Background Art In general, an engine has been used as a power source to make moving a vehicle. A vehicle, for example when a car is started, it need a big force as in a case when it drives on the hill, and when drives express way, it need fast speed more than big force.

But, there are limit of power and range of speed in output of power of the engine.

Therefore, in order to supplement disadvantage, a transmission apparatus is placed between the engine and the driving wheel. Thus when a big force is needed, the gear ratio (the number of rotation of output power/the number of rotation of input power) is made small; in other words, the transmission apparatus is used by making the final drive gear ratio (the number of rotation of input power/the number of rotation of output power) large, whereas when a fast speed is needed, it is used oppositely by making the gear ratio large.

These variable transmission apparatus are classified largely as manual transmission, automatic transmission and continuously variable transmission in general.

A manual transmission has been used widely for small-sized car and large-sized commercial car because the manufacturing cost is cheapest and efficiency is good.

However, the speed stage of manual transmission is comprised multistage, so it has a disadvantage of the transmission lever and clutch installed at the driver seat to obtain the proper transmission ratio according to the road situation. Therefore, in order to solve said discomfort of manual transmission, the automatic transmission and the continuously variable transmission have been developed.

The automatic transmission is can be classified into a semiautomatic transmission and a full automatic transmission. The former is attached with an actuator which operates a clutch and a transmission lever in manual transmission, and a sensor is attached which detecting the engine accelerating pedal, number of engine rotation and the number of input/output power rotation, thereby calculating the measured signals, and directing the calculated results to the actuator and changing the speed to proper transmission level. The latter is installed with a hydraulic torque converter and a planetary gear, and a brake and a clutch operated by a hydraulic pressure on the continuously variable speed of the torque converter and planetary element such as the ring gear and carrier and changes speed automatically according to the driving situation.

However, when speed is changed, the shock is generated and it makes a feeling of ride is to be bad and it is difficult to operate precisely because it responses nonlinear in change of speed by using torque converter. That is to say, if a vehicle equipped with the torque converter is parked on the flat ground and the transmission lever set in the D (drive) or R (reverse) position, it becomes to move forward. And further, when a vehicle stops on the sloping place where the vehicle can be halted, and the transmission lever set in the D (drive), the vehicle does not move at the initial stage of step on the pedal of the engine accelerator, but it moves suddenly at certain moment, much faster than expected. For that

reason, the continuously various transmission is needed which response linearly and can operate changing speed precisely and without shock.

On the other hand, the continuously variable transmission has been developed having a various types and use methods, but commercial transmission is almost belt-type continuously variable transmission and the applying range is limited only in the range of small size car. The reason is that the belt-type continuously variable transmission is carried out by using friction force, due to there is a limit of its efficiency by slip between the driving body and intermediary, and the slip between the intermediary and the driven body. Moreover, in order to make the transmission having a better efficiency, the main body of the transmission is to be a big. Therefore, because of such problems, there are many subjects dealing with miniaturized size of continuously variable transmission in the patent applications in respect of continuously variable transmission.

As mentioned above, the continuously variable transmission is an ideal method of change of speed, but there is a limit in applying to all kinds of vehicles, and there are still many problems to be improved.

Disclosure of the Invention Thus, the object of the present invention is to suggest the revolutionary CVT can solve the problems of the conventional CVT. hi order to achieve the object, it is aimed is make the range of application of the CVT is to be from the small-sized car to the large-sized commercial car in the present invention.

Moreover, still other object of the present invention is to provide a wide range of CVT

gear ratio in the present invention. When the vehicle starts by providing the 0 gear ratio, that is infinite of reducing ratio, the geared neutral start is possible which can start most ideally without impact.

And still other object is to provide the CVT which can reduce the cost of manufacturing and its operational expenses. According to the CVT of the present invention, by the section of the change of speed comprises unitary and stepless, thus it is not necessary to have a complicate control apparatus such as a sensor, operational unit and an actuator in order to be automatic the movement among the sections of change of speed and the movement among the stages of change of speed, so the cost of manufacturing is reduced and its operational expenses can also be reduced by high efficiency of the engine.

