CN1896561A - Continuously variable transmission - Google Patents

Abstract

A continuously variable transmission is disclosed for rotationally or linearly driven machines and vehicles. The single-shaft transmission device provides a user with a convenient manual gear shifting method. Another embodiment is disclosed that automatically shifts gears based on the rotational speed of the wheels. Furthermore, the actual commercialization of traction roller drives requires improvements in reliability, ease of shifting, functionality and simplicity of the transmission. The disclosed transmission can be used in vehicles such as automobiles, motorcycles and bicycles. The transmission may for example be driven by a power transmission mechanism such as a sprocket, gear, pulley or rod, optionally driving a one-way clutch connected to one end of the main shaft.

Description

Continuously variable transmission

technical field

The field of the invention relates to transmissions. The present invention relates more particularly to continuously variable transmissions.

Background technique

In order to provide a continuously variable transmission, traction roller transmissions have been developed in which power is transmitted between torque input and output discs via traction rollers supported in a housing. In such a transmission, traction rollers are mounted on each support structure so that when the support structure rotates, the traction rollers engage torque discs on circles of different diameters depending on the desired transmission. It depends.

However, these conventional solutions have had limited success, for example, in US Patent No. 5,236,403 to Schievelbusch, which discloses a drive hub for a vehicle having a variable adjustable transmission ratio. Schievelbusch teaches the use of two spacers, one on each side of the traction rollers, to skew the axis of rotation of each roller. However, the use of two dividers can be complicated because many components are required to adjust each divider during a shift of the transmission. A further difficulty with this transmission is that it has a guide ring which is constructed essentially stationary relative to each roller. Since the guide ring is fixed, it is difficult to move the axis of rotation of each traction roller. Yet another limitation of this design is that it requires two half shafts, one on each side of the rollers, to create a gap between the two half shafts. This clearance is necessary because the rollers are moved in rotation rather than linear sliding. The use of two shafts is undesirable and requires a complex fastening arrangement to prevent bending of the shafts should the transmission be accidentally bumped, as often happens when the transmission is used in a vehicle. Yet another limitation of this design is that it does not provide an automatic transmission.

Accordingly, there is a need for a continuously variable transmission having a simpler shifting method, a single shaft, and a support ring having a substantially uniform outer surface. In addition, an automatic traction roller transmission is required, which is designed as an automatic gearshift. Furthermore, the actual commercialization of traction roller drives requires improvements in reliability, ease of shifting, functionality and simplicity of the transmission.

Contents of the invention

The invention includes a transmission for rotationally or linearly driven machines and vehicles. For example, the transmission can be used in machinery such as drill presses, turbines and food processing equipment, as well as in vehicles such as automobiles, motorcycles and bicycles. The transmission may for example be driven by a power transmission mechanism such as a sprocket, gear, pulley or rod, optionally driving a one-way clutch connected to one end of the main shaft.

In one embodiment of the present invention, the transmission device includes: a rotatable driving member; three or more power regulating devices, wherein each power regulating device rotates around a rotating shaft located at the inner center of each power regulating device ; a support member providing a bearing surface in frictional contact with each power regulating device, wherein the support member rotates about an axis located at the inner center of the support member; at least one platform for actuating the axial movement of the support member and to actuate the transfer of the axis of rotation of the power adjustment device, wherein the platform provides a convex surface; at least one fixed support, which cannot rotate around the axis of rotation defined by the support member, wherein the at least one fixed support provides a concave surface; and a plurality of spindle supports, wherein each spindle support is in sliding engagement with the convex surface of the platform and the concave surface of the stationary support, and wherein each spindle support adjusts the power adjustment device in response to axial movement of the platform axis of rotation.

