Multi-stage planetary gearbox for a bicycle or pedelec

Abstract

Multi-stage planetary gear unit for a bicycle or pedelec, with a gear input shaft (1) as the drive and a gear output shaft (2) as the driven shaft, with at least four planetary gear sets (RS1, RS2, RS3, RS4), wherein at least four freewheel clutches (F1, F2, F3, F4) and at least four brakes (B1, B2, B3, B4) are provided for realizing at least sixteen gears (G1, G2, G3, G4, G5, G6, G7, G8, G9, G10, G11, G12, G13, G14, G15, G16), wherein a planet carrier (11) of a third planetary gear set (RS3) is connected to a sun gear (13) of a fourth planetary gear set (RS4), wherein a ring gear (12) of a third planetary gear set (RS3) can be locked via a fourth brake (B4) and via a fourth freewheel clutch (F4) can be connected to a planet carrier (14) of the fourth planet gear set (RS4) or to a ring gear (15) of the fourth planet gear set (RS4),wherein the planet carrier (14) of the fourth planetary gear set (RS4) is connected to the transmission input shaft (1) or to a gear set element as the output of a second planetary gear set (RS2), wherein the ring gear (15) of the fourth planetary gear set (RS4) is connected to the transmission output shaft (2) or to a gear set element as the input of the second planetary gear set (RS2), and wherein a sun gear (10) of the third planetary gear set (RS3) can be locked via a third brake (B3) and can be connected via a third freewheel clutch (F3) to the planet carrier (14) of the fourth planetary gear set (RS4) or to the ring gear (15) of the fourth planetary gear set (RS4).

Description

[0001] The invention relates to a multi-stage planetary transmission for a bicycle or pedelec. Furthermore, the invention relates to a bicycle or pedelec with the multi-stage transmission.

[0002] A variety of bicycles and pedelecs are known from the state of the art, usually equipped with derailleur or hub gears. Pedelecs differ from bicycles in that they feature an electric motor to assist the rider. In some pedelecs, a hub motor is installed in the front or rear wheel. Hub motors in the front wheel have a negative impact on handling due to their high weight. Hub motors mounted in the rear wheel, on the other hand, have so far been used with derailleur gears that are difficult to maintain and also have a negative impact on handling due to their high weight. For this reason, pedelecs have already been developed in which a countershaft transmission and an electric motor are arranged in a bottom bracket.The disadvantage of the known bottom bracket gears in countershaft design is that they have a low power density and, in addition, due to the fact that only rolling power occurs, a poor efficiency.

[0003] The publications DE 10 2016 225 157 A1 and WO 2014 / 072 344 A1 disclose bicycle transmissions in planetary design.

[0004] The present invention is based on the object of specifying a multi-stage transmission or a bicycle or a pedelec with the multi-stage transmission, which have a high power density and a high efficiency with a high number of gears.

[0005] This object is achieved according to the invention by the features of patent claim 1 or 24, wherein advantageous and claimed developments result from the subclaims and the description as well as the drawings.

[0006] Accordingly, a multi-stage planetary transmission is proposed, e.g., as a bottom bracket transmission for a bicycle or pedelec, with a transmission input shaft as the input, e.g., a manual drive shaft or pedal crankshaft or the like, and a transmission output shaft, preferably arranged coaxially to the transmission input shaft, as the output. The multi-stage transmission or bottom bracket transmission comprises at least four planetary gear sets, preferably arranged coaxially to the transmission input shaft. Furthermore, at least four freewheel clutches and at least four brakes, which can also be designed as freewheel brakes or the like, are provided for realizing at least sixteen gears. In the multi-stage transmission according to the invention, a planetary gear carrier of a third planetary gear set is connected to a sun gear of a fourth planetary gear set.wherein a ring gear of a third planetary gear set can be locked via a fourth brake and can be connected via a fourth one-way clutch to a planetary gear carrier of the fourth planetary gear set or to a ring gear of the fourth planetary gear set. The planetary gear carrier of the fourth planetary gear set is connected to the transmission input shaft or to a gear set element as the output of a second planetary gear set. The ring gear of the fourth planetary gear set is connected to the transmission output shaft or to a gear set element as the input of the second planetary gear set. A sun gear of the third planetary gear set can be locked via a third brake and can be connected via a third one-way clutch to the planetary gear carrier of the fourth planetary gear set or to the ring gear of the fourth planetary gear set.

[0007] In this way, a gear set arrangement for the multi-stage transmission is realized which, due to the interconnection of the gear sets, achieves a particularly high power density with the highest possible efficiency, thus achieving a high level of system integration, regardless of the axial order in which the individual planetary gear sets are arranged. Preferably, a hybridized multi-stage transmission can also be provided which has a medium gear ratio spread and preferably has a U-shaped gear step diagram and whose individual gear sets have conventional stationary gear ratios. A U-shaped gear step diagram is understood to mean that the gear steps of the first two and the last two gears are approximately twice as high as the other gear steps.

[0008] With regard to the axial arrangement of the gear sets, the first and second planetary gear sets form a first gear set pair and the third and fourth planetary gear sets form a second gear set pair, wherein the gear set pairs can be arranged axially next to one another in such a way that a gear set element is connected to the transmission input shaft as the input of the second planetary gear set, that a gear set element is connected to the input of the fourth planetary gear set as the output of the second planetary gear set, and that a gear set element is connected to the transmission output shaft as the output of the fourth planetary gear set.Furthermore, it is also possible for the gear set pairs to be arranged axially next to one another in such a way that one gear set element, as the input of the fourth planetary gear set, is connected to the transmission input shaft, one gear set element, as the output of the fourth planetary gear set, is connected to one gear set element, as the input of the second planetary gear set, and one gear set element, as the output of the second planetary gear set, is connected to the transmission output shaft. In this way, various axial arrangement variants are conceivable.

[0009] In the present invention, the first and second planetary gear sets can preferably be designed as a negative planetary gear set or as a positive planetary gear set. A negative planetary gear set can preferably be converted into a positive planetary gear set if the planet carrier and ring gear connections on this gear set are interchanged and the value of the stationary gear ratio is increased by 1. As is known, a negative planetary gear set has rotatably mounted planet gears on its planet 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 direction of rotation of the sun gear when the planet carrier is held stationary and the sun gear rotates.As is well known, a plus planetary gear set has inner and outer planetary gears that are rotatably mounted on its planetary gear carrier and mesh with one another, with the sun gear of this planetary gear set meshing with the inner planetary gears and the ring gear of this planetary gear set meshing with the outer planetary gears, so that the ring gear rotates in the same direction as the sun gear when the planetary gear carrier is held stationary and the sun gear is rotating.

[0010] For the person skilled in the art, this means that in the first planetary gear set, a planetary gear carrier is provided as a minus gear set for coupling to the second planetary gear set, wherein a sun gear of the first planetary gear set can be locked via a first brake and can be connected via a first one-way clutch either to a gear set element as the input of the second planetary gear set or to a gear set element as the output of the second planetary gear set, and wherein a ring gear of the first planetary gear set can be locked via a second brake and can be connected via a second one-way clutch either to a gear set element as the output of the second planetary gear set or to a gear set element as the input of the second planetary gear set.If the first planetary gear set is designed as a plus gear set, this means that the ring gear is provided for coupling with the second planetary gear set, wherein the sun gear of the first planetary gear set can be locked via the first brake and can be connected via the first one-way clutch either to the gear set element as the input of the second planetary gear set or to the gear set element as the output of the second planetary gear set, and wherein the planet gear carrier of the first planetary gear set can be locked via the second brake and can be connected via the second one-way clutch either to the gear set element as the output of the second planetary gear set or to the gear set element as the input of the second planetary gear set.

