CONE WITH TORQUE TRANSMITTING SEGMENTS

Abstract: A cone (26) to which one/several torque transmitting flexible segment(s) (46) is/are attached. The flexible segment(s) will be used to transmit torque between a coupling member and the cone. Since the flexible segment(s) can be made toothed (47), torque between the coupling member and the cone can be transmitted without the need of friction. The flexible segment(s) is/are attached so that it/they can slide in the axial direction of the cone. When slid in the axial direction, the pitch of the teeth (47) of the flexible segment(s) (26) remain constant so that one coupling member can engage with the teeth (47) of the toothed flexible segment(s) regardless of the axial location of the flexible segment(s) relative to the cone to which it is attached. The cone with torque transmitting flexible segment(s) can be used to construct various Continuous Variable Transmissions.

Description: TITLE: CONE WITH TORQUE TRANSMITTING SEGMENTS BACKGROUND-CROSS REFERENCE TO RELATED APPLICATONS This invention is entitled to the benefit of Provisional Patent Application Ser.# 60/220,532, Filed 2000 July 24. Variation of this invention has been discussed in Non- Provisional Application Ser.# 09/637,437 and Ser. #09/758,707, and Provisional Patent Application Ser. # 60/252375. BACKGROUND— FIELD OF INVENTION This invention relates to variable torque/speed transmission, specifically to a variable transmission where the transmission ratio can be varied continuously between any two predetermined values. BACKGROUND— DESCRIPTION OF PRIOR ART In most applications the transmission ratio, which is the torque vs. speed ratio transmitted by a motor or engine, needs to be adjustable in order for the motor or engine to operate efficiently and effectively. For example, for a vehicle, during start-up, assuming that it is on a level road, the engine needs to provide torque to accelerate the vehicle and torque to overcome the resisting forces mainly due to friction and wind resistance, which is insignificant during start-up. Once the vehicle has reached its desired speed, again assuming that it is on level road, the engine only needs to provide torque to overcome the resisting forces, which in this case are likely to be greater than during start-up but less than the combined torque needed during start-up. Hence in this case the torque that the engine needs to provide is less than needed during start-up. However, here the engine needs to rotate the output shaft at a higher speed since the desired speed of the vehicle is assumed to be greater than the speed of the vehicle during start-up. From the example above it can be seen that during start-up, the engine needs to provide a relatively large torque and operate at a relatively low speed. And once the desired speed is reached, the engine needs to provide a relatively small torque and operate at a relatively high speed. Here a relatively large torque would be wasteful and makes the engine/motor inefficient. Hence in order to increase the efficiency of the motor/engine most vehicles have a transmission, which can vary the torque vs. speed ratio of the engine/motor. Most vehicles, such as cars, bikes, or motorcycles use a discrete variable transmission. Here the operator can select between several discrete transmission ratios usually by selecting an input gear or sprocket to be coupled to an output gear or sprocket. The main advantage of a continuous variable transmission (CVT) over a discrete variable transmission is that a CVT can provide the engine/motor with a more efficient transmission ratio under most conditions. It seems that CVTs are not extensively used because most CVTs need to use friction to transmit torque. The need of friction limits the torque that can be transmitted using a CVT. This is because materials have a strength limit and coefficient of friction limit. Also these devices are most likely less efficient than variable transmissions that use gears or timing belts because of slippage. And using a gearbox to reduce the torque that needs to be transmitted will increase the cost of the CVT and reduce the efficiency and relia ity of the CVT. Furthermore, although the need of friction to transmit torque in continuously variable transmissions might be avoided by using intricate mechanisms, the efficiency of the mechanisms are most likely considerably less than that of gears, belts, or chains. Since a cone is extensively used in CVTs, it seems that a cone would be an ideal device to use in a continuously variable transmission, if it was not for the