In another embodiment, the transmission device includes: a rotatable driving member; three or more power regulating devices, wherein each power regulating device rotates around a rotation axis respectively being the center of each power regulating device; a support member providing a bearing surface in frictional contact with each power regulating device, a rotatable drive member for rotating each power regulating device; a bearing plate having a plurality of inclined ramps for actuating rotation of the drive member; a coil spring for biasing the rotatable drive member to each power adjustment device; at least one locking pawl ratchet, wherein the locking pawl ratchet is rigidly connected to the rotatable drive member, at least A locking pawl is operatively connected to the coil spring; and at least one locking pawl is used to lock the locking pawl ratchet correspondingly to the rotatable drive member disengaged from the power adjusting device.

In yet another embodiment, the transmission comprises: a rotatable drive member; three or more power regulating devices, wherein each power regulating device rotates about an axis which is respectively the center of each power regulating device; a support member providing a bearing surface in frictional contact with each power regulating device, wherein the support member rotates about an axis centrally located within the support member; a bearing plate having a plurality of inclined ramps for actuating the rotation of the drive member; a threaded member coaxially and rigidly connected to the rotatable drive member or bearing disc; and a nut, if the threaded member is connected to the rotatable drive member, the nut is coaxially and rigidly connected Attached to the bearing disc, or if the threaded member is rigidly attached to the bearing disc, the nut is coaxially and rigidly attached to the rotatable drive member, wherein the inclined ramp of the bearing disc has a greater lead than the threaded member (lead).

Description of drawings

Fig. 1 is the side sectional view of transmission device of the present invention;

Figure 2 is a partial perspective view of the transmission of Figure 1;

Figure 3 is a perspective view of two fixed supports of the transmission of Figure 1;

Fig. 4 is a partial end face sectional view of the transmission device of Fig. 1;

Figure 5 is a perspective view of a drive plate, bearing housing, screw and ramp bearing of the transmission of Figure 1;

6 is a perspective view of a ratchet and pawl subsystem of the transmission of FIG. 1 for engaging and disengaging the transmission;

Figure 7 is a partial perspective view of the transmission of Figure 1 with a rotatable drive disc removed;

Figure 8 is a partial perspective view of the transmission of Figure 1 with the hub shell particularly removed;

Fig. 9 is a partial perspective view of the transmission of Fig. 1, wherein shifting is performed automatically;

Figure 10 is a perspective view of a shift handle mechanically connected to the transmission of Figure 1;

Figure 11 is an end view of a thrust bearing of the transmission shown in Figure 1, which is used for automatic shifting of the transmission;

Figure 12 is an end view of the weight structure of the transmission shown in Figure 1;

Figure 13 is a perspective view of another embodiment of the actuator bolted to a planar surface;

Figure 14 is a side sectional view of the transmission shown in Figure 13;

Figure 15 is a schematic end view of the transmission of Figure 1 showing cables routed across the spacer extension of the automatic portion of the transmission;

FIG. 16 is a schematic end view of the cable routing of the transmission shown in FIG. 13 .

Detailed ways

The following detailed description is directed to certain specific embodiments of the present invention. However, the invention can be implemented in many different ways as defined and covered by the claims. In this specification, in the various drawings referred to, the same components are denoted by the same reference numerals. Furthermore, embodiments of the invention may include several novel features, no one of which is solely responsible for its required attributes or which are essential to practicing the invention described herein.

The present invention includes a continuously variable transmission that can be used in conjunction with any type of machine that requires a transmission. For example, transmissions can be used in (i) motorized vehicles such as automobiles, motorcycles, or boats, (ii) non-motorized vehicles such as bicycles, tricycles, scooters, exercise equipment, or (iii) industrial equipment such as drill presses, power equipment , or looms.

