WHEELSET ARRANGEMENT AND BICYCLE GEARBOX

Description

Technical field

[0001] The present invention relates to a gear set arrangement for a planetary gear system of a bicycle. Furthermore, the invention relates to a bicycle gearbox. State of the art

[0002] German patent DE 10 2018 208 380 A1 describes a multi-stage planetary gear unit for a bicycle or pedelec. These multi-stage gear units have three or four planetary gear sets to provide eight or sixteen gears. A planetary gear set of the multi-stage gear unit, which is arranged at the front or rear of the torque flow as a pre-selector or post-selector, can only provide two rotational speeds for changing a gear ratio. Description of the invention

[0003] A first aspect of the invention relates to a gear set arrangement for a planetary gear system of a bicycle. The planetary gear system can, for example, be designed to be arranged in a bottom bracket of the bicycle. The gear set arrangement comprises a planetary assembly. The planetary assembly can, for example, comprise one or more planetary gear sets.

[0004] The wheelset assembly includes a stationary component. Furthermore, the wheelset assembly includes a first brake and a second brake. Additionally, the wheelset assembly includes a first freewheel coupling and a second freewheel coupling.

[0005] The stationary component could be, for example, a gearbox housing or a section of a bicycle frame. A stationary component can be, for instance, a component that is immobile relative to the rotating elements of the gearbox. The stationary component can also be formed by several spaced-apart elements.

[0006] A brake can be a positive-locking or friction-locking switching element. The respective brakes can be designed to prevent or reduce the rotation of an associated rotary element, for example, to a stop. The respective brakes can be designed to connect a rotary element to the stationary component in a rotationally fixed manner, but without permanently locking the rotary element to the stationary component. The connection or locking mechanism provided by the brake can be switchable. The brakes can be actively actuated by a switching device, for example, by means of a cable pull of a manual switch.

[0007] A freewheel clutch can be a clutch that only acts in one direction of rotation. Two elements that can be connected to each other by means of a freewheel clutch are permanently and rotationally fixed relative to each other in one direction of rotation. Elements that are rotationally fixed to each other run at the same speed. In the opposite relative direction of rotation, which can also correspond to the driven element overtaking the driving element, the two elements are not connected to each other by means of the freewheel clutch, but are decoupled from each other. When the relative direction of rotation is reversed from a freewheel direction to a clutch direction, the freewheel clutch can lock automatically. The freewheel clutch can be designed, for example, as a pawl freewheel or a roller clutch. A freewheel clutch can also be a switching element that does not require active switching.This allows the transmission to be more nested and compact. For example, a freewheel clutch is not actuated and therefore does not need to be accessible for actuation. This means that, in the wheelset arrangement, a freewheel clutch can be radially enclosed on the outside by a hollow shaft or other rotating element. The wheelset arrangement can be designed so that the transmission from the input to the output is either high-speed or neutral in each gear. The respective freewheel clutches can be oriented accordingly.

[0008] In the case of a friction-based switching element, such as a freewheel clutch or a brake, speed differences between the components can persist even after the clutch has engaged. This condition, whether intended or unintended, is nevertheless referred to as a rotationally fixed connection between the respective components. In a friction-based connection, a certain speed difference between the two connected elements can occur, for example, due to slippage.

[0009] The gear set is designed to provide three gear ratios. For example, the gear set can provide three different gears. These gears can be shifted, for instance, by actuating the respective brakes. Each gear, for example, provides a different gear ratio. The freewheel clutches can change their state automatically, so no active actuation is necessary for gear changes. A fixed mechanical gear ratio between the input and output of the planetary gear set can be present in each gear, thus providing additional gears in the bicycle transmission. The gear set is therefore particularly suitable for forming a pre-selector or post-selector gear set in a bicycle transmission, in order to increase the gear range and, alternatively or additionally, the number of gears with simple means.Each gear can have a fixed mechanical transmission ratio between input and output. The gear set arrangement can be designed to provide exactly three transmission ratios using a planetary gear set.