need of friction to transmit torque between a cone the coupling member. SUMMARY In accordance with the present invention a cone with one/several torque transmitting flexible segment(s), that can be used to construct CVTs that do not relay on friction to transmit torque, some which are discussed in the application. OBJECTIVES AND ADVANTAGES Accordingly, besides the objectives and advantages of the cone with torque transmitting flexible segment(s) described in my above patent, several objectives and advantages of the present invention are: (a) To provide a cone with a/several torque transmitting segment(s) that can be used to construct CVTs that do not relay on friction to transmit torque. (b) To provide several CVTs, which use at least one cone with a/several torque transmitting segments), that have better efficiency than friction dependent CVTs of prior art due to the elimination of slippage. (c) To provide several CVTs, which use at least one cone with a/several torque transmitting segment(s), that are able to transmit more torque than friction dependent CVTs of prior art. Still further objectives and advantages will become apparent from a consideration of the ensuing description and drawings. DRAWING FIGURES In the drawings, closely related figures have the same number but different alphabetic suffixes. Fig 1 A and IB show the general configuration for the cone with flexible segments), where a flexible segment is positioned at the larger end of the cone. Fig IC and ID show the general configuration for the cone with flexible segments), where a flexible segment is positioned at the smaller end of the cone. This cone s labeled as cone 26. Fig 2A, 2B, 2C, and 2D are drawings of a cone with two flexible segments, which are placed opposite of each other. This cone is labeled as cone 26A Fig 3 A, 3B, 3C, and 3D are drawings of a cone with one flexible segments and one non-toothed flexible segment, which is placed opposite of the flexible segment. This cone is labeled as cone 26B. In addition, Fig 3A, 3B, 3C, and 3D also show a mover mechanism that will be used to move the flexible segments) and non-toothed flexible segment(s) attached on a cone in the axial direction. Fig 4A, 4B, 4C, and 4D are drawings of a cone with one flexible segment, which at the smaller end of the cone covers less than half of the circumferential area of the cone. This cone is labeled as cone 26C. Fig 5A and 5B shows a CVT using two cones 26A. This CVT will be labeled as CVT1. Fig 6A is a top-view a CVT that uses two cones 26B, which are coupled to two transmission pulleys. This CVT will be labeled as CVT2. Fig 6B is a top-view a CVT that uses two cones 26C, which are coupled to two transmission pulleys. This CVT will also be labeled as CVT2. Fig. 6C is a cross-sectional front view of CVT2 at the axial midpoint of a flexible segment, which is positioned at the larger end of cone 26B. Fig. 6D is a cross-sectional front view of CVT2 at the axial midpoint of a flexible segment, which is positioned at the smaller end of cone 26B. Fig. 6E shows a joiner mechanism that will be used to connected the slider bushing of the cones 26B. A slider bushings is used to move or maintain the axial position of one/several flexible segments) relative to the surface of its respective cone. Reference Numerals in Drawings 12 driver shaft 14 driven shaft 16 shaft 26 A cone A 26B cone B 26C cone C 27 slot 28 inter-segment space 36 attachment sleeve 37 end cover support sleeve flexible segment N non-toothed flexible segment teeth on flexible segment attachment plate attachment wheel (so it rolls) slider bushing rotor telescope loop transmission belt connector B connectorB gear rack gear marked wheel marked wheel decoder (sensor) slider joiner base slider joiner rod transmission pulley spline sleeve 5 tensioning wheel 6 tensioning slider 7 tensioning constrainer 8 tensioning mover 9 tensioning actuator DESCRIPTION OF TNVENTION-Preferred Embodiments The inventor believes that there is no best method to utilize this invention. Here for some machines one variation, say variation A, works better than the other, say variation B, but the opposite can also true for some other machines. The inventor will clearly identify the advantages of one variation over the other. Here first the basic idea of the invention will be presented in the General Cone Section. Then some alternate configuration of the invention, labeled as cone 26A, cone 26B, and Cone 26C will be presented. Next, a mover mechanism for the invention will be described. Finally, several preferred configurations for a