In order to achieved said objectives in the present invention, which comprises an input means inputting torque; an inclined rotator which connected as curve is possible to the step end opposite to the input side of said input means and rotating with certain angle of inclination; A gear shaft which is formed in the input shaft with a regular interval in radial manner, and a cylinder; A shaking rotating means accepted to a bearing lace having same center is formed between said gear shaft and cylinder; A connecting rod, one end is connected to the inclined rotator and another end is connected to a piston screw combined at said shaking rotator ; A clutch means which transmitting or cutting the torque of the shaking rotator to the gear; A output means connected to said gear; An angle of inclination control means controlling the slope angle of said inclined rotator, one end is connected to said output means and the other end is connected to the tilting

rotating means; and A seesaw lever system, its one end is connected to the slope angle control system, and the other end is connected to the engine accelerating pedal.

And as in the CVT of the present invention, wherein clutch is mechanical dog clutch type or hydraulic clutch type.

Moreover, as in the CVT of the present invention, wherein each friction element minimizing fiction resistance by interposed with bearings.

Brief Description of Drawings Fig. 1 is a side sectional view of transaxle type CVT of FF vehicles in the embodiment according to the present invention; Fig. 2 is a cross sectional view of input shaft (3) in Fig. 1 ; Fig. 3 is a detailed cross sectional view of H-H in Fig. 1; Fig. 4 is a detailed cross sectional view of G-G in Fig. 1; Fig. 5 and Fig. 7 are cross sectional view of shaking rotator (23), the dog clutch (17) and the gear (15) in Fig. l ; Fig. 8 is a detailed cross sectional view of D-D in Fig. 1; Fig. 9 is a cross sectional view of the clutch lever (21) in Fig. 1; Fig. 10 is a detailed cross sectional view of E-E in Fig. 1; Fig. 11 is a cross sectional view of showing the guide ring (19) in Fig. 1; Fig. 12 is a detailed cross sectional view of C-C in Fig. 1 ; Fig. 13 and Fig. 15 are respectively showing the operation of the seesaw lever system marked by A in Fig. 1;

Fig. 16 is a side sectional view of the transaxle type CVT for FF vehicles in the embodiment 2 according to the present invention; Fig. 17 is a detailed sectional view of 1-1 in Fig. 16; Fig. 18 is a side sectional view of the transmission type CVT for FR vehicles in the embodiment 3 according to the present invention; Fig. 19 is a detailed sectional view of J-J in Fig. 18; Fig. 20 is a side sectional view of CVT using a hydraulic clutch as in the embodiment according to the present invention; Fig. 21 is a detailed enlarged view of P-part in Fig. 20; Fig. 22 is a detailed cross-sectional view of 0-0 in Fig. 20; and Fig. 23 is a chart showing a characteristic of the second power output gear against the angle of inclination of the inclined rotator and the rotating speed of the engine.

Best Mode for Carrying Out the Invention Below, each embodiment of the present invention is described in details with reference to the attached drawings.

In order to achieve the purpose of the present invention, the transaxle type is applied to the FF vehicle (FF vehicle=a vehicle equipped an engine in the front of the vehicle having front drive wheel) and an ordinary transmission type is applied to the FR vehicle (FR vehicle = a vehicle equipped an engine in the front of vehicle and having rear drive wheels) and change speed ratio of each CVT is interlocked with the acceleration or deceleration speed controls, and automatically controlled.

Embodiment 1 (The Transaxle Type for FF vehicle) Hereafter, the embodiment 1 of the present invention is explained with attached drawing

as Fig. 1 and Fig. 16.

