DE2317467A1 - DRIVE MECHANISM WITH VARIABLE TRANSMISSION RATIO FOR BICYCLES - Google Patents

Description

Tokheim Corporation
Port Wayne, Indiana 46 Oil / USA

Variable gear ratio drive mechanism

for bicycles

The invention relates to a mechanism for changing the drive ratio between the crank and the rear wheel of a bicycle.A single drive chain is connected to the pedal sprocket so that any of a number of rear sprockets can be driven, which can be driven selectively by advancing toothed drive segments from their retracted positions effective positions are formed in which they can engage with the chain.

There are numerous mechanisms for changing the pedal to rear wheel ratio known from bicycles.

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In some cases, multiple sprockets and clutches are installed in the area of the crank and an appropriate number of chains and rear sprockets are required to allow the wheel to be driven. Other mechanisms involve various other devices. Change the speed to which are attached to the pedal hub, which the selected drive on the Ha ·! transmits via a single chain or axis of rotation. In no other cases similar Iecharisms are attached to or in the hub. In still other cases, some one-piece chain wheels are connected to the wheel hub and facilities provided so that the chain axially from a sprocket zn the other moved v / ground came · "In allan cases, the above-mentioned mechanisms are relatively obvious, large in size, Materxalmäöig more complex to manufacture and less operationally reliable in operation than the only transmission ratio that is normally used for the drive. These disadvantages usually become more pronounced as soon as the number of gear ratios provided is increased.

The purpose of the invention is to provide a translation system which is able to translate a relatively to provide a large number of gear ratios, but that is simple compared to the known systems.

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Another feature of the invention is that a system is provided which is based on the existing Bicycle frame is attached without changing the frame, with the exception of a few hand movements, which are required to attach additional parts, must be done and without the need for a special rear hub must be provided.

Another feature of the invention is to provide a mechanism which uses a disc comprising a plurality of toothed drive segments on a sprocket which is so attached are that they are between the withdrawn and the advanced or the operating position are shifted and which in concentric, annular Rows are arranged so that, when the segments of a row are advanced, the teeth thereof form a sprocket limit which is in the same plane as the tracks of the chain so that they are in engagement and are driven by it.

Yet another feature of the invention is that means for adjusting the gear ratio be created, which are movable relative to the surfaces of the disc, so that a drive segment is brought into position, which by a

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Cam in the case of a chosen ring-shaped Heine is advanced and a retracting cam in the path of the drive segments in line of a larger one Diameter ds the elected Jjurc urn see r in position is brought.

A still further Lerkmal of the invention is to scnaffen a Einricntung to select the gear ratio, welcne for the operator to actuate the Einricntung for adjusting the ubersetzungsvernältnisses is located in a convenient area.

Yet another feature of the invention is that To create a communicating device placed on the latch side of the chain to make a change of the beginning to compensate for the shifting the chain results in another sprocket.

Yet another feature of the invention is that a translation mechanism is created that compared with the known facilities nui "low Causes costs.

Yet another feature of the invention is to create a mechanism that is operationally reliable and is durable.

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The invention thus creates a drive mechanism in which the drive segments are arranged in annular rows which have different diameters and are concentric with the wheel axis. Each segment is mounted on one end of a non-rotatable bolt which is mounted in the disk so that it is pushed in and out parallel to the axis. A pair of Scüalthe legs. is pivotally attached at one end and has a long and a short arm which extends parallel to the opposite S ¹ u erien of the disc. A first cam is attached adjacent the end of the long arm so that it can sweep the free ends of the bolts from the inner to the outer row as soon as the lever moves through its limited range, while the shorter arm has a second cam, which is arranged along the length of the arm and which can move the drive segments from the next to the inner row to a position outside the outer row. When the first cam is in position in the track of a particular row of bolts, it causes the disc to rotate in the forward direction so that the drive segments of that row are advanced and form a corresponding sprocket, whereas the second causes the segments to flake of all larger diameter sprockets are withdrawn or remain withdrawn. Each

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vorgescnobene Antriebsse ^ Aeni engages in the chain shortly after it was vorgescxioben, so that: i the higher-setzungswech.se 1 wänrend one revolution ücaeiöe aer is completed. A one-way coup ^ lunt; is connected to the pulley so that the rear wheel hub is driven and the hub can rotate in relation to the pulley even when idling.

