JPH09210175A - Continuously variable transmission with gear ratio of infinity - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make miniaturizing and reducing the total number of of shaft in a transmission. SOLUTION: A transmission comprises a troidal type continuously variable transmission 2 and reduction gear 3 connected in parallel to a unit input shaft 1, a planetary gear mechanism 5 comprising a sun gear 5a coupled to the output gear 2a of the continuously variable transmission 2, a carrier 5b coupled to the reduction gear output shaft 3c, and a ring gear 5c couplet to the unit output shaft 6, a power cycling mode clutch 9 interposed within the power transmission path from the unit input shaft 1 to the carrier 5b, a direct coupling mode clutch 10 interposed within the power transmission path from the sun gear 5a to the unit output shaft 6. An output gear 2a of the continuous transmission mounted coaxially with the output shaft of the continuously variable transmission 2 engages to a counter gear 40 supported in parallel to the output shaft of the transmission 2 and further to the gear 4a, which is coaxially disposed on the sun gear 5a, the reduction gear 3 engages to the input gear 3a coaxially mounted to the unit input shaft 1 and an output gear 3b coaxially mounted to the carrier 5b.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a continuously variable transmission used in a vehicle or the like, and particularly to an infinitely variable transmission having an infinite transmission ratio used in an FF vehicle.

[0002]

2. Description of the Related Art Conventionally, a belt type or toroidal type continuously variable transmission has been known as a transmission for a vehicle in which a gear ratio can be continuously set. For further expansion, a continuously variable transmission and a speed reducer are arranged in parallel, and the output shafts of these are input to the planetary gear mechanism so that the gear ratio can be controlled to infinity. A gear transmission is known, for example, Japanese Patent Laid-Open No. 6-1.
It is disclosed in Japanese Patent Publication No. 01754.

As shown in FIG. 11, this is a unit input shaft 1 of an infinite transmission continuously variable transmission coupled to an engine.
And a continuously variable transmission 2 capable of changing the reduction ratio almost continuously,
The reduction gear 30 mainly composed of the counter gear 31 is connected in parallel, and the output shaft 4 of the continuously variable transmission 2 and the output shaft 3c of the reduction gear 30 are respectively input to the planetary gear mechanism 5 to output the unit output. As will be described later, the drive force is transmitted to the drive shaft of the vehicle via the shaft 6.

The reduction gear 3 has an input gear 3a provided coaxially with the unit input shaft 1 and a counter gear 3 provided on a gear 3b of a reduction gear output shaft 3c coaxially supported with the unit output shaft 6.
1 meshes with each other, and the speed reducer output shaft 3c rotates in accordance with the predetermined speed reduction ratio set in the speed reducer 3.

On the other hand, the output gear 2a formed on the output shaft of the continuously variable transmission 2 and the gear 4a provided on the output shaft 4 of the continuously variable transmission 2 which is coaxially supported by the unit output shaft 6 and teeth. The output shaft 4 of the continuously variable transmission according to the reduction ratio of the continuously variable transmission 2.
Rotates.

The output shaft 4 of the continuously variable transmission 2 is a planetary gear mechanism 5
Of the sun gear 5a, the output shaft 3c of the speed reducer 3 is connected to the carrier 5b of the planetary gear mechanism 5 composed of a single pinion through the power circulation mode clutch 9, and the ring gear 5c is an infinitely variable transmission continuously variable transmission. Is connected to the unit output shaft 6, which is the output shaft of the. And continuously variable transmission 2
A direct coupling mode clutch 10 is provided between the output shaft 4 and the unit output shaft 6.

In the continuously variable transmission 2, two sets of input disks 21, 21 and output disks 22, 22 are provided.
A case is shown in which the pair of power rollers 20, 20 are sandwiched by a toroidal type, and the gear ratio is continuously changed according to the tilt angle of the power roller 20.

Here, in the infinite transmission ratio mounted on the FF vehicle, the drive shafts 11a and 11b are mounted on the transmission housing.
The unit output shaft 6 is provided with a transmission output gear 7, and the transmission output gear 7 is provided with a final gear 12 of the differential gear 8 via a counter gear 70. And the driving force is transmitted to the drive shafts 11a and 11b coupled to the differential gear 8 at a predetermined total reduction ratio.

In such a continuously variable transmission with an infinite transmission ratio, the power circulation mode clutch 9 is released while the direct connection mode clutch 10 is engaged, so that output is performed only with the transmission ratio of the continuously variable transmission 2. By engaging the direct coupling mode and the power circulation mode clutch 9 and releasing the direct coupling mode clutch 10, the infinite transmission ratio continuously variable transmission according to the difference in the transmission ratio between the continuously variable transmission 2 and the speed reducer 3. The power circulation mode, which controls the entire unit speed ratio Ii (the speed ratio between the unit input shaft 1 and the unit output shaft 6) from the negative value to the positive value including infinity almost continuously, is selectively used. can do.

[0010]

However, in the above-described conventional infinitely variable transmission continuously variable transmission, the unit input shaft 1 and the final gear 12 of the differential gear 8 are coaxial with the unit input shaft 1 between the unit input shaft 1 and the final gear 12. Input / output shaft of the speed change gear 2 and reduction gear 3
Of the counter gear 31, the unit output shaft 6 (the output shaft 4 of the continuously variable transmission 2, the output shaft 3c of the speed reducer 3 and the planetary gear mechanism 5 are coaxial), the shaft of the counter gear 70, and the drive shaft 11a. 11b and a total of five axes including the drive axis are required, so the structure becomes complicated and the size of the entire apparatus increases,
There has been a problem that not only the manufacturing cost increases, but also the power transmission efficiency decreases due to the increase in the number of bearings that support the shaft.

Therefore, the present invention has been made in view of the above problems. By reducing the total number of shafts of a continuously variable transmission with an infinite transmission ratio, the size and weight of the device can be reduced and the power transmission efficiency can be improved. The purpose is to plan.

[0012]

A first invention is a continuously variable transmission and a speed reducer respectively connected to a unit input shaft,
A planetary gear mechanism including a sun gear connected to the output shaft of the continuously variable transmission, a carrier composed of a single pinion and connected to the output shaft of the reduction gear, and a ring gear connected to the unit output shaft, and a planetary gear from the unit input shaft. The mechanism includes a power circulation mode clutch interposed in the power transmission path to the carrier of the mechanism, and a direct coupling mode clutch interposed in the power transmission path from the output shaft of the continuously variable transmission to the unit output shaft. In the continuously variable transmission with an infinite transmission ratio capable of selectively engaging and releasing the power circulation mode clutch and the direct connection mode clutch, the power transmission path from the continuously variable transmission is the output shaft of the continuously variable transmission. And a sun gear of the planetary gear mechanism, which meshes with a continuously variable transmission output gear that is coaxial with and a counter gear that is axially supported in parallel with the output shaft of the continuously variable transmission. The power transmission path from the speed reducer meshes with the input gear coaxial with the unit input shaft and is coaxial with the carrier of the planetary gear mechanism. It is composed of an installed output gear.

