JP2866377B2 - Continuously variable transmission - Google Patents

Description

The present invention relates to a continuously variable transmission, particularly to a belt (including a chain type).
)) To a continuously variable transmission that incorporates a continuously variable transmission that uses
In particular, torque ratio width by planetary gear device etc.
The present invention relates to a continuously variable transmission in which is increased. (B) Conventional technology Recently, the demand for improvement of fuel consumption rate and
Incorporates a belt-type continuously variable transmission as a transmission
The use of continuously variable transmissions has attracted attention. Generally, the continuously variable transmission is a belt-type continuously variable transmission,
Body joint (or powder clutch), forward / reverse switching device and
And a reduction gear unit and a differential gear unit.
However, the above-mentioned continuously variable transmission has the minimum
Increase the torque ratio width by limiting the rate radius, etc.
Is not possible, and the range of the torque ratio width only by the continuously variable transmission
Responds to various requirements for automobiles, such as fuel efficiency and shifting performance.
Is not enough to work. Therefore, as disclosed in Japanese Patent Application Laid-Open No. 59-110954,
Continuously variable transmission with increased torque ratio by combining a gear
Machine 1 has been devised. The continuously variable transmission 1 has, as shown in FIG.
The carrier C of the tally gear device 2 is a belt type continuously variable transmission 3
And the ring gear R or the sun gear S
Either (for example, sun gear)
To the input shaft 6 via the device 8 and to the other (for example, ring gear).
) Is connected to an output member 7 such as a differential gear device,
The clutch 10 is connected between the power shaft 6 and the input unit 9 of the continuously variable transmission 3.
And a brake 11. Therefore, when the vehicle advances, the rotation of the input shaft 6 is
The torque is changed to a predetermined torque ratio via the latch 10 and the continuously variable transmission 3.
And the speed-change rotation is carried by the carrier of the planetary gear device 2.
C, and via the transfer device 8
Directly transmitted to the sun gear S, whereby the carrier C
Is amplified and extracted from the ring gear R to the output member 7
Is done. Also, the brake 11 is activated when the vehicle moves backward.
At the same time, the clutch 10 is disengaged, so that rotation of the input shaft 6 is exclusively performed.
Gear unit 2 via the transfer device 8
Of the carrier C which is transmitted to the sun gear S
Together, the reverse rotation is extracted from the ring gear R. (C) Problems to be Solved by the Invention By the way, the continuously variable gear provided with the planetary gear device 2 described above.
The gear 1 is a combined torque of the carrier C and the sun gear S.
Is removed from the ring gear R.
The number of teeth of the ring gear R is considerably larger than the number of teeth of the gear S.
In connection with this, the transmission to the carrier C transmitted through the continuously variable transmission 3 is performed.
The torque is transmitted via the sun gear S and the transfer device 8
The torque transmitted to the input shaft 6 and the continuously variable transmission 3 again
A circulation path is formed and thus via the transfer device 8
Negative torque is transmitted to the sun gear.
In this way, the continuously variable transmission 3 transmits the torque transmitted to the output member 7.
It will carry a larger torque. For example,
As disclosed in JP-A-59-110954, a sun gear
(Z _S ) And ring gear (Z _R ) And the number of teeth ρ (Z _S / Z _R )
If 0.5, T _C + T _R + T _S = 0, T _S = ΡT _R (T _C , Carrier torque, T _R Ring gear torque;
T _S ; Sun gear torque) T _C = T _R + T _S = (1 + ρ) T _R = 1.5T _R become. That is, the carrier torque T _C That is, continuously variable transmission from the input shaft 6
The torque transmitted through the device 3 is a ring gear torque.
T _R That is, the output torque transmitted to the output member 7 is 1.5
Double. Therefore, the present continuously variable transmission can increase the torque ratio width.
Transmission torque applied to the surface and belt type continuously variable transmission 3 is large.
The problem is increased. As a result, friction in the entire system of the continuously variable transmission
Belt-type stepless change that is structurally least reliable due to transmission
Excessive torque acts on the transmission, and the torque
Large side pressure must be applied to the pulley
This reduces the durability and transmission of the continuously variable transmission.
There is a possibility that the delivery efficiency may be reduced. Therefore, the present invention is to move the planetary gear device to the low speed side.
Is used as a simple deceleration mechanism and at high speed
By using it as a split drive mechanism,
To prevent the formation of a torque circulation path as
To provide a continuously variable transmission that solves the above problems.
It is the purpose. (D) Means for Solving the Problems The present invention has been made in view of the above circumstances, and
For example, the reference numerals of the embodiments shown in FIG. 1 and FIG.
In reference, the input member (60) and the rotation of the input member
A continuously variable transmission (30) for continuously changing the speed;
Planetary gear device for inputting torque from gear (20)
And an output for inputting torque from the planetary gear device.
And a member (70), wherein the planetary gear device (20) has at least a first
It has a second element and a third element, and the first element (20R)
Linked to the output (30a) of the continuously variable transmission (30),
The second element (20c) is linked to the output member (70), and the third element (20S) is linked to the locking means (F, B1).
And the third element and the front
The clutch (C2) is arranged between the input member (60) and the locking means (F, B1) is operated on the low speed side (L).
And the planetary gear device (20) is connected to the continuously variable transmission.
(30) to increase and transmit the torque to the output member
No deceleration mechanism, and on the high speed side (H)
(C2) to connect the planetary gear unit (20)
Torque from the continuously variable transmission (30) and the input member
Combining the torque from (60) and outputting the combined torque
Split drive mechanism that transmits to the force member (70)
It is characterized by the following. As an example, the continuously variable transmission 12 is, as shown in FIG.
