JP5862184B2 - Continuously variable transmission - Google Patents

Description

  The present invention relates to various continuously variable transmissions that can be used in transmissions of automobiles and various industrial machines, and more particularly to a continuously variable transmission that is a combination of a toroidal continuously variable transmission mechanism and a planetary gear mechanism.

  Conventionally, a toroidal type continuously variable transmission has been known as a transmission of a vehicle. However, in a conventional continuously variable transmission including such a toroidal type continuously variable transmission, there is no need to 2. Description of the Related Art There is known a stepless transmission (infinite transmission ratio infinitely variable transmission) that is capable of controlling a transmission ratio to infinity by combining a planetary gear mechanism with a step transmission mechanism. For example, a continuously variable transmission 1 shown in FIG. 5 as disclosed in Patent Document 1 includes a variator 2 including a toroidal continuously variable transmission mechanism between an input shaft 5 and an output shaft 27, and a first and a second. Planetary gear mechanisms 3a and 3b are provided. The variator 2 includes an input shaft 5 that is rotatably supported by a fixed portion via a bearing or the like and that has one end connected to a drive source 4 such as an engine.

  The input shaft 5 is provided with a hydraulic piston 6 as a hydraulic pressing mechanism, and power is transmitted to the variator 2 through the hydraulic piston 6. The variator 2 is provided with a power transmission shaft 7 that rotates in conjunction with the hydraulic piston 6, and the power transmission shaft 7 is provided with a pair of input side disks 8 a and 8 b that face each other. Further, between the pair of input side disks 8a and 8b, a pair of output side disks 9a and 9b that are loosely fitted to the power transmission shaft 7 are arranged coaxially and rotate in synchronization with each other. ing.

  The power transmission shaft 7 protrudes rearward from the input side disk 8b constituting the variator 2 and is connected to the first planetary gear mechanism 3a. In addition, a plurality of power rollers 10 that are in rolling contact with each other are provided between the input side disks 8a and 8b and the output side disks 9a and 9b. The output side disks 9a and 9b are connected via a loosely fitted shaft 11 that is loosely fitted to the power transmission shaft 7.

  In the variator 2, the rotational driving force transmitted to the power transmission shaft 7 is transmitted to the loose fitting shaft 11 via the input side disks 8a and 8b, the power roller 10, and the output side disks 9a and 9b, and the speed ratio, That is, a value obtained by dividing the rotational speed of the output side disks 9 a and 9 b by the rotational speed of the input side disks 8 a and 8 b is determined by the tilt angle of the power roller 10.

  That is, when the power roller 10 is in the horizontal state, the speed ratio becomes neutral, and when the output side disks 9a and 9b of each power roller 10 are tilted away from the power transmission shaft 7, Accordingly, the speed ratio decreases, and conversely, when the output side disks 9a, 9b of each power roller 10 tilt in the direction approaching the power transmission shaft 7, the speed ratio increases accordingly. A first gear 12 as an output gear is fitted to the loose fitting shaft 11, and the first gear 12 meshes with a second gear 13 provided at one end of the counter shaft 14. A third gear 15 is provided at the other end of the counter shaft 14, and the third gear 15 meshes with the fifth gear 17 via the fourth gear 16, and the second planetary gear mechanism 3 b. It is linked.

  The first planetary gear mechanism 3 a includes a first sun gear 18, a plurality of first planetary gears 19 that mesh with the first sun gear 18, a first carrier 20 that links the planetary gears 19, and a first planetary gear. The first ring gear 21 meshing with the first sun gear 18 is connected to the power transmission shaft 7.

  The second planetary gear mechanism 3b includes a second sun gear 22, a plurality of second planetary gears 23 that mesh with the second sun gear 22, a second carrier 24 that links the planetary gears 23, and a second A second ring gear 25 meshing with the planetary gear 23, the second sun gear 22 is connected to the fifth gear 17, and the second carrier 24 is connected to the first planetary gear 26 via the center shaft 26. It is connected to the first carrier 20 of the gear mechanism 3a. The second ring gear 25 is provided with an output shaft 27.

  Further, the rotation of the first ring gear 21 is constrained and released between the first ring gear 21 of the first planetary gear mechanism 3a and a fixed portion (a fixed portion such as a casing for housing the variator 2). A low speed clutch 28 is provided, and a high speed clutch 29 is provided between the second ring gear 25 and the second carrier 24 of the second planetary gear mechanism 3b to contact and separate them.

