KR950002991B1 - Continuously variable transmission - Google Patents

Abstract

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Description

Continuously variable transmission

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a continuously variable transmission, particularly a continuously variable transmission having a continuously variable transmission using a belt (including a chain shape). More particularly, the present invention relates to a continuously variable transmission in which torque torque is increased by a planetary gear device or the like. .

(Prior art)

In recent years, due to the demand for improvement of fuel consumption rate, it has been focused to use a continuously variable transmission having a belt type continuously variable transmission as a transmission of an automobile.

In general, the continuously variable transmission includes a belt continuously variable transmission, a fluid coupling (or electromagnetic powder clutch), a forward / backward shifting device and a reduction gear device, and a differential gear device. Due to the limitation of space and the minimum radius of curvature of the belt, the torque ratio cannot be largely caught, so it is not sufficient to meet the demand for automobiles such as fuel cost and shifting performance in the range of torque ratio by this continuously variable transmission. .

Thus, a continuously variable transmission in which a torque ratio is expanded by combining a planetary gear device is conceived.

As shown in FIG. 23, the continuously variable transmission 1 has a carrier C of the planetary gear device 2 connected to an output portion 5 of the belt type continuously variable transmission 3, and also has a ring gear. Either (e.g., sun gear) of (R) or sun gear (S) is connected to the input shaft (6) via the transmission (8) and the other (e.g., ring gear) to the output member (7), such as a differential gear device. Moreover, the input shaft 6 is comprised between the input part 9 of the continuously variable transmission 3 via the clutch 10 and the brake 11.

Therefore, the rotation of the input shaft 6 is shifted to a predetermined torque ratio through the clutch 10 and the continuously variable transmission 3 when the vehicle is advanced, and the shift rotation is transmitted to the carrier C of the planetary gear device 2. At the same time, it is transmitted directly to the sun gear S through the transmission 8, whereby the rotation of the carrier (C) is amplified and output from the ring gear (R) to the output member (7). In addition, when the vehicle reverses, the brake 11 is actuated and the clutch 10 is disconnected. Accordingly, the rotation of the input shaft 6 is transmitted to the sun gear S of the planetary gear device 2 through the transmission 8 only. The reverse rotation is output from the ring gear R together with the carrier C in the stationary state.

However, in the continuously variable transmission 1 having the planetary gear device 2, the combined torque between the carrier C and the sun gear S is output from the ring gear R, but the ring is compared with the number of teeth of the sun gear S. Due to the large number of teeth of the gear R, the torque to the carrier C transmitted through the continuously variable transmission 3 is again transmitted through the sun gear S and the transmission 8 to the input shaft 6 and the continuously variable transmission ( A torque circulation path propagated to 3) is formed, so that negative torque is transmitted to the sun gear through the transmission 8, so that the continuously variable transmission 3 is larger than the transmission torque to the output member 7. Torque will be charged.

For example, assuming that the sun gear (Z _S) with the ring gear ratio ρ (Z _S / _S R) of the number of teeth (R _S) 0.5,

T _C + T _R + T _S = 0, T _S = ρ T _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

Becomes

In other words, the carrier torque T _C , that is, the torque transmitted from the input shaft 6 through the continuously variable transmission 3, becomes 1.5 times the ring torque torque T _R , that is, the output torque transmitted to the output member 7. .

Therefore, the present continuously variable transmission can increase the torque ratio, but the transmission torque that is applied to the belt-type continuously variable transmission 3 is greatly increased.

As a result, in the system of the continuously variable transmission, excessive torque is applied to the belt type continuously variable transmission which is the least reliable in structure due to frictional transmission, and it is necessary to apply a large side pressure to the pulley to cope with this torque. There is a concern that the durability of the continuously variable transmission may be lowered and the transmission efficiency may be lowered.

(Summary of invention)

Therefore, one object of the present invention is to expand the shift torque ratio by using a planetary gear device as a simple reduction mechanism in a low speed mode and as a split drive mechanism in a high speed mode. It is to provide a continuously variable transmission that prevents the formation of the same torque circulation path.

Another object of the present invention is to improve the durability by increasing the transmission torque of the transmission device with high transmission efficiency while reducing the transmission torque of the continuously variable transmission in the high speed mode with a long service time, and also improves the transmission efficiency. It is to provide a continuously variable transmission.

It is another object of the present invention to provide a continuously variable transmission that enables quick kick-down by switching from a split mechanism to a reduction mechanism.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and the planetary gear device increases torque from a continuously variable transmission (for example, a belt type continuously variable transmission) and transmits it to an output member. A split drive mechanism for synthesizing the torque and transmitting the combined torque to the output member, and selecting means for selectively functioning either of the reduction mechanism and the split drive mechanism, is provided in the low speed mode, for example, Referring to the figure, by operating the engagement means F or B1 constituting the selection means, the third element 20S is stopped to make the deceleration mechanism function, and also, for example, the selection means in the high speed mode. Clutch C2 is connected to transmit torque from the continuously variable transmission 30 to the first element 20R and the third yaw from the transmission 80. By passing the torque to the (20S), it characterized in that the function for the divided driving mechanism.

Detailed Description of the Examples

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of this invention is described based on drawing.

The continuously variable transmission 12 is, for example, as shown in FIG. 1, the gear device 20, the continuously variable transmission 30, the transmission 80, the input 60 shaft, the clutch C2 and the engagement means F. As shown in FIG. And an output member 70 composed of a selection means consisting of B1 and a reduction gear device 71 and a differential gear device 72. The gear device 20 includes a first element 20R interlocked with the output portion 30a of the continuously variable transmission 30, a second element 20c interlocked with the output member 70, and a transmission device 80. ) Is composed of a third element 20S which is interlocked with (), and the third element serves as a reaction force supporting member when the gear device is used as a reduction mechanism, and is engaged by the transmission device (F, B1). ) And the input shaft 60 and this element 20S can be released and connected via the clutch C2.

