JP2521298B2 - Continuously variable transmission - Google Patents

Description

TECHNICAL FIELD The present invention relates to a continuously variable transmission incorporating a belt (including chain type) continuously variable transmission, and more specifically, to the belt type continuously variable transmission. The present invention relates to a continuously variable transmission in which a torque ratio width is increased by combining a transmission device and a planetary gear mechanism.

(B) Conventional Technology Recently, due to demands such as improvement in fuel consumption rate, it has been attracting attention to use a continuously variable transmission incorporating a belt type continuously variable transmission as a transmission of an automobile.

Generally, the continuously variable transmission comprises a belt type continuously variable transmission, a fluid coupling (or an electromagnetic powder clutch), a forward / reverse switching device, a reduction gear device, and a differential gear device. The device cannot take a large torque ratio width due to restrictions on the space and the minimum radius of curvature of the belt, etc., and responds to various demands of the automobile such as fuel consumption and gear shifting performance within the range of the torque ratio width only by the continuously variable transmission. Not enough to do.

Therefore, as disclosed in Japanese Patent Laid-Open No. 60-252857, a Rabinio type forward / reverse switching planetary gear mechanism is arranged in alignment with the secondary shaft of the belt type continuously variable transmission, and each element of the planetary gear mechanism is arranged. Forwardly by connecting or locking the
A continuously variable transmission has been devised in which a gear ratio of one gear position and one reverse gear position is obtained, and the torque ratio width is increased by appropriately combining the continuously variable transmission of the continuously variable transmission with the continuously variable gear shift of the planetary gear mechanism. ing.

(C) Problems to be Solved by the Invention By the way, in the above-mentioned continuously variable transmission, the locking means for locking a predetermined element of the planetary gear mechanism is coaxial with the planetary gear mechanism, that is, coaxial with the secondary shaft of the continuously variable transmission. Are arranged in a shape. For this reason, the number of constituent elements arranged on the side of the second shaft constituted by the secondary shaft and the like increases, making it difficult to shorten the axial dimension. In particular, it is necessary to install a gear connected to the reduction gear device and the differential device at one end of the second shaft, and in order to dispose the locking means, especially the one-way clutch, on the second shaft, the gear is used as a reaction force support portion. The case must be placed in the intermediate portion of the second shaft, which leads to lengthening of the axial dimension.

Therefore, an object of the present invention is to reduce the axial dimension, particularly the axial dimension of the second shaft, in a continuously variable transmission in which a planetary gear mechanism is combined with a belt shaft continuously variable transmission to increase the torque ratio width. It is to try to realize.

(D) Means for Solving the Problems The present invention has been made in view of the above circumstances, and for example, referring to FIG. 1, the input member (60) and the input member (60) Belt continuously variable transmission (30) for continuously rotating rotation, planetary gear mechanism (20) for inputting torque from the belt continuously variable transmission (30), and output member for inputting torque from the planetary gear mechanism. (70) and
In the continuously variable transmission including: a belt type continuously variable transmission (30), a primary shaft (30b) is aligned with the input member (60) to form a first shaft (A); Secondary shaft (30)
a) and the center of the planetary gear mechanism (20) and the input portion (70a) of the output member to form a second shaft (B). The planetary gear mechanism (20) has at least first, second and third elements, and the first element (20R) is interlocked with the secondary shaft (30a) of the belt type continuously variable transmission. , The second element (20C) is interlocked with the output member (70), and the third element (20S) is interlocked with the locking means (F, B1) to rotate and stop. And the locking means (F, B1) has a fixed member and a rotating member that can be locked to the fixed member, and is arranged coaxially with the first shaft (A), and the rotating member and the third member And the input member (60) can be connected and disconnected freely via the clutch (C2), and The clutch is arranged coaxially with the first shaft (A), and the locking means is arranged on the first shaft side. At least one of F, B1) and the clutch (C) and the planetary gear mechanism (20) arranged on the second shaft side are arranged so as to share at least a part of a plane orthogonal to the axial direction. Characterize.

(E) Operation Based on the above configuration, in the (low speed) mode with the clutch (C2) disengaged, the planetary gear mechanism (20)
The third element (20S) is the transfer device (8S
It is stopped by the locking means (F or B1) via 0). In this state, the rotation of the input member (60) is appropriately changed by the belt type continuously variable transmission (30) and transmitted to the first element (20R), and the changed rotation is further changed by the planetary gear mechanism (20). For example, the second element (20
Output from C) to the output member (70).