  Therefore, with the above configuration, the following two operation modes can be obtained. That is, first, in the differential mode in which the low speed clutch 28 is connected and the high speed clutch 29 is released, the first ring gear 21 of the first planetary gear mechanism 3a is in a fixed state, and the first sun gear 18 rotation is transmitted to the first carrier 20 through the first planetary gear 19, and the rotation of the central shaft 26 is transmitted to the second carrier 24 of the second planetary gear mechanism 3b and rotated. The second sun gear 22 is transmitted to the second ring gear 25 at a relative speed to the rotation of the second sun gear 22.

  That is, when the low-speed clutch 28 is connected and the high-speed clutch 29 is released, the rotation of the input shaft 5 causes the power transmission shaft 7 → the first sun gear 18 of the first planetary gear mechanism 3a → the first planetary gear. 19 → first carrier 20 → center shaft 26 → path for transmission to the second carrier 24 of the second planetary gear mechanism 3b, hydraulic piston 6 → input side disks 8a, 8b → power roller 10 → output side disk 9a , 9b → first gear 12 → second gear 13 → counter shaft 14 → third gear 15 → fourth gear 16 → fifth gear 17 → second sun gear of the second planetary gear mechanism 3b 22 is transmitted to the second planetary gear mechanism 3b through two paths, and the infinite gear ratio is combined with the variator 2 using the differential of the second planetary gear mechanism 3b. Is obtained. In the present specification, the low speed clutch 28 may be referred to as a differential clutch and the second planetary gear mechanism 3b may be referred to as a differential planetary mechanism based on the above action. Further, the first planetary gear mechanism 3a may be referred to as a reduction planetary mechanism.

  On the other hand, in the direct connection mode in which the high speed clutch 29 is connected and the low speed clutch 28 is released, the rotation of the input shaft 5 rotates the loosely fitted shaft 11 via the output side disks 9a and 9b and the first gear 12 Power is transmitted to the second gear 13 and the counter shaft 14 is rotated. Then, the rotation of the counter shaft 14 is transmitted to the second sun gear 22 of the second planetary gear mechanism 3b through the third gear 15, the fourth gear 16, and the fifth gear 17.

  The rotation of the second sun gear 22 is transmitted to the second ring gear 25 via the second planetary gear 23 and is transmitted to the output shaft 27. Accordingly, the input shaft 5 is directly connected to the output shaft 27, and while maintaining this state, the variator 2 is set to the speed increasing side, that is, the power roller 10 in the direction in which the output side disks 9a and 9b approach the power transmission shaft 7. When tilted, the rotational speed of the counter shaft 14 increases according to the tilt, and accordingly, the rotational speed of the second sun gear 22 of the second planetary gear mechanism 3b increases, and the output shaft 27 The rotational speed increases, and the speed ratio of the continuously variable transmission 1 as a whole increases. In the present specification, the high-speed clutch 29 may be referred to as a direct coupling clutch based on the above operation.

Japanese Patent No. 3702598

  However, in the configuration of Patent Document 1 shown in FIG. 5, the power of the variator 2 is transmitted from the two gears 16 and 17 in the direct connection mode in which the direct connection clutch 29 is connected and the power of the variator 2 is directly transmitted to the output shaft 27. Since it is transmitted to the output shaft 27 via the idle gear part 50 which comprises, transmission efficiency falls. That is, for example, if the gear meshing efficiency is 99%, there are two meshes in the idle gear unit 50, so the gear meshing efficiency is 99% × 99% = 98.01%, and the power transmission efficiency is about 2%. Decrease. For example, if the engine power is 100 kW, the loss is 2 kW, which cannot be ignored.

  The present invention has been made in view of the above circumstances. In a power transmission mode (direct coupling mode) in which the rotation of the variator is taken out as it is, the output rotation of the variator is transmitted to the output shaft with a small number of meshes, and the size and weight are reduced. An object is to provide a low-cost continuously variable transmission that can be achieved.