Continuous Variable Transmission (CVT) utilizing the invention will be presented. General Cone (cone 26)-Fig 1A, IB, IC, &1D The corner stone of the invention is shown in Fig 1A, IB, IC, and ID. It consists of a cone 26, which is keyed to shaft 16, to which one/several flexible segment(s) or group of flexible segment(s) 46 is/are attached. The flexible segment(s) 46 will be used to transmit torque from a coupling member to cone 26 without the need of friction. In Fig 1 A/B/C/D, one flexible segment 46, which consists of one continuous member is used. Having a group of flexible segments attached on cone 26 so that it forms one/several continuous segments on the cone 22 would also work. The flexible segment 46 is channel shaped, with two sides and a base. Here the bottom surface of the base of the flexible segment 46 rests on the surface of the cone, and a leveling loop 66 rests on the top surface of the base of flexible segment 46. The purpose of the leveling loop 66 is to provide a level-resting place for a coupling member. The inner side surfaces of flexible segment 46 have teeth 47, which will be used to transmit torque between a coupling member and cone 26. The flexible segment 46 is preferably made out of steel reinforced rubber. In order prolong the live of the flexible segments 46, and reduce the required force to slide the flexible segments 46 to a different axial position on the surface of the cone, the bottom surface of the base of the flexible segments should be PTFE coated. Furthermore, the flexible segment 46 has one attachment plate 48 attached near its ends. The heads of the attachment plates 48 are preferably molded into the flexible segments 46. The length of flexible segment 46 can be varied according to the need of the CVT where the flexible segment is utilized. In order to attach the flexible segments 46 to the cone 26, the cone 26 has two slots 27. Here the attachment plates 48 of the flexible segment 46 are placed in the slots 27, and secured to cone 26 using an attachment wheel 49. The attachment wheels 49 are aligned so that they roll when the flexible segment 46 is moved from one axial position on cone 26 to another. Furthermore, the attachment plates 48 can also be used to attach a mover mechanism, which will be described in the following sections, used to move the flexible segment 46. The flexible segment 46 is attached on cone 26 so that it can only slide in the axial direction of the cone, which is the direction along the length of shaft 16. The arc length and hence pitch of the flexible segment 46 remains constant regardless of its location on cone 26. Therefore, here one coupling member is able to transmit torque to cone 26 via the flexible segment 46 at all axial locations of the flexible segment 46 on the cone 26. Furthermore, in order to prevent a coupling member such as transmission belt to deform as it comes in and out of contact with flexible segment 46, the surface of cone 26 that will not be covered by flexible segment 46, should be made flush with the top surface of the base of flexible segment 46. Another method would be to eliminate the base of the flexible segment entirely, so that the two side surfaces of flexible segment 46 sit directly on the surface of the cone. This can be achieved by constructing flexible segment 46 out of two side surfaces, which will be joined beneath the surface of cone 26. In order to reduce vibrations due to the centrifugal force of flexible segment 46, the cone should be properly balanced The cones should be made out of die-cast stainless steel. And in order to obtain better dimensional tolerances and a smoother surface finish the cones obtained from the die-cast process should are machined. This invention does not relay on friction on the surface of the cones to transmit torque. And since it is also desirable to minimize the friction between the transmission belt and the surface of the cone, the surface of the cone should be PTFE coated. This will minimize the force necessary to change to the position of flexible segment 46 on cone 26, and will extend the live of flexible segment 46. Cone 26A-Fig 2A, 2B, 2C, & 2D Cone 26A, is a cone 26 with the restriction described in this section. Cone 26A has two flexible segments 46, which are attached opposite from each other on the surface of the cone. Furthermore, at the smallest end of cone 26 A, each flexible segment 46 covers less than half of the circumference surface area of cone 26 at the axial section where the flexible segments 46 is located. The space between the flexible segments 46 will be