INFINITELY VARIABLE SPEED TRANSMISSION

Abstract: Disclosed is an infinitely variable speed transmission, including: a first speed changing mechanism (10) for primarily changing power from an engine (E) into a necessary speed ratio, including: a sun gear (18) disposed on an input shaft (12) for transmitting power generated from the engine (E); a plurality of planet rollers (20) which are disposed around the sun gear (18) at a predetermined distance from each other, each planet roller (20) having a truncated cone-shape and being revolvable around the sun gear (18) and rotatable about its axis (22); a carrier (26, 28) for connecting the planet rollers with each other; a movable ring (24) disposed to be circumscribed on outer tangential line of the planet rollers (20) and movable by a moving member (34) along a longitudinal direction of the planet rollers (20) to change a rotational speed of the planet rollers (20) by varying an operating diameter so that an output speed outputted through the carriers (26, 28) connecting the planet roller with each other can be varied; and a second speed changing mechanism for finally changing the output speed from the first speed changing mechanism (10) as a necessary final output speed, including: low and high speed control member (46, C1, C2) which are selectively connected with the first speed changing mechanism.

Description: INFINITELY VARIABLE SPEED TRANSMISSION FIELD OF THE INVENTION The present invention relates to a transmission for infinitely variable power transmitted from a power generating system to a driving means into a necessary speed ratio, and particularly to a friction wheel-type of an infinitely variable speed transmission which is compact in size, has improved power transmission efficiency, and can widen the speed changing range. BACKGROUND OF THE INVENTION Generally, automotive vehicles use a transmission controlling output of a power generating means so that rotational speed of the power generating means can be controlled to be appropriate for the load applied to the driving means and operating state thereof. Transmissions used for this purpose can be classified into two types. One is a manual transmission which is manually shifted to each speed changing stage, and the other is an automatic transmission which can be automatically shifted to each speed changing stage. In recent years, the automatic transmission has been popular because of the convenience in its manipulation. Furthermore, in the automatic transmission, various speed ratios are predetermined and the automatic shift is accomplished while various operating elements arc selectively operated in accordance with th vehicle's driving condition. Accordingly, the conventional automatic transmission generally comprises a plurality of planetary gear units, a plurality of friction elements for controlling each elements of the planetary ear unit, and a complex control system for controlling the operating elements. This results in complicating and enlarging the structure thereof. Therefore, it is impossible to commonly applv the automatic transmission specified as an fixed model to various driving means. In addition, when applying the automatic transmission to the driving means such as automotive vehicles, the big size of the automatic transmission requires a big mounting space, resulting in making it difficult to mount the specified automatic transmission into the various type of vehicle. Furthermore, in the conventional automatic transmissions, the shift operation is not accomplished linearly. That is, a speed change from one stage to another stage is not continuously realized such that the engine which is the power generating device is overloaded, thereby deteriorating ride comfort by shift shock. To solve the above described problems of the conventional automatic transmission, there has been developed infinetely variable speed transmission which can continuously accomplish the speed changing operation in accordance with the vehicle's driving condition, thereby preventing the speed changing shock to improve ride comfort as well as preventing the engine from being overloaded. An example of this kind of transmission is disclosed in U.S. Patent No. 4,641,548. The size of the this transmission described in the U.S Patent, however, becomes larger since it comprises a plurality of operating elements such as disks, pistons and the like. Furthermore, since the transmission is designed such that a plurality of shift mechanisms are arranged on a common axis in a series, the length of the transmission becomes longer. This makes it difficult to apply the transmission to automotive vehicles which have limited space for the mounting of parts. In addition, there is another problem in that it is not economical to apply the transmission to a practical vehicle side since the transmission is costly. SUMMARY OF THE INVENTION Therefore, the present invention is made in an effort to solve the above described problems of the prior transmission. It is an object of the present invention to provide an infinitely variable speed transmission which is comaμci in size and has smalle number of operating elements so that the structure thereof is simple, and can be operated in the wide speed changing range. It is another object of the present invention to provide an infinitely variable speed transmission which can infinitely change the speed, which can smoothly accomplish a speed changing from a medium speed range to a high speed range. To achieve the above objects, the present invention provides an infinetly variable speed transmission, comprising: a first speed changing mechanism for primarily changing rotational speed from an engine into a necessary rotation speed, including: a sun gear disposed on an input shaft which receives the power from the engine; a plurality of planet rollers which are disposed around the sun gear at a predetermined distance from each other, each planet roller having a truncated cone- shape and being revolvable around the sun gear and rotatable about its axis: a carrier for connecting the planet rollers with each other and outputting the rotational troque changed in the planet rollers; a movable ring disposed to be circumscribed on outer peripheral lines of the planet rollers and movable by a moving means along the longitudinal direction of the planet rollers to change rotational speed of the planet rollers by varying a rotating diameter thereof to the movavble ring so that the output speed outputted through the carrier connecting the planet rollers with each other can be varied; and a second speed changing mechanism for finally changing the output speed from the first speed changing mechanism into a necessary final output speed, including: a planetary gear unit mounted on an output shaft; a low speed control means having a first clutch for controlling a operation of the planetary gear unit; and a high speed control means having a second clutch mounted on the output shaft; the planetary gear unit and the second clutch being parallel and directly connected with the carrier of the first speed changing mechanism: and the planetary gear unit being directly connected with the input shaft through the first clutch. And, a one way clutch is installed between the both friction plates of the first clutch to obtain smooth speed changing from a medium speed range to a high speed range. According to the features of the present invention, the peripheral line of the rollers contacting the movable ring is defined to be parallel to the input shaft such that each distance from the input shaft to the circumscribed circle of the planet rollers is the same over the whole length of each planet roller. Therefore, the movable ring can move along the longitudinal direction of the planet rollers in a state where the movable ring contacts the outer perepheral line of the planet rollers with constant pressure. As described above, by means of the movable ring along the longitudinal direction of the planet rollers, the revolving diameter of the planet rollers rotating in an inscribed state on the movable ring is varied linearly along the longitudinal direction of the truncated cone-shaped planet rollers, whereby the rotational speed outputted through the carriers interconnecting the planet rollers is changed linearly even under the same rotational speed thereof, thereby accomplishing the primary speed changing operation. According to another feature of the present invention, the low control means of the second speed changing mechanism is comprised of a planetary gear unit carried on an output shaft and a first clutch for controlling the planetary gear unit, and the high speed control means thereof is comprised of a second clutch carried on the output shaft. Both of the planetary gear unit and the second clutch are connected with the carrier of the first speed changing mechanism to be parallel therewith. One element of the planetary gear unit is also directly connected with the input shaft through the first clutch. Therefore, the planetary gear unit is designed to have two input elements so that the rotational speed controlled in the first speed changing mechanism and rotational speed of the engine can be simultaneously inputted thereto. Accordingly, by selection of the low speed control means and the high speed control means, the rotational speed which is primarily changed in the first speed changing mechanism is finally changed once more and differently outputted to the output shaft according to the locking state of the first clutch or second clutch. That is, in case where the first clutch is locked, rotational speed changed in the first speed changing mechanism and rotational speed of the engine can be simultaneously inputted to the planetary gear unit. The rotational speed inputted to planetary gear unit is changed to a proper speed ratio by combination of the operating elements in the planetary gear unit and outputted to the output shaft. Accordingly, in the first speed changing mechanism which receives constant rotational speed of the engine, when the contacting position between the movable ring and the planet rollers is varied in accordance with the movement of the movable ring along the planet rollers, the output rotational speed of the first speed changing mechanism is also varied and this changed rotational speed is then transmitted to the planetary gear unit and changed fianally therein. That is, since the rotational speed changed in the first speed changing mechanism and the rotational speed of the engine are combined and changed in the planetary gear unit and the changed result is transmitted to the output shaft, the output speed of the planetary gear unit is varied according to the variation of the rotational speed transmitted from the first speed changing mechanism to the planetary gear unit. This operation of the planetary gear unit is realized by locking the first clutch so that the rotational speed of the first speed changing mechanism and the engine are simultaniously transmitted to the planetary gear unit. On the