DE102020206299A1 - Multi-stage gearbox in planetary design for a bicycle or a pedelec - Google Patents

Abstract

A planetary multi-stage transmission is proposed for a bicycle or a pedelec with a transmission input shaft (1) as the drive and a transmission output shaft (2) as the output, with at least three planetary gear sets (RS1, RS2, RS3, VRS, NRS) being provided, with at least three overrunning clutches (F1, F2, F3, FV, FN) and at least three brakes (B1, B2, B3, BV, BN) to achieve at least eight gears (G1, G2, G3, G4, G5, G6, G7, G8 , G9, G10, G11, G12, G13, G14, G15, G16) are provided, a second element of the first planetary gear set (RS1) being connected as an input element directly or via at least one further element to the transmission input shaft (1), with a The first element of the first planetary gear set (RS1) is connected as an output element directly or via at least one further element to the transmission output shaft (2), a third element of the first planetary gear set (RS1) as a coupling element with a second element of the second planetary gear atzes (RS2) is connected, wherein a first element of the second planetary gear set (RS2) can be fixed via a first brake (B1), the first element of the second planetary gear set (RS2) via a first one-way clutch (F1) to the second element of the first Planetary gear set (RS1) can be connected, a third element of the second planetary gear set (RS2) being connected to a second element of a third planetary gear set (RS3), a first element of the third planetary gear set (RS3) being fixable via a second brake (B2), the first element of the third planetary gear set (RS3) being connectable to the first element of the first planetary gear set (RS1) via a second overrunning clutch (F2), a third element of the third planetary gear set (RS3) being connected to the first via a third overrunning clutch (F3) Element of the first planetary gear set (RS1) can be connected and wherein the third element of the third planetary gear set (RS3) is fixed via a third brake (B3) is etchable. A bicycle or pedelec with the multi-speed transmission is also proposed.

Description

The present invention relates to a multi-stage transmission in planetary design for a bicycle or a pedelec. The invention also relates to a bicycle or pedelec with the multi-stage transmission.

For example from the publication DE 10 2018 208 380 a multi-stage transmission in planetary design for a bicycle or pedelec is known. The multi-speed transmission comprises two main gear sets and an upstream gear set and a rear-mounted gear set. Furthermore, four overrunning clutches and four brakes are provided in order to achieve 16 gear steps. With the usual stationary gear ratios of the individual gear sets between -2.4 and -1.6, the multi-stage gearbox delivers a large gear ratio spread of approx. 6, which is favorable for mountain bikes, with constant gradation. It has been shown that for a smaller gear ratio spread of approx. 2.6, which is necessary for racing bikes, for example, complex individual wheel sets with stepped planets are necessary in order to achieve the aforementioned gear ratio spread.

The present invention is based on the object of proposing an efficient multi-step transmission and a bicycle or pedelec with the multi-step transmission, which implement a low gear ratio common for road bikes of about 2.6 with almost constant gear steps in a structurally simple manner.

This object is achieved by the features of patent claims 1 and 21, with advantageous and claimed developments can be found in the subclaims and the description as well as the drawings.

Thus, a planetary multi-stage transmission is proposed for a bicycle or a pedelec with a transmission input shaft as the drive and a transmission output shaft as the output. The multi-speed transmission comprises at least three planetary gear sets, with at least three overrunning clutches and at least three brakes being provided for realizing at least 8 gears or gear steps. In order to realize a structurally particularly simple multi-speed transmission, it is provided that a second element of the first planetary gear set is coupled as an input element directly or via at least one further element to the transmission input shaft, a first element of the first planetary gear set as an output element with the transmission output shaft directly or via at least one further element is coupled. Furthermore, a third element of the first planetary gear set is connected as a coupling element with a second element of the second planetary gear set, wherein a first element of the second planetary gear set can be fixed via a first brake and wherein the first element of the second planetary gear set is connected to the second element of the first via a first overrunning clutch Planetary gear set is connectable. In addition, a third element of the second planetary gear set is connected to a second element of a third planetary gear set, a first element of the third planetary gear set being lockable via a second brake and the first element of the third planetary gear set being connectable to the first element of the first planetary gear set via a second overrunning clutch is. Furthermore, a third element of the third planetary gear set can be connected to the first element of the first planetary gear set via a third overrunning clutch, the third element of the third planetary gear set being lockable via a third brake.

Due to the proposed interconnection of the three planetary gear sets in the multi-speed transmission, at least twice four or eight different speeds or ratios can be generated on the first planetary gear set via the second element of the second planetary gear set on the first planetary gear set, since the connection of the first element of the second planetary gear set and the provided brakes and freewheels already two speeds and by connecting the third element of the second planetary gear set to the second element of the third planetary gear set, four speeds can be achieved. The individual gear sets of the proposed multi-speed transmission that are interconnected or interconnected in this way are not only structurally simple and require as little space as possible, but also implement a multi-speed transmission with a low gear ratio spread of approx can be used. Furthermore, with the proposed particularly efficient multi-speed transmission with a low gear ratio spread with only three planetary gear sets and only three overrunning clutches as well as only three brakes eight gears or gear steps are realized, the stationary gear ratio of the planetary gear sets of the multi-speed transmission approximately between -2.4 and -1.5, preferably lie between -2.0 and -1.5.

As part of an advantageous development of the invention, the number of gears can be doubled in the proposed multi-speed transmission by adding a further planetary gear set as an upstream or downstream gearset with an additional upstream or downstream brake and an upstream or downstream freewheel clutch, so that sixteen gears can be shifted. In the case of the fourth individual gear set as an upstream or downstream gear set, an input element, an output element and a coupling element can be provided, the coupling element being fixable via a series brake or a downstream brake and via an upstream freewheel clutch or upstream freewheel clutch of the upstream gear set or the downstream gear set can be locked. The input element of the transfer gear set is connected to the drive or the transmission input shaft, the output element of the transfer gear set being connected to the input element of the first planetary gear set and coupling it on the drive side. The input element of the rear-mounted gear set is connected to the output element of the first planetary gear set, the output element of the rear-mounted gear set being connected to the output or the transmission output shaft and thus coupling the first planetary gear set on the output side.

A preferred embodiment of the invention can provide that at least one of the individual gear sets provided is designed as a minus planetary gear set, which results in an arrangement that is particularly advantageous in terms of installation space. It is also conceivable that one or more of the individual gear sets are designed as plus planetary gear sets.