[0011] For a second planetary gear set designed as a negative gear set, this means that a ring gear is provided for coupling to the first planetary gear set, with a planet gear carrier serving as the input of the second planetary gear set and a sun gear as the output of the second planetary gear set. If the second planetary gear set is designed as a positive gear set, this means that for the second planetary gear set, the planet gear carrier is provided for coupling to the first planetary gear set, with the ring gear serving as the input of the second planetary gear set and the sun gear as the output of the second planetary gear set.

[0012] For the mechanical connection between the planetary gear sets, so-called coupling shafts and intermediate shafts can be used in the proposed multi-stage transmission. The intermediate shafts are intended for the mechanical connection between the gear pairs, while the coupling shafts couple the planetary gear sets of a gear pair to each other.

[0013] Furthermore, shafts or shaft-like elements are used to connect the various gear set elements of the intended planetary gear sets. The term "shaft" does not exclusively refer to a cylindrical, rotatably mounted machine element for transmitting torque, but rather also encompasses general connecting elements that connect the individual gear set elements to one another.

[0014] In order to enable an electrical support power in addition to the manual drive by the driver, the multi-stage transmission according to the invention can be provided with at least one electric machine or the like.

[0015] The electric motor can be connected, for example, to the transmission input shaft, the transmission output shaft, or similar shafts, either directly or via one or more gear stages, chains, toothed belts, or the like. A shifting element, such as a one-way clutch or the like, can also be used for this purpose. This offers the advantage that, when the electric motor drive is switched off, no drag torque is generated by an electric motor driven by pedaling. If connected, for example, via a gear stage, a gear reduction can be achieved if necessary.

[0016] When the electric motor is connected to the transmission input shaft, the electric motor is operated with the gear ratio. When the electric motor is connected to the transmission output shaft, the electric motor EM is operated with the chain ratio. This allows for a power shift if the load is applied exclusively by the electric motor during a shift and the transmission is in a load-free state.

[0017] When designing the multi-stage transmission as a bottom bracket drive, a freewheel can preferably be implemented between the bottom bracket crankshaft and the transmission input. This offers the advantage that a connected electric motor can continue to rotate without the pedals of the bottom bracket crankshaft rotating.

[0018] As already described, the brakes provided can also be designed as switchable freewheels or freewheel brakes, which has the advantage of allowing faster and easier skipping of individual gears when shifting.

[0019] A further aspect of the present invention is to also provide a bicycle or a pedelec or the like with the prescribed multi-stage transmission, whereby the advantages already described and further advantages result.

[0020] The present invention is further explained below with reference to the drawings. They show: Fig. 1 a transmission diagram of a first embodiment of a multi-stage transmission according to the invention with four planetary gear sets designed as a minus gear set with a medium overall spread; Fig. 2 a transmission diagram of a second embodiment of the multi-stage transmission with a modified axial sequence and with a stepped planet in the second planetary gear set; Fig. 2A a transmission diagram of a third embodiment of the multi-stage transmission with three planetary gear sets designed as a minus gear set and a second planetary gear set as a plus gear set; Fig. 3 a circuit diagram for the variants according to Fig. 1, Fig. 2 and Fig. 2A; Fig. 4 a transmission diagram of a fourth embodiment of the multi-stage transmission with three planetary gear sets designed as a minus gear set and with a first planetary gear set as a plus gear set and a fourth planetary gear set with a stepped planet; Fig. 5 a transmission diagram of a fifth variant of the multi-stage transmission with a modified axial sequence and four planetary gear sets designed as a minus gear set with two stepped planets; and Fig. 6 a circuit diagram for the variants according to Fig. 4 and Fig. 5.

[0021] In the Fig. 1, Fig. 2, Fig. 2A and 4 and 5 show various embodiments of a multi-stage transmission according to the invention, exemplified as a bottom bracket drive in coaxial design with the respective stationary gear ratios i0 of the individual gear sets, wherein the stationary gear ratios i0 are indicated in the respective figures. In the corresponding circuit diagrams according to Fig. 3 and Fig. 6 shows the possible gears G1 to G16 with the corresponding gear ratio i and the gradation or spread φ. In addition, the individual states of the brakes B1, B2, B3, B4 and the one-way clutches F1, F2, F3, F4 are indicated in the switching diagrams, whereby for the brakes B1, B2, B3, B4 a circle indicates the closed state and a cross the open state, whereas for the one-way clutches F1, F2, F3, F4 a circle indicates the locking direction state and a line indicates the overrunning drive state. The overrunning drive or overrunning drive state of a freewheel means that the freewheel is not locking. The freewheel can be in overrunning drive if one of the elements connected to the freewheel is rotating so fast that the freewheel cannot lock. The locking direction state of a freewheel means that the freewheel is locking.

[0022] Regardless of the specific design variant of the multi-speed transmission, the multi-speed transmission in planetary design is intended to be used for a bicycle, a pedelec, or the like. The multi-speed transmission comprises a transmission input shaft 1 as the drive, which in the figures is designed, for example, as a pedal crankshaft, and a transmission output shaft 2 as the output, which can be designed, for example, as a chain or toothed belt wheel. The multi-speed transmission comprises four planetary gear sets, namely a first planetary gear set RS1, a second planetary gear set RS2, a third planetary gear set RS3, and a fourth planetary gear set RS4. In addition, four overrunning clutches F1, F2, F3, F4 and four brakes or overrunning brakes B1, B2, B3, B4 are provided as shifting elements for implementing 16 gears.

[0023] In all design variants of the multi-stage transmission, a planetary gear carrier 11 of a third planetary gear set RS3 is connected to a sun gear 13 of a fourth planetary gear set RS4, wherein a ring gear 12 of a third planetary gear set RS3 can be locked via a fourth brake B4 or connected to a housing 3 of the multi-stage transmission and can be connected via a fourth one-way clutch F4 to a planetary gear carrier 14 of the fourth planetary gear set RS4 or to a ring gear 15 of the fourth planetary gear set RS4. In addition, the planetary gear carrier 14 of the fourth planetary gear set RS4 is connected to the transmission input shaft 1 or to a gear set element as the output of a second planetary gear set RS2, wherein the ring gear 15 of the fourth planetary gear set RS4 is connected to the transmission output shaft 2 or to a gear set element as the input of the second planetary gear set RS2.Furthermore, a sun gear 10 of the third planetary gear set RS3 can be fixed via a third brake B3 and can be connected via a third one-way clutch F3 to the planetary gear carrier 14 of the fourth planetary gear set RS4 or to the ring gear 15 of the fourth planetary gear set RS4.

[0024] A first version of the multi-stage transmission is in Fig. 1. The illustrated transmission layout features a medium overall gear ratio and a U-shaped step pattern, preferably for trekking bikes. The couplings of the four planetary gear sets RS1, RS2, RS3, and RS4, designed as negative gear sets, are described in detail below.

