MXPA99004711A - Continuously variable transmission - Google Patents

Abstract

The present invention relates to a continuously variable transmission contructed in such a way that it can speed-change the power inputted to an input shaft according to the load applied to an output shaft and transmit the power to the output shaft even though all the gears remain engaged, and in addition reverse operation can also be effectuated in a simple way. Reviewing the construction thereof, it is mainly composed of a speed change system, which receives power generated by an engine, changes speed and transmits it to the output shaft, a speed change controlling system which automatically adjusts the rotational ratio to correspond to the condition of the load on the output shaft, and a reverse rotation system. The present invention, comprises two (compound) gear sets in which each same element is removed from two planet gear sets;and a reverse rotation system, and the power inputted through an input element selected from the two gear sets is changed into the required speed and transmitted to the output shaft. Reviewing the operational characteristics, the present invention is constructed in such a way that the decelerated rotation smaller than the input rotation is transmitted to the impeller by utilizing a direct clutch. Therefore, it is a characteristic of the present invention that the rotational force transmitted to the impeller is always larger than the input torque. In view of the effects, the present invention can obtain a large propulsion force, preferable performance, smooth and quiet operation, and can speed-change steplessly at the time of reverse operation.

Description

CONTINUOUSLY VARIABLE TRANSMISSION TECHNICAL FIELD The present invention relates to a continuously variable transmission, and more particularly, to a continuously variable transmission constructed in such a way that the power supply to an input shaft can be transmitted to an output shaft according to the state of an applied load. to the output shaft without decoupling or changing gears when the speed is changed under the state in which all gears are engaged, and that a reverse rotation pulse can also be performed steplessly or in a fixed relationship in a simple manner.

TECHNICAL BACKGROUND Generally, in a transmission, the speed change is made by selecting one of a number of predetermined gear ratios and at the time of making a change of speed, there is the tedious work of carefully decoupling and changing gears. Conventional automatic transmissions are of a type of band that has a very complicated structure, are expensive to manufacture and can not be widely used because they have a limited scale of capacity due to wear, noise and sliding.

BRIEF DESCRIPTION OF THE INVENTION The present invention was made in view of the problems as described above, therefore, an object of the present invention is to provide a continuously variable transmission that does not use the complicated mechanism, responds quickly to a change in load, transmits the rotating force Gently, it changes speed without steps to forward thrust and push back by simple construction, reduces manufacturing cost, and provides improved durability. To achieve this and other objects, the present invention consists of a speed change system that receives energy generated by a motor, changes the speed and transmits it to the output shaft, a speed control system that can automatically control the speed rotation ratio corresponding to the load condition of the output shaft, and several reverse rotation systems type 4, and especially the reverse rotation pulse can be performed without steps. Summing up the construction of the system of change of speed, the system of control of change of speed and the system of rotation in reverse, the main characteristics of the system of the change of speed is that it uses a unit of compound of planetary gear that is, has 2 gear sets in which each equal element (sun gear or ring gear) is removed from 2 sets of planetary gears (including each one a sun gear, a carrier, and a ring gear) and transmits to the output shaft the power supplied through a suitable combinatorial connection between the elements that constitute the gear set and at the same time through the selected input elements of the 2 sets of gears. The speed change control system uses an improved torque converter which is improved over the torque converter of known automatic transmissions. Reviewing the construction of the speed change control system using the terminologies related to the parts that constitute it used in the conventional torque converter, for convenience of explanation, the speed change control system consists of an impeller which it is a driving body, a turbine that is a driving body, a stator for increasing torque, a connecting shaft to be connected to the speed change system, a control shaft, and a fixed shaft to fix the stator. A reverse rotation system has a planetary gear set (sun gear, ring gear, carrier) and a brake, and is built to achieve reverse rotation without steps with a proper combinatorial connection between each constituent element of the gear set and the speed change system. The clutch and brake applied to the system of the present invention can use wet-type clutch of multiple discs and known automatic transmission brakes, and the brake can use a band brake, however, the clutch and the brake are not limited to them .

BRIEF DESCRIPTION OF THE DRAWINGS For a full understanding of the nature and objects of the invention, reference should be made to the following detailed description taken in conjunction with the appended drawings in which: Figure 1 to Figure 10 illustrate a first embodiment of a transmission continuously variable of the present invention; Figure 1 is a schematic drawing of the continuously variable transmission of the present invention which is capable of operating in the reverse I state of rotation; Figure 2 is a schematic drawing of the continuously variable transmission of the present invention which is capable of operating in the reverse-state II state; Figure 3 is a schematic drawing of the continuously variable transmission of the present invention which is capable of operating in the reverse-state III of rotation; Fig. 4 is a schematic drawing of the continuously variable transmission of the present invention which is capable of operating in the reversed rotation state IV; Fig. 5 is an operational view showing a state in which the continuously variable transmission of the present invention rests in the neutral state; Figure 6 is an operational view showing the forward rotation state in the continuously variable transmission of the present invention; Figure 7 is an operational view showing the state I of reverse rotation in the continuously variable transmission of the present invention, Figure 8 is an operational view showing the state II of reverse rotation in the continuously variable transmission of the present invention; Figure 9 is an operational view showing the state III of reverse rotation in the continuously variable transmission of the present invention; Fig. 10 is an operational view showing the state IV of reverse rotation in the continuously variable transmission of the present invention; Figure 11 to Figure 21 are schematic drawings of a second embodiment to a 12th embodiment of the continuously variable transmission of the present invention; Similar reference numbers refer to similar parts through the different views of the drawings.

BEST WAYS TO CARRY OUT THE INVENTION There follows a description of the continuously variable transmission comprising the speed change control system and the speed change system of various modes to which the speed change control system is connected. That is, the speed change system can have several constructions, and the speed change without steps can be effected by properly connecting the speed change control system to the speed change system of different modes. First of all, the first embodiment 100 of the present invention comprised of a speed change control system 10, a speed change system 110 and a reverse rotation system Rl ~ R [V connected thereto is described in detail with reference to the drawings that are attached.

Speed change control system 10 The speed change control system 10 uses a conventional torque converter of an automatic transmission which is a well-known apparatus. In conventional automatic transmission, the energy generated by the motor is transmitted as a driving force to the output shaft of the transmission through the torque converter, whereas in the present invention, the energy generated by the motor is transmitted. directly to the output shaft and the rotational force of the output shaft is transmitted to the impeller as a large rotating force due to a reduced rotation in speed through the gear set. While the torque converter of a conventional automatic transmission has a power transmission function to receive energy generated from the engine and directly transmit power to the output shaft of the automatic transmission, the speed change control system of the present invention has two roles, one is to control the speed ratio to adjust the impulse resistance, the other is to transmit the energy that passes through the speed control system to the speed change control system. Output shaft. The construction of the speed change control system 10 is described in detail below. As shown in Figure 1, a hollow connection shaft 14 is installed coaxially on an input shaft 12, and a hollow control shaft 16 is coaxially installed on the connection shaft 14. A housing of the impeller 18 is formed integrally with the connecting shaft 14, and an impeller 20 is formed integrally with the impeller housing 18. A turbine 22, facing the impeller 20, is integrated with the control shaft 16, a stator 24 is positioned between the impeller 20 and the turbine 22, a hollow fixed shaft 26 is installed coaxially on the control shaft 16 within the stator 24, and a one-way clutch 28 is inserted between the stator 24 and the fixed shaft 26 to prevent a reverse rotation of the stator 24.