On the other hand, in the (high-speed) mode in which the clutch (C2) is connected, the locking means (F, B1) is released,
The rotation of the input member (60) is transmitted through the clutch (C2) and the transfer device (80) to the planetary gear mechanism (20).
Of the first element (20S) while being transmitted to the third element (20S) of the
R) is transmitted. And the planetary gear mechanism (20)
At, the rotation of the third element (20S) and the rotation of the first element (20R) are combined, and the output element (70) is output from the second element (20C).
Is output to

The reference numerals shown in parentheses above are for reference to FIG. 1 and do not limit the configuration in any way.

(F) Embodiment First, the first embodiment of an automatic continuously variable transmission to which the present invention is applied
To explain its outline with reference to the figure, the automatic continuously variable transmission 12
Is a single planetary gear mechanism 20, a belt type continuously variable transmission device 30, a transfer device 80, an input shaft 60 and an output member 70 composed of a reduction gear device 71 and a differential gear device 72,
A forward / reverse rotation switching device 90 including a fluid coupling 13 having a lockup clutch CL and a dual planetary gear mechanism is provided. And the single planetary gear mechanism 20
The element 20S (or 20R) that serves as a reaction force support member when using it as a speed reduction mechanism is interlocked with the locking means F, B1 via the transfer device 80, and the input shaft via the high clutch C2. Can connect with 60.

More specifically, the ring gear of the planetary gear mechanism 20.
20R is interlocked with the output part 30a of the continuously variable transmission 30, the carrier 20C is interlocked with the output member 70, and the sun gear 20S is a locking means via the transfer device 80. Reverse brake
It is linked to B1 and high clutch C2.

In the dual planetary gear mechanism 90, the sun gear 90S is connected to the input shaft 60, the carrier 90C is connected to the input shaft 60 via the forward clutch C1, and the ring gear 90R is connected to the reverse brake B2.

Based on the above configuration, each clutch, brake and one-way clutch in the automatic continuously variable transmission 12 operate at each position as shown in FIG. It should be noted that * indicates that the lockup clutch CL can be operated appropriately.

More specifically, on the low speed side L in the D range, the low one-way clutch F is operated in addition to the connection of the forward clutch C1. In this state, the rotation of the engine crankshaft causes the lockup clutch CL or the fluid coupling 13 to rotate.
Is transmitted to the input shaft 60 via the input shaft 60, is further transmitted directly to the sun gear 90S of the dual planetary gear mechanism 90, and is transmitted to the carrier 90C via the forward clutch C1.
Therefore, the dual planetary gear mechanism 90 rotates integrally with the input shaft 60, transmits positive rotation to the primary shaft 30b of the belt type continuously variable transmission 30, and is further continuously steplessly changed by the continuously variable transmission 30. The rotation is transmitted from the secondary shaft 30a to one element of the single planetary gear mechanism 20, specifically, the ring carrier 20R. On the other hand, in this state, the reaction force supporting element that receives the reaction force, specifically, the sun gear 20S is stopped by the low one-way clutch F that is arranged coaxially with the input shaft 60 via the transfer device 80. The rotation of the ring gear 20R is decelerated rotation and the carrier 20C
And the reduction gear device 71 and the differential gear device 72.
Is transmitted to the axle shaft 73 via.

On the high-speed side H in the D range, the high clutch C2 is connected in addition to the forward clutch C1. In this state, in the same manner as described above, the forward rotation appropriately changed by the continuously variable transmission 30 is taken out from the secondary shaft 30a and input to the ring gear 20R of the single planetary gear mechanism 20. On the other hand, at the same time, the rotation of the input shaft 60 is transmitted to the sun gear 20S of the single planetary gear mechanism 20 via the high clutch C2 and the transfer device 80, whereby the torque of the ring gear 20R and the sun gear 20S is combined in the planetary gear mechanism 20. And is output from the carrier 20C. At this time, since rotation against the reaction force is transmitted to the sun gear 20S via the transfer device 80, a predetermined positive torque is transmitted via the transfer device 80 without causing torque circulation. Then, the combined torque from the carrier 20C is transmitted to the axle shaft 73 via the reduction gear device 71 and the differential gear device 72.

