WO2014072344A1

WO2014072344A1 - Hub transmission for a bicycle

Info

Publication number: WO2014072344A1
Application number: PCT/EP2013/073170
Authority: WO
Inventors: Franz Kurth; Andreas Ziegler; Markus BAAR; Stefan SCHURER
Original assignee: Technische Universität München
Priority date: 2012-11-06
Filing date: 2013-11-06
Publication date: 2014-05-15

Abstract

The invention relates to a hub transmission (1) for a bicycle having a plurality of planetary gear units (3, 5, 7, 9, 11) arranged on a central shaft (13) that are coupled to one another. The hub transmission (1) comprises one or more complete planetary gear units (3, 5, 11), each of which comprises a sun gear (37, 41, 57), a set of planet gears (35, 39, 59) and a ring gear (31, 45, 63) and/or one or more extended planetary gear units (7, 9). An extended planetary gear unit comprises a first and a second sun gear (53, 55), a set of stepped planet gears (47), each having a first (43) and a second (49) planet gear section, wherein the first planet gear section (43) meshes with the first sun gear (53) and the second planet gear section (49) meshes with the second sun gear (55). The hub transmission (1) additionally includes a plurality of shifting means (15, 17, 19, 21) for reversibly locking and/or arresting individual planet gear units. One shifting means (15, 17, 19, 21) and one free-wheel (23, 25, 27, 29) are provided for each complete planetary gear unit (3, 5, 11) and for each extended gear unit (7, 9).

Description

Hub gear for a bicycle

The invention relates to a hub gear for a bicycle, comprising a number of arranged on a central axis, coupled planetary gears, and a number of arranged on the central axis switching means for reversibly locking and / or inhibiting individual planetary gear components.

Hub gears are used in bicycles and especially in trekking and city bicycles. They are installed inside the rear hub of a bicycle and consist in the simplest case of a planetary gear, whereby a 3-speed gearbox can be implemented. With more than three gears, several planetary gears are combined in a hub gear.

An advantage of hub gears over conventional derailleurs lies in their encapsulated construction. In this way, in particular their protection against dirt and moisture can be ensured with sufficient lubrication of the gear units. The wear of a hub gear is correspondingly low. In addition, the wear is also reduced by the simple executed primary ratio, since in hub gears only one chainring paired with a pinion is used. This results in a constant chain line regardless of the gear engaged. Furthermore, hub gears are switchable both when stationary and under load, so that you can easily change, for example, for starting easier routes. The actuation of a hub gear via only one handlebar mounted rotary handle.

In order to meet the ever increasing demands on modern bicycle hub gears, these are being continuously developed. Here, especially the ride comfort is put in the foreground. This is characterized for example by a high number of gears and high transmission spread as well as a comfortable gear and a low gearbox weight. _.

From DE 43 42 347 Cl, for example, a hub gear is known, which realizes twelve gears by the coupling or the combination of two planetary gears. In this case, the planetary gear in each case two multi-stage planetary gears, which are coupled together via a common planet carrier. The planet gears mesh with sun gears, which are arranged around a central axis. The sun gears can be connected to the central axis via freewheels acting in one direction of rotation, with the freewheels being controlled in such a way that different gear ratios can be implemented within the hub gear. The gear spread of the approximately 3.5 kg hub gear is 3.39. Such a hub gear is sold under the name "Elanl2" by the manufacturer Fichtel and Sachs.

Furthermore, from EP 2 017 175 A1 an 11-speed hub gear is known, which is based on the coupling of four planetary gears. The planetary gears are arranged one behind the other on a central axis. To illustrate the translations, two of the four planetary gears are made here with stepped planetary gears. In addition, switching means in the form of clutches are arranged on the central axis in order to achieve the required ratio. The gear spread is about 4.09. Such a hub gear is known as "Shimano Alvine 11-speed hub gearshift" manufacturer Shimano.

EP 0 910 530 (WO 98/52817) discloses a hub gear for a bicycle which realizes fourteen gears by the combination of three planetary gears each having a stepped double planetary gear. For this purpose, two of the planet wheels are coupled to one another via a common planet carrier and are arranged in mirror image relative to a plane of symmetry perpendicular to the central axis. The third planetary gear is connected via a ring gear-sun gear coupling with the first two planetary gears. In order to achieve the desired translations, a number of switching devices designed as switching clutches is furthermore included, by means of which the sun gears of the individual planetary gears can optionally be connected in a rotationally fixed manner to the central axis. The hub gear according to EP 0 910 530 has a gear spread of 5.26 and a gearbox weight of about 1.7 kg and is marketed under the name "Rohloff Speed Hub 500/14" of the manufacturer Rohloff. Although all the above-described hub gears have in common that they combine the advantage of a straight chain run with the dirt immunity of a sealed gearbox. However, the hub gears reach their limits, in particular with regard to the number of gears that can be realized. Especially higher gears, which are desirable, for example, when driving downhill, are missing so far. In addition, the incremental steps in the gear change partly deviate significantly from the area perceived as pleasant for cyclists.