Speed change system 110 In the speed change system 110 of the first embodiment of the present invention, as shown in figure 1, an inlet solar gear 112 is formed integrally with the input shaft 12 within which the Motor power is supplied. A first planetary gear 114 is meshed with the outside of the input sun gear 112, and a second planetary gear 116 is integrally formed with the first planetary gear 114. The first planetary gear 114 and the second planetary gear 116 are installed on output carriers. 118, 120 as to turn freely. A control solar gear 122 is engaged with the second planetary gear 116 and formed integrally with the connection shaft 14. On the other hand, an output shaft 124 is installed coaxially with the input shaft 112 and is connected to the output carriers 118, 120 through the direct clutch of the reverse rotation system that is installed between the output carriers 118, 120 and the output shaft 124. The output carriers 118, 120 are integrally connected to the control shaft 16 which is integrally connected to the turbine 22 of the speed change control system. 1. Reverse rotation system (Rl ~ RIV) Next, the reverse rotation system of the first embodiment of the present invention is described. In the present invention, there are 4 different systems of reverse rotation. For reference, the reverse rotation system can be installed on the power line connected to the impeller for a reverse rotation pulse of a fixed ratio, however, a description of the construction and operation of such a reverse rotation system is skip 1. - Reverse rotation system Rl As shown in figure 1, the reverse rotation system Rl is provided between the output shaft 124 and the output carriers 118, 120, of the speed change system 110. A shaft 212 Reverse rotation sun gear is integrally connected to the output carriers 118, 120 of the speed change system 110, and a reversed rotation sun gear 214 is integrally formed with the reversed rotation sun gear shaft 212. A planetary gear 216 of reverse rotation is engaged with the outside of the reversed rotation sun gear 214 and is installed in a reverse rotation carrier 218 to rotate freely. A reversed rotation ring gear 220 is engaged with the outside of the reverse planetary gear 216 and is integrally formed with the output shaft 124. A reverse rotation brake 222 is installed on the outside of the rotation carrier 218. backwards. A direct clutch 226 is installed between the output shaft 124 and the reversed rotation sun gear shaft 212 so that the output carriers 118, 120 and the output shaft 124 can be connected when the direct clutch 226 is driven. A gear unit constituting the reverse rotational Rl system present is a single planetary gear unit. 2. Reverse rotation system Rll As shown in Figure 2, the reverse rotation system Rll is provided between the output shaft 124 and the output carriers 118, 120 of the speed change system 110. A reversed rotation solar gear 312 is integrally formed with the output shaft 124. A reverse planetary gear 314 is engaged with the outside of the reversed rotation sun gear 312 and is installed on a reverse rotating carrier 316 to rotate freely. A reversing gear ring gear 318 is engaged with the outside of the reverse planetary gear 314 and is integrally connected to the output carriers 118, 120 of the speed change system 110. A reverse rotation brake 320 is installed on the outside of the reverse rotation carrier 316. A direct clutch 324 is installed between the output carriers 118, 120 and the output shaft 124 so that the output carriers 118, 120 and the output shaft 124 can be connected when the direct clutch 324 is driven.

A gear unit constituting the current reverse rotation system Rll is a single planetary gear unit. 3. - Reverse rotation system RUI As shown in figure 3, the reverse rotation system RUI is provided between the output shaft 124 and the output carriers 118, 120 of the speed change system 110. A reversed rotation sun gear shaft 412 is integrally connected to the output carriers 118, 120 of the speed change system 110, and a reversed rotation sun gear 414 is integrally formed with the shaft 412 of the rotating solar gear. backwards. A planetary gear 416 of reverse rotation is engaged with the outside of the reversed rotation sun gear 414, and another reverse planetary gear 418 is engaged adjacent to the planetary gear 416 of reverse rotation. These two (double) planetary rotational gears 416, 418 in reverse are installed in a reverse rotation carrier 420 so as to rotate freely. The reverse rotation carrier 420 is integrally formed with the output shaft 124. A reversing gear ring gear 422 is engaged with the outside of a reverse gear planetary gear 418, and a reverse rotation brake 424 is installed on the outside of the reverse gear ring gear 422. A direct clutch 428 is installed between the axis 412 of the reversed rotation sun gear and the reverse rotation carrier 420 so that the output carriers 118, 120 and the output shaft 124 can be connected when the direct clutch 428 is actuated. A gear unit constituting the present system of reverse rotation RUI is a double unit of planetary gear. 4. - Reverse rotation system RIV As shown in Figure 4, the reverse rotation system RIV is provided between the output shaft 124 and the output carriers 118, 120 of the speed change system 110. A reversed rotation sun gear 512 is integrally formed with the output shaft 124. A reverse planetary gear 514 is engaged with the outside of reverse rotation sun gear 512, and another reverse planetary gear 516 is engaged adjacent to the reverse planetary gear 514. These two (double) planetary rotational gears 514, 516 in reverse are installed in a reverse rotation carrier 518 so as to rotate freely, and the reverse rotation carrier 518 is integrally connected to the output carriers 118, 120 of the system 110 of change of speed. A reversing gear ring gear 520 is engaged with the outside of the reverse gear planetary gear 516, and a reverse rotation brake 522 is installed on the outside of the reversing gear ring gear 520. A direct clutch 526 is installed between the reverse rotation carrier 518 and the output shaft 124 so that the output carriers 1 18, 120 and the output shaft 124 can be connected when the direct clutch 526 is driven. A gear unit constituting the present system of reverse rotation RIV is a double unit of planetary gear. Each direct clutch 226, 324, 428, 526 in the Rl system ~ Reverse rotation RIV is provided to cause the output carriers 118, 120 and the output shaft 124 to be integrally connected by their drive in the forward rotation state, however, they are not driven in the reversed rotation state. . The methods of operation and the energy transmission method according to the same for each state of change of speed (neutral, forward and reverse rotation) of the continuously variable transmission of the present invention constructed as described above are described below. Before the explanation, it should be noted that although the continuously variable transmission of the present invention can be used in any mechanism, whose speed changes and emits the driving force, as motor vehicles and industrial machines, the motor vehicles will be explained as an example in the present. For the purpose of defining terminologies, a rotation of each planetary gear means a rotation around its own axis (safe pin in the present) and a revolution means the case where the carrier rotates, in which case the planetary gear normally rotates. and combined translation. Furthermore, for convenience of explanation, the direction of counter-clockwise rotation when viewed from the left side of the drawings is taken as the direction of the input axis, the direction equal to that of the input axis is defined as the direction of the input axis. direction f (or direction A) in each drawing, similarly the direction opposite to that of the input axis is defined as direction i (or direction B), the rotation after the stop (acceleration state) is denoted as 0 • t (or 0 • i), the height after rotation (deceleration state) is denoted as t • 0 (or - • 0), and the state in which the planetary gear does not rotate around its own axis after rotation and all the rotating bodies rotate as an integral body at the same revolutions as the input revolutions is denoted as t. 1 (or • 1). The method of operation for the state of neutral and forward rotation is described based on the construction to which the reverse rotation system Rl is combined.

