KR100328382B1 - Continuously Variable Transmission - Google Patents

Abstract

The present invention relates to a continuously variable transmission configured to shift the power input to the input shaft in accordance with the load on the output shaft in the state in which all the gears are connected, the reverse drive is also made in a simple manner.

Its configuration consists of a transmission system that receives the power generated by the engine and shifts it to the output shaft, a speed adjustment system that automatically adjusts the rotation ratio corresponding to the load state of the output shaft, and a forward / reverse switching system.

Due to the characteristics of the configuration, it is possible to continuously vary the power input through the input elements selected from the planetary gear set, including the planetary gear set and the forward and reverse switching system.

Operationally, the connection between the output shaft and the transmission system allows the impeller to transmit a rotation slower than the input rotational force.

Therefore, the rotational force transmitted to the impeller is characterized in that it is always configured to transmit a larger rotational force than the input torque.

In effect, it can be shifted with great propulsion, good performance, smooth and quiet running as well as stepless driving.

Description

Continuously Variable Transmission

The present invention relates to a continuously variable transmission, and more particularly, to a continuously variable transmission configured to transmit power to an output shaft while power is inputted to an input shaft through a transmission system and shifted according to a load state applied to the output shaft.

In general, a summary of the configuration of the shifting system, the shifting adjustment system, and the forward and reverse switching system, the shifting system is based on a planetary gear unit, which includes an input shaft, an output shaft, and two sets of planetary gears (including sun gear and carrier). In addition, it is configured to transmit the input power to the output shaft through the selected input element simultaneously with the proper connection combination between the components of the gear set.

The shift control system uses an improved torque converter that is an application-improved torque converter of a known automatic transmission. For convenience of description, the gear chain impeller and the terms related to the components used in the existing torque converter are described. It consists of a driven chain turbine, a stator for increasing torque, a connecting shaft connected to the transmission system, an adjusting shaft, and a fixed shaft for fixing the stator.

The forward and reverse switching system uses the synchronizer used in the existing manual transmission, and it is configured to allow the forward and reverse to be unauthorized by an appropriate connection combination between the element selected by the synchronizer and the transmission system.

In particular, since the shift adjustment system and the shift system are described in Korean Patent Application No. 96-56980 (hereinafter referred to as an earlier application), the technical contents of the prior application are referred to.

By the way, the conventional transmission device is shifted by selecting a gear train configured according to a predetermined gear ratio, and when shifting, troublesome and very careful operation of selectively connecting a gear of a gear train is required.

In addition, the belt type continuously variable automatic transmission, which is used in part with the conventional automatic transmission, is similar in structure and is very complicated and requires a lot of cost in manufacturing, and in the belt type continuously variable automatic transmission, due to belt wear, noise and slip phenomenon, There was an inconvenience that could not be used and used only within a limited output capacity range.

Therefore, the present invention has been made in view of the various problems as described above, the object of the present invention is to respond quickly to changes in the load, without using complicated mechanisms, the rotational force can be transmitted smoothly, as well as a simple configuration By continuously shifting forward and backward, the present invention provides a continuously variable transmission that can reduce manufacturing costs and improve durability.

In particular, the forward and reverse switching system does not use hydraulic clutches or brakes by using the synchronizer mechanism used in the existing manual transmissions, which can achieve a great cost in terms of elimination of complicated hydraulic devices. .

In order to achieve the above object, the present invention provides a transmission system that receives power generated from an engine and shifts the transmission to an output shaft, a shift adjustment system capable of automatically adjusting a rotation ratio corresponding to a load state of the output shaft, and forward and backward switching. The present invention provides a continuously variable transmission that is configured to continuously and continuously move forward and backward with a system.

1 is a schematic view showing a first embodiment of a continuously variable transmission according to the present invention;

FIG. 2 is an operation diagram in which the continuously variable transmission in FIG. 1 shows a neutral state; FIG.