The second aspect of the present invention comprises a continuously variable transmission and a speed reducer each connected to a unit input shaft, a ring gear connected to the output shaft of the continuously variable transmission, and a single pinion to output the speed reducer. A planetary gear mechanism consisting of a carrier connected to the shaft and a sun gear connected to the unit output shaft; a power circulation mode clutch interposed in the middle of the power transmission path from the unit input shaft to the carrier of the planetary gear mechanism; And a direct connection mode clutch interposed in the power transmission path from the output shaft of the continuously variable transmission to the unit output shaft so that the power circulation mode clutch and the direct connection mode clutch can be selectively engaged and released. In the infinite ratio continuously variable transmission, the power transmission path from the continuously variable transmission is the continuously variable transmission output gear coaxial with the output shaft of the continuously variable transmission, and the output of this continuously variable transmission. A gear that meshes with a counter gear that is axially supported in parallel with the shaft and that is composed of a ring gear of the planetary gear mechanism and a first gear that is coaxially arranged, while transmitting power from the speed reducer. The path includes an output gear that meshes with an input gear that is coaxial with the unit input shaft and that is coaxially arranged with the carrier of the planetary gear mechanism.

A third aspect of the invention is a continuously variable transmission and a speed reducer respectively connected to the unit input shaft, a sun gear connected to the output shaft of the continuously variable transmission, a ring gear connected to the output shaft of the speed reducer, and A planetary gear mechanism consisting of a carrier coupled to the unit output shaft, a power circulation mode clutch interposed in the power transmission path from the unit input shaft to the ring gear of the planetary gear mechanism, and an output of the continuously variable transmission. A direct coupling mode clutch interposed in the power transmission path from the shaft to the unit output shaft to selectively engage and release the power circulation mode clutch and the direct coupling mode clutch. In the machine, the carrier of the planetary gear mechanism is configured by a double pinion, and a power transmission path from the continuously variable transmission is a coaxial shaft with an output shaft of the continuously variable transmission. A transmission output gear and a first gear that meshes with a counter gear that is axially supported in parallel with the output shaft of the continuously variable transmission and that is coaxial with the sun gear of the planetary gear mechanism. On the other hand, the power transmission path from the speed reducer includes an output gear that meshes with an input gear that is coaxial with the unit input shaft and that is coaxial with the ring gear of the planetary gear mechanism.

A fourth aspect of the invention is a continuously variable transmission and a speed reducer respectively connected to the unit input shaft, a carrier connected to the output shaft of the continuously variable transmission, a ring gear connected to the output shaft of the speed reducer, and A planetary gear mechanism consisting of a sun gear connected to the unit output shaft, a power circulation mode clutch interposed in the power transmission path from the unit input shaft to the ring gear of the planetary gear mechanism, and an output of the continuously variable transmission. A direct coupling mode clutch interposed in the power transmission path from the shaft to the unit output shaft to selectively engage and release the power circulation mode clutch and the direct coupling mode clutch. In the machine, the carrier of the planetary gear mechanism is configured by a double pinion, and a power transmission path from the continuously variable transmission is a coaxial shaft with an output shaft of the continuously variable transmission. A transmission output gear and a first gear that meshes with a counter gear that is axially supported in parallel with the output shaft of the continuously variable transmission and that is coaxial with the carrier of the planetary gear mechanism. On the other hand, the power transmission path from the speed reducer includes an output gear that is meshed with an input gear that is coaxial with the unit input shaft and that is coaxial with a ring gear of the planetary gear mechanism.

A fifth aspect of the present invention is the first to fourth aspects of the invention.
The reduction ratio of the speed reducer according to any one of
Ig is the gear ratio Id of the counter gear train input from the output shaft of the continuously variable transmission to the planetary gear mechanism through the counter gear,
It is set to be equal to or less than the product of the maximum gear ratios Ic _LOW that can be set in the continuously variable transmission, or less than these products and as large as possible.

Further, a sixth invention is the above-mentioned first to fourth inventions.
In any one of the inventions, the continuously variable transmission is
It is composed of a toroidal type continuously variable transmission in which the rotation direction of the input / output shaft is reversed, and the unit output shaft has a transmission output gear directly meshed with a final gear that drives a differential gear connected to the drive shaft. Set up.

[0018]

Therefore, in the first aspect of the present invention, the driving force input to the unit input shaft is transmitted in parallel to the continuously variable transmission and the speed reducer, respectively, and the driving force input to the continuously variable transmission is not transmitted. It is transmitted to a first gear that is arranged coaxially with the sun gear of the planetary gear mechanism, through a counter gear that meshes with a continuously variable transmission output gear that is coaxial with the output shaft of the continuously variable transmission. On the other hand, the driving force input to the speed reducer is transmitted from the input gear that is coaxial with the continuously variable transmission to the output gear that is coaxial with the carrier of the planetary gear mechanism that is configured by a single pinion, and the engaged state of the power circulation mode clutch. The carrier of the planetary gear mechanism is driven accordingly. Since the rotation direction of the sun gear is the same as that of the output shaft of the continuously variable transmission because the counter gear is interposed, the rotation direction of the carrier is opposite to that of the unit input shaft. When a toroidal type with an input / output shaft coaxial with the shaft is adopted, the rotation direction of the output shaft of the continuously variable transmission is opposite to that of the unit input shaft, so the rotation directions of the sun gear and carrier are the same. In the direct connection mode in which the direct connection mode clutch is engaged and the power circulation mode clutch is released, the gear ratio Ii between the unit input shaft and the unit output shaft is the gear ratio Ic set in the continuously variable transmission and the counter gear. In the power circulation mode in which the direct transmission mode clutch is disengaged and the power circulation mode clutch is engaged, the gear ratio Ic of the continuously variable transmission,
The ring gear connected to the unit output shaft is driven at the unit speed ratio Ii corresponding to the speed reduction ratio Ig of the speed reducer.