An additional device supporting the slack of the chain is built in on the slack side so that for changing the chain wheel diameter, the sag the chain is added. Can be regulated manually Translation-dial mechanism is handy for the driver attached and is connected to the control lever, which can be pivoted as described. Of the / Vähler is provided with facilities. which aie settings of the various gear ratios Show.

These and other features become one of these registration documents and the Drawings which are attached to these registration documents form part of it. In the drawings shows:

Fig. 1 is a view of an i'anrrades, which the improved Mechanism contains and in its

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üeccmtneit represented the Italian, the Pedalke ttcnrao, luenrere Ke ttenradiiiecii & nismen, iiecna- niv.ii.en for elections and changes of the translation ratio and a control for a chain slack shows.

i / ig. FIG. 2 is an enlarged view of the disk of FIG Slack control and the i.iechanismus to the iVecxicling the translation relationship.

Fi ^. 3 is a view of the mechanism for controlling the legal slope of the chain according to FIG. 2 seen by recnts.

if'ig. 4 is a section along the line IV-I ^ of the if'ig. 2, of the disc and the cage hub, the axle, bearings, a one-way drive ratchet for driving the wheel hub and drive train with Arms and cams for snapping.

Fig. 5 is a section along the line V-V of the i'ig.

Fig. Ό is a view of the sprocket disc, which aie the position and arrangement of the bolt openings and the drive segments in a stationary state.

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7 is an enlarged view of a sprocket drive segment.

"S ¹ Ig. Ö is a view of the mechanism according to FIG. Partially cut, viewed from the right according to this figure and illustrating the locking mechanism.

The Hauptre ^ irneii ctes Faiirrades designated in its entirety in Fig. 1 with 1 has an upper, a front and a lower tubular member. These glutes are numbered 3, and 7 in the order listed. The front ends of Figures 3 and 5 are attached to the bearing housings provided for the front fork (not shown). The rear end of Fig. 3 is attached to the limb 7 adjacent but spaced below it from the upper end of the limb, which protrudes upwardly behind the limb 3 to receive a seat post (also not shown). The lower ends of the links 5 and 7 converge and are attached to the have 11 in which the crank 13 is rotatably mounted.

upper and lower lower fork, which have parallel, spaced-apart arms 15, 15A and 17, 17A extend from the tips

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of the frame on which the links 3 and 7 or 5 and 7 run together, backwards and hunch down the rear axle 19 together. The arms 15A and 17Δ terminate in an axle support plate 21A (see Fig. 4) and are normally integrated into this, which has a slot 2 5A, which serves to accommodate the rear axle 19 of the rear wheel. The above construction will usually used in known forms of execution of this type, which have a similar axle support plate for the fork arms 15 and 17.

In the new embodiment, however, is around the Rear axle 19 an intermediate carrier plate 23 is arranged, which serves to support the intermediate arrangement (later in detail described) to wear and limit. Part of the intermediate support plate 2 3 is the locking device 2, which engages a slot 2 5 to serve as a further device, the intermediate support plate to prevent rotation about the center line of the wheel axle, according to FIGS. The location and the size the locking device 2 depends on the bike that is equipped with the transmission.

Δη of the intermediate support plate 2 3 is a pivot pin 29 attached, which sicn extends at right angles from this plate for the viewer of FIG. The umochalt

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The arrangement 31, which has U-shaped levers 35 and 37, is attached in such a way that it is articulated to the pivot pin 29 at both ends. The two levers 35 and 37, which extend rearwardly towards the rear axle, are substantially perpendicular to the rear axle. The 'file connecting the two levers 35 and 37 runs parallel to the central case of the rear axle. These arms are spaced from one another in a direction parallel with the rear axle and pivot pin to span a disc 39 which is concentric with the rear wheel axle. Each arm carries a driver, which will be described below. The switching arrangement 31 has a pin 40, which extends parallel to the rear wheel axis and through the slot 36 of the intermediate carrier plate 23 in the opposite direction to that of the Drenzappens 29, but essentially in a different plane, so that it can pivot about the pivot pin 29. The free end of the core wire 45 of a Bowden cable is attached to the eyelet of 4 ^ and is held by a spring ring 34 so that the Uraschaltanordnung 31 can be operated. The cable jacket 47 is attached to the intermediate support plate 23 via a nut, and the core wire fine adjustment is performed with the aid of Io . It can be seen that the cable is attached in this way

is, daii when the wire comes in or out of the cable jacket 47, the switching arrangement 3i i * ^{; i}