I.- Neutral state (fig 5): output shaft 124 stopped Input shaft 12 t Solar gear of first gear input 112 Planetary 114 - 1 (1) Second planetary gear 116 i -1 - control solar gear 122 t- connecting shaft 14 t - drive housing 18 t - impeller 20 f - turbine 22 t • 1 - control shaft 16 t • 1 - carriers exit 118, 120 ¬ reverse rotation 212 t • 1 - reverse rotation solar gear 214 t • 1 - reverse rotation planetary gear 216 - - reverse rotation carrier 218 t: (lnactive). The neutral state is a state in which the forward clutch 226 and the reverse rotary brake 222 are released, the motor energy can not rotate the output shaft 124, and the system is inactive as shown in FIG. 5. That is, if the direct clutch 226 that is installed between the output shaft 124 and the integral reverse rotation sun gear shaft 212 with the output carriers 118, 120 is released, the energy between the speed change system 110 is released. and the output shaft 124 is disconnected. The input shaft 12 rotates with the input of the motor power, the input solar gear 112, formed integrally with the input shaft 12, also rotates in the direction A, the same as that of the input shaft 12, and the first planetary gear 114, engaged with the input sun gear 112, rotates in the direction B, as opposed to that of the input sun gear 112. The second planetary gear 116, formed integrally with the first planetary gear 114, is rotated in the direction B, and the control solar gear 122, meshed with the interior of the second planetary gear 116, is rotated in the direction A, as opposed to that of the second planetary gear 116. The connection shaft 14, integrally connected to the solar gear of control 122, the housing of the impeller 18, connected to the connection shaft 14, and the impeller 20, integral with the impeller housing 18, are rotated in the direction A. The turbine 22 installed to face the impeller 20 is rotates in the direction A by the fluid flow, the control shaft 16 integrally connected to the turbine 22 is rotated in the direction A, and the output carriers 118, 120 integrally connected to the control shaft 16 are rotated in the direction A The integral reverse rotation sun gear shaft 212 with the output carriers 118, 120 is also rotated in the direction A, the reverse integral rotation sun gear 214 with the reversed rotation sun gear shaft 212 is rotated in the direction A, and the reverse gear planetary gear 216 rotates geared to the outside of the reverse sun gear 214 in the reverse direction in the direction B. Because the output ring gear 220 meshed with the outside of the planetary gear 216 of reverse rotation is stopped by the load of the output shaft 124, the reverse rotation carrier is inactive in the direction A.

II.- State of forward rotation (Fig. 6) Input shaft 12 t - Input solar gear 112 t - First planetary gear 114 i • (1) Second planetary gear 116 i • 1 - Solar control gear 122 t - Connection shaft 14 t - Impeller housing 18 t - Impeller 20 t - Turbine 20 0 • t - Control shaft 16 0 - t - Carriers exit 118, Reverse rotation solar gear 212 0 • t- (direct clutch) - Output shaft 124 0 - t This is a state in which the direct clutch 226 installed between the output shaft 124 and the rotation sun gear shaft 212 in integral reverse with the output carriers 118, 120 is actuated.

If the energy of the motor is supplied to the input shaft 12, the solar input gear 112, formed integrally with the input shaft 12, is rotated in the direction A, the same as that of the input shaft 12, the first planetary gear 114, meshed with the solar input gear 112, is rotated in the direction B opposite that of the solar input gear 112 because the output carriers 118, 120 are stopped by the load of the output shaft 124 connected through the direct clutch 226. By the rotation of the first planetary gear 114, the second planetary gear 116, integrally connected to the first planetary gear 114, is rotated in the direction B and the rotation of the direction A of the solar control gear 122 geared with the second planetary gear 116 decreases. The connection shaft 14, integrally connected to the solar control gear 122, the housing of the impeller 18, integrally connected to the connection shaft 14, and the impeller 20, integral with the housing of the impeller 18, are decelerated and rotated in the direction A. In the present, reviewing the speed change procedure without steps from a lower step to a high pass, under the condition in which the output shaft 124 connected by driving the direct clutch 226, the output carriers 118, 120, the control shaft 16 and the turbine 22 are stopped, the rotating force The transmission to the first planetary gear 114 through the solar input gear 112 is decreased by the second planetary gear 116 and transmitted to the control solar gear 122.

The increased rotational force is transmitted through the connecting shaft 14, integrally formed with the solar control gear 122, and the impeller housing 18 integrally connected with the connecting shaft 14 to the integral impeller 20 with the impeller housing 18. At that time, because the turbine 22 is stopped by the load of the output shaft 124 due to the actuation of the direct clutch 226, a rotating difference occurs between the impeller and the turbine. In view of the characteristics of the torque converter, the increased rotational force of the impeller 20 is transmitted to the turbine 22, and the rotational force transmitted to the turbine 22 is transmitted through the control shaft 16 and the output carriers 118. , 120 integrally connected to the control shaft to the output shaft 124, and if the resistance acting on the output shaft 124 and the rotational force transmitted to the turbine 22 are in equilibrium, then the output shaft 124 is driven. This is the low speed start state. If the rotation of the motor increases, the rotational difference between the impeller 20 and the turbine 22 becomes larger and therefore, the rotational force transmitted to the turbine 22 increases, and if the rotational force transmitted to the turbine 22 is larger than the resistance acting on the turbine 22 due to the load of the output shaft 124, the output shaft 124 is accelerated until the rotating force of the turbine 22 transmitted from the impeller 20 comes in equilibrium with the resistor acting on the turbine 22.