3 is an operation diagram showing a state in which the continuously variable transmission in FIG. 1 is advanced;

4 is an operation diagram showing a reverse state in the continuously variable transmission in FIG.

5 is a schematic diagram showing a second embodiment of a continuously variable transmission according to the present invention.

* Explanation of symbols for main parts of the drawings

10: shift control system 12: input shaft

14: connecting shaft 16: adjusting shaft

18: impeller housing 20: impeller

22: turbine 24: stator

26: fixed shaft 28: one-way clutch

110: shifting system 112: input sun gear

114: first planetary gear 116: second planetary gear

118, 120: Output carrier 122: Adjustment sun gear

124: output carrier shaft 126: output shaft

210, 310: Forward and reverse switching system 212: Reverse connecting gear

214: Synchronizer Cone 216: Reverse transmission gear

218: forward transmission gear 220: idle gear shaft

222: idle gear 224: forward coupling gear

226: synchronizer cone 228: clutch hub

230: sleeve 232, 234: synchronizer ring

312: reverse connection gear 316: reverse transmission gear

318: forward transmission gear 320: children gear shaft

322: idle gear 324: forward gear

326: reverse clutch 328: forward clutch

In order to achieve the above object, the present invention corresponds to a load state applied to the output shaft receives the power generated from the engine, and also transmits power to the shift control system comprising an impeller, a turbine and a stator and loads the output shaft A continuously variable transmission having a transmission system including an output carrier, an input sun gear and an adjustment sun gear to adjust at a rotation ratio corresponding to a state, comprising: a reverse connecting gear rotatably installed on an output carrier shaft, and the reverse connecting gear. A forward synchronizer cone formed on the output carrier shaft and rotatably mounted on the output carrier shaft, a forward transmission gear integrated with the output shaft while engaging with the backward connecting gear, and a forward direction integrally formed with the output shaft at a distance required from the reverse transmission gear. On the gears of the child gear while engaging the transmission gears and the above-mentioned forward transmission gears. A rotatable idler gear, a forward connecting gear meshing with the above idle gear, a synchronizer cone formed integrally with the forward connecting gear at a required distance, and being positioned between the above-described synchronizer cones and being output. Provides a continuously variable transmission comprising a clutch hub integrated with a carrier shaft, a sleeve installed outside the clutch hub, and a synchronizer ring positioned on both sides of the clutch hub and freely rotating on the synchronizer cone. do.

(Example)

Hereinafter, with reference to the accompanying drawings will be described with respect to the continuously variable transmission system consisting of the shift control system, the shift system and the forward and reverse switching system as follows.

1 is a schematic view showing a first embodiment of a continuously variable transmission according to the present invention, FIG. 2 is an operation diagram showing a neutral state of the continuously variable transmission in FIG. 1, and FIG. 3 is a continuously variable transmission in FIG. 4 is an operation diagram showing a forward state, and FIG. 4 is an operation diagram showing a reverse state in the continuously variable transmission in FIG.

First, the first embodiment of the present invention 100, which is composed of the shift adjustment system 10, the shift system 110, and the forward / backward switching system 210 connected thereto, will be described with reference to the accompanying drawings.

The shift adjustment system 10 applies a torque converter of an automatic transmission, which is a known device. In a typical automatic transmission, power generated in an engine is directly transmitted to the input shaft of the transmission via a torque converter. Power generated in the engine is decelerated through the planetary gear set, which is the transmission system 110, through the input shaft, and thus the increased rotational force is transmitted to the impeller.

That is, the torque converter of the conventional automatic transmission has a power transmission function that receives the power generated from the engine and directly transmits it to the input shaft of the transmission, while the shift adjustment system 10 of the present invention has two points, namely, one. It is characterized by adjusting the speed ratio appropriately for the drive resistance, and the other is that power through the shift adjusting system is transmitted to the output shaft.