one hand, when the second clutch is locked instead of the first clutch, since no rotational speed of the engine is transmitted to the planetary gear unit through the first cluch, the planetary gear unit is set to be in an idling stale and rotational speed transmitted from the first speed changing mechanism is directly transmitted to the output shaft through the second clutch. Accordingly, since the rotation il speed changed in the first speed changing mechanism is directly transmitted to the output shaft through the first clutch without being further changed, the rotational speed higher than that when the first clutch is locked is outputted. Therefore, when the second clutch is locked, the final output is operated at a higher speed than in the case where the first clutch is locked. Furthermore, as the output rotational speed of the first speed changing mechanism is increased, the speed of vehicle is gradually increased. According to still another feature of the present invention, each planet roller can be made up of one truncated cone-shaped body or two truncated cone-shaped bodies which are combined such that large diameter end of the planer rollers are opposite to each other. In case of latter, the speed chang range can be widened. BRIEF DESCRIPTION OF THE INVENTION The accompanying drawings, which are incorporated in and constitute a part of the specification, illustrate an embodiment of the invention, and, together with the description, serve to explain the principles of the invention: Fig.l is a schematic diagram illustrating an infinitely variable speed transmission in accordance with a first embodiment of the present invention; Fig. 2 is a schematic diagram illustrating a continuously variable transmission in accordance with a second embodiment of the present invention: Fig. 3 is a schematic diagram illustrating an infinitely variable speed transmission in accordance with a third embodiment of the present invention; Fig. 4A is a schematic diagram showing a state where the transmission depicted in Fig. 3 is in a first low speed level outputted from a neutral state: Fig. 4B is a schematic diagram showing a state where the transmission depicted in Fig. 3 is in a second low speed level: Fig. 4C is a schematic diagram showing a state where the transmission depicted in Fig. 3 is in a third low speed level: Fig. 5A is a schematic diagram showing a state where the transmission depicted in Fig. 3 is in a first high speed level: Fig. 5B is a schematic diagram showing a state where the transmission depicted in Fig. 3 is in a second high speed level; Fig. 5C is a schematic diagram showing a state where the transmission depicted in Fig. 3 is in a third low speed level; Fig. 6 is a table illustrating the combination of acting elements at each speed mode of the transmission according to the third embodiment of thepresent invention; Fig. 7 is a graphical illustration of an equation of speed outputted from the planetary gear unit depicted in Fig. 3; Fig. 8 is a schematic diagram illustrating an infinitely variable speed transmission in accordance with a fourth embodiment of the present invention; Fig. 9 is a partial sectional view illustrating an embodiment of a load cam depicted in Fig. 8; Fig. 10 is a partial sectional view illustrating another embodiment of the load cam; Fig. 11 is a schematic diagram illustrating an infinitely variable speed transmission in accordance with a fifth embodiment of the present invention: Fig. 12 is a schematic diagram illustrating an infinitely variable speed transmissionsion in accordance with a sixth embodiment of the present invention: Fig. 13 is a schematic diagram illustrating an infinitely variable speed transmission in accordance with a seventh embodiment of the present invention: Fig. 14 is a schematic diagram illustrating a transmission where a position sensor for detecting a moving distance of the movable ring is applied: Fig. 15 is a schematic diagram illustrating an infinitely variable speed transmission in accordance with an eighth embodiment of the present invention: Fig. 16 is a table illustrating combination of acting elements at each speed mode of the transmission according to the eighth embodiment of the present invention; and Fig. 17 is a graphical illustration of a speed outputted from the transmission depicted in Fig. 15. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT Reference will now be made in detail to the present preferred embodiment of the invention, an example of which is illustrated in the accompanying drawings. Wherever possible, the same reference numbers will be used throughout the drawings to refer to the same or like parts. Fig.l shows schematically an infinitely variable speed transmission in accordance with a first embodiment of the present invention. The transmission comprises a first speed changing mechanism 10 for primarily changing rotational speed from an engine E arranged on an input shaft 12 to which the rotational speed from the engine E is transmitted, and a second speed changing mechanism 14 meshing with the first speed changing mechanism 10 to finally change the rotational speed changed in the first speed changing mechanism 10 and output it to an output shaft 16. The first speed changing mechanism 10 includes a sun gear 18 splined on the input shaft 12, a plurality of planet rollers 20 which are disposed around the sun gear 18 at a predetermined distance from each other, each planet roller 20 having a truncated cone-shape and being revolvable around the sun gear 18 and rotatable about an pivot axis 22, a movable ring 24 disposed to friction contact outer tangential lines of the planet rollers 20 with a predetermined pressure and movable along the longitudinal direction of the planet rollers 20 to change rotational speed of the planet rollers 20, and support and output carriers 26 and 28 for interconnecting the planet rollers 20 and outputting rotational speed changed by the planet rollers 20. Each planet roller 18 is provided with a gear 30 which meshes with the sun gear 18 so that the planet roller 20 can receive rotational speed from the sun gear IS. The support and output carriers 26 and 28 respectively support both sides of the planet rollers 20 to be rotatable about a pivot axis 22 of the planet roller 18. The output carrier 28 is provided with a transfer drive gear 32 for transferring the changed rotational speed in the first speed changing mechanism 10 to the output shaft 16. The movable ring 24 is designed not to rotate but to reciprocate by a moving member 34, such as a hydraulic cylinder, a solenoid valve or a worm gear, along the longitudinal direction of the planet rollers 20. Accordingly, the planet rollers 20 which are inscribed on the movable ring 24 rotate about their pivot axes 22 and revolve around the movable ring 24. Therefore, the movable ring 24 performs the same function as the ring gear of the common planetary gear unit such that it can receive power to thereby serve as a supporting member for the planet rollers 20. As a result, as the supporting point for the planet rollers 20 which rotate about the pivot axis 22 in a constant speed by the rotational speed transformed from the sun gear 18 varies, and the rotational speed of the planet roller 20 around the movable ring 24 is also infinitely variable. Furthermore, to make the movable ring 24 move along the outer tangential line S of the planet rollers 20 having an infinitely variable diameter along its longitudinal direction while contacting with a constant pressure, as shown in Figs. 1 and 2, the planet rollers 20 are arranged such that their outer tangential lines S are to be parallel with the input shaft 12. As the planet rollers 20 are major elements for the speed changing operation within the first speed changing mechanism 10, each planet roller 20 rotates about the pivot axis 22 while receiving speed from the sun gear 18 and revolves around the movable ring 24. At this point, as the diameter of the supporting point supported by the movable ring 24 is varied, the rotational speed is also varied. That is, since the supporting point where the movable ring 24 and the planet rollers 20 contact is varied as the movable ring 24 associated with the moving member 13 moves along the outer tangential line S of the truncated cone shaped planet rollers 20 in its longitudinal direction in accordance with the expansion and contraction operations of the moving member 34, the revolving diameter defined when the planet rollers 20 revolves with respect to the movable ring 24 is varied linearly. This linear variation of the revolving diameter makes the rotational speed of the planet rollers 20 with respect to the movable ring 24 vary linearly. As a result, the constant rotational speed from the engine is changed linearly. On the assumption that load applied to a driving means is the same in a state where the engine E operates with a same condition in a specific point, the rotational speed transformed to the gear 30 of the planet roller 20 meshing with the sun gear 18 becomes constant to thereby make the rotational speed constant. However, since the contacting diameter between the planet roller 20 and the movable ring 24 is varied as the movable ring 24 moves along the longtudinal direction of the planet roller 20, the revolving diameter of the planet rollers 20 is also varied. Accordingly, since the variable speed of the planet rollers 20 is transformed through the povot axis 22 to the output carrier 28 interconnecting the planet rollers 20, the rotational speed of the transfer drive gear 32 mounted on the output carrier 28 is to be varied while increasing and reducing. Consequently, the linear variation of the output rotational speed of the first speed changing mechanism 10 makes the rotational speed of the output carrier 28 interconnecting the planet rollers 20 increase when the movable ring 6 is contacted with a large diameter portion of the planet rollers 20. and reduce when the movable ring 24 is contacted with a small diameter portion of the planet rollers 20. Therefore, as the movable ring 24 moves from the large diameter portion to the small diameter portion of the planet rollers 20. each rotational speed of the output carrier 28 and the transfer drive gear 32 connected with the output carrier 32 becomes decreased. On the one hand, in the first speed changing mechanism 10 as described above, the arrangement state of the pivot axis 22 of the planet rollers 20 can be variably mounted. That is, according to a first embodiment as shown in Fig. 1, the pivot axis 22 of the planet roller 20 can be separated and a bearing 36 is mounted between the planet roller 20 and the pivot axis 22 to improve the rotating performance therebetween. According to a second embodiment as shown in Fig. 2. the planet roller 20 is designed to be integral with the pivot axis 22 and bearings 36 and 38 are respectively mounted on opposite ends of the pivot axis 22. This integral design makes the planet roller 20 longer than that of the first embodiment, resulting in widening the variable