Specifically, as shown in FIG. 1, the gear unit is composed of a single planetary gear unit 20, and the continuously variable transmission is composed of a belt type continuously variable transmission 30, and the transmission is a chain transmission. Is done. In addition, the first element of the gear device is made of ring (inner) gear 20R, the second element is made of carrier 20C, and the third element is made of sun gear 20S, so that the planetary gear device 20 is The ring gear 20R interlocks with the output portion 30a of the continuously variable transmission 30, the carrier 20C interlocks with the output member 70, and the sun gear 20S passes through the transmission 80. It is interlocked with the low speed one way clutch F and the low speed and backward brake B1 which comprise the engagement means, and is interlocked with the high speed clutch C2.

In addition, the continuously variable transmission 12 is provided with a fluid coupling 13 having a lock-up clutch and a forward reversing switching device 90 composed of a double planetary gear device. The double planetary gear device 90 has its sun gear 90S. Is connected to the input shaft 60, and the carrier 90C is connected to the input portion 30b of the continuously variable transmission 30, and is connected to the input shaft 60 through the forward clutch C1, and also the ring gear 90R. ) Is connected to the reverse brake B2.

Based on the above configuration, each clutch, brake, and general clutch in the continuously variable transmission 12 operate as shown in FIG. 2 at each position. And * indicates that the lock-up clutch CL can be operated properly.

In detail, in the low speed mode L in the D range, the forward clutch C1 is connected and the low speed one-way clutch F operates. In this state, the rotation of the engine crankshaft is transmitted to the input shaft 60 through the lock-up clutch CL or the fluid coupling 13, and is also directly transmitted to the sun gear 90S of the dual planetary gear device 90 and the forward clutch. It is delivered to the carrier 90C via C1. Therefore, the double planetary gear device 90 rotates integrally with the input shaft 60, and transmits the forward rotation to the input portion 30b of the belt type CVT 30, and then to the CVT 30 again. An appropriately shifted rotation is transmitted from the output portion 30a to the first element of the single planetary gear device 20, specifically, the ring gear 20R.

On the other hand, in this state, the third element subjected to the reaction force, specifically, the sun gear 20S is stopped by the low speed one-way clutch F through the transmission 80, so that the rotation of the ring gear 20R is decelerated. As a result, it is output from the second element, specifically, the carrier 20C, and is again transmitted to the axle 73 through the reduction gear device 71 and the differential gear device 72.

In the high speed mode H in the D range, the high speed clutch C2 is connected to the forward clutch C1. In this state, the forward rotation properly shifted to the continuously variable transmission 30 as described above is output from the output unit 30a and input to the ring gear (first element) 20R of the single planetary gear device 20.

At the same time, the rotation of the input shaft 60 is transmitted to the sun gear (third element) 20S of the single planetary gear device 20 through the high speed clutch C2 and the transmission 80, whereby the planetary gear In the apparatus 20, the torques of the ring gear 20R and the sun gear 20S are combined and output from the carrier (second element) 20C.

At this time, since the rotation against the reaction force is transmitted to the sun gear 20S through the transmission device 80, torque circulation is not generated and a predetermined positive torque is transmitted through the transmission device 80. The torque from the synthesized carrier 20S is transmitted to the axle 73 via the reduction gear unit 71 and the automatic gear unit 72.

In the D range, the one-way clutch F frees the reverse torque action type (when the engine brakes), but in the S range, the low-speed and reverse brakes B1 operate in addition to the low-speed one-way clutch F. It also transmits power even when reverse torque is applied.

Moreover, in the R range, the reverse brake B2 operates together with the low speed and the reverse brake B1. In this state, the rotation of the input shaft 60 is input to the belt type CVT 30 as a reverse rotation from the carrier 90C based on the ring gear 90R being fixed in the double planetary gear device 90.

On the other hand, the sun gear 20S of the single planetary gear device 20 is fixed by the operation of the low speed and reverse brake B1, so that the reverse rotation from the continuously variable transmission 30 is decelerated in the planetary gear device 20. And is output to the output member 70.

In the P range and the N range, the low speed and reverse brakes B1 operate.

Next, the present invention is described according to FIG.

The continuously variable transmission 12 has a transmission case 15 in three divisions, and the input shaft 60 and the input shaft 30b of the continuously variable transmission 30 are freely rotated coaxially to the case 15. In addition, the first shaft constitutes the first shaft, and the output shaft 30a and the gear shaft 70a of the continuously variable transmission 30 are freely supported on the same shaft to constitute the second shaft.

Further, on the first axis, the fluid coupling 13 having the lock-up clutch CL, the forward clutch C1, the high speed clutch C2, the low speed and the reverse brake B1, the reverse brake B2, and the low speed one-way clutch ( The control unit 40 which consists of F), the double planetary gear unit 90 and the hydraulic pump 17 which comprise the reverse switching apparatus are provided, and the single planetary gear unit 20 is provided on the 2nd axis. .

In addition, with reference to the control part 40 and the input part, while the output member of the lockup clutch CL and the fluid coupling 13 is engaged with the one end of the input shaft 60, the other end part of the input shaft 60 is engaged. The sun gear 20S of the dual planetary gear device 90 is engaged, and a sleeve 15a fixed to the case 15 is disposed on the input shaft 60. The sprocket 81 is connected to the sleeve 15a via one clutch F, and the sleeve shaft 41 connected to the input shaft 60 is freely supported for rotation. Further, the flange portion 41a, which stands up from the sleeve shaft 41, has a forward clutch C1 provided on one side thereof with the hydraulic actuator 42, and a high speed clutch C2 on the other side thereof. It is installed together with 43.