It is therefore an object of the invention to provide a hub gear for a bicycle, which allows improved ride comfort while maintaining the highest possible number of gears.

This object is achieved by a hub circuit according to claims 1 and 19. Advantageous developments are specified in the dependent claims.

In one aspect, the invention includes a hub gear for a bicycle having a number of planetary gears coupled to one another on a central axis. These planetary gears include one or more "complete planetary gears" and / or one or more "extended planetary gears". As will be explained in more detail below, the term "complete planetary gear" in the present disclosure means a planetary gear that includes a sun gear, a set of planetary gears and a ring gear, and an "extended planetary gear" a gearbox with two sun gears, a ring gear and a set stepped planetary gears whose stepped portions mesh with one sun gear each. The hub circuit further comprises a number of switching means for reversibly locking and / or inhibiting individual planetary gear components, wherein a switching means and a freewheel are provided for each complete planetary gear and for each extended planetary gear. Of course, a second switching means may be provided instead of the freewheel, provided that this assumes the function of a freewheel in the context of the shift pattern of the hub gear, d. H. would be replaceable by a freewheel.

If only one switching means is provided for each complete or extended planetary gear, each complete or extended planetary gear can be equipped with two , Achieve states. For example, in four consecutively connected complete or extended planetary gears 16 gears can thus be realized with only four switching means. In contrast, for example, requires the hub gear from DE 107 20 796 AI seven clutches for the realization of 14 gears.

Note that with the approach chosen here in the planetary gearboxes inherently existing translations can be unused, since a complete planetary gear provides, for example, three different translations, but in practice at least two switching means would be needed. In view of the limited installation space and the weight to be reduced, it may at first glance seem to contradict the intuition of leaving existing translations unused. The inventors have found, however, that the limitation to two switching states for each full or extended planetary gear opens up further degrees of freedom in the design of the hub gear, allowing for a comparatively large number of gears, a very even distribution of gear ratios and a larger gear spread reach, as has been achieved in the prior art. Moreover, it is even possible to use a comparatively large number of identical parts in the different complete or extended planetary gears, which reduces the manufacturing cost.

The object of the invention is further achieved by a hub gear for a bicycle, comprising a number of arranged on a central axis, coupled planetary gears, and a number of arranged on the central axis switching means for reversibly locking and / or inhibiting individual planetary gear components. The planetary gears are in this case coupled together such that the ratio of the ratio of the lowest gear to the translation of the highest gear is more than 5.40.

The invention recognizes that a high gear spread can be made possible by the mechanical coupling of planetary gears. A ratio between the lowest gear and the highest gear, which is in the range above 5.40, enables comfortable driving on steep inclines as well as high speeds. _.

The translation of a transmission basically describes the relationship between the output speed and the input speed. The translation in bicycle hub gears results from the ratio of the number of teeth and diameter of the coupled planetary gear. A high or long gear ratio is particularly suitable here for achieving a high final speed, whereas a small or short gear ratio is suitable for driving in rough terrain or on steep climbs.

In the technical literature, it is customary for this purpose to specify the transmission spread, ie the ratio of the ratio of the lowest gear to the gear ratio of the highest gear, in%. The percentage indication of the gear spread designates the translation of the highest gear as a percentage of the translation of the lowest gear.

The desired gear spread, ie the gear ratio between the highest and the lowest gear, is achieved by the coupling of several planetary gear or individual planetary gear components. As a compact gear transmission, a planetary gearing makes it possible to achieve a high power density in relation to other types of gearing and high torque transmission in the smallest possible space. At the same time a planetary gear meets the requirements for the lowest possible construction or transmission weight. Here, the planetary gear may be formed depending on the required transmission or reduction ratio with one or more planetary gear, so that the desired number of gears can be achieved.

A simple form of a planetary gear comprises, as planetary gear components, a sun gear, a planetary gear set arranged on a planet carrier and having a number of planet gears and / or a ring gear. The sun gear is in this case positively connected via the planet gears with the internally toothed ring gear, wherein the planetary gears can be arranged by the internal toothing of the ring gear compact and space-saving. The planetary gears are preferably arranged on a planet carrier, wherein they may be arranged, for example, in a plane adjacent to the inner periphery of the ring gear or on an axis as stepped planets. _

In the present description, "planetary gearboxes" are any coupling of a set of planetary gears with a sun gear, to distinguish them as a "complete planetary gearbox", which in addition to a sun gear and a planetary gear set also comprises a ring gear. Finally, the term "extended planetary gear" in the present disclosure means a transmission comprising two sun gears, a ring gear and a set of stepped planetary gears each having first and second planetary gear portions of different diameters rotatably connected to each other and of which the first planetary gear portion is meshed with the first sun gear and the second planetary gear portion is meshed with the second sun gear, as will become apparent below with reference to two of an exemplary embodiment.