As shown in Fig. 1, at the housing of the transmission, the input shaft (3), the slave gear shaft (57), the shaft (referred to Fig. 3, 31a) of the holder (31), and the differential means (59) shaft are interposed with bearing (2,16, 46) respectively can rotate freely. Besides, said housing (1) of the transmission supports the after mentioned weight cover (45) by the trust bearings (20), as shown in Fig. 13 or 15, the hole elements are formed which connected to the orifice (5 la, 51c) of the after mentioned counter lever link (51) and to the pins (63,65). And the block rings (69, see Fig. 13) determining the central position of the rod assembly (41) are fixed. Said CVT housing (1) is easy to disassemble and assemble the inner parts, protect the inner parts, lubrication of part is smooth and prevent the lubricating oil does not leak.

As in the CVT of the example 1 of the present invention, the input shaft (3) as an input means, inputting torque, as shown in Fig. 2 is composed of a spline (3a) receiving a torque from the outside on the one end, and an inner lace (3g) on the other end, which is an element of connecting shaft to convey said torque to the after mentioned inclined rotator (29). A big diametrical part larger than that of said spline (3a) is formed between said spline (3a) and inner lace (3g), and the gear a regular interval is kept in a radial manner above the circumference. The circumference is interposed with bearings, thus forming a gear shaft (13c) in the form of central void supporting the gear (15) (refer to Fig. 8). And the shaking rotator (23) as shaking rotating means, the bearing lace (3e) accepting bearing (24), the cylinder part (3f) in the form of spline accepting pistons (24) are formed in order to shaft direction. The orifice (3d) accepting the clutch lever (21) as possible to rotate, which is formed between said bearing lace (3e) and the cylinder part (3f). The second output shaft gear (5) interposed with bearings (6,8) are set up so as to rotate freely between the spline (3 a) of said input shaft (3) and the big diametrical part.

The end part opposite to the spline (3a) of said input shaft (3) is connected to the inclined rotator (29) and the torque of said input shaft (3) is transmitted. As shown in Fig. 1 and Fig. 2, said input shaft (3) and the inclined rotator (29) is connected to the inner lace (3g) formed at end of the input shaft (3), the outer lace (29a) of the inclined rotator (29) combined with said inner lace (3g) and the gauges (28) and a number of balls (26).

On the other hand, each 5 gear shaft (3c), the bearing lace (3e), the cylinder part (3f), and the inner lace (3g) have been formed in a radial manner in this embodiment of the present invention, but this invention is not limited to within. As after mentioned, when the piston (25) makes a reciprocal movement in said cylinder part (3f) according to the rotation of the inclind rotator (29), it will be good if the dog clutch (17) combined with the spline at the outer part of screw part of one piston (25) in said pistons (25), can be connected to the gear (15).

Then, as in the CVT of the embodiment 1 of the present invention, the inclined rotator (29) as a rotating means which is nearly a rotator having a shape of a top, the outer lace (29a) of the universal joint is installed on the center of the surface on the wide side facing opposite to the input shaft (3), as shown in Fig. 3 and a number of spherical grooves are formed with regular interval on the prescribe circumference of the around. Said center position of the spherical grooves (29b) and rotating center of the outer lace (29a) exist in the level of the right angle against the rotating shaft of the inclined rotator (29), and its opposite side is fixed by the nut (30) to the holder (31) interposed with bearings so that a free rotation is made possible.

Said holder (31) supports the inclined rotator (29) to rotate freely, in order to the shaft of the inclined rotator (29) is refracted centering around the center of the universal joint, the shaft (3 lu) of both side of the holder (31) is formed as to be protrude, and the bearing (46) is interposed so the housing (1) of the transmission is rotate freely. And the inclined

rotator (29) controls the inclined angle (a) to the input shaft (3) by forming the arm (31b) at the one side of said holder (31) (refer to Fig. 3).

Said inclined rotator (29) is connected to the piston (25) by a number of connecting rods (27), and both sides of the connecting rods are formed spherically and installed in the spherical grooves (25c) of the piston (25) and in the spherical grooves (29b) of the tilting rotator (29) respectively, can rotate freely (refer to Fig, 4). Herein, the connecting rod (27) should not deviate from the spherical grooves of the piston (25) and the inclined rotator (29) respectively.