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uhrzeigercinn or counterclockwise about the pivot 2 ¹ J will pivot. On the pivot pin 29, a cylindrical helical torsion spring 47 is arranged in such a way that one end oü is mounted in an opening dl in the intermediate carrier plate 23 and that its other end ö2 is mounted in an opening d3 (not shown) of the arm 37, to the switching arrangement in an anti-clockwise direction (FIG. 2) to push the pivot pin 29. In addition, the cutter Ö4 according to FIG. 4 is connected to the end of the pivot pin 29 and thereby both arms (levers) 35 and 37 of the switching arrangement 31 are rotatably mounted about the pivot pin.

According to FIGS. 2 and 3, a pin 51 extends through the intermediate carrier plate 2 3 in such a way that it extends parallel with and in the same direction as the pivot pin 29. A chain tensioning and bearing mechanism, which is designated in its entirety by the numeral 52, has a fork-shaped lever 53 which is perforated for receiving the pin 51 so that the lever can pivot about it. A sprocket 59, which is held in its position by a snap ring 61, is rotatably mounted on the pin 51. The free end of the fork-shaped lever 53 carries an attached pin 65 which extends parallel to the pin 51 and in the direction thereof; on

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A sprocket 67 is rotatably attached to the pin 65 and is held in place by a snap ring β'-J . The pin 51 carries a helical spring 71, one of which is end 73 engages in a bore 75 in the intermediate support plate 23 and the other linden 72 engages in the existing lever 53 to turn it clockwise (FIG. 2). to push the pin 51. Dv. the chain wheels are all aligned with one another in one plane, this also applies to the flexible drive device, for example the chain 7'J, and for ax chain wheels, which are formed on the disk 3'9, which is described in detail below This mechanism has both, namely on the one hand it prevents excessive leeway when running the chain, which extends from the lower side of the crank oil to the chain wheel 67, and on the other hand it guides this part of the chain to the chain wheels formed on the disk 39. It is pointed out here that Fig. 2 is partially cut in order to expose all five effective diameters (A to E).

As can be seen in Figures 4 and 5, the rear axle 19 is replaceably fastened in the slots 25, 25a by means such as washers and nuts which have the threaded ends

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the locking axis are in engagement. jJie rear axle tragx ball bearing races ö ^r f _t UE9, the balls are braced welcne 91 which are in rolling engagement with the hub rings 93 "95th

The disc 39 is relatively thick along the center line of the rear axle with an inner end which extends inside the disc in the direction of the wheel hub 97 and the kingpin 9, which also serves to keep the ball joint 105 in contact in the ring 101 to hold. The other end of the disc holds the ring 103 for the balls 107, which are held in place by a third axle mounted on the ring 109. The disc is thus rotatably mounted on the rear axle for rotation with respect to the rear axle. The pulley is driven clockwise (i ^fl . 2 and 5) by the chain, as will be explained later, and will drive the wheel hub 97 and 90 by means of pawls 119 and 119A passing through parts 115 and 115A are pressed to the outside under tension and which are driven by the disk 39 and which in turn drive the lathe II3 which is attached to the wheel hub 97.

As can be seen in FIG. 4, the wheel hub ring is attached to an axial flange 111, which one

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has a greener inner diameter than the protruding end of the disk 39. An annular inner ratchet is attached within the flange 111 in such a way that it engages over the disk 39. This disk 39 has a circumferential slot 121, which is aligned radially with the slit 113, and a diametrically opposite slot 121a. These slots extend radially inward from the itsoden aer iiille which serve to receive the ends of the curved springs 115 and 115A and pawls 119 and 119A which are in driving engagement with the strands of the ratchet in the groove with internal free teeth. The pawls 119 and 119A spring radially outwards and backwards in their free position so that they can be installed. The drive ends of the pawls are in constant engagement with the eating screw 113 and will drive it as soon as the series i be rotates counterclockwise (Fiü · ö) I; ad continues to rotate so that the bike can keep moving. Slots 121 and 121A hold the pawls in precise alignment with the hatch.