The planetary gears are arranged in particular on a central axis, which may be formed as a hollow axle or hollow shaft. The central axis is mounted in the installed state within a hub expediently both drive and driven side. On the central axis, the planetary gear are preferably arranged axially adjacent. In particular, a shaft for actuating the switching means used in the hub gear is positioned in the central axis. The switching means can be actuated by a movement of this shaft and thus enable the insertion of various gears by blocking and / or inhibiting individual planetary gear components. The switching means can be designed, for example, as a clutch or as a brake, depending on the requirement.

The hub gear itself is arranged in the installed state within a hub shell of the bicycle hub. The hub shell protects the gear from dirt and moisture and also ensures permanent lubrication of the planetary gear components. In addition to the planetary gearboxes, further units such as a coaster brake, a hub dynamo or the like can be integrated into the hub shell with little design effort. This offers on the one hand the advantage of reducing the number of components on the bike, on the other hand, these are protected just like the mechanics of the transmission by the encapsulation of water and dirt.

In an advantageous embodiment of the invention are planetary gear sets as planetary gear components, of which at least two are formed with identical parts. , ,

In particular, the planet gears of at least two planetary gear sets are therefore designed as identical parts with the same circumferential toothing. The planet carrier can also be designed as a common part. By a high degree of identical parts, ie a plurality of identical components, the production costs for a hub circuit can be reduced and costs can be saved. In this way, with the least possible number of planetary gear components improved ride comfort can be implemented with the highest possible number of gears at the same time.

Preferably, as planetary gear components, ring gears are included, which are at least partially formed as identical parts with the same circumferential toothing. As with the planetary gears designed as identical parts, a cost-effective provision of a planetary gear can be made possible by identical configuration of the ring gears. Preferably, planetary gear components include sun gears that are at least partially formed as identical parts with the same circumferential toothing. Thus, a material-saving and cost-effective design of the hub gear is also implemented. Overall, the hub gear is simplified by a variety of common parts in planetary gear sets, ring gears and sun gears in terms of their basic buildability and complexity compared to previously common circuits and offers improved ride comfort with at least constant and especially increased number of gears. Thus, by coupling the respective planetary gear in addition to a 14-speed hub gear with a gear spread of about 5.45 in particular a 16-speed hub gear with a gear spread of about 6.39 can be provided.

The number of identical parts of the Planetenradkomponen- used in the hub gear is hereby not limited to only two equal parts, but can be suitably adapted to the overall design of the hub gear.

Preferably, the planet gears of two or more planetary gears are coupled together. By such a coupling, for example, via a common - -

Planet carrier, a common ring gear or a common sun can be done in a small space with a few parts high translation can be achieved with a high mechanical stability at the same time. Particularly preferably, two or more of the planetary gear are coupled via planet gears designed as stepped planetary gears. A stepped planetary gear is characterized in particular by the possibility of translation change with little radial space. In principle, a stepped planetary gear can be manufactured from a plurality of partial wheels with different toothings and / or diameters. The partial gears of a stepped planetary gear can in this case, for example, rotatably connected to each other be arranged on an axis. Alternatively, the stepped planet can also be made in one piece. The number of subplanes is dependent on the arrangement within the planetary gear. Thus, the planet gears may be formed, for example, as so-called stepped double planet wheels or as multi-stepped planetary gears.

In a preferred embodiment of the invention, two or more of the planetary gear are coupled via a common planet carrier, whereby the total weight of the resulting hub circuit can be kept low. The planet gears of each to be coupled together planetary gear are arranged on a common planet carrier, so that the rotational speed of a planetary gear is transmitted via the planet carrier directly to an adjacent planetary gear.

In a further advantageous embodiment of the invention, two or more of the planetary gear are coupled via a common ring gear. The coupling is done Werbei on the planetary gear sets of several planetary gear. Planet wheels of adjacent planetary gears mesh with the same ring gear. Such a configuration, the number of components within the hub circuit and thus the material and manufacturing costs as well as the assembly costs can be reduced. The ring gear can be formed over its axial width with a uniform continuous circumferential toothing. Alternatively, however, the ring gear can also have a divided over its axial width peripheral teeth. Here, the planetary gears used in each case mesh with one of the differing part gears of the ring gear. - -

Further advantageously, two or more of the planetary gear are coupled via a common sun gear. The coupling can for example be such that a planetary gear meshes with two or more sun gears of adjacent planetary gear. Even with such a configuration only a small radial space is needed. The sun gear may also have a divided peripheral toothing over its axial width, wherein the peripheral toothings meshing with the sun gear are in each case in engagement with one of the partial toothings of the sun gear. Overall, the use of stepped planet gears and common planet carriers, sun gears and / or ring gears leads to savings in manufacturing as well as a simplified assembly. The weight and the required space for the hub gears can be kept low. Preferably, the coupled planetary gear are driven on the drive side via a ring gear. The pedaling power introduced by the driver during driving is thus coupled into the first planetary gear via the ring gear and from there overhanging beyond the further planetary gears up to the output side. The output-side decoupling preferably takes place via a planet carrier.