In the operation in the D range, the reverse torque is applied (when the engine is braked) based on the one-way clutch F (when the engine is braked). However, in the S range, the low cost & reverse brake B1 operates in addition to the low one-way clutch F, and Power is transmitted even when torque is applied.

Further, in the R range, the reverse brake B2 operates together with the low coast & reverse brake B1. In this state, the rotation of the input shaft 60 is input to the belt type continuously variable transmission 30 as reverse rotation from the carrier 90C because the ring gear 90R is fixed by the dual planetary gear mechanism 90. On the other hand, the sun gear of the single planetary gear mechanism 20 based on the operation of the low coast & reverse brake B1.
Since 20S is fixed, the reverse rotation from the continuously variable transmission 30 is reduced by the planetary gear mechanism 20, and the output member 70
Taken out.

In the P range and the N range, the low coast & reverse brake B1 operates.

Next, one embodiment of the present invention will be described with reference to FIG.

The automatic continuously variable transmission 12 has a transmission case 15 composed of three divisions, and an input shaft 60 of the case 15 and a primary shaft 30b of a belt type continuously variable transmission 30 are coaxially and rotatably supported. And the secondary shaft of the belt type continuously variable transmission 30
30a and the gear shaft 70a are coaxially and rotatably supported to form a second shaft B. Further, a control unit 40 including a fluid coupling 13 having a lockup clutch CL coaxially with the first axis A, a forward clutch C1, a high clutch C2, a low coast & reverse brake B1, a reverse brake B2, and a low one-way clutch F. A dual planetary gear mechanism 90, which constitutes a forward / reverse rotation switching device, and a hydraulic pump 17 are provided, and a single planetary gear mechanism 20 is provided coaxially with the second axis B.

Further describing the control unit 40 and the input portion, the input shaft 60 has the lockup clutch CL and the output member of the fluid coupling 13 engaged at one end thereof, and the sun gear 90S of the dual planetary gear mechanism 90 engaged at the other end thereof. In addition, a sleeve portion 15a fixed to the case 15 is disposed on the input shaft 60. Also, the sleeve portion 15a
, A sprocket 81 is connected via a one-way clutch F, and a sleeve shaft 41 connected to the input shaft 60 is rotatably supported. Further, the sleeve shaft
A forward clutch C1 is installed with its hydraulic actuator 42 on one side of the flange 41a rising from 41, and a high clutch C2 is installed with its hydraulic actuator 43 on the other side. The driven side of the high clutch C2 is connected to a boss of the sprocket 81, and the boss is connected to a low coast and reverse brake B1 disposed in the case 15 together with the hydraulic actuator 45. On the other hand, the forward clutch C1
The driven side of the carrier 90 of the dual planetary gear mechanism 90
It is connected to C and has dual planetary gear mechanism 90.
Ring gear 90R of Case 1 with hydraulic actuator 46
It engages with the reverse brake B2 arranged at 5. The carrier 90C supports the pinion 90P1 meshing with each other and the sun gear 90S, and the pinion 90P2 meshing with the ring gear 90R.