Referring to Figures 1 and 2, a continuously variable transmission 100 is disclosed. The transmission 100 is covered within a hub shell 40 covered by a hub cover 67 . At the center of the transmission 100 are three or more power conditioning devices 1a, 1b and 1c, which are spherical and equally spaced circumferentially around the centerline or axis of rotation of the transmission 100 . As can be seen more clearly from Figure 2, the spindles 3a, 3b and 3c are inserted through the centers of the power regulating devices 1a, 1b and 1c to define the axes of rotation of the power regulating devices 1a, 1b and 1c. In Fig. 1, the rotation axis of the power regulating device is shown in the horizontal direction. The mandrel supports 2a-2f are vertically attached to and attached to the respective exposed ends of the mandrels 3a, 3b and 3c. In one embodiment, each mandrel support has a hole to receive one end of one of the mandrels 3a, 3b and 3c. The spindles 3a, 3b and 3c also have spindle rollers 4a-4f coaxially and slidingly positioned on the exposed ends of the spindles 3a, 3b and 3c outside the spindle supports 2a-2f.

When changing the rotation axis of the power regulating devices 1a, 1b and 1c by tilting the spindles 3a, 3b and 3c, each of the spindle rollers 4a-4f follows the grooves cut in the fixed supports 5a, 5b Slots 6a-6f move. Referring to FIGS. 1 and 3 , the fixed supports 5 a , 5 b are substantially in the form of parallel discs with an axis of rotation along the center line of the transmission 100 . The grooves 6 a - 6 f extend from the outer periphery of the fixed supports 5 a , 5 b toward the centerline of the transmission 100 . Although the sides of the grooves 6 a - 6 f are substantially parallel, the bottom surfaces of the grooves 6 a - 6 f form a decreasing radius as they extend toward the centerline of the transmission 100 . When the transmission 100 is shifted to a lower gear or a higher gear by changing the axis of rotation of the power regulating devices 1a, 1b and 1c, each pair of spindle rollers 4a on a single spindle 3a, 3b and 3c -4f move in opposite directions along their respective grooves 6a-6f.

Referring to Figures 1 and 3, central holes 7a, 7b in the fixed supports 5a, 5b allow a hollow shaft 10 to be inserted through the fixed supports 5a, 5b. Referring to Figure 4, in one embodiment of the invention, one or more of the fixed support holes 7a, 7b may have a non-cylindrical shape 14 which fits onto a corresponding non-cylindrical body 15 along the hollow shaft 10 In order to prevent any relative rotation between the fixed supports 5 a , 5 b and the hollow shaft 10 . If the rigidity of the fixed supports 5a, 5b is insufficient, additional structures may be employed to minimize any relative rotation or bending of the fixed supports 5a, 5b. Such movement of the fixed supports 5a, 5b results in a constraint on the spindle rollers 4a-4f as they move along the grooves 6a-6f.

As shown in Figures 4 and 7, the additional structure may take the form of spacers 8a, 8b and 8c connected between the fixed supports 5a, 5b. The spacers 8a, 8b and 8c increase the stiffness between the fixed supports 5a, 5b and, in one embodiment, are located near the outer periphery of the fixed supports 5a, 5b. In one embodiment, the fixed supports 5a, 5b are connected to the spacers 8a, 8b and 8c by means of bolts or other fastening means 45a-45f inserted through holes 46a-46f in the fixed supports 5a, 5b.

Referring again to FIGS. 1 and 3 , the fixed support 5 a is fixedly connected to a fixed support sleeve 42 coaxially surrounding the hollow shaft 10 and extending through the wall of the hub shell 40 . The end of the fixed support sleeve 42 extending through the hub shell 40 is connected to the frame support and preferably has a non-cylindrical shape to enhance the subsequent connection of a torque rod 43 . As shown more clearly in FIG. 7 , a torque rod 43 is placed on the non-cylindrical end of the fixed support sleeve 42 and held in place by a torque nut 44 . The torque rod 43 is rigidly connected at its other end to a strong, stationary member, such as a frame (not shown). A fixed support bearing 48 supports the hub shell 40 and allows rotation of the hub shell 40 relative to the fixed support sleeve 42 .