referred to as the inter-segments space 28. Also, since cone 26A is symmetrical about its axis of rotation, there is no need to balance this cone. Cone 26B-Fig 3A, 3B, 3C, & 3D The only difference between cone 26A and cone 26B is that for cone 26B one flexible segment 46 is replaced with a non-toothed flexible segment 46N. The non-toothed flexible segment 46N is identical to the flexible segment 46 except that its inner side surfaces are not toothed, and it side surfaces are PTFE coated and shaped as not to transmit torque. The function of non-toothed flexible segment 46N is to counterbalance the centrifugal force of flexible segment 46 and contain the transmission belt that will be used as a coupling member. Cone 26C-Fig 4A, 4B, 4C, & 4D Cone 26A, is a cone 26 with the restriction described in this section. Here, at the smaller end of cone 26C, the flexible segment 46 covers less than half of the circumferential surface area of cone 26C at the axial location where the flexible segment 46 is positioned. Like before, in order to reduce vibration due to the centrifugal force of the flexible segment the cone should be balanced. Moving Mechanism-Fig 3A, 3B, 3C, & 3D The flexible segments 46 and the non-toothed flexible segments 46N will be moved relative to the surface of the cone to which they are attached using a mover mechanism. Here the non-toothed flexible segments 46N are attached to the mover mechanism in the same manner as the flexible segments 46, for clarity the non-toothed flexible segments 46N will not be referred to in this section. The mover mechanism consists of a slider bushing 55, which is attached to a shaft in such a manner that it tightly fits onto the shaft but is free to slide along the length of the shaft. A rotor 56 is fitted into the slider. A locking collar will be used to fix the axial position of rotor 56 relative to slider bushing 55, however rotor 56 is free to rotate on slider bushing 55. In order to attach telescopes 57 to rotor 56, pin-holed plates are attached to the outer surface of rotor 56. The telescopes 57 will be used to attach the flexible segments 46 to rotor 56, so that the axial position of the flexible segment(s) 46 depend(s) on the axial position of rotor 56. The length of telescopes 57 can vary so that they can connect the flexible segment(s) 46 to rotor 56 when the flexible segment(s) 46 is/are located at the smallest end of cone 26(A/B/C) and at the largest end of their cone 26 (A/B/C). The bottom end of each telescope 57 has a two pin-holed plates, which will be used to join the bottom end of each telescope 57 to a pin-holed plate on the rotor using a bolt and nut or a locking pin. The top end of each telescope 57 has an attachment plate, which is free to rotate only along the axis of rotation of cone 26(A B/C). The attachment plate of a telescope 57 is joined to an attachment plate 48 of a flexible segment 46 using a bolt and a nut or a locking pin. All parts discussed above are preferably made out of stainless steel, except the slider bushing 55, which is preferably made out of oil- impregnated bronze. Hence, using this mechanism the axial location of the flexible segments 46 or the non-toothed flexible segments 46N on the cones 26 and the cones 26(A B/C) can be changed by changing the axial location of slider bushing 55. Continuous Variable Transmission Variation 1 (CVTl)-Fig 5A & 5B CVT1 consists of a pair of cones 26A, each equipped with a mover mechanism described in the previous paragraph, that are coupled by a transmission belt 67. Here one cone 26 A will be keyed to a driver shaft 12 and the other cone 26A will be keyed to a driven shaft 16. Torque between the cones 26A is transmitted via the timing belt 67, which axial location is fixed relative to the flexible segments 46. The transmission ratio depends on the location of the flexible segments 46 on the surface of the cones 26A. Under this configuration, the length of transmission belt 67 should be perpendicular to the length of the driven shaft 12 and driving shaft 14. In order to achieve this, the slider bushing 55 on the driver shaft 12 and the slider bushing 55 on the driven shaft 14 are rigidly connected using a connector 75. In order to change the transmission ratio, an actuator, will be used to change the axial position of the connector 75, which in turn will change the axial location of transmission belt 67 on the cones 26 A. Under this configuration transmission belt 67 is only moveable when it is not in contact with one complete inter-segment space 28 of a cone 26 A. This is because the arc length of