The belt type continuously variable transmission 30 is a primary pulley.
31, a secondary pulley 32, and a belt 33 wound around these pulleys, and both pulleys are fixed sheaves 31a, 32a and movable sheaves 31b, 32b, respectively. Further, the primary pulley 31 is provided between a thrust holding member 34a and a fixed sheave 31a which are supported by bearings and are connected to the primary shaft 30b so as to rotate integrally with each other through a plurality of disc springs 38. , A pressure adjusting cam mechanism 34 for applying an axial force corresponding to the transmission torque is arranged, and the movable sheave 31b is supported by the boss portion 31c of the fixed sheave 31a only by sliding through a ball spline. At the same time, a ball screw device 35 is arranged on the back of the device. The ball screw device 35 has its bolt portion 35a non-rotatably connected to the case 15 and axially immovable to the primary shaft 30b via a thrust bearing, and its nut portion 35.
b is connected to the movable sheave 31b via a thrust bearing so as to move integrally in the axial direction. On the other hand, in the secondary pulley 32, the fixed sheave 32a is rotatably supported by the case 15 integrally with the secondary shaft 30a,
Moreover, the movable sheave 32b is slidably supported by the secondary shaft 30a via a ball spline. Further, a ball screw device 36 is arranged on the back surface of the movable sheave 32b, and a bolt portion 36a of the ball screw device 36 is non-rotatably attached to the case 15 and a flange 30d fixed to the secondary shaft 30a.
Is axially immovably connected to the movable sheave 32b via a thrust bearing so as to move integrally with the movable sheave 32b in the axial direction. An operation shaft 37 is rotatably supported between the primary pulley 31 and the secondary pulley 32. Incidentally, since FIG. 3 is a developed view, the operating shaft 37 is drawn upward, but in actuality, the operating shaft 37 is located at an intermediate portion between the primary shaft 30b and the secondary shaft 30a in a front view. The operation shaft 37 has a circular gear 37a.
And a non-circular gear 37b and a worm wheel 37c are fixed, and the wheel 37c is connected to an electric motor controlled by an electric signal from the control unit.
37d meshes. Further, the circular gear 37a meshes with the wide circular gear 35c fixed to the nut portion 35b on the primary pulley 31 side, and the non-circular gear 37b extends to the wide circular gear 35b fixed to the nut portion 36b on the secondary pulley 32 side. Meshes with the non-circular gear 36c.

Further, the single planetary gear mechanism 20 is disposed on the gear 70a that constitutes the second shaft B, and the ring gear 2
0R is connected to the secondary shaft 30a of the belt type continuously variable transmission 30 adjacent to the flange 30d. Further, a sprocket 82 is rotatably supported integrally with a sun gear 20S on a gear shaft 70a that is a central shaft of the planetary gear mechanism 20, and a carrier that rotatably supports a pinion 20P on the gear shaft 70a. 20C is fixed.

On the other hand, between the sprocket 82 integrated with the sun gear 20S on the second shaft B and the sprocket 81 supported by the low one-way clutch F arranged on the sleeve portion 15a coaxial with the first shaft A. Is wrapped around a silent chain 83, and the sprocket and chain form a transfer device 80.

The gear shaft 70a integrally forms a gear 71a to form an output member 70, and the gear 71a is engaged with a gear 71c fixed to an intermediate shaft 71b. Further, a small gear 71d is formed on the intermediate shaft 71b, and the gear 71d meshes with a ring gear 72a fixed to the differential gear device 72,
It constitutes the speed reducer 71. Left and right front axle shafts 73 extend from the differential gear unit 72.

 Next, the operation of this embodiment will be described.

The rotation of the engine crankshaft is the lockup clutch CL
Alternatively, it is transmitted to the input shaft 60 via the fluid coupling 13, further transmitted to the sun gear 90S of the dual planetary gear mechanism 90, and further transmitted to the sleeve shaft 41. In the D range and the S range, since the forward clutch C1 is connected and the reverse brake B2 is released, the dual planetary gear mechanism 90 causes the sun gear 90S and the carrier 90C to integrally rotate, and the ring gear 90R also integrally rotates. It is transmitted to the primary shaft 30b of the belt type continuously variable transmission 30.