A minus planetary gear set can preferably be converted into a plus planetary gear set if the planetary gear carrier and ring gear connection on this gear set are interchanged and the stationary gear ratio is increased by 1. A minus planetary gear set has rotatably mounted planet gears on its planetary gear carrier, which mesh with the sun gear and the ring gear of this planetary gear set, so that the ring gear rotates in the opposite direction to the sun gear direction when the planet gear carrier is held and the sun gear is rotating. A plus planetary gear set has inner and outer planetary gears that are rotatably mounted on its planetary gear carrier and are in meshing engagement with one another, the sun gear of this planetary gear set meshing with the inner planetary gears and the ring gear of this planetary gear set with the outer planetary gears, so that the ring gear rotates when the planetary gear carrier is held and rotating Sun gear rotates in the same direction of rotation as the sun gear.

For those skilled in the art, this means that in the case of the individual gear sets designed as minus planetary gear sets, a first element is designed as a ring gear, a second element is designed as a planetary gear carrier and a third element is designed as a sun gear. Furthermore, this means that in a single gear set designed as a plus planetary gear set, the first element is designed as a planetary gear carrier, the second element is designed as a ring gear and the third element is designed as a sun gear.

In the context of the invention, it is provided that in a third planetary gear set designed as a minus planetary gear set, a split sun gear or a split ring gear is provided in order to make it compatible with the other planetary gear sets in a space-saving manner. The divided sun gear has a first sun gear part and a second sun gear part which are operatively connected to one another, the divided ring gear having a first ring gear part and a second ring gear part which are also operatively connected to one another. When using a split sun gear instead of a split ring gear, there is the advantage of lower construction costs. Alternatively, it would be conceivable to use the third planetary gear set as a plus planetary gear set with z. B. to use a stationary gear ratio of about 3 to simplify a bond with the other planetary gear sets due to the interchanging of the ring gear and the planetary gear carrier.

In order to enable electrical support in addition to the manual drive by the driver, it can be provided in the case of the multi-step transmission according to the invention that at least one electrical machine or the like is provided. The electrical machine can, for example, be connected to the transmission input shaft, the transmission output shaft and / or to other shafts of the transmission directly or via one or more transmission stages, chains, toothed belts or the like. For this purpose, a switching element, such as. B. an overrunning clutch or the like can be used. This has the advantage that while pedaling when the e-machine drive is switched off, no drag torques occur due to an electric machine driven by the pedaling. With a connection z. B. via a gear stage, a translation z. B. be realized slowly.

When executing the multi-speed transmission z. B. as an electrically assisted bottom bracket drive, an overrunning clutch can preferably be implemented between the bottom bracket crankshaft and the transmission input. This has the advantage that a connected electrical machine can continue to rotate without the pedals of the bottom bracket crankshaft rotating.

Another aspect of the present invention is to claim a bicycle or a pedelec or the like with the multi-step transmission described above, with the advantages already described and other advantages resulting.

• 1 eine schematische Ansicht einer ersten Ausführungsvariante eines erfindungsgemäßen Mehrstufengetriebes mit drei Planetenradsätzen zum Realisieren von acht Gängen;
• 2 eine schematische Ansicht einer zweiten Ausführungsvariante mit drei Planetenradsätzen sowie einem vorgeschalteten Vorschaltradsatz zum Realisieren von sechzehn Gängen;
• 3 eine schematische Ansicht einer dritten Ausführungsvariante des Mehrstufengetriebes mit drei Planetenradsätzen sowie einem nachgeschalteten Nachschaltradsatz zum Realisieren von sechzehn Gängen;
• 4 eine schematische Ansicht einer vierten Ausführungsvariante des Mehrstufengetriebes mit hinsichtlich der dritten Ausführungsvariante geänderter axialer Reihenfolge der Planetenradsätze; und
• 5 ein Schaltschema für die zweite, dritte und vierte Ausführungsvariante des Mehrstufengetriebes.

The present invention is further explained below with reference to the drawings. Show it:

• 1 a schematic view of a first embodiment of a multi-speed transmission according to the invention with three planetary gear sets for realizing eight gears;
• 2 a schematic view of a second embodiment variant with three planetary gear sets as well as an upstream transfer gear set for realizing sixteen gears;
• 3 a schematic view of a third embodiment of the multi-speed transmission with three planetary gear sets and a downstream rear gear set for realizing sixteen gears;
• 4th a schematic view of a fourth variant of the multi-speed transmission with a modified axial sequence of the planetary gear sets with respect to the third variant; and
• 5 a shift pattern for the second, third and fourth variant of the multi-speed transmission.

In the 1 until 4th different design variants of a multi-speed transmission according to the invention are shown as an example of a bottom bracket drive in a coaxial construction of a bicycle or pedelec, with FIG 5 a shift pattern for the gears G1 until G8 according to a first embodiment variant 1 and for the aisles G1 until G16 for a second to fourth variant according to 2 until 4th with the associated gear ratios and gear steps as well as the gear ratio spread are specified.

In the circuit diagram according to 5 are the individual states of the as brakes B1 , B2 , B3 , BV , BN and the overrunning clutches F1 , F2 , F3 , FV , FN executed switching elements indicated, with the brakes B1 , B2 , B3 , BV , BN a circle indicates the closed state and a cross the open or disengaged state, while with the overrunning clutches F1 , F2 , F3 , FV , FN a circle indicates the reverse drive state and a line indicates the overtaking drive state. The overrunning operation or the overrunning drive state of an overrunning clutch F1 , F2 , F3 , FV , FN means that the freewheel does not block and therefore does not transmit any torque. An overrunning clutch F1 , F2 , F3 , FV , FN can be in an overrunning drive if one of the elements connected to the freewheel rotates so fast that the freewheel cannot lock. The reverse direction state in an overrunning clutch F1 , F2 , F3 , FV , FN means that the freewheel blocks and thus transmits a moment.

Regardless of the particular variant of the multi-stage transmission, it is provided that the multi-stage transmission in planetary design can be used for a bicycle, a pedelec or the like. The multi-stage transmission includes a transmission input shaft 1 as a drive, which in the 1 until 4th is designed for example as a bottom bracket crankshaft, and a transmission output shaft 2 as output, which z. B. can be designed as a chainring or chain or toothed belt wheel.

Depending on the variant, the multi-speed transmission includes at least one first planetary gear set RS1 , a second planetary gear set RS2 and a third planetary gear set RS3 . In addition, there are at least three one-way clutches F1 , F2 , F3 and at least three brakes or freewheel brakes B1 , B2 , B3 as shift elements for realizing at least eight gears G1 , G2 , G3 , G4 , G5 , G6 , G7 , G8 intended.