[0010] The planetary assembly comprises a planet gear set. The planet gear set includes a first rotating element (designed as a sun gear), a second rotating element, and a third rotating element. The second element is a ring gear in the case of a negative planet gear set and a planet carrier in the case of a positive planet gear set. The third element is a planet carrier in the case of a negative planet gear set and a ring gear in the case of a positive planet gear set. A negative planet gear set has a negative gear ratio, and a positive planet gear set has a positive gear ratio. The planet gears can be rotatably mounted on the planet carrier. Depending on the design, a gear set can contain one or more sets of planet gears. The individual planet gears of a planet gear set can mesh with its ring gear and its sun gear.If multiple sets of planet gears are present, only the planet gears of one set can mesh with the sun gear, and only the planet gears of another set can mesh with the ring gear. The respective planet gears of the two planet gear sets can then mesh with each other in pairs.

[0011] The planetary assembly has a drive input, to which, for example, the quantity to be translated can be fed into the gear set. The planetary assembly has an output input, to which, for example, the quantity translated by the gear set can be output. The output can be mechanically connected to, for example, a bicycle's rear wheel, such as by means of a bicycle chain or a belt. The gearbox can have a drive shaft, which can form the drive at one end. The output can be formed by an output shaft, which can be parallel to or coaxial with the drive. The output shaft can form the output at one end. The drive input of the planetary assembly can correspond to an input or drive of the gearbox. Alternatively, the output input of the planetary assembly can correspond to an output of the gearbox.The planetary assembly can be configured to transmit torque from the input to the output. This transmission can be achieved with three different gear ratios. The gear set can also be configured to transmit torque.

[0012] A bicycle gearbox is typically designed to provide drive torque in only one direction of rotation, since bicycles are only ridden forwards. In this respect, a bicycle gearbox already differs from conventional motor vehicle gearboxes. For example, the gearbox may be designed to prevent the transmission of torque in the opposite direction of rotation. Similarly, a bicycle gearbox does not offer the possibility of changing the direction of rotation of the output relative to the input, for example, by using a reversing mechanism.

[0013] The first rotating element can be locked to the stationary component by means of the first brake. The first rotating element can be connected to the output shaft in a rotationally fixed manner by means of the first freewheel clutch. The second rotating element can be locked to the stationary component by means of the second brake. The second rotating element can be connected to the output shaft in a rotationally fixed manner by means of the second freewheel clutch. The third rotating element is permanently connected to the drive shaft in a rotationally fixed manner. For example, the third rotating element can be bolted to the drive shaft or formed as a single piece. The third rotating element and the drive shaft can be formed by a common shaft. The wheelset assembly is thus designed to provide three gear ratios between the drive shaft and the output shaft. Only two actively actuated switching elements in the form of brakes are required for this, which makes the wheelset assembly compact and easy to integrate into a bicycle gearbox.No additional planetary gear set is required to provide extra gears in otherwise conventional bicycle transmissions. Additional planetary gear sets would be more complex and require more installation space, which can be avoided in this way.

[0014] The gear set arrangement can thus provide two gear ratios instead of three with a single planetary gear set. For the first gear ratio, both brakes are open. The two freewheel clutches then operate in the locking direction. In this case, the gear ratio can be, for example, one. By closing the first brake, a higher gear ratio can be selected. The first freewheel clutch is then in the overrunning position, and the second freewheel clutch continues to operate in the locking direction. By opening the first brake and closing the second brake, a further higher gear ratio can be selected. The first freewheel clutch then operates in the locking direction, and the second freewheel clutch is then in the overrunning position.