The rotation of the primary shaft 30b is transmitted to the pressure adjusting cam mechanism 34 via the thrust holding member 34a, and further transmitted to the movable sheave 31b via the fixed sheave 31a of the primary pulley 31 and the ball spline. At this time, in the pressure adjusting cam mechanism 34, an axial force corresponding to the input torque acting on the input shaft 30b acts on the back surface of the sheave 31a via the disc spring 38,
On the other hand, the other sheave 31b is in a state in which the ball screw device 35 is fixed in the longitudinal direction corresponding to the predetermined gear ratio, and therefore an equivalent reaction force acts on the back surface of the sheave 31b via the thrust bearing, Thus, the primary pulley 31 holds the belt 33 with a holding force corresponding to the input torque.
Further, the rotation of the belt 33 is transmitted to the secondary pulley 32 and further to the secondary shaft 30a. Also,
When the belt is transmitted, the motor is controlled based on signals from sensors such as throttle opening and vehicle speed, and the operating shaft 37 is rotated via the worm 37d and the worm wheel 37c. Then, the nut portion 35b of the ball screw device 35 on the primary pulley 31 side rotates via the circular gears 37a and 35c, and the nut portion 36b of the ball screw device 36 on the secondary pulley 32 side rotates via the non-circular gears 37b and 36c.
As a result, the bolt portion 35 that is prevented from rotating in the case 15
The nut portions 36a, 36b rotate relative to the a, 36a, and the ball screw devices 35, 36 move the movable sheaves 31b, 32b via the thrust bearings so that the primary pulley 31 and the secondary pulley 32 have a predetermined effective diameter. It is set and the set torque ratio is obtained. At this time, since both ball screw devices move linearly, a difference occurs with the original moving amount of the movable sheave defined by the belt 33, but since the secondary pulley 32 side rotates via the non-circular gears 37b, 36c. , The movable sheave is moved by an amount that matches the original amount of movement. Further, the belt clamping pressure by both sheaves 31a, 31b and 32a, 32b acts to pull the primary shaft 30b via the thrust bearing on the primary pulley 31 side, and the case 1
Similarly, the secondary shaft 32a does not act on the secondary pulley 32 side and does not act on the case 15 without acting on the case 5.

Further, the secondary shaft of the belt type continuously variable transmission 30
The rotation of 30a is transmitted to the ring gear 20R of the single planetary gear mechanism 20, and further via the carrier 20C to the gear shaft 70a.
Is transmitted to

In the low range L in the D range, the low one-way clutch F is in an operating state as shown in FIG. 2, and therefore, when the torque is transmitted from the ring gear 20R to the carrier 20C, the sun gear 20S receives a reaction force. The sun gear 20S is prevented from rotating by a low one-way clutch F arranged in the sleeve portion 15a on the first axis A via the transfer device 80, and the single planetary gear mechanism 20
Constitutes a reduction mechanism. Therefore, the rotation of the secondary shaft 30a of the belt type continuously variable transmission 30 is simply decelerated by the single planetary gear mechanism 20, and further the gears 71a, 71
The speed is further reduced through the reduction gear device 71 including the intermediate shaft 71b, the gear 71d and the mount gear 72a, and then transmitted to the left and right front axle shafts 73 through the differential gear device 72.

Also, when the throttle opening and vehicle speed reach a predetermined value,
The high clutch C2 is connected by a signal from the control unit and is switched to the high speed side. Then, the rotation of the input shaft 60 is transmitted to the belt-type continuously variable transmission 30 and the sleeve shaft
It is transmitted to the sprocket 81 via 41 and the high clutch C2, and further transmitted to the sun gear 20S of the single planetary gear mechanism 20 via the silent chain 83 and the sprocket 82. At this time, since the sprocket 81 on the input side of the transfer device 80 was receiving the reaction force from the sun gear 20S of the single planetary gear mechanism by the low one-way clutch F, the shift shock due to the grip change was prevented, and the high clutch C2 was connected. The rotation starts smoothly and torque is transmitted to the sun gear 20S. Thus, the torque continuously changed by the belt type continuously variable transmission 30 and the torque via the transfer device 80 are combined by the single planetary gear mechanism 20, and the combined torque is generated by the carrier 20.
It is transmitted from C to the gear shaft 70a. Further, similarly to the low speed side, it is transmitted to the left and right front axle shafts 73 via the reduction gear device 71 and the differential gear device 72.

Further, on the low speed side L in the S range, a negative torque due to the engine brake or the like is also received, so that the low coast & reverse brake B1 arranged coaxially with the first axis A engages and the sprocket 81 rotates in both forward and reverse directions. Be blocked. The high-speed side H in the S range is the same as the high-speed side in the D range.

On the other hand, in the R range, the forward clutch C1 is released and the reverse brake B2 is engaged. Therefore, the rotation of the input shaft 60 transmitted to the sun gear 90S of the dual planetary gear mechanism 90 is transmitted as reverse rotation from the carrier 90C to the primary shaft 30b of the belt type continuously variable transmission 30 when the ring gear 90R is stopped. At this time, the reaction torque from the sun gear 20S of the single planetary gear mechanism 20 acts on the sprocket 81 as a reverse rotation via the transfer device 80, so the low coast & reverse brake is applied.
B1 operates to stop the sprocket 81.