Ur.i a number of Tretku.rbel- zu Hadnabenveraltnisse to be provided is the disk 39 rides a Liehrzanl of toothed drive sprocket segments I3I,

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which are integrally connected to the bolts 137. The bolts are mounted verrutschbar in the ticneibe for advancement and retraction to the drive bless to move te sv.ischen aen zurucicgezogenen and advanced positions in circular rows, so that, out collar when the Bolsen in different .lüstern!, The Uegnente sprockets of form different diameters.

As shown in Figures 7 and 7, each drive segment 131 has two teeth 133 and 133A which are spaced apart and shaped so that they effectively mesh with and within the adjacent rollers of the chain 79 Connection, it has been found in actual operation that the angle A of the teeth according to FIG. 7 must be smaller than that of the teeth of the sprockets which are normally used for the present application in order to prevent the chain from drifting out of the teeth. The tooth tips are rounded sphäroidiscn how the leading and nacnlaufenden parts 135 and 135A of the segment to the wear of squatting 153 (i'ig x 4) reduce ouer to prevent, which pushes back the segments.

The surface 139 of each bolt is provided with two locking devices axially spaced from one another.

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strand 141 and 143, which are attached so as to alternately pick up the bolt 145 as soon as the segment according to Fig. d has been snapped back (Ls, ge shown in a knitted line) or advanced (position shown in a solid line) . iier bolt 14.5 is fitted in the slot 147 in the 3ciBi.be i'rei movable back and forth from the plate 14 according to FIG. 4, is aagebraent to the pulley yj by screwing, in order to hold the bolt 14b and aie spring 149 in place.

In Fig. G is; a view of the disk 39 is shown. On this disc, four fences A are equidistant from attached to the center line of the rear axle 19 and each Arranged at equal angles (90 °) at the same distance from each other. The teeth 133 of the four drive segments are on the disk 39 by screws I37 attached, this sprocket enables the next Oversized event.

The middle line of the openings B of the chain wheel with the next lower transmission ratio are arranged at a greater distance from the center line of the axis than the lines in over no A. They are also at their middle line at a distance separated from each other by yö °. They are, however, at 45 ° from eggs

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radial center line, which runs through the no A, offset.

The openings G are also four in number and around from the radial center line passing through the openings U runs, offset. But they're on a bigger one Umf cingsicreis arranged as the openings Ü so that a correspondingly small crosslinking ratio results.

The openings Ii, also four at aer Zsiil, are separated by 10 ° from the radial center lines running through the openings B. They are, however, at a greater distance from the middle than the openings G. This results in a smaller transmission ratio in this case than with the chain wheel C. It can be seen that, although the angular distance (yO °) between the bolt centers different chain wheels, which were brushed above, was kept constant, the distance in circumference has increased with the diameter of the corresponding chain harvester until it has the length of the cantilevered chain between the adjacent segments to provide additional support for the chain during its engagement with the largest To achieve chain wheel ti , eight openings (45 ° apart) are in this chain wheel marked ü instead of the four in the No D.

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intended. The difference between de.:. JJurcLinescer of

Sprockets ß-A, CB and JJ-O ει approximately the same, whereas that of the chain wheels is larger, so the angular spacing of the bolts changes. According to this, two bolts, one on each cieite aei cadius, are arranged through the ax ACiice of each bolt and are arranged approximately across from each other. The sprocket l ·;, which is formed by the segments of these bolts, allows the lowest gear ratio available with the arrangement shown. It can be seen, however, that more or less translation relationships may be provided, without upper or lower limits, and that above the differences shown, the principles of translation can be created, ολιιθ the principles explained in the orange to leave.