[0015] In one embodiment of the transmission, the planetary gear set is designed as a negative planetary gear set. The second rotating element can be a ring gear. The third rotating element can be a planet carrier. With negative planetary gear sets, one set of planet gears is usually sufficient, which can result in cost and friction advantages. The individual planet gears of a planetary gear set can mesh with its ring gear and sun gear. Furthermore, the planet carrier connected to the drive can have a disc-shaped section where torque sensing is easily possible. The planet carrier can be integrally formed with the drive, for example, as a common shaft. Alternatively, the planet carrier can be permanently and rotationally fixed to the drive.

[0016] In one embodiment of the transmission, the planetary gear set is configured as a plus planetary gear set. The second rotating element can be configured as a planet carrier. The third rotating element can be configured as a ring gear. The plus planetary gear set can comprise two sets of planet gears. The planet gears of one set can mesh with the sun gear, and the planet gears of the other set can mesh with the ring gear. The respective planet gears of the two sets of planet gears can then mesh with each other in pairs.

[0017] In one embodiment of the transmission, the sun gear is designed in two parts. The sun gear may be interrupted in the axial direction. It may comprise a first sun gear element and a second sun gear element. Both sun gear elements may, for example, be identical. Other rotating elements may be made in one piece and, alternatively or additionally, be undivided. The split sun gear allows the planet carrier to be connected to the drive radially on the inside in the design with a negative planetary gear set. This allows the gear set assembly to be particularly compact. Furthermore, this design enables the planet carrier to be easily connected to the drive despite the negative planetary gear set design. The respective planet gears of the negative planetary gear set may, for example, mesh with both sun gear elements.

[0018] In one embodiment of the transmission, the ring gear is designed as a split ring gear. The ring gear can be interrupted in the axial direction. Thus, the ring gear can have a first ring gear element and a second ring gear element. Both ring gear elements can, for example, be identical. Other rotating elements can be made in one piece and, alternatively or additionally, be undivided. The split ring gear allows the planet carrier to be connected to the drive radially on the outside in the design with a negative planetary gear set. The planet carrier can thus have a disk-shaped area that is arranged axially on the outside. Torque sensing is easily achieved with this design. The respective planet gears of the negative planetary gear set can, for example, mesh with both ring gear elements.

[0019] In one embodiment of the transmission, the first and second brakes are designed to be actuated simultaneously in order to lock the planetary gear set. In the locked state, for example, all rotating elements of a planetary gear set can be prevented from rotating. The locked planetary gear set cannot transmit any torque. This provides an anti-theft and, alternatively or additionally, an immobilizer. This function can therefore be provided as an additional switching state of the gear set assembly, alongside the three gears, each with a different gear ratio.

[0020] Alternatively, the first and second brakes can be designed as a dual switching element, which can only be actuated alternately. This makes operation particularly simple and allows for a particularly compact wheelset arrangement.

[0021] In one embodiment of the transmission, the first freewheel clutch is designed to automatically switch to the locked position when the second brake is applied. The first freewheel clutch can also be designed to automatically switch to the overrunning position when the first brake is applied. With the brakes reversed, the freewheel clutches can have the opposite state. For example, the first freewheel clutch can automatically switch to the locked position when the first brake is released.

[0022] In one embodiment of the transmission, the second freewheel clutch is designed to automatically switch to the locking position when the first brake is applied. The second freewheel clutch can also be designed to automatically switch to the overrunning position when the second brake is applied. Reversing the brake direction can result in the freewheel clutches being in the opposite state.

[0023] The gear set assembly can be free of additional planetary gear sets. The individual gear sets can be free of further elements, such as additional ring gears, planet carriers, planet gears, and sun gears. For example, in one embodiment, the planetary assembly and the transmission have no planetary gear sets other than those described here. Likewise, in one embodiment, the gear set assembly can have no further spur gear stages other than those described here. In the gear set assembly and the transmission, it can be provided that the entire planetary assembly, or at least all planetary gear sets, are designed together as a planetary roller and thus have only coaxial elements.

[0024] A second aspect of the invention relates to a bicycle transmission. The bicycle transmission has a wheelset arrangement according to the first aspect. Further features, embodiments, and advantages are described in the first aspect.