Single planetary gear unit 20, belt type continuously variable transmission
30, transfer device 80, input shaft 60, and reduction gear device
In addition to the output member 70 composed of the gear 71 and the differential gear device 72,
Fluid coupling 13 with backup clutch CL and dual
The forward / reverse switching transmission 90 consisting of a planetary gear
Have. And the single planetary gear device 20
Is a reaction force support member when it is used as a speed reduction mechanism.
Element 20S (or 20R) is transferred via the transfer device 80
It is interlocked with the locking means F and B1, and is connected via the high clutch C2.
As a result, the input shaft 60 and the element 20S may be disconnected and connected. More specifically, the ring gear of the planetary gear device 20
20R interlocks with the output 30a of the continuously variable transmission 30 and
Gear 20C is linked to the output member 70, and the sun gear 20S is
Row one which constitutes the locking means via the transfer device 80
Way clutch F and low coast & reverse brake
It is linked to B1 and to high clutch C2. The dual planetary gear device 90 is
Gear 90S is connected to the input shaft 60, and the carrier 90C is continuously variable.
Connected to the input section 30b of the
Connected to the input shaft 60 via the switch C1 and the ring gear 90R
Connected to reverse brake B2. (E) Operation Based on the above configuration, each clutch in the continuously variable transmission 12
H, brake and one-way clutch
Operates as shown in FIG. 2, for example. In addition, ※
Indicates that the lock-up clutch CL can operate as appropriate.
You. More specifically, on the low speed side L in the D range,
Low one-way outside when the forward clutch C1 is connected
The clutch F operates. In this state, the engine
The rotation of the lock shaft is performed by the lock-up clutch CL or the fluid coupling 13.
Is transmitted to the input shaft 60 via the
Directly transmitted to sun gear 90S of gear device 90 and
The power is transmitted to the carrier 90C via the word clutch C1.
Therefore, the dual planetary gear device 90 is connected to the input shaft 60.
Rotate integrally and forward rotation input to belt type continuously variable transmission 30
Transmission to the section 30b, and the
Rotation from the output unit 30a to the single planetary gear unit 2
0 is transmitted to the ring gear 20R. one
On the other hand, in this state, the reaction force supporting element that receives the reaction force
Is the sun gear 20S is lower through the transfer device 80
Is stopped by the one-way clutch F
The rotation of gear 20R is taken out of carrier 20C as deceleration rotation.
Through a reduction gear device 71 and a differential gear device 72.
The power is transmitted to the wheel shaft 73. On the high-speed side H in the D range,
The high clutch C2 is connected in addition to the hard clutch C1. this
In this state, the speed is appropriately changed by the continuously variable transmission 30 as described above.
Positive rotation is output from the output unit 30a and
The signal is input to the ring gear 20R of the transmission 20. On the other hand,
Sometimes, the rotation of the input shaft 60 is
Of the single planetary gear unit 20 through the gear unit 80.
To the planetary gear device 20S.
20 combines the torque of the ring gear 20R and the sun gear 20S
And output from the carrier 20C. In this case,
Gear 20S resists reaction force via transfer device 80
Rotation is transmitted, so that torque circulation does not occur.
And a predetermined plus torque is transferred via the transfer device 80.
Transmitted. And from the synthesized carrier 20C
Is transmitted through the reduction gear device 71 and the differential gear device 72.
The power is transmitted to the axle shaft 73. In operation in the D range, the one-way
When the reverse torque is applied (when the engine is braked)
Free, but in the S range, low one way
Low coast & reverse brake B1 in addition to clutch F
Operates to transmit power even when reverse torque is applied. In the R range, low coast and reverse brake
The reverse brake B2 operates together with the rake B1. This state
In this state, the rotation of the input shaft 60 is controlled by a dual planetary gear
When the ring gear 90R is fixed at the
Enters belt-type continuously variable transmission 30 as reverse rotation from rear 90C
Is forced. On the other hand, low coast & reverse brake B1
Sun gear of single planetary gear unit 20 based on operation
20S is fixed, so the reverse from the continuously variable transmission 30
The rotation is reduced by the planetary gear device 20 and the output member 70
Is taken out. In the P range and N range, low course
And reverse brake B1 operates. (F) Embodiment Next, an embodiment of the present invention will be described with reference to FIG.
Will be explained. The continuously variable transmission 12 is a transmission composed of three parts.
The case 15 has an input shaft 60 and a
The input shaft 30b of the step transmission 30 is rotatably supported coaxially.
To form the first shaft, and the output of the continuously variable transmission 30.
The power shaft 30a and the gear shaft 70a are rotatably supported coaxially
It comprises two axes. In addition, lock-up on axis 1
Fluid coupling 13 with clutch CL, forward clutch C
1, high clutch C2, low coast & reverse brake B
1, reverse brake B2, low one-way clutch F
Control unit 40, dual constituting forward / reverse switching device
The planetary gear unit 90 and the hydraulic pump 17 are provided.
And a single planetary gear unit 20 on the second shaft.
Are arranged. The control unit 40 and the input unit will be further described.
The shaft 60 has a lock-up clutch CL and a fluid connection at one end.
The output member of hand 13 is engaged and the other end
The sun gear 90S of the planetary gear unit 90
Further, a switch fixed to the case 15 is provided on the input shaft 60.
A leave part 15a is provided. Also, the sleeve portion 15a
Is connected to sprocket 81 via one-way clutch F
Sleeve that is connected and connected to input shaft 60
A shaft 41 is rotatably supported. Further, the sleeve shaft
Flange 41a rising from 41 is formed on one side
Word clutch C1 is installed together with its hydraulic actuator 42.
High clutch C2 on the other side.