[0025] Here, the transmission input shaft 1 is connected to the planetary gear carrier 8 as the input of the second planetary gear set RS2. The ring gear 9 of the second planetary gear set RS2 is connected to the planetary gear carrier 5 of the first planetary gear set RS1, whereby the two planetary gear sets RS1 and RS2 are coupled to one another as a first gear set pair, wherein a coupling shaft or the like is provided for coupling. The sun gear 4 of the first planetary gear set RS1 can be locked via the first brake B1 and connected via the first one-way clutch F1 to the transmission input shaft 1 and thus also to the planetary gear carrier 8 of the second planetary gear set (RS2). In addition, the ring gear 6 of the first planetary gear set RS1 can be locked via the second brake B2 and connected via the second one-way clutch F2 to the sun gear 7 as the output of the second planetary gear set RS2 and to the planetary gear carrier 14 as the input of the fourth planetary gear set RS4.The ring gear 12 of the third planetary gear set RS3 can be locked via the fourth brake B4 and connected via the fourth one-way clutch F4 to the ring gear 15 as the output of the fourth planetary gear set RS4. The planet gear carrier 14 of the fourth planetary gear set RS4 is connected to the sun gear 7 of the second planetary gear set RS2, with the ring gear 15 of the fourth planetary gear set RS4 being connected to the transmission output shaft 2. The sun gear 10 of the third planetary gear set RS3 can be locked via the third brake B3 and connected via the third one-way clutch F3 to the planet gear carrier 14 of the fourth planetary gear set RS4 and to the sun gear 7 of the second planetary gear set RS2, with the planet gear carrier 11 of the third planetary gear set RS3 being connected to the sun gear 13 of the fourth planetary gear set RS4, whereby the two planetary gear sets RS3 and RS4 are coupled together as a second gear set pair.

[0026] Furthermore, the standard translation i 01 of the first planetary gear set RS1 with -1.70, the stationary gear ratio i 02 of the second planetary gear set RS2 with -1.55, the stationary gear ratio i 03 of the third planetary gear set RS3 with -1.55 and the stationary gear ratio i 04 of the fourth planetary gear set RS4 with -1.50 in Fig. 1 is specified.

[0027] In Fig. 2 shows a second variant of the multi-stage transmission, in which the multi-stage transmission has a smaller overall spread compared to the transmission scheme in Fig. 1. Furthermore, a modified axial sequence of the individual gear sets is provided. Furthermore, the second planetary gear set RS2 has a stepped planetary gear. The couplings of the planetary gear sets RS1, RS2, RS3, and RS4 are described in detail below.

[0028] Specifically, the planetary gear carrier 11 of the third planetary gear set RS3 is connected to the sun gear 13 of the fourth planetary gear set RS4, thereby coupling the two planetary gear sets RS3 and RS4 together as a second gear set pair. The ring gear 12 of the third planetary gear set RS3 can be locked via the fourth brake B4 and connected to the ring gear 15 of the fourth planetary gear set RS4 via the fourth one-way clutch F4, with the planetary gear carrier 14, as the input of the fourth planetary gear set RS4, being connected to the transmission input shaft 1. The ring gear 15, as the output of the fourth planetary gear set RS4, is connected to the planetary gear carrier 8, as the input of the second planetary gear set RS2. The sun gear 10 of the third planetary gear set RS3 can be locked via the third brake B3 and connected to the transmission input shaft 1 and thus also to the planetary gear carrier 14 of the fourth planetary gear set RS4 via the third one-way clutch F3.The sun gear 7, as the output of the second planetary gear set RS2, is connected to the transmission output shaft 2. The ring gear 9 of the second planetary gear set RS2 is connected to the planet gear carrier 5 of the first planetary gear set RS1, whereby the two planetary gear sets RS1 and RS2 are coupled to one another as a first gear set pair. The sun gear 4 of the first planetary gear set RS1 can be locked via the first brake B1 and can be connected via the first one-way clutch F1 to the planet gear carrier 8 of the second planetary gear set RS2 and to the ring gear 15 of the fourth planetary gear set RS4. The ring gear 6 of the first planetary gear set RS1 can be locked via the second brake B2 and can be connected to the transmission output shaft 2 via the second one-way clutch F2.

[0029] Furthermore, the standard translation i 01 of the first planetary gear set RS1 with -1.85, the stationary gear ratio i 02 of the second planetary gear set RS2 with -1.11, the stationary gear ratio i 03of the third planetary gear set RS3 with -1.64 and the stationary gear ratio i 04 of the fourth planetary gear set RS4 with -2.00 in Fig. 2 is specified.

[0030] In Fig. Figure 2A shows a third variant of the multi-speed transmission, which has the same axial sequence of planetary gear sets RS1, RS2, RS3, and RS4, with the second planetary gear set RS2 being designed as a positive gear set. The couplings of the planetary gear sets RS1, RS2, RS3, and RS4 are described in detail below.

[0031] In detail, the planet gear carrier 11 of the third planetary gear set RS3 is connected to the sun gear 13 of the fourth planetary gear set RS4, whereby the two planetary gear sets RS3 and RS4 are coupled together as a second gear set pair. The ring gear 12 of the third planetary gear set RS3 can be locked via the fourth brake B4 and can be connected to the ring gear 15 as the output of the fourth planetary gear set RS4 via the fourth one-way clutch F4. The planet gear carrier 14 as the input of the fourth planetary gear set RS4 is connected to the transmission input shaft 1, with the ring gear 15 of the fourth planetary gear set RS4 being connected to the ring gear 9 as the input of the second planetary gear set RS2. The sun gear 10 of the third planetary gear set RS3 can be locked via the third brake B3 and can be connected to the transmission input shaft 1 and thus also to the planet gear carrier 14 of the fourth planetary gear set RS4 via the third one-way clutch F3.The sun gear 4 of the first planetary gear set RS1 can be locked via the first brake B1 and connected via the first one-way clutch F1 to the ring gear 9 of the second planetary gear set RS2 and to the ring gear 15 of the fourth planetary gear set RS4. The ring gear 6 of the first planetary gear set RS1 can be locked via the second brake B2 and connected via the second one-way clutch F2 to the transmission output shaft 2, with the planet gear carrier 5 of the first planetary gear set RS1 being connected to the planet gear carrier 8 of the second planetary gear set RS2, whereby the two planetary gear sets RS1 and RS2 are coupled to one another as a first gear set pair. The sun gear 7, as the output of the second planetary gear set RS2, is connected to the transmission output shaft 2.

[0032] Furthermore, the standard translation i 01 of the first planetary gear set RS1 with -1.85, the stationary gear ratio i 02 of the second planetary gear set RS2 with 2.11, the stationary gear ratio i03 of the third planetary gear set RS3 with -1.64 and the stationary gear ratio i 04 of the fourth planetary gear set RS4 with -2.00 in Fig. 2A is specified.

