JP3446279B2 - Continuously variable transmission - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a continuously variable transmission, and more particularly to a first power transmission path for outputting an input torque inputted from the engine side through a torque converter and a continuously variable transmission by bypassing the torque converter. And a second power transmission path that outputs the power via a mechanism.

[0002]

2. Description of the Related Art As a continuously variable transmission mounted on an automobile or the like, for example, as disclosed in Japanese Unexamined Patent Publication No. Hei 5-26326, an engine output outputted from a torque converter is decelerated by a reduction mechanism and outputted. A first power transmission path,
There is a second power transmission path that outputs an engine output via a continuously variable transmission mechanism that bypasses the torque converter and that switches these power transmission paths according to operating conditions.

According to this, when the first power transmission path is formed, good starting performance or acceleration performance can be obtained by the torque increasing action of the torque converter.
On the other hand, when the second power transmission path is formed, taking advantage of the characteristics of the continuously variable transmission mechanism, it is possible to realize without the appropriate gear ratio in accordance with the operating state Ru cause shift shock.

[0004]

However, in the prior art, for example, the first power transmission path and the second power transmission path are switched with the maximum reduction ratio of the continuously variable transmission mechanism as a boundary. When the power transmission path is formed, the continuously variable transmission must handle all the transmission torque, which causes a problem that the continuously variable transmission becomes large.

The present invention relates to the continuously variable transmission in which the first power transmission path passing through the torque converter and the second power transmission path bypassing the torque converter and passing through the continuously variable transmission mechanism can be set. The present invention addresses the above problem and aims to make a continuously variable transmission mechanism or continuously variable transmission compact.

[0006]

That is, the invention according to claim 1 of the present application (hereinafter referred to as the first invention) is a first power transmission that outputs an input torque input from the engine side through a torque converter. a path, in a continuously variable transmission and a second power transmission path for outputting via a continuously variable transmission mechanism, bypassing the torque converter, the torque converter
The torque ratio of the motor is greater than the maximum reduction ratio of the continuously variable transmission.
Together are Ku set, the a first power transmission path connecting and disconnecting means for first disconnecting the power transmission path, and a second power transmission path connecting and disconnecting means in contact also disconnects the second power transmission path, the stepless
The transmission gear ratio is the maximum reduction ratio and torque of the continuously variable transmission mechanism.
In the region between the speed ratio of the converter and the gear ratio where the speed ratio is 1, the first and second power transmission path connecting / disconnecting means so that power is transmitted through both the first and second power transmission paths. And a control means for operating the.

[0007] The invention according to claim 2 of the present application (hereinafter,
The second invention of) is between said control means in the first shot Akira, speed ratio of the continuously variable transmission, the maximum reduction ratio and the speed ratio of the torque converter of the continuously variable transmission mechanism is 1 transmission ratio in the region, when the input torque is larger than a predetermined value, the first upper SL, the first such power through both the second power transmission path is transmitted, the second power transmission path connecting and disconnecting means It is characterized in that it is configured to operate.

[0008]

According to the above structure, the following effects can be obtained.

[0009] That is, first, in either of the second invention, the transmission ratio of the continuously variable transmission, the maximum reduction ratio of the continuously variable transmission mechanism provided in the second power transmission path and a torque converter
Since the first and second power transmission paths are used together in the range between the speed ratio of the gear and the gear ratio where the transmission speed ratio is 1 , the transmission torque is shared by the torque converter on the first power transmission path side. As a result, the continuously variable transmission mechanism is made compact as a whole.

In addition, since the torque ratio of the torque converter is set to be larger than the maximum reduction ratio of the continuously variable transmission mechanism, the reduction mechanism for decelerating the output of the torque converter is not required and the continuously variable transmission is not required. The axial size of the machine is reduced, and the transmission efficiency when using the second power transmission path is improved.

[0011] According to the second invention, the first when the input torque is large, so that the combination of the second power transmission path, particularly deterioration reliably avoid the transmission efficiency in a low speed ratio side Will be done.