The high speed clutch C2 has a driven side connected to the boss portion of the sprocket 81, and the boss portion is provided with the hydraulic actuator 45 in the case 15 at a low speed and backward brake B1. )

On the other hand, the driven side of the forward clutch C1 is connected to the carrier 90 of the double planetary gear device 90, and the ring gear 90R of the double planetary gear device 90 is connected with the hydraulic actuator 46 to the case. It is engaged with the reverse brake B2 provided in (15).

The carrier 90C supports the pinion 90P1 meshed with the sun gear 90S and the pinion 90P2 meshed with the ring gear 90R.

In addition, the continuously variable transmission 30 has a first pulley 31, a second pulley 32 and a belt wound around both pulleys, as described in detail in US Patent Application 06-881 / 057 (not disclosed). 33), and both pulleys are composed of fixed sheaves 31a and 32a and movable sheaves 31b and 32b, respectively.

In addition, between the thrust support member 34a and the fixed sheave 31a, which are supported by the first pulley 31 and connected to the input shaft 30b integrally through the plurality of disc-shaped springs 38, respectively. A pressure regulating cam mechanism 34 for imparting an axial force corresponding to the transmission torque is disposed, and the movable sheave 31b slides freely through the ball spline to the boss portion 31c of the fixed sheave 31a. It is supported so that it can move, and the ball screw apparatus 35 is provided in the back part. The ball screw device 35 has its bolt portion 35a rotatably connected to the input shaft 30b axially to the case 15 and through the thrust bearing, and its nut portion 35b. Is connected to the movable sheave 31b to integrally move laterally through the thrust bearing.

On the other hand, the fixed pulley 32a of the second pulley 32 is freely supported on the case 1 by being integral with the output shaft 30a, and the movable sheave 32b is disposed on the output shaft 30a. It is only supported so that it can slide freely through the spline. In addition, a ball screw device 36 is disposed on the rear surface of the movable sheave 32b, and the bolt portion 36a is fixed to the output shaft 30a so that the bolt portion 36a is not rotatable to the case 15 and 30d. ) Is axially immovable through the thrust bearing, and the nut part 36b is connected to the movable sheave 32b axially integrally through the thrust bearing.

The rotation of the operation shaft 37 is freely supported between the first pulley 31 and the second pulley 32.

3 is an exploded view, the operation shaft 37 is drawn on the upper side. In reality, the operation shaft 37 is located at the middle of the input shaft 30b and the output shaft 30a when viewed from the front. A circular gear 37a, a non-circular gear 37b, and a worm wheel 37c are fixed to the operation shaft 37. The wheel 37C is connected to an electric motor controlled by an electric signal from a control unit. The hook 37d which is connected is engaged.

The circular gear 37c is engaged with the wide circular gear 35c fixed to the nut part 35b on the first pulley 31 side, and the non-circular gear 37b is the second pulley 32. Is engaged with a wide non-circular gear 36c fixed to the nut part 36b on the side thereof.

In addition, the single planetary gear device 20 is provided on the storage shaft 70a constituting the second shaft, and the ring gear 20R is adjacent to the flange 30d, and the output shaft of the belt-type continuously variable transmission device 30 is provided. It is connected to 30a. In addition, the sprocket 82 is freely supported on the gear shaft 70a by rotating the sprocket 82 integrally with the sun gear 20S, and the carrier 20c on which the pinion 20P is rotatably supported on the gear shaft 70a is provided. It is fixed.

On the other hand, the silent chain 83 is wound between the sprocket 82 integral with the second gear 20S on the second shaft and the sprocket 81 supported by the low speed one-way clutch F. These sprockets are wound. And a transmission device 80 by a chain.

The gear shaft 70a integrally constitutes the gear 71a to form the output member 70, and the gear 71a meshes with the gear 71c fixed to the intermediate shaft 71b. .

A small gear 71d is formed on the intermediate shaft 71b, and the gear 71b meshes with the ring gear 72a fixed to the differential gear device 72 to form the reduction gear 71. As shown in FIG. Doing. The left and right front axles 73 extend from the differential gear device 72.

Next, the operation of the present embodiment will be described.

The rotation of the engine crankshaft is transmitted to the input shaft 60 through the lock-up clutch CL or the fluid coupling 13, and then to the sun gear 90S of the dual planetary gear device 90 and at the same time as the sleeve shaft 41. Is passed on.

In the D and S ranges, since the forward clutch C1 is connected and the reverse brake B2 is released, the double planetary gear device 90 has a ring gear along with the sun gear 90S and the carrier 90C. 90R is also integrally rotated so that the forward rotation is transmitted to the input shaft 30b of the belt-type continuously variable transmission 30.

Then, the rotation of the input shaft 30b is transmitted to the pressure regulating cam mechanism 34 through the thrust support member 34a, and is operated again through the fixed sieve 31a and the bull spline of the first pulley 31. It is delivered to Eve 31b. At this time, the pressure regulating cam mechanism 34 has an axial force corresponding to the input torque acting on the input shaft 30b acting on the rear surface of the sieve 31a via the disc spring 38, while the other sieve 31b is in a state where the ball screw device 35 is fixed in the longitudinal direction corresponding to the predetermined speed ratio, and thus acts on the rear surface of the sieve 31a through the thrust bearing, while The eve 31b is in a state where the ball screw device 35 is fixed in the longitudinal direction corresponding to the predetermined speed ratio, so that an equal reaction force acts on the rear surface of the sheave 31b through the thrust bearing, thereby The first pulley 31 presses and supports the belt 33 at a pressure corresponding to the pressure torque. In addition, the rotation of the belt 33 is transmitted to the second pulley 32, and again to the output shaft 30a.