Regardless of whether minus or plus planetary gear sets are provided in the proposed multi-stage transmission, the result is that a second element of the first planetary gear set RS1 as an input element directly or via at least one additional element with the transmission input shaft 1 is connected, wherein a first element of the first planetary gear set RS1 as an output element directly or via at least one further element with the transmission output shaft 2 connected is. Furthermore, there is a third element of the first planetary gear set RS1 as a coupling element with a second element of the second planetary gear set RS2 connected, wherein a first element of the second planetary gear set RS2 via a first brake B1 can be fixed and wherein the first element of the second planetary gear set RS2 via a first one-way clutch F1 with the second element of the first planetary gear set RS1 is connectable. There is also a third element of the second planetary gear set RS2 with a second element of a third planetary gear set RS3 connected, with a first element of the third planetary gear set RS3 via a second brake B2 can be fixed and wherein the first element of the third planetary gear set RS3 via a second one-way clutch F2 with the first element of the first planetary gear set RS1 is connectable. There is also a third element of the third planetary gear set RS3 via a third one-way clutch F3 with the first element of the first planetary gear set RS1 connectable, the third element of the third planetary gear set RS3 a third brake B3 is determinable.

The rule here is that with a minus planetary gear set, the first element is a ring gear HR1 , HR2 , HR3 , HR3A , HR3B , HRV , HRN , the second element as a planet carrier PT1 , PT2 , PT3 , PTV , PTN and the third element as a sun gear SR1 , SR2 , SR3 , SR3A , SR3B , SRV , SRN are executed, and that in a plus planetary gear set, the first element as a planetary gear carrier PT1 , PT2 , PT3 , PTV , PTN , the second element as a ring gear HR1 , HR2 , HR3 , HR3A , HR3B , HRV , HRN and the third element as a sun gear SR1 , SR2 , SR3 , SR3A , SR3B , SRV , SRN are executed.

Regardless of the variant embodiment, the first planetary gear set RS1 a standard translation i01 of preferably about -1.78, the second planetary gear set RS2 a standard translation i02 of about -1.67 and the third planetary gear set RS3 a standard translation i03 from about -2.00 to. If, depending on the variant, an upstream gear set VRS or a rear wheel set NRS is present, the transfer gear set VRS and the rear wheel set NRS a stationary ratio i0V resp. ion of preferably about -1.50.

The various gear set arrangements of the multi-speed transmission according to the invention thus enable a small overall spread of approximately 2.6, so that use preferably for racing bicycles or racing pedelecs is particularly advantageous.

A first variant of the multi-speed transmission as an 8-speed variant is shown in 1 shown in the axial sequence of the first planetary gear set RS1 , the second planetary gear set RS2 and the third planetary gear set RS3 are each provided as a minus planetary gear set.

In the first variant, it is provided in detail that the transmission input shaft 1 with a planet carrier PT1 of the first planetary gear set RS1 is connected, with a sun gear SR1 of the first planetary gear set RS1 with a planet carrier PT2 of the second planetary gear set RS2 is connected and wherein a ring gear HR1 of the first planetary gear set RS1 with the transmission output shaft 2 connected is. There is also a ring gear HR2 of the second planetary gear set RS2 over the first brake B1 can be fixed, the ring gear HR2 of the second planetary gear set RS2 via the first one-way clutch F1 with the planet carrier PT1 of the first planetary gear set RS1 is connectable and a sun gear SR2 of the second planetary gear set RS2 with a planet carrier PT3 of the third planetary gear set RS3 connected is. There is also a ring gear HR3 of the third planetary gear set RS3 via a second brake B2 can be fixed, the ring gear HR3 of the third planetary gear set RS3 via a second one-way clutch F2 with the ring gear HR1 of the first planetary gear set RS1 is connectable, with a split sun gear SR3A , SR3B in the third planetary gear set RS3 with a first sun gear part SR3A and a second sun gear part SR3B is provided, the first sun gear part SR3A of the third planetary gear set RS3 about the third brake B3 can be fixed and wherein the second sun gear part SR3B of the third planetary gear set RS3 via the third overrunning clutch F3 with the ring gear HR1 of the first planetary gear set RS1 is connectable.

The first variant according to 1 realized without using an upstream or downstream gear set VRS , NRS an 8-speed bottom bracket transmission with a very small overall spread. The gear ratios and gear steps are in 5 for the aisles G1 until G8 specified. The first variant is therefore particularly suitable for use in a time trial machine. To establish the connection between the sun gear SR2 of the second planetary gear set RS2 and the planet carrier PT3 of the third planetary gear set RS3 is a split sun gear SR3A , SR3B intended.

A second variant of the multi-speed transmission as a 16-speed variant is shown in 2 shown in which an upstream gearset in axial order VRS , the first planetary gear set RS1 , the second planetary gear set RS2 and the third planetary gear set RS3 are each provided as a minus planetary gear set. To establish the bond between the sun gear SR2 of the second planetary gear set RS2 and the planet carrier PT3 of the third planetary gear set RS3 In contrast to the first variant, it is a split ring gear HR3A , HR3B intended.

In the second variant, it is provided in detail that the transmission input shaft 1 with a planet carrier PTV of the transfer gear set VRS is connected, with a sun gear SRV of the transfer gear set VRS via the intermediate brake BV can be fixed and wherein the sun gear SRV of the transfer gear set VRS via the upstream freewheel clutch FV with the planet carrier PTV of the transfer gear set VRS is connectable for interlocking. There is also a ring gear HRV of the transfer gear set VRS with the planet carrier PT1 of the first planetary gear set RS1 connected, the ring gear HR1 of the first planetary gear set RS1 with the transmission output shaft 2 is connected and wherein the sun gear SR1 of the first planetary gear set RS1 with the planet carrier PT2 of the second planetary gear set RS2 connected is. In addition, the ring gear is HR2 of the second planetary gear set RS2 over the first brake B1 can be fixed, the ring gear HR2 of the second planetary gear set RS2 via the first one-way clutch F1 with the planet carrier PT1 of the first planetary gear set RS1 is connectable and wherein the sun gear SR2 of the second planetary gear set RS2 with the planet carrier PT3 of the third planetary gear set RS3 connected is. Further is the sun gear SR3 of the third planetary gear set RS3 about the third brake B3 fixable, the sun gear SR3 via the third overrunning clutch F3 with the ring gear HR1 of the first planetary gear set RS1 is connectable. There is also a split ring gear HR3A , HR3B of the third planetary gear set RS3 with a first ring gear part HR3A and a second ring gear part HR3B provided, the first ring gear part HR3A of the third planetary gear set RS3 via the second one-way clutch F2 with the ring gear HR1 of the first planetary gear set RS1 is connectable and wherein the second ring gear part HR3B the third Planetary gear set RS3 over the second brake B2 is determinable.
Due to the selected axial gear set sequence VRS-RS1-RS2-RS3 results in the second variant according to 2 a wide bearing base for the transmission output shaft 2 . By coupling the with the transmission input shaft 1 connected planet carrier PTV of the transfer gear set VRS with the sun gear SRV of the transfer gear set VRS via the upstream freewheel clutch FV this results in a space-saving arrangement radially between the sun gear SRV and the transmission input shaft 1 .