Based on the i'ig. 2 and 4, the actuating arm 3> Gn on its inside, adjacent to the free end of the arm on a curved piece 149. The curve piece is a rod material which has a triangular cross-section and the crest 151 of the rod extends in the direction of the rear axle, while the bevelled sides of the curve piece run obliquely under the spell of the rounded i & iüeii of the bolts

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special iieiue of the segments arranged sina, '/. oak graze forward in effective positions should, so that they form a special chain wheel.

jjie dome or comb 151 aes curve piece is with a solciien distance from the adjoining flaciie of the Scneibe arranged that, as soon as each bolt passes the churned line of the curve piece, it follows far enough right moves wildly that the bolt 145 penetrate into the locking point 143 in the form of a recess (Fig. d) can. The segment is thus placed in the same plane as the chain at that point in time at which the Segment can engage in the chain to be driven thereby.

The surface of the arm 37, which is on the opposite surface of the disc 39, related to the actuating arm 35, adjacent, is provided with the wedge-shaped cam 153, which extends substantially over the whole Extends length of the arm and is fastened by screws 92. The thin part 155 of the roof-shaped Crouching is located adjacent to the upper edge of the arm, whereas the thick part is at the base. The greatest thickness of the cam is such that each Segment I3I »which in the joint between the crouching and

the upper side of the disk (Fig. 4) penetrates, far enough nacii left can be printed so that the bolt

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can penetrate into the locking point I4I (Fig. 6), which complete the retraction of the segment seeks. If the switch arm 3I is used to change the Gear ratio assumes its position for third gear (Fig. 2). is the cam 153 in retracted Position arranged transversely to the path of the segments that form the outer two sprockets, that is across the annular grooves containing bolts E and D as cam 149 moves into the Path of the bolt in the No C. extends. It is thus established that the segments of the C, B and A bolts will take their operative position; these are the advanced positions, while all the others are theirs will occupy withdrawn positions. Since the Heihe A is never withdrawn, it is possible for the chain wheel A standardized sprocket can be used instead of the segmented sprocket if this is desirable.

When the shift lever assumes its position E, the cam 149 is set so that it advances the bolts of the hehe ü, whereas the cam 153 moves unloaded out of the depth of the segments E and all other segments are in their advanced positions after a whole Rotation of the pulley as soon as all drive segments have been brought into position.

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As stated above, "the arm of the switching arrangement 3I is operated by the Bowden cable. The the other end of the protective jacket 47 of the cable is on any conventional remote adjustment device of the gear ratio attached, for example to a switch handle 161, which has five switching positions having, wherein a lock is provided for each switching position. One built into the handlebar The control handle has proven to be the most effective device for operating the Bowden cable.

In the following, the functioning of the inventive Facility described in more detail. Assuming the bicycle has been set to fifth gear, then the actuating device comprising the switching arrangement 31 is furthest away from it in the counterclockwise direction Take up the position as shown in FIG. The toothed segments of A or the innermost row become the be the only segments present in the advanced or operative positions. Sieve limits the sprocket with the little Durciiraesser. All other Segments have been withdrawn by the cam 153 and remain in this withdrawn due to the cam Position. The rear wheel is therefore oil several rotary movements for each rotary movement of the sprocket run and this is the largest gear ratio available.

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Assume that the toggle selector is turned while riding the bicycle 161, which is part of the remote control device, is turned into position B. Such a process solves a clockwise movement of the reversing assembly 31 about the pivot pin 29 to the cam 149 for one Engaging with the bolt of number B into engagement so that the segments of B are in their operative. Positions be advanced so that they can form the second largest sprocket. As soon as each drive segment is advanced it is rotated into engagement with the slack side of the chain and the tension lever rotates counterclockwise around the pin 51 »so that the Chain can yield sufficiently to adapt to the enlarged circumference of the sprocket. It will care pointed out that the open tree between the chain sections in a clockwise rotating sprocket is provided between the point where the drive segments are advanced and the chain engagement point, which enables engagement with a slack side of the chain rather than engagement with its tensioned side Part. The cam 149 has no function at this point unless a number G, D, or A bolt has become somehow moved from its withdrawn position. In this case the cam will move them back to their retracted position.

The same function ε processes occur :: eYixi der, -, - c

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is turned so that the sprockets C, D and E mesh reach. For example, the chain wheel E sees the smallest transmission ratio from the pedal crank the rear wheel drive in front. Even when the sprocket E is fully in use, all segments take theirs advanced positions, provided the had has at least one turn between the following Switching operations carried out.