In order to achieve the above object, the present invention provides an input shaft that is rotationally driven by a drive source, an output shaft that extracts power accompanying the rotation of the input shaft, and a coaxial shaft between the input shaft and the output shaft. And a differential planetary gear mechanism, the variator being coaxial with the pair of input side disks facing each other and the pair of input side disks rotating in conjunction with the input shaft. A pair of output-side disks that are arranged and rotate synchronously with each other, an output gear that rotates integrally with these output-side disks, a power transmission shaft that connects the pair of input-side disks, and the input-side disk And the output planetary power roller, and the differential planetary gear mechanism includes a sun gear, a ring gear arranged around the sun gear, and the sun gear. A continuously variable transmission comprising a plurality of planetary gears rotatably supported by a carrier between a vehicle and the ring gear and coupled to the output shaft, wherein the output gear and the differential planetary gear The sun gear of the gear mechanism is directly connected only by a counter shaft having counter gears at both ends so that the output gear and the sun gear rotate in the same direction, and the power of the variator is used as the differential planetary gear. A power transmission mechanism for transmitting to the mechanism, and the rotation of the input shaft is reversed via the power transmission mechanism and transmitted to the carrier of the differential planetary gear mechanism, and at the same time, the differential planetary gear via the counter shaft A differential mode in which a differential component of the differential planetary gear mechanism is transmitted to the output shaft by also transmitting to the sun gear of the mechanism, and rotation of the input shaft is performed only on the counter shaft. A clutch mechanism for giving a direct mode to communicate directly to the output shaft via, and further comprising a.

  According to the present invention, the output gear and the sun gear of the differential planetary gear mechanism are directly connected only by a counter shaft having counter gears at both ends, and a direct connection mode that is a power transmission mode for taking out the rotation of the variator as it is. , The output rotation of the variator is transmitted to the output shaft only through the counter shaft parallel to the variator (with a small number of meshes without the idle gear portion), so it is a low-cost continuously variable transmission that is highly efficient and can be reduced in size and weight. Equipment can be provided.

1 is a system diagram of a continuously variable transmission according to a first embodiment of the present invention. FIG. 2 is a graph showing a relationship between a variator transmission ratio and a transmission transmission ratio in the continuously variable transmission of FIG. 1. It is a systematic diagram of the continuously variable transmission which concerns on the 2nd Embodiment of this invention. It is a systematic diagram of the continuously variable transmission which concerns on the 3rd Embodiment of this invention. It is a systematic diagram of the conventional continuously variable transmission.

Embodiments of the present invention will be described below with reference to the drawings.
The feature of the present invention lies in the power transmission mechanism in the direct connection mode, which is the power transmission mode in which the rotation of the variator is taken out as it is, and the other configurations and operations are the same as the conventional configurations and operations described above. Only the characteristic part of the present invention will be referred to, and other parts will be simply described with the same reference numerals as those in FIG.

FIG. 1 shows a first embodiment of the present invention.
As shown in the figure, the continuously variable transmission 1A of the present embodiment is similar to the prior art shown in FIG. 5 between the input shaft 5 (not shown in FIG. 1; see FIG. 5) and the output shaft 27. A variator 2 composed of a toroidal-type continuously variable transmission mechanism and first and second planetary gear mechanisms 3a and 3b are provided. The variator 2 is rotatably supported by a fixed portion (a fixed portion such as a casing that accommodates the variator 2) via a bearing or the like, and one end side is connected to a drive source 4 such as an engine (see FIG. 1 is not shown; see FIG.

  The input shaft 5 is provided with a hydraulic piston 6 (not shown in FIG. 1; see FIG. 5) as a hydraulic pressing mechanism, and power is transmitted to the variator 2 through the hydraulic piston 6. It has become. The variator 2 is provided with a power transmission shaft 7 that rotates in conjunction with the hydraulic piston 6, and the power transmission shaft 7 is provided with a pair of input side disks 8 a and 8 b that face each other. Further, between the pair of input side disks 8a and 8b, a pair of output side disks 9a and 9b that are loosely fitted to the power transmission shaft 7 are arranged coaxially and rotate in synchronization with each other. ing.

  The power transmission shaft 7 protrudes rearward from the input side disk 8b constituting the variator 2 and is connected to a first planetary gear mechanism 3a as a power transmission mechanism and a reverse reduction planetary gear mechanism. In addition, a plurality of power rollers 10 that are in rolling contact with each other are provided between the input side disks 8a and 8b and the output side disks 9a and 9b. The output side disks 9a and 9b are connected via a loosely fitted shaft 11 that is loosely fitted to the power transmission shaft 7.