speeed range. According to a third embodiment as shown in Figs. 3 to 5, each planet roller 20 is made up of two truncated cone-shaped bodies while the planet roller 20 disclosed in the first and second embodiments is made up of one truncated cone-shaped body. That is, the planet roller 20 is made up of two truncated cone-shaped bodies 20a and 20b which are combined such that they are symmetrically faced with each other at their large diameter portions. In the latter case, the speed changingrange can be widened. A bearing 20c is mounted between the two truncated cone-shaped bodies 20a and 20b for smooth sliding of the body 20b inside of the other body 20a when the pressure from the movable ring 24 is applied to the body 20b, as the movable ring 24 moves along the surface of the body 20b. The two truncated cone-shaped bodies always rotate in one body and are arranged to be movable toward each other. For this movement, the two truncated cone-shaped bodies 20a and 20b may be coupled by interposing a coupling member such as a ball spline therebetween. When using the two cone-shaped bodies 20a and 20b as a means for transferring power of the engine, a movable sun ring 40 is used. The sun ring 40 is splined on the input shaft 12 to rotate therewith and is movable in a longitudinal direction of the input shaft 12. And, like the movable ring 24, the movable sun ring 40 also tightly contacts the inner tangential lines SI of each planet roller 20 with a predetermined pressure. A moving member 42 such as a hydraulic cylinder, a solenoid valve, or a worm gear, is used for moving the movable sun ring 40. In the first speed changing mechanism using the two truncated cone shaped bodies 20a and 20b as the planet roller 20. one body 20a is circumscribed on the movable sun ring 40 and the other body 20b is inscribed on the movable ring 24. The movable sun ring 40 and the movable ring 24 respectively move by the moving members 34 and 42 along the longitudinal directions of the bodies 20a and 20b while contacting the bodies 20a and 20b both having a variable diameter. For enabling this, the bodies 20a is arranged such that the surfaces S which is respectively designed to be in contact with the movable sun ring 40 and the movable ring 24 are designed respectively to be parallel to the input shaft 12. Accordingly, when the input shaft 12 rotates to thereby rotate the sun ring 40, the rotational speed of the movable sun ring 40 is transformed to the planet roller 20 by tight contacting force between the movable sun ring 40 and the body 6a, thereby rotating the planet roller 20. At this point, since the movable ring 24 fixed in a rotating direction supports the planet roller 20, the planet roller 20 rotates about the pivot axis 22 which is inserted through the planet roller 20 and revolves around the movable ring 24. The rotational speed of the movable ring 24 is varied in accordance with the positions of the movable ring 24 and the movable sun ring 40, thereby accomplishing the speed changing operation. The speed changing operation of the planet roller 20 is linearly realized as the movable sun ring 40 and the movable ring 24 moves respectively along the bodies 20a and 20b of the planet roller 20 by the moving members 34 and 42 respectively. That is, when the movable sun ring 40 moves along each surfaces of the planet rollers 20 in the longitudinal direction in a state where the position of the movable ring 24 is fixed, a circular diameter defined where the movable sun ring 40 is to be in contact with each body 40a having a variable diameter is to be varied. This operation will be described more in detail hereinafter referring to Fig. 1 and Fig 3. When the movable sun ring 40 is displaced toward each large diameter portion of each cone- shaped body 20a, since the supporting point with re ided to the movable ring 24 is fixed, the rotational speed of each planet roller 20 becomes reduced, whereby the rotational speed thereof becomes reduced. On the contrary, when the movable sun ring 40 is displaced toward each small diameter portion of each cone shaped body 20a. since the rotating diameter of each planet roller 20 becomes reduced, resulting in increasing the rotational speed of each planet roller 20. As a result, the rotational speed of the planet rollers 20 around the movable ring 24 is to be increased. Further, when the position of the movable sun ring 40 is fixed and the movable ring 24 is displaced along each cone-shaped body 20b of the planet rollers 20 while being in contact therewith, the rotational speed transferred from the movable sun ring 40 to the cone-shaped body 20a is constant, but the moving distance of the planet rollers 20, which are supported inside the movable ring 24, thereby being revolvable around the sun gear, increases or decreases in proportion to the contacting diameter of the movable ring 24, thereby accomplishing the speed changing operation. This variable speed is transmitted to the second speed changing mechanism 14 through the output carrier 28. During the speed changing operation as described above, as the diameters of the planet roller 20a and 20b are linearly varied, the speed changing is also linearly accomplished. Consequently, the transmission according to the invention makes it possible to linearly vary the rotational speed in the constant engine RPM. The first speed change mechanism 10 in accordance with the third embodiment, the speed changing operation is accomplished through both cone-shaped body 20a and 20b, so that the whole speed changing range is widened. The shift control mechanism 14 which receives the rotational speed firstly changed in the first speed changing mechanism 10 and varies it secondly, comprises a transfer driven gear 44 mounted on the output shaft 16, a low speed control means including a planetary gear unit 46 and a first clutch Cl. and a high speed control means having a second clutch C2 wherein the transfer driven gear 44 meshes with the transfer drive gear 32 mounted on the output carrier 28 of the first speed changing mechanism 10 thereby transmitting the rotational speed firstly changed in the first speed changing mechanism 10 into the second speed changing mechanism 14. In additon. the transfer driven gears 44 are parallel and connected with a planetary gear unit 46 constituting the low speed control means and the second clutch C2 constituting the high speed control means respectively. There are two types of connections between the transfer driven gear 44 and the planetary gear unit 46 in the present invention and the shift operation is changed according to the type of connection therebetween. Firstly, as shown in FIGS 1 to 13, the first type of the second speed changing mechanism 14 according to the present invention is accomplished such that the sun gear 48 of the planetary gear unit 46 is directly connected with the transfer driven gear 44, a pinion gear 50 is connected with one friction plate 52 of the first clutch Cl, the other friction plate 54 of the first clutch Cl is directly connected with a high speed gear 56 disposed on the input shaft 12 through a carrier 58 and direct connection gear 60, and a ring gear 62 of the planetary gear unit 46 is connected with the output shaft 16. Accordingly, the planetary gear unit 46 of the first type of the second speed changing control mechanism 14 is constructed such that an input end for receiving driving power includes two elements, the sun gear 48 and pinion gear 50, and output end is the ring gear 62 connected with the output shaft 16. Therefore, the rotational speed firstly changed in the first speed changing mechanism 10 thereby inputted into the sun gear 62 of the planetary gear unit 46, and the rotational speed of engine E inputted into the pinion gear 50 of the planetary gear unit 46 through the high speed gear 56, the direct connection gear 58 and the first clutch Cl from the input shaft 12 are combined and varied in the planetary gear unit 46, and the final varied rotational speed is transmitted to the output shaft 16 through the ring gear 62. Among the first type of the transmission of the present invention, the speed changing operation of the continuously variable transmission in accordance with the first embodiment having only one planet roller 20. as shown in FIG 1. will be described as follows. At this point, the combination of each operarting element operating for accomplishing each speed changing stage is shown in FIG. 6. Before concretely describing the process of accomplishing the infinitely variable speed operation with the transmission according to the present invention, features in accordance with a structural condition thereof will be described to help the infinitely speed changing process of the transmission in accordance with the present invention to be understood. The infinitely variable speed transmission of the present invention is constructed such that the rotation speed of the engine E is firstly changed in the first speed changing mechanism 10 and the result of the first variable speed is transmitted to the second speed changing mechanism 14 thereby accomplishing the final variable speed. The variable speed process from neutral state and a low speed range to a medium speed range is accomplished by locking the first clutch Cl. The variable speed process from a medium speed range to a high speed range is accomplished by disengaging the first clutch Cl and locking the second clutch C2. Further, an equation of specific speed relation according to the first type of the second speed changing mechanism 14, in which the input ends of the planetary gear unit 46 receiving the power when the second clutch Cl is locked are composed of two elements, the sun gear 48 and pinion gear 50, is accomplished. That is, as described above, the equation of speed relation obtained from the planetary gear unit 46 wherein the diving power of the engine E is simultaneously inputted into the sun gear 48 and pinion gear 50 receiving the changed output is defined by, ( l+λ)ω r = λu„ +Q Π ( 1) where, λ = Nυs. of teeth of the sun gear, Uc = Nos. of rotations of the carrier connecting the pinion gears, <■>.. = Nos. of rotations of the sun gear, ωπ = Nos. of rotations of the ring gear. The result is, UR/U C = λ • u^/ω t . + 1 + λ - (2) In FIG. 7, the equation is graphically illustrated. As shown in the graph, in the planetary gear unit 46 having the pinion gear 50 and the sun gear 48 as input end. and the ring gear 62 as output end. the speed of the carrier ω c is constant, wherebv as the speed ω.. of the sun gear 48 increases, the speed of the ring gear UR decreases, and on the contrary, as the speed ω s of the sun gear 48 decreases, the speed &>R of the ring gear 62 increases. Further* if the speed ratio of the sun gear 48 with respect to the pinion gear 50, that is, Us/u c is more than (l+λ ) A, UR/ΘC is a negative value. This means that as the speed u c of the carrier connected to the pinion gear 50 is the common denominator, if the speed ω s of the sun gear 48 increased more than a predetermined value, the value of &>R is negative, and this means that the ring gear 62 rotates reversely. This can be easily understood from the graph in FIG. 6. The planetary gear unit 46 employed on the first type of the second speed changing mechanism 14 according to the present invention has the features as described above. The variable speed process employing the planetary gear unit 46 will be concretely described as follows. Neutral Mode (Initial mode) A neutral state of the infinitely variable speed transmission according to the invention is accomplished by 2 processes. A first operating process is that, in case that the first clutch Cl and second clutch C2 mounted on the output shaft 16 are disengaged, though the rotational speed is transmitted from the first speed changing mechanism 10 to the transfer driven gear 44 through the transfer drive gear 32 mounted on the output carrier 28 of the first speed changigng mechanism 10, because the first clutch Cl and second clutch Cl are respectively disengaged, the rotational speed is transmitted from the first speed changing mechanism 10 is not transmitted to the second speed changing mechanism 14 so that the transfer driven gear 44 is idle whereby the power is not transmitted to the output shaft 16. Accordingly, in case that the first and second clutches Cl and C2 are disengaged, the power is not transmitted to the output shaft 16 thereby being in the neutral state. On the other hand, the second operating process for accomplishing the neutral slate is that, in a state where the second clutch C2 is disengaged and the first clutch Cl for a low speed range is engaged, if the movable ring 24 is positioned in the neutral line C formed adjacent to a vertical hem in a large diameter portion of the planet roller 20, a rotational speed firstly changed in the first speed changing mechanism 10 is inputted into the sun gear 48 of the planetary gear unit 46 through the transfer drive gear 32 and transfer driven gear 44, and at the same time through the first clutch Cl being engaged, the rotational speed of the input shaft 12 is inputted into the pinion gear 50 of the planetary gear unit 46 through the high speed gear 56, direct connection gear 58 and the first clutch Cl. Therefore, the rotational speed of the sun gear 48 is equal to that of the pinion gear 50 so that the sun gear 48 and the pinion gear 50 rotates together and does not transmit the rotational speed to the ring gear 62. Accordingly, the ring gear 62 does not transmit the rotational speed to the output shaft 16 thereby accomplishing the neutral state that the output shaft 16 is not driven thereby. That is, in case that the first clutch Cl is locked and the movable ring 24 is placed in the neutral line C, even if the rotational speed firstly changed in the first speed changing mechanism 10 is inputted into the sun gear 48 of the planetary gear unit 46 through the transfer drive gear 32 and the transfer driven gear 44, and the rotational speed of the engine E is transfered into the pinion gear 50 of the planetary gear unit 46 through the high speed gear 56, direct connection gear 58 and first clutch Cl mounted on the input shaft 12. In this stale, the sun gear 48 and pinion gear 50 are rotated same rotational speed and the rotational speed from the planetary gear unit 17 is not transmitted to the ring gear 62 around the pinion gear 50. Accordingly, the ring gear 62 does not drive the output shaft 16 thereby being in the neutral state. Further, in state that the first clutch Cl is locked, if the movable ring 24 moves from the neutral line C lo a small diameter portion of the planet roller 20. the forward driving is accomplished, and if it moves from the neutral line C lo a large diameter portion of the planet roller 20, the reverse driving is accomplished. This forward and reverse direction converting process will be described later in detail. Low -To-Medium Speed Mode In a state of the neutral state described above, when the first clutch Cl is locked and the movable ring 24 moves from the neutral line C to the small diameter portion thereof, the operating diameter of the planet roller 20 contacted and supported to the movable ring 24 gradually decreases. Because the rotational speed of the planet roller 20 with respect to the movable ring 24 decreases as much as the operating diameter of the planet roller 20 decreases, if the operating diameter of the planet roller 20 decreases, the rotational speed of the output carrier 28 which connects a plurality of the planet rollers 20 to each other and revolves with the planet roller 20 is decreased too. Therefore the rotational speed inputted into the sun gear 48 of the planetary gear unit 46 from the output carrier 28 through the output carrier 28, transfer drive gear 32 and transfer driven gear 44 will decrease simultaneously. On the contrary, the rotational speed transmitted from the input shaft 12 into the pinion gear 50 through the high speed gear 56, direct connection gear 58 and first clutch Cl is not changed between the high speed gear 23 and direct connection gear 58, so that the pinion gear 50 rotates relatively fast around the sun gear 48 which is a center member. Accordingly, as shown in the equation (1 ) and the graph of FIG. 7. as the rotational speed ω<. of the sun gear 48 is gradually reduced, the rotational speed of the sun gear 48 is compounded with the rotational speed of the pinion gear 50, and the resull rotational speed outputted through the ring gear 62 gradually increases. And the rotational speed of the output shaft 16 connected with the ring gear 62 increases. Therefore, as the movable ring 24 moves to the small diameter portion of the planet roller 20. the rotational speed transmitted to the output shaft 16 through the ring gear 62 gradually increases. This is the variable speed process of the first type of the infinitely variable speed transmission according to the invention from the low speed range to medium speed range. As described above, the diameter of the planet roller 20 contacting with the movable ring 24 is linearly variable so that the rotational speed outputted through the planetary gear unit 46 connected to ihe planet roller 20 gradually increases. Consequently, the speed changing from the. low speed range to medium speed range is continuously accomplished. Medium-to-High Speed Mode When the speed changing from the low speed range to the medium speed range is accomplished by the above described processes, the movable ring 24 is positioned in the vertical hem of the small diameter portion of the planet roller 20. In this state, if the first clutch Cl is released and the second clutch C2 is locked at the same time, because the first clutch Cl is released, the rotary power is not transmitted from the input shaft 12 into the pinion gear 50 of the planetary gear unit 46, and the sun gear 48 of the planetary gear unit 46 meshed with the transfer driven gear 44 all the time continuously rotates. However, as the pinion gear 50 does not rotate, the planetary gear unit 46 is set to be in an idling state on the whole so that rotational speed is not transmitted to the ring gear 62. In this state, if the second clutch C2 for high speed is locked, the rotational speed of the first speed changing mechanism 10 is transmitted into the output shaft 16 through the transfer driven gear 44. In this process, as the rotational speed changed in the first speed changing mechanism 10 is not reduced again but transmitted into the output shaft 16 through the second clutch C2 without chnaging. If the rotational speed outputted from the first speed changing mechanism 10 is increased, the rotational speed of the output shaft 16 receiving the rotational speed through the second clutch C2 is increased in the same ratio thereof. Accordingly, as described above, as the movable ring 24 moves from the vertical hem of the small diameter portion of the planet rollers 20 to that of the large diameter portion of the planet roller 20, the rptational speed of the carrier 28 connecting a plurality of the planet rollers 20 lo each other, whereby this increased rotational speed is directly transmitted into the output shaft 16 through the second clutch C2 thereby increasing the rotational speed. In the process from the medium speed range lo the high speed range as described above, since the rotational speed outputted from the first speed changing mechanism 10 is directly transmitted into the output shaft 16, other complicated speed changing processes which are caused by a intermediate shifting means, for instance, additional planetary gear unit 46 in the low speed state, is not needed. Accordingly, in case of speed changing from the medium speed range to the high speed range, only a process where the rotational speed outputted from the first speed changing mechanism 10 is transmitted through the second clutch C2, is accomplished. Also, in the process of speed changing to the high speed range, since the diameter of the planet roller 20 linearly increases, the speed of the output shaft 16 rotated by receiving the output of the planet roller 20 gradually increases thereby accomplishing the continuous speed changing in the high speed range. Reverse Mode As is described in detail, the operating processed in accordance with the structural features of the infinitely variable transmission according to the present invention, and as shown in FIG. 6, to reverse the output shaft 16 of the transmission, if the first clutch Cl is locked in a state of releasing the second clutch C2, as the speed changing processes to the medium speed range already described above, the rotational speed changed from the first speed changing mechanism 10 is inputted into the sun gear 48 of the planetary gear unit 46 and the rotational speed of the input shaft 12 is inputted into the pinion gear 50 of the planetary gear unit 46 through the high speed gear 56, the direct connection gear 58 and the first clutch Cl. Accordingly, as shown in the equation (2), since the speed ω ς - of the pinion gear 50 of the planetary gear unit 46 is the same condition, if the speed ω„ of the sun gear 48 increases to the predetermined value so that the value of ω.yω c i larger than that of ( l +λ)A, the value of b /u,. is negative. In this state, the speed u c inputted into the pinion gear 50 is alternately the same condition. Consequently, the rotational speed is determined by the speed of the sun gear 48, and the critical line between the positive rotation and negative rotation of this sun gear 48 becomes the neutral line C indicated on the planet roller 20. Accordingly, when the movable ring 24 moves to the large diameter portion over the neutral line C, the rotational speed of the transfer drive gear 32 provided in the output carrier 28 supporting the planet rollers 20 increases in accordance with the principle described above so that the rotational speed of the sun gear 21 of the planetary gear unit 46 connected with the transfer drive gear 32 is increased more than the critical value thereby reversing the ring gear 62 of the planetary gear unit 46 as