According to a second aspect of the invention, the driving force input to the unit input shaft is transmitted in parallel to the continuously variable transmission and the speed reducer, respectively, and the driving force input to the continuously variable transmission is not transmitted. It is transmitted to the first gear arranged coaxially with the ring gear of the planetary gear mechanism via a counter gear that meshes with the output gear of the continuously variable transmission coaxial with the output shaft of the continuously variable transmission. On the other hand, the driving force input to the speed reducer is transmitted from the input gear that is coaxial with the continuously variable transmission to the output gear that is coaxial with the carrier of the planetary gear mechanism, and the planetary gear mechanism is selected according to the engaged state of the power circulation mode clutch. Carrier is driven. Since the rotation direction of the ring gear is the same as that of the output shaft of the continuously variable transmission because the counter gear is interposed, the rotation direction of the carrier is opposite to that of the unit input shaft. When a toroidal type that has an input / output shaft coaxial with the shaft is used, the rotation direction of the output shaft of the continuously variable transmission is opposite to that of the unit input shaft, so the ring gear and carrier rotate in the same direction. In the direct connection mode where the direct connection mode clutch is engaged and the power circulation mode clutch is released, the gear ratio between the unit input shaft and the unit output shaft
Ii is equal to the product of the gear ratio Ic set in the continuously variable transmission and the counter gear train Id, and in the power circulation mode where the direct coupling mode clutch is released and the power circulation mode clutch is engaged, the transmission of the continuously variable transmission is changed. The sun gear connected to the unit output shaft is driven at the ratio Ic and the unit speed ratio Ii corresponding to the reduction ratio Ig of the speed reducer.

According to the third aspect of the invention, the driving force input to the unit input shaft is transmitted in parallel to the continuously variable transmission and the speed reducer, respectively, and the driving force input to the continuously variable transmission is not transmitted. It is transmitted to a first gear that is arranged coaxially with the sun gear of the planetary gear mechanism, through a counter gear that meshes with a continuously variable transmission output gear that is coaxial with the output shaft of the continuously variable transmission. On the other hand, the driving force input to the reduction gear is transmitted from the input gear coaxial with the continuously variable transmission to the output gear coaxial with the ring gear of the planetary gear mechanism,
The ring gear of the planetary gear mechanism is driven according to the engagement state of the power circulation mode clutch. Since the rotation direction of the sun gear is the same as that of the output shaft of the continuously variable transmission because the counter gear is interposed, the rotation direction of the ring gear is opposite to that of the unit input shaft. When a toroidal type with an input / output shaft coaxial with the shaft is adopted, the rotation direction of the output shaft of the continuously variable transmission is opposite to that of the unit input shaft, so the sun gear and ring gear rotate in the same direction. In the direct connection mode in which the direct connection mode clutch is engaged and the power circulation mode clutch is released, the gear ratio Ii between the unit input shaft and the unit output shaft is
Is equal to the product of the gear ratio Ic and the counter gear train gear ratio Id set in the continuously variable transmission, the direct connection mode clutch is released, and the power circulation mode clutch is engaged. The unit output shaft connected to the carrier constituted by the double pinion is driven at the unit speed ratio Ii corresponding to the speed ratio Ic and the speed reduction ratio Ig of the speed reducer.

According to a fourth aspect of the invention, the driving force input to the unit input shaft is transmitted in parallel to the continuously variable transmission and the speed reducer, respectively, and the driving force input to the continuously variable transmission is zero. Through a counter gear that meshes with the output gear of the continuously variable transmission coaxial with the output shaft of the continuously variable transmission, it is transmitted to the first gear that is arranged coaxially with the carrier of the planetary gear mechanism configured by the double pinion. . On the other hand, the driving force input to the speed reducer is transmitted from the input gear that is coaxial with the continuously variable transmission to the output gear that is coaxial with the ring gear of the planetary gear mechanism, and the drive force of the planetary gear mechanism is changed according to the engaged state of the power circulation mode clutch. The ring gear is driven. Since the rotation direction of the carrier is the same as that of the output shaft of the continuously variable transmission because the counter gear is interposed, the rotation direction of the ring gear is opposite to that of the unit input shaft. When a toroidal type with an input / output shaft coaxial with the shaft is adopted, the rotation direction of the output shaft of the continuously variable transmission is opposite to that of the unit input shaft, so the rotation directions of the carrier and ring gear are the same. In the direct connection mode in which the direct connection mode clutch is engaged and the power circulation mode clutch is released, the gear ratio Ii between the unit input shaft and the unit output shaft is the gear ratio Ic set in the continuously variable transmission and the counter gear train. In the power circulation mode in which the direct transmission mode clutch is released and the power circulation mode clutch is engaged, the gear ratio Ic of the continuously variable transmission and the reduction gear ratio Ig of the reduction gear are matched with the product of the gear ratio Id. The unit output shaft connected to the sun gear is driven at the corresponding unit speed ratio Ii.

A fifth aspect of the present invention is the reduction gear ratio Ig of the speed reducer.
Is set equal to the product of the gear ratio Id of the counter gear train input from the output shaft of the continuously variable transmission to the planetary gear mechanism through the counter gear and the maximum gear ratio Ic _LOW that can be set by the continuously variable transmission. As a result, at the maximum speed ratio Ic _LOW of the continuously variable transmission, the unit speed ratios of the direct drive mode and the power circulation mode can be matched, and the direct drive mode and the power circulation mode can be smoothly switched without causing a step difference in the speed ratio. The speed ratio of the continuously variable transmission can be effectively used from Ic _LOW to Ic _Hi . If the reduction gear ratio Ig cannot be set to Ig = counter gear train gear ratio Id × maximum gear ratio Ic _LOW , the maximum reduction ratio Ig that can be set below this product is set to obtain the continuously variable transmission. In the vicinity of the maximum gear ratio Ic _LOW , the unit gear ratios of the direct drive mode and the power circulation mode can be matched, and the direct drive mode and the power circulation mode can be smoothly switched without causing a step in the gear ratio. The gear ratio of the multi-speed transmission can be effectively used from Ic _LOW to Ic _Hi .

According to a sixth aspect of the present invention, the continuously variable transmission is a toroidal type continuously variable transmission in which the rotation direction of the input / output shaft is reversed, so that the continuously variable transmission is installed coaxially with the unit input shaft. The output shaft can be arranged, and the unit output shaft directly meshes with the final gear that drives the differential gear connected to the drive shaft via the transmission output gear. A unit input shaft coaxial with the step transmission, a counter gear shaft, a unit output shaft coaxial with the planetary gear mechanism, and a drive shaft can be included in total of four shafts.

[0024]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to the accompanying drawings.

FIG. 1 shows an FF using the toroidal type continuously variable transmission shown in FIG. 11 of the conventional example as the continuously variable transmission 2.
1 shows an example of a continuously variable transmission having an infinite transmission ratio mounted on a vehicle, in which the counter gear 31 of the conventional example is eliminated and the output gear 2a of the continuously variable transmission 2 and the gear 4a of the output shaft 4 are shown. A counter gear 40a is newly provided between the above and other parts, and the other parts are configured in substantially the same manner as the conventional example,
The same components are denoted by the same reference numerals, and redundant description will be omitted.