If the output shaft 124 is accelerated, the load of the output shaft 124 is decreased, therefore, the resistance acting on the turbine 22 also decreases. If the resistance acting on the turbine 22 is decreased, the rotating difference is decreased between the impeller 20 and the turbine 22 until it comes into equilibrium with this resistance. Therefore, the rotation of the turbine 22 increases in the direction A, the same as that of the impeller 20, and also the rotation of the output carriers 118, 120, connected to the turbine 22, increases in the direction A The rotation of the output shaft 124 integral with the output carriers 118, 120 is increased and if the load of the output shaft 124 is further reduced due to the increase in the rotation of the output shaft 124 and therefore the load comes in equilibrium with the driving force of the output shaft 12, the impeller 20 and the turbine 22 are rotated in the ratio of 1: 1, and the first planetary gear 114 and the second planetary gear 116 do not rotate around their own axes but all the Rotating bodies rotate integrally. This is the high-speed state. In the present embodiment, reviewing the rotational force transmitted to the impeller 20, because the rotational force increased more than that of the input shaft 12 by the first planetary gear 114 and the second planetary gear 116, acts on the impeller 20 through the control solar gear 122 and the connection shaft 14 as to be transmitted to the turbine 22, the large rotating force is applied to the output shaft 124 in the low speed state thereby obtaining excellent acceleration and efficiency.

III State of rotation in reverse (Fig. 7 ~ Fig. 10) 1. - Reverse rotation status I (Fig. 7) Input shaft 12 t - Input solar gear 112 t - First planetary gear 114 ^ .1 - ¡- (1) (2) (1) Second planetary gear 116 i. 1 - Solar control gear 122 t - Connection bolt 14 t - Impeller housing 18 t - Impeller 20 t - Turbine 22 0. t - Control shaft 16 0. t Output holders 118, 120.0. t- Gear shaft (2) Output carriers 118, 120 0. Reverse rotation solar t 212 0. t - Reverse rotation solar gear 214 0. t - Reverse rotation planetary gear 216 0. i (3) Reverse rotation carrier 218: stopped (by reverse rotation brake drive) (4) Reverse rotation ring gear 220 0. i -Exit dial 124 0 In the reversed rotation state I, the direct clutch 226 is released, and the reverse rotation brake 222 installed on the reverse rotation carriers 218 is actuated. If the motor power is supplied to the input shaft 12, the input solar gear 112, formed integrally with the input shaft 12, is rotated in the direction A, the same as that of the input shaft 12.

Because the output carriers 118, 120, the reversed rotation sun gear shaft 212, integrally connected to the output carriers 118, 120, and the reverse rotation sun gear 214, integral with the reverse rotation sun gear shaft 212, are in a momentarily stationary condition together with the output shaft 124 by driving the reverse rotation brake 222, the first planetary gear 114 meshed with the input solar gear 112 is rotated in the direction B opposite that of the input solar gear 112 and decelerates and rotates the solar control gear 122 in the direction A through the second planetary gear 116 In addition, the connecting shaft 14, integrally connected to the solar control gear 122, the impeller housing 18, formed integrally with the connecting shaft 14, and the impeller 20, integral with the impeller housing 18, are decelerated and rotated in the direction A. In the present, reviewing the stepless speed change procedure, the carrier of reverse rotation 218 and the reverse rotation ring gear 220 integrally connected to the output shaft 124, are in a stationary condition due to the drive of the reverse rotation brake 222, installed on the outside of the reverse rotation carriers 218 , and in addition, the reversed rotation sun gear shaft 212, integral with the reverse rotation sun gear 214, and the output carriers 118, 120 integrally connected with the reversed rotation sun gear shaft 212, and the control shaft 16 and turbine 22 connected to output carriers 118, 120 by direct clutch 226, are also in a momentarily stationary condition. In this state, a part of the rotating force transmitted to the first planetary gear 114 through the solar input gear 112 is transmitted to the control solar gear 122 through the second planetary gear 116, and is also transmitted to the driver 20 through the connection shaft 14, formed integrally with the control solar gear 122 and the impeller housing 18. At that time, because the turbine 22 is stopped, a rotating difference occurs between the impeller 20 and the turbine 22. In view of the characteristics of the torque converter, while the rotational difference between the impeller 20 and the turbine 22 is larger, the rotational force becomes larger, and the increased rotational force of the impeller 20 is transmitted to the turbine 22, and both, the rotational force transmitted to the turbine 22 is transmitted to the reversed rotation sun gear shaft 212 and the reverse rotation sun gear 214 through the shaft control 16 and the output carriers 118, 120 integrally connected to the control shaft, and if the resistance acting on the solar gear 214 of reverse rotation by the load of the output shaft 124 establishes equilibrium with the rotational force transmitted to the turbine 22, the solar 214 gear of reverse rotation is driven. The rotational force is transmitted to the reverse rotation planetary gear 216, engaged with the reversed rotation sun gear 214, with rotation of the reverse rotation sun gear 214, and because the reverse rotation carrier 218 is stopped by actuating the reverse rotation brake 22, the reverse rotation planetary gear 216 rotates in the direction B which is opposite to the direction A and rotates the reverse rotation ring gear 220, engaged with the outside of the planetary gear reverse rotation 216, in the B direction. This is the start state of reverse rotation. If the rotation of the motor increases, the rotational difference between the impeller 20 and the turbine 22 becomes larger, and therefore the rotational force transmitted to the turbine 22 increases, and wherein the rotational force transmitted to the turbine 22 is larger than the resistance acting on the turbine 22 through the reversed rotation sun gear 214 due to the load of the output shaft 124, the solar rotation gear in reverse 214 is accelerated until the rotating force of the turbine 22 transmitted from the impeller 20 establishes equilibrium with the resistance acting on the turbine 22, and the rotation of the reverse rotation ring gear 220, integral with the output shaft 124, is increased in the direction B through the planetary gear of reverse rotation 216.

If the rotation of the output shaft 124 increases, because the output shaft letter 124 is decreased, the resistance acting on the turbine 22 through the reversed rotation sun gear 214 is also decreased. If the resistance acting on the turbine 22 is decreased, the rotating difference between the impeller 20 and the turbine 22 is decreased until the rotating force establishes equilibrium with the resistance. Therefore, the rotation of the turbine 22 increases in the direction A, the same as that of the impeller 20, and also, the rotation of the control shaft 16, integrally connected with the turbine 22 and the output carriers 118, 120 integrally connected to the control shaft 16 is increased in the direction A. If the rotation of the output carriers 118, 120 is increased, also the rotation of the reversed rotation sun gear shaft 212, integrally connected to the output carriers 118 , 120 and reversed rotation solar gear 214 is increased, and the rotation of the reverse rotation ring gear 220 and the output shaft 124 is also increased through the reverse rotation planetary gear 216. As described above , the operational characteristics of the reverse rotation state I according to the present reverse rotation system Rl (the same as in the other reverse rotation systems) is e the reverse pulse without steps can be achieved according to the load of the output shaft 124 even at the moment of rotation in reverse.