[0012]

Embodiments of the present invention will be described below with reference to the drawings.

As shown in FIG . 1, an continuously variable transmission 2 according to the first embodiment is connected to an engine 1 which constitutes a power train of the automobile. The continuously variable transmission 2 includes a torque converter 3 connected to an output shaft 1a of an engine 1.
And a pair of toroidal type continuously variable transmission mechanisms 4 having a similar structure to the rear of the torque converter 3.
A continuously variable transmission 4 having a and 4b is arranged. At the rear of the continuously variable transmission 4, the torque converter 3 or the power that has bypassed the torque converter 3 and that has passed through the continuously variable transmission mechanisms 4a and 4b, or the power that has passed through both of the forward and reverse movements is reversed. The switching device 5 is arranged, and the power output from the forward / reverse switching device 5 is transmitted to the drive wheels (not shown) via the output shaft 6.

[0014] The torque converter 3 comprises a casing 3a integral with the pump 3b connected to an output shaft of the engine 1
And a turbine 3c which is arranged to face the pump 3b and is driven by the pump 3b via hydraulic oil, and a pair of stators 3d, 3d which are arranged between the turbine 3c and the pump 3b. The turbine shaft 3e that rotates integrally with the turbine 3c has a first clutch 61 for forming a first power transmission path on an intermediate shaft 7 arranged on the same axis.
Are connected via. Further, the front end side of the hollow shaft 3f fitted onto the turbine shaft 3e is connected to the stators 3d and 3d via the one-way clutches 3g and 3g.
And the rear end side of the hollow shaft 3f is integrated with the transmission casing 8. further,
Pump shaft 3h fitted onto the hollow shaft 3f
Has a front end side connected to the casing 3a and an oil pump 9 provided at an intermediate portion thereof. A second clutch 62 for forming a second power transmission path is provided between the rear end side of the pump shaft 3h and the output gear 81 loosely fitted to the hollow shaft 3f.

Meanwhile, a pair of continuously variable transmission mechanism 4a in the continuously variable transmission 4, 4b is input disc 4, each provided rotatably relative to the shaft 7 on the intermediate shaft 7
c, 4c, and output disks 4d, 4d that are arranged to face the input disks 4c, 4c and rotate integrally with the intermediate shaft 7,
Between the output discs 4d, 4d and the input discs 4c, 4c, there are provided a pair of power rollers 4e ... 4e which are rotatably and tiltably arranged in contact with both discs.

[0016] Then, the both continuously variable transmission mechanism 4a, the input disks 4c in 4b, is between 4c, these input disks 4c, with an intermediate disk 4f which is rotatable relative to 4c are arranged A plurality of loading cams 4g ... 4g are respectively interposed between the intermediate disc 4f and the input discs 4c, 4c. These loading cams 4g ... 4g are used for the input disk 4
As the input torque input to c, 4c increases, the pressing force of each cam 4g ... 4g on each input disk 4c, 4c increases.

Furthermore, the intermediate disk 4f through each input disc 4c, the power transmission shaft 10 for inputting the output of the engine 1 to 4c are arranged in parallel to the intermediate shaft 7. The first provided on the front end side of the power transmission shaft 10.
An output gear 81 loosely fitted to the hollow shaft 3f is meshed with the gear 82 via an intermediate gear 83, and the second gear 8 provided on the rear end side of the transmission shaft 10 is connected to the gear 82.
4 is an input gear 8 provided on the intermediate disc 4f.
5 is meshed. Therefore, the second clutch 6
When 2 is engaged, the engine output bypassing the torque converter 3 is input to the input disks 4c, 4c of the continuously variable transmission mechanisms 4a, 4b in the continuously variable transmission 4 via the power transmission shaft 10, respectively. And as shown in the figure
The rotations of the input disks 4c, 4c are speed-changed and transmitted to the output disks 4d, 4d at a predetermined gear ratio according to the tilt angle of each power roller 4e ... 4e.