When the switch selector gradually moves to position B, C, D or E is brought, the cam 149 will take no puncture until a segment in its path the cam is in position, moved towards its retracted position, or during was not advanced to an earlier switching process. In the first step, the cam 153 becomes the segments of the sprocket with the number E so that the following teeth of the sprocket with the number D mesh with the chain. The lever 53 will rotate clockwise to accommodate each resulting Can absorb slack in the chain. The same process occurs with every additional step, until the parts have taken the initially highest translation position again, in which all segments, except those of the sprocket A, are withdrawn.

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The rotation of the gear selector from the low to the high gear position while the vehicle is in motion is essentially continuous and uninterrupted. Should the free end of one of the arms 35 or 37 touch a bolt or a segment in such a way that the rotation of the switching arrangement 31 cannot continue for a short time, then the core wire 45, which has a relatively long lung, bends behind the lower rim of the Cable jacket 47 extends so that the lever continues its movement in the direction of the desired setting as soon as the resistance is increased. During a reverse movement of the counter, such a radial contact between the loose 149 and a flat side of a bolt briefly interrupts the switching of the switching arrangement 31.

It should be noted that: i during a fast Switching process through different translation levels from a honing to a low gear ratio not all bolts of the sprockets, which ubasetzuiags between the initial and the desired must be actuated. From Figure 6 it can be seen, for example, that the switching process is initiated by moving the cam 149 outward from the bolt A, softer at the upper vertical Center line is arranged} he touches the bolt ^,

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which is immediately to the right of it, with bolt C lagging behind bolt B and bolt D again lags behind the bolt C, etc., so that a complete or entire chain wheel is created only in the row, in which the cam comes to rest. The chain thus rises to the desired lever in one Spiral up. Similarly, it increases rapidly when switching in the opposite direction again 'off. The lever 53 prevents or promotes sagging of the chain, provided that it is required by the sprocket-like devices that by the cams can be set up.

Again based on the intermediate support plate 2 3f it should be noted that the movement of the plate is a pivoting movement about the pivot pin 29. One such Pivoting movement is desirable for various reasons, for example when it is a with is a movement comparable to a sliding movement. Above all, the pivoting movement is independent from any other adjacent surfaces. It is also less prone to failure due to dirt or other Foreign matter or an influence, for example reveal, between two adjacent surfaces.

Are at the erfindungEgemcliien Einrichtimg at a BEWE ^ _t unf_: contacting surfaces low.

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Furthermore, they can easily be sealed. Something like that is not possible in an arrangement with a sliding movement process.

Now referring to the structure of teeth I33 and 133A, it should be noted that the configuration of the teeth according to Pig. 7 different extremely desirable ones Features brings with it. A number of I3I drive segments - this is more desirable than just one Drive system - increases contact with the chain 79 and distributes the load on that chain more evenly on her than a single tooth does. In addition, a certain number of drive segments 131 are therefore required. It will also point out pointed out that the drive segments I3I include a projection 135 adjacent to the tooth 133. The projection 135 forms a curse for the iräger Chain 79 so that the chain can be reduced from falling out of its desired position from de.-xi tooth I3I ve can and thus the load between the tooth I3I and the tooth I33A is distributed, just as a greater resistance with respect to the versciileiioes is achieved thereby will. Thus, the structure o.er drive components ljl

a iaechanisnus, richer gleicriiri ^ ii- and effectively distributes the burden of the chain, without ae.j> the chain ausd di r'a ^ rer des ι-'ε.ιαώθΐι _& 63 eir.o

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steady and pleasant experience.

While a particular embodiment of the invention illustrated and written down for the purpose of the illustrations it is desirable that the protection afforded by any patent which is based on this application is granted, is not limited; but it is to be extended to all structures and arrangements, which contain the essence of the invention and which fall entirely within the scope of the claims which are listed below.