Referring again to FIGS. 1 and 2 , gear shifting is manually actuated by axially sliding a rod 11 located in a hollow shaft 10 . One or more pins 12 are inserted into one or more transverse holes in the rod 11 and also extend through one or more longitudinal slots 16 (not shown) in the hollow shaft 10 . A slot 16 in the hollow shaft 10 enables the axial movement of the pin 12 and rod 11 assembly within the hollow shaft 10 . When the rod 11 slides axially in the hollow shaft 10 , each end of the transverse pin 12 projects into and is connected to a coaxial sleeve 19 . The sleeve 19 is fixedly connected at each end to a substantially planar platform 13 a , 13 b forming a groove around the circumference of the sleeve 19 .

As can be more clearly seen from Figure 4, the planar platforms 13a, 13b each contact and push a plurality of wheels 21a-21f. The wheels 21a-21f fit into grooves in the spindle supports 2a-2f and are held in place by the wheel axles 22a-22f. The axles 22a-22f are supported at their respective ends by the spindle supports 2a-2f and allow the wheels 21a-21f to rotate.

Referring again to Figures 1 and 2, the substantially planar platforms 13a, 13b transform into a raised surface at their outer periphery (furthest from the hollow shaft 10). This area can clear the gap when shifting the transmission 100 while the spindle supports 2a-2f and the power regulating devices 1a, 1b and 1c are skewed. A cylindrical support member 18 is located in a recess formed between the planar platforms 13a, 13b and the sleeve 19 and thereby moves in unison with the planar platforms 13a, 13b and the sleeve 19. The support member 18 rides on contact bearings 17a, 17b at the intersection of the planar platforms 13a, 13b and the sleeve 19 so that the support member 18 is free to rotate about the axis of the transmission 100 . Thus, when the transmission 100 is shifted, the bearings 17a, 17b, the support member 18 and the sleeve 19 all slide axially with the planar platforms 13a, 13b.

Referring now to Figures 3 and 4, fixed support rollers 30a-301 are attached in pairs to each spindle leg 2a-2f by roller pins 31a-31f and held in place by roller clamps 32a-321. The roller pins 31a-31f allow the fixed support rollers 30a-301 to freely rotate about the roller pins 31a-31f. The rollers 30a-301 of the fixed support roll on concave radii in the fixed supports 5a, 5b along a path substantially parallel to the grooves 6a-6f. As the spindle rollers 4a-4f move back and forth within the grooves 6a-6f, the fixed support rollers 30a-301 allow neither the ends of the spindles 3a, 3b and 3c nor the spindle rollers 4a-4f The bottom surfaces of the grooves 6a-6f are contacted in order to maintain the position of the mandrels 3a, 3b and 3c and to minimize any frictional losses.

Figure 4 shows the rollers 30a-301, roller pins 31a-31f and roller clamps 32a-321 of the fixed support, as can be seen from the fixed support 5a for ease of viewing. For the sake of clarity, many reference numbers of the rollers 30a-301, roller pins 31a-31f and roller clamps 32a-321 of the stationary support in FIG. 1 are not labeled in FIG.