Besides, the cylinder part (3f) of said input shaft (3), as shown in Fig. 4, is composed of the grooves which are formed in the big diametrical part of the input shaft (3) facing said inner lace (3g) radically having regular intervals. Said cylinder part (3f) is formed as to be concentric with the hollow-type shaft (3c) supporting the above gear (15). A number of pistons (25) connected to the connecting rod (27) are guided to the spline and are equipped there so that they have free access to it. Herein, the screw part and the spline part (25a) are formed in one in the above respective piston (25); said screw part is combined by screw with the screws formed in the inner circumference of the shaking rotator (23), while, said spline part (25a) is combined with the spline formed in the inner circumference of the cylinder part (3f). In the central part of the section of the spline part (25a), a spherical groove (25c) in the form of sphere is formed, as mentioned above, said spherical groove (25) connected to the connecting rod (27), thereby making the spherical groove (25c) operated (by interlocking it with the inclined of the tilting rotator (29).

The shaking rotator (23) as a shaking rotation means which is connected by screw to the screw part of the piston (25), as shown in Fig. 5, the spline part (23a) is formed on the outer circumference of its end part, and the trust bearing lace (23c) is protruded and formed, and interposed the bearing 24, and it form the bearing lace (3e) of input shaft (3).

Moreover, the screw part (23b) screw combined with screw part of said piston (25) on the inner periphery. Herein, said spline part (23a) is combined with the after mentioned clutch means, that is, the spline part (17a) of the dog clutch (17).

And next, will be explained about the clutch means as in CVT of the example of the present invention. As shown in Fig. 6, the dog clutch (17), in its inner periphery, the spline is formed, the dog (17b) is formed on one end, and the home is formed along the periphery e at the central part of its periphery. Herein, said dog (17b) is to be a pair with the god (15b) formed on after-mentioned gear (15) and said groove (17c) is to be a pair with the latch (21c) of the after-mentioned clutch lever (21).

Said gear 15, as shown in Fig. 7, the gear 15a is formed on the outer periphery of thereto, and dog 15b which can connect to the dog 17b of said dog clutch 17 at one end. Said gear 15, as shown in Fig. 8, is formed can rotate freely by interpose the bearing 14 at the gear shaft 3c formed radically with regular interval at the outer of the big diametrical part of the input shaft part 3.

Moreover, the clutch lever 21 connected to the groove 17c of said dog clutch 17, as shown in Fig. 9 and 10, which having approximately a shape of semi-circular shape, and the tip (21a) and the shaft (21b) is formed as to be protrude at the central part and middle part of the outer periphery respectively, and the latch (21c) is formed as to be protrude in the inner periphery of its open end. Herein, said shaft (21b) is combined to the orifice 3d formed in the input shaft (3) can rotate freely (refer to Fig. 2), said tip (21a) is combined to the grooves (19a, 19b) formed at after-mentioned guide ring (19).

Said guide rings (19), as shown in Fig. 1 and 11, is fixed on the housing (1) of the transmission, and the grooves (19a, 19b) combined the tip (21a) of said clutch lever (21), is formed in the circular direction of inner periphery. Said grooves (19a, 19b) comprises as two parts, that is to say, the groove (19a) which moves the dog clutch (17) to the gear

(15) and connects them, and the groove (19b) separates each dog clutch (17) and the gear (15).

On the other hand, the respective gears (15) are installed on the gear shaft (3c) of the input shaft (3) interposed with bearings (14) and are connected or separated from the dog clutch (17), thus transmitting or cutting the torque and they are connected to the output power means as shown in Fig. 1 and 8.

Said output power means as in the CVT of the embodiment 1 of the present invention, comprises the first output power gear (13), the second output gear (5), the slave gear and the differential gear. Herein, said gear (15) is geared to the inner circumference of said first output gear (13). The gear is formed at the part of the said first output power gear (13) and the gear (15) are touched internally, and the spring seat (13a) is formed at its opposite side of the connecting the second output power gear (5) as shown in Fig. 12.