described above. On the other hand, in the case of high speed positive rotation, also the movable ring 24 moves over the neutral line C indicated on the planet roller 20. In the case of the high speed positive rotation, however, the movable ring 24 moves to the largest diameter portion over the neutral line C thereby accomplishing the speed changing to the highest speed and avoiding the output shaft 16 from being reversed as the reverse range. This results in that in the case of the high speed positive rotation, the second clutch C2 is locked and the first clutch Cl is released, but in the case of reverse rotation, the first clutch Cl is locked and the second clutch C2 is released, so that the state of the positive rotation is not the same as that of the reverse rotation. That is. though the movable ring 24 moves to the largest diameter portion of the planet roller 20, if the clutch Cl is released and the second clutch C2 is locked, the planetary gear unit 46 does not operate so that the equations ( 1 ) and (2) do not apply. Since the rotational speed changed in the first speed changing mechanism 10 is directly transmitted into the output shaft 16 through the second clutch C2, even if the movable ring 24 moves to the large diameter portion of the planet roller 7 during the forward high speed range, the output speed transmitted to the output shaft 16 increases high. Therefore, the infinitely variable speed transmission according to the present invention is designed such that the forward and reverse modes can be mutually converted by controlling only the rotational speed outputted from the first speed changing mechanism 10 without using a special direction converting means, such that the conversion between the forward drive and the reverse drive can simply smoothly be realized and the structure of the transmission becomes compact and simple. On the one hand, the transmission according to the third embodiment of the present invention depicted in Fig 3 is different in its speed changing operation from those of the first and second embodiments, since the movable sun ring 40 and the movable ring 24 are respectively displaced by the moving members 42 and 34. However, since the power input and output elements for the planetary gear unit 46 constituting the second speed changing mechanism 14 are the same as those of the first embodiment, the basic operating concept is the same as those of the first and second embodiments, in which the speed changing operation is accomplished as follows: Neutral Mode (Initial Mode) In the third embodiment, the neutral mode can be achieved in two states. Likewise the first embodiment, one is a state where the first and second clutches Cl and C2 are released. In this state, the rotational speed from the first speed changing mechanism 10 cannot be transmitted to the second speed changing mechanism 14, thereby accomplishing the neutral mode. The other is a state where the second clutch C2 is released while the first clutch Cl is locked, furthermore the movable sun ring 40 is positioned on the neutral line C proximal to the small diameter portion of the cone- shape body 6a, and the movable ring 24 is positioned on the front end of the large diameter portion of the cone-shaped body 6b as shown in Fig. 3. In this state, the rotational speed primarily changed in the first speed changing mechanism 10 is inputted to the sun gear 48 of the planetary gear unit 46 through the transfer drive and transfer driven gears 32 and 44. And al the same time, since the rotational speed of the input shaft 12 is inputted to the pinion gear 50 of the planetary gear unit 46 through the high speed gear, direct gear and first clutch 56, 58 and Cl, the rotational speed of the sun gear 4S and the rotational speed of the pinion gear 50 becomes the same as each other. Accordingly, jjower is not transmitted to the ring gear 62. thereby realizing the neutral mode. In addition, in a state where the first clutch Cl is locked and the position of the movable ring 24 is fixed, when the movable sun ring 40 is displaced from the neutral line C to the large diameter portion of the cone-shaped body 6a, the speed changing operation is realized positively, and when the movable sun ring 40 is displace from the neutral line C to the small diameter portion of the cone-shaped body 6a, the speed changing operation is achieved negatively. This operation will be described in detail in the following low-to-medium speed mode. Low -To-Medium Speed Mode At the neutral mode as described above, as the movable sun ring 40 moves toward the largest diameter portion of the cone-shaped body 6a in a state where the first clutch Cl is locked and the movable ring 24 is moved toward the largest diameter portion of the cone-shaped body 6b, the diameter of the cone-shaped body 6a being in contact with the movable sun ring 7 is gradually increased. As a result, the rotational speed of the planet rollers 20 inscribed on the movable ring 24 is gradually reduced, and this reduced rotational speed is transmitted to the sun gear 48 of the planetary gear unit 46 constituting the second speed changing mechanism 14 through the transfer drive and transfer driven gears 32 and 44. As described above, as the rotational speed outputted from the first speed changing mechanism 10 is gradually reduced, while the sun gear 48 of the planetary gear unit 46 gradually rotate slowly, since the contant rotational speed to the pinion gear 50 is transmitted from the inpul shaft 12, as can be known from the equation (2) and graph in Fig. 7, the rotational speed of the ring gear 62 disposed around the pinion gear 50 and rotating by receiving the rotational speed from the pinion gear 50 is gradually increased. After the movable sun ring 40 is completely displaced toward the large diameter portion of the cone shaped body 6a. as the movable ring 24 moves from the large diameter portion to the small diameter portion of the cone-shaped body 6b, the rotational speed of the planet rollers 20 which rotate by receiving the constant rotational speed from the sun ring 40 is gradually reduced, such that the output rotational speed from the first speed changing mechanism 10 is also reduced. Accordingly, since the sun gear 48 of the planetary gear unit 46 receives the reduced speed from the first speed changing mechanism 10 and rotates with the further reduced speed, as shown from the equation (2) and graph in Fig. 7, as the rotational speed of the sun gear 48 is gradually reduced, the output rotational speed from the ring gear 62 becomes increased. Finally, when the movable ring 24 of the first speed changing mechanism 10 is positioned on the smallest diameter portion of the cone-shaped body 6b, the transmission becomes the medium mode. Therefore, during the transmission changes the output rotational speed from the low speed to the medium speed, since the rotating diameters of each cone-shaped bodies 6a and 6b are linearly varied while the movable sun ring 40 and the movable ring 24 respectively contacting therewith move along the longitudinal directions thereof, the output rotational speed from the planetary gear unit 46 connected to the planet rollers 20 is gradually increased so that the speed change from the low speed to the medium speed can be infinitely realized. Medium- to- High Speed Mode When the output rotationa speed reaches to the medium speed as described above, as shown in Fig. 5A, the movable sun ring 40 is lo be positioned on the largest diameter portion of the cone-shaped body 6a. while the movable ring 24 is to be positioned on the smallest diameter portion of the cone- shaped body 6b. At this stale, afler releasing the first clutch Cl and locking the second clutch C2, as shown in Figs. 5A and 5B, as the movable ring 24 moves from the small diameter portion to the large diameter portion of the cone- shaped body 6b and the movable sun ring 40 is displaced from the large diameter portion to the small diameter portion of the cone shaped body 6a, the rotational speed transmitted from the engine to the planet roller 20 is increased, and this increased rotational speed is transmitted to the output shaft 16 through the second clutch C2 via the first speed chnaging mechanism 10. At this point, as described in the first embodiment, the planetary gear unit 46 is set to be in an idling state so that the rotational speed cannot be transmitted to the ring gear 62. Furthermore, the rotational speed of the first speed changing mechanism 10 is transmitted to the output shaft 16 through the second clutch C2, and at this point, since the rotational speed changed in the first speed changing mechanism 10 is transmitted to the output shaft 16 through the second clutch C2 without further speed change, when the rotational speed outputted from the first speed changing mechanism 10 is increased, the rotational speed of the output shaft 16 receiving the rotational speed through the second clutch C2 is also increased in the same ratio. That is, as in the first embodiment, as the rotating diameter of the planet rollers 20 revolving around the movable ring 24 is increased, the rotational speed thereof is increased, whereby the rotational speed outputted from the first speed changing mechanism 10 through the transfer drive gear 32 to the secong speed changing mechanism 14 is to be increased. At this point, in a state where the sun ring 40 is fixed on a position of the cone-shaped body 6a, the movable ring 24 is displaced from the large diameter portion to the small diameter portion of the cone-shaped body 6b. When the movable ring 24 is positioned on the smallest diameter portion of the cone-shaped body 6b, the movable sun ring 40 is to be displaced from the small diameter portion to the large diameter portion of the cone- shaped body 6a. At this point, since the diameter of the movable sun ring 40 transmitting rotational speed is fixed, the rotating diameter of the planet roller 20 receiving the rotational speed from the movable sun ring 40 is reduced to thereby increase the rotational speed of the planet rollers 20. As a result, since the rotational speed of the planet rollers 20 around the movable ring 24 is increased so that the output rotational speed is gradually increased. Reverse Mode The reverse mode of the transmission according to the third embodiment is similarly realized to the first and second embodiments, except that the position where the movable sun ring 40 is in contact with the cone-shaped body 6a at a critical point C where the forward mode and the reverse mode are mutually converted, are different from those of the first and second embodiments. That is, to reversely rotate the output shaft 16 of the transmission according to the third embodiment, if the output rotational speed from the first speed changing mechanism 10 through the transfer drive gear 32 is increased over a critical value in a state where the second clutch C2 is release and the first clutch Cl is locked, the output rotational speed changed in the planetary gear unit 46 of the second speed changing mechanism 14 becomes