It is installed together with the tutor 43. And Hykra
The switch C2 has its driven side connected to the boss of the sprocket 81.
And the boss is attached to the case 15 by the hydraulic actuator.
Coast and reverse buses installed with Data 45
Connected to rake B1. Meanwhile, the forward clutch C1
The driven side of the carrier 90 of the dual planetary gear unit 90
C and dual planetary gear unit 90
The ring gear 90R of the case 1 together with the hydraulic actuator 46
5 is engaged with the reverse brake B2 disposed. What
Note that the carriers 90C mesh with each other and mesh with the sun gear 90S.
Meshing with the pinion 90P1 and the ring gear 90R
Support pinion 90P2. Further, the continuously variable transmission 30 is disclosed in Japanese Patent Application No. 60-298794 (not disclosed).
As detailed in (Open), the primary pulley 31,
Secondary pulley 32 and both pulleys
It consists of a belt 33, and both pulleys are fixed sheaves respectively.
31a and 32a and movable sheaves 31b and 32b. In addition,
The multiple pulleys 31
To rotate integrally with the input shaft 30b via the disc spring 38
Between the thrust holding member 34a and the fixed sheave 31a
Pressure adjusting cam machine that applies an axial force corresponding to the transmission torque during
Structure 34 is provided, and movable sheave 31b is fixed
Only sliding on the boss 31c of the boss 31a via the ball spline
It is freely supported and has a ball screw mounted on its back.
35 is provided. Ball screw device 35 is the bolt
The part 35a cannot rotate to the case 15 and the thrust bearing
Is connected to the input shaft 30b via the
The nut 35b is attached to the movable sheave 31b
Connected so that they can move together in the axial direction
Have been. On the other hand, the secondary pulley 32 has its fixed sheave
32a is rotatably supported by the case 15 integrally with the output shaft 30a.
The movable sheave 32b
Only the sliding is supported via the in. Further,
A ball screw device 36 is provided on the back of the movable sheave 32b.
And the bolt portion 36a cannot rotate to the case 15 and
Thrust bearings on the flange 30d fixed to the output shaft 30a
Is connected via a bush so that it cannot move in the axial direction.
The part 36b is connected to the movable sheave 32b via a thrust bearing and the shaft.
Connected to move in one direction. And
There is no operation between the primary pulley 31 and the secondary pulley 32.
An operation shaft 37 is rotatably supported. Fig. 3 shows the exhibition
Since it is an open figure, the operation axis 37 is drawn at the top, but actually
Is the operation shaft 37 of the input shaft 30b and the output shaft 30a in a front view.
Located in the middle part. The operation shaft 37 has a circular shape.
Gear 37a, non-circular gear 37b, and worm wheel 37c
Is fixed, and the wheel 37c is
Connected to an electric motor controlled by an electric signal
Worm 37d is engaged. The circular gear 37a is
Wide fixed to the nut 35b on the side of the pulley 31
Gear 35c, and the non-circular gear 37b
The width fixed to the nut part 36b on the side of the pulley 32
It meshes with the wide non-circular gear 36c. In addition, the single planetary gear device 20 has a second shaft.
The ring gear 2 is disposed on the gear shaft 70a
0R of the belt type continuously variable transmission 30 is adjacent to the flange 30d.
It is connected to the output shaft 30a. The gear shaft 70a has a sun
A sprocket 82 is rotatably supported integrally with the gear 20S.
And the pinion 20P is rotatable around the gear shaft 70a.
The supporting carrier 20C is fixed. On the other hand, a sprocket mounted integrally with the sun gear 20S on the second shaft.
And the low one-way clutch F
Between the sprocket 81 and the silent chain 83
It is hung, with these sprockets and chains
The transfer device 80 is configured. In addition, the gear shaft 70a outputs the gear 71a by integrally forming the gear 71a.
Constitutes the member 70, and the gear 71a is fixed to the intermediate shaft 71b
Gear 71c. Furthermore, the intermediate shaft 71b
Is formed with a small gear 71d, and the gear 71d is a differential gear.
Meshing with a ring gear 72a fixed to the vehicle device 72,
The reduction gear 71 is constituted. Also, from the differential gear device 72
The left and right front axle shafts 73 extend. Next, the operation of the present embodiment will be described. Engine crankshaft rotation lock-up clutch CL
Or, it is transmitted to the input shaft 60 via the fluid coupling 13 and further
Transmitted to sun gear 90S of al planetary gear unit 90
Is transmitted to the sleeve shaft 41. D range and S ren
Forward clutch C1 is connected and
Since the brakes B2 are released, dual planetary
In the gear device 90, the sun gear 90S and the carrier 90C integrally follow.
The ring gear 90R also rotates integrally, and forward rotation is a belt type
The power is transmitted to the input shaft 30b of the continuously variable transmission 30. The rotation of the input shaft 30b is performed via the thrust holding member 34a.
And transmitted to the pressure adjustment cam mechanism 34,
Movable via 31 fixed sheep 31a and ball spline
It is transmitted to sheave 31b. At this time, the pressure adjustment cam mechanism 34
The axial force corresponding to the input torque acting on the force shaft 30b is
8 acts on the back of the sheave 31a, while the other
The ball screw device 35 is driven by the ball screw device 35 corresponding to a predetermined speed ratio.