The spring seat (5a) is formed in the inner circular line of said second output gear (4), as shown in Fig. land 12, and receiving a torque from the spring seat (13a) of said first output gear (13), with interposing damping spring. Moreover, the gear (5b) geared after- mentioned slave gear (57a, 57b) is formed on the outer periphery of said second output gear (5). Herein, said second output (5) is installed on the input shaft (3) can rotate freely with interposing the bearing (6,8).

At the slave gear shaft (57), as shown in Fig. 1, the slave gear (57a, 57b), and the fly weight shaft (55) are formed in order in the direction of the shaft with forming the same central axis. Herein, the slave gear (57b) and the differential gear (59) are geared and transmit a driving force to the drive wheels.

A spline is formed on said fly weight shaft (55), and connects to the control means of inclined angle of the tilting rotator. Said control means of inclined angle comprises rod assembly (41) connected to the inclined rotator, the housing (1) of the transmission, the

weight cover (45,49) positioned at the push rod (53) with interposing bearing and the counter lever link 51 connected (or separated) with said rod assembly (41), push rod (53) and housing of the transmission by the pin.

Herein, said fly weight shaft (55) transmits the torque to the weight cover (45,49) by the spline formed on said shaft, and when said weight cover (49) is expand and narrows by centrifugal force of said weight cover (49) along the axis, it guides the push rod (53) which contact with weight cover (49), can move along the axis of said fly weight (55).

Said weight cover (45,49) equip a number of weight (47) and when it rotating, can rotate with guiding the weight (47) moves to the direction of circumference by a centrifugal force.

Said push rod (53) closes said weight cover (49) by interposing the trust bearing 22, and installed on axis (55) of said fly weight and can move along the axis. Herein, said push rod 53 is connected to after-mentioned counter lever link 51 and the transmission link 61d.

On said counter lever link (51), as shown in Fig. 13 and 14, the push rod (53) is pierced and installed in said counter lever link (51) and in the direction of the counter lever lengthwise are formed four holes (51a, 51b, 51c, 51d). Herein, said holes (51a, 51c) are connected to the housing (1) of the respective transmission through the pin (63), the hole (5 lb) is formed as a lengthy hole and connected to the shaft of the push rod (53) by using pin (53a) and the hole (52d) is connected as can rotate freely to the yoke (41i) formed on the front step of the rod assembly (41) by using a pin (67).

Said assembly (41), as shown in Fig. 13, forms a yoke (41i) and a ball joint (41a) on its both ends respectively, and the rod (41d) formed between both ends is pierced and installed in the block ring (69) with interposing two washers (41f, 41e) and the spring (41g, 41c) are installed by the nuts (41h, 41b) and the washers (41f, 41e) on the both ends of the rod (41d) on the boundary of said block ring (69). At the ball joint (41a) formed on

the end part of said rod assembly (41), the arm (31b) of the holder (31) is inserted and is contracted by the nut (18).

Next, explain the seesaw lever system (61) which is interlocked with engine to control the gear ratio of the CVT with reference to Fig. 13 and 15.

Said seesaw lever system (61) comprises the engine accelerating pedal (61a), the link (61b) connecting said engine accelerating pedal (61a) and the seesaw lever (61c), the transmission link (61d) connecting said seesaw lever (61c) and the push rod (53), and the engine accelerating link (61d) connecting said seesaw lever (61c) and engine governor (not shown), and herein, said seesaw lever (61c) performing the seesaw function centering around link (61b) connected to its central part.

On the other hand, as in the CVT of the present invention, the composition to insert or eliminate the pins (63,65) connected to the counter lever link (51) by operating them is done by the input and output power devices which make said pins (63,65) operated so as to be interlocked with the drive and reverse motion of the shift lever. For example, the pins are inserted or eliminated by the manipulator operated in a hydraulic or air pressure and electrical law, these are enough to accept the technique of the disclosure publication, so the detailed explanation is omitted. Moreover, the composition of connecting the shift link (61d) to the outside and installing the transmission to the external engine or the source of drive may be the same as the already disclosed techniques. Therefore, the detailed explanation or its illustration of drawing is also omitted here.