In the torque transmission of the continuously variable transmission 12 described above, the fourth
As shown in the figure, on the low speed side L, all the transmission torque is transmitted through the belt type continuously variable transmission 30, but on the high speed side H
In this case, the torque passing through the belt type continuously variable transmission device 30 and the torque passing through the transfer device 80 are shared at a predetermined ratio according to the torque ratio.

Further, as shown in FIG. 5, the torque ratio of the continuously variable transmission 12 to the torque ratio of the belt type continuously variable transmission 30 is L on the low speed side.
The curve L'indicates a curve L ', and the curve H'in a high speed side. Therefore, the step ratio (low speed side torque ratio / high speed side torque ratio) when stepping from the low speed side L to the high speed side H (or vice versa) is shown by the curve S. In addition, from the low speed side L (L ') to the high speed side H
When stepping to (H ') (or vice versa), as shown by the chain line A, the torque ratio of the belt type continuously variable transmission 30 may be changed without changing the torque ratio, and only by connecting the high clutch C2. Also, as indicated by the chain line B, the torque ratio of the belt type continuously variable transmission 30 is set to a predetermined amount by a signal from the control unit at the same time as the high clutch C2 is connected so that the torque ratio of the continuously variable transmission 12 is not changed. It may be operated so as to be higher so that there is no shift shock, and further, it may be controlled so as to pass through an arbitrary line in the middle portion between the chain lines A and B.

Next, various modifications of the present invention will be described with reference to FIGS. 6 to 12. The same parts as those in FIGS. 1 and 3 are designated by the same reference numerals and the description thereof will be omitted.

FIG. 6 shows a single planetary gear mechanism 20.
Connects the sun gear 20S to the secondary shaft 30a of the belt type continuously variable transmission 30 and connects the ring gear 20R to the gear 8
A transfer which is connected to the input shaft 60 by a high clutch C2 via a transfer device 80 composed of 3'and is prevented from rotating by a low one-way clutch F or a low coast & reverse brake B1 arranged on the first shaft A. It is connected to the input unit 81.

Since the step ratio of the low speed side L and the high speed side is increased in the present embodiment, the torque ratio width of the continuously variable transmission 12 can be increased and the torque acting on the belt type continuously variable transmission 30 can be increased. Can be reduced.

In FIG. 7, the forward and reverse switching means, that is, the dual planetary gear mechanism 90 and the forward clutch C1 are arranged on one side of the belt type continuously variable transmission 30 on the first axis A,
Low speed switching means on the other side, namely high clutch C2, low coast & reverse brake B1, low one-way clutch F
Has been arranged.

In FIG. 8, the forward / reverse switching means 90, the forward clutch C1, and the reverse brake B2 are arranged on the side of the second shaft B and on the opposite side of the single planetary gear mechanism 20 to the belt type continuously variable transmission 30. And also high clutch
C ₂ , low coast & reverse brake B 1 and low one-way clutch F are arranged on the side of the first shaft A.

Similar to that shown in FIG. 6, in FIG. 9, the secondary shout 30a of the belt type continuously variable transmission 30 is connected to the sun gear 20S of the single planetary gear mechanism 20, and the ring 20R is connected to the transfer device 80. However, the transfer device 80 includes a chain 83.

The one shown in FIG. 10 has two sun gears 21S1 and 21S in which the low / high speed switching means and the forward / reverse switching means are integrally formed.
2 and one sun gear 21S1 is connected to the secondary shaft 30a of the belt type continuously variable transmission 30 and the other sun gear 21S2 is connected to the transfer device 80, and two pinions 21P1 and 21P2 are connected in parallel to the carrier 21C. Support,
Further, a forward brake B3, which consists of a Ravigneaux type planetary gear mechanism 21 consisting of one ring gear 21R, and which releases in the R range, is installed.