Fixed in the longitudinal direction and therefore the thrust bearing
Equivalent reaction force acts on the back of sheave 31b via the ring
As a result, the primary pulley 31
The belt 33 is clamped with the corresponding clamping force. In addition, belt 33
Is transmitted to the secondary pulley 32, and further the output shaft 30
conveyed to a. At the time of belt transmission,
Based on signals from sensors such as torque opening and vehicle speed,
The worm 37d and worm wheel 3
The operation shaft 37 is rotated via 7c. Then, the circular gear 37
Ball screw device on primary pulley 31 side through a and 35c
As the nut 35b rotates, the non-circular gears 37b and 36c
Through the nut of the secondary pulley 32 side ball screw device 36
The rotating part 36b rotates. This stops rotation on case 15.
The nuts 35b and 36b are between the bolts 35a and 36a
After relative rotation, the ball screw devices 35 and 36
Move the movable sheaves 31b and 32b through the
Set the pulley 31 and secondary pulley 32 to a specified effective diameter
Then, the set torque ratio is obtained. At this time, both ball
Because the device moves linearly, it is defined by a belt 33.
There is a difference from the original moving amount of the movable sheave,
Dali pulley 32 rotates through non-circular gears 37b and 36c
Therefore, the movable sheave should be
Be moved. In addition, both sheaves 31a, 31b and 32a, 32b
The belt clamping pressure is
Acts to pull the input shaft 30b through the strike bearing
Does not affect case 15 and
The pulley 32 also acts to pull the output shaft 30a.
Does not act on the case 15. Further, the rotation of the output shaft 30a of the belt-type continuously variable transmission 30 is
Transmission to ring gear 20R of single planetary gear unit 20
And transmitted to the gear shaft 70a via the carrier 20C.
You. In the case of the low speed side L in the D range, FIG.
As shown, the low one-way clutch F is
Transmission from the ring gear 20R to the carrier 20C.
The sun gear 20S receives a reaction force when
YA 20S is low one way via transfer device 80
The rotation is stopped by the clutch F.
The transmission 20 constitutes a speed reduction mechanism. Therefore, the bell
The rotation of the output shaft 30a of the
The speed is simply reduced by the planetary gear unit 20, and the gears 71a, 71
c, an intermediate shaft 71b, a gear 71d, and a mount gear 72a.
The gear is further reduced via the speed gear 71 and the differential gear
The power is transmitted to the left and right front axle shafts 73 via the mounting 72. When the throttle opening and the vehicle speed reach predetermined values,
The high clutch C2 is connected by a signal from the control unit.
To the high speed side. Then, the rotation of the input shaft 60 is
Transmission to the automatic transmission 30 and the sleeve shaft
41 and the sprocket 81 via the high clutch C2.
Through the silent chain 83 and sprocket 82
To the sun gear 20S of the single planetary gear unit 20
Is reached. At this time, the input side of the transfer device 80
Sprocket 81 is thin with low one-way clutch F
Receives reaction force from sun gear 20S of the glue planetary gear unit.
To prevent shift shocks
And start smooth rotation by connecting high clutch C2
To transmit the torque to the sun gear 20S. As a result,
The torque and torque that have been continuously variable by the
The torque through the transfer device 80 and the single planet
Tally gear device 20 combines the combined torque and carrier
It is transmitted from 20C to the gear shaft 70a. Furthermore, the same as the low speed side
In the same way, through the reduction gear device 71 and the differential gear device 72,
The power is transmitted to the front axle shaft 73. At low speed L in the S range, engine shake
The low coast &
The reverse brake B1 is engaged and the sprocket 81 rotates forward and backward.
It is also prevented from rolling. The high-speed side H in the S range is
This is the same as the high speed side of 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,
Transmitted to the sun gear 90S of the dual planetary gear unit 90.
The rotation of the input shaft 60 is locked when the ring gear 90R stops.
The belt-type continuously variable transmission 30 is rotated in reverse from the carrier 90C.
The power is transmitted to the input shaft 30b. At this time, single planetary
Transfer device 80 from sun gear 20S of gear device 20
The reaction torque acts as a reverse rotation on the sprocket 81
So the low coast and reverse brake B1 operates
To stop the sprocket 81. In the transmission of the torque of the continuously variable transmission 12, the fourth
As shown in FIG.
The transmission is performed via the
The torque and torque through the belt-type continuously variable transmission 30
Where the torque passing through the transfer device 80 corresponds to the torque ratio
It is shared at a fixed rate. Further, as shown in FIG.
The torque ratio of the continuously variable transmission 12 to the torque ratio is L
At the high speed side.
Thus, a curve H 'is obtained. Therefore, low speed side L
When stepping from high to high speed H (or vice versa)
Curve ratio (low-speed side torque ratio / high-speed side torque ratio)
I will be. Note that the low-speed side L (L ') to the high-speed side H
When stepping to (H ') (or vice versa)
Change the torque ratio of the belt type continuously variable transmission 30 as shown
Switching by simply connecting the high clutch C2
As shown by a chain line B, and
At the same time as connecting the high clutch C2 so that the torque ratio does not change.
Belt type continuously variable transmission by signal from control unit
Operate to increase the torque ratio of 30 by a predetermined amount and shift
It may be controlled so that there is no shock.
May be controlled so as to pass through an arbitrary line in an intermediate portion between the line and the line. Next, based on FIG. 6 to FIG.
A modification example will be described. 1 and FIG.
The same reference numerals are used for the same parts as those described above, and the description is omitted.
You. FIG. 6 shows a single planetary gear device 20.
The sun gear 20S to the output shaft 3 of the belt-type continuously variable transmission 30.
0a, and the ring gear 20R is
Engage with high clutch C2 via transfer device 80
Connected to the force shaft 60 and low one-way clutch F or
Rotation is prevented by low coast & reverse brake B1
It is connected to the transfer input unit 81. In this embodiment, the step ratio between the low speed side L and the high speed side is
The torque ratio of the continuously variable transmission 12 must be increased.