an inter-segment space 28 changes as the axial location of the transmission belt 68 is changed. Hence changing the position of transmission belt 68 while it is contact with a complete inter-segment space 29 will stretch the transmission belt 68. In order to solve this problem, the actuator, is equipped with a spring-loaded piston. Here when the transmission belt 67 is in a moveable position, than the flexible segments 46 will move with the actuator. However, when the transmission belt 67 is not in a moveable position then moving the actuator 75 will not move the flexible segments 46 but will stretch or compress spring loaded, until a limit switch on the spring-loaded piston are activated. And once both cones have rotated to a moveable position than the tension or compression in the spring-loaded piston will move the transmission belt 68 in the direction the actuator 75 was moved. When the transmission belt 68 is in a position where the cone 26A on the driver shaft 12 rotates at the same speed as the cone 26A on the driven shaft 14. Then the transmission belt 67 can get stuck in a position where the transmission belt 67 is not moveable. One method to avoid this problem is to have a configuration where the smaller end of one cone 26A is slightly larger than the larger end of the other cone 26 A. Under this configuration the cones 26A will never rotate at the speed, so that the angular position of one cone 26A relative to the other cone 26A changes with the rotation of the cones 26A. Another method to avoid having the transmission belt stuck in an immovable position is to have a mover control system control the movement of the actuator. Here, every time the actuator is about to move the transmission belt 67 to position where the transmission ratio between the cones 26A is unity, the mover control system will stop the actuator. Then the mover control system will wait until both cones 26A have moved to a angular position so that transmission belt 67 will be in a moveable position once the actuator moves it to the position where the transmission ratio between the cones 26A is unity. In order for this system to work the actuator needs to be fast enough so that the speed variation of the input shaft will not significantly affect the radial position of the flexible segments 46 when they are being moved by the actuator. Here the mover control system consists of several sensors, a computer, and an actuator. In order for the mover control system to determine the angular position and angular speed of the cones 26A, a marked wheel 85 is keyed to the driver shaft 12 and to driven shaft 14, and a marked wheel decoder 86 is attached to the frame of the CVT. Furthermore, in order to determine the axial locations of the flexible segments 46, a gear rack 76 is attached so that it moves with the actuator, and a gear 77, which engages the gear rack 76 is attached to the frame of the CVT. A marked wheel 85 is attached to the gear, and a marked wheel decoder 86 decodes the information from this marked wheel 85. The information from the sensors above will be transmitted and processed by a computer, which will then use this information to properly move the actuator. Since the mover control system can also be used to determine when the transmission belt 67 is in a moveable position, the spring-loaded piston is not needed for this design. Furthermore, when gear 77 is coupled to a rotary actuator it can be used as the actuator, which controls the axial position of the transmission belt 67 (Fig 5 A). Continuous Variable Transmission Variation 2 (CVT2)-Fig 6A, 6B, 6C, 6D, & 6E CVT2 consist of either two cones 26B, which are keyed to a driver shaft 12 so that the flexible segment 46 of one cone 26B is opposite from the flexible segment 46 of the other cone 26B, or two cones 26C, which are attached in the same manner. Each cone 26(B/C) is coupled to a transmission pulley 98 by a transmission belt 68. The transmission pulleys 98 are attached on the driven shaft 14. In order to avoid having to use the leveling loop 66 for this CVT, the bottom surface of the base of each transmission belt 68 and the surface of each transmission pulley 98 has to be angled so that the entire bottom surface of each transmission belt 68 can rest on the surface its respective cone 26C and transmission pulley 98 without being twisted. Here, the transmission ratio is controlled by controlling the axial location of the flexible segments 46 relative to their respective cones using the mover mechanism described in the previous sections. In order to ensure that the axial location