[0018] Here, the torque converter 3, the torque ratio is the continuously variable transmission 4 (continuously variable transmission mechanism 4a, 4
It is configured to be larger than the maximum reduction ratio of b).

The forward / reverse switching device 5 has a double pinion type planetary gear mechanism 5a, and a sun gear 5b connected to the rear end of the intermediate shaft 7 has an inner pinion 5c.
, And a carrier 5e for fixedly supporting the inner pinion 5c and the outer pinion 5d is connected to the output shaft 6 arranged on the same axis as the intermediate shaft 7. A ring gear 5f meshed with the outer pinion 5d is attached to the output shaft 6 by a third clutch 63.
Are connected via. Furthermore, this ring gear 5f
Are connected to the transmission casing 8 via brakes 64. Therefore, the brake 64 is released and the third
When the clutch 63 is engaged, the rotation transmitted to the intermediate shaft 7 is transmitted to the output shaft 6 as it is, and the output shaft 6 is rotationally driven in the forward direction. Further, when the brake 64 is engaged and the third clutch 63 is released, the rotation transmitted to the intermediate shaft 7 is reversely transmitted to the output shaft 6 and the output shaft 6 is rotationally driven in the reverse direction. become.

[0020] Next, referring to FIG. 2, each of the clutch 61 to
A control system for controlling the operation of the brake 63 and the brake 64 will be described.

[0021] That is, the from the hydraulic control valve unit 110 provided in the continuously variable transmission 2 are respectively operating pressure lines 111 to 114 is led to the first to third clutches 61 to 63 and brake 64, these The first to third clutches 6 are provided on the operating pressure lines 111 to 114.
1-63 and the brake 64, the 1st-4th ON-OFF solenoid valve 121 which switches supply / discharge of the operating pressure is carried out.
~ 124 are installed. These ON-OFF solenoid valves 121 to 124 are ON / OFF controlled by receiving a control signal from the controller 130. In that case, for example, the first ON-OFF solenoid valve 121
When is turned on, the operating pressure is supplied to the actuator of the first clutch 61, and accordingly, the first clutch 6
1 concludes. Then, when the first ON-OFF solenoid valve 121 is turned off, the operating pressure is exhausted and the first clutch 61 is released. The second to third ON / OFF solenoid valves 1 are also used for the second and third clutches 62 and 63 and the brake 64.
When 22 to 124 are turned on, they are fastened.

[0022] Here, the controller 130, signals from the shift position sensor 131 for detecting the position of a shift lever operated by a driver, a signal from an engine speed sensor 132 for detecting an engine speed, turbine speed A signal from a turbine rotation sensor 133 for detecting the above, a signal from a throttle sensor 134 for detecting a throttle opening representing the input torque of the continuously variable transmission 2, and the like are input. And the controller 1
30 indicates the first to fourth ON- based on these signals.
OFF solenoid valves 121-124 are turned on and off
By doing so, the engagement states of the first to third clutches 61 to 63 and the brake 64 are controlled.

[0023] That is, the controller 130, when the signal from the shift position sensor 131 indicates the reverse position, the first, second 4ON-OFF solenoid valves 121,
Turn on 124. Therefore, the second clutch 62 is released, the first clutch 61 is engaged, and
The brake 64 in the forward / reverse switching device 5 is engaged. As a result, the first power transmission path passing through the torque converter 3 is formed, and the rotation transmitted from the turbine shaft 3e to the intermediate shaft 7 via the first clutch 61 is reversed and transmitted to the output shaft 6. Then, the output shaft 6 is rotationally driven in the reverse direction.

When the signal from the shift position sensor 131 indicates the neutral position, the controller 130 has the first to fourth ON-OFF solenoid valves 121 to 121.
All 124 are turned off. Therefore, all of the first to third clutches 61 to 63 and the brake 64 are released.

It should be noted, may be entered into the third clutch 63 only the 3ON-OFF solenoid valve 121 as ON. In this case, since the first and second clutches 61 and 62 on the upstream side of the power transmission path are both released, the power is not transmitted to the output shaft 6.