Hereafter, explain the operation of said embodiment 1 of the present invention.

First, if the input shaft (3) is rotated by the driving force from the outside, said rotation the shaking rotator (23) and the dog clutch (17) racing with the same speed as that of input shaft through the screw parts (25a) of the piston inserted in the inner part of the gear shaft (3c), meanwhile, the first output gear (13) rotate by interposing the gear connected

to said dog (17), the second output gear (5) and the slave gear (57a) geared to said second output power (5) are rotated according to the rotation of said first output gear (13).

Meanwhile, the inclined rotator (29) connected to the inner lace (3g) formed on the end of said input shaft (3), by universal joint according to said input shaft (3), and it rotates with same velocity of input shaft (3) through the medium of numerous balls (26), at this time, according to inclination angle of said inclined rotator (29) and the input shaft (3), the connecting rod (27) connected to said inclined rotator (29) is moved alternating in the direction of the shaft.

According to the reciprocating movement of said connecting rod (27), the piston (25) connected to the other end of the connecting rod (27) makes a reciprocating movement in the cylinder part (3f) of the input shaft (3), and the shaking rotator (23) connected by screw with the screw part (23) formed on the end of the piston (25) according to the reciprocating movement of said piston (25), begin to make a shaking rotation (for instance, automatic rotation). According to the shaking rotation of the shaking rotator (23), the dog clutch (17) installed on the spline (23a) of the shaking rotator (23) is connected to or separated from the gear (15) as the tip (21a) of the clutch lever (21) rotates, following the grooves (19a, 19b) of the guide ring (19). At this time, the dog (17b) of the dog clutch (17) connecting and separation repeatedly the torque of the shaking rotator (23) is transmitted to the first output gear (13).

Herein, the shaking rotator (23) combined with the piston (25), as shown in Fig. 23, changes the transmit speed according to the angle of the inclination Q of the inclined rotator (29).

For example, if angle of the inclination Cl is 90 degree, the shaking rotator (23) does not rotate and comes to halt, although the input shaft (3) rotates, because the piston does not makes a reciprocating movement. Besides, one of the dog clutches (17) connected to the

first output gear (13) holds said first output gear (13) and then the first output gear (13) rotates the same direction and speed of the input shaft (3).

However, if the angle of the inclination a is larger than 90 degree, the input shaft (3) rotates, the each piston (23) makes a reciprocating movement and the shaking rotator (23) rotates. At this time, each shaking rotator (23), clutch lever (21) and dog clutch (17) add the torque having opposite to the direction of the first output gear (13), and reduce the speed of the first power gear (13) that much.

On the contrary, if the angle of the inclination a of the inclined rotator (29) is smaller than 90 degree, it transmits a more increase speed than that of the input shaft (3) to the first output gear (13), thus increasing the speed of the first output power gear 13.

On the other hand, the torque transmitted to the first output gear (13) is transmitted to the driving wheel through the second output gear (5), the slave gear (57a, 57b) and the differential gear (59). Herein, the impact produced when the torque of the first output gear (13) transmitted to the second output gear (5), becomes relieved through the damping spring (11) installed between said first and second output gears (13,5).

Hereafter, explain the operation of the counter lever link (51) with reference to the Fig. 13 and 15.

The counter lever link (51), as shown in Fig. 13, is fixed to CVT housing with the pins (63,65), the transmission link (61b) does not operate even if the accelerating pedal is stepped on, but only the accelerating link (61e) of the engine operates, thus it becomes the accelerating or decelerating the rotating speed of the engine.