[0033] In Fig. 3 is a circuit diagram for the first, second and third embodiments according to Fig. 1 and Fig. 2 and 2A. From the circuit diagram according to Fig. 3, for the previously described embodiments, it can be seen that to engage a first gear G1, the first, second, third, and fourth brakes B1, B2, B3, B4 are open, with the first, second, third, and fourth one-way clutches F1, F2, F3, F4 being in the locking direction state. To engage a second gear G2, the third brake B3 is closed and the first, second, and fourth brakes B1, B2, B4 are open, with the third one-way clutch F3 being in the overrunning drive state and the first, second, and fourth one-way clutches F1, F2, F4 being in the locking direction state. To engage a third gear G3, the first brake B1 is closed and the second, third, and fourth brakes B2, B3, B4 are open, with the first one-way clutch F1 being in the overrunning drive state and the second, third, and fourth one-way clutches F2, F3, F4 being in the locking direction state.To engage a fourth gear G4, the first, second, and third brakes B1, B2, B3 are open and the fourth brake B4 is closed, with the first, second, and third one-way clutches F1, F2, F3 in the blocking direction state and the fourth one-way clutch F4 in the overrunning drive state. To engage a fifth gear G5, the first and third brakes B1, B3 are closed and the second and fourth brakes B2, B4 are open, with the second and fourth one-way clutches F2, F4 in the blocking direction state and the first and third one-way clutches F1, F3 in the overrunning drive state. To engage a sixth gear G6, the first and second brakes B1, B2 are open and the third and fourth brakes B3, B4 are closed, with the first and second one-way clutches F1, F2 in the blocking direction state and the third and fourth one-way clutches F3, F4 in the overrunning drive state.To engage a seventh gear G7, the first and fourth brakes B1, B4 are engaged and the second and third brakes B2, B3 are disengaged, with the first and fourth one-way clutches F1, F4 in the overrunning drive state and the second and third one-way clutches F2, F3 in the locking direction state. To engage an eighth gear G8, the first, third and fourth brakes B1, B3, B4 are disengaged and the second brake B2 is engaged, with the first, third and fourth one-way clutches F1, F3, F4 in the locking direction state and the second one-way clutch F2 in the overrunning drive state. To engage a ninth gear G9, the first, third and fourth brakes B1, B3, B4 are engaged and the second brake B2 is disengaged, with the first, third and fourth one-way clutches F1, F3, F4 in the overrunning drive state and the second one-way clutch F2 in the locking direction state.To shift a tenth gear G10, the first and fourth brakes B1, B4 are opened and the second and third brakes B2, B3 are closed, with the first and fourth one-way clutches F1, F4 in the blocking direction state and the second and third one-way clutches F2, F3 in the overrunning drive state. To shift an eleventh gear G11, the first and second brakes B1, B2 are closed and the third and fourth brakes B3, B4 are opened, with the first and second one-way clutches F1, F2 in the overrunning drive state and the third and fourth one-way clutches F3, F4 in the blocking direction state. To shift a twelfth gear G12, the second and fourth brakes B2, B4 are closed and the first and third brakes B1, B3 are opened, with the second and fourth one-way clutches F2, F4 in the overrunning drive state and the first and third one-way clutches F1, F3 in the blocking direction state.To shift a thirteenth gear G13, the first, second and third brakes B1, B2, B3 are closed and the fourth brake B4 is opened, with the first, second and third one-way clutches F1, F2, F3 in the overrunning drive state and the fourth one-way clutch F4 in the blocking direction state. To shift a fourteenth gear G14, the second, third and fourth brakes B2, B3, B4 are closed and the first brake B1 is opened, with the second, third and fourth one-way clutches F2, F3, F4 in the overrunning drive state and the first one-way clutch F1 in the blocking direction state. To shift a fifteenth gear G15, the third brake B3 is opened and the first, second and fourth brakes B1, B2, B4 are closed, with the third one-way clutch F3 in the blocking direction state and the first, second and fourth one-way clutches F1, F2, F4 in the overrunning drive state.To engage a sixteenth gear G16, the first, second, third and fourth brakes B1, B2, B3, B4 are closed, with the first, second, third and fourth freewheel clutches F1, F2, F3, F4 being in the overrunning drive state.

[0034] In Fig. Figure 4 shows a fourth embodiment of the multi-stage transmission, which has a medium overall gear ratio spread and a constant step progression. The second planetary gear set RS2, the third planetary gear set RS3, and the fourth planetary gear set RS4 are each designed as negative gear sets, while the first planetary gear set RS1 is designed as a positive gear set. Furthermore, the fourth embodiment provides for the fourth planetary gear set RS4 to have a stepped planetary gear. The couplings of the planetary gear sets RS1, RS2, RS3, and RS4 are described in detail below.

[0035] In detail, the planetary gear carrier 11 of the third planetary gear set RS3 is connected to the sun gear 13 of the fourth planetary gear set RS4, thereby coupling the two planetary gear sets RS3 and RS4 together as a second gear set pair. The ring gear 12 of the third planetary gear set RS3 can be locked via the fourth brake B4 and connected via the fourth one-way clutch F4 to the ring gear 15 as the output of the fourth planetary gear set RS4. The planetary gear carrier 14, as the input of the fourth planetary gear set RS4, is connected to the transmission input shaft 1. The ring gear 15 of the fourth planetary gear set RS4 is connected to the planetary gear carrier 8 as the input of the second planetary gear set RS2, wherein the sun gear 10 of the third planetary gear set RS3 can be locked via the third brake B3 and can be connected via the third one-way clutch F3 to the transmission input shaft 1 and thus also to the planetary gear carrier 14 of the fourth planetary gear set RS4.The sun gear 4 of the first planetary gear set RS1 can be locked via the first brake B1 and connected via the first one-way clutch F1 to the planet gear carrier 8 of the second planetary gear set RS2 and to the ring gear 15 of the fourth planetary gear set RS4. The planet gear carrier 5 of the first planetary gear set RS1 can be locked via the second brake B2 and connected via the second one-way clutch F2 to the transmission output shaft 2. The ring gear 6 of the first planetary gear set RS1 is connected to the ring gear 9 of the second planetary gear set RS2, whereby the two planetary gear sets RS1 and RS2 are coupled to one another as a first gear set pair. The sun gear 7, as the output of the second planetary gear set RS2, is connected to the transmission output shaft 2.

[0036] Furthermore, the standard translation i 01 of the first planetary gear set RS1 with 2.15, the stationary gear ratio i 02 of the second planetary gear set RS2 with -2.18, the stationary gear ratio i 03of the third planetary gear set RS3 with -1.73 and the stationary gear ratio i 04 of the fourth planetary gear set RS4 with -2.96 in Fig. 4 is specified.

[0037] In Fig. Figure 5 shows a fifth embodiment of the multi-stage transmission. Compared to the fourth embodiment, it has a smaller overall gear ratio spread and a modified axial sequence of the planetary gear sets RS1, RS2, RS3, and RS4. Furthermore, the first planetary gear set RS1 and the fourth planetary gear set RS4 each have a stepped planetary gear. The couplings of the planetary gear sets RS1, RS2, RS3, and RS4 are described in detail below.

[0038] Specifically, the planetary gear carrier 11 of the third planetary gear set RS3 is connected to the sun gear 13 of the fourth planetary gear set RS4, thereby coupling the two planetary gear sets RS3 and RS4 together as a second gear set pair. The ring gear 12 of the third planetary gear set RS3 can be locked via the fourth brake B4 and connected via the fourth one-way clutch F4 to the planetary gear carrier 14 as the input of the fourth planetary gear set RS4, wherein the planetary gear carrier 14 of the fourth planetary gear set RS4 is connected to the sun gear 7 as the output of the second planetary gear set RS2. The ring gear 15 as the output of the fourth planetary gear set RS4 is connected to the transmission output shaft 2, wherein the sun gear 10 of the third planetary gear set RS3 can be locked via the third brake B3 and connected via the third one-way clutch F3 to the ring gear 15 of the fourth planetary gear set RS4.The sun gear 4 of the first planetary gear set RS1 can be locked via the first brake B1 and connected via the first one-way clutch F1 to the sun gear 7 of the second planetary gear set RS2 and to the planet gear carrier 14 of the fourth planetary gear set RS4. The ring gear 6 of the first planetary gear set RS1 can be locked via the second brake B2 and connected via the second one-way clutch F2 to the planet gear carrier 8 as the input of the second planetary gear set RS2, wherein the planet gear carrier 8 of the second planetary gear set RS2 is connected to the transmission input shaft 1. The ring gear 9 of the second planetary gear set RS2 is connected to the planet gear carrier 5 of the first planetary gear set RS1, whereby the two planetary gear sets RS1 and RS2 are coupled to one another as a first gear set pair.