  In the variator 2, the rotational driving force transmitted to the power transmission shaft 7 is transmitted to the loose fitting shaft 11 via the input side disks 8a and 8b, the power roller 10, and the output side disks 9a and 9b, and the speed ratio, That is, a value obtained by dividing the rotational speed of the output side disks 9 a and 9 b by the rotational speed of the input side disks 8 a and 8 b is determined by the tilt angle of the power roller 10.

  That is, when the power roller 10 is in the horizontal state, the speed ratio becomes neutral, and when the output side disks 9a and 9b of each power roller 10 are tilted away from the power transmission shaft 7, Accordingly, the speed ratio decreases, and conversely, when the output side disks 9a, 9b of each power roller 10 tilt in the direction approaching the power transmission shaft 7, the speed ratio increases accordingly. A first gear 12 as an output gear is fitted to the loose fitting shaft 11, and the first gear 12 is only by a counter shaft 14 (parallel to the input shaft 5) having counter gears 13 and 15 at both ends. It is directly connected to a second sun gear 22 of a second planetary gear mechanism 3b as a differential planetary gear mechanism described later. That is, the first gear 12 as the output gear meshes with the second gear 13 as the first counter gear provided at one end portion of the counter shaft 14, and the second gear 13 at the other end portion of the counter shaft 14. The third gear 15 as the counter gear is directly connected to the second sun gear 22 of the second planetary gear mechanism 3b as the differential planetary gear mechanism.

  The first planetary gear mechanism 3a serving as a power transmission mechanism and a reverse reduction planetary gear mechanism reverses the rotation of the input shaft 5 and transmits it. The first planetary gear mechanism 3a meshes with the first sun gear 18 and a single meshing gear. A plurality of pinion type first planetary gears 19, a first carrier 20 that links the planetary gears 19, and a first ring gear 21 that meshes with the first planetary gears 19 are provided. The sun gear 18 is connected to the power transmission shaft 7.

  The second planetary gear mechanism 3b as a differential planetary gear mechanism connects the second sun gear 22, a plurality of single pinion type second planetary gears 23 meshing with the second sun gear 22, and the planetary gears 23. A second carrier gear 24 and a second ring gear 25 meshing with the second planetary gear 23, and the second sun gear 22 is located at the other end of the counter shaft 14. And the second carrier 24 is connected to the first ring gear 21 of the first planetary gear mechanism 3a through the central shaft 26. The second ring gear 25 is provided with an output shaft 27. In this configuration, the input shaft 5, the power transmission shaft 7, the center shaft 26, and the output shaft 27 are on the same axis.

  Further, a low speed clutch 28 as a first clutch (differential clutch) that restrains and releases the rotation of the first carrier 20 between the first carrier 20 and the fixed portion of the first planetary gear mechanism 3a. A high-speed clutch 29 is provided as a second clutch (direct coupling clutch) for contacting and separating the second ring gear 25 and the second carrier 24 of the second planetary gear mechanism 3b. It has been.

  Therefore, with the above configuration, the following two operation modes can be obtained. That is, first, in the differential mode in which the low speed clutch 28 is connected and the high speed clutch 29 is released, the first carrier 20 of the first planetary gear mechanism 3 a is in a fixed state, and the first sun gear 18. Is transmitted to the first ring gear 21 via the first planetary gear 19, and the rotation of the central shaft 26 is transmitted to the second carrier 24 of the second planetary gear mechanism 3b (the output gear). 12 and the countershaft 14) and transmitted to the second ring gear 25 at a relative speed to the rotation of the rotating second sun gear 22.

  That is, when the low speed clutch 28 is connected and the high speed clutch 29 is released, the rotation of the input shaft 5 (see FIG. 5) causes the power transmission shaft 7 → the first sun gear 18 of the first planetary gear mechanism 3a → First planetary gear 19 → first ring gear 21 → center shaft 26 → path for transmission to the second carrier 24 of the second planetary gear mechanism 3b, hydraulic piston 6 (see FIG. 5) → input-side disk 8a , 8b → power roller 10 (see FIG. 5) → output side disks 9a, 9b → first gear (output gear) 12 → first counter gear (second gear) 13 → counter shaft 14 → second counter The second planetary gear mechanism 3b is transmitted to the second planetary gear mechanism 3b through two paths, the gear (third gear) 15 and the second planetary gear mechanism 3b. Variety using differential of planetary gear mechanism 3b By a combination of two infinite speed ratio is obtained (the ... output rotation transmitted to the differential planetary gear mechanism differential component output shaft 27 of 3b is reversed with respect to the input rotation).