Herein, if remove the pin (65), as shown in Fig. 14, the rotation of the counter lever link (41) is possible centering around the pin 53, so if the accelerating pedal is stepped on, the transmission link (61d) and the accelerating link (61e) of the engine operate at the same time, thereby the gear ratio in the forward direction of the angle of inclination D of the

inclined rotator (29) is increased through the rod assembly (41), and also the speed of the engine is increased. At the beginning of accelerating speed, the speed of the engine increases relatively, but the speed of the fly weight shaft (55) is increased by increasing speed of the output power gear gradually, so that it increasing the centrifugal force of the fly weight (47), so the accelerating link of the engine (61e) is operated in such way that the engine speed is reduced relatively by moving the push rod (53). As such, only through treading on the accelerating pedal of the engine (61a), the vehicle drives with the proper gear ratio.

On the contrary, as shown in Fig. 15, the state of pin (65) is inserted and after pin (63) is removed, it makes that the pin (65) becomes the axis of the rotation of the count lever link (51) thereby the vehicle drives backward when the accelerating pedal of the engine (61a) is stepped on in a state.

On the other hand, the bearing can be installed in order to minimize the resistance of friction of various frictional elements in the CVT of the present invention. That is to say, interposing ball bearing at the area where the friction between the members such as gap which combined by screw with piston (25), the cylinder part (3f) of the input shaft (3), the screw part (25a) of the piston (25) and the screw part (23a) of the shaking rotator (23), so that it makes the friction resistance to be minimize.

Embodiment 2 (Transaxle Type for FF Vehicles) Next, below is the detailed description of the present invention with references to the Figs. 16 and 17.

The embodiment 2 of the present invention is a transaxle-type for FF vehicles, it is all the same with the construction of said embodiment 1, only different from construction related to the gear combination of the first output gear (13) and the gear (15). So the same

marks are used herein about the same construction as the embodiment 1, and the detailed explanation is omitted.

The different factor of the embodiment 2 to embodiment 1 is that the gear in the embodiment 1 is constituted as it touched internally with the ring gear (13a) of the first output gear (13), but in the embodiment 2 these elements are constituted so that they are touched externally. That is to say, as shown in Fig. 17, the gear (15) is geared as touched externally on the first output gear (213), and the groove is formed on the big diametrical part of the input shaft (13) formed the gear shaft (203c) thereon, in the direction of shaft lengthwise, wherein the first output gear (213) is inserted and set up. Moreover, the gear (15) is touched externally to the first output gear (213), the screw direction of the screw part of the piston (25) and screw part of the shaking rotator (23) is opposite to the embodiment 1.

Meanwhile, the other composition and operation is the same as those of the embodiment 1, thus the detailed explanation is omitted.

Embodiment 3 (Transmission-Type for FR Vehicles) Hereafter, below is the detailed description of the present invention with references to the Figs. 18 and 19.

The embodiment 3 of the present invention is a transmission-type for FR vehicles, it has a difference of the composition of the input shaft (3), the inclined rotator (29) and the differential gear (59) of the embodiment compare with embodiment 1.

That is to say, torque is inputted through the input shaft (3) and outputted via the second output gear (5) in the embodiment 1, but in the embodiment 3, as shown in Fig. 18, the input shaft (403) installed by interposing the bearing 332 on the housing 1 of transmission on the inclined rotator (329), and torque is inputted via the spline (403a)

formed on end part of said input shaft (403).

Moreover, installing the output shaft (405) having the same center as the input shaft (405) and can face each other and is made up as outputting via spline (405c) formed on the end part of said output shaft.

Besides, in the output shaft (405) on the side facing to said input shaft (405), the second output gear is formed in one body and the slave gear is geared on said second output gear. Here, said input shaft (403) is connected with interposing the bearing (8) on the inner periphery of the second output gear formed as one body, and also the first output gear (13) is installed on the second output gear of said output shaft (405) with interposing the bearing (10).

Moreover, as shown in Figs. 18 and 19, the inclined rotator (329) in the present embodiment 3 is formed in a shape of donuts having certain thickness, and said inclined rotator (329) is formed with certain thickness, wherein the holder (331) is supported with interposing the bearing in order to accept said inclined rotator (329).