[0039] Furthermore, the standard translation i 01 of the first planetary gear set RS1 with -3.20, the stationary gear ratio i 02of the second planetary gear set RS2 with -1.52, the stationary gear ratio i 03 of the third planetary gear set RS3 with -2.25 and the stationary gear ratio i 04 of the fourth planetary gear set RS4 with -3.85 in Fig. 5 is specified.

[0040] In Fig. 6 is a circuit diagram for the fourth and fifth embodiments according to Fig. 4 and Fig. 5. From the circuit diagram according to Fig.6, for the previously described embodiments, it can be seen that to engage a first gear G1, the first, second, third, and fourth brakes B1, B2, B3, B4 are open, with the first, second, third, and fourth one-way clutches F1, F2, F3, F4 being in the locking direction state. To engage a second gear G2, the third brake B3 is closed and the first, second, and fourth brakes B1, B2, B4 are open, with the third one-way clutch F3 being in the overrunning drive state and the first, second, and fourth one-way clutches F1, F2, F4 being in the locking direction state. To engage a third gear G3, the fourth brake B4 is closed and the first, second, and third brakes B1, B2, B3 are open, with the fourth one-way clutch F4 being in the overrunning drive state and the first, second, and third one-way clutches F1, F2, F3 being in the locking direction state.To engage a fourth gear G4, the first and second brakes B1, B2 are opened and the third and fourth brakes B3, B4 are closed, with the first and second one-way clutches F1, F2 in the blocking direction state and the third and fourth one-way clutches F3, F4 in the overrunning drive state. To engage a fifth gear G5, the first brake B1 is closed and the second, third and fourth brakes B2, B3, B4 are opened, with the second, third and fourth one-way clutches F2, F3, F4 in the blocking direction state and the first one-way clutch F1 in the overrunning drive state. To engage a sixth gear G6, the first and third brakes B1, B3 are closed and the second and fourth brakes B2, B4 are opened, with the first and third one-way clutches F1, F3 in the overrunning drive state and the second and fourth one-way clutches F2, F4 in the blocking direction state.To shift a seventh gear G7, the first and fourth brakes B1, B4 are closed and the second and third brakes B2, B3 are opened, with the first and fourth one-way clutches F1, F4 in the overrunning drive state and the second and third one-way clutches F2, F3 in the locking direction state. To shift an eighth gear G8, the first, third and fourth brakes B1, B3, B4 are closed and the second brake B2 is opened, with the first, third and fourth one-way clutches F1, F3, F4 in the overrunning drive state and the second one-way clutch F2 in the locking direction state. To shift a ninth gear G9, the first, third and fourth brakes B1, B3, B4 are opened and the second brake B2 is closed, with the first, third and fourth one-way clutches F1, F3, F4 in the locking direction state and the second one-way clutch F2 in the overrunning drive state.To shift a tenth gear G10, the first and fourth brakes B1, B4 are opened and the second and third brakes B2, B3 are closed, with the first and fourth one-way clutches F1, F4 in the blocking direction state and the second and third one-way clutches F2, F3 in the overrunning drive state. To shift an eleventh gear G11, the first and third brakes B1, B3 are opened and the second and fourth brakes B2, B4 are closed, with the first and third one-way clutches F1, F3 in the blocking direction state and the second and fourth one-way clutches F2, F4 in the overrunning drive state. To shift a twelfth gear G12, the second, third and fourth brakes B2, B3, B4 are closed and the first brake B1 is opened, with the second, third and fourth one-way clutches F2, F3, F4 in the overrunning drive state and the first one-way clutch F1 in the blocking direction state.To shift a thirteenth gear G13, the first and second brakes B1, B2 are closed and the third and fourth brakes B3, B4 are opened, with the first and second one-way clutches F1, F2 in the overrunning drive state and the third and fourth one-way clutches F3, F4 in the locking direction state. To shift a fourteenth gear G14, the first, second and third brakes B1, B2, B3 are closed and the fourth brake B4 is opened, with the first, second and third one-way clutches F1, F2, F3 in the overrunning drive state and the fourth one-way clutch F4 in the locking direction state. To shift a fifteenth gear G15, the third brake B3 is opened and the first, second and fourth brakes B1, B2, B4 are closed, with the third one-way clutch F3 in the locking direction state and the first, second and fourth one-way clutches F1, F2, F4 in the overrunning drive state.To engage a sixteenth gear G16, the first, second, third and fourth brakes B1, B2, B3, B4 are closed, with the first, second, third and fourth freewheel clutches F1, F2, F3, F4 being in the overrunning drive state. Reference symbol 1 Gearbox input shaft or crankshaft 2 gearbox output shaft 3 housings 4 Sun gear of the first planetary gear set 5 Planetary gear carrier or web of the first planetary gear set 6 Ring gear of the first planetary gear set 7 Sun gear of the second planetary gear set 8 Planet gear carrier of the second planetary gear set 9 Ring gear of the second planetary gear set 10 Sun gear of the third planetary gear set 11 Planet gear carrier of the third planetary gear set 12 Ring gear of the third planetary gear set 13 Sun gear of the fourth planetary gear set 14 Planet gear carrier of the fourth planetary gear set 15 Ring gear of the fourth planetary gear set RS1 first planetary gear set RS2 second planetary gear set RS3 third planetary gear set RS4 fourth planetary gear set B1 first brake or freewheel brake B2 second brake or freewheel brake B3 third brake or freewheel brake B4 fourth brake or freewheel brake F1 first freewheel clutch F2 second overrunning clutch F3 third overrunning clutch F4 fourth 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 i 01 Standby ratio of the first planetary gear set i 02 Standby ratio of the second planetary gear set i 03 Standby ratio of the third planetary gear set i 04 Standby ratio of the fourth planetary gear set i Translation φ Grading φ ges Overall classification