negative(-). In other words, when the rotational speed of the transfer drive gear 32 is increased over a critical value, likewise at the medium-to-high forward speed mode, as the movable sun ring 40 is displaced forward the smallest diameter portion of the cone-shaped body 6a in a state where the movable ring 24 is positioned on the largest diameter portion of the cone-shaped body 6b. the output rotational speed from the planet roller 20 comes to be increased. At this point, once the movable sun ring 40 is displaced over a predetermined position, the input rotational speed to the planetary gear unit 46 of the second speed changing mechanism 14 comes to be over a critical rotational speed, the transmission is converted from the forward mode into the reverse mode through the neutral mode. Accordingly, in the third embodiment, the movable sun ring 40 is displaced passing the neutral line C proximal to the smallest diameter poπion of the cone-shaped body 6a, the rotating direction outputted from the second speed changing mechanism 14 comes to be converted into the reverse direction. Fig. 8 shows an infinitely variable speed transmission according to the fourth embodiment of the present invention, the transmission according to the fourth embodiment is similar to the first, second, third embodiments except that following additional elements are added thereto. First, a spring 64 is mounted on a front end of the pivot axis 22 rotatably supporting the planet rollers 20 to elastically biasing the planet roller 20. Further, there is provided a pre-load nut 66 to control frictional force between the planet roller 20 and the movable ring 24. Second, a load cam 68 is mounted on the output carrier 28 of the first speed changing mechanism 10 to absorb excessive resistance applied to the second speed changing mechanism 14, thereby preventing the excessive resistance from transmitting to the planet rollers 20. Third, a one way clutch 70 is mounted in parallel between the friction plate 52 of the first clutch Cl and the friction plate 54 connected to the direct gear 58. As described above, by proving some additional elements to the transmission, the function of the infinitely variable transmission can be increased. That is, when a big load is applied to the output gear 72 of the second speed changing mechanism 14, to prevent the big load from directly being transmitted to the planet rollers 20, the load cam 68 absorbs part of the big load. Generally, the load cam 68, as shown in Fig. 10 is divided in its input and output ends 68a and 68b and each end of the input and output ends 68a and 68b facing each other is provided with saw teeth. Balls 74 are inserted between the input and output ends 68a and 68b according to one embodiment shown in Fig. 9, while the input and output ends 68a and 68b mesh with each other at their saw teeth according to another embodiment shown in Fig. 10. Accordingly, when load is applied from the second speed changing mechanism 14 to the output end 68b of the load cam 68, a slip occurs at the saw teeth through clearance between the balls 74 and the saw teeth in Fig. 9 and through clearance between the saw teeth of the input end 68a and the saw teeth of the output end 68b, thereby absorbing the load. As a result, since the load can not be applied to the planet roller 20 connected to the input end 34a by means of the load cam 68, the speed changing operation can be smoothly realized. That is. when the transmission according to the present invention is applied to a practical vehicle, when drive resistance applied to the drive wheel becomes larger, this drive resistance is transmitted to the output carrier 28 of the first speed changing mechanism 10 through the second speed changing mechanism 14 and is then induced to the load cam 68. At this point, since the drive resistance is absorbed in the load cam 68 and is then transmitted to the planet rollers 20, the planet rollers 20 are not overloaded. In addition, since the spring 64 mounted on the front end of the pivot axis 22 of the planet rollers 20 functions as a means for supporting force transmitted to the planet rollers 20 through the load cam 68 in case the driving resistance becomes larger as described above, when the planet rollers 20 moves along the axial direction, the planet rollers 20 move while compressing the spring 64. And, when the applied driving resistance is released, the planet rollers 20 returns to its original position while the compressed spring 64 is restored. Furthermore, the pre-load nut 66 mounted on the pivot axis 22 serves as means for tightening the pivot axis 22 of the planet rollers 20. Accordingly, rotating resistance of the planet rollers 20 is varied in accordance with the degree of the tightness. In other word, the friction resistance generating between the movable ring 24 and the planet roller 20 is determined in accordance with the degree of tightness. As described above, by regulating the rotating resistance of the planet rollers 20 using the pre-load nut 66, the friction resistance between the planet roller 20 and the movable ring 24 can be properly regulated according to characteristics of the driving means where the transmission of the present invention will be applied. On the one hand, the one-way clutch 74 is for smoothly connecting or disconnecting power when the first clutch Cl is released. That is, when the power is transmitted by locking the first clutch Cl, the one- way clutch is set to be in an idling state so that the power can not be transmitted therethrough. However, when the first clutch Cl is released and the second clutch C2 is locked, the rotational speed transmitted from the first speed changing mechanism 10 is transmitted into the output shaft 16 through the second clutch C2. The moment that the first clutch Cl is released and the second clutch C2 is locked, the rotational speed does not transmitted to the pinion gear 50 of the planetary gear unit 46 but continuously transmitted to the sun gear 48. At the moment, as shown in FIG. 14, the one way clutch 70 is locked by the difference between the rotational speed of the pinion gear 50 and the instant rotational speed of the sun gear 48. At this time, the state that the rotational speed of the input shaft 12 is transmitted into the pinion gear 50 of the planetary gear unit 46 through the instantaneously locked one way clutch 70 is maintained and the second clutch C2 is locked thereby smoothly accomplishing the speed changing from the medium speed range to the high speed range. FIG. 11 shows a fifth embodiment according to the present invention, and FIG. 12 shows a sixth embodiment according to the present invention. In these embodiments, an elastic means 72 is disposed between the vertical hem of the large diameter portion of the planet roller 20 and a transmission case 74 in addition to the fourth embodiment. As the planet rollers 20 are provided with the elastic means 72, when the moving ring 24 moves along the surface of the large diameter portion of the planet rollers 20, the friction resistance of the moving ring 24 with respect to the planet rollers 20 is occured and the planet rollers 20 are pushed by the friction resistance in the direction of large diameter portion thereof. In this case, the elastic means 72 elastically supports the planet rollers 20 thereby preventing it from being escaped from the carriers 26 and 28 or being permanently moved. Also, the elastic meas 72 can supports bearings 36 supporting the pivot axis 22 of the planet rollers 20, and the elastic means 72 can be supported to the transmission case 76 or the output carrier 28. Also, ihe elastic means 72 can be simply constituted by a spring as the fifth embodiment according to the present invention shown in FIG. 11, and it can be constituted by a hydraulic cylinder operated by a compressed fluid or gas as shown in FIG. 12. As a seventh embodiment is shown in FIG. 13, a position detecting sensor 78 electronically controlled is disposed on the moving ring 24 moving along the surface of the planet rollers 20, thereby correctly detecting the moving distance of the moving ring 24 thereby precisely controlling the speed changing state. FIG. 15 shows an eighth embodiment according to the present invention. In this embodiment, the structure of the second speed changing mechanism 14, which is connected to the first speed changing mechanism 10 for firstly speed changinging the power transmitted from the engine thereby secondly speed changing mechanism 14 according to the condition required, is changed. On the other hand, the first speed changing mechanism 10 connected to the second speed changing mechanism 14 of the eighth embodiment can be the structure of the first to third embodiments of the present invention. The figures are shown with reference to the second embodiment. As shown in FIG. 15, the second speed changing mechanism 14 according to the eighth embodiment, in the same manner of another embodiments described above, is constituted by the low speed control means composed of the first clutch Cl, the planetary gear unit 46, the direct connection gear 58 and the high speed gear 56, and the high speed control means composed of the second clutch C2. In the eighth embodiment, the input element and output element of the planetary gear unit 46 are differently disposed from thai of another embodiments, but the other elements, for instance the second clutch C2 and the first clutch Cl are connected to the high speed gear 56 through the direct connection gear58. are the same. That is, in the eighth embodiment of the present invention, the ring gear 62 of the planetary gear unit 46 is connected to the transfer driven gear 44, the pinion gear 50 is connected to the direct connection gear 58. and the sun gear 48 is connected to the output shaft 16. According!). , the input element of the planetary gear unit 46 is constituted by the ring gear 62 receiving the power from the first speed changing mechanism 10 and the pinion gear 50 directly receiving the power of the engine through the first clutch Cl from the high speed gear 56, and the output element thereof is constituted by the sun gear 48. In the eighth embodiment of the present invention, another equation of the speed relation different from that of the first to seventh embodiments is defined by, λω s = (l+λ)ω c - ω R (3) where, λ = diameter of the sun gear/diameter of the ring gear ω = rotational speed of the carrier for connecting the pinion gear U = rotational speed of the ring gear ω = rotational speed of the sun gear. The result is, US/U = (1 + λ)A • "C/U • 1/ λ (4) In FIG. 17, the equation is graphically illustrated. As shown in the graph, in the planetary gear unit 46 where the input ends are the ring gear 62 and the pinion gear 50 and the output end is the sun gear 48, since the rotational speed ωc of the carrier connected with the pinion gear 50 is constant, if the rotational speed ω κ of the ring gear 62 increase, the rotational speed ratio UC/UR of the pinion gear 50 with respect to the ring gear 21 is reduced thereby