By checking the rotational force transmitted to the output shaft 124 in the present reverse rotation system Rl, the rotational force increased more than that of the input shaft 12 by the first planetary gear 114 and the second planetary gear 116, is transmitted to the solar gear of control 122, which acts on the impeller 20 through the connection shaft 14, and the rotational force is further increased by the impeller 20 acting on the turbine 22, it is also transmitted to the reversed rotation sun gear 214 through of the control shaft 16, integrally connected to the turbine 22, and through the output carriers 118, 120 integrally connected to the control shaft and to the reversed rotation sun gear shaft 212, and drives the ring gear 220 of rotation in integral reverse with the output shaft 124 through the planetary gear 216 of reverse rotation, and therefore, the large rotational force mpulsal output shaft 1 24 at the time of reverse rotation, so that acceleration and efficiency are improved and a steady and even advance can be achieved even during reverse operation. 2. - State of reverse rotation II (figure 8) Input shaft 12-t - Input solar gear 112 t - First planetary gear 114 • 1 -, (1) _ (2) (1) Second planetary gear 116 4 * 1 -Screw control solar 112 t - Connecting shaft 14 t Impeller stay 18 t - Impeller 20t - Turbine 22 0 • t Control axis 16 0 • t Output chokes 118,120 0 • (2) output carriers 118 120 0 • t- of reverse rotation ring 318 0 • t (3) Reverse rotation carrier 316: stopped (by reverse rotation brake drive) (4) Reverse rotation planetary gear 314 0 • t - Reverse rotation solar gear 312 0 • i - Output shaft 124 0 • i In the reversed rotation state II, the direct clutch 324 is released, and the reverse rotation brake 320 installed on the reverse rotation carrier 316 is actuated. Because the direction of rotation and the energy transmission method in the present state of reverse rotation II in the speed change system 110 and speed change control system 10 is the same as in the state of rotation in Reverse I based on the reverse rotation system RI described above, a description of it is omitted, and here, only the method of transmitting energy to the output shaft 124 through the reverse rotation system Rll is described. As shown in FIG. 8, the reverse rotation ring gear 318 integrally connected to the output carriers 118, 120 is rotated in the direction A, the same as that of the output carriers 118, 120, by rotation of the output carriers 118, 120 of the speed changing system 110. Because the reverse rotation carrier 316 is stopped by the reverse rotation brake drive 320, the planetary gear 314 of reverse rotation, engaged with the interior of the reversing gear ring gear 318 is rotated in the direction A, the same as that of the reverse gear ring gear 318, and rotates the reverse rotation sun gear 312, engaged with the interior of the planetary gear 314 of reverse rotation, in the direction B opposite to the direction A. In addition, the output shaft 124, integrally connected to the sun gear 312 of reverse rotation, is rotated in the direction B by rotation n of sun gear 312 reverse rotation. 3. - State of rotation in reverse III (figure 9) Input shaft 12 t - Input solar gear 112 t - First planetary gear 114 4 * 1 -, - (1) (2) (1) Second planetary gear 116 i • 1 -Screw control solar 122 t - Connection shaft 14 t - drive housing 18 t - Impeller 20 t - Turbine 22 0 • t - Control unit 16 0 • t Output chokes 118, 120 0 • t (2) Output carriers 118, 120 0 • t reversed rotation sun gear 412 0 • t - Reverse rotation planetary gear 416 0 • i (2) Reverse rotation planetary gear 418 0 • t - Ring gear Reverse rotation 422: stopped (by rotary brake drive in reverse) (3) reverse rotation carrier 420 0 • i - Output shaft 124 0 • 4 In the reverse rotation system III, the direct clutch 428 is released, and the reverse rotation brake 424, installed on the reverse gear ring gear 422 is actuated. Because the rotation direction and the energy transmission method in the present state of reverse rotation III and the speed change system 110 and the speed change control system 10 are the same as in the state of rotation in reverse I, based on the operation of the reverse rotation system R1 described above, a description thereof is omitted, and here, only the method of transmitting energy to the output shaft 124 through the reverse rotation system is described. R III.

As shown in Figure 9, the reversed rotation sun gear shaft 412, integrally connected to the output carriers 118, 120, is rotated in the direction A, the same as that of the output carriers 118, 120, by the rotation of the output carriers 118, 120 of the speed change system 110, and also the sun gear 414 of reverse rotation, integrally connected to the reversed rotation sun gear shaft 412, is rotated in the direction A. The sun gear 414 of reverse rotation rotates the planetary gear 416 of reverse rotation, meshed with the reverse sun gear 414 in reverse, in the opposite direction B, and the planetary gear 416 of reverse rotation rotates another planetary gear 418 of reverse rotation adjacent to and engaged with the planetary gear 416 of reverse rotation in the direction A. Although the planetary gear 418 of reverse rotation attempts to rotate the ring gear 422 of rotation in reverse gear geared to the outside of the planetary gear 418 of reverse rotation, because the ring gear 422 in reverse rotation is stopped due to the actuation of the reverse rotation brake 424, the planetary gear 418 rotational reverse gear carrier 420 of reverse rotation in the direction B. In addition, the output shaft 124 integrally connected to the reverse rotation carrier 420 rotates in the direction B. 4. - State of rotation in reverse IV (figure 10) Input shaft 12 t - solar input gear 112 t first planetary gear 114 4 * 1 - r- (1) ~ (2) (1) Second planetary gear 116 4 * 1 - solar control gear 122 t - connecting shaft 14 t - impeller housing 18 t - impeller 20 t - turbine 22 0 • t - control shaft 16 0 • t - carriers output 118, 120 0 • t. Porta¬ (2) output carriers 118, 120 0 • reverse rotation drivers 518 0 • t (2) Reverse rotation planetary gear 516 0 • 4 - reverse rotation ring gear 520: stopped (by reverse drive) rotation brake in reverse). (4) reverse rotation planetary gear 514 0 - t - reverse rotation sun gear 512 0 - 4 - output shaft 124 O - 4. In the reversed rotation state IV, the direct clutch 526 is released, and the reverse rotation brake 552 installed on the ring gear 520 of reverse rotation in actuated. Because the rotational direction and the energy transmission method in the present state of reverse rotation IV in the speed change system 110 and the speed change control system 10 are the same as in the state of rotation in Reverse I based on the operation of the reverse rotation system Rl described above, a description of the same is omitted, and here, only the method of transmitting the energy to! output shaft 124 through the reverse rotation system RIV. As shown in Figure 10, the reverse rotation carrier 518 integrally connected to the output carriers 118, 120 is rotated in the direction A, the same as that of the output carriers 118, 120, by rotation of the carriers output 118, 120 of the speed change system 110. The rotation is transmitted to the planetary gears 514, 516 of reverse rotation as the reverse rotation carrier 518 rotates, and because the ring gear 520 rotates in reverse, geared to the outside of the planetary gear 516 of reverse rotation, is stopped by the drive of the reverse rotation brake 522, the planetary gear 516 of reverse rotation is rotated in the opposite direction B and rotates the planetary gear 514 of reverse rotation, geared in adjacent thereto, in the direction A. The sun gear 512 of reverse rotation, engaged with the interior of the planetary gear 514 of reverse rotation, gi in the opposite direction B and giral output shaft 124 integrally connected thereto in the same direction B. Hereinafter, the second embodiment to the XII embodiment of the present invention is described. In the second embodiment up to the XII modality of the present invention, because the installation structure and the operation method of the speed change control system is the same as that of the speed change control system of the first mode , a description of the construction and method of operation of the speed change control system is omitted, and although there is a difference in the construction of the speed change system as well, the principle of the method of operation or the speed change procedure it is similar to that of the first modality, and therefore, a detailed description of it is omitted. Likewise, also the installation construction of the reverse rotation system is the same as that of the first mode, and the operation method and speed change procedure is similar to that of the first mode, therefore, the detailed description of it is omitted. In addition, although the positions of the impeller I and the turbine T can be changed in the speed control system, because the method of operation and the method of transmitting energy at the time of change of speed in the control system of change of speed is the same as that of the first embodiment of the present invention, a description thereof is also omitted. Therefore, considering the similarity of construction, method of operation, and rate change procedure, as described above, the construction of each mode is shown schematically for simplification and convenience of explanation.