Next, the configuration of the shift adjustment system 10 will be described in detail.

As shown in Fig. 1, a hollow connecting shaft 14 is provided coaxially on the input shaft 12 and a hollow adjusting shaft 16 is provided coaxially on the connecting shaft 14.

The impeller housing 18 is integrally connected with the connecting shaft 14 and the impeller 20 is integrally connected with the impeller housing 18.

The turbine 22 is installed integrally with the adjusting shaft 16 to face the impeller 20, and the stator 24 is positioned between the impeller 20 and the turbine 22, and the stator 24 is described above. A hollow fixed shaft 26 is provided coaxially with the adjusting shaft 16 inside the inner side of the inner side thereof, and a one-way clutch 28 is inserted between the fixed shaft 26 and the stator 24 so that the stator 24 is reversed. Prevents rotation

As shown in FIG. 1, the transmission system 110 of the first embodiment of the present invention is provided with an input sun gear 112 integrally with an input shaft 12 into which engine power is input, and the input sun gear 112 described above. The outer side of the first planetary gear 114 is engaged with each other, and the second planetary gear 116 is integrally formed with the first planetary gear 114 described above.

The first planetary gear 114 and the second planetary gear 116 are installed so as to rotate freely in the output carriers 118 and 120 and have different gear ratios. The second planetary gear ( 116 to be decelerated through the adjustment line gear 122, the adjustment line gear 122 is formed integrally with the connecting shaft (14).

Meanwhile, an output carrier shaft 124 is provided coaxially with the input shaft 12, and the output carrier shaft 124 is integrally connected with the output carriers 118 and 120.

Next, the forward and backward switching system 210 in the first embodiment of the present invention will be described. In the present invention, it is possible to achieve the forward and backward by using the synchronizer used in the existing manual transmission.

As shown in FIG. 1, as shown in FIG. 1, the output carrier shaft is formed integrally with the reverse coupling gear 212 rotatably installed on the output carrier shaft 124 and the reverse coupling gear 212. The synchronizer cone 214 rotatably installed on the 124, the reverse transfer gear 216 integral with the output shaft 126 while engaging with the reverse connecting gear 212, and the reverse transfer gear 216. A forward transmission gear 218 integrally formed with the output shaft 126 at a predetermined distance from the output shaft 126, and an idle gear 222 rotatably installed on the idle gear shaft 220 while engaging with the forward transmission gear 218. And, the forward connecting gear 224 meshing with the idle gear 222, the synchronizer cone 226 integrally formed with a required distance from the forward connecting gear 224, and the above-described synchronizers. A clutch located between the cones 214 and 226 and integral with the output carrier shaft 124 The tooth hub 228, the sleeve 230 provided outside the clutch hub 228, and the synchronizer rings 232 and 234 positioned on both sides of the clutch hub 230 and free to rotate on the synchronizer cones 214 and 226. Install).

The operation method according to the shift state (neutral, forward, backward) of the continuously variable transmission of the present invention configured as described above and the power transmission process according thereto will be described as follows.

Prior to the description, the continuously variable transmission of the present invention can be used in any mechanism for shifting and outputting a driving force of automobiles and industrial machines, and the like.

In addition, for convenience of explanation, when viewed from the left side of the drawing, the direction that rotates in the counterclockwise direction is the direction of the input axis, and the same direction as the direction of the input axis is defined as the ↑ direction (or A direction) in each drawing. The direction opposite to the direction is defined as the ↓ direction (or B direction) .When rotating after stop (acceleration state), it is indicated as 0 · ↑ (or 0 · ↓), and after rotating (stop state) as ↑ · 0 ( Or ↓ · 0), and describe the state in which all the rotating bodies rotate together with the input rotational speed ↑ · 1 (or ↓ · 1) without rotating the planetary gear after rotation. do.

First, the neutral state is a state in which the sleeve 230 of the forward and backward switching system is in the 'N' position, and the engine power is idling as shown in FIG. 2 without rotating the output shaft 126.