A third variant of the multi-speed transmission as a 16-speed variant is shown in 3 shown in the axial order of the first planetary gear set RS1 , the second planetary gear set RS2 , the third planetary gear set RS3 and a rear-wheel set NRS are each provided as a minus planetary gear set. The selected axial gear set sequence RS1-RS2-RS3-NRS enables lower input speeds for the three planetary gear sets RS1 , RS2 , RS3 .

In the third variant, it is provided in detail that the transmission input shaft 1 with the planet carrier PT1 of the first planetary gear set RS1 is connected, the ring gear HR1 of the first planetary gear set RS1 with a planet carrier PTN of the rear wheel set NRS is connected and wherein the sun gear SR1 of the first planetary gear set RS1 with the planet carrier PT2 of the second planetary gear set RS2 connected is. Furthermore, the ring gear is HR2 of the second planetary gear set RS2 over the first brake B1 can be fixed, the ring gear HR2 of the second planetary gear set RS2 via the first one-way clutch F1 with the planet carrier PT1 of the first planetary gear set RS1 is connectable and wherein the sun gear SR2 of the second planetary gear set RS2 with the planet carrier PT3 of the third planetary gear set RS3 connected is. Furthermore, the ring gear is HR3 of the third planetary gear set RS3 over the second brake B2 can be fixed, the ring gear HR3 of the third planetary gear set RS3 via the second one-way clutch F2 with the ring gear HR1 of the first planetary gear set RS1 is connectable. The split sun gear SR3A , SR3B of the third planetary gear set RS3 is with the first sun gear part SR3A about the third brake B3 can be fixed and with the second sun gear part SR3B of the third planetary gear set RS3 via the third overrunning clutch F3 with the ring gear HR1 of the first planetary gear set RS1 connectable. A sun gear SRN of the rear wheel set NRS is about the secondary brake BN fixable, the sun gear SRN of the rear wheel set NRS via the additional freewheel clutch FN with the ring gear HRN of the rear wheel set NRS can be connected for interlocking and wherein the ring gear HRN of the rear wheel set NRS with the transmission output shaft 2 connected is.

As with the first variant, the third variant also has a split sun gear SR3A , SR3B provided, which opposite a split ring gear HR3A , HR3B realized a lower construction cost. By locking the sun gear SRN and ring gear HRN of the rear wheel set NRS via the additional freewheel clutch FN the result is a lower supporting torque on the secondary freewheel clutch FN compared to other blocking variants.

A fourth variant of the multi-speed transmission as a 16-speed variant is shown in 4th shown in the axial sequence of the second planetary gear set RS2 , the third planetary gear set RS3 , the first planetary gear set RS1 and the rear wheel set NRS are each provided as a minus planetary gear set. The selected axial gear set sequence RS2-RS3-RS1-NRS realizes an approximately central introduction of the main torque via the transmission input shaft 1 , which optimizes acoustic decoupling in the multi-speed transmission. By relocating the rear wheel set NRS Radially outwards within a chainring of the bicycle or pedelec, a reduction in the overall length within the bottom bracket transmission is made possible.

In detail, it is provided in the fourth variant that the transmission input shaft 1 with the planet carrier PT1 of the first planetary gear set RS1 is connected, the sun gear SR1 of the first planetary gear set RS1 with the planet carrier PT2 of the second planetary gear set RS2 connected is. The ring gear HR1 of the first planetary gear set RS1 is with the planet carrier PTN of the rear wheel set NRS connected, the ring gear HR2 of the second planetary gear set RS2 over the first brake B1 can be fixed and wherein the ring gear HR2 of the second planetary gear set RS2 via the first one-way clutch F1 with the planet carrier PT1 of the first planetary gear set RS1 is connectable. The sun gear SR2 of the second planetary gear set RS2 is with the planet carrier PT3 of the third planetary gear set RS3 connected, the ring gear HR3 of the third planetary gear set RS3 over the second brake B2 can be fixed and wherein the ring gear HR3 of the third planetary gear set RS3 via the second one-way clutch F2 with the ring gear HR1 of the first planetary gear set RS1 is connectable. The split sun gear SR3A , SR3B of the third planetary gear set RS3 is with the first sun gear part SR3A about the third brake B3 can be fixed and the second sun gear part SR3B of the third planetary gear set RS3 is via the third one-way clutch F3 with the ring gear HR1 of the first planetary gear set RS1 connectable. The ring gear HRN of the rear wheel set NRS is with the transmission output shaft 2 connected, the sun gear SRN of the rear wheel set NRS via the additional brake BN can be fixed and wherein the planet carrier PTN of the rear wheel set NRS via the additional freewheel clutch FN with the ring gear HRN of the rear wheel set NRS is connectable for interlocking.

In the fourth variant embodiment, the rear-mounted gear set is blocked NRS by connecting planetary gear carriers PTN and ring gear HRN of the rear wheel set NRS via the additional freewheel clutch FN . This has the advantage that when the secondary brake is open BN the transmission output torque is directed directly to the chainring of the bicycle or pedelec, with the rear-wheel set NRS remains load-free and thus statically unloaded.

In 5 is a circuit diagram of the first embodiment according to 1 for the aisles G1 until G8 and for the second, third and fourth variant embodiment according to 2 until 4th for the aisles G1 until G16 shown as an example.