decreasing the speed ratio (JS/U outputted through the sun gear 48. On the contrary, if the rotational speed inputted through the ring gear 62 decreases, the rotational speed of the sun gear 48 gradually increases. Accordingly, as the moving ring 24 of the first speed changing mechanism 10 moves along the longitudinal direction of the planet rollers 20 and the operating diameter of the planet rollers 20 with respect to the moving ring 24 is varied, the rotational speed outputted through the output carrier 28 of the first speed changing mechanism 10 is varied. Since the rotational speed of the ring gear 62, receiving the rotational speed of the output carrier 28 thereby rotating, is also varied, the rotational speed, transmitted from the sun gear 48 into the output shaft 16 according to the operating principle of the planetary gear unit 46 described above, linearly increases or decreases. Further, if the rotational speed ratio of the pinion gear 50 with respect to the ring gear 62, that is, t)c/ω s is smaller than l/(l+λ), ϋs ω R is a negative value. This means that as the rotational speed UR of the ring gear 62 is the common denominator, if the rotational speed of the ring gear 62 with respect to the pinion gear 50 increases more than a predetermined value, the rotation of the sun gear 48 reverse rotates. This can be easily understood from the graph in FIG. 17. The planetary gear unit 46 constituted as the eighth embodiment has operating features as described above, wherein the features of this planetary gear unit 46 and the first speed changing mechanism 10 described in another embodiments are compounded thereby accomplishing the continuously speed changing. The operating processes will be concretely described in accordance with each speed changing state as follows. Neutral Mode (Initial Mode) Likewise another embodiments, the neutral mode can be achieved in two stales. That is, the first operating process is that, as shown in the table of FIG. 16, in case that the first clutch Cl and second clutch C2 disposed on the output shaft 16 are released, though the power is transmitted from the first speed changing mechanism 10 into the transfer driven gear 44 of the second speed changing mechanism 14 through the transfer drive gear 32 disposed on the output carrier 28 of the first speed changing mechanism 10. since the first clutch Cl and the second clutch C2 does noi transmit the power respectively, the transfer driven gear 44 is idling so that the power is not transmitted into the output shaft 16. Accordingly, as described above, in case that the first clutch Cl and the second clutch C2 are released, the power is not transmitted into the output shaft 16 so that the output shaft 16 can not rotate thereby accomplishing the neutral mode. On the other hand, the second operating process is that, in state that the second clutch C2 is released and only the first clutch Cl is locked, if the moving ring 24 is positioned on the neutral line C adjacent to the vertical hem of the large diameter portion of the planet rollers 20, the rotational speed firstly changed in the first speed changing mechanism 10 is inputted into the ring gear 62 of the planetary gear unit 46 through the transfer drive gear 32 and the transfer driven gear 44, and at the same time, the power of the input shaft 12, which is not changed through the locked first clutch Cl, is inputted into the pinion gear 50 of the planetary gear unit 46 through the high speed gear 56, the direct connection gear 58 and the first clutch Cl, so that the rotational speed of the ring gear 62 is equal to that of the pinion gear 50 and the ring gear 62 and pinion gear 50 rotate at the same speed, so that relative rotation does not occur, whereby the rotational speed can not be transmitted to the sun gear 48 internally touched to the pinion gear 50. Accordingly, the sun gear 48 does not transmit the power to the output shaft 16 thereby accomplishing the neutral mode where the output shaft 16 is not driven. That is, in case that the first clutch Cl is locked and the moving ring 24 is positioned on the neutral line C, though the rotational speed firstly changed in the first speed changing mechanism 10 is transmitted into the speed changing control mechanism 14, the rotational speed transmitted from the first speed changing mechanism 10 and the rotational speed directly transmitted from the input shaft 12 are equal to each other in the planetary gear unit 46 of the speed changing control mechanism 14 so that the sun gear 48 of the planetary gear unit 46 does not rotate, whereby the power is not outputted lo the output shaft 16 thereby accomplish the neutral mode. Low . To Medium Speed Mode In the neutral mode, as the first clutch Cl is locked and the moving ring 24 moves from the neutral line C of the planet roller 20 to the small diameter portion, the operating diameter of the planet rollers 20 contacted and supported to the moving ring 24 gradually decreased, and as the operating diameter of the planet rollers 20 is reduced, since the rotational speed of the planet rollers 20 with respect to the moving ring 24 decreases as much as the diameter of the supporting point decreases, the circulation speed of the output carrier 28 which connects a plurality of the planet rollers 20 each other decreases, and the rotational speed of the ring gear 62 of the planetary gear unit 46, which is connected through the output carrier 28 to the transfer drive gear 32 and the transfer driven gear 44, gradually decreases. On the contrary, since the rotational speed transmitted from the input shaft 12 into the pinion gear 50 through the high speed gear 56, the direct connection gear 58 and the first clutch Cl is always changed in a constant ratio between the high speed gear 56 and the direct connection gear 58 and is not varied, as the moving ring 24 moves to the small diameter portion of the planet roller 20, the speed of the pinion gear 50 with respect to the ring gear 62 gradually increases. Accordingly, as shown in the equation 4 and the graph of FIG. 17. as the rotational speed U of the ring gear 62 gradually decreases, the rotational speed of the ring gear 62 and the rotational speed of the pinion gear 50 are compounded each other. As a result, the rotational speed ωs outputted through the sun gear 48 gradually increases and the rotational speed of the output shaft 16 connected with the sun gear 48 increases. Therefore, as the moving ring 24 moves to the small diameter ponion of the planet roller 20. the rotational speed transmitted into the output shaft 16 through the sun gear 48 gradually increases. This is the processes of speed changing from the low speed range to the medium speed range of the infinitely variable transmission according to the present invention. The diameter of the planet rollers 20 contacted with the moving ring 24 is linearly varied so that the rotational speed exhausted through the planetary gear unii 46 gradually increases, thereby continuously accomplishing the speed changing from the low speed range to the medium speed range. Medium-to-High Speed Mode When the speed changing to the medium speed range is accomplished by the above described processes, the moving ring 24 is positioned in the vertical hem of the small diameter portion of the planet roller 24. In this state, if the first clutch Cl is released and the second clutch C2 is locked at the same time, because the first clutch Cl is released, the power transmitted from the input shaft 12 to the direct connection carrier 58 through the high speed gear 56 and the direct connection gear 58, is closed in the first clutch Cl so that it is not transmitted to the pinion gear 50 of the planetary gear unit 46, and the rotational speed changed in the first speed changing mechanism 10 is directly transmitted into the output shaft 16 through the second clutch C2. This is the converting state from the medium speed mode to the high speed mode. If the second clutch C2 is locked, the power of the first speed changing mechanism 10 is transmitted into the output shaft 16 through the transfer driven gear and the second clutch C2. In this processes, since the rotational speed changed in the first speed changing mechanism 10 is not changed again but is directly transmitted into the output shaft 16 through the second clutch C2, if the rotational speed outputted from the first speed changing mechanism 10 increase, the rotational speed of the output shaft 16 receiving the rotational speed through the second clutch C2 increases at the same ratio. Accordingly, as the movable ring 24 is displace from the small diameter portion to the large diameter portion of each planet roller 20. the rotational speed of the output carrier 28 connecting the planet rollers 20 with each other is increased and the increased speed is directly transmitted to the output shaft 16 through the second clutch C2 to thereby increase the rotational speed. As described above, in the medium-to high forward speed mode, the rotational speed outputted from the first speed changing mechanism 10 is directh transmitted lo the output shaft 16 without a special complicate speed changing operation. Therefore, in the medium-to-high forward speed mode, the rotational speed from the first speed changing mechanism is transmitted only through the second clutch C2 of the second speed changing mechanism 14. In addition, since the rotating diameter of each planet rollers 20 is linearly increased, the output speed of the output shaft 16 which receives the output of each planet roller 20 is gradually increased such that in this high speed mode, the speed is changed continuously. Reverse Mode In the reverse mode, as charted in Fig. 16, when the first clutch Cl is locked while the second clutch C2 is released, the output rotational speed from the first speed changing mechanism 10 is transmitted to the ring gear 62 of the planetary gear unit 46, and at the same time, the rotational speed of the input shaft 12 is transmitted to the pinion gear 50 of the planetary gear unit 46 through the high speed gear 56, the direct connection gear 58 and the first clutch Cl. Accordingly, as shown in the equation (4), since the speed G) of the ring gear 62 of the planetary gear unit 46 is the same condition, if the speed U of the ring gear 62 increases to the predetermined value so that the value of U /(0C is smaller than that of 1/1 +λ, the value of s/ R becomes negative(- ). In this state, since the rotational speed (O inputted into the ring gear 62 is the same condition in its input and output speed ratios and the rotational speed u t - inputted to the pinion gear 50 is constant, the rotational speed ratio ω / R of the sun gear 48 to the ring gear 62 is determined by the speed ω R of the ring gear 62. According to this, the rotating direction is also determined. Therefore, the critical line between the positive rotation and negative rotation of this sun gear 48 becomes the neutral line C indicated on the planet roller 20. Accordingly, when the movable ring 24 is displaced toward the large diameter portion