Claims

[1] Multi-stage transmission in planetary design for a bicycle or a pedelec, with a transmission input shaft (1) as input and a transmission output shaft (2) as output, with at least four planetary gear sets (RS1, RS2, RS3, RS4), wherein at least four freewheel clutches (F1, F2, F3, F4) and at least four brakes (B1, B2, B3, B4) are provided for realising at least sixteen gears (G1, G2, G3, G4, G5, G6, G7, G8, G9, G10, G11, G12, G13, G14, G15, G16), wherein a planetary gear carrier (11) of a third planetary gear set (RS3) is connected to a sun gear (13) of a fourth planetary gear set (RS4), wherein a ring gear (12) of a third planetary gear set (RS3) can be locked via a fourth brake (B4) and via a fourth overrunning clutch (F4) is connectable to a planetary gear carrier (14) of the fourth planetary gear set (RS4) or to a ring gear (15) of the fourth planetary gear set (RS4),wherein the planetary gear carrier (14) of the fourth planetary gear set (RS4) is connected to the transmission input shaft (1) or to a gear set element as the output of a second planetary gear set (RS2), wherein the ring gear (15) of the fourth planetary gear set (RS4) is connected to the transmission output shaft (2) or to a gear set element as the input of the second planetary gear set (RS2), and wherein a sun gear (10) of the third planetary gear set (RS3) can be locked via a third brake (B3) and can be connected to the planetary gear carrier (14) of the fourth planetary gear set (RS4) or to the ring gear (15) of the fourth planetary gear set (RS4) via a third overrunning clutch (F3). [2] Multi-stage transmission according to claim 1, characterized bythat the first and the second planetary gear set (RS1, RS2) form a first gear set pair and the third and fourth planetary gear set (RS3, RS4) form a second gear set pair, wherein the gear set pairs are arranged axially next to one another in such a way that a gear set element is connected to the transmission input shaft (1) as the input of the second planetary gear set (RS2), that a gear set element is connected to the input of the fourth planetary gear set (RS4) as the output of the second planetary gear set (RS2), and that a gear set element is connected to the transmission output shaft (2) as the output of the fourth planetary gear set (RS4). [3] Multi-stage transmission according to claim 1, characterized bythat the first and the second planetary gear set (RS1, RS2) form a first gear set pair and the third and fourth planetary gear set (RS3, RS4) form a second gear set pair, wherein the gear set pairs are arranged axially next to one another in such a way that a gear set element is connected to the transmission input shaft (1) as the input of the fourth planetary gear set (RS4), that a gear set element is connected to the input of the second planetary gear set (RS2) as the output of the fourth planetary gear set (RS4), and that a gear set element is connected to the transmission output shaft (2) as the output of the second planetary gear set (RS2). [4] Multi-stage transmission according to one of the preceding claims, characterized byin that, in a first planetary gear set (RS1) designed as a minus gear set, a planetary gear carrier (5) is provided for coupling to the second planetary gear set (RS2), wherein a sun gear (4) of the first planetary gear set (RS1) can be locked via a first brake (B1) and can be connected via a first one-way clutch (F1) either to a gear set element as the input of the second planetary gear set (RS2) or to a gear set element as the output of the second planetary gear set (RS2), and wherein a ring gear (6) of the first planetary gear set (RS1) can be locked via a second brake (B2) and can be connected via a second one-way clutch (F2) either to a gear set element as the output of the second planetary gear set RS2 or to a gear set element as the input of the second planetary gear set (RS2). [5] Multi-stage transmission according to one of claims 1 to 3, characterized byin that, in a first planetary gear set (RS1) designed as a plus gear set, a ring gear (6) is provided for coupling to the second planetary gear set (RS2), wherein a sun gear (4) of the first planetary gear set (RS1) can be locked via a first brake (B1) and can be connected via a first one-way clutch (F1) either to a gear set element as the input of the second planetary gear set (RS2) or to a gear set element as the output of the second planetary gear set (RS2), and wherein a planet gear carrier (5) of the first planetary gear set (RS1) can be locked via a second brake (B2) and can be connected via a second one-way clutch (F2) either to a gear set element as the output of the second planetary gear set (RS2) or to a gear set element as the input of the second planetary gear set (RS2). [6] Multi-stage transmission according to one of the preceding claims, characterized byin that, in a second planetary gear set (RS2) designed as a minus gear set, a ring gear (9) is provided for coupling with the first planetary gear set (RS1), a planet gear carrier (8) being provided as the input of the second planetary gear set (RS2) and a sun gear (7) being provided as the output of the second planetary gear set (RS2). [7] Multi-stage transmission according to one of claims 1 to 5, characterized by in that, in a second planetary gear set (RS2) designed as a plus gear set, a planetary gear carrier (8) is provided for coupling with the first planetary gear set (RS1), a ring gear (9) being provided as the input of the second planetary gear set (RS2) and a sun gear (7) being provided as the output of the second planetary gear set (RS2). [8] Multi-stage transmission according to one of the preceding claims, characterized by that freewheel brakes are provided as brakes (B1, B2, B3, B4). [9] Multi-stage transmission according to one of the preceding claims, characterized bythat the first, second, third and fourth planetary gear sets (RS1, RS2, RS3, RS4) are each designed as minus gear sets. [10] Multi-stage transmission according to claim 9, characterized bythat the transmission input shaft (1) is connected to the planetary gear carrier (8) as the input of the second planetary gear set (RS2), that the ring gear (9) of the second planetary gear set (RS2) is connected to the planetary gear carrier (5) of the first planetary gear set (RS1), that the sun gear (4) of the first planetary gear set (RS1) can be locked via the first brake (B1) and can be connected to the transmission input shaft (1) via the first one-way clutch (F1), that the ring gear (6) of the first planetary gear set (RS1) can be locked via the second brake (B2) and can be connected via the second one-way clutch (F2) to the sun gear (7) as the output of the second planetary gear set (RS2) and to the planetary gear carrier (14) as the input of the fourth planetary gear set (RS4), that the ring gear (12) of the third planetary gear set (RS3) can be locked via the fourth brake (B4) and can be connected via the fourth freewheel clutch (F4) to the ring gear (15) as the output of the fourth planetary gear set (RS4),that the planetary gear carrier (14) of the fourth planetary gear set (RS4) is connected to the sun gear (7) of the second planetary gear set (RS2), that the ring gear (15) of the fourth planetary gear set (RS4) is connected to the transmission output shaft (2), that the sun gear (10) of the third planetary gear set (RS3) can be locked via the third brake (B3) and can be connected to the planetary gear carrier (14) of the fourth planetary gear set (RS4) and to the sun gear (7) of the second planetary gear set (RS2) via the third overrunning clutch (F3). (, Fig. 1) [11] Multi-stage transmission according to claim 9, characterized by that the second planetary gear set (RS2) has a stepped planet. [12] Multi-stage transmission according to claim 11, characterized bythat the ring gear (12) of the third planetary gear set (RS3) can be locked via the fourth brake (B4) and can be connected to the ring gear (15) of the fourth planetary gear set (RS4) via the fourth one-way clutch (F4), that the planet gear carrier (14) is connected to the transmission input shaft (1) as the input of the fourth planetary gear set (RS4), that the ring gear (15) is connected to the planet gear carrier (8) as the input of the second planetary gear set (RS2), that the sun gear (10) of the third planetary gear set (RS3) can be locked via the third brake (B3) and can be connected to the transmission input shaft (1) via the third