And acts on the belt-type continuously variable transmission 30
The torque can be reduced. FIG. 7 shows a belt type continuously variable transmission 30
And put forward clutch C1 and high clutch C2 side by side
Dual planetarizer for forward and reverse switching transmission
The gearing device 90 is arranged adjacent to the fluid coupling 13, and
Coast & reverse brake B1 and low one way club
Switch F to the single planetary gear on the side of the second shaft 30a, 70a.
In the vicinity of the head device 20. Therefore, on the low speed side L, the single planetary gear
The sun gear 20S of the gear unit 20 is the low one-way clutch F or
Stops direct rotation with low coast & reverse brake B1
Is stopped, creating unnecessary load torque on the transfer device 80.
Do not use. Fig. 8 shows a bell on the first axis (30b, 60).
G-type continuously variable transmission 30 has a forward / reverse switching transmission means
Dual planetary gear unit 90 and forward clutch
C1 is arranged, and the low-speed switching transmission means,
Switch C2, low coast and reverse brake B1 and lower
One-way clutch F is arranged. The one shown in FIG.
Positioned adjacent to the joint 13 and on the other side, forward / reverse switching
Transmission dual planetary gear unit 90 and forward
Distribute clutch C1, high clutch C2 and reverse brake B2.
On the other side of the second shaft,
Gearing device 20, low coast and reverse brake B1 and
A low one-way clutch F is provided. FIG. 10 shows a forward / reverse switching transmission means 90,
Move the reverse clutch B1 and reverse brake B2
Planetary for single belt type continuously variable transmission 30
It is arranged on the opposite side of the gear device 20. The one shown in FIG.
Separated from the joint 13 and adjacent to the high clutch C2
Deploy, low coast and reverse brake B1 and
-One-way clutch F with single planetary gear
Along with 20, it is arranged on the second shaft side. FIG. 12 shows a single planetary gear device 20.
, The forward clutch C1, the high clutch C
2, low coast & reverse brake B1, and forward / reverse turning
Replacement transmission means 90 'are all disposed on the first shaft side, and
Power is taken out to the output member 70 from one shaft side. The book
In the embodiment, the forward / reverse switching power transmission means is an idle gear.
Consists of a reverse clutch C3 via a lug 91 and therefore R
In the range, the rotation of the input shaft 60
91, gear 93 and gear 95 via reverse clutch C3.
And transmitted to the output member 70. The one shown in FIG. 13 is similar to the one shown in FIG.
The output shaft 30a of the automatic transmission 30 is a single planet
To the sun gear 20S and the ring gear 20R of the transmission 20
Although connected to the transfer device 80, the transfer
The device 80 comprises a chain 83. FIG. 14 shows a belt type continuously variable transmission 30 similarly.
Output shaft 30a of single planetary gear unit 20 sangi
Gear 20R and the ring gear 20R to the transfer device 80
And one-way
Disconnect clutch F and low coast & reverse brake B1.
Along with the single planetary gear unit 20
And the lock-up clutch CL is separated from the fluid coupling 13
Separated. The one shown in Fig. 15 is a low / high speed switching transmission
And two sun gears.
21S1, 21S2 and one sun gear 21S1 is a belt
Connected to the output shaft 30a of the continuously variable transmission 30 and
The gear 21S2 is connected to the transfer device 80, and
The two pinions 21P1 and 21P2 are supported in parallel with the yam 21C.
Ravigneaux planetarigi consisting of one ring gear 21R
That is released in the R range.
Forward brake B3 is installed. Therefore, on the low speed side L, the belt-type continuously variable transmission
The rotation of the output shaft 30a of the first sun gear 21S1
Transmitted to the nonion 21P1 and further formed of a long pinion.
The first pinion 21P1 meshes with the second pinion 21P2 to
The second pinion 21P2 is rotated
Fake clutch F or low coast & reverse brake B1
Meshes with the second sun gear 21S2 held in a stopped state at
As a result, the carrier 21C rotates and is reduced to the output member 70.
Transmits high speed rotation. On the high-speed side H, the belt
With the rotation of the first sun gear 21S1 from the
The high clutch C2 and the transfer
The rotation of the second sun gear 21S2 transmitted through the
It is provided to the gno-type planetary gear device 21. This
And synthesized via the first and second pinions 21P1 and 21P2.
Rotation is removed from the carrier 21C and transmitted to the output member.
It is. In the R range, the forward brake B3 is released.
Release the second sun gear 21S2 to free and reverse
The brake B2 is engaged to fix the ring gear 21R.
The rotation of output shaft 30a is taken out of carrier 21C as reverse rotation
Is done. The one shown in Fig. 16 is a low / high speed switching transmission means and forward / reverse
Switching transmission means, two singles arranged side by side
Consisting of planetary gear units 23 and 25, belt type continuously variable transmission
The output shaft 30a of the device 30 is connected to the sun of the first planetary gear device 23.
Connected to the gear 23S and the second planetary gear device 25
Connected to the ring gear 25R and the first planetary gear device 2
Carrying the third ring gear 23R and the second planetary gear unit 25
And 25C are connected to each other and to the output member 70,
The carrier 23C of the first planetary gear unit 23 is
To the brake B2 and the second planetary gear unit 25.
The gear 25S is connected to the transfer device 80. Therefore, on the low speed side L, the belt-type continuously variable transmission
The rotation of the output shaft 30a of the second planetary gear device 25
Transmitted to the gear 25R, and a low one-way clutch
Stopped by F or low coast & reverse brake B1
Deceleration rotation from carrier 25C based on sun gear 25S
And is transmitted to the output member 70. Also on the high-speed side
In H, rotation through the transfer device 80
The belt-type continuously variable transmission that is transmitted to the sun gear 25S
The output member 7 is combined with the rotation of the ring gear 25R from the device 30.