  On the other hand, in the direct coupling mode in which the high speed clutch 29 is connected and the low speed clutch 28 is released, the rotation of the input shaft 5 rotates the loosely fitted shaft 11 via the output side disks 9a and 9b and the output gear (first gear). The gear 12) is directly transmitted to the second sun gear 22 of the second planetary gear mechanism 3b via the counter shaft 14 (counter gears 13, 15).

  Further, the rotation of the second sun gear 22 is transmitted to the second ring gear 25 via the second planetary gear 23 and is transmitted to the output shaft 27 (the output rotation is opposite to the input rotation). . Accordingly, the input shaft 5 is directly connected to the output shaft 27, and while maintaining this state, the variator 2 is set to the speed increasing side, that is, the power roller 10 in the direction in which the output side disks 9a and 9b approach the power transmission shaft 7. When tilted, the rotational speed of the counter shaft 14 increases according to the tilt, and accordingly, the rotational speed of the second sun gear 22 of the second planetary gear mechanism 3b increases, and the output shaft 27 The rotational speed increases, and the speed ratio of the continuously variable transmission 1 as a whole increases.

  As described above, according to the present embodiment, the output gear 12 and the sun gear 22 of the differential planetary gear mechanism 3b are directly connected only by the counter shaft 14 having the counter gears 13 and 15 at both ends. In the direct connection mode, which is a power transmission mode for taking out the rotation of the variator 2 as it is, the output rotation of the output of the variator 2 is made only through the counter shaft 14 parallel to the variator 2 (with a small number of meshes by omitting the idle gear portion). Therefore, it is possible to provide a low-cost continuously variable transmission that is highly efficient and can be reduced in size and weight. Data capable of demonstrating such an effect of the present embodiment is shown in FIG. FIG. 2 shows that the variator ratio is 7.000, the reverse reduction planetary ratio (the gear ratio between the ring gear and the sun gear) is 3.850, the GN planetary ratio is 2.160, and the total counter gear ratio is 1.455. It is a graph which shows the relationship between a variator gear ratio and a mission gear ratio. In the case of the total counter gear ratio, a so-called geared neutral (GN) type transmission is used, and depending on the total counter gear ratio, a power split type is used.

FIG. 3 shows a second embodiment of the present invention.
As shown in the figure, in the present embodiment, the plurality of planetary gears 19 of the reverse reduction planetary gear mechanism 3a are of a double pinion type, and the first carrier 20 that rotatably supports these planetary gears 19 has a central shaft 26. To the second carrier 24 of the differential planetary gear mechanism 3b, and a low speed clutch 28 is provided between the first ring gear 21 and the fixed portion of the reverse reduction planetary gear mechanism 3a. The rotation of the gear 21 is restricted and released. Other configurations are the same as those in the first embodiment. Even with such a configuration, the same effects as those of the first embodiment can be obtained.

FIG. 4 shows a third embodiment of the present invention.
As shown in the figure, in the present embodiment, the plurality of planetary gears 23 of the differential planetary gear mechanism 3b are of a double pinion type, and the second carrier 24 that rotatably supports these planetary gears 23 is provided on the output shaft 27. It is connected. Further, the second ring gear 25 of the reverse reduction planetary gear mechanism 3b is connected to the first ring gear 21 of the differential planetary gear mechanism 3a via the center shaft 26. Other configurations are the same as those in the first embodiment. Even with such a configuration, the same effects as those of the first embodiment can be obtained.

  The present invention can be applied to a continuously variable transmission including a variator including various types of toroidal-type continuously variable transmission mechanisms and a differential planetary gear mechanism continuously variable transmission.