[0026] Then, the controller 130, when the signal from the shift position sensor 131 indicates the forward position,
According to the flowchart shown in FIG. 3, the first to fourth ONs are performed.
-OFF solenoid valves 121-124 are turned on and off
By performing F, the first to third clutches 61 to 63
And the operation of the brake 64 is controlled as follows.

[0027] That is, the controller 130, on reading the various signals in Step S1, the speed ratio of the torque converter 3 based on the engine speed and the turbine speed at step S2 e (= engine speed / turbine speed
Then , in step S3, it is determined whether or not this speed ratio e is larger than the maximum reduction ratio α of the continuously variable transmission 4 (continuously variable transmission mechanism 4a, 4b).

When the controller 130 determines that the speed ratio e is larger than the maximum speed reduction ratio α, the controller 130 proceeds to step S4 and turns the first to fourth ON-OFF solenoid valves 121 to 124 ON, OFF, ON, OFF. And Therefore, the second clutch 62 is released, the first clutch 61 is engaged, and the forward / reverse switching device 5 is engaged.
The third clutch 63 in is engaged. This allows
A first power transmission path passing through the torque converter 3 is formed, and the rotation transmitted from the turbine shaft 3e to the intermediate shaft 7 via the first clutch 61 is directly transmitted to the output shaft 6, The output shaft 6 is rotationally driven in the forward direction.

The controller 130 uses the above step S3.
When it is determined that the speed ratio e is smaller than the maximum speed reduction ratio α, the process proceeds to step S5 and it is determined whether the throttle opening θ is larger than a predetermined value β. That is,
It is determined whether or not the input torque of the continuously variable transmission 2 is large. When it is determined that the throttle opening θ is not larger than the predetermined value, the process proceeds to step S6 and the first
~ Fourth ON-OFF solenoid valves 121 to 124
Are OFF, ON, ON, and OFF, respectively. Therefore, while the first clutch 61 is released, the second clutch 62 is engaged. As a result, the second power transmission path that bypasses the torque converter 3 is formed, and the output torque of the engine 1 is input to the continuously variable transmission mechanisms 4a and 4b in the continuously variable transmission 4. .

[0030] Thus, in the case the input torque of the CVT 2 is small, as shown in FIG. 4, the gear ratio of the continuously variable transmission 2 is larger than α the maximum reduction ratio of the continuously variable transmission 4 <br /> during have, together with the first power transmission path via the torque converter 3 is used alone, the gear ratio of the continuously variable transmission 2 is bypassed and Kunar smaller than the maximum reduction ratio alpha, the torque converter 3 Thus, the second power transmission path via the continuously variable transmission mechanism 4a, 4b in the continuously variable transmission 4 is used alone.

Returning to step S5 of the flowchart of FIG . 3, when the controller 130 determines that the throttle opening θ of the engine 1 is larger than the predetermined value β, step S7 is executed and the speed ratio e of the torque converter 3 is set to 1 Is greater than. When the speed ratio e is larger than 1, step S8 is executed to turn on the first to fourth ONs.
-OFF The solenoid valves 121 to 124 are turned on, on, on, and off, respectively. Therefore, the first,
Since the second clutches 61 and 62 are engaged together, the continuously variable transmission 4 bypasses the first power transmission path passing through the torque converter 3 and the torque converter 3.
Both of the second power transmission paths passing through the continuously variable transmission mechanisms 4a and 4b in FIG.

On the other hand, the controller 130, when it is determined that the speed ratio e of the torque converter 3 in step S7 is not greater than 1 executes step S6, first to 4ON-OFF solenoid valve 121 to
124 is set to OFF, ON, ON, and OFF, respectively. Therefore, while the first clutch 61 is released, the second clutch 62 is engaged, bypassing the torque converter 3 and passing through the continuously variable transmission mechanisms 4a and 4b in the continuously variable transmission 4. Two power transmission paths will be formed.