Referring to Figures 1 and 5, a concave drive plate 34 is positioned adjacent to the fixed support 5b, partially enclosing but not in contact with the fixed support 5b. The drive disc 34 is rigidly connected through its center to a threaded member 35 . The screw 35 is coaxial with the hollow shaft 10 adjacent to the fixed support 5b and forms a sleeve around the hollow shaft 10 and faces a drive member 69 . The drive plate 34 is rotatably connected to the power regulating devices 1a, 1b and 1c along a peripheral bearing surface on the lip of the drive plate 34 . A nut 37 is threaded onto the threaded member 35 and is rigidly attached to a bearing disk 60 around its periphery. One face of the nut 37 is also connected to the drive member 69 . Also rigidly attached to the surface of the bearing disc 60 are a plurality of ramps 61 facing the drive disc 34 . For each ramp 61 there is provided a ramp bearing 62 held in place by a bearing cage 63 . The ramp bearing 62 contacts the ramp 61 and the drive plate 34 . A spring 65 is connected at one end to bearing housing 63 and at the other end to drive plate 34 or, in another embodiment, bearing plate 60 to bias ramp bearing 62 against ramp 61 . The bearing plate 60 contacts a hubcap bearing 66 on its side opposite the ramp 61 and on approximately the same circumference. The hubcap bearing 66 contacts the hubcap 67 and the bearing disc 60 so that they can move relative to each other. Hub cap 67 is threaded or pressed into hub shell 40 and secured by an inner race 68 . A sprocket or pulley 38 is rigidly connected to the rotating drive member 69 and is held in place externally by a tapered bearing 70 secured by a tapered nut 71 and internally by a drive bearing 72 in which the drive Bearing 72 contacts drive member 69 and hubcap 67 .

In operation, an input rotation from the sprocket or pulley 38 fixedly connected to the drive member 69 rotates the bearing plate 60 and the plurality of ramps 61 causing the ramp bearings 62 to roll on the ramps 61 and drive the The disk 34 is pressed against the power regulating devices 1a, 1b and 1c. At the same time, the nut 37 rotates to combine the screw 35 and the nut 37 , wherein the lead of the nut 37 is smaller than that of the ramp 61 . This structure gives the rotation of the drive disc 34 pressed against the power regulating devices 1a, 1b and 1c. The power adjusting devices 1a, 1b, and 1c contact and rotate the hub shell 40 when rotating.

When the transmission 100 is coasting, the sprocket or pulley 38 stops rotating while the hub shell 40 and power regulators 1a, 1b and 1c continue to rotate. This causes the drive disc 34 to rotate causing the threaded member 35 to thread into the nut 37 until the drive disc 34 no longer contacts the power regulating means 1a, 1b and 1c.

Referring to Figures 1, 6 and 7, a coil spring 80 coaxial with the transmission 100 is located between the bearing disc 60 and the drive disc 34 and is secured at each end of the coil spring 80 by means of pins or other fasteners (not shown). Connected on the bearing disc 60 and the drive disc 34. During operation of the transmission 100 , the coil spring 80 ensures the contact between the power adjustment devices 1 a , 1 b and 1 c and the drive plate 34 . A pawl bracket 83 cooperates with a coil spring 80 which is connected with its middle helix to the pawl bracket 83 by means of pins or standard fasteners (not shown). Since the pawl bracket 83 is attached to the middle coil of the coil spring 80, it rotates at half the speed of the drive disc 34 when the bearing disc 60 is not rotating. This can cause one or more locking pawls 81a, 81b and 81c to engage drive plate ratchet 82, wherein each locking pawl 81a, 81b and 81c is connected to the pawl bracket by means of one or more pins 84a, 84b and 84c 83 , the ratchet 82 is coaxial with the drive disc 34 and is rigidly connected to the drive disc 34 . The one or more locking pawls 84 a , 84 b , and 84 c are preferably spaced asymmetrically about the drive plate ratchet 82 . Once engaged, the resistively loaded coil spring 80 presses the drive disc 34 against the power regulating means 1a, 1b and 1c. Therefore, since the drive plate 34 is not in contact with the power regulating devices 1a, 1b, and 1c, the transmission 100 is in neutral and the ease of shifting is improved. Transmission 100 may also be shifted while operating.