In a further advantageous embodiment, the or each switching means is designed as a clutch or as a brake. By the switching means the insertion of desired gears is possible. Here, the number and type of switching means, which are necessary to realize the individual gears, for the construction and production costs of great importance. By means of the switching means, each of the components of a planetary gear shiftable from the central axis are blocked, coupled, coupled and / or braked and unlocked accordingly, decoupled, decoupled and / or dissolved. Conveniently, a number of freewheels are included, over which a number of planetary gear components is coupled to the central axis. By a specific coupling on the freewheels different translations in the hub gear can be realized because the planetary gear components can alternately free from the central axis. _ _{1 Q} _ 73170

Preferably, the coupling of the planetary gear is designed such that the gear jumps between two adjacent courses are possible in the entire transmission in a range between 12% and 15%. A gear jump indicates how the gear ratio between two adjacent gears changes. A gear jump is given by the percentage increase in gear ratio when changing from a higher gear to the adjacent lower gear. By a uniform sequence of gears or by uniform gear jumps over the entire gear sequence of a hub gear the driver is given a comfortable driving experience. In the following, embodiments of the invention will be explained in more detail with reference to a drawing. It shows a schematic structure of a 14-speed hub gear for a bicycle with five planetary gears,

2 shows a tabular listing of the numbers of teeth of the respective circumferential toothings of the planetary gear components of the 14-gear hub gear according to FIG.

3 is a circuit diagram for the 14-speed hub gear according to FIGS. 1 and 2, FIG. 4 is a schematic structure of a 16-speed hub gear for a bicycle with six planetary gears,

5 shows a tabular listing of the numbers of teeth of the respective circumferential toothings of the planetary gear components of the 16-gear hub gear according to FIG

6 is a circuit diagram for the 16-speed hub circuit according to FIGS. 4 and 5.

Fig. 1 shows the schematic structure of a 14-speed hub gear 1 for a bicycle. The hub gear 1 achieved by the coupling of five planetary gears 3, 5, 7, 9, 1 1 at 14 gears a total spread (ratio of the ratio of the lowest gear to the translation of the highest gear) of 5.45. The total spread of 5.45 results from the ratio of the translation of the 1st gear to the translation of the 14th. _ _

Corridor. Between the first gear and the 14th gear, the gear jumps, ie the respective ratio of the gear ratio of one gear to the next gear, are evenly in the range between 12% and 15%. The two additionally designated in Table 81 gears 0 and 15 are optional switchable and have as end gears higher gear jumps of about 30% to the respective adjacent aisles. The 0th gear is suitable for extreme climbs, the 15th gear allows the achievement of high speeds. Such a hub gear 1 allows a high ride comfort with a high number of gears.

With regard to the designation of the planetary gear 3, 5, 7, 9, 1 1 is to be considered that in the present case, each coupling of a planetary gear with a sun gear as a separate planetary gear 3, 5, 7, 9, 11 is considered. However, among these "planetary gears" in the broadest sense, only those are referred to as "complete planetary gear" comprising a sun gear, a set planetary gears and a ring gear. Thus, the planetary gears 3, 5 and 11 are "complete planetary gears." The planet gears 7 and 9 together form an "extended planetary gear". The first portion of this "extended planetary gear" is formed by the planetary gear 7, which in itself forms a "complete planetary gear", since it contains a sun gear 53, a set of planet gears 43 and a ring gear 45. The second section of the "extended planetary gear" is formed by the planetary gear 9, which comprises only a sun gear 55 and a set of planetary gears 49. The planet gears 43 and 49 are sections of one and the same stepped planetary gear 47. This construction will be referred to as "Extended planetary gear" called.

The planetary gear 3, 5, 7, 9, 11 are arranged axially adjacent to a schematically indicated central axis 13. On the central axis 13 further designed as clutches switching means 15, 17, 19, 21 and four freewheels 23, 25, 27, 29 are arranged, whereby a switching of the desired gears is made possible by a corresponding locking and / or inhibiting individual planetary gear components.

The first planetary gear 3 consists of a ring gear 31, arranged on a planet carrier 33 first planetary gear 35 and a sun gear 37. As the expert The planetary gear 3 will not only comprise a first planetary gear 35, but a plurality of similar first planetary gears 35. However, this understanding of those skilled in the art will be referred to in the following for the sake of simplicity on the planetary gears in the singular. The ring gear 31 is driven from the outside and meshes with its internal teeth with the planetary gear 35. The planetary gear 35 in turn meshes with the sun gear 37, which is arranged on the central axis 13 via a first freewheel 23. The planet carrier 33 is connected to the first clutch 15 and can be locked via this relative to the central axis 13. The second planetary gear 39 of the second planetary gear 5 is coupled via the planet carrier 33 with the first planetary gear 3. The second planetary gear 39 in turn meshes with the sun gear 41 of the second planetary gear 5. In this case, the sun gear 41 can be fixed to the central axis 13 via the coupling 17. Furthermore, a second freewheel 25 is arranged on the planet carrier 33, via which the planet carrier 33 is coupled to the sun gear 41.