[0025] The bicycle transmission can have an input and an output. The bicycle transmission can have a main gear set, which is connected in series with the wheelset assembly for torque transmission. The main gear set can have one or more planetary gear sets. The bicycle transmission can be designed to transmit torque from the input via the respective gear sets to the output. The input of the wheelset assembly can, for example, be permanently and rotationally fixed to the input of the bicycle transmission or form the input itself. Alternatively, the output of the wheelset assembly can, for example, be permanently and rotationally fixed to the output of the bicycle transmission or form the output itself. To transmit torque, it may be necessary to actuate one or more shift elements and, alternatively or additionally, brakes.

[0026] The main gear set can be configured as follows, for example. The main gear set can have at least one input and at least one output. The gear set assembly can be connected to the input or output of the main gear set for torque transmission. The main gear set can have a first planetary gear set and a second planetary gear set. The two planetary gear sets can be configured as negative planetary gear sets. The first planetary gear set can have a first sun gear, a first planet carrier, and a first ring gear. The second planetary gear set can have a second sun gear, a second planet carrier, and a second ring gear. Each planet carrier can have one or more planet gears rotatably mounted on it, which mesh with the respective sun gear and ring gear of the planetary gear set.

[0027] The numbering of the rotating elements and the planetary gear sets serves only for identification purposes. Therefore, the first rotating elements can be part of the first planetary gear set, and the second rotating elements can be part of the second planetary gear set. Similarly, the first planetary gear set can have a first set of planet gears, which can also be referred to as the first planet gears. Likewise, the second planetary gear set can have a second set of planet gears, which can also be referred to as the second planet gears.

[0028] The bicycle gearbox can also have a third brake, a fourth brake, a third freewheel clutch, and a fourth freewheel clutch to shift the respective gear ratios of the main gear set. Again, the numbering serves only for identification purposes. The entire bicycle gearbox can therefore have four brakes and four freewheel clutches. Furthermore, the bicycle gearbox can include the main gear set and the gear set assembly, or three planetary gear sets.

[0029] The drive of the bicycle gearbox can be non-rotatably connected to the first planet carrier. The first planet carrier can thus form the drive of the main gear set. The first ring gear can be permanently non-rotatably connected to the third rotating element of the gear set assembly, and thus its drive. The first sun gear can be permanently non-rotatably connected to the second planet carrier. The drive of the bicycle gearbox and the first planet carrier can be non-rotatably connected to the second sun gear by means of the third freewheel clutch. The second sun gear can be locked to the stationary component by means of the third brake. The second ring gear can be locked to the stationary component by means of the fourth brake. The second ring gear can be non-rotatably connected to the third rotating element of the gear set assembly, and thus its drive, by means of the fourth freewheel clutch.In this example, the drive of the main wheelset forms the drive of the bicycle gearbox, and the output of the wheelset assembly forms the output of the bicycle gearbox. The main wheelset is thus arranged on the drive side of the wheelset assembly. However, a reverse connection in series and in the torque flow is also possible.

[0030] The individual planetary gear sets may be free of additional, undescribed elements. The bicycle gearbox may be free of additional, undescribed planetary gear sets, shifting elements, and brakes.

[0031] The bicycle gearbox can include a shifting device. This device might, for example, consist of a cable and a shift lever, allowing the user to pull the cable to shift gears. Alternatively, the shifting device could include electric actuators for operating the respective brakes. For instance, the shifting device could also incorporate a control unit with a microcontroller.

[0032] InIn one embodiment, the transmission incorporates an electric motor. The electric motor can, for example, provide torque generated by the electric motor to the output of the bicycle transmission and, alternatively or additionally, to the input of the bicycle transmission. The bicycle transmission can also be designed as a drive unit with an electric motor. This transmission with an electric motor can enable a motor-assisted bicycle and, for example, be used in a pedelec. The electric motor can be configured to convert electrical energy into drive torque. The bicycle transmission can also include a control device and a power source, such as a battery, for the electric motor.