one-way clutch (F3), that the sun gear (7) is connected to the transmission output shaft (2) as the output of the second planetary gear set (RS2), that the ring gear (9) of the second planetary gear set (RS2) is connected to the planetary gear carrier (5) of the first planetary gear set (RS1),that the sun gear (4) of the first planetary gear set (RS1) can be locked via the first brake (B1) and can be connected via the first one-way clutch (F1) to the planet gear carrier (8) of the second planetary gear set (RS2) and to the ring gear (15) of the fourth planetary gear set (RS4); that the ring gear (6) of the first planetary gear set (RS1) can be locked via the second brake (B2) and can be connected via the second one-way clutch (F2) to the transmission output shaft (2). (, Fig. 2) [13] Multi-stage transmission according to one of claims 1 to 8, characterized by that the first, third and fourth planetary gear sets (RS1, RS3, RS4) are each designed as minus gear sets and that the second planetary gear set (RS2) is designed as plus gear sets. [14] Multi-stage transmission according to claim 13, characterized bythat the ring gear (12) of the third planetary gear set (RS3) can be locked via the fourth brake (B4) and can be connected via the fourth one-way clutch (F4) to the ring gear (15) as the output of the fourth planetary gear set (RS4), that the planet gear carrier (14) is connected to the transmission input shaft (1) as the input of the fourth planetary gear set (RS4), that the ring gear (15) of the fourth planetary gear set (RS4) is connected to the ring gear (9) as the input of the second planetary gear set (RS2), that the sun gear (10) of the third planetary gear set (RS3) can be locked via the third brake (B3) and can be connected to the transmission input shaft (1) via the third one-way clutch (F3), that the sun gear (4) of the first planetary gear set (RS1) can be locked via the first brake (B1) and can be connected via the first one-way clutch (F1) to the ring gear (9) of the second planetary gear set (RS2) and with the ring gear (15) of the fourth planetary gear set (RS4),that the ring gear (6) of the first planetary gear set (RS1) can be locked via the second brake (B2) and can be connected to the transmission output shaft (2) via the second overrunning clutch (F2), that the planet gear carrier (5) of the first planetary gear set (RS1) is connected to the planet gear carrier (8) of the second planetary gear set (RS2), and that the sun gear (7), as the output of the second planetary gear set (RS2), is connected to the transmission output shaft (2). (, Fig. 2A) [15] Multi-stage transmission according to one of claims 9 to 14, characterized bythat for shifting a first gear (G1) the first, second, third and fourth brakes (B1, B2, B3, B4) are opened, wherein the first, second, third and fourth freewheel clutches (F1, F2, F3, F4) are in the locking direction state, or that for shifting a second gear (G2) the third brake (B3) is closed and the first, second and fourth brakes (B1, B2, B4) are opened, wherein the third freewheel clutch (F3) is in the overrunning drive state and the first, second and fourth freewheel clutches (F1, F2, F4) are in the locking direction state, or that for shifting a third gear (G3) the first brake (B1) is closed and the second, third and fourth brakes (B2, B3, B4) are opened, wherein the first freewheel clutch (F1) is in the overrunning drive state and the second, third and fourth freewheel clutches (F2, F3, F4) are in Locking direction state, or that to engage a fourth gear (G4) the first, second and third brakes (B1, B2,B3) are opened and the fourth brake (B4) is closed, wherein the first, second and third freewheel clutches (F1, F2, F3) are in the blocking direction state and the fourth freewheel clutch (F4) are in the overrunning drive state, or that for shifting a fifth gear (G5) the first and third brakes (B1, B3) are closed and the second and fourth brakes (B2, B4) are opened, wherein the second and fourth freewheel clutches (F2, F4) are in the blocking direction state and the first and third freewheel clutches (F1, F3) are in the overrunning drive state, or that for shifting a sixth gear (G6) the first and second brakes (B1, B2) are opened and the third and fourth brakes (B3, B4) are closed, wherein the first and second freewheel clutches (F1, F2) are in the blocking direction state and the third and fourth freewheel clutches (F3, F4) are in the overrunning drive state, or that to engage a seventh gear (G7) the first and fourth brakes (B1,B4) are closed and the second and third brakes (B2, B3) are open, wherein the first and fourth freewheel clutches (F1, F4) are in the overrunning drive state and the second and third freewheel clutches (F2, F3) are in the blocking direction state, or that for shifting an eighth gear (G8) the first, third and fourth brakes (B1, B3, B4) are open and the second brake (B2) is closed, wherein the first, third and fourth freewheel clutches (F1, F3, F4) are in the blocking direction state and the second freewheel clutch (F2) is in the overrunning drive state, or that for shifting a ninth gear (G9) the first, third and fourth brakes (B1, B3, B4) are closed and the second brake (B2) is open, wherein the first, third and fourth freewheel clutches (F1, F3, F4) are in the overrunning drive state and the second freewheel clutch (F2) is in the blocking direction state, or that to engage a tenth gear (G10) the first and fourth brakes (B1,B4) are opened and the second and third brakes (B2, B3) are closed, wherein the first and fourth freewheel clutches (F1, F4) are in the blocking direction state and the second and third freewheel clutches (F2, F3) are in the overrunning drive state, or that for shifting an eleventh gear (G11) the first and second brakes (B1, B2) are closed and the third and fourth brakes (B3, B4) are opened, wherein the first and second freewheel clutches (F1, F2) are in the overrunning drive state and the third and fourth freewheel clutches (F3, F4) are in the blocking direction state, or that for shifting a twelfth gear (G12) the second and fourth brakes (B2, B4) are closed and the first and third brakes (B1, B3) are opened, wherein the second and fourth freewheel clutches (F2, F4) are in the overrunning drive state and the first and third freewheel clutches (F1, F3) are in the blocking direction state are, or that to engage a thirteenth gear (G13) the first, second and third brakes (B1, B2,B3) are closed and the fourth brake (B4) is opened, wherein the first, second and third freewheel clutches (F1, F2, F3) are in the overrunning drive state and the fourth freewheel clutch (F4) is in the blocking direction state, or that for shifting a fourteenth gear (G14) the second, third and fourth brakes (B2, B3, B4) are closed and the first brake (B1) is opened, wherein the second, third and fourth freewheel clutches (F2, F3, F4) are in the overrunning drive state and the first freewheel clutch (F1) is in the blocking direction state, or that for shifting a fifteenth gear (G15) the third brake (B3) is opened and the first, second and fourth brakes (B1, B2, B4) are closed, wherein the third freewheel clutch (F3) is in the blocking direction state and the first, second and fourth freewheel clutches (F1, F2, F4) are in the overrunning drive state, or that to engage a sixteenth gear (G16) the first, second, third and fourth brakes (B1, B2, B3, B4) are closed,wherein the first, second, third and fourth overrunning clutches (F1, F2, F3, F4) are in the overrunning drive state. (, Fig. 3) [16] Multi-stage transmission according to one of claims 1 to 8, characterized by that the second, third and fourth planetary gear sets (RS2, RS3, RS4) are each designed as minus gear sets, that the first planetary gear set (RS1) is designed as a plus gear set and that the fourth planetary gear set (RS4) has a stepped planet. [17] Multi-stage transmission according to claim 16, characterized bythat the ring gear (12) of the third planetary gear set (RS3) can be locked via the fourth brake (B4) and can be connected via the fourth one-way clutch (F4) to the ring gear (15) as the output of the fourth planetary gear set (RS4), that the planet gear carrier (14) is connected to the transmission input shaft (1) as the input of the fourth planetary gear set (RS4), that the ring gear (15) of the fourth planetary gear set (RS4) is connected to the planet gear carrier (8) as the input of the second planetary gear set (RS2), that