From the circuit diagram according to 5 For the variant embodiments described above, it results that for shifting a first gear G1 the first brake B1 , the second brake B2 , the third brake B3 and the upstream or downstream brake BV , BN are open, the first one-way clutch F1 , the second one-way clutch F2 , the third one-way clutch F3 and the upstream or downstream freewheel clutch FV , FN are in the reverse direction. For shifting a second gear G2 are the first brake B1 , the second brake B2 and the upstream or downstream brake BV , BN open and the third brake B3 closed, the first one-way clutch F1 , the second one-way clutch F2 and the upstream or downstream freewheel clutch FV , FN in the reverse direction and the third overrunning clutch F3 are in the overtaking state. For shifting a third gear G3 are the first brake B1 , the third brake B3 and the upstream or downstream brake BV , BN open and the second brake B2 closed, the first one-way clutch F1 , the third one-way clutch F3 and the upstream or downstream freewheel clutch FV , FN in the reverse direction and the second one-way clutch F2 are in the overtaking state. For shifting a fourth gear G4 are the first brake B1 and the upstream or downstream brake BV , BN open and the second brake B2 and the third brake B3 closed, the first one-way clutch F1 and the upstream or downstream freewheel clutch FV , FN in the reverse direction and the second one-way clutch F2 and the third one-way clutch F3 are in the overtaking state. For shifting a fifth gear G5 are the first brake B1 closed and the second brake B2 , the third brake B3 and the upstream or downstream brake BV , BN opened, the first one-way clutch F1 in overrunning state and the second overrunning clutch F2 , the third one-way clutch F3 and the upstream or downstream freewheel clutch FV , FN are in the reverse direction. For shifting a sixth gear G6 are the first brake B1 and the third brake B3 closed and the second brake B2 and the upstream or downstream brake BV , BN opened, the first one-way clutch F1 and the third one-way clutch F3 in the overrunning state and the second overrunning clutch F2 and the upstream or downstream freewheel clutch FV , FN are in the reverse direction. For shifting a seventh gear G7 are the first brake B1 and the second brake B2 closed and the third brake B3 and the upstream or downstream brake BV , BN opened, the first one-way clutch F1 and the second one-way clutch F2 in the overrunning state and the third overrunning clutch F3 and the upstream or downstream freewheel clutch FV , FN are in the reverse direction. For shifting an eighth gear G8 are the first brake B1 , the second brake B2 and the third brake B3 closed and the upstream or downstream brake BV , BN opened, the first one-way clutch F1 , the second one-way clutch F2 and the third one-way clutch F3 in the overrunning state and the upstream or downstream overrunning clutch FV , FN are in the reverse direction. For shifting a ninth gear G9 are the first brake B1 , the second brake B2 and the third brake B3 open and the primary or secondary brake BV , BN closed, the first one-way clutch F1 , the second one-way clutch F2 and the third one-way clutch F3 in the reverse direction and the upstream or downstream freewheel clutch FV , FN are in the overtaking state. For shifting a tenth gear G10 are the first brake B1 and the second brake B2 open and the third brake B3 and the upstream or downstream brake BV , BN closed, the first one-way clutch F1 and the second one-way clutch F2 in the reverse direction and the third overrunning clutch F3 and the upstream or downstream freewheel clutch FV , FN are in the overtaking state. For shifting an eleventh gear G11 are the first brake B1 and the third brake B3 open and the second brake B2 and the upstream or downstream brake BV , BN closed, the first one-way clutch F1 and the third one-way clutch F3 in the reverse direction and the second one-way clutch F2 and the upstream or downstream freewheel clutch FV , FN are in the overtaking state. For shifting a twelfth gear G12 are the first brake B1 open and the second brake B2 , the third brake B3 and the upstream or downstream brake BV , BN closed, being the first One-way clutch F1 in the reverse direction and the second one-way clutch F2 , the third one-way clutch F3 and the upstream or downstream freewheel clutch FV , FN are in the overtaking state. For shifting a thirteenth gear G13 are the first brake B1 and the upstream or downstream brake BV , BN closed and the second brake B2 and the third brake B3 opened, the first one-way clutch F1 and the upstream or downstream freewheel clutch FV , FN in the overrunning state and the second overrunning clutch F2 and the third one-way clutch F3 are in the reverse direction. For shifting a fourteenth gear G14 are the first brake B1 , the third brake B3 and the upstream or downstream brake BV , BN closed and the second brake B2 opened, the first one-way clutch F1 , the third one-way clutch F3 and the upstream or downstream freewheel clutch FV , FN in the overrunning state and the second overrunning clutch F2 are in the reverse direction. For shifting a fifteenth gear G15 are the first brake B1 , the second brake B2 and the upstream or downstream brake BV , BN closed and the third brake B3 opened, the first one-way clutch F1 , the second one-way clutch F2 and the upstream or downstream freewheel clutch FV , FN in the overrunning state and the third overrunning clutch F3 are in the reverse direction. For shifting a sixteenth gear G16 are the first brake B1 , the second brake B2 , the third brake B3 and the upstream or downstream brake BV , BN closed, the first one-way clutch F1 , the second one-way clutch F2 , the third one-way clutch F3 and the upstream or downstream freewheel clutch FV , FN are in the overtaking state.

This results in the ratios and the gear steps for the gears G1 until G16 . The gear steps are comparable to the preferred gear step of around 1.066 with a derailleur when changing from a 16-tooth pinion to a 15-tooth pinion on the ring gear.

List of reference symbols

1

Transmission input shaft or bottom bracket crankshaft

2

Transmission output shaft

B1

first brake

B2

second brake

B3

third brake

BV

Upstream brake

BN

Secondary brake

F1

first one-way clutch

F2

second overrunning clutch

F3

third overrunning clutch

FV

Upstream freewheel clutch

FN

Additional overrunning clutch

G1

first course

G2

second gear

G3

third gear

G4

fourth gear

G5

fifth gear

G6

sixth gear

G7

seventh gear

G8

eighth gear

G9

ninth gear

G10

tenth gear

G11

eleventh gear

G12

twelfth gear

G13

thirteenth gear

G14

fourteenth gear

G15

fifteenth gear

G16

sixteenth gear

HR1

Ring gear of the first planetary gear set

HR2

Ring gear of the second planetary gear set

HR3

Ring gear of the third planetary gear set

HR3A

first ring gear part of the split ring gear

HR3B

second ring gear part of the split ring gear

HRV

Ring gear of the transfer gear set

HRN

Ring gear of the rear-mounted gear set

PT1

Planet carrier of the first planetary gear set

PT2

Planet carrier of the second planetary gear set

PT3

Planet carrier of the third planetary gear set

PTV

Planetary gear carrier of the transfer gear set

PTN

Planetary gear carrier of the secondary gear set

RS1

first planetary gear set

RS2

second planetary gear set

RS3

third planetary gear set

VRS

Transfer gear set

NRS

Rear wheel set

SR1

Sun gear of the first planetary gear set

SR2

Sun gear of the second planetary gear set

SR3

Sun gear of the third planetary gear set

SR3A

first sun gear part of the split sun gear

SR3B

second sun gear part of the split sun gear

SRV

Sun gear of the transfer gear set

SRN

Sun gear of the rear gear set

i01

Stationary gear ratio of the first planetary gear set

i02

Stationary gear ratio of the second planetary gear set

i03

Stationary gear ratio of the third planetary gear set

iOV

Stationary translation of the transfer gear set

ion

Stationary translation of the rear wheel set

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent literature cited

• DE 102018208380 [0002]