[0033] In one embodiment, the bicycle transmission includes a crankshaft. The bicycle transmission can be designed to transmit torque from the crankshaft to the drive unit. The crankshaft can, for example, be mounted in the bottom bracket housing of the bicycle. The crankshaft can be designed, for example, to allow for the movement of cranks with pedals, at least partially by muscle power, to propel the bicycle. The crankshaft can, for example, be permanently mechanically connected to the drive unit. For example, the drive unit of the bicycle transmission can be formed by the same shaft as the crankshaft. The crankshaft can be designed as the drive unit.The crankshaft can also be connected to the drive via another switching element, such as a freewheel clutch, and alternatively or additionally via a spur gear stage. The crankshaft can extend axially along a central axis of rotation of the bicycle gearbox, passing completely through the gearbox.

[0034] The gearbox can be equipped with a torque sensor. This torque sensor can be designed to detect torque applied to the crank axle. Alternatively or additionally, the torque sensor can be designed to detect torque applied to the drive mechanism of the bicycle gearbox. The gears, and alternatively or additionally, the drive power of the electric motor, can then be controlled, for example, depending on the respective detected torque values. Brief description of the characters

[0035] Fig. 1Figure 1 shows a schematic view of a first embodiment of a wheelset arrangement for a planetary gear unit of a bicycle, which has a plus planetary wheelset. Fig. 2 Figure 1 shows a schematic view of a second embodiment of a gear set arrangement for a planetary gear set of a bicycle, which has a negative planetary gear set. Fig. 3 A schematic view shows a third embodiment of a gear set arrangement for a planetary gear set of a bicycle, which also has a negative planetary gear set. Fig. 4 shows a schematic view of a bicycle gearbox with a wheelset arrangement according to Fig. 1 . Fig. 5 illustrates a switching logic of the transmission according to Fig. 4 . Detailed description of embodiments

[0036] Fig. 1Figure 1 shows a schematic view of a first embodiment of a gear set arrangement 10. The gear set arrangement 10 comprises a planetary gear set 12, which is designed as a plus planetary gear set. The planetary gear set 12 includes a sun gear 14, a planet carrier 16, and a ring gear 18. A radially inner set of planet gears 20 and a radially outer set of planet gears 22 are rotatably mounted on the planet carrier 16. The radially inner planet gears 20 mesh with the sun gear 14. The radially outer planet gears 22 mesh with the ring gear 18. The radially inner planet gears 20 mesh in pairs with the radially outer planet gears 22.

[0037] The wheelset assembly 10 also includes a stationary component 24, a first brake B1, a second brake B2, a first freewheel clutch F1, and a second freewheel clutch F2. A drive 34 of the wheelset assembly 10 is formed by a central shaft and is permanently and rotationally fixed to the ring gear 18. An output 36 of the wheelset assembly 10 is formed by a hollow shaft arranged radially outside it.

[0038] The first brake B1 secures the sun gear 14 to the stationary component 24. The second brake B2 secures the planet carrier 16 to the stationary component 24. The first freewheel clutch F1 connects the sun gear 14 to the output 36 in a rotationally fixed manner. The second freewheel clutch F2 connects the planet carrier 16 to the output 36 in a rotationally fixed manner.

[0039] This results in a first gear ratio stage in which the first brake B1 and the second brake B2 are open. If a torque is applied to the drive 34, the first freewheel clutch F1 and the second freewheel clutch F2 switch to the locked position. The planetary gear set 12 is thus locked, and the output 36 rotates at the same speed as the drive 34. If the planet carrier 16 is now held by the second brake B2, the second freewheel clutch F2 automatically switches to the overrunning position. Thus, only the sun gear 14 is connected to the output 36 via the first freewheel clutch F1, and one input variable is increased in speed. If, instead, the sun gear 14 is held by the first brake B1, the first freewheel clutch F1 automatically switches to the overrunning position.Thus, only the planet carrier 16 is connected to the output 36 via the second freewheel clutch F2, and one input signal is also increased in speed. This provides three gear ratios. Additionally, in another state, the first brake B1 and the second brake B2 are engaged. This locks the planetary gear set and provides anti-theft protection.