In this belt transmission, the motor is controlled based on signals from the sensors such as the throttle opening degree and the vehicle speed, and the operation shaft 37 is rotated through the wheel 37d and the wheel 37c. Then, while the nut part 35b of the ball screw device 35 toward the first pulley 31 rotates through the circular gears 37a and 35c, the second pulley 32 through the non-circular gears 37b and 36c. The nut part 36b of the side ball screw device 36 rotates. Thereby, the nut parts 35b and 36b rotate relative to the bolt parts 35a and 36a which are prevented from rotating in the case 15, and the ball screw devices 35 and 36 move movable through the thrust bearing. 31b and 32b are moved, and the 1st pulley 31 and the 2nd pulley 32 are set to a predetermined effective diameter, and a set torque ratio is obtained. At this time, since both ball screw screws move linearly, a difference occurs between the original movement amount defined by the belt 33 and the second pulley 32 has non-circular gears 37b and 36c. Since it rotates through, the movable sheave is moved in an amount that matches the original movement amount.

Further, the belt pressing pressure by both sieves 31a, 31b and 32a, 32b acts on the case 15 by pulling the input shaft 30b through the thrust bearing on the first pulley 31 side. In the same manner, the second pulley 32 also does not act on the case 15 by pulling the output shaft 30a.

In addition, the rotation of the output shaft 30a of the belt-type continuously variable transmission 30 is transmitted to the ring gear 20R of the single planetary gear device 20, and again to the gear shaft 70a through the carrier 20c. .

In the case of the low speed mode L in the D range, as shown in FIG. 2, the low speed one-way clutch F is in an operating state, and thus the torque transmission from the ring gear 20R to the carrier 20C is applied. Although the sun gear 20S receives a reaction force, the sun gear 20S is prevented from rotating by the low speed one-way clutch F through the transmission 80, and the single planetary gear 20 constitutes a speed reducer. Therefore, the rotation of the output shaft 30a of the belt-type continuously variable transmission 30 is decelerated only in the single planetary gear device 20, and also the gears 71a and 71c, the intermediate shaft 71b, the gear 71d and the mount gear. It is decelerated again through the reduction gear device 71 of 72a, and is transmitted to the left and right front axles 73 through the differential gear device 72.

When the throttle opening degree and the vehicle speed reach a predetermined value, the high speed clutch C2 is connected to the high speed mode by a signal from the control unit. Then, the rotation of the input shaft 60 is transmitted to the belt-type continuously variable transmission 30 and at the same time to the sprocket 81 through the sleeve shaft 41 and the high-speed clutch (C2), and again the silent chain 83 and the sprocket Through 82, it is transmitted to the sun gear 20S of the single planetary gear device 20.

At this time, the sprocket 81 on the input side of the transmission 80 receives a reaction force from the sun gear 20S of the single planetary gear device at the low speed one-clutch F, thereby preventing shift shock due to shifting. Rotation starts smoothly by the connection of the high speed clutch C2, and torque is transmitted to the sun gear 20S. Thereby, the torque continuously variable by the belt-type continuously variable transmission 30 and the torque through the transmission 80 are synthesized in the single planetary gear device 20, and the combined torque is stored from the carrier 20c to the storage shaft 70a. Is delivered).

In addition, it is transmitted to the left and right front axles 73 through the reduction gear device 71 and the differential gear device 72 as in the low speed mode.

Further, in the low speed mode L in the S range, negative torque caused by the engine brake or the like is also received, so that the low speed and reverse brakes B1 are engaged, and the sprocket 81 is prevented from both forward and reverse rotations. In addition, the high speed mode H in the S range is the same as the high speed mode 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, the rotation of the input shaft 60 transmitted to the sun gear 20S of the double planetary gear device 90 is the reverse rotation from the carrier 90c in response to the stop of the ring gear 20R. Delivered to 30b. At this time, since the reaction torque acts as a reverse rotation to the sprocket 81 from the sun gear 20S of the single planetary gear device 20 through the transmission device 80, the low-speed and reverse brakes B1 operate to operate the sprocket 81. Is stopping.

Further, in the torque transmission of the continuously variable transmission 12, as shown in FIG. 4, in the low speed mode L, all the transmission torques are transmitted through the belt type continuously variable transmission 30, but the high speed mode H ), The torque passing through the belt continuously variable transmission 30 and the torque passing through the transmission 80 are shared at a predetermined ratio in accordance with the torque ratio.

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 indicated by the curve L 'in the low speed mode L. As shown in FIG. In the high speed mode, the curve is indicated by the curve H '.

Therefore, the step ratio (low speed mode torque ratio / high speed mode torque ratio) at the time of transition from the low speed mode L to the high speed mode H (or vice versa) becomes as indicated by the high speed S.

Then, when shifting from the low speed mode L (L ') to the high speed mode H (H') (or vice versa), the torque ratio of the belt-type continuously variable transmission 30 is not changed as indicated by the dotted line A. FIG. However, the high speed clutch C2 may be switched only to the connection of the high speed clutch C2, and as indicated by the dotted line B, the torque unit C2 is connected to the control unit at the same time as the high speed clutch C2 so as not to change the torque ratio. By operating the torque ratio of the belt-type continuously variable transmission device 30 in a predetermined amount, the signal may be controlled so that there is no shift shock, or it may be controlled to pass through an arbitrary line between the middle portions of the dotted lines A and B. .