of the flexible segments 46 relative to their respective cones 26(B/C) is identical, the slider bushing 55 of each cone 26(B/C) are rigidly connected using a slider joiner base 97 and slider joiner rods 97 (Fig 6E). The change in axial location of the flexible segments 46 has to be accompanied by the change in axial location of the transmission pulleys 98. In order to achieve this, the transmission pulleys 98 are keyed to a spline sleeve 99, which is free to slide along the length of the driven shaft 14 but is not free to rotate relative to driven shaft 14. Furthermore, the slider bushing 55 of the cone 26(B/C) located closes to an actuator and the spline sleeve 99 are connected by a connector 75B so that the flexible segments 46 are properly aligned with the transmission pulleys 99. I Furthermore, in order to avoid creating an excessive slack in the transmission belts 67 as they and are moved from the larger ends of cones 26(B/C) to the smaller ends of cones 26(B/C), each transmission belt 67 is equipped with a tensioning mechanism. The tensioning mechanism consists of two tensioning wheels 105, two tensioning sliders 106, two tensioning constrainers 107, a tensioning moverl08, and a tensioning actuator 109. The tensioning wheels 105 will be attached so that they touch the base of the transmission belts 67 at/near the midpoint between the driver shaft 12 and the driven shaft 14. Each tensioning wheel 105 is attached to a tensioning slider 106. Each tensioning slider 106 slides on a tensioning constrainer 107. Furthermore, in order to move a tensioning slider 106, each tensioning slider 106 has two vertical sleeves. Tensioning constrainer 107 is angled so that the tensioning wheels 105 will eliminate excessive slack in the transmission belts 67 as it is moved from the larger end of the cones 26(B/C) to the smaller ends of the cones 26(B/C). Furthermore, the tensioning actuator 109 will be used to move the tensioning slider 106 and hence the tensioning wheels 105 with the transmission belts 67, when the transmission belts 67 are moved to a different axial position. The tensioning mover 108 consists mainly of two pairs of vertical guides, which move with the tensioning actuator 109. Here the vertical sleeves of the tensioning sliders 106 will slide on the vertical guides of the tensioning mover 108, so that the vertical movements of the tensioning sliders 106 will not be constricted by the movement of the tensiomng actuator 109. Furthermore, tensioning wheels 105 should have smooth non-teethed side surfaces to maintain the alignment of the transmission belts 67, this is especially important if cones 26C are used. The main advantage of CVT2 over CVTl is that the transmission ratio can be changed regardless of the radial position of the cones. This increases the reliability and response time of CVT2. Also here the surface of the transmission pulleys 98 can be made so that there is no need for the leveling loop 66. However, CVT2 needs two transmission belts 67 in order to operate properly, while CVTl only needs one. This and the fact that CVTl also needs two timing pulley's 95 reduces the reliability of CVT2 and might increases the price of CVT2 ADVANTAGES From the description above, a number of advantages of the cone with torque transmitting segments become evident: (a) Compared to discrete transmission ratio transmission, which is used in almost any high torque application, one/several cone(s) with torque transmitting segment(s) can be used to construct a CVT, which allows the engine/motor to perform more efficiently. This is because in most cases a CVT will be able to provide a more efficient transmission ratio than a discrete transmission ratio transmission. (b) Compared to friction dependent CVTs, one/several cone(s) with torque transmitting segments can be used to construct a CVT with higher torque capacity, higher efficiency, and longer live. OPERATION In order to use one/several cone(s) 26, the designer first determines the requirements and constraints of the CVT needed. From there he/she can construct a CVT using one/several cone(s) 26 according to his/her needs. In order to use a CVT constructed out of one/several cone(s) 26, such as CVTl and CVT2, the operator first couples a motor or engine to the input shaft 12 of the CVT and couples the member to be driven to the output shaft 14 of the CVT. Next, in order to change the transmission ratio, which is achieved by changing the axial location of the transmission belt 68, he/she manually or automatically moves an actuator. CONCLUSION, RAMIFICATION, AND SCOPE