In this way, when the input torque of the continuously variable transmission 2 is large, as shown in FIG. 5, the gear ratio of the continuously variable transmission 2 is larger than the maximum reduction ratio α of the continuously variable transmission 4. At this time, the first power transmission path via the torque converter 3 is used alone, and the speed ratio is smaller than the direct connection state (speed ratio = 1) corresponding to 1 of the speed ratio e.
When Ru kuna, so that the continuously variable transmission mechanism 4a to bypass the torque converter 3, the second power transmission path through 4b is used alone.

In the region where the gear ratio of the continuously variable transmission 2 is between the maximum reduction ratio α and 1 described above, the first and second power transmission paths are used together. As a result, the excessive input torque is also shared by the torque converter 3 side, and the holding torque of the continuously variable transmission 4 or the continuously variable transmission mechanisms 4a and 4b is reduced by that amount, so that the continuously variable transmission is performed. The device 4 can be made compact as a whole.

[0035] In particular, as in the embodiment, the continuously variable transmission mechanism 4a the torque ratio of the torque converter 3, by setting larger than the maximum reduction ratio 4b, the speed reduction mechanism for decelerating the output of the torque converter 3 It becomes unnecessary and the dimension of the continuously variable transmission 2 in the axial direction is shortened. Moreover, since the reduction mechanism is not provided, when the second power transmission path is used, mechanical loss due to idling of the reduction mechanism in conjunction with the torque converter 3 is prevented, and transmission efficiency is improved. It will also be done.

Next, referring to FIG. 6, a description will be given of a second embodiment of the merits.

The continuously variable transmission 20 according to the second embodiment is
Similar to the first embodiment, the torque converter 23 is connected to the output shaft 1a of the engine 1, and a pair of toroidal type continuously variable transmission mechanisms 34a having a similar structure is provided behind the torque converter 23. , 34b is arranged. Then, behind the continuously variable transmission 24, the torque converter 23 or the power that has bypassed the torque converter 23 and that has passed through the continuously variable transmission mechanisms 4a and 4b, or the power that has passed through both of the forward and reverse movements, is moved forward and backward. The switching device 25 is arranged, and the power output from the forward / reverse switching device 25 is transmitted to drive wheels (not shown) via the output shaft 11.

[0038] The torque converter 23, engine 1
A pump 23b that is integral with a casing 23a that is connected to the output shaft 1a of the turbine, and a turbine 2 that is disposed facing the pump 23b and that is driven by hydraulic oil by the pump 23b.
3c, a pair of stators 23d, 23d arranged in series between the turbine 23c and the pump 23b, and the input shaft 12 for transmitting power to a continuously variable transmission 24 described later is the turbine 23c. Is disposed so as to pass through a hollow turbine shaft 23e that rotates integrally with the first shaft between the output gear 86 loosely fitted to the input shaft 12 and the rear end side of the turbine shaft 23e. A first clutch 65 that forms a power transmission path is provided.

Further, the turbine shaft 23e to fitted on the hollow shaft 23f of the front side one-way clutch 23g, the stator 23d through 23g, 23d
And the rear end side of this hollow shaft 23f is integrated with the transmission casing 8. Further, the pump shaft 23h externally fitted to the hollow shaft 23f is connected to the casing 23a at its front end side, and the oil pump 9 is provided at its rear end portion. A second clutch 66 for forming a second power path is disposed in contact with the casing 23a, and the front end side of the input shaft 12 is connected to the second clutch 66.

Further , in this embodiment, the continuously variable transmission 24 is constructed as follows. That is,
The input disks 24c, 24 constituting a pair of continuously variable transmission mechanisms 34a, 34b provided in the continuously variable transmission 24.
c is rotatably provided on the input shaft 12 with respect to the input shaft 12, and these input disks 24c,
Integrated output disks 24d, 2 disposed opposite to each other between 4c
4d is rotatably supported by a hollow connecting shaft 24e that connects both input disks 24c, 24c. A pair of power rollers 24f are provided between the output disks 24d and 24d and the input disks 24c and 24c.
... 24f is arranged so as to be rotatable and tiltable while being in contact with both disks.