[0040] As in Fig. 1 As can be seen, the connection between drive 34 and ring gear 18, which is designed as part of the ring gear 18, surrounds the planet gear set 12 on the drive side and extends radially in a disc shape at one of the drive-side axial ends of the planet gear set 12. A torque sensor can easily be connected there.

[0041] Fig. 2Figure 1 shows a schematic view of a second embodiment of a wheelset arrangement 100. The wheelset arrangement 100 functions identically to the first embodiment and has the same switching states. Therefore, only relevant differences are explained. The wheelset arrangement 100 has a differently designed planetary gear set 112. The planetary gear set 112 is designed as a negative planetary gear set. The planetary gear set 112 comprises a sun gear 114, a planet carrier 116, and a ring gear 118. Only one set of planet gears 120 is rotatably mounted on the planet carrier 116. The planet gears 120 mesh with the sun gear 114 and the ring gear 118.

[0042] In gear set arrangement 100, the planet carrier 116 is permanently and rotationally fixed to the drive 34. For this purpose, the sun gear 114 is designed in two parts. The sun gear 114 has an axially drive-side first sun gear element 150 and an axially output-side second sun gear element 152. Both sun gear elements 150 and 152 mesh with the planet gears 120, whose teeth have a corresponding axial extension. The radially extending connection of the drive 34 to the planet carrier 116 is arranged axially between the first sun gear element 150 and the second sun gear element 152.

[0043] The sun gear 114 can be locked to the stationary component 24 by means of the first brake B1. The ring gear 118 can be locked to the stationary component 24 by means of the second brake B2. The sun gear 114 can be connected to the output 36 in a rotationally fixed manner by means of the first freewheel clutch F1. The ring gear 118 can be connected to the output 36 in a rotationally fixed manner by means of the second freewheel clutch F2.

[0044] Fig. 3 Figure 1 shows a schematic view of a third embodiment of a wheelset arrangement 200. The wheelset arrangement 200 is functionally identical to the second embodiment, has the same switching states, and also features a planetary gear set 112 designed as a negative planetary gear set. Therefore, only relevant differences are explained.

[0045] In the third embodiment of the planetary gear set 112, the drive 34 is permanently and rotationally fixed to the planet carrier 116 radially from the outside, instead of radially from the inside as in the second embodiment. Accordingly, in the third embodiment, the sun gear 114 is formed in one piece and the ring gear 118 in two pieces. In the third embodiment, the ring gear 118 has an axially drive-side first ring gear element 250 and an axially output-side second ring gear element 252. Both ring gear elements 250, 252 mesh with the planet gears 120, whose teeth have a corresponding axial extension. The radially extending connection of the drive 34 to the planet carrier 116 is arranged axially between the first ring gear element 250 and the second ring gear element 252.

[0046] In the third embodiment, the connection between drive 34 and planet carrier 116, which is designed as part of the planet carrier 116, encompasses the planet gear set 112 on the drive side and extends radially in a disc shape at a drive-side axial end of the planet gear set 112. A torque sensor can easily be connected there.

[0047] Fig. 4 Figure 400 shows a schematic view of a bicycle transmission 400 with a wheelset arrangement 100 according to the first embodiment, which is downstream of a main wheelset 402 of the bicycle transmission 400 in the torque flow. In other embodiments, the wheelset arrangement 10 or the wheelset arrangement 200 are used instead of the wheelset arrangement 100 according to the first embodiment. The bicycle transmission 400 also includes a main wheelset 402, a third brake B3, a fourth brake B4, a third freewheel clutch F3, and a fourth freewheel clutch F4.