Next, various modifications of the present invention will be described with reference to FIGS. 6 to 22. In addition, about the same part as FIG. 1 and FIG. 3, the same code | symbol is attached | subjected and description is abbreviate | omitted.

6, the single planetary gear device 20 connects the sun gear 20S to the output shaft 30a of the belt-type continuously variable transmission 30, and also connects the ring gear 20R to the gear 83 '. To the input shaft 60 by the high speed clutch C2 through the transmission device 80, and at the same time to the motor input unit 81 which is rotationally stopped by the low speed one-side clutch F or the low speed and reverse brake B1. Is connecting.

In this embodiment, since the step ratio of the low speed L and the high speed H is enlarged, the torque ratio of the continuously variable transmission 12 can be increased, and the torque acting on the belt continuously variable transmission 30 can be reduced. can do.

In FIG. 7, the forward clutch C1 and the high speed clutch C2 are arranged side by side adjacent to the belt-type continuously variable transmission 30, and at the same time, the dual planetary gear device 90 for forward and reverse switching transmission is provided. Adjacent to the fluid coupling 13, and the low speed and reverse brakes B1 and the low speed one-way clutch F are arranged adjacent to the single planetary gear device 20 on the second shafts 30a and 70a. have.

Therefore, in the low speed mode L, the sun gear 20S of the single planetary gear device 20 is directly stopped by the low speed one-side clutch F or the low speed and the reverse brake B1, which is unnecessary for the transmission 80. Load torque does not work.

In FIG. 8, only one of the electrostatic shift switching motors, that is, the double planetary gear device 90 and the forward clutch C1, is provided on one side of the belt-type continuously variable transmission 30 in the first shafts 30b and 60. As shown in FIG. On the other side, low-speed switching transmission means, that is, the high speed clutch C2, the low speed and reverse brakes B1, and the low speed one-way clutch F are arranged.

9, the belt-type continuously variable transmission 30 is disposed adjacent to the fluid coupling 13, and the reverse planetary reversing transmission is provided on the other side of the dual planetary gear device 90 and the forward clutch C1. , The high speed clutch C2, the reverse brake B2, and the single planetary gear device 20, the low speed and reverse brake B1, and the low speed one-way clutch F on the other side of the second shaft side. have.

10 shows a single planetary gear device 20 with the forward and reverse switching transmission means 90, the forward clutch C1, the reverse brake B2 toward the second shaft and the belt type CVT 30. As shown in FIG. On the other side of the.

In FIG. 11, the lock-up clutch CL is separated from the fluid coupling 13, is disposed adjacent to the high speed clutch C2, and the low speed and reverse brakes B1 and the low speed one-way clutch F are shown in FIG. ) Is disposed on the second axis side together with the single planetary gear device 20.

As shown in FIG. 12, a single planetary gear 20 includes a forward shaft C1, a high speed clutch C2, a low speed and reverse brake B1, and a forward and reverse switching transmission means 90 '. It is arranged at the side and outputs power to the output member 70 from the first shaft side. In the present embodiment, the forward and reverse switching transmission means is composed of the reverse clutch C3 through the idler gear 91. Therefore, in the R range, the rotation of the input shaft 60 is performed by the gear 92, the idler gear 91, It is transmitted to the gear 95 via the gear 93 and the reverse clutch C3, and is again transmitted to the output member 70.

As shown in FIG. 13, the output shaft 30a of the belt-type continuously variable transmission 30 is connected to the sun gear 20S of the single planetary gear device 20, and the ring gear 20R, as shown in FIG. Although connected to the transmission 80, the transmission 80 is made of a chain (83).

Similarly to FIG. 14, the output shaft 30a of the belt-type continuously variable transmission 30 is connected to the sun gear 20S of the single planetary gear device 20, and the ring gear 20R is connected to the transmission 80. At the same time as in Fig. 11, the low speed one-side clutch F and the low-speed and reverse brake B1 are disposed on the second shaft side together with the single planetary gear device 20, and the lock-up clutch CL is fluidly coupled. It is separated from (13).

In FIG. 15, the low speed changeover transmission means and the forward reverse changeover transmission means are integrally formed, have two sun gears 21S1 and 21S2, and one sun gear 21S1 is a belt type continuously variable transmission. It is connected to the output shaft 30a of the apparatus 30, and the other sun gear 21S2 is connected to the transmission 80, and supports two pinions 21P1 and 21P2 in parallel with the carrier 21c, It is made up of a revolution type planetary gear device 21 made of one ring gear 21R again, and a forward brake B3 which is released in the R range is provided.

Therefore, in the low speed mode L, the rotation of the output shaft 30a of the belt-type continuously variable transmission 30 is transmitted from the first sun gear 21S1 to the first pinion 21P1, and the first pin is made of long pinion. The pinion 21P1 is engaged with the second pinion 21P2 to rotate this pinion, and the second pinion 21P2 is made of the low speed one-way clutch F or the low-speed and reverse brake B1, which are held in a stopped state. Engages with the two-wire gear 21S2, whereby the carrier 21C rotates to transmit the deceleration rotation to the output member 70. Moreover, in the high speed mode H, the 2nd transmitted from the input shaft 60 via the high speed clutch C2 and the transmission 80 with rotation of the 1st sun gear 21S1 from the belt continuously variable transmission 30. In addition, in FIG. Rotation of the sun gear 21S2 is given to the revolution type planetary gear device 21. As a result, the combined rotation through the first and second pinions 21P1 and 21P2 is output from the carrier 21C and transmitted to the output member.