Accordingly the reader will see that the cone with torque transmitting flexible segments can be used to construct a non-friction dependent Continuous Variable Transmission (CVT), which has the following advantages over an existing Variable Transmissions: • Compared to Discrete Variable Transmissions, it is able to provide a more efficient ttansmission ratio for the motor or engine under most circumstances due to its infinite ttansmission ratio over a predetermined range. • It provides a torque transmission ability and efficiency almost as good as transmissions utilizing gears, and sprocket and chains, which have not yet been effectively used to construct CVTs. Gears, and sprocket and chains are currently almost used in any high torque ttansmission application due to their superior torque ttansmission ability and efficiency over any other transmissions. • Hence the CVT transmissions constructed out of the cone(s) with torque transmitting flexible segments will most likely provide higher torque ttansmission ability and efficiency over other CVT transmissions. Although the description above contains many specificities, these should not be construed as limiting the scope of the invention but as merely providing illustrations of some of the presently preferred embodiments of this invention. For example, a CVT can be constructed out of one cone 26A described above coupled to a timing pulley. Under this configuration only one cone 26A is needed, and the transmission belt 67 will never get stuck in an unmovable position. Also in order to reduce cost, the toothed flexible segments 46 might be replaced with a non-toothed flexible segment so that a V-belt can be used instead of a toothed ttansmission belt 67. Furthermore by using a cone 26D, which is identical to cones 26 described in the general cone section, except for having a flexible segment 46 with a square cross section instead of a channel shaped one, gears can used to transmit torque from one/several cones 26D on a driver shaft to a driven shaft and vice versa. For example if the arc length of the flexible segment 46 at the largest end of the cone 26D is not less than half the circumference of cone 26D at that axial location, than a CVT can be constructed where two gears, which are attached so that they can engage with the teeth 47 of the flexible segment 46, sandwich a cone 26D. Also a CVT, which consist of several cones 26D, which engage directly with another cone 26D can also be designed. The CVTs mentioned in this paragraph need additional parts to be workable. However given the time and need, a workable model for the designs mentioned in this paragraph as well as many other design could be conceived. Here the concept of the cone with torque transmitting flexible segments might be treated like a gear, which can be used to construct a device according to the specific requirements and constraints of the designer. Thus the scope of the invention should be determined by the appended claims and their legal equivalents, rather than by the examples given.

Claims: Claims: I claim: 1. A cone assembly that can be used to construct various non-friction dependent CVTs, comprising: (a) A cone (b) At least one torque transmitting flexible segment or one group of torque transmitting segment, which is/are attached to said cone in such a manner that it/they partially wrap around the surface of said cone and can only slide in the direction of the axis of rotation of the cones. The arc length of each said flexible segment or group of flexible segment remains constant as it is being slid from the smaller end of said cone to the larger end of said cone. (c) Means for slide-ably attaching said flexible segments) to the surface of said cone. 2. The cone assembly of claiml wherein surface of said cone has several slots used to slide-ably attach said flexible segments) to said cone. 3. The cone assembly of claim 2 wherein attachment plates are molded to the bottom surface of said flexible segments. Then in order to secure the said flexible segments to the said cone, the said attachment plates are placed in said slots of said cone and secured using an attachment wheel. 4. The cone assembly of claim 1 wherein radial cross sections of said flexible segments are channel shaped with two sides and a base. 5. The cone assembly of claim 4 wherein inner surfaces of said sides of said flexible segment are toothed. 6. The cone assembly of claim 5 wherein a leveling loop is placed between said sides of said flexible segment. The said leveling loop will be used to provide a level-resting surface for a transmission belt on the surface of said cone assembly. 