That is, the schematic drawings of the second embodiment to the XII embodiment are shown in Figure 11 to Figure 21, the construction to which the reverse rotation system Rl is combined is shown. Although the speed change system basically uses the planetary gear compound unit, there are differences in the input method, the method of connecting the gear set to the impeller and turbine, and the method of combining the elements that constitute them. However, because the method of operation and the speed change procedure are the same as those of the first mode, each mode of the speed change system is shown in a table together with a concurrent presentation of the corresponding figure.

PICTURE the picture and the figures are described immediately.

I: Impeller T: Turbine S: Stator B1: Reverse rotation brake CLD: Direct clutch DP: A set of double planetary gears DP12: A first set of double planetary gears DP21: A second set of double planetary gears SP: A set simple planetary gear SP12: A first single planetary gear set SP21: A second set of simple planetary gears S1: First solar gear S2: Second solar gear C1: First carrier C2: Second carrier C12, C21: Planetary carrier R1: First gear of ring R2: Second ring gear SR: Solar gear in reverse rotation CR: Planetary carrier of reverse rotation RR: Reverse gear ring gear In the present, the order of the suffix numbers 1 and 2 of the same elements on the two gear sets is determined as follows, that is, the first (or right) is numbered as 1 and the second (or left) is numbered as 2. Two digits (12 or 21) for the suffix number means an integrated type, that is, it means that the elements are integrally connected to each other. In the present, 12 indicates the right portion, and 21 indicates the left portion. The planetary gear unit used in the reverse rotation system R1 through RIV comprises a single planetary gear unit or a double planetary gear unit. The simple planetary gear unit includes a reversed rotation sun gear SR, a simple planetary gear set SP, a reverse rotation planetary carrier CR and a reverse rotation ring gear RR. In addition, the double planetary gear unit includes a reversed rotation sun gear SR, a double planetary gear set DP, a reverse rotation planetary carrier CR and a reverse rotation ring gear RR.

Each reference number in the first embodiment corresponds as follows. 12? IS 124? OS 20 22? T 24 112 - »S1 114? SP12 116? SP21 118, 120? C12, C21 122? S2 222, 320, 424, 522? B1 226, 324, 428, 526? CLD 214, 312, 414, 512? SF 216, 314? SP 416, 418; 514, 516? DP 218, 316, 420, 518? CR 220, 318, 422, 520? RR In the present invention, various embodiments can be realized by providing the sun gear, the carrier supporting the planetary gear and the ring gear and by proper combination between each element, suitable selection of input element and method for setting the gear ratio, and also the connection to the turbine, impeller, and reverse rotation brake can be varied, therefore, in scope of the present invention is not limited to the modalities shown as examples. For example, the V mode (whose construction is represented as (T) (I) - (A) is shown in Figure 14 and in the present, the desired object can be achieved with the construction in which the lateral disposition of ( T) and (I) is inverted, that is, the construction of (l) (T) - (A), and the example thereof is shown in Fig. 14A.In addition, even if the input element is changed considering the symmetry of the input element, the desired object can also be achieved., the example of the construction of (T) (l) - (B) in which the input element is changed considering the symmetry in the V mode is shown in Figure 14B, and here, in desired object can be achieved with the construction in which the lateral disposition of (T) and (I) is reversed, that is, the construction of (I) (T) - (B) and an example thereof is shown in Figure 14C. For reference, if the reverse rotation system that is installed on the power line connected to the impeller instead of the reverse rotation system (Rl ~ RIV) is provided (the reverse rotation pulse is performed at a fixed ratio when it works), (T) and (I) can be located next to the output axis and the example of such construction of (A) - (T) (I) is shown in Figure 14D. Here, the example of the construction in which the lateral arrangement of (T) and (I) is reversed, that is, the construction of (A) - (l) (T) is shown in Figure 14E. In the construction in which the input element is changed considering the symmetry of the input element, if the reverse rotation system in which it is installed on the power line connected to the impeller is provided, (T) and (I) it can be located next to the output shaft and the example of such construction of (B) - (T) (I) is shown in Figure 14F, and here, the example of the construction in which the lateral arrangement of (T) ) and (I) is reversed, that is, the construction of (B) - (l) (T) is shown in Figure 14G. As described above, in the present invention, on the basis of the embodiment shown as an example, not only the input element can be changed, but also the turbine and impeller connection, it can be changed if desired, and Of course, the operation varies according to the characteristics of each modality. Although each of such probable examples is not specifically described in the present specification, such probable examples naturally fall within the scope of the present invention in view of the tone of the present invention. Although the gear ratio between the first and second planetary gear, and the gear ratio between the sun gear and the ring gear are not described in the claims, because the embodiments of the present invention can be fully understood in view of the The operating principle of the present invention or with reference to the drawings if required, it is natural that the omission of the description of the gear ratio does not limit the scope of the present invention. It is obvious that the continuously variable transmission of the present invention is not limited to the present embodiments but can be applied to all the apparatuses that can change speed the impulse force and send it to the output shaft in all vehicles and industrial machines based in the tone of the present invention, and that various modifications and alterations can be made in the scope of the present invention. As described above, the continuously variable transmission of the present invention can respond rapidly to a change in load and transmit the rotary force uniformly under the state in which all gears are engaged, in addition, it can change the speed without steps in a rotation forward and reverse rotation by simple construction, reduced manufacturing constellation, and improved durability.