passing the neutral line C indicated on the planet rollers 20, the output rotational speed of the output carrier 28 supporting the planet rollers 20 is increased to thereby increase the rotational speed of the transfer drive gear 32 connected to the output carrier 28, such that the rotational speed of the planetary gear unit 46 connected to the transfer drive gear 32 through the transfer driven gear 44 is increased over the critical value. As a result, the rotating direction outputted through the sun gear 48 of the planetary gear unit 46 is reversed. On the other hand, in case of a high speed positive rotation, also the movable ring 24 moves over the neutral line C indicated on the planet rollers 20. However, in case of the high speed positive rotation, the movable ring 24 moves to the largest diameter portion over the neutral line C thereby accomplishing the speed changing to the highest speed and avoiding the output shaft 16 from being reversed as the reverse mode. This results in that in case of the high speed positive rotation, the second clutch C2 is locked and the first clutch Cl is released, on the contrary, in case of reverse rotation, the first clutch Cl is locked and the second clutch C2 is released, so that the state of the positive rotation is not same as that of the reverse rotation. That is, even the movable ring 24 moves to the largest diameter portion of the planet roller 20, if the clutch Cl is released and the second clutch C2 is locked, the planetary gear unit 46 does not operate so that the equations (3) and (4) do not applied. Since the speed changinging state accomplished in the first speed changing mechanism 10 is transmitted into the output shaft 16 through the second clutch C2. the output speed, increasing as the movable ring 24 moves to the large diameter portion of the planel rollers 20 during the forward high speed range, is transmitted to the output shaft 16 so that the speed increases high. In this eighth embodiment, like the seventh embodiment, the one- way clutch 70 can be additionally mounted on the first clutch Cl so that the smooth speed changing operation can be realized in the medium-to-high forward speed mode. That is. in the medium to high forward speed mode, since the ring gear 62 of the planetary gear unit 46 alway meshes with the transfer drive gear 32 through the transfer driven gear 44, the ring gear 62 rotates continuously while power is not transmitted to the pinion gear 50 of the planetary gear unit 46. Accordingly, in a moment the first clutch Cl is released, the rotational speed of the ring gear 62 and the rotational speed of the planetary gear unit 46 become different from each other. The speed difference makes the pinion gear 50 rotate reverse. As described above, as the pinion gear 50 rotate reversely, the one-way clutch 70 which has been released is to be locked to transmit power from the input shaft 12 to the pinion gear 50 through the high speed gear 56 and the direct gear 58 the same manner as the first clutch Cl is in a locking state. Accordingly, since the second clutch C2 is locked while the medium state outputted from the planetary gear unit 46 is continued, the medium-to-high forward speed mode is smoothly accomplished. In addition, as described in each above embodiment, the finally changed power in the second speed changing mechanism 14 is to be transmitted to the output shaft 16 and is then transmitted to a differential gear 80 of the driving means through an output gear 72 arranged on an output end of the output shaft 16, thereby driving the driving means such as an automotive vehicle with proper speed and rotational speed. As described above, the infinitely variable speed transmission according to the present invention is designed such that the output rotational speed is continuously varied while the movable ring 24 of the first speed changing mechanism 10 moves along the surface of the planet roller 20. In addition, the infinitely variable speed transmission according to the present invention is designed such that the positive and negative rotation can mutually converted by controlling only the rotational speed outputted from the first speed changing mechanism 10 without using a special direction converting means, such that the conversion between the forward drive and the reverse drive can simply smoothly be realized and the structure of the transmission becomes compact and simple, making it easy to install the transmission in the mounting space of the driving means. While this invention has been described in connection with what is presently considered to be the most practical and preferred embodiments, it is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, it is intended to cover various modification and equivalent arrangements included within the spirit and scope of the appended claims.

Claims: WHAT IS CLAIMED IS 1. An infinitely variable speed transmission, comprising: a first speed changing mechanism for primarily changing rotational speed from an engine into a necessary rotation speed, including: * a sun gear disposed on an input shaft which receives the power from an engine; a plurality of planet rollers which are disposed around the sun gear at a predetermined distance from each other, each planet roller having a truncated cone- shape and being revolvable around the sun gear and rotatable about its povot axis; a carrier for connecting the planet rollers with each other and outputting the rotational speed changed in the planet rollers; a movable ring disposed to be circumscribed on outer peripheral lines of the planet rollers and movable by a moving means along the longitudinal direction of the planet rollers to change rotational speed of the planet rollers by varying a rotating diameter thereof to the movavble ring so that the rotational speed outputted through the carrier connecting the planet rollers with each other can be varied; and a second speed changing mechanism for finally changing the rotational speed from the first speed changing mechanism into a necessary final output speed, including: a planetary gear unit mounted on an output shaft; a low speed control means having a first clutch for controlling a operation of the planetary gear unit; and a high speed control means having a second clutch mounted on the output shaft; the planetary gear unit and the second clutch being parallel and directh connected with the carrier of the first speed changing mechanism ; and the planetary gear unit being directly connected with the input shaft through the first clutch. 2. An infinitely variable speed transmission according to claim 1. wherein each planet roller is made of one truncated cone-shaped body and the carrier is provided with a transfer drive gear for transmitting power to the output shaft, the cone-shaped body being provided with a gear meshing with the sun gear. 3. An infinitely variable speed transmission according to claim 1, wherein a circumscribed line of each planet roller contacting the movable roller is parallel with the imput shaft to maintain a pressed state of the movable ring on each planet roller while the movable ring moves along the surface of each planet roller in a longitudinal direction. 4. An infinitely variable speed transmission according to claim 1 comprising a movable sun ring instead of the sun gear, wherein the planet roller is made up of two truncated cone-shaped bodies which are combined such that they are symmetrically faced with each other at their large diameter portions, the movable sun ring tightly contacting and movable along one of the truncated cone-shaped bodies by a moving member to thereby varying a contacting changing diameter of each planet roller. 5. An infinitely variable speed transmission according to claim 1 or 4, wherein a pivot axis of the planet roller 20 is separated and a bearing is mounted between the planet roller 20 and the pivot axis 22 to improve the rotating performance therebetween. 6. An infinitely variable speed transmission according to claim 4, wherein an inscribed line of the one of the two cone shaped bodies contacting the movable sun ring is parallel with the input shaft. 7. An infinitely variable speed transmission according to claim 4. wherein the two cone shaped bodies is movable in their longitudinal direction and a bearing is mounted therebetween. 8. An infinitely variable speed transmission according to claim 1, wherein a sun gear of the planetary gear unit constituting the second speed changing mechanism is connected with the transfer driven gear, a pinion gear of the planetary gear unit is one friction plate of the first clutch, one friction plate of the second clutch is connected to a high speed gear disposed on the input shaft through the direct gear, and the ring gear of the planetary gear unit is connected to the output shaft. 9. An infinitely variable speed transmission according to claim 8, wherein a one-way clutch is mounted between the friction plates. 10. An infinitely variable speed transmission according to claim 1, wherein a spring for biasing planet roller is mounted on one end of the pivot axis. 11. An infinitely variable speed transmission according to claim 1, wherein a pre-load nut is mounted on the one end of the planet roller to adjust friction force generating between the planet roller and the ring friction wheel by determining rotating resistance of the planet roller. 12. An infinitely variable speed transmission according to claim 1, wherein a load cam is mounted on the carrier to prevent excessive resistance from being applied to the first speed changing mechanism. 13. An infinitely variable speed transmission according to claim 1, wherein a position sensor for detecting a moving distance of the movable ring is mounted on the movable ring. 14. An infinitely variable speed transmission according to claim 1, wherein an elastic means are mounted between an large diameter end of the planet roller and a transmission case to prevent the planet roller from moving its longitudinal direction by friction resistance. 15. An infinitely variable speed transmission according to claim 1. wherein the ring gear is connected with the transfer driven gear, the pinion gear is connected with the direct gear as well as the high speed gear through the first clutch, and the sun gear is connected to the output shaft. 16. An infinitely variable speed transmission according to claim 1. wherein a one way clutch is mounted between both friction plates of the first clutch.

Inventors: CHOI YOUNG DEOK, EUM TAE KWAN, KIM JEONG CHEOL, KIM JEONG YOON, KIM KYEONG HWAN, KIM MAN SHIK, YEO IN WOOK, CHOI, YOUNG, DEOK, EUM, TAE, KWAN, KIM, JEONG, CHEOL, KIM, JEONG, YOON, KIM, KYEONG, HWAN, KIM, MAN, SHIK, YEO, IN, WOOK
Applicants: CHOI YOUNG DEOK, DAEWOO MOTOR CO LTD, EUM TAE KWAN, KIM JEONG CHEOL, KIM JEONG YOON, KIM KYEONG HWAN, KIM MAN SHIK, YEO IN WOOK, CHOI, YOUNG, DEOK, DAEWOO MOTOR CO., LTD., EUM, TAE, KWAN, KIM, JEONG, CHEOL, KIM, JEONG, YOON, KIM, KYEONG, HWAN, KIM, MAN, SHIK, YEO, IN, WOOK
Application year: 1996
Main classification: F16H37
IPC codes: F16H37