When the transmission 100 resumes operation by turning the sprocket or pulley 38, one or more release pawls 85a, 85b, and 85c contact the opposing bearing plate ratchet 87, each of which releases the pawls 85a, 85b, and 85c. It is connected to one of the locking pawls 81a, 81b and 81c by means of a pawl pin 88a, 88b and 88c. The bearing plate ratchet 87 is coaxial with the bearing plate 60 and rigidly connected to the bearing plate 60 . Since the release pawls 85a, 85b and 85c are connected to the pawl bracket 83 via the locking pawls 81a, 81b and 81c, the bearing plate ratchet 87 actuates the release pawls 85a, 85b and 85c. In operation, release pawls 85a, 85b and 85c rotate at half the speed of bearing disc 60 because drive disc 34 does not rotate and disengage locking pawls 81a, 81b and 81c from drive disc ratchet 82 to allow coil spring 80 to The drive disc 34 is screwed against the power adjustment devices 1a, 1b and 1c. One or more pawl tensioners (not shown), one on each release pawl 85a, 85b and 85c, ensure that the locking pawls 81a, 81b and 81c are pressed against the drive disc ratchet 82 and secure The release pawls 85 a , 85 b and 85 c are pressed against the bearing plate ratchet 87 . The pawl tensioner is attached to pawl bracket 83 at one end and contacts release pawls 85a, 85b and 85c at the other end. An assembly hole 93 (not shown) through hubcap 67, bearing plate 6 and drive plate 34 allows an assembly pin (not shown) to be inserted into loaded coil spring 80 during assembly of transmission 100 . The assembly pin prevents the tension loss of the coil spring 80 and is taken out after the assembly of the transmission 100 is completed.

Referring to Figures 1, 11, 12 and 15, automatic shifting of transmission 100 is achieved by means of spindle cables 602, 604 and 606 which are connected at one end to a stationary transmission 100 component, such as a hollow shaft 10 or a fixed support 5a. The mandrel cables 602, 604 and 606 are then passed around the mandrel pulleys 630, 632 and 634, which are all coaxially positioned on the mandrels 3a, 3b and 3c. The mandrel cables 602, 604, and 606 also pass around spacer pulleys 636, 638, 640, 644, 646, and 648, which are each attached to a spacer extension 642 that can be rigidly attached to the spacer pieces 8a, 8b and 8c. As more clearly shown in FIGS. 11 and 12 , the other ends of the mandrel cables 602 , 604 and 606 are connected to a plurality of holes 620 , 622 and 624 in the non-rotating annular bearing race 816 . A plurality of weight cables 532 , 534 and 536 are connected at one end to a plurality of holes 610 , 612 and 614 in the rotating annular bearing race 806 . An annular bearing 808 is positioned between the rotating annular bearing race 806 and the non-rotating annular bearing race 816 such that they can move relative to each other.

Referring to FIG. 15 , a transmission 100 including cable routing for automatic shifting is shown.

As shown in Figures 1, 9, 11 and 12, the weight cables 532, 534, 536 also pass around the hub shell pulleys 654, 656 and 658, pass through holes in the hub shell 40, and enter the hollow spokes 504, 506 and 508 (most clearly seen in FIG. 12 ), in which are attached weights 526, 528 and 530. Weights 526, 528, and 530 are attached to and receive support from weight assist means 516, 518, and 520, which are attached at their opposite ends to a wheel 514 or other rotating body . As wheel 514 increases its rotational speed, weights 526 , 528 and 530 are pulled radially away from hub shell 40 , pulling rotating annular bearing race 806 and non-rotating annular bearing race 816 axially toward hubcap 67 . The non-rotating annular bearing race 816 pulls the spindle cables 602, 604, 606 which pull the spindle pulleys 630, 632 and 634 closer to the hollow shaft 10 and thus transform the transmission 100 into a relatively high gear. As the rotational speed of the wheels 514 decreases, one or more tension members 9 positioned inside the quill 100 and held in place by the cap 92 push the arbor pulleys 630, 632 and 634 away from the quill 10 and The transmission 100 is thus shifted into a lower gear.

Alternatively, or together with the tensioning member 9 , a plurality of tensioning members (not shown) may be connected to the spindles 3 a , 3 b and 3 c opposite the spindle pulleys 630 , 632 and 634 .