Claims (21)

Multi-stage transmission in planetary design for a bicycle or a pedelec, with a transmission input shaft (1) as the drive and a transmission output shaft (2) as the output, with at least three planetary gear sets (RS1, RS2, RS3, VRS, NRS), with at least three overrunning clutches (F1, F2, F3, FV, FN) and at least three brakes (B1, B2, B3, BV, BN) to achieve at least eight gears (G1, G2, G3, G4, G5, G6, G7, G8, G9, G10, G11, G12, G13, G14, G15, G16) are provided, a second element of the first planetary gear set (RS1) being connected as an input element directly or via at least one further element to the transmission input shaft (1), a first element of the first planetary gear set (RS1) is connected as an output element directly or via at least one further element with the transmission output shaft (2), a third element of the first planetary gear set (RS1) being connected as a coupling element to a second element of the second planetary gear set (RS2), a first s element of the second planetary gear set (RS2) can be fixed via a first brake (B1), the first element of the second planetary gear set (RS2) being connectable to the second element of the first planetary gear set (RS1) via a first overrunning clutch (F1), whereby a The third element of the second planetary gear set (RS2) is connected to a second element of a third planetary gear set (RS3), a first element of the third planetary gear set (RS3) being fixable via a second brake (B2), the first element of the third planetary gear set (RS3 ) can be connected to the first element of the first planetary gear set (RS1) via a second overrunning clutch (F2), a third element of the third planetary gear set (RS3) being connectable to the first element of the first planetary gear set (RS1) via a third overrunning clutch (F3) and wherein the third element of the third planetary gear set (RS3) can be fixed via a third brake (B3). Multi-speed transmission according to Claim 1 , characterized in that an upstream gearset (VRS) or a rear-mounted gearset (NRS) is provided as a further planetary gear set. Multi-speed transmission according to Claim 2 , characterized in that a second element of the transfer gear set (VRS) is connected as an input element to the transmission input shaft (1), that a first element of the transfer gear set (VRS) is connected as an output element to the second element of the first planetary gear set (RS1) and that a The third element of the transfer gearset (VRS) can be fixed via an upstream brake (BV) and that the third element of the upstream gearset (VRS) is connected to the second or third element of the upstream gearset (VRS) or the second element of the transfer gearset (VRS) via an upstream freewheel clutch (FV) ) can be connected to the first element of the transfer gearset (VRS) for interlocking. Multi-speed transmission according to Claim 2 , characterized in that a second element of the rear-wheel set (NRS) is connected as an input element with the first element of the first planetary gear set (RS1), that a first element of the rear-wheel set (NRS) is connected as an output element with the transmission output shaft (2), that a The third element of the rear-mounted gear set (NRS) can be fixed with a rear-mounted brake (BN) and that the third element of the rear-mounted gear set (NRS) is connected to the first or second element of the rear-mounted gear set (NRS) or the second element of the rear-mounted gear set (NRS) via a rear-mounted freewheel clutch (FN) ) can be connected to the first element of the rear-wheel set (NRS) for interlocking. Multi-speed transmission according to one of the preceding claims, characterized in that the first planetary gear set (RS1) and / or the second planetary gear set (RS2) and / or the third planetary gear set (RS3) and / or the front gear set (VRS) or the rear gear set (NRS), respectively are designed as a minus planetary gear set. Multi-speed transmission according to Claim 5 , characterized in that in the case of a minus planetary gear set, the first element as a ring gear (HR1, HR2, HR3, HR3A, HR3B, HRV, HRN), the second element as a planetary gear carrier (PT1, PT2, PT3, PTV, PTN) and the third Element as a sun gear (SR1, SR2, SR3, SR3A, SR3B, SRV, SRN) are designed. Multi-speed transmission according to one of the preceding claims, characterized in that the first planetary gear set (RS1) and / or the second planetary gear set (RS2) and / or the third planetary gear set (RS3) and / or the front gear set (VRS) or the rear gear set (NRS), respectively are designed as a plus planetary gear set. Multi-speed transmission according to Claim 7 , characterized in that with a plus planetary gear set, the first element as a planetary gear carrier (PT1, PT2, PT3, PTV, PTN), the second element as a ring gear (HR1, HR2, HR3, HR3A, HR3B, HRV, HRN) and the third Element as a sun gear (SR1, SR2, SR3, SR3A, SR3B, SRV, SRN) are designed. Multi-step transmission according to one of the preceding claims, characterized in that a split sun gear (SR3A, SR3B) with a first sun gear part (SR3A) and with a second sun gear part (SR3B) is provided in the third planetary gear set (RS3), the first Sun gear part (SR3A) and the second sun gear part (SR3B) are operatively connected to one another. Multi-speed transmission according to one of the Claims 1 until 8th , characterized in that the third planetary gear set (RS3) has a split ring gear (HR3A, HR3B) with a first ring gear part (HR3A) and a second ring gear part (HR3B), the first ring gear part (HR3A) and the second ring gear part (HR3B ) are operatively connected to each other. Multi-speed transmission according to one of the preceding claims, characterized in that the axial sequence of the individual gear sets is selected such that the transfer gear set (VRS) as the first individual gear set, the first planetary gear set (RS1) as the second single gear set, the second planetary gear set (RS2) and the third single gear set the third planetary gear set (RS3) are arranged as the fourth individual gear set. Multi-speed transmission according to one of the Claims 1 until 10 , characterized in that the axial sequence of the individual gear sets is selected such that the first planetary gear set (RS1) as the first single gear set, the second planetary gear set (RS2) as the second single gear set, the third planetary gear set (RS3) as the third single gear set and the rear-mounted gear set as the fourth single gear set (NRS) are arranged. Multi-speed transmission according to one of the Claims 1 until 10 , characterized in that the axial sequence of the individual gear sets is chosen such that the second planetary gear set (RS2) as the first single gear set, the third planetary gear set (RS3) as the second single gear set, the first planetary gear set (RS1) as the third single gear set and the secondary gear set as the fourth single gear set (NRS) are arranged. Multi-stage transmission according to one of the preceding claims, characterized in that the transmission input shaft (1) is connected to a planetary gear carrier (PT1) of the first planetary gear set (RS1), that a sun gear (SR1) of the first planetary gear set (RS1) is connected to a planetary gear carrier (PT2) of the second