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Claims (1)

Patent claims: 1. ij translation mechanism with changeable transmission ratio, which cooperates with a drive device and a translation element with a variable Having diameter, characterized in that; i a) a plurality of drive segments is provided, which cooperate with a flexible .antriebseinrichtung, wherein the drive segments on the transmission link with the changeable diameter for movement between an axially retracted and an axially advanced position are attached so that: i a plurality of changeable effective jury knives is adjustable and. b) an actuating device is provided which is arranged pivotably movable in the path of the drive segments and is operated so that the Drive segments are forward and retractable and the desired effective diameter is adjustable. 2. translation mechanism according to claim 1, characterized in that the translation member with variable diameter ve ine Scneibe and since: 3 each drive segment has a bolt which is slidable in the - 29 409817/0277 2317A67 Washer for a reciprocating motion parallel to the Disc axis is arranged and that this bolt has a length which is greater than the thickness this disc and at one end a toothed segment, so that the bolt between its advanced Position, with the toothed segment lying in a plane defined by the flexible drive device is limited, and is movable to its retracted position, the toothed segment in a plane lies outside the path of the flexible drive device. 3. translation mechanism according to claim 2, characterized in that that the drive segments are arranged on the disc in a number of annular rows are that have different diameters, so that the toothed segments of the outermost advanced Position are in engagement with the flexible drive device. 4. Translation mechanism according to claim 2, characterized characterized in that a locking or release device in the disk for cooperation with your bolt is provided, which releasably secures the bolt against back and forth movement when the iiolzen ce ine \ / or retracted position aüimiü t. - 30 - 409817/0277 5. Translation mechanism according to claim 2, characterized by that a jintriebsexnrichtung with an axle and a clutch are provided, which through. the disc is rotatable and is provided for driving the axle when the disc is in its predetermined position Direction is driven by the flexible drive device. 6. transmission mechanism according to claim 2, characterized in that the toothed segments for cooperation are provided with the flexible drive means with a plurality of teeth and that adjacent a projection for supporting the flexible drive device is provided on the teeth. 7. translation mechanism according to claim 6, characterized in that that the edges and corners of the toothed segments that outline the outer edge are rounded are. O. Translationalism according to Claim 1, characterized in that that the actuating device has: a) a device for retracting a drive segment, which for a pivotable movement between Scan a first limit position that is outside the extreme ring shape of the drive segments 409817/0277 -U- close order, and a second border control, which is arranged in the path of the next to the innermost hole, so that it is in the path of the advanced drive segments of each row except the innermost one to retract the drive segments be brought into position when the disc is rotated, b) an actuator for moving the Drive segment that is between a first limit position, which lies in the bay of the outermost height of the advanced drive segments, and one second limit position, which is in the path of the innermost fieihe is pivotally mounted to track any row of the drive segments is brought into position for advancing the corresponding drive segments when the Disc is rotated, and c) a Zusaminensclialteinrichtung between the Means for retraction and the ejection means for simultaneous movement between their respective first and their second limit position is arranged, so that the special effective diameter through the drive segments is limited, can be selected and so is the selected transmission ratio of the transmission mechanism 7 _ ₃₂ _ 9. Translation mechanism according to claim ö, characterized characterized in that the actuating device is pivotable in aen open barely between the chain sections is inserted. 10. translation mechanism according to claim 6, characterized in that aass the device for retracting the drive segment has an elongated cam, which is arranged in such a way that it gradually enters the orbits of the ring-shaped ones of the toothed ones Segments penetrates and remains there as soon as the device for withdrawing the drive segment pivoted from the first to the second limit position is that the cam has a surface which is inclined with respect to the adjacent surface of the disc is so that when the disc is driven by the flexible drive means, the drive segments of the legs crossed by the cam will be pressed into their retracted position once they are across the surface of the cam move. 11. translation mechanism according to claim 6, characterized in that da.d the actuating device for advancing the drive segment has a cam, the one such lung along the bar on his way to work between its borderline positions has that 409817/0277 ³³ 2 31 7 Λ 6 7 it can be pivoted out of the path of a 'row of' bolts is, before it penetrates into that orbit of an adjacent Heine, that the cam has a surface, which is inclined with respect to the adjacent surface of the disc is so that when the disc is rotated, the ends of the pin of the in the drive segment, which in a row is arranged, which crossed by the skirt is engaged with the surface of the cam arrive and is