Claims (16)

NOVELTY OF THE INVENTION CLAIMS

1. - A continuously variable transmission comprising: an input shaft IS for supplying power to the transmission; an output shaft OS for supplying power from the transmission; a planetary gear compound unit including (i) a first sun gear S1 driven by the input shaft IS; (ii) a first set of simple planetary gears SP12 meshed with the first sun gear S1; (iii) a second set of simple planetary gears SP21 rotatably secured to the first set of simple planetary gears SP12; (iv) a second solar gear S2 engaged with the second set of simple planetary gears SP21, and (v) a planetary carrier C12, C21 to rotatably support said first and second sets of planetary gears SP12, SP21; an impeller (I) connected by impulse to the second solar gear S2; A turbine (T) connected by impulse to the planetary carrier C12, C21; and a stator (S) positioned between the impeller and the turbine by means of a one-way clutch.

2. A continuously variable transmission comprising: an input shaft IS to supply power to the transmission; an output shaft OS for supplying power from the transmission; a planetary gear compound unit including (i) a first ring gear R1; (ii) a first set of simple planetary gears SP12 meshed with the first ring gear R1; (iii) a second set of simple planetary gears SP21 rotatably secured to the first set of simple planetary gears SP12; (iv) a second gear of ring R2 engaged with the second set of simple planetary gears SP21, and driven by the input shaft IS; and (v) a planetary carrier C12, C21 to rotatably support said first and second planetary gear sets SP12, SP21; an impeller (I) connected by means of a pulse to the first ring gear R1; A turbine (T) connected by impulse to the planetary carrier C12, C21; and a stator (S) positioned between the impeller and the turbine by means of a one-way clutch.

3. A continuously variable transmission comprising: an input shaft IS to supply power to the transmission; an output shaft OS for supplying power from the transmission; a planetary gear compound unit including (i) a first solar gear S1; (ii) a first set of simple planetary gears SP12 meshed with the first sun gear S1; (iii) a second set of simple planetary gears SP21 rotatably secured to the first set of simple planetary gears SP12 rotatably secured to the first set of single planetary gears SP12; (iv) a second solar gear S2 engaged with the second set of simple planetary gears SP21, and (v) a planetary carrier C12, C21 to rotationally support said first and second sets of planetary gears SP12, SP21 and driven by the input shaft IS; an impeller (I) connected by means of a pulse to the first solar gear S1; A turbine (T) connected by impulse to the second solar gear S2; and a stator (S) positioned between the impeller and the turbine by means of a one-way clutch.

4. A continuously variable transmission comprising: an input shaft IS for supplying power to the transmission; an output shaft OS for supplying power from the transmission; a planetary gear compound unit including (i) a first ring gear R1; (ii) a first set of simple planetary gears SP12 meshed with the first ring gear R1; (iii) a second set of simple planetary gears SP21 rotatably secured to the first planetary gear set SP12; (iv) a second gear of ring R2 engaged with the second set of simple planetary gears SP21, and (v) a planetary carrier C12, C21 to rotationally support said first and second sets of planetary gears SP12, SP21 and driven by the shaft of IS entry; an impeller (I) connected by means of an impulse to the second ring gear R2; A turbine (T) connected by impulse to the first ring gear R1; and a stator (S) positioned between the impeller and the turbine by means of a one-way clutch.

5. A continuously variable transmission comprising: an input shaft IS to supply power to the transmission; an output shaft OS for supplying power from the transmission; a planetary gear compound unit including (i) a first sun gear S1 driven by the input shaft IS; (ii) a first set of double planetary gears DP12 meshed with the first sun gear S1; (iii) a second set of double planetary gears DP21 rotatably secured to the first set of double planetary gears DP12; (iv) a second solar gear S2 engaged with the second set of double planetary gears DP21, and (v) a planetary carrier C12, C21 to rotatably support said first and second sets of planetary gears DP12, DP21; an impeller (I) connected by impulse to the second solar gear S2; A turbine (T) connected by impulse to the planetary carrier C12, C21; and a stator (S) positioned between the impeller and the turbine by means of a one-way clutch.

6. A continuously variable transmission comprising: an input shaft IS to supply power to the transmission; an output shaft OS for supplying power from the transmission; a planetary gear compound unit including (i) a first sun gear S1 driven by the input shaft IS; (ii) a first set of simple planetary gears SP12 meshed with the first sun gear S1; (iii) a second set of double planetary gears DP21 rotatably secured to the first set of simple planetary gears SP12; (iv) a second sun gear S2 engaged with the second set of double planetary gears DP21, and (v) a planetary carrier C12, C21 to rotatably support said first and second sets of planetary gears SP12, DP21; an impeller (I) connected by impulse to the planetary carrier C12.C21; A turbine (T) connected by impulse to the second solar gear S2; and a stator (S) positioned between the impeller and the turbine by means of a one-way clutch.

7. A continuously variable transmission comprising: an input shaft IS to supply power to the transmission; an output shaft OS for supplying power from the transmission; a planetary gear compound unit including (i) a first sun gear S1 driven by the input shaft IS; (ii) a first set of double planetary gears DP12 meshed with the first sun gear S1; (iii) a second set of simple planetary gears SP21 rotatably secured to the first set of double planetary gears DP12; (V) a second solar gear S2 engaged with the second set of simple planetary gears SP21, and (v) a planetary carrier C12, C21 to rotationally support said first and second sets of planetary gears DP12, SP21; an impeller (I) connected by impulse to the planetary carrier C12.C21; A turbine (T) connected by impulse to the second solar gear S2; and a stator (S) positioned between the impeller and the turbine by means of a one-way clutch.

8. A continuously variable transmission comprising: an input shaft IS to supply power to the transmission; an output shaft OS for supplying power from the transmission; a planetary gear compound unit including (i) a first planetary gear R1 driven by the input shaft IS; (ii) a first set of double planetary gears DP12 meshed with the first ring gear R1; (iii) a second set of double planetary gears DP21 rotatably secured to the first set of double planetary gears DP12; (iv) a second gear of ring R2 engaged with the second set of double planetary gears DP21, and (v) a planetary carrier C12, C21 to rotatably support said first and second sets of planetary gears DP12, DP21; an impeller (I) connected by means of an impulse to the second ring gear R2; A turbine (T) connected by impulse to the planetary carrier C12, C21; and a stator (S) positioned between the impeller and the turbine by means of a one-way clutch.

9. A continuously variable transmission comprising: an input shaft IS for supplying power to the transmission; an output shaft OS for supplying power from the transmission; a planetary gear compound unit including (i) a first ring gear R1 driven by the input shaft IS; (ii) a first set of simple planetary gears SP12 meshed with the first ring gear R1; (Ii) a second set of double planetary gears DP21 rotatably secured to the first set of single planetary gears SP12; (iv) a second gear of ring R2 engaged with the second set of double planetary gears DP21, and (v) a planetary carrier C12, C21 to rotatably support said first and second sets of planetary gears SP12, DP21; an impeller (I) connected by impulse to the planetary carrier C12, C21; A turbine (T) connected by means of a pulse to the ring gear R2; and a stator (S) positioned between the impeller and the turbine by means of a one-way clutch.