That is, since the sleeve 230 is in the 'N' position, the connection between the synchronizer cone 214 integral with the output carrier shaft 124 and the clutch hub 228 integral with the output shaft 126 is blocked. Since it is a state, power is not transmitted.

When the engine power is input, the input shaft 12 rotates while the input sun gear 112 integrally formed with the input shaft 12 also rotates in the same direction A, and the first planetary gear 114 meshed with the input sun gear 112 is It rotates in the B direction opposite to the rotation direction of the input sun gear 112.

The second planetary gear 116 integral with the first planetary gear 114 is also rotated in the same direction as the first planetary gear 114 in the B direction, and the regulating sun gear meshed inside the second planetary gear 116. Reference numeral 122 rotates in the direction A opposite to the rotation direction of the second planetary gear 116.

Of course, the connecting shaft 14 integrally connected with the adjusting sun gear 122, the impeller housing 18 integral with the connecting shaft 14, and the impeller 20 integral with the impeller housing 18 are the same A. Direction of rotation.

Due to the flow of the fluid, the turbine 22 facing the impeller 20 also rotates in the same direction A, and the adjustment shaft 16 integrally connected to the turbine 22 also rotates in the direction A and integrally connected to the output carrier ( 118 and 120 also rotate in the A direction.

The output carrier shaft 124 integrated with the output carriers 118 and 120 also rotates in the same A direction, and the backward connecting gear 212 integrally formed with the output carrier shaft 124 also rotates in the same A direction and is engaged therewith. The reverse transmission gear 216 and the output shaft 126 integral with the reverse transmission gear 216 are rotated.

At this time, the forward transmission gear 218 integrally formed on the output shaft 126 is rotated by meshing with the idle gear 222, meshes with the idle gear 222 and is connected to the synchronizer cone 226. The synchronizer cone 226 also rotates in the B direction while the forward connecting gear 224 rotates. In this state, the sleeve 230 is in the 'N' position, and thus, the output shaft 126 is not rotated. .

On the other hand, in the forward state, the clutch hub integral with the output shaft 126 is operated by operating the output carrier shaft 124 integrated with the output carriers 118 and 120 and the forward / reverse switching system 210 provided between the output shaft 126. The sleeve 230 on 228 is moved in the 'D' direction, and the sleeve 230 is connected to the synchronizer cone 214 integrated with the output carrier shaft 124.

When the sleeve 230 and the synchronizer cone 214 are connected, the power is transmitted to the output shaft 126 through the forward connecting gear 224 and the idle gear 222, the output carrier shaft 124 In the state where power from the engine is applied, the output shaft 126 is in a state where the vehicle is stopped, and thus the load due to the initial driving is applied.

At this time, when the engine power is input to the input shaft 12, the input line gear 112 formed integrally with the input shaft 12 is rotated in the direction A, the same direction as the input shaft 12, and meshed with the input line gear 112. The first planetary gear 114 is in the opposite direction to the input sun gear 112 because the output carriers 118 and 120 are stopped by the load of the output shaft 126 connected through the forward and backward switching system 210. Rotate in the B direction.

The second planetary gear 116 integrally connected to the first planetary gear 114 by the rotation of the first planetary gear 114 rotates in the B direction while the adjustment sun gear 122 engaged with the inner gear 122 is rotated in the A direction. To decelerate and rotate.

That is, the output shaft 126, the output carrier shaft 124, the output carriers 118 and 120, the adjustment shaft 16 and the turbine 22 are stopped by the operation of the forward and backward switching system 210. The rotational force transmitted to the first planetary gear 114 through the input sun gear 112 is transmitted to the adjustment sun gear 122 in a state where the rotational force is increased by the gear ratio via the second planetary gear 116 connected integrally.