[0048] The main gear set 402 comprises a first planet gear set 410 and a second planet gear set 420. The first planet gear set 410 includes a first sun gear 412, a first planet carrier 414, and a first ring gear 416. First planet gears 418 are rotatably mounted on the first planet carrier 414 and mesh with the first sun gear 412 and the first ring gear 416. The second planet gear set 420 includes a second sun gear 422, a second planet carrier 424, and a second ring gear 426. Second planet gears 428 are rotatably mounted on the second planet carrier 424 and mesh with the second sun gear 422 and the second ring gear 426. Both planet gear sets 410 and 420 of the main gear set 402 are designed as negative planet gear sets.

[0049] The first planet carrier 414 is permanently and rotationally fixed to a drive 430 of the bicycle transmission 400, which is designed as a pedal crank shaft. The first sun gear 412 is permanently and rotationally fixed to the second planet carrier 424. The first planet carrier 414 can be rotationally fixed to the second sun gear 422 by means of the third freewheel clutch F3. The first ring gear 416 is connected to the planet carrier 116 of the wheelset assembly 100 via a hollow shaft 434, which forms the drive 34 of the wheelset assembly 100. The second sun gear 422 can be locked to the stationary component 24 by means of the third brake B3. The second ring gear 426 can be locked to the stationary component 24 by means of the fourth brake B4. In addition, the second ring gear 426 can be connected to the hollow shaft 434 and thus to the planet carrier 116 of the wheelset arrangement 100 in a rotationally fixed manner by means of the fourth freewheel coupling F4.

[0050] The output 36 of the wheelset arrangement 100 also forms the output of the bicycle gearbox 400. The output 36 can be connected to a rear wheel of a bicycle for torque transmission.

[0051] Fig. 5 This illustrates the switching logic of the bicycle gearbox 400, where only the four brakes B1, B2, B3, and B4 are actively engaged. The four freewheel clutches F1, F2, F3, and F4 automatically change their state when the bicycle gearbox 400 is engaged. The bicycle gearbox 400 can, for example, provide twelve gears, each with a different ratio, numbered G1 to G12. A total gear ratio spread of, for example, 3.77.

[0052] The rows show the shift states for each gear. For the brakes, dots indicate a closed state, in which an element is connected to the stationary component in a rotationally fixed manner and thus locked in place. A dash indicates an open brake. For the freewheel clutches, a dash indicates an overrun state and a dot an interlock state. The column marked "i" shows the gear ratio for each gear. The column marked "j" shows the gear ratio spread between two adjacent gears. In each gear, those freewheel clutches in which the brake with the corresponding number is closed switch to the overrun state.

[0053] In gear G1, all four brakes B1, B2, B3, B4 are open. Accordingly, all four freewheel clutches F1, F2, F3, F4 are in the locked position.

[0054] In gear G2, the third brake B3 was closed. Accordingly, the third freewheel clutch F3 switched to the overtaking drive state.

[0055] In gear G3, the fourth brake B4 was closed instead. Accordingly, the fourth freewheel clutch F4 switched to the overtaking drive state.

[0056] In gear G4, the third brake B3 and the fourth brake B4 were closed. Accordingly, the third freewheel clutch F3 and the fourth freewheel clutch F4 switched to the overtaking drive state.

[0057] In gear G5, only the first brake B1 is closed. Accordingly, only the first freewheel clutch F1 has switched to the overtaking drive state.

[0058] In gear G6, the third brake B3 and the first brake B1 were closed. Accordingly, the third freewheel clutch F3 and the first freewheel clutch F1 switched to the overtaking drive state.

[0059] In gear G7, the fourth brake B4 and the first brake B1 were closed. Accordingly, the fourth freewheel clutch F4 and the first freewheel clutch F1 switched to the overtaking drive state.

[0060] In gear G8, the fourth brake B4, the third brake B3, and the first brake B1 were closed. Accordingly, the fourth freewheel clutch F4, the third freewheel clutch F3, and the first freewheel clutch F1 switched to the overrunning drive state.