Therefore, at the low speed side L, the belt type continuously variable transmission 30
Rotation of the secondary shaft 30a of the first sun gear 21S1
From the long pinion, the first pinion 21P1 meshes with the second pinion 21P2 to rotate the pinion, and the second pinion 21P2 is transferred to the first pinion 21P1 via the transfer device 80. The second sun gear held in a stopped state by the low one-way clutch F or the low coast & reverse brake B1 arranged on the axis A side.
It meshes with 21S2, whereby the carrier 21C rotates and transmits decelerated rotation to the output member 70. Further, on the high speed side H, the rotation of the first sun gear 21S1 from the belt type continuously variable transmission 30, the input shaft 60 to C2, and the transfer device 80 are performed.
The rotation of the second sun gear 21S2 transmitted via the is given to the Ravigneaux planetary gear mechanism 21. This allows
The rotation combined through the first and second pinions 21P1 and 21P2 is taken out from the carrier 21C and transmitted to the output member. Further, in the R range, the forward brake B3 is released and the second sun gear 21S2 becomes free, and the reverse brake B2 is engaged to fix the ring gear 21R, whereby the rotation of the output shaft 30a is taken out as the reverse rotation from the carrier 21R. It

In FIG. 11, the low / high speed switching means and the forward / reverse switching means are composed of two single planetary gear mechanisms 23 and 25 arranged in parallel, and the output shaft 30a of the belt type continuously variable transmission 30 is the first. The ring gear 23 of the first planetary gear mechanism 23 is connected to the ring gear 25R of the planetary gear mechanism 25.
R and the carrier 25C of the second planetary gear mechanism 25 are connected to each other and to the output member 70, and the carrier 23C of the first planetary gear mechanism 23 is connected to the reverse brake B2.
In addition, the sun gear 25S of the second planetary gear mechanism 25 is connected to the transfer device 80.

Therefore, on the low speed side L, the belt type continuously variable transmission is provided.
The rotation of the secondary shaft 30a of 30 is transmitted to the ring gear 25S of the second planetary gear mechanism 25, and further, via the transfer device 80, to the low one-way clutch F or the low coast & reverse brake B1 arranged on the first axis A side. Is taken out from the carrier 25C as decelerated rotation based on the sun gear 25S in the stopped state and transmitted to the output member 70. Further, on the high speed side H, the rotation via the transfer device 80 is transmitted to the sun gear 25S, combined with the rotation of the ring gear 25R from the belt type continuously variable transmission 30 described above, and transmitted to the output member 70. Further, in the R range, the rotation of the secondary shaft 30a of the belt type continuously variable transmission is controlled by the sun gear 2 of the first planetary gear mechanism 23.
3S, further transmitted to the ring gear 23R as reverse rotation through the carrier 23C in the stopped state, and the second
In the planetary gear mechanism 25, the carrier 25C from the ring gear 23R rotates together with the rotation of the ring gear 25R and is output to the output member 70.

FIG. 12 shows a belt type continuously variable transmission output shaft 3 in which the low / high speed switching means and the forward / reverse switching means are composed of two single planetary gear mechanisms 26 and 27 arranged in parallel.
0a is connected to the ring gear 26R of the first planetary gear mechanism 26 and the sun gear 27S of the second planetary gear mechanism 27, the carrier 26C of the first planetary gear mechanism 26 and the carrier 27C of the second planetary gear mechanism 27 are connected, and the first planetary gear mechanism is further connected. 26 sun gear 26S transfer device 8
The ring gear 27R of the second planetary gear mechanism 27 is connected to the output member 70.

Therefore, on the low speed side L, the belt type continuously variable transmission is provided.
The rotation of the secondary shaft 30a of 30 is transmitted from the ring gear 26R of the first planetary gear mechanism 26 to the carrier 26C based on the sun gear 26S in the stopped state, and further the rotation of the sun gear 27S from the secondary shaft 30a by the second planetary gear mechanism 27. The rotation of the carrier 27C from the carrier 26C is combined, taken out from the ring gear 27R, and transmitted to the output member 7. Further, on the high speed side, the rotation via the transfer device 80 causes the first planetary gear mechanism 26 to rotate.
Is transmitted to the sun gear 26S, is combined with the rotation of the ring gear 26R from the secondary shaft 30a of the belt type continuously variable transmission described above, and is taken out from the carrier 26C.
In the planetary gear mechanism 27, the rotation of the sun gear 27S from the output shaft 30a and the rotation of the carrier 27C from the carrier 26C are combined and taken out to the output member 70. Further, in the R range, the carrier 27C of the second planetary gear mechanism 27 is used.
Is in a stopped state, and the rotation of the output shaft 30a is taken out as reverse rotation by the ring gear 27R via the pinion and transmitted to the output member 70a.