Still referring to FIG. 1 , transmission 100 may also be manually shifted to bypass or replace an automatic shift mechanism. A rotatable shifter 50 has an internal thread which is screwed onto an outer thread of a shifter screw 52 which is connected to the hollow shaft 10 . The shifting device 50 has a cover 53 with a hole which fits over the rod 11 which is inserted into the hollow shaft 10 . The rod 11 is threaded where it protrudes from the hollow shaft 10 so that the nuts 54 , 55 can be screwed onto the rod 11 . Nuts 54 , 55 are positioned on either side of cover 53 . A shift rod 56 is rigidly connected to the shifter 50 and provides a moment arm to the lever 11 . The shift cable 51 is connected to the shift lever 56 through slots 57a, 57b, 57c in the lever. Slots 57a, 57b, 57c on the plurality of rods provide speed variation and ease of shifting.

Referring now to Figures 1 and 10, the shift cable 51 is routed to a handle 300 and is coaxially wound thereon. When the handle 300 is turned in the first direction, the shifting device 50 axially winds or unwinds on the hollow shaft 10 and pushes the rod 11 into or out of the hollow shaft 10 . When the handle 300 is turned in the second direction, a shift spring 58 positioned coaxially on the shifter 50 returns the shifter 50 to its initial position. Each end of the shift spring 58 is connected to the shifter 50 and a stationary member, such as a frame (not shown).

As can be seen more clearly in FIG. 10, the handle 300 is positioned on a handle bar (not shown) or other rigid member. The handle 300 includes a turning handle 302 that includes a cable attachment 304 for connection of the shift cable 51 and a groove 306 that allows the shift cable 51 to be wrapped around the turning handle 302 . A flange 308 is also provided to prevent the user from interfering with the routing of the shift cable 51 . Handle ratchet teeth 310 are located on the rotating handle 302 at their interface with a rotating clamp 314 . When the turning handle 302 is turned in a first direction, the handle ratchet teeth 310 are locked to the opposite set of clamp ratchet teeth 312 . The clamp ratchet teeth 312 form a ring and are connected to a rotating clamp 314 which rotates with the rotating handle 302 when the handle ratchet teeth 310 and clamp ratchet teeth 312 are locked together. The force required to rotate the rotating clamp 314 can be adjusted with a set screw 316 or other fastener. When the turning handle 302 is turned in the second direction, the handle ratchet teeth 310 and the clamp ratchet teeth 312 are disengaged. Referring again to FIG. 1 , when the rotary handle 302 is rotated in the second direction, the tension of the shift spring 58 increases. A non-rotating clamp 318 and a non-rotating handle 320 prevent excessive axial movement of the handle 300 components.

Referring to Figures 13 and 14, another embodiment of a transmission 900 is disclosed. For brevity, only the differences between transmission 100 and transmission 900 are discussed.

In place of the rotating hub shell 40 is a stationary housing 901 and outer shell 902 which are joined together by one or more set screws 903 , 904 and 905 . Set screws 903 , 904 and 905 can be removed to provide access to the transmission 900 . Housing 901 and housing 902 have coplanar flanges 906, 907 with a plurality of bolt holes 908, 910, 912 and 914 for inserting a plurality of bolts 918, 920, 922 and 924 to secure the transmission 900 in place. Mounted to a stationary part such as a frame (not shown).

The spacer extension part 930 is compressed between the fixed housing 901 and the outer shell 902 with the fixing screws 903, 904 and 905, and extends toward the spacers 8a, 8b and 8c and is rigidly connected thereto. The spacer extension 930 prevents rotation of the fixed supports 5a, 5b. The fixed bearing 5 a does not have a fixed bearing sleeve 42 as in the transmission 100 . The fixed supports 5a, 5b hold the hollow shaft 10 in a fixed position. The hollow shaft 10 terminates at one end in the fixed support 5 a and at the other end in the screw 35 . Add an output driving disc 942 and support it on the housing 901 with a housing bearing 944 . The output drive plate 942 is connected to an output drive member, such as a drive shaft, gear, sprocket or pulley (not shown). Similarly, drive member 69 is connected to an input drive member, such as a motor, gear, sprocket or pulley.