The difference from the conventional example is that the counter gear 3
1 is eliminated and the input gear 3a provided on the unit input shaft 1 of the speed reducer 3 and the gear 3b as an output gear connected to the speed reducer output shaft 3c are directly meshed with each other, while the continuously variable transmission is used. A counter gear 40a is interposed between the output gear 2a of the second gear 2 and the gear 4a of the continuously variable transmission output shaft 4 which is coaxially supported by the planetary gear mechanism 5, and these output gear 2a, the counter gear 40, the gear A counter gear train 40 is composed of 4a. The gear 4a of the continuously variable transmission output shaft 4 constitutes a first gear.

Then, the transmission output gear 7 provided on the unit output shaft 6 and the final gear 12 of the differential gear 8 are directly meshed with each other, so that the shaft of the continuously variable transmission with an infinite transmission ratio is changed to the continuously variable transmission 2. The input / output shaft, the shaft of the counter gear 40, the unit output shaft 6, and the drive shafts 11a and 11b, which are a total of four shafts, reduce the total number of shafts by one compared with the conventional example. To be done.

In the planetary gear mechanism 5, the sun gear 5a is connected to the output shaft 4 of the continuously variable transmission, the carrier 5b formed of a single pinion is connected to the output shaft 3c of the speed reducer 3, and the ring gear 5c is a unit, as in the conventional case. It is coupled to the output shaft 6.

The operation of the infinitely variable transmission continuously variable transmission having such a configuration will be described in detail below.

First, consider the power circulation mode in which the direct circulation mode clutch 10 is released while the power circulation mode clutch 9 is engaged. When the unit input shaft 1 and the individual elements such as the continuously variable transmission 2 and the counter gear 40 have different rotational directions, the rotational speed is indicated by a negative value, while the same is indicated by a positive value. .

Now, since the rotation speed inverted by the speed reducer 3 with respect to the rotation direction of the unit input shaft 1 is input to the carrier 5b, the rotation speed N _C of the carrier 5b is

[0032]

[Equation 1]

Here, N _{IN is the} unit input shaft rotation speed Ig, and the reduction ratio of the speed reducer 3.

On the other hand, the rotation direction of the sun gear 5a coupled to the output shaft 4 of the continuously variable transmission 2 is the toroidal type of the continuously variable transmission 2. Therefore, the rotation direction of the output gear 2a is the same as that of the unit input shaft 1. is inverted for, since this direction of rotation is interposed the counter gears 40a, is input directly to the output shaft 4 becomes a direction opposite to the rotation direction unit input shaft 1 of the sun gear 5a, the rotation speed N _S of the sun gear 5a It becomes like the following formula.

[0035]

[Equation 2]

However, Ic: gear ratio of the continuously variable transmission Id: counter gear train gear ratio, that is, the counter gear 4
The reduction ratio of the output gears 2a-4a which mesh with 0 is shown.

The unit output shaft 6 is the ring gear 5
Since it is coupled to c, the rotation speed N _OUT of the unit output shaft 6
Is expressed by the following equation.

[0038]

(Equation 3)

Where N _{R is the} number of revolutions of the ring gear 5c α is the number of teeth of the sun gear 5a / the number of teeth of the ring gear 5c.

Since the transmission output gear 7 and the final gear 12 provided on the unit output shaft 6 are directly meshed with each other, the drive shaft 1
The rotation speed N _V of 1a and 11b can be expressed by the following equation. However, the drive shaft rotational speed N _V indicates the case where the differential gear 8 is in the locked state (the rotational speeds of the left and right drive shafts 11a and 11b are the same).

[0041]

(Equation 4)

However, If; reduction ratio of the final gear train.

Therefore, in the power circulation mode, as shown in FIG. 2, the gear ratio Ic of the continuously variable transmission 2 is changed from the speed increasing side to the speed reducing side by the gear change ratio Iv including the final gear speed reducing ratio. Can smoothly shift from the reverse rotation (gear ratio <0) to the stop (geared neutral) to the mode switching point P on the forward rotation side. In FIG. 2, the reciprocal of the unit total speed ratio Iv is the unit input shaft 1
The drive shaft rotational speed N _V when the rotational speed N _IN = 1 is shown, and an example in which each gear ratio is set as follows is shown.

Continuously variable transmission gear ratio Ic = 0.5 to 2.0 Counter gear train gear ratio Id = 1.0 Reduction gear reduction ratio Ig = 2.0 Final gear reduction ratio If = 3.5 Planetary gear reduction ratio (Number of teeth of sun gear 5a / ring gear 5c
On the other hand, while releasing the power circulation mode clutch 9,
The CVT direct mode to enter into a direct mode clutch 10, since the reduction gear 3 and the planetary gear mechanism 5 is split off from the power transmission path, the rotational speed N _OUT of the unit output shaft 6
Is

[0045]

(Equation 5)

Similarly, the drive shaft speed N _V is also

[0047]

(Equation 6)

Is as follows.

That is, the drive shaft speed N _V is 1 / IdIc _LOW If to 1 when the gear ratio Ic of the continuously variable transmission 2 decreases from the deceleration side to the acceleration side as in the direct connection mode shown in FIG. / IdI
c It is possible to continuously shift gears up to _Hi If.

However, Ic _LOW is the maximum Low gear ratio that can be set by the continuously variable transmission 2. Ic _Hi is the maximum Hi gear ratio that can be set by the continuously variable transmission 2.

Here, by switching from the direct coupling mode to the power circulation mode at the lowest Low gear ratio of the continuously variable transmission 2, any gear ratio including stop can be set between forward movement and reverse movement (forward rotation to reverse rotation). In the meantime, the number of shafts of the entire transmission including the drive shafts can be reduced from 5 to 4 shafts as compared with the conventional example, and the overall size and weight of the transmission can be reduced. By reducing the total number of bearings as compared with, it is possible to promote the improvement of power transmission efficiency.

FIG. 3 shows a second embodiment, which is replaced with a counter gear train 40 'which increases the speed ratio Id of the counter gear train of the first embodiment, and other structures are the same as those of the first embodiment. This is similar to that of the first embodiment.

The graph of FIG. 4 shows the relationship between the reciprocal of the continuously variable transmission gear ratio Ic and the unit gear ratio Ii when the respective gear ratios are set as follows.

Continuously variable transmission gear ratio Ic = 0.5 to 2.0 Counter gear train gear ratio Id = 0.8 Reduction gear reduction ratio Ig = 1.6 Final gear reduction ratio If = 3.5 Planetary gear reduction ratio (Number of teeth of sun gear 5a / ring gear 5c
Here, the reduction ratio Ig of the reduction gear 3 is set to the gear ratio Id of the counter gear train 40 and the maximum Low gear ratio Ic _LOW of the continuously variable transmission 2 here.
It is set to be equal to the product of, Ig = Id × Ic _LOW .