Further, in the R range, the forward brake B3 is released to free the second sun gear 21S2, and the reverse brake B2 engages to fix the ring gear 21R, thereby rotating the output shaft 30a. The output is reversed from the carrier 21c.

16, the output shaft 30a of the belt-type continuously variable transmission device 30 is composed of two single planetary gear devices 23 and 25 in which low and high speed changeover transmission means and reverse changeover transmission means are arranged side by side. ) Is connected to the sun gear 23S of the first planetary gear device 23, and is connected to the ring gear 25R of the second planetary gear device 25, and the ring gear of the first planetary gear device 23 23R and the carrier 25C of the second planetary gear device 25 are connected to each other and to the output member 70, and the carrier 23C of the first planetary gear device 23 is the reverse brake B2. In addition, the sun gear 25S of the second planetary gear device 25 is connected to the transmission device 80.

Therefore, in the low speed mode L, the rotation of the output shaft 30a of the belt-type continuously variable transmission 30 is transmitted to the ring gear 25R of the second planetary gear device 25, and again, the low speed one-way clutch F. Alternatively, it is transmitted to the output member 70 as decelerating rotation from the carrier 25C on the basis of the sun gear 25S in the stationary state with the low speed and reverse brake B1.

Further, in the high speed mode H, rotation through the transmission 80 is transmitted to the sun gear 25S, which is combined with the rotation of the ring gear 25R from the belt-type continuously variable transmission 30 to output the output member ( 70).

In addition, in the R range, the rotation of the belt-type continuously variable transmission output shaft 30a is transmitted to the sun gear 23S of the first planetary gear device 23, and again rotates through the pinion of the carrier 23c in the stopped state. Is transmitted to the ring gear 23R, and in the second planetary gear device 25, since the sun gear 25S is freed by the release of the forward brake B3, the rotation from the ring gear 23R is It is output to the output member 70 through the carrier 25C.

In FIG. 17, there are two single planetary gear units 26 and 27 in which low speed, high speed gears and reverse gears are arranged side by side, and a belt type CVT output shaft 30a is formed of a first planetary gear. It is connected to the ring gear 26R of the gear device 26 and the sun gear 27S of the second planetary gear device 27, and the carrier 26C of the first planetary gear device 26 and the second planetary gear device ( The carrier 27C of the 27 is connected, the sun gear 26S of the first planetary gear device 26 is connected to the transmission device 80, and the ring gear 27R of the second planetary gear device 27. Is connected to the output member 70.

Therefore, in the low speed mode L, the rotation of the output shaft 30a of the belt-type continuously variable transmission 30 is based on the sun gear 26S stationary from the ring gear 26R of the first planetary gear device 26. The rotation of the sun gear 27S from the output side 30a and the rotation of the carrier 27C from the carrier 26C are combined to be transmitted to the carrier 26C, and the second planetary gear device 27 combines the ring gear ( 27R) is outputted to the output member 70.

In the high speed mode H, rotation through the transmission 80 is transmitted to the sun gear 26S of the first planetary gear device 26, and the ring gear from the belt-type continuously variable transmission output side 30a. Combined with the rotation with the 26R and output from the carrier 26C, in the second planetary gear device 27, the rotation of the sun gear 27S from the output side 30a and the carrier 27C from the carrier 26C. The rotation of) is synthesized and output to the output member 70.

In the R range, the carrier 27C of the second planetary gear device 27 is at a stationary partner, and the rotation of the sun gear 27S by the output side 30a is reversely output to the ring gear 27R via the pinion. And is transmitted to the output member 70a.

In FIG. 18, the low-speed changeover transmission means is composed of a double planetary gear device 120, and the planetary gear device 120 is supported by the pinions 120P1 and 120P2. It is connected to the output side 30a of the continuously variable transmission 30, and the sun gear 120S is made up of an idler 83 'and is connected to the transmission 80, and the ring gear 120R is connected to the output member ( 70).

Therefore, in the low speed mode L, the rotation of the output side 30a of the continuously variable transmission 30 is based on the sun gear 120S which is stationary from the carrier 120C of the dual planetary gear device 120. 120R) and this deceleration rotation is transmitted to the output member 70 again.

In the high speed mode H, the rotation from the transmission 80 is transmitted to the sun gear 120S, and the rotation with the carrier 120C from the continuously variable transmission output side 30a is the double planetary gear device ( Synthesized at 120, this composite rotation is transmitted from the ring gear 120R to the output member 70.

In FIG. 19, a low speed motor and a high speed electric field are used for separate transmission means. That is, the deceleration mechanism 121 possible in the low speed mode L includes a small gear 121a, a standby gear 121b meshed with the small gear 121a, and a transmission gear connecting the standby gear 121b to the output member 70. The splitter synchronizing tool 122 which consists of the side 121c and functions in the high speed mode H consists of a single planetary gear device. The continuously variable transmission output side 30a can be connected to the small gear 121a through the low speed and reverse clutch C4, and the small gear 121a is interlocked through the low speed one-way clutch F. And the ring gear 122R of the single planetary gear device 122.

The carrier 122C of the gear device 122 is connected to the output member 70, and the sun gear 122S is connected to the transmission 80 through the high speed clutch C2.

Therefore, in the low speed mode L, the rotation of the output side 30a of the valve-type continuously variable transmission 30 is performed through the low speed one-way clutch F (D range), or through the low speed and the reverse clutch C4 (S). Range) is transmitted to the small gear 121a, and again to the ejection member 70 through the standby gear 121b and the transmission shaft 121c constituting the reduction mechanism of the series transmission system.

At this time, rotation is also transmitted to the ring gear 122R of the planetary gear device 122 constituting the split drive mechanism to the output shaft 30a, but since the high speed clutch C2 is released, the ring gear 122R is idle. It does not function as a transmission.