Referring to FIG. 16 , shifting of the transmission 900 is accomplished with a single cable 946 that is wound through each of the spindle pulleys 630 , 632 and 634 . A single cable 946 is connected at one end to a non-moving part of the transmission 900, such as the hollow shaft 10 or the stationary support 5a. After passing around each of the mandrel pulleys 630 , 632 , and 634 and the spacer pulleys 636 , 644 , a single cable 946 exits the transmission 900 through a hole in the housing 902 . Alternatively, a rod (not shown) connected to one or more of the spindles 3a, 3b, 3c may be used instead of a single cable 946 to shift the transmission 900.

The foregoing description details certain embodiments of the invention. It should be understood, however, that no matter how detailed the above description herein may be, the present invention can be practiced in many ways. Also as noted above, it should be noted that the use of particular terminology in describing certain features or aspects of the invention should not be construed to mean that the terminology is redefined herein to be limited to include the terms of the invention to which the terminology is related. any specific characteristic of a feature or aspect. The scope of the invention should therefore be construed in accordance with the appended claims and any equivalents thereof.

Claims (20)

1. A roller traction drive, comprising: a rotatable drive member mounted on a shaft; power regulators in frictional contact with the drive member; a rotatable support member mounted on the shaft, the rotatable support member being axially movable along the shaft and in frictional contact with the power regulator; and A platform is located at one end of the support member and is adapted to move axially with the support member along the shaft. 2. A transmission as claimed in claim 1, wherein the drive member comprises a disc. 3. The transmission of claim 1, wherein the power regulator comprises spherical rollers. 4. The transmission of claim 1, wherein the support member includes a substantially cylindrical surface. 5. The transmission of claim 1, wherein the platform includes a raised surface. 6. The transmission of claim 1, further comprising a rotatable driven member mounted on the shaft, the rotatably driven member in frictional contact with the power regulator. 7. A transmission as claimed in claim 6, wherein the driven member comprises a disc. 8. The transmission of claim 7, further comprising a plurality of spindle supports slidingly engaging the raised surface, wherein at least one spindle support engages the spindle of the power regulator. 9. A roller traction drive comprising: a rotatable drive disc mounted on a shaft; power regulators in frictional contact with the drive plate; a rotatable driven disc mounted on the shaft, the rotatable driven disc in frictional contact with the power regulator; a rotatable support member mounted on the shaft, the rotatable support member being axially movable along the shaft and in frictional contact with the power regulator; and A first platform located at the first end of the support member and adapted to move axially with the support member along the shaft, wherein the first platform includes a raised surface. 10. The transmission of claim 9, further comprising a second platform located at the second end of the support member and adapted to move axially along the shaft with the support member, wherein the The second platform includes a raised surface. 11. A transmission as claimed in claim 10, wherein the shaft comprises a hollow shaft having a slot. 12. The transmission of claim 10, further comprising a sleeve slidably and coaxially disposed on the shaft. 13. The transmission of claim 12, further comprising a pin through the slot in contact with the sleeve, wherein The platform moves axially in response to axial movement of the sleeve and pin. 14. The transmission of claim 9, wherein each power regulator includes a central bore. 15. The transmission of claim 14, further comprising one mandrel for each hole. 16. The transmission of claim 15, further comprising two spindle supports for each spindle. 17. A transmission as claimed in claim 16, wherein each spindle support includes a wheel in sliding engagement with the raised surface. 18. A transmission according to claim 17, wherein each spindle support includes an aperture for receiving one end of the spindle. 19. The transmission of claim 18, further comprising at least one fixed support adapted to guide and support the spindle support. 20. The transmission of claim 19, wherein the fixed support includes a plurality of grooves.

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