Transmitted to 0. Furthermore, in the R range, the belt type
The rotation of the continuously variable transmission output shaft 30a is controlled by the first planetary gear.
It is transmitted to the sun gear 23S of the device 23 and is in a stopped state.
Ring gear as reverse rotation via pinion of carrier 23C
Gear 23R, and to the second planetary gear unit 25
Then, forward brake B _Three Release of sun gear 25
Since S is free, the ring gear 23R
The rotation is output to the output member 70 via the carrier 25C. The one shown in Fig. 17 is a low / high speed switching transmission
Switching transmission means, two singles arranged side by side
Consisting of planetary gear units 26 and 27, belt type continuously variable transmission
The device output shaft 30a is the ring gear of the first planetary gear device 26.
Gear 26R and the sun gear 27S of the second planetary gear unit 27.
And the carrier 26C of the first planetary gear device 26
The carrier 27C of the second planetary gear unit 27 is connected and
The sun gear 26S of the first planetary gear unit 26 is
Connected to the fur device 80 and a second planetary gear device
27 ring gears 27R are connected to the output member 70. Therefore, on the low speed side L, the belt-type continuously variable transmission
The rotation of the output shaft 30a of the first planetary gear device 26
Based on the sun gear 26S in the stopped state
Transmitted to the carrier 26C and further to the second planetary gear device 2
At 7 the rotation of the sun gear 27S from the output shaft 30a and the carry
The rotation of the carrier 27C from the gear 26C is combined with the ring gear 27
It is extracted from R and transmitted to the output member 70. Also fast
On the side, rotation via the transfer device 80
Transmitted to the sun gear 26S of the first planetary gear device 26,
Ring from the output shaft 30a of the belt type continuously variable transmission described above.
Combined with rotation with gear 26R, removed from carrier 26C
Further, in the second planetary gear device 27, the output shaft 30
The rotation of sun gear 27S from a and the carrier from carrier 26C
The rotation of the gear 27C is combined and taken out to the output member 70. Change
In the R range, the second planetary gear unit 27
Carrier 27C is in a stopped state, and the output shaft 30a
The rotation of gear 27S reverses to ring gear 27R via pinion
And is transmitted to the output member 70a. FIG. 18 shows a low / high speed switching transmission
It is composed of an al planetary gear device 120,
The planetary gear device 120 has its pinions 120P1 and 120P2.
The carrier 120C that supports the belt-type continuously variable transmission 30
The sun gear 120S is connected to the output shaft 30a and the idler gear 8
3 'transfer device 80
A gear gear 120R is connected to the output member 70. Therefore, on the low speed side L, the output of the continuously variable transmission 30
The rotation of the shaft 30a is carried by the dual planetary gear device 120.
From the gear 120C based on the stopped sun gear 120S.
To the output gear 70.
Is transmitted. On the high-speed side H, transfer
-The rotation from the device 80 is transmitted to the sun gear 120S, and
From the output shaft 30a of the continuously variable transmission with the carrier 120C
Are synthesized in the dual planetary gear device 120,
Synthetic rotation is extracted from the ring gear 120R and is output to the output member 70.
Is transmitted. The one shown in Fig. 19 separates the low-speed transmission system from the high-speed transmission system.
Is used. That is, in the low speed side L
Reduction mechanism 121 functions as a small gear 121a and meshes with it.
Large gear 121b and the large gear 121b are connected to the output member 70.
Transmission shaft 121c and functions on the high speed side H
Split drive mechanism 122 is a single planetary gear
Device. Then, the continuously variable transmission output shaft 30a is driven low.
Connected to small gear 121a via coast & reverse clutch C4
And the small gear 121a can be
It is linked via Chi-F, and single planetary
The gear device 122 is connected to the ring gear 122R. Also,
The carrier 122C of the gear device 122 is connected to the output member 70.
And the sun gear 122S is driven through the high clutch C2.
It is connected to a transfer device 80. Therefore, on the low speed side L, the belt-type continuously variable transmission
The rotation of the output shaft 30a of the 30
Via (D range) or low coast & reverse crack
And transmitted to the small gear 121a (S range) via the switch C4.
Large gear 121b and transmission shaft that constitute a reduction mechanism of the series transmission system
It is transmitted to the output member 70 via 121c. At this time,
Planetary gear unit 12 constituting the split drive mechanism
The rotation is also transmitted from the output shaft 30a to the second ring gear 122R.
However, since the high clutch C2 is released, the ring gear
The 122R only spins and does not function as a transmission. Ma
On the high-speed side H, the output shaft 30a of the continuously variable transmission
Planetary gears that make up the split drive mechanism
While being transmitted to the ring gear 122R of the device 122,
The connection of the latch C2 causes the transfer device 80 to
122 122S, which is similar to that shown in FIG.
Then, the combined rotation is transmitted to the output member 70. Naoko
At this time, via the gears 71a, 71b, the transmission shaft 121c, and the large gear 121b.
The small gear 121a also rotates, but the gear 121a
It is connected to the output shaft 30a just by idling with the clutch F.
Never. In addition, at the time of reverse, reverse brake
Dual switch that constitutes forward / reverse switching means based on the operation of B2
The reverse rotation is transmitted to the continuously variable transmission 30 by the planetary gear unit 90.
Reached, low coast & reverse clutch C4 connection
The reverse rotation output from the continuously variable transmission 30 is
The light is transmitted to the output member 70 via the first signal. Fig. 20 shows a low-speed transmission
Using a separate transmission means with the split drive mechanism of the dynamic system
Although the reduction mechanism is a single planetary gear
Consists of 123. The split drive mechanism is configured
The single planetary gear device 122 is the first planetary gear device described above.