Further, in the present embodiment 3, forms the gear shaft (3c), the bearing lace (3e) and the cylinder part (3f) in the input shaft (403) in the same shape with that of the embodiment 1 in order from the side of the second output gear of said output shaft (405).

Meanwhile, as in the present embodiment 3, the other structure and operation is the same with the those of the embodiment 1 and 2, thus the same marks are given to the same structure, and detailed explanation is omitted.

Embodiment 4 Hereinafter, below is the detailed description of the embodiment 4 of the present invention with references to the Figs. 19 and 22.

The embodiment 4 is that it transmits the torque of the shaking rotator (23) to the gear

(13) using the hydraulic clutch instead of dog clutch (17), the clutch lever (21) and the guide ring (19) used in said embodiments 1 and 3. Herein, the hydraulic clutch comprises the gear (715), the disk (717), the hydraulic clutch pack (715b), and oil circuit ring (719) and as shown in Fig. 22, the fluid road (703h) is formed in the input shaft (703). Herein, said input shaft (703) is the same of the embodiment 1 except for composition related part of said hydraulic clutch.

In the inside of said respective hydraulic clutch pack (715b), the disk (717a), (717b) connected to the spline (715c) formed on the inner periphery of the gear and to the spline (23a) formed in the outer periphery of the shaking rotator (23), are installed crosswise.

And the fluid road (703h) is formed in the hydraulic clutch pack (715b) accepting the piston (712) to compress the above mentioned connected device.

Moreover, said oil circuit ring (719), as shown in Fig. 21, is fixed in the housing 1 of the transmission and rotates freely against the input shaft. As shown in Fig. 22, if the hydraulic pressure is put to the P port of said oil circuit ring (719), the hydraulic pressure is put to the hydraulic clutch pack (715b) via the fluid road of the input shaft. And while the input shaft rotates, the hydraulic clutch transmits the torque of the shaking rotator (23) to the gear (715), and the transmitted torque at said gear (715) is transmitted back to the gear (13).

As in the present embodiment 4, the other structure and operation are the same as those of above mentioned embodiments, so, the same marks are given to the same composition and the detailed explanations are omitted.

Industrial Applicability According to the present invention, the limit of application of CVT is can extent to not only small-sized cars but also to large-sized commercial vehicles that is to all kind of

vehicles. Thus, conventional CVT accepts the indirect power transmission through the friction power of the belt can slip easily and roller, so only applicable to small-sized car in the vehicle cannot limit to the size, however, the CVT of the present invention accepts the transmission method through the dog clutch or hydraulic clutch having high efficiency same as the gear transmitting the power. So CVT is can be produced as a size of manual transmission or an automatic transmission.

Moreover, it accepts the geared neutral start system having endless speed reduction ratio, so the starting of vehicle becomes smooth without conventional clutch or torque converter and this brings about correctness of driving. That is to say, in the case of manual transmission, the operation of starting vehicle requires skill, and when starting a vehicle on sloping hill, it needs more skillful operation of starting a vehicle and consumption of fuel. In addition, in case of the automatic transmission accepting a torque converter, when the transmission lever is set to the driving position or to the reverse position, certain torque is transmitted to the final driving part constantly in order to have a good initial response, thus the brake is used all the time, nevertheless, in case of starting a vehicle on the hill having more than a certain gradient, the vehicles tend to move backward at the moment when the foot moves from the brake to the accelerating pedal.

On the contrary, as for the CVT of the present invention, even if the clutch operation or not even the stepping on the brake, the moving backward situation of the vehicles does not occurred and the vehicle start promptly by only stepping the engine accelerating pedal, so its operation is simple.

Moreover, according to the CVT of the present invention, the energy cost is reduced.

That is to say, it is possible to start vehicles by using minimum energy and it does not accept the mechanical clutch or the hydraulic converter so energy consumption when slip of the mechanical clutch or the hydraulic sip of the hydraulic converter can be reduced efficiently. In addition, the scope of continuously transmission is wide, so vehicles can be driven in range of good fuel mileage of the engine.