thereby pivoted in the direction of the disk by a sufficient distance, so that the drive segments are brought into their advanced positions as soon as the bolts are the Cross cams. 12. translation mechanism according to claim ö, characterized characterized in that the means for interconnection further has: ^a ) a first lever attached to the device for retracting the drive segment, b) a second on the actuating device for Advancing the drive segment attached lever, each end of the first and second Lever around an axis running parallel to the disk axis Pivot axis is hinged yielding, de ..; aie lever in the direction of the pivot axis ij. χιbc land are arranged from each other, so ä & .i they 409817/0277 - 34 - which by means of the first lever parallel away from the entire Sement side of the disc and "the second lever parallel in dist & nc. extend from the bolt side of the pulley, c) a device for connecting the z: l.ockens to retract the drive segment on the first lever so that the cam extends along the inside of the nebeIs, and d) a facility; for connecting the actuation ξ-cam to advance the drive segment the inside of the second lever, so that the Squatting on a matching Uaiui at the same time can be moved as soon as ax Lever can be pivoted. 13.Translation mechanism according to claim 1, characterized in that da3 a device for precisely moving the device to the assembly: imensciialten in the desired Position under the spell of the chosen keixia;.: Eseiieii is. 14. seaianism of translation nacxi ünsprucn Il, dadurcn marked, da: i add a suitable facility accumulate is provided in engagement with the - 35 A09817 / 0277 lie ine of the flexible drive device is to Accumulate and spend in accordance with the Decrease or increase in the effective circumferential diameter of the translation mechanism with changeable translation * relationship. Translation meciianism according to claim 14, characterized in that characterized in that the yielding device has for accumulation: a) an arm, the upper end of which can be pivoted about a fixed axis that runs parallel to the disk axis, is appropriate b) an axle attached to the lower end of the arm and parallel to the disc axis extends, c) a first sprocket which is rotatably mounted with respect to the fixed axis, d) a second sprocket mounted on the axle, the first and second sprockets im are arranged essentially in the plane of the flexible drive mechanism, which is below the second sprocket, between aem second and the - 36 409817/0277 - 26 - first sprocket, running over the first sprocket and then to the translation meclianism with variable gear ratio reached, and d) a compliant device for pivoting the lever in a liichtung so that the second lever of the variable ratio transmission mechanism is moved away so that the flexible drive device is under tension. 16. Translation mechanism according to claim 1, characterized in that that it further comprises a bicycle having a frame, front and rear wheels, the are rotatably mounted in the liah that it comprises a translation system, which a front Sprocket assembly, which can be rotated around a 'Uretkurbe 1-axis is attached, and a rear sprocket assembly for driving the rear wheel, the front or rear sprocket assembly having variable diameter transmission link, as well as the Disc with the drive segments, which are used to effectively change the diameter of the transmission link in Can be brought into position, the drive segments, those for engagement with the flexible drive mechanism, The flexible drive mechanism can be operated which the front and the rear Zettenraclanor-unung connects, an actuation device with a 409817/0277 _, ₇ _ Setup for remote setting of the gear ratio for swiveling adjustment of the operating device into the path of the drive segments, causing a change in the effective diameter of the translation member with the variable diameter takes place, a device welcne the remote control device operable with the actuation device connects, and an accumulation device for the resiliently pretensioned flexible drive having. 17 · Transmission mechanism according to claim 16, characterized in that aaij the facility for remote setting of the gear ratio is attached to the frame and has a selector member which is for movement from one to another of a number of predetermined positions, the one The same number of predetermined effective diameters are assigned. Ιό. Translation mechanism according to claim 16, characterized marked that the translation element with changeable Diameter for rotation about an axis is mounted on the rear sprocket assembly. 409817/0277 19. Translation mecnanisinus according to. Claim 16, characterized in, there: i as the transmission link with variable diameter for a rotation about an axis on the front Chain rake is attached. 20. translation mechanism with variable transmission ratio, characterized by the fact that it is far aen Engagement with a flexible drive mechanism. a Transmission link with a variable diameter uaifaiöt and has ;: a) a number of drive segments that fit effective engagement with the flexible drive mechanism are suitable, with the drive segments on the variable diameter transmission member for movement between an axially retracted position and an axially advanced position Position are fixed so that; i created a teaching number of effective variable diameters is, whereby the drive integr.ente one multiple teeth for engagement: iit the flexible .drive device and form a projection, which is adjacent to the Zaxine and to support the flexible drive mechanism is used, and - 33 409817/0277 id b) an actuating device for the operational Pushing the drive segments back and forth to set the desired effective diameter. 409817/0277