the sun gear (10) of the third planetary gear set (RS3) can be locked via the third brake (B3) and can be connected to the transmission input shaft (1) via the third one-way clutch (F3), that the sun gear (4) of the first planetary gear set (RS1) can be locked via the first brake (B1) and can be connected via the first one-way clutch (F1) to the Planet gear carrier (8) of the second planetary gear set (RS2) and can be connected to the ring gear (15) of the fourth planetary gear set (RS4),that the planetary gear carrier (5) of the first planetary gear set (RS1) can be locked via the second brake (B2) and can be connected to the transmission output shaft (2) via the second overrunning clutch (F2), that the ring gear (6) of the first planetary gear set (RS1) is connected to the ring gear (9) of the second planetary gear set (RS2), and that the sun gear (7) as the output of the second planetary gear set (RS2) is connected to the transmission output shaft (2). ( , Fig. 4) [18] Multi-stage transmission according to one of claims 1 to 8, characterized by that the first, second, third and fourth planetary gear sets (RS1, RS2, RS3, RS4) are designed as minus gear sets and that the first and fourth planetary gear sets (RS1, RS4) each have a stepped planet. [19] Multi-stage transmission according to claim 18, characterized bythat the ring gear (12) of the third planetary gear set (RS3) can be locked via the fourth brake (B4) and can be connected to the planet gear carrier (14) as the input of the fourth planetary gear set (RS4) via the fourth one-way clutch (F4), that the planet gear carrier (14) of the fourth planetary gear set (RS4) is connected to the sun gear (7) as the output of the second planetary gear set (RS2), that the ring gear (15) as the output of the fourth planetary gear set (RS4) is connected to the transmission output shaft (2), that the sun gear (10) of the third planetary gear set (RS3) can be locked via the third brake (B3) and can be connected to the ring gear (15) of the fourth planetary gear set (RS4) via the third one-way clutch (F3),that the sun gear (4) of the first planetary gear set (RS1) can be locked via the first brake (B1) and can be connected via the first one-way clutch (F1) to the sun gear (7) of the second planetary gear set (RS2) and to the planet gear carrier (14) of the fourth planetary gear set (RS4); that the ring gear (6) of the first planetary gear set (RS1) can be locked via the second brake (B2) and can be connected via the second one-way clutch (F2) to the planet gear carrier (8) as the input of the second planetary gear set (RS2); that the planet gear carrier (8) of the second planetary gear set (2) is connected to the transmission input shaft (1), and that the ring gear (9) of the second planetary gear set (RS2) is connected to the planet gear carrier (5) of the first planetary gear set (RS1). (, Fig. 5) [20] Multi-stage transmission according to one of claims 16 to 19, characterized bythat for shifting a first gear (G1) the first, second, third and fourth brakes (B1, B2, B3, B4) are opened, wherein the first, second, third and fourth freewheel clutches (F1, F2, F3, F4) are in the locking direction state, or that for shifting a second gear (G2) the third brake (B3) is closed and the first, second and fourth brakes (B1, B2, B4) are opened, wherein the third freewheel clutch (F3) is in the overrunning drive state and the first, second and fourth freewheel clutches (F1, F2, F4) are in the locking direction state, or that for shifting a third gear (G3) the fourth brake (B4) is closed and the first, second and third brakes (B1, B2, B3) are opened, wherein the fourth freewheel clutch (F4) is in the overrunning drive state and the first, second and third freewheel clutches (F1, F2, F3) are in Locking direction state, or that to engage a fourth gear (G4) the first and second brakes (B1,B2) are opened and the third and fourth brakes (B3, B4) are closed, wherein the first and second freewheel clutches (F1, F2) are in the blocking direction state and the third and fourth freewheel clutches (F3, F4) are in the overrunning drive state, or that for shifting a fifth gear (G5) the first brake (B1) is closed and the second, third and fourth brakes (B2, B3, B4) are opened, wherein the second, third and fourth freewheel clutches (F2, F3, F4) are in the blocking direction state and the first freewheel clutch (F1) is in the overrunning drive state, or that for shifting a sixth gear (G6) the first and third brakes (B1, B3) are closed and the second and fourth brakes (B2, B4) are opened, wherein the first and third freewheel clutches (F1, F3) are in the overrunning drive state and the second and fourth freewheel clutches (F2, F4) are in Locking direction state, or that to engage a seventh gear (G7) the first and fourth brakes (B1,B4) are closed and the second and third brakes (B2, B3) are opened, wherein the first and fourth freewheel clutches (F1, F4) are in the overrunning drive state and the second and third freewheel clutches (F2, F3) are in the blocking direction state, or that for shifting an eighth gear (G8) the first, third and fourth brakes (B1, B3, B4) are closed and the second brake (B2) is opened, wherein the first, third and fourth freewheel clutches (F1, F3, F4) are in the overrunning drive state and the second freewheel clutch (F2) is in the blocking direction state, or that for shifting a ninth gear (G9) the first, third and fourth brakes (B1, B3, B4) are opened and the second brake (B2) is closed, wherein the first, third and fourth freewheel clutches (F1, F3, F4) are in the blocking direction state and the second freewheel clutch (F2) is in the overrunning drive state, or that to engage a tenth gear (G10) the first and fourth brakes (B1,B4) are opened and the second and third brakes (B2, B3) are closed, wherein the first and fourth freewheel clutches (F1, F4) are in the blocking direction state and the second and third freewheel clutches (F2, F3) are in the overrunning drive state, or that for shifting an eleventh gear (G11) the first and third brakes (B1, B3) are opened and the second and fourth brakes (B2, B4) are closed, wherein the first and third freewheel clutches (F1, F3) are in the blocking direction state and the second and fourth freewheel clutches (F2, F4) are in the overrunning drive state, or that for shifting a twelfth gear (G12) the second, third and fourth brakes (B2, B3, B4) are closed and the first brake (B1) is opened, wherein the second, third and fourth freewheel clutches (F2, F3, F4) are in the overrunning drive state and the first freewheel clutch (F1) is in the blocking direction state are, or that to engage a thirteenth gear (G13) the first and second brakes (B1,B2) are closed and the third and fourth brakes (B3, B4) are opened, wherein the first and second freewheel clutches (F1, F2) are in the overrunning drive state and the third and fourth freewheel clutches (F3, F4) are in the blocking direction state, or that for shifting a fourteenth gear (G14) the first, second and third brakes (B1, B2, B3) are closed and the fourth brake (B4) is opened, wherein the first, second and third freewheel clutches (F1, F2, F3) are in the overrunning drive state and the fourth freewheel clutch (F4) is in the blocking direction state, or that for shifting a fifteenth gear (G15) the third brake (B3) is opened and the first, second and fourth brakes (B1, B2, B4) are closed, wherein the third freewheel clutch (F3) is in the blocking direction state and the first, second and fourth freewheel clutches (F1, F2, F4) are in overtaking drive condition, or that to engage a sixteenth gear (G16) the first, second, third and fourth brakes (B1, B2, B3,B4) are closed, with the first, second, third and fourth overrunning clutches (F1, F2, F3, F4) in the overrunning drive state. (, Fig. 6) [21] Multi-stage transmission according to one of the preceding claims, characterized by that the multi-stage transmission is designed as a bottom bracket transmission with coaxially arranged planetary gear sets (RS1, RS2, RS3, RS4). [22] Multi-stage transmission according to one of the preceding claims, characterized by that at least one electrical machine is provided. [23] Multi-stage transmission according to claim 22, characterized by that the transmission input shaft (1) can be connected to the electric machine via a further freewheel clutch. [24] Bicycle or pedelec with a multi-stage transmission according to one of the preceding claims.

Images