In addition, an increased rotational force is also provided to the connecting shaft 14 integrally connected with the adjusting sun gear 122, the impeller housing 18 integrally connected with the connecting shaft 14, and the impeller 20 integral with the impeller housing 18. In addition to being transmitted, the motor is decelerated in the direction A and rotated.

At this time, since the turbine 22 is stopped by the load of the output shaft 126 by the operation of the forward and backward switching system 210, a very large rotation difference occurs between the impeller 20 and the turbine 22. .

Due to the characteristics of the torque converter, the multiplied rotational force of the impeller 20 is transmitted to the turbine 22, so that the rotational force transmitted to the turbine 22 is integrally connected to the adjustment shaft 16 and the output carriers 118 and 120, and It is transmitted to the output shaft 126 through the output carrier shaft 124, the forward connection gear 224, the idle gear 222 integral with one output carrier 118, 120, the resistance and the turbine acting on the output shaft 126 When the rotational force transmitted to 22 is balanced, the output shaft 126 is driven, which is a low speed start state.

In this state, increasing the rotation of the engine increases the rotation difference between the impeller 20 and the turbine 22, thereby increasing the rotational force transmitted to the turbine 22, and the rotational force transmitted to the turbine 22 is output shaft 126. The output shaft 126 is rotated until the rotational force of the turbine 22 transmitted from the impeller 20 is in equilibrium with the resistance applied to the turbine 22 when the load is greater than the resistance acting on the turbine 22 by the load of. Will accelerate.

When the output shaft 126 is accelerated, that is, when the speed of the vehicle is faster, the load on the output shaft 126, which is the resistance on the road surface, is reduced, so that the resistance acting on the turbine 22 is also reduced.

When the resistance applied to the turbine 22 is reduced, the rotational difference between the impeller 20 and the turbine 22 is reduced until equilibrium with this resistance.

Accordingly, the rotation of the turbine 22 is increased in the direction A, which is the same direction as the impeller 20, and the rotation of the output carriers 118 and 120 integrally connected to the turbine 22 is also increased in the A direction.

In addition, while the rotation of the output carrier shaft 124 integrally connected to the output carriers 118 and 120 and the output carrier shaft 124 and the output shaft 126 connected through the forward and backward switching system 210 also increases, the output shaft ( When the load of the output shaft 126 is further reduced due to the increase of the rotation of the shaft 126 to balance the driving force of the input shaft 12, the impeller 20 and the turbine 22 perform 1: 1 rotation and the first planetary gear. The 114 and the second planetary gear 116 are rotated integrally without rotating the bar, which is referred to as a high speed state.

In other words, the low speed and high speed state is repeated according to the RPM of the engine, thereby making the stepless speed change.

In this embodiment, when looking at the rotational force transmitted to the impeller 20, the rotational force multiplied by the rotational force of the input shaft 12 by the first planetary gear 114 and the second planetary gear 116 passes through the adjustment sun gear 122. It acts on the impeller 20 through the connecting shaft 14 and is transmitted to the turbine 22, so that a large rotational force is driven to the output shaft 126 at a low speed, thereby improving acceleration and efficiency.

On the other hand, in the reverse state, the sleeve 230 of the forward and reverse switching system 210 is moved in the 'R' direction. When the engine power is input to the input shaft 12, the input sun gear 112 formed integrally with the input shaft 12 is rotated in the direction A, which is the same direction as the input shaft 12.

At this time, the output carrier 118, 120, the output carrier shaft 214 integrally connected with the output carriers 118, 120, the reverse coupling gear 212 integral with the output carrier shaft 124, and the reverse coupling gear As the backward transmission gear 216 engaged with the 212 is rotated, the output shaft 126 is rotated in the reverse direction.

At this time, the forward transmission gear 218, the idle gear 222 and the forward connection gear 224 meshed with the forward transmission gear 218 is rotated while the synchronizer cone 226 is in an idle state. .