The planetary gear 39 of the second planetary gear 5 and the planetary gear 43 of the third planetary gear 7 are in the present case coupled together via a common second ring gear 45. The ring gear 45 is formed over its entire axial width with the same circumferential toothing. By using a common ring gear 45, the number of components in the production of the hub circuit 1 can be reduced.

The planetary gear 43 of the third planetary gear 7 is formed as a double-stepped double planetary gear 47. The double planetary gear 47 may be made in one piece and has, in addition to the planetary gear 43, yet another planetary gear 49. In the present case, the planetary gear 49 is already associated with the fourth planetary gear 9. Both planetary gears 43, 49 have different diameters and divergent numbers of teeth on its outer periphery. As a result, a ratio change is achieved with little radial space.

The double planetary gear 47 or the two planetary gears 43, 49 designed as partial planet wheels are arranged on a common second planet carrier 51 and mesh with a sun gear 53, 55. The sun gear 53 of the third planetary gear 53 Drive 7 can in this case be fixed via the clutch 19 to the central axle 13, whereas the sun gear 55 of the fourth planetary gear 9 is coupled via the freewheel 27 to the central axle. As mentioned above, the third planetary gear 7 and the fourth planetary gear 9 together form an "extended planetary gear".

The speed of the second planetary carrier 51 is coupled via the fifth sun gear 57 in the fifth planetary gear 1 1. For this purpose, the sun gear 57 driven by the planetary carrier 51 meshes with the planetary gear 59 of the fifth partial transmission 1 1. The planetary gear 59 is arranged on a third planet carrier 61, via which the rotational speed is decoupled on the drive side. Furthermore, the planet gear 59 meshes with a fourth ring gear 63, which in turn is connected via a further freewheel 29 with the central axis 12. The sun gear 57 of the fifth planetary gear 11 is additionally coupled via the clutch 21 to the planet carrier 51.

FIG. 2 shows a table 71 which lists the respective numbers of teeth of the circumferential toothing of the planetary gear components of the 14-speed hub gear according to FIG. In the present case, the two sun gears 41, 53 shown in Table 71 under PG II and PG III, the same number of teeth of 40 teeth. The planetary gears 39, 43 as part of each planetary gear set have the same number of teeth (PG II and PG III) with 47 teeth each. The three used in the hub 1 ring gears 31, 45, 63, each with 134 teeth all three have the same number of teeth on the inner circumference.

By using a high number of identical parts within the hub circuit 1 a desired high transmission ratio is achieved with a low structural complexity and low production costs. FIG. 3 shows a circuit diagram 81 for the 14-speed hub gear according to FIGS. 1 and 2. With the numbers of teeth listed in table 71 (FIG. 2), the gear ratios indicated in circuit diagram 81 can be implemented for the respective gears engaged. The crosses in the tables show which switching means 15, 17, 19, 21 is effective, ie inhibits or blocks, or which freewheel 23, 25, 27, 29 is used. A lack of the cross means correspondingly that the respective switching means 15, 17, 19, 21 are unlocked or released or the respective freewheel 23, 25, 27, 29 is not used. _ _

It can be seen from the circuit diagram 81 that the direct gear, in which the gear ratio is 1: 1, is in the 15th gear. Here, all coupled to the sun gears 37, 41, 53, 57 clutches 15, 17, 19, 21 are connected. The 15th gear, as well as the O.Gang, is here optional switchable. If both gears are additionally engaged, it is 16-speed gearbox, but the gear jump between the 0th gear and the 1st gear, as well as the gear jump between the 14th gear and the 15th gear at each about 30% lie.

In Fig. 4, a schematic structure of a 16-speed hub gear 91 for a bicycle is shown. The hub gear 91 achieves a total spread of 6.39 by coupling six planetary gears 93, 95, 97, 99, 101, 103 at 16 gears. Such a hub gear 91 allows a high level of ride comfort compared to common circuits increased number of gears. Note, however, that of the six "planetary gears", two together form an "extended planetary gear", namely planetary gears 93 and 95 and planetary gears 97 and 99. Planetary gears 101 and 103 are "full planetary gears" in the sense of the present disclosure In other words, the hub gear 91 consists of two "complete planetary gears" 101, 103 and two "extended planetary gears" 93/95, 97/99. As with the sub-circuit 1 according to Fig. 1, the planetary gears 93, 95, 97, 99, 101, 103 arranged side by side on a schematically indicated central axis 105. Furthermore, on the central axis 105 four formed as clutches switching means 107, 109, 1 1 1, 113 and four freewheels 1 15, 1 17, 1 19, 121 for locking and / or inhibiting individual planetary gear components arranged.