Moreover, in the high speed mode H, it is transmitted from the continuously variable transmission output side 30a to the ring gear 122R of the planetary gear device 122 which comprises a division drive mechanism, and is transmitted by the connection of the high speed clutch C2. It is transmitted from the device 80 to the sun gear 122S, whereby the synthesized rotation is transmitted to the output member 70 as shown in FIG. At this time, the small gear 121a is also rotated through the gears 71a and 71b, the transmission side 121c and the standby gear 121b, but the gear 121a rotates only by the low speed one-way clutch F and output side ( There is no connection to 30a).

Further, at the time of reversing, the reverse rotation is transmitted to the continuously variable transmission 30 by the double planetary gear device 90 constituting the forward / backward switching means based on the operation of the reverse brake B2, and again the low speed and reverse clutch C4. The reverse rotational output from the continuously variable transmission 30 is transmitted to the output member 70 through the reduction mechanism 121 by the connection of.

In FIG. 20, the speed reduction mechanism of the low speed transmission system and the split drive mechanism of the high speed transmission system use separate transmission means, and the reduction mechanism consists of a single oil-based gear device 123. As shown in FIG. The single planetary gear device 122 constituting the split drive mechanism is the same as that of FIG. 19 as described above.

The single planetary gear device 123 has a small gear 121 'whose ring gear 123R is connected to the output portion 30a of the continuously variable transmission, and the carrier 123c is linked to the output member 70. The sun gear 123S is connected to the low speed one-way clutch F and the low speed and the reverse brake B1.

Therefore, in the low speed mode L, the rotation of the continuously variable transmission output side 30a is in a stopped state based on the action of the low speed one-side clutch F (D range) or the low speed and reverse brake B1 (S range). It is transmitted as a deceleration rotation from the ring gear 123R to the carrier 123C by the sun gear 123S, and again outputs 70 through the small gear 121a ', the standby gear 121b', and the transmission shaft 121c '. Is delivered).

Further, in the high speed mode H, the high speed clutch C2 is connected, and the planetary gear device 122 constituting the split drive mechanism is electrically driven with the continuously variable transmission output side 30a as in the embodiment shown in FIG. The rotation of the device 80 is synthesized and transmitted to the output member 70.

At this time, rotation is also transmitted to the carrier 123C of the planetary gear device 123 constituting the reduction mechanism through the gears 71a and 71b, the transmission shaft 121c ', and the gears 121b' and 121a ', but the one-way clutch (F) becomes free and does not sell.

At the time of reversing, on the basis of the operation of the reverse brake B2 and the low speed and reverse brake B1, reverse rotation of the continuously variable transmission output side 30a is carried out through the planetary gear device 123 constituting the reduction mechanism. 70).

In FIG. 21, the planetary gear device 125 made of a bevel gear device is used as the low-speed switching electric transmission means, and the rest of the structure is the same as the embodiment shown in FIGS. The bevel gear device 125 has a left bevel 125L on the two-speed transmission output side 30a, a right bevel 125R on the transmission 80, and a center bevel 125c on the output member 70. Are connected to each other.

Therefore, in the low speed mode L, the rotation of the continuously variable transmission output side 30a is based on the left bevel 125R on the basis of the right bevel 125R in the stopped state by the low speed one-way clutch F or the low speed and reverse brake B1. 125L) is transmitted while decelerating to the center bevel 125c, and is again transmitted to the output member 70.

In the high speed mode, the rotation of the left bevel 125L from the output side 30a and the rotation from the transmission 80 based on the connection of the high speed clutch C2 are combined in the bevel gear device 126. It is transmitted to the output member 70.

As shown in FIG. 22, the second side will be composed of multiple sides, and will be compactly constructed. That is, the output side 30a of the continuously variable transmission 30 is hollow and connected to the ring gear 20R of the single planetary gear device 20, and the carrier 20C is connected to the output member 70, and again. The sun gear 20S is connected to the low speed unidirectional clutch and the low speed and reverse brake B1 through the sleeve side 126 which is fitted on the hollow side 30a, and is connected to the transmission 80.

The output member 70 includes a planetary gear reduction gear device 71 and a differential device 72 which are coaxial with the second pulley 32 and the single planetary gear device 20 of the continuously variable transmission 30. The left front axle 73L extends through the hollow shaft 30a and the second pulley 32 from this differential device 72, and the right front axle 73R extends to the right. .

In addition, the reduction gear device 71 has its sun gear 71S connected to the carrier 20C of the single planetary gear device 20, the ring gear 71R is fixed, and the carrier 71C is the differential device 72. ) Is entered.

As mentioned above, the effect based on each Example is as follows.

Since the gear device 20 constitutes a simple deceleration mechanism in the low speed mode L of the continuously variable transmission 12 and a split drive mechanism in the high speed mode H, the torque ratio width as the whole continuously variable transmission 12 is formed. In addition to improving fuel cost and shifting performance, the high speed mode (H) used for normal driving is longer than the low speed mode (L) used for acceleration. In this long high speed mode H, the transmission torque applied to the continuously variable transmission 30 is greatly reduced, and the rotation speed thereof also decreases, so that durability can be improved, and in this high speed mode H, friction transmission means Torque is also applied to the continuously variable transmission 30 made of gears or chains and has a high transmission efficiency, so that the transmission efficiency can be improved, and the split drive mechanism Quick kickdown is possible by switching to the reduction mechanism.

Further, the reduction mechanism and the split drive mechanism can be constituted by one planetary gear device, and can be configured compactly.