That is, in this embodiment, Ig = 0.8 × 2.0 = 1.6.

As shown in FIG. 4, at the maximum Low gear ratio Ic _LOW of the continuously variable transmission 2 at the mode switching point P, the unit gear ratio Ii in the direct coupling mode and the power circulation mode become the same, and the direct coupling mode and the power circulation The mode can be switched smoothly at this gear ratio Ic _LOW without causing a step, and the gear ratio Ic of the continuously variable transmission 2 can be set to the maximum Hi.
It is possible to effectively utilize from the gear ratio to the lowest Low gear ratio.

In the power circulation mode, when Ic = Ic _LOW , the drive shaft rotational speed N _V is expressed by the following equation.

[0058]

(Equation 7)

On the other hand, in the direct connection mode, when Ic = Ic _LOW , the drive shaft rotational speed N _V is expressed by the following equation.

[0060]

(Equation 8)

Therefore, since the above equations (7) and (8) are equal, the unit _low gear ratio Ii in the direct connection mode and the power circulation mode is equal at the maximum Low gear ratio Ic _{LOW which} is the mode switching point P. I understand.

The gear ratio Id = of the counter gear train 40 '
Even if 1 (constant speed) and Id> 1 (deceleration), if Ig = Id × Ic _LOW is set in the same manner as above, at the lowest Low gear ratio Ic _LOW of the continuously variable transmission 2 at the mode switching point P. Since the unit speed ratio Ii in the direct connection mode and the power circulation mode are the same, and the infinite speed ratio continuously variable transmission has four axes, smooth switching can be performed without causing a step difference in the total reduction ratio. The gear ratio of the stage transmission 2 can be effectively used from Ic _Hi to Ic _LOW .

Further, the number of teeth of the input gear 3a and the output gear 3b
If Ig = Id × Ic _LOW cannot be set due to the relationship of the number of teeth of, the speed reduction ratio Ig of the speed reducer 3 is set to the counter gear train speed change ratio.
Id × Maximum Low Gear ratio Ic _LOW or less, and set to a value as large as possible.

In this case, at the mode switching point (in other words, the gear ratio of the continuously variable transmission at the time of mode switching) Ig / Id, the direct reduction mode and the power circulation mode are smoothly operated without causing a step difference in the total reduction ratio. Can be connected to.

At this time, the reduction ratio Ig is a value as large as possible below Id × Ic _LOW , and therefore the mode switching point Ig / Id is
Since the value is close to Ic _LOW when Ic _LOW or less, continuously variable transmission 2
The gear ratio Ic can be effectively used from the highest Hi gear ratio to almost the lowest Gear ratio.

FIG. 5 shows a third embodiment, in which the first
By changing the planetary gear mechanism 5 of the embodiment to 105,
Other configurations are the same as those of the first embodiment.

The planetary gear mechanism 105 includes a single pinion carrier 105b, which is coupled to the output shaft 3c of the speed reducer 3, the sun gear 105a serving as the unit output shaft 6, and the ring gear 105c serving as the continuously variable transmission 2. The gears 4a as the first gears are respectively coupled to the coupled output shafts 4 and are arranged coaxially with the ring gear 5c.

While the direct coupling mode clutch 10 is released,
In the power circulation mode in which the circulation mode clutch 9 is engaged,
The rotation speed N _C of the carrier 105b rotated by the input from the speed reducer 3 and the rotation speed N _R of the ring gear 105c rotated by the input from the continuously variable transmission 2 are

[0069]

[Equation 9]

The rotation speed of the unit output shaft 3 N _OUT
Is expressed by the following equation.

[0071]

(Equation 10)

Therefore, the rotation speed N _V of the drive shafts 11a and 11b is

[0073]

[Equation 11]

Is obtained.

On the other hand, the power circulation mode clutch 9 is released and the direct coupling mode clutch 10 is engaged. In the direct coupling mode, the rotation speed N _OUT of the unit output shaft 6 is

[0076]

(Equation 12)

Thus, the drive shaft speed N _V is

[0078]

(Equation 13)

Is obtained.

Here, the continuously variable transmission gear ratio Ic = 0.5 to 2.0, the counter gear train gear ratio Id = 1.0, the reduction gear reduction ratio Ig = 2.0 = Id × Ic _LOW = 1.0 × 2.
0 Final gear reduction ratio If = 3.5 Planetary gear reduction ratio (number of teeth of sun gear 5a / ring gear 5c
The number of teeth of α) is set to 36/67, and the relationship between the continuously variable transmission gear ratio Ic and the reciprocal of the unit total gear ratio Iv including the final gear reduction ratio is shown in the graph of FIG.

In this embodiment, in the power circulation mode and the direct connection mode, it is possible to function as an infinitely variable transmission continuously variable transmission. In addition, since Ig = Id × Ic _LOW is set, there is a step in the total reduction ratio. Smooth mode switching can be performed.

FIG. 7 shows a fourth embodiment, which is replaced with a planetary gear mechanism 205 in which the input / output relationship of the planetary gear mechanism 5 of the first embodiment is changed, and other configurations are as follows.
This is the same as the first embodiment.

The planetary gear mechanism 205 includes a carrier 205b composed of a double pinion.
5b is connected to the unit output shaft 6, and the output shaft 3 of the speed reducer 3 is connected.
c is connected to the ring gear 205c, and the output shaft 4 connected to the continuously variable transmission 2 is connected to the sun gear 205a.

While the direct coupling mode clutch 10 is released,
In the power circulation mode in which the circulation mode clutch 9 is engaged,
Ring gear 205c rotated by input from the speed reducer 3
The rotational speed N _R and the rotational speed N _S of the sun gear 205a which is rotated by the input from the continuously variable transmission 2,

[0085]

[Equation 14]

Is the number of rotations N _OUT of the unit output shaft 3.
Is

[0087]

(Equation 15)

Therefore, the rotational speed N _V of the drive shafts 11a and 11b is

[0089]

(Equation 16)

## EQU10 ##

On the other hand, the rotational speed N _OUT of the unit output shaft 6 in the direct coupling mode in which the power circulation mode clutch 9 is released and the direct coupling mode clutch 10 is engaged is

[0092]

[Equation 17]

Therefore, the drive shaft speed N _V is

[0094]

(Equation 18)

Is obtained.

Here, the continuously variable transmission gear ratio Ic = 0.5-
2.0 Counter gear train gear ratio Id = 1.0 Reduction gear reduction ratio Ig = 2.0 = Id × Ic _LOW = 1.0 × 2.
0 Final gear reduction ratio If = 3.5 Planetary gear reduction ratio (number of teeth of sun gear 5a / ring gear 5c
The number of teeth of α) is set to 29/67, and the relationship between the continuously variable transmission gear ratio Ic and the reciprocal of the unit total gear ratio Iv including the final gear reduction ratio is shown in the graph of FIG.