The first planetary gear 93 consists of a ring gear 123, a planetary gear 125 arranged on a first planetary gear 127 and a sun gear 129. The ring gear 123 is driven from the outside and meshes with its internal teeth with the planetary gear 127. The planetary gear 127 is present part of a two-stepped Doppelp lane- tenrades 129. By using a double planetary gear 129, the desired ratio change is achieved in a small radial space. The double planetary gear 129 may be made in one piece and has in addition to the planetary gear 127 another _ _

Planet wheel 131 on. About the two planetary gears 127, 131, the first planetary gear 93 is coupled to the second planetary gear 95.

The two planet gears 127, 131 of the double planetary gear 129 have different diameters and have on their outer circumference divergent numbers of teeth. The planet gear 127, which has the larger diameter and a smaller number of teeth, meshes with the first sun gear 133, which in turn is connected to the first clutch 107. About the clutch 107, the sun gear relative to the central axis 105 can be set or locked. The planetary gear 131 meshes with the second sun gear 135 of the second planetary gear 95. The Sonnenradi 35 is presently arranged via a first freewheel 115 on the central axis 105.

The speed of the planetary gear 131 as part of the stepped double planetary gear 129 is coupled via the common planet carrier 125 in the third planetary gear 97 and equally in the fourth planetary gear 99. This coupling is achieved by the double stepped double planetary gear 139. The double planetary gear 139 may also be made in one piece and consists of two planetary gears 141, 143, each with different diameters and circumferential teeth. The planetary gear 141 of the stepped double planetary gear 129 meshes with the sun gear 145 of the third planetary gear 97, wherein the sun gear 145 is connected via the second freewheel 117 with the central axis 105. The planetary gear 143 meshes with the sun gear 147 of the fourth planetary gear 99. The sun gear 147 can be fixed via the second clutch 109 to the central axis 105.

Furthermore, the planetary gear 143 meshes with a ring gear 149. About this ring gear 149, the planetary gear 143 of the fourth planetary gear 99 is coupled to the Planetenradi 51 of the fifth planetary gear 101. In addition to the desired coupling, the use of a common ring gear 149 reduces the number of components required for the hub gear 91 and thus the material and manufacturing costs when they are completed. _.

The planetary gear 151 further meshes with a sun gear 1 53, which in turn is arranged on the central axis 105 via a further freewheel 1 19. In addition, the sun gear 153 is coupled to the planetary carrier 155 of the fifth planetary gear 101 via the third switching means 11 1 designed as a clutch. The planet carrier 155 additionally serves to transmit the speed from the fifth planetary gear 101 to the sixth planetary gear 103 of the hub gear 91. For this purpose, the planet carrier 155 is connected to the sun gear 157 of the sixth planetary gear 103.

The sun gear 157 continues to mesh with the sixth planetary gear 159, which is arranged on a further planet carrier 161. The planet gear 159 itself meshes with a fourth ring gear 163, which in turn is connected via a further freewheel 121 with the central axis 105. The decoupling of the rotational speed takes place on the output side via the third planet carrier 161. FIG. 5 shows a table 171 which lists the respective numbers of teeth of the peripheral teeth of the planetary gear components of the 16-gear hub transmission according to FIG. In the present case, the two sun gears 147, 153, listed in Table 171 under PG IV and PG V, each have the same number of teeth of 47 teeth. The planet wheels 127, 143, 151 (listed as PG I, PG IV and PG V in Table 171) have the same circumferential toothing, each with 37 teeth. The ring gears 123, 139, 161 of the hub gear 91 have all three teeth with the same number of teeth on their inner circumference with 134 teeth.

Even with the hub gear 91, a desirably high gear ratio is achieved by using a large number of identical parts with a low outlay on construction and reduced production costs.

FIG. 6 shows a circuit diagram 181 for the 16-speed hub gear according to FIGS. 4 and 5. With the numbers of teeth shown in table 171 according to FIG. 5, the gear ratios indicated in circuit diagram 181 can be realized at the respectively engaged gears. As already explained in the description of FIG. 3, the crosses in the circuit diagram 181 indicate which switching means 107, 109, 111, 114 are effective, ie blocked or inhibited, or which freewheel 15, 117, 119, 121 are used is. A lack of the cross means corresponding , _ chend that the respective switching means 107, 109, III, 114 unlocked or released or the corresponding freewheel 1 15, 1 17, 1 19, 121 is not used.

The shift pattern 181 shows that the direct gear in the 16-speed hub gear as well as the 14-speed hub gear is in 15th gear. Again, all couplings 107, 109, 1 1 1, 1 13 are connected accordingly to obtain a ratio of 1.