1A continuously variable transmission 2 variator 3a first planetary gear mechanism (power transmission mechanism; reverse reduction planetary gear mechanism)
3b Second planetary gear mechanism (differential planetary gear mechanism)
4 Drive source 5 Input shaft 7 Power transmission shaft 8a, 8b Input side disk 9a, 9b Output side disk 10 Power roller 12 Output gear
13 First counter gear 14 Counter shaft 15 Second counter gear 18, 22 Sun gears 19, 23 Planetary gears 20, 24 Carrier 21, 25 Ring gear 26 Central shaft 27 Output shaft

Claims (4)

An input shaft that is rotationally driven by a drive source, an output shaft that extracts power associated with the rotation of the input shaft, a variator and a differential planetary gear mechanism that are coaxially disposed between the input shaft and the output shaft And
The variator includes a pair of opposed input disks that rotate in conjunction with the input shaft, and a pair of output disks that are arranged coaxially between the pair of input disks and rotate synchronously with each other. The output gear that rotates integrally with the output side disc, the power transmission shaft that connects the pair of input side discs, and the input side disc and the output side disc are in a freely tiltable rolling contact. Consisting of power rollers,
The differential planetary gear mechanism includes a sun gear, a ring gear arranged around the sun gear, and a plurality of planetary gears rotatably supported by a carrier between the sun gear and the ring gear. And coupled to the output shaft,
A continuously variable transmission,
While the output gear and the sun gear of the differential planetary gear mechanism are directly connected only by a counter shaft having counter gears at both ends , the output gear and the sun gear rotate in the same direction ,
A power transmission mechanism for transmitting the power of the variator to the differential planetary gear mechanism;
By reversing the rotation of the input shaft through the power transmission mechanism and transmitting it to the carrier of the differential planetary gear mechanism, and simultaneously transmitting it to the sun gear of the differential planetary gear mechanism through the counter shaft. A clutch mechanism that provides a differential mode for transmitting a differential component of the differential planetary gear mechanism to the output shaft, and a direct coupling mode for transmitting the rotation of the input shaft directly to the output shaft only through the counter shaft;
The continuously variable transmission characterized by further comprising. The ring gear of the differential planetary gear mechanism is connected to the output shaft;
The power transmission mechanism is composed of a reverse reduction planetary gear mechanism that reverses and transmits the rotation of the input shaft, and the reverse reduction planetary gear mechanism includes a sun gear connected to the power transmission shaft and the sun gear. A ring gear disposed around the center and connected to the carrier of the differential planetary gear mechanism via a central shaft, and a single pinion type rotatably supported by the carrier between the sun gear and the ring gear A plurality of planetary gears,
The clutch mechanism is provided between the carrier and a fixed portion of the reverse reduction planetary gear mechanism and is engaged with the differential mode for restricting and releasing the rotation of the carrier, and the differential planetary gear. A second clutch that is provided between the ring gear of the gear mechanism and the carrier and is involved in the direct connection mode that contacts and separates both of them;
The continuously variable transmission according to claim 1. The ring gear of the differential planetary gear mechanism is connected to the output shaft;
The power transmission mechanism is composed of a reverse reduction planetary gear mechanism that reverses and transmits the rotation of the input shaft, and the reverse reduction planetary gear mechanism includes a sun gear connected to the power transmission shaft and the sun gear. And a plurality of double pinion planetary gears rotatably supported by a carrier between the sun gear and the ring gear, and the carrier of the reverse reduction planetary gear mechanism. Is connected to the carrier of the differential planetary gear mechanism through a central axis,
The clutch mechanism is provided between the ring gear and the fixed portion of the reverse reduction planetary gear mechanism, and the first clutch involved in the differential mode for restricting and releasing the rotation of the ring gear; A second clutch that is provided between the ring gear of the moving planetary gear mechanism and the carrier and that is involved in the direct connection mode that contacts and separates both of them;
The continuously variable transmission according to claim 1. The plurality of planetary gears of the differential planetary gear mechanism is a double pinion type, the carrier of the differential planetary gear mechanism is connected to the output shaft,
The power transmission mechanism is composed of a reverse reduction planetary gear mechanism that reverses and transmits the rotation of the input shaft, and the reverse reduction planetary gear mechanism includes a sun gear connected to the power transmission shaft and the sun gear. A ring gear disposed around the ring, and a plurality of planetary gears of a single pinion type rotatably supported by a carrier between the sun gear and the ring gear, and the ring of the reverse reduction planetary gear mechanism A gear is connected to the ring gear of the differential planetary gear mechanism via a central axis;
The clutch mechanism is provided between the carrier and a fixed portion of the reverse reduction planetary gear mechanism and is engaged with the differential mode for restricting and releasing the rotation of the carrier, and the differential planetary gear. A second clutch that is provided between the ring gear of the gear mechanism and the carrier and is involved in the direct connection mode that contacts and separates both of them;
The continuously variable transmission according to claim 1.

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