Also in this embodiment, in the power circulation mode and the direct connection mode, it is possible to function as an infinitely variable transmission continuously variable transmission, and in addition, since Ig = Id × Ic _LOW is set, there is a step in the total reduction ratio. It is possible to smoothly switch modes.

FIG. 9 shows a fifth embodiment, in which the input / output relationship of the planetary gear mechanism 105 of the third embodiment is changed and the carrier is replaced with a planetary gear mechanism 305 constituted by a double pinion. The other configurations are the same as those in the third embodiment.

In the planetary gear mechanism 305, the carrier 305b composed of a double pinion is connected to the output shaft 4 connected to the continuously variable transmission 2, the ring gear 305c is connected to the output shaft 3c of the speed reducer 3, and the unit output shaft 6 is connected. They are respectively connected to the sun gear 305a.

While the direct coupling mode clutch 10 is released,
In the power circulation mode in which the circulation mode clutch 9 is engaged,
Ring gear 305c rotated by input from the speed reducer 3
The rotational speed N _C of the carrier 305b which is rotated by the input from the rotational speed N _R and the continuously variable transmission 2,

[0101]

[Equation 19]

And the rotational speed N _OUT of the unit output shaft 3
Is

[0103]

(Equation 20)

Therefore, the rotational speed N _V of the drive shafts 11a and 11b is

[0105]

(Equation 21)

The following is obtained.

On the other hand, the rotational speed N _OUT of the unit output shaft 6 in the direct coupling mode in which the power circulation mode clutch 9 is released and the direct coupling mode clutch 10 is engaged is

[0108]

(Equation 22)

Therefore, the drive shaft speed N _V is

[0110]

(Equation 23)

Is obtained.

Here, the continuously variable transmission gear ratio Ic = 0.5 to 2.0, the counter gear train gear ratio Id = 1.0, the reduction gear reduction ratio Ig = 2.0 = Id × Ic _LOW = 1.0 × 2.
0 Final gear reduction ratio If = 3.5 Planetary gear reduction ratio (number of teeth of sun gear 5a / ring gear 5c
The graph of FIG. 10 shows the relationship between the continuously variable transmission gear ratio Ic and the reciprocal of the unit total gear ratio Iv including the final gear reduction ratio when α = 29/67 is set.

Also in this embodiment, in the power circulation mode and the direct connection mode, it is possible to function as an infinitely variable transmission continuously variable transmission, and in addition, since Ig = Id × Ic _LOW is set, there is a step in the total reduction ratio. It is possible to smoothly switch modes.

Thus, by reducing the number of shafts (the number of shafts including the drive shafts 11a and 11b) of the continuously variable transmission having an infinite transmission ratio applied to the FF vehicle from the five shafts of the conventional example to four shafts, The size and weight of the device can be reduced, and the number of bearings can be reduced as the number of shafts is reduced, so that the power transmission efficiency can be improved and the reduction ratio Ig of the reduction gear 3 can be improved.
Is set to be approximately equal to the product of the gear ratio Id of the counter gear train 40 and the maximum Low gear ratio Ic _LOW of the continuously variable transmission 2 so that the total reduction ratio (unit gear ratio) at the switching point between the direct coupling mode and the power circulation mode. The ratio Ii) is smoothly switched without causing a step, and at the same time, the gear ratio of the continuously variable transmission 2 is changed.
Ic from the lowest Low gear ratio Ic _LOW to the highest Hi gear ratio Ic _Hi ,
It can be used effectively.

[0115]

As described above, according to the first aspect of the invention, the rotation direction of the sun gear to which the driving force is transmitted from the output shaft of the continuously variable transmission is such that the unit output shaft coaxial with the planetary gear mechanism and the continuously variable transmission. Since a counter gear is installed between the output shaft of the unit and the output shaft of the continuously variable transmission, the direction of rotation of the carrier is reverse to that of the unit input shaft by the speed reducer. , For example, when a toroidal type with an input / output shaft coaxial with the unit input shaft is adopted, the rotation direction of the output shaft of the continuously variable transmission is reversed with respect to the unit input shaft. The rotation directions can be the same, and in the direct connection mode in which the direct connection mode clutch is engaged and the power circulation mode clutch is released, the gear ratio Ii between the unit input shaft and the unit output shaft is the gear ratio set by the continuously variable transmission. Ratio Ic and In the power circulation mode where the product of the counter gear train gear ratio Id matches, the direct coupling mode clutch is disengaged, and the power circulation mode clutch is engaged, the unit corresponding to the gear ratio Ic of the continuously variable transmission and the reduction ratio Ig of the speed reducer. If the ring gear connected to the unit output shaft is driven at the gear ratio Ii and the differential gear connected to the drive shaft is meshed with this unit output shaft, the number of shafts of the entire transmission will be the same as that of the unit input shaft and counter gear. Axis, unit output axis, including drive axis 4
With the shaft configuration, it is possible to reduce the number of shafts compared to the conventional five shafts. By promoting reduction in size and weight of an infinite transmission ratio transmission and reducing the number of bearings. The power transmission efficiency can be improved.

According to the second aspect of the invention, the driving force input to the unit input shaft is transmitted in parallel to the continuously variable transmission and the speed reducer, respectively, and the driving force input to the continuously variable transmission is zero. It is transmitted to the first gear, which is arranged coaxially with the ring gear of the planetary gear mechanism, through the counter gear that meshes with the output gear of the continuously variable transmission that is coaxial with the output shaft of the stepped transmission, while being input to the reduction gear. The generated driving force is from the input gear coaxial with the continuously variable transmission,
It is transmitted to the output gear that is coaxial with the carrier of the planetary gear mechanism,
In the direct coupling mode in which the direct coupling mode clutch is engaged and the power circulation mode clutch is released, the gear ratio Ii between the unit input shaft and the unit output shaft is the gear ratio I set in the continuously variable transmission.
In the power circulation mode where the product of c and the gear ratio Id of the counter gear train matches, the direct connection mode clutch is disengaged, and the power circulation mode clutch is engaged, depending on the gear ratio Ic of the continuously variable transmission and the reduction ratio Ig of the speed reducer. With the unit gear ratio Ii, the sun gear connected to the unit output shaft is driven, and if the differential gear connected to the drive shaft is engaged with this unit output shaft, the number of shafts of the entire transmission is It becomes the counter gear shaft and unit output shaft, and the drive shaft is combined into a four-axis configuration.
It is possible to reduce the number of shafts as compared with the conventional five shafts, which promotes downsizing and weight reduction of a transmission with an infinite transmission ratio, and also reduces the number of bearings to improve power transmission efficiency. It is possible to improve.