Both variants of the hub gear 1 and 91 is a number of four freewheels and four switching means or couplings in common. With a comparatively small number of different components, a circuit with a high gear spread is realized in a small space.

More specifically, each of the complete planetary gears 3, 5, 11; 101, 103 or extended planetary gear 7/8, 93/95, 97/99 exactly one switching means and a freewheel. This allows each of these complete or extended planetary gear taken in turn switch to two different transmission states, so that each of these complete or extended planetary gear two translations contributes to the overall transmission. Since the total number of complete planetary gear or extended planetary gear is four, you get 2 ⁴ = 16 different switching states of the hub gear 1, 91 as a whole, ie 16 gears. It is irrelevant whether all of these gears are actually used in the proposed shift pattern. For example, as in the case of the hub gear 1 of FIG. 1, the highest and the lowest gear ratios may be omitted within the scope of the designated shift pattern, however, the associated gear ratio exists and is therefore counted as "gear".

Although a complete planetary gear could basically provide three different translations, but this will require at least two active switching means. This route is therefore not covered in the preferred embodiments of the invention. Rather, it turns out that in the approach chosen here, to use only two switching states per complete or extended planetary gear, sufficient degrees of freedom in the transmission design result in optimally dimensioned shift hubs, of which two concrete embodiments are presented here. Significant Here, "optimal" means that a relatively large number of gears (here 16) can be obtained with a relatively uniform transmission distribution and a high spread, in fact this approach, as shown in the exemplary embodiments, leads to hub gears having a allow greater girth spread than in the prior art, and with only four active switching means, thereby even reducing the complexity of the hub circuitry despite the improved performance.

LIST OF REFERENCE NUMBERS

I hub gear

3 first planetary gear

5 second planetary gear

7 third planetary gear

9 fourth planetary gearbox

I I fifth planetary gear

13 central axis

15 first switching means

17 second switching means

19 third switching means

21 fourth switching means

23 freewheel

25 freewheel

27 freewheel

29 freewheel

31 ring gear

33 planet carrier

35 planetary gear

37 sun wheel

39 planetary gear

41 sun wheel

43 planetary gear

45 ring gear

47 double planetary gear

49 planetary gear

51 planet carrier

53 sun wheel

55 sun wheel

57 sun wheel

59 planetary gear Planetary gear ring gear

table

switching scheme

Hub gearbox First planetary gearbox Second planetary gearbox Third planetary gearbox Fourth planetary gearbox Fifth planetary gearbox Sixth planetgetget Central axis

first switching means second switching means third switching means fourth switching means freewheel

freewheel

ring gear

Planet carrier planetary gear

Double planetary gear planet

sun

Double planetary gear planet

planet

sun

ring gear

planet 153 sun wheel

155 planet carrier

157 sun wheel

159 planetary gear

161 planet carrier

163 ring gear

171 table

181 circuit diagram

Claims

claims

A hub gear (1, 91) for a bicycle, comprising a number of planetary gears (3, 5, 7, 9, 11, 93, 95, 97, 99, 101, 103)

- One or more complete planetary gear (3, 5, 11, 101, 103), each having a sun gear (37, 41, 57, 153, 157), a set planetary gears (35, 39, 59, 149, 163) and a Ring gear (31, 45, 63, 149, 163) comprises and / or

- One or more advanced planetary gear (7/9; 93/95, 97/99), each comprising

A first and a second sun gear (53, 55, 133, 135, 145, 147)

• a set of stepped planet wheels (47, 129, 139) each having a first (43;

127, 141) and a second (49, 131, 143) planetary gear portion of different diameter, which are rotatably connected to each other, wherein the first Planetenradabschnitt (43; 127, 141) meshes with the first sun gear (53; 133, 145) and the second Planetenradabschnitt (49, 131, 143) with the second sun gear (55; 135, 147) meshes,

the hub circuit (1, 91) further comprising a number of switching means (15, 17, 19, 21, 107, 109, 111, 113) for reversibly locking and / or inhibiting individual planetary gear components, characterized in that for each complete planetary gear ( 3, 5, 1 1, 101, 103) and for each extended planetary gear (7/9; 93/95, 97/99)

- A switching means (15, 17, 19, 21, 107, 109, 111, 113) and a freewheel (23, 25, 27, 29;

115, 117, 119, 121) are provided, or

- Two switching means are provided, one of which would be replaceable in the context of the switching pattern by a freewheel.

2. hub gear (1, 91) according to claim 1, wherein the planetary gear (3, 5, 7, 9, 11, 93, 95, 97, 99, 101, 103) are coupled together such that the ratio of the translation of lowest gear to the translation of the highest gear is more than 5.40.

3. hub circuit (1, 91) according to claim 1 or 2, wherein the switching means (15, 17, 19, 21;

107, 109, 111, 113) are arranged on the central axis (13, 105).

4. hub gear (1, 91) according to any one of the preceding claims, comprising four complete (3, 5, 1 1, 101, 103) and / or extended planetary gear (7/9; 93/95, 97/99), in particular three complete and one extended or two complete and two advanced planetary gearboxes.

