun gear connected to one of the output disks, a carrier connected to the other output disk, and a first pinion gear meshed with the sun gear and rotatably supported by the carrier. ,
The second pinion gear, which meshes with the first pinion gear and is rotatably supported by the carrier, and the ring gear, which meshes with the second pinion gear and is drivingly connected to the output shaft. Toroidal type continuously variable transmission. 4. The planetary gear mechanism includes a sun gear connected to one of the output disks, a ring gear connected to the other output disk, and a first gear meshing with the sun gear.
A pinion gear, a second pinion gear meshing with the first pinion gear and meshing with the ring gear, and the first pinion gear
3. The toroidal type continuously variable transmission according to claim 2, further comprising a carrier that rotatably supports the pinion gear and the second pinion gear and is drivingly connected to the output shaft.