According to the third aspect of the invention, the driving force input to the unit input shaft is transmitted in parallel to the continuously variable transmission and the speed reducer, respectively, and the driving force input to the continuously variable transmission is zero. It is transmitted to the first gear, which is arranged coaxially with the sun gear of the planetary gear mechanism, through the counter gear that meshes with the output gear of the continuously variable transmission that is coaxial with the output shaft of the stepped transmission, while being input to the reduction gear. The generated driving force is transmitted from the input gear that is coaxial with the continuously variable transmission to the output gear that is coaxial with the ring gear of the planetary gear mechanism, and the ring gear of the planetary gear mechanism is driven according to the engagement state of the power circulation mode clutch to directly connect the gears. Fasten the mode clutch,
Power circulation mode In the direct connection mode where the clutch is released, the gear ratio Ii between the unit input shaft and the unit output shaft matches the product of the gear ratio Ic set in the continuously variable transmission and the counter gear train gear ratio Id, and the direct connection mode In the power circulation mode with the clutch disengaged and the clutch engaged, in the power circulation mode Ic of the continuously variable transmission and the unit speed ratio Ii according to the reduction ratio Ig of the speed reducer.
The unit output shaft connected to the carrier composed of the double pinion is driven by. If the differential gear connected to the drive shaft is meshed with this unit output shaft, the number of shafts of the entire transmission becomes the unit input shaft, the counter gear shaft, and the unit output shaft. With this structure, the number of shafts can be reduced compared to the conventional five shafts, and the size and weight of a transmission with an infinite transmission ratio can be reduced, and the number of bearings can be reduced to reduce power consumption. It is possible to improve the transmission efficiency.

According to the fourth aspect of the invention, the driving force input to the unit input shaft is transmitted in parallel to the continuously variable transmission and the speed reducer, respectively, and the driving force input to the continuously variable transmission is zero. Through a counter gear that meshes with the output gear of the continuously variable transmission coaxial with the output shaft of the continuously variable transmission, it is transmitted to the first gear that is arranged coaxially with the carrier of the planetary gear mechanism configured by the double pinion. On the other hand, the driving force input to the speed reducer is transmitted from the input gear that is coaxial with the continuously variable transmission to the output gear that is coaxial with the ring gear of the planetary gear mechanism, and the drive force of the planetary gear mechanism is changed according to the engaged state of the power circulation mode clutch. The ring gear is driven,
In the direct connection mode in which the direct connection mode clutch is engaged and the power circulation mode clutch is released, the gear ratio Ii between the unit input shaft and the unit output shaft is the product of the gear ratio Ic set in the continuously variable transmission and the counter gear train gear ratio Id. In the power circulation mode in which the direct connection mode clutch is disengaged and the power circulation mode clutch is engaged, the gear ratio Ic of the continuously variable transmission and the reduction ratio of the speed reducer
The unit output shaft connected to the sun gear is driven at the unit speed ratio Ii according to the difference in Ig. If the differential gear connected to the drive shaft is meshed with this unit output shaft, the number of shafts of the entire transmission becomes the unit input shaft, the counter gear shaft, and the unit output shaft. It becomes the composition,
It is possible to reduce the number of shafts as compared with the conventional five shafts, which promotes downsizing and weight reduction of a transmission with an infinite transmission ratio, and also reduces the number of bearings to improve power transmission efficiency. It is possible to improve.

The fifth aspect of the present invention is the reduction gear ratio Ig of the speed reducer.
Is a gear ratio Id of the counter gear train input from the output shaft of the continuously variable transmission to the planetary gear mechanism via the counter gear,
By setting it equal to the product of the maximum gear ratio Ic _LOW that can be set in the continuously variable transmission, the unit gear ratios of the direct coupling mode and the power circulation mode can be made to match at the maximum gear ratio Ic _LOW of the continuously variable transmission. It is possible to smoothly switch between the direct coupling mode and the power circulation mode without causing a step in the gear ratio, and it is possible to effectively use the gear ratio of the continuously variable transmission from Ic _LOW to Ic _Hi . If the gear ratio Ig cannot be set to Ig = counter gear train gear ratio Id x maximum gear ratio Ic _LOW , the maximum gear ratio that can be set below the product of these
By setting Ig, it is possible to make the unit speed ratios of the direct drive mode and the power circulation mode almost match in the vicinity of the maximum speed ratio Ic _LOW of the continuously variable transmission. The mode can be switched smoothly, and the gear ratio of the continuously variable transmission can be changed from Ic _LOW to Ic _Hi.
Can be used effectively.

The sixth aspect of the present invention is that the continuously variable transmission is a toroidal type continuously variable transmission in which the rotation direction of the input / output shaft is reversed, so that the continuously variable transmission can be installed coaxially with the unit input shaft. The output shaft can be arranged, and the unit output shaft directly meshes with the final gear that drives the differential gear coupled to the drive shaft through the transmission output gear. Since it is not necessary to provide a counter gear between the final gear and the final gear, the number of shafts of the entire transmission can be changed from the five-shaft configuration as in the conventional example to the unit input shaft coaxial with the continuously variable transmission and the counter gear. A total of four shafts, a shaft, a unit output shaft coaxial with the planetary gear mechanism, and a drive shaft, can be configured. By reducing the number of shafts, the transmission can be made smaller and lighter, and the total number of bearings can be reduced. To improve power transmission efficiency It becomes possible.

[Brief description of drawings]

FIG. 1 is a conceptual diagram of an infinitely variable transmission continuously variable transmission according to an embodiment of the present invention.

FIG. 2 is a graph showing the relationship between the gear ratio Ic of the continuously variable transmission and the reciprocal of the unit total gear ratio Iv including the final gear reduction ratio.

FIG. 3 is a conceptual diagram of an infinitely variable transmission continuously variable transmission according to a second embodiment.

FIG. 4 is a graph showing the relationship between the gear ratio Ic of the continuously variable transmission and the reciprocal of the unit total gear ratio Iv including the final gear reduction ratio.

FIG. 5 is a conceptual diagram of an infinitely variable transmission continuously variable transmission according to a third embodiment.

FIG. 6 is a graph showing the relationship between the gear ratio Ic of the continuously variable transmission and the reciprocal of the unit total gear ratio Iv including the final gear reduction ratio.

FIG. 7 is a conceptual diagram of an infinitely variable transmission continuously variable transmission according to a fourth embodiment.

FIG. 8 is a graph showing the relationship between the gear ratio Ic of the continuously variable transmission and the reciprocal of the unit total gear ratio Iv including the final gear reduction ratio.