planetary gear set (RS2) is connected, that a ring gear (HR1) of the first planetary gear set (RS1) is connected to the transmission output shaft (2) that a ring gear (HR2) of the second planetary gear set (RS2) can be fixed via the first brake (B1) that the ring gear (HR2) of the second planetary gear set (RS2) can be connected to the planetary gear carrier (PT1) of the first planetary gear set (RS1) via the first overrunning clutch (F1), that a sun gear (SR2) of the second planetary gear set (RS2) can be connected to a planetary gear carrier (PT3) of the third planetary gear set (RS3) is connected, that a ring gear (HR3) of the third planetary gear set (RS3) can be fixed via a second brake (B2), that the Hoh lrad (HR3) of the third planetary gear set (RS3) can be connected to the ring gear (HR1) of the first planetary gear set (RS1) via a second overrunning clutch (F2) and that the split sun gear (SR3A, SR3B) of the third planetary gear set (RS3) is a first sun gear part (SR3A) and a second sun gear part (SR3B), wherein the first sun gear part (SR3A) of the third planetary gear set (RS3) can be fixed via the third brake (B3) and the second sun gear part (SR3B) of the third planetary gear set (RS3) via the third overrunning clutch (F3) can be connected to the ring gear (HR1) of the first planetary gear set (RS1). ( 1 ) Multi-speed transmission according to one of the Claims 1 until 13th , characterized in that the transmission input shaft (1) is connected to a planetary gear carrier (PTV) of the transfer gear set (VRS), that a sun gear (SRV) of the transfer gear set (VRS) can be fixed via the front-mounted brake (BV), that the sun gear (SRV) of the transfer gearset (VRS) can be connected to the planetary gear carrier (PTV) of the transfer gearset (VRS) via the upstream freewheel clutch (FV) so that a ring gear (HRV) of the transfer gearset (VRS) can be connected to the Planetary gear carrier (PT1) of the first planetary gear set (RS1) is connected, that the ring gear (HR1) of the first planetary gear set (RS1) is connected to the transmission output shaft (2), that the sun gear (SR1) of the first planetary gear set (RS1) is connected to the planetary gear carrier ( PT2) of the second planetary gear set (RS2) is connected, that the ring gear (HR2) of the second planetary gear set (RS2) can be fixed via the first brake (B1), that the ring gear (HR2) of the second planetary gear set (RS2) via the first overrunning clutch ( F1) can be connected to the planetary gear carrier (PT1) of the first planetary gear set (RS1), that the sun gear (SR2) of the second planetary gear set (RS2) is connected to the planetary gear carrier (PT3) of the third planetary gear set (RS3), that the sun gear (SR3) of the third planetary gear set (RS3) can be fixed via the third brake (B3) that the sun gear (SR3) can be connected to the ring gear (HR1) of the first planetary gear set (RS1) via the third overrunning clutch (F3), that ei n split ring gear (HR3A, HR3B) of the third planetary gear set (RS3) has a first ring gear part (HR3A) and a second ring gear part (HR3B), the first ring gear part (HR3A) of the third planetary gear set (RS3) via the second overrunning clutch (F2) with the ring gear (HR1) of the first planetary gear set (RS1) can be connected and the second ring gear part (HR3B) of the third planetary gear set (RS3) can be fixed via the second brake (B2). Multi-speed transmission according to one of the Claims 1 until 13th , characterized in that the transmission input shaft (1) is connected to the planetary gear carrier (PT1) of the first planetary gear set (RS1), that the ring gear (HR1) of the first planetary gear set (RS1) is connected to a planetary gear carrier (PTN) of the rear gear set (NRS) that the sun gear (SR1) of the first planetary gear set (RS1) is connected to the planetary gear carrier (PT2) of the second planetary gear set (RS2), that the ring gear (HR2) of the second planetary gear set (RS2) can be fixed via the first brake (B1), that the ring gear (HR2) of the second planetary gear set (RS2) can be connected to the planetary gear carrier (PT1) of the first planetary gear set (RS1) via the first overrunning clutch (F1), that the sun gear (SR2) of the second planetary gear set (RS2) with the planetary gear carrier ( PT3) of the third planetary gear set (RS3) is connected, that the ring gear (HR3) of the third planetary gear set (RS3) can be fixed via the second brake (B2), that the ring gear (HR3) of the third planetary gear set (RS3) via the second overrunning clutch (F2) with the ring gear (HR1) of the first planetary gear set (RS1) can be connected that the split sun gear (SR3A, SR3B) of the third planetary gear set (RS3) with the first sun gear part (SR3A) via the Third brake (B3) can be fixed and the second sun gear part (SR3B) of the third planetary gear set (RS3) can be connected to the ring gear (HR1) of the first planetary gear set (RS1) via the third overrunning clutch (F3), so that a sun gear (SRN) of the rear-mounted gear set (NRS) can be fixed via the secondary brake (BN) and that the sun gear (SRN) of the secondary gear set (NRS) can be connected via the secondary freewheel clutch (FN) to the ring gear (HRN) of the secondary gear set (NRS) for locking and that the ring gear (HRN ) of the rear-mounted gear set (NRS) is connected to the gearbox output shaft (2). ( 3 ) Multi-speed transmission according to one of the Claims 1 until 13th , characterized in that the transmission input shaft (1) is connected to the planetary gear carrier (PT1) of the first planetary gear set (RS1), that the sun gear (SR1) of the first planetary gear set (RS1) is connected to the planetary gear carrier (PT2) of the second planetary gear set (RS2) is that the ring gear (HR1) of the first planetary gear set (RS1) is connected to the planetary gear carrier (PTN) of the downstream gear set (NRS), that the ring gear (HR2) of the second planetary gear set (RS2) can be fixed via the first brake (B1), that the ring gear (HR2) of the second planetary gear set (RS2) can be connected to the planetary gear carrier (PT1) of the first planetary gear set (RS1) via the first overrunning clutch (F1), that the sun gear (SR2) of the second planetary gear set (RS2) with the planetary gear carrier ( PT3) of the third planetary gear set (RS3) is connected, that the ring gear (HR3) of the third planetary gear set (RS3) can be fixed via the second brake (B2), that the ring gear (HR3) of the third planetary gearsa tzes (RS3) via the second overrunning clutch (F2) with the ring gear (HR1) of the first planetary gear set (RS1) is that the split sun gear (SR3A, SR3B) of the third planetary gear set (RS3) with the first sun gear part (SR3A) via the Third brake (B3) can be fixed and the second sun gear part (SR3B) of the third planetary gear set (RS3) can be connected to the ring gear (HR1) of the first planetary gear set (RS1) via the third overrunning clutch (F3), so that the ring gear (HRN) of the rear-mounted gear set (NRS) is connected to the transmission output shaft (2), that the sun gear (SRN) of the rear-mounted gear set (NRS) can be fixed via the rear-mounted brake (BN) and that the planetary gear carrier (PTN) of the rear-mounted gear set (NRS) is