It is the same as that of FIG. And single planetary
The gear device 123 is such that its ring gear 123R is
It is connected to the output shaft 30a, and the carrier 123C is
Connected to the small gear 121a 'linked to the material 70,
3S is low one way clutch F and low coast & river
Connected to the brake B1. Therefore, on the low speed side L, the continuously variable transmission output shaft 30
The rotation of a is performed by the low one-way clutch F (D range) or
Is a product of low coast & reverse brake B1 (S range)
The sun gear 123S is stopped based on the
The gear 123R is transmitted to the carrier 123C as decelerated rotation,
Further, through a small gear 121a ', a large gear 121b' and a transmission shaft 121c '.
Then, it is transmitted to the output member 70. On the high-speed side H
Is the same as the embodiment shown in FIG. 19 in which the high clutch C2 is connected.
Similarly, the planetary that constitutes the split drive mechanism
The gear device 122 is transferred to the continuously variable transmission output shaft 30a.
The rotation with the device 80 is combined and transmitted to the output member 70. this
Gears 71a, 71b, transmission shaft 121c ', and gears 121b', 121a '.
Of the planetary gear device 123 that constitutes the speed reduction mechanism
The rotation is also transmitted to carrier 123C, but the one-way
Chi F becomes free and does not participate in transmission. In addition, the river
In reverse, reverse brake B2 and low coast & river
Based on the operation of the brake B1, the continuously variable transmission output shaft 30a
The reverse rotation of the planetary gear device 12
The light is transmitted to the output member 70 via the third member 3. The one shown in Fig. 21 is used as a low / high speed switching transmission means.
Using a planetary gear device 125 consisting of a bevel gear device
Other structures are shown in FIGS. 1 and 6.
This is the same as the embodiment. The bevel gear unit 125 is
The bell 125L is connected to the continuously variable transmission output shaft 30a,
25R to transfer device 80 and its central bevel 1
25C are respectively connected to the output members 70. Therefore, on the low speed side L, the continuously variable transmission output shaft 30
The rotation of a is low one way clutch F or low course
Right bevel stopped by the reverse & reverse brake B1
From left bevel 125L to center bevel 125C
It is transmitted as decelerated rotation, and further transmitted to the output member 70.
You. On the high-speed side, the left vehicle from the output shaft 30a
Torque based on the rotation of the bell 125L and the connection of the high clutch C2
The rotation from the transfer device 80 and the bevel gear device 125
It is synthesized and transmitted to the output member 70. In the one shown in FIG. 22, the second axis is composed of multiple axes,
It is a compact structure. That is, the continuously variable transmission 30
Single planetary gears with the output shaft 30a of the
Connected to the ring gear 20R of the device 20 and output the carrier 20C
Connected to the member 70, and further fitted the sun gear 20S on the hollow shaft 30a
Low one-way clutch via the sleeve shaft 126
And low coast & reverse brake B1
Both are connected to the transfer device 80. And out
The force member 70 includes the secondary pulley 32 of the continuously variable transmission 30 and the
A planet that is coaxial with the single planetary gear unit 20
From the reduction gear device 71 and the differential device 72,
And further, from the differential 72, a left front axle 73L
Extends through the hollow shaft 30a and the secondary pulley 32
And the right front axle 73R extends to the right.
You. The reduction gear device 71 has a sun gear 71S
Connected to the carrier 20C of the
Gear 71R is fixed, and carrier 71C is differential gear 72.
Has been entered. (G) Effects of the Invention As described above, according to the present invention,
Gear unit 20 is a simple speed reducer on the low speed side L of the continuously variable transmission 12.
Split drive at high speed H
Since the mechanism is structured, the torque ratio of the continuously variable transmission 12 as a whole is
The width can be increased, and the fuel efficiency and speed change performance can be improved. On the low-speed side L, the planetary gear unit 20 is simply
Since it is a pure reduction mechanism, the torque ratio width of the continuously variable transmission 30
The torque ratio width of the entire continuously variable transmission 12 remains unchanged.
Large output torque ratio range compared to lit drive mechanism
And reduced by the planetary gear device 20.
Output and no torque from the input member 60
In combination with the output via the step transmission 30, the low
On the high-speed side L, a large torque ratio width is finely controlled.
Large torque ratio at the time of vehicle transmission, etc.
Can respond to demands such as smooth acceleration due to changes
You. Furthermore, it is more constant than the low speed side L which is generally used during acceleration, etc.
High-speed side H used during normal driving has a longer usage time
However, the continuously variable transmission 30
Transmission torque is greatly reduced, and the
As it decreases, the durability can be improved and the high speed side H
Gears for the continuously variable transmission 30 comprising friction transmission means.
Or a transfer device consisting of a chain with high transmission efficiency
Since the torque is carried even by the device 80, etc., the transmission efficiency is also improved.
Switch from the split mechanism to the reduction mechanism.
Quick kickdown is possible by replacement. In addition, the speed reduction mechanism and the split drive mechanism
It is compact because it is composed of gears.
it can. Particularly, as a continuously variable transmission, a V-belt type continuously variable transmission
Using 30 reduces the overall torque capacity of the transmission 12.
The load on the belt can be reduced
Obstacles to the practical use of continuously variable transmissions
It is easy to solve the problem of tilt durability. In addition, the locking means (low
One-way clutch, low coast & reverse brake
The third element connected to B1) is used as a reduction gear mechanism.