[0041] Further, the both continuously variable transmission mechanism 34a, 34
On the outside of each input disk 24c, 24c in b,
End disks 24g, 24g, which are rotatable relative to the input disks 24c, 24c, are arranged, respectively, and the end disks 24g, 2
A plurality of loading cams 24h ... 24h are respectively interposed between 4g and each input disk 24c, 24c. The end disks 24g, 24g are connected to the input shaft 12, respectively.

Further, the power transmission shaft 13 which constitutes a part of the second power transmission path, is arranged parallel to the said input shaft 12. The first gear 87 provided on the front end side of the power transmission shaft 13 is meshed with the output gear 86 loosely fitted to the input shaft 12 and is provided on the rear end side of the transmission shaft 13. The second gear 88 meshes with a third gear 89 provided on the front end side of the intermediate shaft 14 on the same axis as the input shaft 12. The output disc 24 is attached to the fourth gear 90 provided in the middle portion of the power transmission shaft 13.
A second output gear 91 formed on the outer peripheral portions of d and 24d is meshed and coupled via an intermediate gear 92.

[0043] Thus, the when the first clutch 65 is fastened, the engine output bypassing the torque converter 23, the continuously variable transmission mechanism 34a in the continuously variable transmission 24 via the input shaft 12, 34b of the The rotations of the input disks 24c, 24c are input to the input disks 24c, 24c, respectively, and the rotations of the input disks 24c, 24c are speed-changed and transmitted to the output disks 24d, 24d at a predetermined gear ratio according to the tilt angle of each power roller 24f. Become. The output rotation transmitted to the output disks 24d, 24d is transmitted to the power transmission shaft 13 via the second output gear 91 and the forward / reverse switching device via the second and third gears 88, 89. 25 will be input.

[0044] Also in this embodiment, the torque converter 23, the torque ratio is the continuously variable transmission 2
4 (continuously variable transmission mechanism 34a, 34b) is configured to be larger than the maximum reduction ratio.

The forward / reverse switching device 25 has the same structure as that of the first embodiment. Therefore, the third
When the clutch 67 is engaged and the brake 68 is released, the rotation transmitted to the intermediate shaft 14 is directly output to the output shaft 11
The output shaft 11 is rotationally driven in the forward direction. Further, if the third clutch 67 is released and the brake 68 is engaged, the rotation transmitted to the intermediate shaft 14 is reversed and transmitted to the output shaft 11,
The output shaft 11 is rotationally driven in the reverse direction.

[0046] Also in this embodiment, the first to third clutches 65 to 67 and brake 68 are controlled in the same manner as the first embodiment.

[0047] That is, in the case the input torque of the continuously variable transmission 20 is large, as shown in FIG. 5 described above, the gear ratio of the continuously variable transmission 20 is larger than α the maximum reduction ratio of the continuously variable transmission 24 When it is not, the first power transmission path via the torque converter 23 is used alone, and the speed change ratio corresponds to 1 of the speed ratio e (the speed change ratio = 1).
When a that less than, the continuously variable transmission mechanism in the continuously variable transmission 24, bypassing the torque converter 23 34a, 3
The second power transmission path via 4b is used alone.

In the region where the speed ratio of the continuously variable transmission 20 is between the maximum reduction ratio α and 1 described above, the first and second power transmission paths are used together. Therefore, also in this embodiment, the excessive input torque is also shared by the torque converter 23 side, and the holding torque of the continuously variable transmission 24 or the continuously variable transmission mechanisms 34a, 34b is reduced accordingly. Therefore, the continuously variable transmission 24 can be made compact as a whole.