connected via the rear-mounted freewheel clutch (FN) the ring gear (HRN) of the rear-mounted gear set (NRS) can be connected for interlocking. ( 4th ) Multi-speed transmission according to one of the preceding claims, characterized in that for shifting a first gear (G1) the first brake (B1), the second brake (B2), the third brake (B3) and the upstream or downstream brake (BV, BN) are open, the first one-way clutch (F1), the second one-way clutch (F2), the third one-way clutch (F3) and the upstream or downstream free-wheeling clutch (FV, FN) in the Are the reverse direction state, and / or that to shift a second gear (G2) the first brake (B1), the second brake (B2) and the upstream or downstream brake (BV, BN) are open and the third brake (B3) are closed, wherein the first overrunning clutch (F1), the second overrunning clutch (F2) and the upstream or downstream overrunning clutch (FV, FN) are in the reverse direction and the third overrunning clutch (F3) are in the overrunning state, and / or that for shifting a third gear (G3) the first brake (B1), the third brake (B3) and the upstream or downstream brake (BV, BN) are open and the second brake (B2) are closed, the first one-way clutch (F1), the third one-way clutch (F3) and the upstream or downstream freewheel clutch (FV, FN) is in the blocking direction and the second overrunning clutch (F2) is in the overrunning state, and / or that for shifting a fourth gear (G4) the first brake (B1) and the upstream or downstream brake (BV, BN) is open and the second brake (B2) and the third brake (B3) are closed, the first overrunning clutch (F1) and the upstream or downstream overrunning clutch (FV, FN) in the blocking direction and the second overrunning clutch (F2) and the third Overrunning clutch (F3) are in the overrunning state, and / or that to shift a fifth gear (G5) the first brake (B1) is closed and the second brake (B2), the third brake (B3) and the upstream or downstream brake (BV, BN) are open, the first one-way clutch (F1) in the overrunning state and the second one-way clutch (F2), the third one-way clutch (F3) and the upstream or downstream free-wheeling clutch (FV, FN) are in the blocking direction, and / or that for switching one sixth gear (G6) the first brake (B1) and the third brake (B3) closed and the second brake (B2) and the upstream or downstream brake (BV, BN) are open, the first overrunning clutch (F1) and the third Fr. Overrunning clutch (F3) in the overrunning state and the second overrunning clutch (F2) and the upstream or downstream freewheeling clutch (FV, FN) are in the blocking direction, and / or that to shift a seventh gear (G7) the first brake (B1) and the second brake (B2) closed and the third brake (B3) and the upstream or downstream brake (BV, BN) are open, the first one-way clutch (F1) and the second one-way clutch (F2) in the overrunning state and the third one-way clutch (F3) and the Upstream or downstream freewheel clutch (FV, FN) are in the reverse direction, and / or that to shift an eighth gear (G8) the first brake (B1), the second brake (B2) and the third brake (B3) are closed and the upstream or secondary brake (BV, BN) are open, the first overrunning clutch (F1), the second overrunning clutch (F2) and the third overrunning clutch (F3) in the overrunning state and the upstream or secondary overrunning clutch (FV, FN) in The reverse direction state is, and / or that to shift a ninth gear (G9) the first brake (B1), the second brake (B2) and the third brake (B3) are open and the upstream or downstream brake (BV, BN) are closed, wherein the first overrunning clutch (F1), the second overrunning clutch (F2) and the third overrunning clutch (F3) are in the reverse direction and the upstream or downstream overrunning clutch (FV, FN) are in the overrunning state, and / or that for shifting a tenth gear (G10) the first brake (B1) and the second brake (B2) are open and the third brake (B3) and the upstream or downstream brake (BV, BN) are closed, the first one-way clutch (F1) and the second one-way clutch (F2) in the Locking direction state and the third overrunning clutch (F3) and the upstream or downstream overrunning clutch (FV, FN) are in the overrunning state, and / or that for shifting an eleventh gear (G11) the first brake (B1) and the third brake (B3) are opened and un d the second brake (B2) and the upstream or downstream brake (BV, BN) are closed, the first overrunning clutch (F1) and the third overrunning clutch (F3) in the reverse direction and the second overrunning clutch (F2) and the upstream or downstream freewheeling clutch (FV, FN) are in the overtaking drive state, and / or that to shift a twelfth gear (G12) the first brake (B1) is opened and the second brake (B2), the third brake (B3) and the upstream or downstream brake (BV , BN) are closed, with the first overrunning clutch (F1) in the blocking direction state and the second overrunning clutch (F2), the third overrunning clutch (F3) and the upstream or downstream overrunning clutch (FV, FN) in the overrunning state, and / or that for shifting of a thirteenth gear (G13) the first brake (B1) and the upstream or downstream brake (BV, BN) are closed and the second brake (B2) and the third brake (B3) are open, the first overrunning clutch (F1) and the upstream or downstream freewheel clutch (FV, FN) are in the overrunning state and the second overrunning clutch (F2) and the third overrunning clutch (F3) are in the reverse direction, and / or that for shifting a fourteenth gear (G14) the first brake (B1), which third brake (B3) and the upstream or downstream brake (BV, BN) are closed and the second brake (B2) are open, the first overrunning clutch (F1), the third overrunning clutch (F3) and the upstream or downstream overrunning clutch (FV, FN) are in the overrunning state and the second overrunning clutch (F2) are in the reverse direction, and / or that for shifting a fifteenth gear (G15) the first brake (B1), the second brake (B2) and the upstream or downstream brake (BV, BN ) are closed and the third brake (B3) is open, the first overrunning clutch (F1), the second overrunning clutch (F2) and the upstream or downstream freewheeling clutch (FV, FN) in the overrunning state and the third freewheel Clutch (F3) are in the reverse direction, and / or that for shifting a sixteenth gear (G16) the first brake (B1), the second brake (B2), the third brake (B3) and the upstream or downstream brake (BV, BN ) are closed, the first one-way clutch (F1), the second one-way clutch (F2), the third one-way clutch (F3) and the upstream or downstream free-wheeling clutch (FV, FN) being in the overrunning state. Multi-stage gearbox according to one of the preceding claims, characterized in that the multi-stage gearbox is designed as a bottom bracket gearbox with planetary gear sets (RS1, RS2, RS3, VRS, NRS) arranged coaxially to one another, the gearbox input shaft (1) being designed as a central bottom bracket crankshaft. Multi-step transmission according to one of the preceding claims, characterized in that at least one electrical machine is provided. Bicycle or pedelec with a multi-step transmission according to one of the preceding claims.

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