10. A continuously variable transmission comprising: an input shaft IS to supply power to the transmission; an output shaft OS for supplying power from the transmission; a planetary gear compound unit including (i) a first ring gear R1 driven by the input shaft IS; (ii) a first set of double planetary gears DP12 meshed with the first ring gear R1; (Ii) a second set of simple planetary gears SP21 rotatably secured to the first DP12 double planetary gear set; (V) a second gear of ring R2 engaged with the second set of simple planetary gears SP21, and (v) a planetary carrier C12, C21 to rotatably support said first and second sets of planetary gears DP12, SP21; an impeller (I) connected by impulse to the planetary carrier C12, C21; A turbine (T) connected by impulse to the second ring gear R2; and a stator (S) positioned between the impeller and the turbine by means of a one-way clutch.

11. A continuously variable transmission comprising: an input shaft IS for supplying power to the transmission; an output shaft OS for supplying power from the transmission; a planetary gear compound unit including (i) a first solar gear S1; (ii) a first set of double planetary gears DP12 meshed with the first sun gear S1; (iii) a second set of double planetary gears DP21 rotatably secured to the first set of double planetary gears DP12; (iv) a second solar gear S2 engaged with the second set of double planetary gears DP21, and (v) a planetary carrier C12, C21 to rotationally support said first and second sets of planetary gears DP12, DP21 and driven by the input shaft IS; an impeller (I) connected by means of a pulse to the first solar gear S1; A turbine (T) connected by impulse to the second solar gear S2; and a stator (S) positioned between the impeller and the turbine by means of a one-way clutch.

12. A continuously variable transmission comprising: an input shaft IS for supplying power to the transmission; an output shaft OS for supplying power from the transmission; a planetary gear compound unit including (i) a first ring gear R1; (ii) a first set of double planetary gears DP12 meshed with the first ring gear R1; (iii) a second set of double planetary gears DP21 rotatably secured to the first set of double planetary gears DP12; (V) a second gear of ring R2 engaged with the second set of double planetary gears DP21, and (v) a planetary carrier C12, C21 to rotatably support said first and second sets of planetary gears DP12, DP21 and driven by the shaft input IS; an impeller (I) connected by means of a pulse to the first ring gear R1; A turbine (T) connected by impulse to the second ring gear R2; and a stator (S) positioned between the impeller and the turbine by means of a one-way clutch.

13. The continuously variable transmission according to any of claims 1 to 12, further comprising: a single planetary gear unit for selectively establishing a reverse pulse, including: (i) a rotational reversed solar shift gear SR by driving the output pulse of the planetary gear compound unit; (I) a set of simple planetary gears SP meshed with the sun gear of reverse rotation SR; (iii) a rotational planetary carrier in reverse CR to rotatably support the simple planetary gear set SP; (iv) a reversing rotation ring gear RR engaged with the simple planetary gear set SP and operatively connected to the output shaft OS; A reverse rotation brake B1 for selectively coupling in planetary carrier CR for reverse impulse; and a direct clutch CLD for selectively coupling the compound output pulse of the planetary gear unit to the output shaft OS for forward drive.

14. The continuously variable transmission according to any of claims 1 to 12 further comprising: a single planetary gear unit for selectively establishing a reverse pulse, including: (i) a reversed reverse rotation sun gear of the SR by driving the output shaft OS; (ii) a set of simple planetary gears SP meshed with the sun gear of reverse rotation SR; (iii) a rotational planetary carrier in reverse CR to rotatably support the simple planetary gear set SP; (V) a reverse rotating ring gear RR connected by pulse to the output pulse of the planetary gear compound unit and engaged with the simple planetary gear set SP; A reverse rotation brake B1 for selectively coupling in planetary carrier CR for reverse impulse; and a direct clutch CLD for selectively coupling the compound output pulse of the planetary gear unit to the output shaft OS for forward drive.

15. The continuously variable transmission according to any of claims 1 to 12, further comprising: a double planetary gear unit for selectively establishing a reverse pulse, including: (i) a reversed SR rotation sun gear by driving the output pulse of the planetary gear compound unit; (ii) a set of double planetary gears DP meshed with the sun gear of reverse rotation SR; (iii) a rotational reverse planetary carrier CR to rotatably support the double planetary gear set DP with the planetary rotary bearer in reverse connected by pulse to the output shaft OS; and (iv) a reverse gear rotation gear RR engaged with the DP planetary gear set; A reverse rotation brake B1 for selectively coupling the reverse rotation ring gear RR for reverse drive; and a direct clutch CLD for selectively coupling the planetary carrier of reverse rotation CR to the output pulse of the planetary gear compound unit for forward drive.

16. The continuously variable transmission according to any of claims 1 to 12 further comprising: a double planetary gear unit for selectively establishing a reverse pulse, including: (i) a rotational reverse sun gear SR connected by driving the output shaft OS; (ii) a set of double DP planetary gears geared to the SR reverse rotation sun gear; (iii) a rotational reverse planetary carrier CR to rotatably support the DP planetary dual gear set with the planetary reversible rotation carrier connected by pulse to the output pulse of the planetary gear compound unit; and (v) an RR reverse gear ring gear engaged with the DP planetary gear set; A reverse rotation brake B1 for selectively coupling the reverse rotation ring gear RR for reverse drive; and a direct clutch CLD for selectively coupling the planetary carrier of reverse rotation CR to the output shaft OS for forward drive. SUMMARY OF THE INVENTION The present invention relates to a continuously variable transmission constructed in such a way that it can change the speed of the energy supplied to an input shaft according to the load applied to an output shaft and transmit the energy to the output shaft even when all the gears remain coupled, and in addition the operation in reverse can also be carried out in a simple way; reviewing the construction of the same, this is composed mainly of a system of speed change, which receives energy generated by a motor, changes the speed and transmits it to the output shaft, a speed control system that automatically adjusts speed the revolving relation to correspond to the condition of the load on the output shaft, and a system of rotation in reverse; the present invention comprises two sets of gears (combined) in which each equal element is removed from two sets of planetary gear; and a reverse rotation system, and the energy supplied through a selected input element of two sets of gears is changed to the required speed and transmitted to the output shaft; by reviewing the operating characteristics, the present invention is constructed in such a way that the decelerated rotation smaller than the input rotation is transmitted to the impeller using a direct clutch; therefore, it is a feature of the present invention that the rotational force transmitted to the impeller is always larger than the input torque; in view of the effects, the present invention can obtain a large propulsive force, preferable performance, uniform and quiet operation, and can change speed without steps at the time of reverse operation. P99 / 670F SR / asg * sff * mmr * sll * mvh *