Further, by setting the torque ratio of the torque converter 23 to be larger than the maximum reduction ratio of the continuously variable transmission mechanisms 34a and 34b, a reduction mechanism for reducing the output of the torque converter 23 becomes unnecessary, and the continuously variable transmission mechanism is not required. The axial dimension of the transmission 20 will be reduced. Moreover, since the reduction mechanism is not provided, mechanical loss due to idling of the reduction mechanism in conjunction with the torque converter 23 is prevented when the second power transmission path is used.
It also improves the transmission efficiency.

[0050]

As described above, according to the present invention, it is possible to set the first power transmission path passing through the torque converter and the second power transmission path bypassing the torque converter and passing through the continuously variable transmission mechanism. in a continuously variable transmission that is, no
The speed ratio of the continuously variable transmission is such that the maximum reduction ratio of the continuously variable transmission mechanism provided in the second power transmission path and the speed ratio of the torque converter are
Since the first and second power transmission paths are used together in the region between the gear ratio of 1 and the transmission torque is also shared by the torque converter on the first power transmission path side. Thus, the continuously variable transmission mechanism is compact as a whole.

In addition, since the torque ratio of the torque converter is set to be larger than the maximum reduction ratio of the continuously variable transmission mechanism, the reduction mechanism for decelerating the output of the torque converter is not required, and the continuously variable transmission is not required. The axial size of the machine is reduced, and the transmission efficiency when using the second power transmission path is improved.

Further, according to the second invention, the first when the input torque is large, so that the combination of the second power transmission path, particularly deterioration reliably avoid the transmission efficiency in a low speed ratio side Will be done.

[Brief description of drawings]

FIG. 1 is a skeleton view of a power train of an automobile equipped with a continuously variable transmission according to a first embodiment.

FIG. 2 is a system diagram of a continuously variable transmission according to the first embodiment.

FIG. 3 is a flowchart showing the control operation of the controller of the first embodiment.

FIG. 4 is a diagram showing a control pattern for a gear ratio during forward traveling in a low load state.

FIG. 5 is a diagram similarly showing a control pattern for a gear ratio during forward traveling in a high load state.

FIG. 6 is a skeleton view of a power train of an automobile equipped with a continuously variable transmission according to a second embodiment.

[Explanation of symbols]

1 engine 3 Torque converter 4 continuously variable transmission 4a, 4b continuously variable transmission mechanism 130 controller 134 Throttle sensor

─────────────────────────────────────────────────── --- Continuation of the front page (56) References JP-A-5-26326 (JP, A) JP-A-1-172679 (JP, A) JP-A-53-137375 (JP, A) JP-A-62- 56661 (JP, A) JP-A-5-296316 (JP, A) JP-A-4-300449 (JP, A) JP-A-4-366051 (JP, A) (58) Fields investigated (Int.Cl. ⁷ , DB name) F16H 47/06

Claims (2)

(57) [Claims] 1. A first power transmission path for outputting an input torque input from the engine side via a torque converter, and a second power transmission path for bypassing the torque converter and outputting it via a continuously variable transmission mechanism. In a continuously variable transmission having a torque ratio of the torque converter
It is set larger than the maximum reduction ratio of the mechanism,
The first power transmission path connection / disconnection means for connecting / disconnecting the first power transmission path, the second power transmission path connection / disconnection means for similarly connecting / disconnecting the second power transmission path, and the speed ratio of the continuously variable transmission are continuously variable. The maximum reduction ratio of the speed change mechanism and the speed ratio of the torque converter are 1
And a control means for activating the first and second power transmission path connecting / disconnecting means so that power is transmitted through both the first and second power transmission paths. A continuously variable transmission characterized by being provided. 2. The control means is a gear ratio of the continuously variable transmission.
However, the maximum reduction ratio of the continuously variable transmission and the speed of the torque converter
In the range between the gear ratio where the degree ratio is 1
Is greater than a predetermined value, the first and second power transmissions
In order to transmit power via both reach paths,
First and second power transmission path connecting / disconnecting means are operated.
The continuously variable transmission according to claim 1, wherein the continuously variable transmission is provided.