In this state, the first planetary gear 114 meshed with the input sun gear 112 rotates in the B direction opposite to the input sun gear 112 and is regulated through the second planetary gear 116 integrally connected thereto. Slow down and rotate (122) in the A direction.

The connecting shaft 14 integrally connected with the adjusting sun gear 122, the impeller housing 18 integrally formed with the connecting shaft 14, and the impeller 20 integral with the impeller housing 18 are also decelerated in the direction A. Rotate

That is, since the reverse connecting gear 212 and the output shaft 126 are connected by the operation of the forward and backward switching system 210, the output carrier shaft 124 integral with the reverse connecting gear 212 and the output carrier The output carriers 118 and 120 integral with the shaft 124, and the adjusting shaft 16 and the turbine 22, which are integrally connected with the output carriers 118 and 120, are also in a stopped state.

The rotational force transmitted to the first planetary gear 114 through the input sun gear 112 is transmitted to the adjustment sun gear 122 through the second planetary gear 116 and is formed integrally with the adjustment sun gear 122. And, it is transmitted to the impeller 20 via the impeller housing 18. At this time, since the turbine 22 is stopped, a rotation difference occurs between the impeller 20 and the turbine 22.

Due to the characteristics of the torque converter, the larger the rotational difference between the impeller 20 and the turbine 22 is generated, the greater the rotational force is generated and the multiplied rotational force of the impeller 20 is transmitted to the turbine 22 so that the rotational force transmitted to the turbine 22 is adjusted Integral with the output carrier shaft 214, the reverse coupling gear 212 integral with the output carrier shaft 124, and the reverse coupling gear 212 via the output carriers 118 and 120 integrally connected to the shaft 16. Power is transmitted to the output shaft 126 installed as.

At this time, when the resistance applied to the output shaft 126 and the rotational force transmitted to the turbine 22 are balanced by the load applied to the output shaft 126, the output shaft 126 is driven. This is the reverse start state.

Increasing the rotation of the engine increases the rotation difference between the impeller 22 and the turbine 22, so that the rotational force transmitted to the turbine 22 is increased, and the rotational force transmitted to the turbine 22 is transmitted by the load of the output shaft 126. If greater than the resistance acting on the turbine 22 through the reverse switching system 210, until the rotational force of the turbine 22 transmitted from the impeller 20 is in equilibrium with the resistance acting on the turbine 22 The reverse gear 228 is accelerated and the rotation is increased in the B direction of the output shaft 126 through the forward and reverse switching system 210.

Increasing the rotation of the output shaft 126 reduces the load on the output shaft 126, thereby reducing the resistance applied to the turbine 22. At this time, when the resistance applied to the turbine 22 is reduced, the rotation difference between the impeller 20 and the turbine 22 is reduced until the resistance is balanced.

Therefore, the rotation of the turbine 22 is increased in the direction A, which is the same direction as the impeller 20, and the output carrier connected integrally with the adjusting shaft 16 and the adjusting shaft 16 integrally connected with the turbine 22. (118, 120) also increases the rotation in the A direction.

As the rotation of the output carriers 118 and 120 increases, the rotation of the output carrier shaft 124 integrally connected also increases in the A direction, and the backward connecting gear 212 integrated with the output carrier shaft 124 also has the same A direction. Will rotate.

When looking at the rotational force transmitted to the output shaft 126 in the reverse system, the rotational force multiplied by the first planetary gear 114 and the second planetary gear 116 than the input shaft 12 is transmitted to the adjustment sun gear 122 and connected. The adjusting shaft 16, which is applied to the impeller 20 through the shaft 14 and multiplied again in the impeller 20, is applied to the turbine 22 and integrally connected to the turbine 22, and the adjusting shaft 16. Drive the output carrier 118, 120 and the output carrier shaft 124 and the output shaft 126 connected through the forward and backward switching system 210 integrally connected to the drive shaft to drive a large rotational force to the output shaft 126 in the reverse direction. This improves acceleration and efficiency, and enables smooth and quiet driving even in reverse.