5. hub circuit (1, 91) according to any one of the preceding claims, comprising four switching means (15, 17, 19, 21, 107, 109, 111, 113), of which

two switching means (17, 19, 107, 109) for reversibly locking and / or inhibiting a sun gear (41, 53, 133, 147) with respect to the central axis (13, 105),

- A switching means (21, 111) for reversibly locking and / or inhibiting a planetary carrier (61, 155) with respect to the associated sun gear (57, 153) and

- A switching means (113, 15) for locking and / or inhibiting another planetary carrier (161) with respect to the associated sun gear (157) or for locking and / or inhibiting a planetary carrier (33) and a ring gear (31) with respect to each other is determined or are.

6. hub gear (1, 91) according to any one of the preceding claims, comprising four freewheels (23, 25, 27, 29, 1 15, 117, 119, 121), of which

two freewheels (23, 27, 115, 117) between the central axis (13, 105) and in each case a sun wheel (37, 55, 135, 145),

- a freewheel (29; 121) between the central axis (13; 105) and a ring gear (63;

163), and

- A freewheel (1 19; 25) between the central axis (105) and another sun gear (153) or between a sun gear (41) and a planet carrier (33) is arranged or are.

7. hub circuit (1, 91) according to any one of the preceding claims, wherein as planetary gear components planetary gear sets are included, of which at least two are formed with identical parts.

8. hub gear (1, 91) according to any one of the preceding claims, wherein as planetary gear components ring gears (31, 45, 63, 123, 149, 163) are included, which are at least partially formed as identical parts, preferably all as identical parts.

9. hub gear (1, 91) according to any one of the preceding claims, wherein as planetary gear sun gears (37, 47, 53, 55, 57, 133, 135, 145, 147, 153, 157) are included, which at least partially formed as equal parts are.

10. hub gear (1, 91) according to any one of claims 2 to 4, wherein the planetary gear sets of two or more planetary gears (3, 5, 7, 9, 11, 93, 95, 97, 99, 101, 103) are coupled together ,

1 1. hub gear (1, 91) according to any one of the preceding claims, wherein two or more of the planetary gear (3, 5, 7, 9, 11, 93, 95, 97, 99, 101, 103) via a common planet carrier (33 , 51, 61, 125, 155, 161) are coupled together.

12. hub gear (1, 91) according to any one of the preceding claims, wherein two or more of the planetary gear (3, 5, 7, 9, 11, 93, 95, 97, 99, 101, 103) via a common ring gear (31, 45, 63, 123, 149, 163) are coupled together.

13. hub gear (1, 91) according to any one of the preceding claims, wherein two or more of the planetary gear sets via a common sun gear (37, 47, 53, 55, 57, 133, 135, 145, 147, 153, 157) are coupled together ,

14. hub gear (1, 91) according to any one of the preceding claims, wherein the coupled planetary gear (3, 5, 7, 9, 11, 93, 95, 97, 99, 101, 103) on the drive side via a ring gear (31, 45, 63, 123, 149, 163) are driven.

15. hub gear (1, 91) according to any one of the preceding claims, wherein the output-side coupling via a planet carrier (33, 51, 61, 125, 155, 161) takes place.

16. hub transmission (1, 91) according to any one of the preceding claims, wherein the or each switching means (15, 17, 19, 21, 107, 109, 111, 113) is formed as a clutch or as a brake.

A hub gear (1, 91) according to any one of the preceding claims, wherein a number of freewheels (23, 25, 27, 29, 115, 117, 119, 121) are included, via which a number of planetary gear components are connected to the central axis (13 , 105) are coupled.

18. hub gear (1, 91) according to any one of the preceding claims, wherein the gear jumps between two respective adjacent gears in a range between 12% and 15%.

19. A hub gear (1, 91) for a bicycle comprising a number of planetary gears (3, 5, 7, 9, 11, 93, 95, 97, 99, 101, 103), and a number of switching means (15, 17, 19, 21, 107, 109, 111, 113) arranged at the central axis for the reversible locking and / or inhibiting of individual planetary gear components, characterized in that the planetary gears (3, 5, 7, 9, 11, 93, 95, 97, 99, 101, 103) are coupled together such that the ratio of the ratio of the lowest gear to the gear ratio of the highest gear is more than 5.40.

20. hub circuit (1, 91) according to claim 19, having one or more features of claims 7 to 18.

21. hub circuit (1, 91) according to claim 19 or 20, with four switching means (15, 17, 19, 21, 107, 109, 111, 113) and four freewheels (23, 25, 27, 29, 115, 117 , 119, 121) 16 gears realized,

wherein instead of one or more of said freewheels (23, 25, 27, 29, 115, 117, 119, 121), a further switching means may be present, as long as this would be replaceable by a freewheel in the context of the switching pattern.