[0061] In gear G9, only the second brake B2 is engaged. Accordingly, only the second freewheel clutch F2 has switched to the overtaking position.

[0062] In gear G10, the third brake B3 and the second brake B2 were closed. Accordingly, the third freewheel clutch F3 and the second freewheel clutch F2 switched to the overtaking drive state.

[0063] In gear G11, the fourth brake B4 and the second brake B2 were closed. Accordingly, the fourth freewheel clutch F4 and the second freewheel clutch F2 switched to the overtaking drive state.

[0064] In gear G12, the fourth brake B4, the third brake B3, and the second brake B2 were closed. Accordingly, the fourth freewheel clutch F4, the third freewheel clutch F3, and the second freewheel clutch F2 switched to the overrunning drive state. Reference sign

[0065] 10; 100; 200 Wheelset arrangement 12; 112 Planetary wheelset 14; 114 Sun wheel 16; 116 Planetary carrier 18; 118 Ring gear 20 Inner set of planet gears 22 Outer set of planet gears 24 Stationary component 34 Input 36 Output 120 Set of planet gears 150, 152 Sun gear elements 250, 252 Ring gear elements 400 Bicycle transmission 402 Main gear set 410, 420 Planetary gear sets 412, 422 Sun gear 414, 424 Planetary carrier 416, 426 Ring gear 418, 428 Planetary gears 434 Hollow shaft B1, B2, B3, B4 Brakes F1, F2, F3, F4 Freewheel clutches G1-G12 Gears

Claims

1. Gear set arrangement (10) for a planetary gear system of a bicycle, comprising a planetary assembly, a stationary component (24), a first brake (B1), a second brake (B2), a first freewheel clutch (F1) and a second freewheel clutch (F2), wherein the planetary assembly comprises a drive (34), an output (36) and a planetary gear set (12) having a first rotating element in the form of a sun gear (14), a second rotating element and a third rotating element, wherein the first rotating element can be fixed to the stationary component (24) by means of the first brake (B1), the first rotating element can be rotationally fixedly connected to the output (36) by means of the first freewheel clutch (F1), the second rotating element can be fixed to the stationary component (24) by means of the second brake (B2), the third rotating element is permanently rotationally fixedly connected to the drive (34) and wherein the gear set arrangement (10) is designed to provide three gear ratios between the drive (34) and the output (36), characterized in that the second rotating element can be rotationally fixedly connected to the output (36) by means of the second freewheel clutch (F2).

2. Gear set arrangement (100; 200) according to Claim 1, characterized in that the planetary gear set (112) is in the form of a minus planetary gear set, wherein the second rotating element is in the form of a ring gear (118) and the third rotating element is in the form of a planet carrier (116).

3. Gear set arrangement (10) according to Claim 1, characterized in that the planetary gear set (12) is in the form of a plus planetary gear set, wherein the second rotating element is in the form of a planet carrier (16) and the third rotating element is in the form of a ring gear (18).

4. Gear set arrangement (100) according to Claim 2, characterized in that the sun gear (114, 150, 152) is divided.

5. Gear set arrangement (200) according to Claim 2, characterized in that the ring gear (118, 250, 252) is divided.

6. Gear set arrangement (10; 100; 200) according to any of the preceding claims, characterized in that the first brake (B1) and the second brake (B2) are designed to be simultaneously operable in order to block the planetary assembly.

7. Gear set arrangement (10; 100; 200) according to any of the preceding claims, characterized in that the first freewheel clutch (F1) is designed to automatically change over to the locking direction state when the second brake (B2) is closed.

8. Gear set arrangement (10; 100; 200) according to any of the preceding claims, characterized in that the second freewheel clutch (F2) is designed to automatically change over to the locking direction state when the first brake (B1) is closed.

9. Bicycle gear system (400) having a gear set arrangement (10; 100; 200) according to any of the preceding claims.