7. The cone assembly of claim 6 wherein two said flexible segments are placed opposite from one another on the surface of said cone. Also at the smaller end of the said cone each said flexible segment covers less than half of the circumferential surface of the said cone. 8. A continuous variable ttansmission (CVT), comprising: a) Two shafts. b) Two said cone assemblies of claim 7, each attached to a different said shaft. The apex of one said cone assembly is opposite of the apex of the other said cone assembly. c) A transmission belt, used to couple said cone assemblies. d) Means for changing the ttansmission ratio by changing the axial position of said flexible segments hence said ttansmission belt. e) Means for controlling the said means for changing the transmission ratio. 9. The CVT of claim 8 wherein the ttansmission ratio is changed by changing the axial position of said flexible segments using a mechanism comprising of: a) A slider bushing, which is slide-ably attached to said shafts. b) A rotor attached to said slider bushing so that it is not restricted to rotate relative to said slider bushing, but is fixed relative to said slider bushing in the axial direction. c) A telescope connecting the said attachment plates of said flexible segment to said rotor. 10. The cone assembly of claim 5 wherein said cone has one flexible segment and one non-toothed flexible segment, which is placed opposite from said flexible segment. Also at the smallest end of said cone, said flexible segment and said non-toothed flexible segment cover less than half of the circumferential surface of the said cone. 11. A CVT, comprising: a) Two shafts b) Two said cone assemblies of claim 10, which are keyed on one said shaft in a manner so that said flexible segment of one said cone assembly is opposite of said flexible segment of the other said cone assembly. The apex of both said cone assemblies point in the same direction. c) Two transmission pulleys. d) A spline sleeve to which the ttansmission pulleys are keyed. The said spline sleeve is attached to one said shaft in such a manner that it can slide along the length of said shaft, but cannot rotate relative to said shaft. e) Two transmission belts. Each ttansmission belt will be used to couple one said cone assembly to one said transmission pulley. f) Means for changing the ttansmission ratio by changing the axial position of the said flexible segments, the said transmission pulleys, and the said transmission belt. g) Means for eliminating the slack in the transmission belt that forms when the said ttansmission belt is moved from the larger end of said cone assemblies to the smaller end of said cone assemblies. 12. The CVT of claim 11 wherein means for changing the axial position of the said flexible segment and the said non-toothed flexible segment utilizes the mechanism of claim 9. 13. The cone assembly of claim 5 wherein said cone has one flexible segment. Also at the smallest end of said cone, said flexible segment cover less than half of the circumferential surface of the said cone. 14. A CVT, comprising: a) Two shafts b) Two said cone assemblies of claim 13, which are keyed on one said shaft in a manner so that said flexible segment of one said cone assembly is opposite of said flexible segment of the other said cone assembly. The apex of both said cone assemblies point in the same direction. c) Two transmission pulleys. d) A spline sleeve to which the ttansmission pulleys are keyed. The said spline sleeve is attached to one said shaft in such a manner that it can slide along the length of said shaft, but cannot rotate relative to said shaft. e) Two ttansmission belts. Each ttansmission belt will be used to couple one said cone assembly to one said transmission pulley. f) Means for changing the ttansmission ratio by changing the axial position of the said flexible segments, the said ttansmission pulleys, and the said transmission belt. g) Means for eliminating the slack in the transmission belt that forms when the said transmission belt is moved from the larger end of said cone assemblies to the smaller end of said cone assemblies. h) Means for maintaining the alignment of said ttansmission belts. 15. The CVT of claim 11 wherein means for changing the axial position of the said flexible segment utilizes the mechanism of claim 9.

Inventors: TAY ARMIN SEBASTIAN, TAY, ARMIN, SEBASTIAN
Applicants: TAY ARMIN SEBASTIAN, TAY, ARMIN, SEBASTIAN
Application year: 2001
Main classification: F16H9
IPC codes: F16H7, F16H9, F16H55