When constituted by a reaction force support member, the planetary gear device 20
When the split drive mechanism is used, the torque circulation path
The torque that is not formed and that the belt-type continuously variable transmission 30 carries
To reduce large
Continuously variable speed with maximum torque capacity and sufficient durability
Machine 12 can be realized. Further, it is linked to the output section 30a of the belt type continuously variable transmission 30.
The first element of the single planetary gear device 20
20R, and the second element linked to the output member 70 is
If the rear element is 20C and the third element is sun gear 20S,
Step ratio between low speed side L and high speed side H is set relatively small
To meet the required torque ratio range and reduce shift shock.
Not a continuously variable transmission 12 can be obtained. The first element is a single planetary gear device 20.
The sun gear 20S, the second element is the carrier 20C, and
If the third element is a ring gear 20R, the low-speed side L and the high-speed side
The step ratio with the side H is expanded to increase the torque ratio
The transmission 12 can be obtained, and the transfer
The load acting on the belt by increasing the torque carrying ratio of the
Can be significantly reduced. Further, the means for locking the third element 20S or 20R is
Way clutch F and low coast & reverse brake
Assuming B1, replace with one-way clutch F
Shift shock and smooth shifting
And the low coast and reverse brake B1
Correspond to reverse torque transmission of engine brakes etc.
be able to. The locking means (low one-way clutch F, low
And reverse brake B1) with belt-type continuously variable transmission
On the first axis aligned with the primary pulley 31 of the device 30
And other control equipment (forward clutch C1 (or forward clutch
Brake B3), high clutch C2, reverse brake
Combined with the arrangement of B2), a compacter with reduced axial dimension
Configuration, and the control devices can be
Simplifies the configuration of oil passages, etc., and is easy to maintain.
Can also be improved. The locking means (low one-way clutch F, low
Bast & reverse brake B1) with belt-type continuously variable transmission
Place on a second axis aligned with 30 secondary pulleys 32
Operating the locking means to reduce the planetary gear device 20
When using a gear mechanism, the reaction force is applied to the transfer device 80.
Improve the durability of the transfer device without acting
Can be.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a schematic diagram showing a continuously variable transmission according to the present invention, and FIG. 2 is a diagram showing the operation of each element in each position. FIG. 3 is a sectional view showing a continuously variable transmission embodied in the present invention. FIG. 4 is a diagram showing a relationship between a torque ratio and a transmission torque sharing ratio, and FIG. 5 is a diagram showing a relationship between a step ratio and a continuously variable transmission torque ratio with respect to a belt torque ratio. 6 to 22 are schematic diagrams showing different embodiments. FIG. 23 is a schematic view showing a conventional example. 12 ... continuously variable transmission, 13 ... fluid coupling, 20 ... (simple planetary) gear device, 20C ... carrier, 20R ... ring gear, 20S ... sun gear, 21, 23, 25, 26, 27 ... Gear device, 30 (belt type) continuously variable transmission, 30a ... output part (shaft), 30b ... input part (shaft), 31 ... primary pulley, 32 ... secondary pulley, 33 ... belt, 70 output member, 71 reduction gear unit, 72 differential gear unit, 7
3,73L, 73R …… axle shaft, 80… transfer device, 90… forward / reverse rotation switching transmission means (dual planetary gear device), 120,121,122,123,125 …… gear device, C2, C
4, B1, F ... selection means, B1, F ... locking means, B1 ... low coast & reverse brake, B2 ... reverse brake,
C1 …… Forward clutch, C2 …… High clutch, C3…
… Reverse clutch, C4 …… Low clutch, CL …… Lock-up clutch, F …… Low one-way clutch.

Continuation of front page (58) Field surveyed (Int.Cl. ⁶ , DB name) F16H 37/02

Claims (1)

(57) [Claims] An input member, a continuously variable transmission that continuously changes the rotation of the input member, a planetary gear device that inputs torque from the continuously variable transmission, and an output member that receives torque from the planetary gear device. In the continuously variable transmission, the planetary gear device has at least first, second, and third elements, and the first element is interlocked with an output unit of the continuously variable transmission, and the second The third element is interlocked with the output member, and the third element is connected to the locking means so that the third element can be stopped, and a clutch is disposed between the third element and the input member. Operating the locking means on the low speed side to reduce the planetary gear device from the continuously variable transmission to a reduction mechanism for transmitting the torque to the output member; and connecting the clutch on the high speed side. And said Wherein the forming a Ranetarigiya device with a split drive mechanism for transmitting torque and combined and the combined torque of the torque from the input member from said continuously variable transmission to the output member, the continuously variable transmission. 2. 2. The continuously variable transmission according to claim 1, wherein the continuously variable transmission is a belt-type continuously variable transmission including a primary and secondary pulleys each having two sheaves whose effective diameters can be changed, and a belt wound around these pulleys. The continuously variable transmission according to the item. 3. 3. The continuously variable transmission according to claim 2, wherein said locking means is disposed on a first shaft aligned with a primary pulley of said belt type continuously variable transmission. 4. 3. The continuously variable transmission according to claim 2, wherein the locking means is disposed on a second shaft aligned with a secondary pulley of the belt-type continuously variable transmission. 5. The third element of the planetary gear device is a reaction force support member when forming the speed reduction mechanism.
The continuously variable transmission according to the item. 6. The planetary gear device is a single planetary gear device, the first element of which is a ring gear;
6. The continuously variable transmission according to claim 5, wherein the second element is a carrier, and the third element is a sun gear. 7. 6. The apparatus according to claim 5, wherein said planetary gear device is a single planetary gear device, wherein said first element is a sun gear, said second element is a carrier, and said third element is a ring gear. Continuously variable transmission. 8. 2. The continuously variable transmission according to claim 1, wherein said locking means is a one-way clutch and a brake.