Next, a second embodiment of the present invention as shown in FIG. 5 will be described.

In the second embodiment of the present invention, since the installation structure and the operation method of the shift adjustment system and the shift system are the same as those in the first embodiment, the description of the configuration and the operation method is omitted. In the second embodiment, the forward / reverse switching system uses a multi-plate clutch rather than a synchronizer method.

First, as shown in FIG. 5, since the shift adjustment system and the shift system have the same structure, description thereof will be omitted and only the forward / backward switching system 310 will be described.

That is, the output carrier shaft 124 integrally formed with the output carriers 118 and 120 of the shifting system, and the reverse coupling gear 312 are integrally installed on the output carrier shaft 124, and the reverse transmission gear is described above. A forward transmission gear 318 is provided integrally with the output shaft 126 at a distance from the 316, and engages with the forward transmission gear 318 while rotating the idle gear on the idle gear shaft 320. 322 is installed, and the forward connecting gear 324 is installed to be engaged with the idle gear 322, and the reverse clutch 326 is interposed between the output carrier shaft 124 and the backward connecting gear 312. The forward clutch 328 is installed between the output carrier shaft 124 and the forward connecting gear 324.

The operation method for the second embodiment of the present invention configured as described above is the same as the first embodiment and will be omitted.

As described above, the continuously variable transmission of the present invention can quickly respond to a change in load even when all the gears are connected, and can transmit the rotational force smoothly, as well as by allowing the variable speed to move forward and backward as a simple configuration. It can reduce the manufacturing cost and has a good effect on durability.

Claims (2)

Output carrier and input to receive power generated from the engine and to respond to the load conditions applied to the output shaft, to transmit power to the shifting adjustment system including impeller, turbine and stator and to adjust the rotation ratio corresponding to the load condition of the output shaft. A continuously variable transmission having a transmission system including a sun gear and an adjustment sun gear, A reverse connection gear 212 rotatably mounted on the output carrier shaft 124, A synchronizer cone 214 formed integrally with the reverse connection gear 212 and rotatably installed on the output carrier shaft 124, A reverse transmission gear 216 integral with the output shaft 126 while meshing with the reverse connection gear 212; A forward transmission gear 218 integrally formed with the output shaft 126 at a predetermined distance from the reverse transmission gear 216; An idle gear 222 rotatably installed on the idle gear shaft 220 while meshing with the forward transfer gear 218; A forward connection gear 224 meshing with the idle gear 222; A synchronizer cone 226 integrally formed with a required distance from the forward connecting gear 224, A clutch hub 228 located between the above-described synchronizer cones 214 and 226 and integral with the output carrier shaft 126; A sleeve 230 provided outside the clutch hub 228, Stepless speed change apparatus characterized in that it comprises a synchronizer ring (232,234) freely rotated on the synchronizer cone (214, 226) located on both sides of the clutch hub (230). Output carrier and input to receive power generated from the engine and to respond to the load conditions applied to the output shaft, to transmit power to the shifting adjustment system including impeller, turbine and stator and to adjust the rotation ratio corresponding to the load condition of the output shaft. In the continuously variable transmission having a transmission system including a sun gear and an adjustment sun gear, A reverse connection gear 312 rotatably mounted on the output carrier shaft 124, A reverse transmission gear 316 integral with the output shaft 126 while meshing with the reverse connection gear 312; A forward transmission gear 318 integrally formed with the output shaft 126 at a required distance from the reverse transmission gear 316, An idle gear 322 rotatably installed on the idle gear shaft 320 while meshing with the forward transfer gear 318; A forward connection gear 324 meshing with the idle gear 322; A reverse clutch 326 installed between the output carrier shaft 124 and the reverse connection gear 312; And a forward clutch (328) installed between the output carrier shaft (124) and the forward connecting gear (324).