(G) Effect of the Invention As described above, according to the present invention, by switching the clutch, the planetary gear mechanism is used as two modes, for example, a simple reduction mechanism and a split drive mechanism, and a belt type continuously variable transmission is provided. By expanding the torque ratio width due to, it is possible to meet various demands such as the shift range of the automobile, and the planetary gear mechanism is arranged on the second shaft,
A plane on which the locking means and the clutch are arranged on the first shaft, and at least one of the clutch and the locking means and the planetary gear mechanism are orthogonal to the axial direction, while facilitating extraction of the output to the output member. Are arranged so as to share a part, it is possible to distribute the components on the first axis and the second axis in a balanced manner, and to reduce the axial dimension.

In particular, when the second shaft is applied to vehicles for F / F (front engine / front drive), it interferes with side members and is in the strictest environment in terms of dimensions, but it is the third element of the planetary gear mechanism. Since the locking means for locking the lock is arranged on the first shaft side via the transfer device, avoiding the second shaft from arranging the case portion or the like that serves as a fixing member of the locking means which causes an increase in the axial dimension. The second axial dimension can be shortened.

In addition, the above effects are combined, and it is possible to apply the present invention to an F / F vehicle having a large axial dimension regulation.

[Brief description of drawings]

FIG. 1 is a schematic view showing a continuously variable transmission according to the present invention, and FIG. 2 is a view showing the operation of each element at each position thereof. Further, FIG. 3 is a sectional view showing a continuously variable transmission embodying the present invention. Further, FIG. 4 is a diagram showing the relationship between the torque ratio and the transmission torque share ratio, and FIG. 5 is a diagram showing the relationship between the step ratio and the continuously variable transmission torque ratio with respect to the belt torque ratio. 6 to 12 are schematic views showing different embodiments. 12 …… continuously variable transmission, 13 …… fluid coupling, 20 …… (simple) planetary gear mechanism, 20C …… carrier, 20R …… ring gear, 20S …… sun gear, 30 …… belt type continuously variable transmission, 30a… ... primary shaft, 30b ... secondary shaft, 31 ... primary pulley, 32 ... secondary pulley, 33 ... belt, 70 ... output member, 70a ... input part (gear shaft), 71 ... reduction gear device, 72 ... Differential gear device, 73 ... Axle shaft, 80 ... Transfer device, 90
...... Forward / reverse switching device (dual planetary gear mechanism), A …… 1st axis, B …… 2nd axis, C1 …… Forward clutch, C2 …… (high) clutch, CL …… Lockup clutch, F, B1 …… Locking means (low one-way clutch, low coast & reverse brake), B2 …… Reverse brake.

Continuation of the front page (56) Reference JP-A-58-160655 (JP, A) JP-A-56-83649 (JP, A) JP-A-56-49455 (JP, A) JP-A-56-66552 (JP , A) JP-A-59-34058 (JP, A) JP-A-59-110954 (JP, A)

Claims (1)

(57) [Claims] 1. An input member, a belt-type continuously variable transmission that continuously changes the rotation of the input member, a planetary gear mechanism that inputs torque from the belt-type continuously variable transmission, and a planetary gear mechanism. A continuously variable transmission including an output member for inputting torque, wherein a primary shaft of the belt type continuously variable transmission is aligned with the input member to form a first shaft, and the belt type continuously variable transmission is also provided. A secondary shaft of the device is aligned with the center of the planetary gear mechanism and the input portion of the output member to form a second shaft, and the planetary gear mechanism has at least first, second and third elements, and The first element interlocks with the secondary shaft of the belt type continuously variable transmission, the second element interlocks with the output member, and the third element interlocks with locking means to rotate / stop. The locking means has a fixed member and a rotating member that can be locked to the fixed member, and is arranged coaxially with the first shaft, and the rotating member and the third element are provided. Is configured to be interlocked via a transfer device, and the rotating member and the input member can be connected and disconnected freely via a clutch, and the clutch is arranged coaxially with the first shaft, At least one of the locking means and the clutch arranged on the first shaft side and the planetary gear mechanism arranged on the second shaft side are arranged so as to share at least a part of a plane orthogonal to the axial direction. What has been done is a continuously variable transmission.