FIG. 9 is a conceptual diagram of an infinitely variable transmission ratio continuously variable transmission according to a fifth embodiment.

FIG. 10 is a graph showing the relationship between the gear ratio Ic of the continuously variable transmission and the reciprocal of the unit total gear ratio Iv including the final gear reduction ratio.

FIG. 11 is a conceptual diagram showing a conventional infinitely variable transmission continuously variable transmission.

[Explanation of symbols]

 1 unit input shaft 2 continuously variable transmission 2a output gear 3 reduction gear 3a input gear 3b gear 3c reduction gear output shaft 4 continuously variable transmission output shaft 4a gear 5 planetary gear mechanism 5a sun gear 5b carrier 5c ring gear 6 unit output shaft 7 speed Machine output gear 8 Differential gear 9 Power circulation mode clutch 10 Direct coupling mode clutch 11a, 11b Drive shaft 12 Final gear 20 Power roller 21 Input disk 22 Output disk 40 Counter gear 105 Planetary gear mechanism 105a Sun gear 105b Carrier 105c Ring gear 205 Planetary gear mechanism 205a Sun gear 205b Carrier 205c Ring gear 305 Planetary gear mechanism 305a Sun gear 305b Carrier 305c Ring gear

Claims (6)

[Claims] 1. A continuously variable transmission and a speed reducer respectively connected to a unit input shaft, a sun gear connected to an output shaft of the continuously variable transmission, a carrier composed of a single pinion and connected to an output shaft of the speed reducer, A planetary gear mechanism consisting of a ring gear connected to the unit output shaft, a power circulation mode clutch interposed in the power transmission path from the unit input shaft to the carrier of the planetary gear mechanism, and an output of the continuously variable transmission. A direct coupling mode clutch interposed in the power transmission path from the shaft to the unit output shaft to selectively engage and release the power circulation mode clutch and the direct coupling mode clutch. In the machine, the power transmission path from the continuously variable transmission is supported by an output gear of the continuously variable transmission coaxial with the output shaft of the continuously variable transmission and a shaft supported in parallel with the output shaft of the continuously variable transmission. And a sun gear of the planetary gear mechanism and a first gear arranged coaxially with the sun gear of the planetary gear mechanism, and a power transmission path from the speed reducer to a unit input shaft. An infinitely variable transmission continuously variable transmission comprising an output gear that meshes with a coaxial input gear and is coaxially arranged with a carrier of a planetary gear mechanism. 2. A continuously variable transmission and a speed reducer respectively connected to the unit input shaft, a ring gear connected to the output shaft of the continuously variable transmission, a carrier composed of a single pinion and connected to the output shaft of the speed reducer, A planetary gear mechanism consisting of a sun gear connected to the unit output shaft, a power circulation mode clutch interposed in the power transmission path from the unit input shaft to the carrier of the planetary gear mechanism, and an output of the continuously variable transmission. A direct coupling mode clutch interposed in the power transmission path from the shaft to the unit output shaft to selectively engage and release the power circulation mode clutch and the direct coupling mode clutch. In the machine, the power transmission path from the continuously variable transmission is supported by an output gear of the continuously variable transmission coaxial with the output shaft of the continuously variable transmission and a shaft supported in parallel with the output shaft of the continuously variable transmission. And a first gear arranged coaxially with the ring gear of the planetary gear mechanism, while the power transmission path from the speed reducer is connected to the unit input shaft. An infinitely variable transmission continuously variable transmission comprising an output gear that meshes with a coaxial input gear and is coaxially arranged with a carrier of a planetary gear mechanism. 3. A continuously variable transmission and a speed reducer respectively connected to the unit input shaft, a sun gear connected to the output shaft of the continuously variable transmission, a ring gear connected to the output shaft of the speed reducer, and a unit output shaft. A planetary gear mechanism including a carrier, a power circulation mode clutch interposed in the power transmission path from the unit input shaft to the ring gear of the planetary gear mechanism, and an output shaft of the continuously variable transmission from the unit output shaft of the continuously variable transmission. A planetary gear in a continuously variable transmission having an infinite transmission ratio capable of selectively engaging and disengaging the power circulation mode clutch and the direct connection mode clutch, including a direct connection mode clutch interposed in the middle of a power transmission path. The mechanism carrier is configured by a double pinion, and the power transmission path from the continuously variable transmission is a continuously variable transmission output gear coaxial with the output shaft of the continuously variable transmission, While being meshed with a counter gear axially supported in parallel with the output shaft of the continuously variable transmission, the sun gear of the planetary gear mechanism and a first gear arranged coaxially with the sun gear are provided. The power transmission path from the speed reducer meshes with an input gear that is coaxial with the unit input shaft, and comprises a ring gear of the planetary gear mechanism and an output gear that is coaxially arranged. Infinity continuously variable transmission. 4. A continuously variable transmission and a speed reducer respectively connected to the unit input shaft, a carrier connected to the output shaft of the continuously variable transmission, a ring gear connected to the output shaft of the speed reducer and a unit output shaft. A planetary gear mechanism composed of a sun gear, a power circulation mode clutch interposed in the power transmission path from the unit input shaft to the ring gear of the planetary gear mechanism, and an output shaft of the continuously variable transmission from the unit output shaft of the continuously variable transmission. A planetary gear in a continuously variable transmission having an infinite transmission ratio capable of selectively engaging and disengaging the power circulation mode clutch and the direct connection mode clutch, including a direct connection mode clutch interposed in the middle of a power transmission path. The mechanism carrier is configured by a double pinion, and the power transmission path from the continuously variable transmission is a continuously variable transmission output gear coaxial with the output shaft of the continuously variable transmission, While being meshed with a counter gear that is axially supported in parallel with the output shaft of the continuously variable transmission, the first gear is arranged coaxially with the carrier of the planetary gear mechanism. The power transmission path from the speed reducer meshes with an input gear coaxial with the unit input shaft, and comprises a ring gear of the planetary gear mechanism and an output gear coaxially arranged. Infinity continuously variable transmission. 5. The reduction gear ratio Ig of the reduction gear can be set by the transmission gear ratio Id of the counter gear train input from the output shaft of the continuously variable transmission to the planetary gear mechanism through the counter gear and the continuously variable transmission. 5. The gear ratio according to any one of claims 1 to 4, wherein the gear ratio is equal to or less than a product of the maximum gear ratio Ic _LOW , and is set to be equal to or less than these products and as large as possible. Infinity continuously variable transmission. 6. The continuously variable transmission comprises a toroidal type continuously variable transmission in which a rotation direction of an input / output shaft is reversed, and the unit output shaft drives a differential gear coupled to a drive shaft. The infinitely variable transmission continuously variable transmission according to any one of claims 1 to 4, further comprising a transmission output gear directly meshed with the final gear.