In particular, when the V-belt continuously variable transmission 30 is used as the continuously variable transmission, the load applied to the belt can be reduced without reducing the torque capacity of the entire transmission 12, so that the practical use of the continuously variable transmission using the belt can be reduced. It is easy to solve the problem of impaired belt durability.

Further, the reaction force supporting member when the reduction gear mechanism is connected to the transmission device 80 of the planetary gear device 20 and the third element connected to the engagement means (low speed one-clutch, low speed and reverse brake B1). In this configuration, the torque circulation path is not formed when the planetary gear device 20 is divided into a drive mechanism, and the torque imposed by the belt continuously variable transmission 30 is reduced, thereby providing a compact and large torque transmission capacity. It is possible to realize the continuously variable transmission 12 having a high durability and sufficient durability.

In addition, the first element of the single planetary gear device 20 interlocked with the output portion 30a of the belt-type continuously variable transmission 30 is a ring gear 20R, and the second element interlocks with the output member 70. Is the carrier 20C, the carrier 20C interlocked with the transmission 80, and the element of FIG. 3 interlocked with the transmission 80 is the sun gear 20S, the low speed mode L And the step ratio of the high speed mode H can be set relatively small, and the continuously variable transmission 12 corresponding to the required torque ratio can be obtained.

In addition, if the first element is the sun gear 20S of the single planetary gear device 20, the second element is the carrier 20C, and the third element is the ring gear 20R, It is possible to obtain a continuously variable transmission 12 having a wide torque ratio by increasing the step ratio between the L and the high speed mode H, and at the same time, increasing the torque burden ratio of the transmission 80 to greatly reduce the load acting on the belt. You can.

Further, when the means for engaging the third element 20S or 20R is the one-way clutch F and the low speed and backward brake B1, the one-way clutch F eliminates the shift shock caused by the shift, thereby smoothly shifting. At the same time, the low speed and reverse brake B1 can reliably cope with the reverse torque transmission of the engine brake and the like.

Further, when the engaging means (low speed one-way clutch F, low speed and reverse brake B1) is disposed on the first shaft coaxial with the first pulley 31 of the belt-type continuously variable transmission 30, another control mechanism ( In addition to the arrangement of the forward clutch C1 (or the forward brake B3, the high speed clutch C2, and the reverse brake B2), the compact configuration is reduced in the axial dimension and the control mechanisms are simply arranged. It is possible to simplify the configuration of the flow path F and the like and to improve the maintainability.

Further, when the engaging means (low speed one-way clutch F, low speed and reverse brake B1) is disposed on a second shaft coaxial with the second pulley 32 of the belt-type continuously variable transmission 30, the engaging means is provided. When the planetary gear device 20 operates as the reduction gear mechanism, the reaction force does not act on the transmission device 80, and the durability of the transmission device can be improved.

1 is a schematic diagram showing a continuously variable transmission of the present invention.

2 is an operation diagram of each element at its respective position,

3 is a cross-sectional view of a continuously variable transmission embodying the present invention,

4 is a relationship between the torque ratio and the transmission torque sharing rate,

5 is a relationship between the step ratio and the transmission torque ratio with respect to the belt torque ratio,

6 to 22 are schematic views of different embodiments, respectively.

23 is a schematic view of a conventional example.

* Explanation of symbols for main parts of the drawings

B1: Low speed and reverse brake B2: Reverse brake

C1: Forward Clutch C2: High Speed Clutch

CL: Lock-up clutch F: Engagement means

12: continuously variable transmission 13: fluid coupling

15a: sleeve 20, 23, 25: single planetary gear device

30: continuously variable transmission 60: input shaft

7Q: Output member 71: Reduction gear device

72: differential gear device 73: axle

80: electric device 90: reverse switching device

Claims (8)

And an input member, a continuously variable transmission for continuously rotating the input member, a planetary gear device for inputting torque from the continuously variable transmission, and an output member for inputting torque from the planetary gear device. In a continuously variable transmission, the planetary gear device has at least first, second and third elements, the first element is interlocked with an output of the continuously variable transmission, and the second element is connected to the output member. And the clutch is disposed between the third element and the input member, and the clutch is disposed between the third element and the input member to operate the engagement means in the low speed mode. To increase the torque from the continuously variable transmission to the output member and to reduce the torque to the output member. To connect the continuously variable transmission to the planetary gear set characterized in that the torque and the synthesized torque, and also the synthesis of the torque from the input member from the continuously-variable transmission device to a separate driving mechanism for transmitting to the output member. 2. The continuously variable transmission as claimed in claim 1, wherein the continuously variable transmission is a belt type continuously variable transmission comprising first and second pulleys having two sheaves each of which can change an effective diameter, and a belt wound around the both pulleys. Continuously variable transmission. 3. A continuously variable transmission as claimed in claim 2, wherein said engaging means is disposed on a first shaft which is arranged on a first pulley of said belt-type continuously variable transmission. 3. The continuously variable transmission as claimed in claim 2, wherein said engaging means is disposed on a second shaft which is arranged on a second pulley of said belt-type continuously variable transmission. The continuously variable transmission as claimed in claim 1, wherein the third element of the planetary gear device is a reaction force supporting member when forming the deceleration mechanism. 6. The continuously variable transmission as claimed in claim 5, wherein the planetary gear device is a single planetary gear device, the first element is a ring gear, the second element is a carrier, and the third element is a sun gear. . 6. The continuously variable transmission as claimed in claim 5, wherein the planetary gear device is a single planetary gear device, the first element is a sun gear, the second element is a carrier, and the third element is a ring gear. . The continuously variable transmission according to Claim 1, wherein said engagement means is a one-way clutch and a brake.

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