Planetary bottom bracket gear for a bicycle or pedelec

Abstract

A bottom bracket gear in planetary design for a bicycle or a pedelec (1) is proposed, with a pedal crankshaft (WAn) as input and a transmission output shaft (WAb) as output, with further shafts (W1, W2, W3, W4, W5), with three planetary gear sets (RS1, RS2, RS3) as a gearshift transmission (4), and with at least five shift elements (B1, B2, B3, K1, K2, K3) for realizing several gears (G1, G1.1, G1.2, G1.3, G2, G2.1, G2.2, G2.3, G3, G4, G5, G5.1, G5.2, G5.3, G6, G6.1, G6.2, G6.3, G7, G7.1, G7.2, G7.3), wherein the pedal crankshaft (WAn) is connected on the input side to at least one gear set element of the planetary gear sets (RS1, RS2, RS3) is connectable and / or connected, wherein the transmission output shaft (WAb) is connectable and / or connected on the output side to at least one gear set element of the planetary gear sets (RS1, RS2, RS3), and wherein at least two of the shift elements (B1, B2, B3, K1, K2, K3) are designed as a positive-locking brake and / or freewheel brake.Furthermore, a bicycle or pedelec (1) with a bottom bracket gear is proposed.

Description

The present invention relates to a bottom bracket transmission of planetary design for a bicycle or a pedelec with a bottom bracket shaft as drive and a transmission output shaft as output as well as further shafts, with at least three planetary gear sets and with at least five shift elements for realizing at least six gears. The invention further relates to a bicycle or pedelec with the bottom bracket transmission.For example, the document DE 10 2022 203 241 B3 discloses a bottom bracket transmission of planetary construction for a bicycle or pedelec. For the realization of six gears, the bottom bracket transmission comprises three planetary gear sets and five shift elements, wherein three of the shift elements are designed as brakes and two of the shift elements are designed as clutches.Accordingly, the object of the present invention is to provide a pedal transmission of the type described at the beginning with improved properties compared to the prior art.This object is achieved according to the invention by the features of patent claims 1 and 9. Advantageous and claimed developments are evident from the dependent claims and the description and the drawings.Thus, a bottom bracket transmission of planetary construction for a bicycle or a pedelec is proposed. The bottom bracket transmission has a crank shaft or transmission input shaft as drive and a transmission output shaft as output and further shafts, wherein the output is preferably effected via a sprocket, a belt wheel or the like. Furthermore, the bottom bracket transmission comprises three planetary gear sets, and at least five shift elements for realizing, for example, at least six gears in the proposed bottom bracket transmission. Furthermore, the pedal crank shaft is connectable and / or connected on the drive side to at least one gear set element of the planetary gear sets, wherein the transmission output shaft is connectable and / or connected on the output side to at least one gear set element of the planetary gear sets and wherein at least two of the shift elements are designed as a form-fit brake and / or freewheel brake.In this way, with the above-described connection, in the proposed bottom bracket transmission with only three planetary gear sets provided and at least five shift elements provided, a particularly simple and compact construction is realized in the bottom bracket transmission. In addition, particularly low component loads and an advantageously high gearing efficiency arise due to the geometric transmission range in the bottom bracket transmission.For the mechanical connection of elements, for example rotating elements or the like of the planetary gear sets, preferably, in addition to the drive and output, further shafts or shaft-like elements are used, wherein the term shaft is not to be understood exclusively as a cylindrical, rotatably mounted machine element for transmitting torques, but rather also to be understood as general connecting elements which connect the individual gear set elements to one another for transmitting torque.The shifting elements embodied as brakes and clutches are preferably embodied as form-locking shifting elements, for example as cost-effective brake claws or shifting claws or the like, for example with a toothed brake ring and a corresponding pawl. Brakes as shift elements have the advantage that they can be easily reached for actuation from the outside. In the case of clutches designed as freewheels, it is advantageous if the brakes are designed, for example, as one-way brakes, in order to prevent the transmission from blocking when the direction of rotation is reversed at the input or at the output. Preferably, freewheels or freewheel brakes that are not actively switchable or actuatable are used as freewheels or freewheel brakes. This has the advantage that no switching actuation is required in the passive switching elements. The non-operable one-way clutch transmits a torque when it locks in the lock-up direction state. No torque is transmitted in the opposite direction of rotation, since the freewheel does not block in the overrun drive state. However, it is conceivable that actively switchable freewheels or also actively switchable freewheel brakes are also used.A preferred embodiment of the invention can provide that at least one of the planetary gear sets provided is designed as a minus planetary gear set, resulting in an arrangement which is particularly advantageous in terms of installation space. It is also conceivable for one of the planetary gear sets to be designed as a plus planetary gear set.A minus planetary gear set can preferably be transferred into a plus planetary gear set if the planetary gear carrier and ring gear connection on this gear set is interchanged with one another and the amount of the stationary transmission ratio is increased by 1. A minus planetary gear set has planetary gears rotatably mounted 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 direction opposite to the sun gear rotation direction when the planetary gear carrier is held stationary and the sun gear rotates. A plus planetary gear set has inner and outer planetary gears rotatably mounted on its planetary gear carrier and in meshing engagement with one another, wherein the sun gear of this planetary gear set meshes with the inner planetary gears and the ring gear of this planetary gear set meshes with the outer planetary gears, so that the ring gear rotates in the same direction of rotation as the sun gear direction when the planetary gear carrier is held stationary and the sun gear rotates.In order to further optimize the control of the proposed bottom bracket transmission, it is provided that at least one torque sensor or the like is provided on the drive and / or on the output.In order to electrically support the drive in the proposed bottom bracket transmission, at least one electric machine or the like can be connected or connectable or permanently or releasably coupled to the drive or to the crank shaft or transmission input shaft and / or to the output or to the transmission output shaft. The electric machine can preferably be arranged axially parallel to the pedal crankshaft or transmission input shaft, while the planetary gear sets are arranged coaxially to the pedal crankshaft or transmission input shaft.In the proposed bottom bracket transmission, the electric machine can be connectable to the pedal crankshaft or to the transmission output shaft via a freewheel or the like. Furthermore, the pedal crank can be connectable to the transmission input of the transmission via a freewheel or the like.A further aspect of the present invention claims a bicycle or pedelec with the above-described bottom bracket transmission. This results in the advantages and further advantages already described.The present invention is explained in more detail below with reference to the drawings. FIG. 1 shows a schematic basic view of a bottom bracket transmission according to the invention on a bicycle or a pedelec with a torque sensor on the drive indicated by way of example; FIG. 2 shows a schematic basic view of the bottom bracket transmission according to FIG. 1 with an electric machine arranged by way of example on the drive; FIG. 3 shows a schematic basic view of the bottom bracket transmission according to FIG. 1 with an electric machine arranged by way of example on the output; and FIG. 4 shows a schematic basic view of the pedal bearing transmission according to FIG. 1 with a freewheel provided between a pedal crank and the transmission input; and FIGS. 5 to 67 show various embodiments of the bottom bracket transmission according to the invention with a shift pattern associated therewith.FIGS. 1 to 4 show various embodiments of a bottom bracket transmission according to the invention in planetary construction only by way of example. FIG. 1 shows, by way of example, a bicycle or pedelec 1 with the bottom bracket transmission, which is only indicated schematically.The pedal transmission is shown in a housing or pedal housing 2 with a pedal crankshaft or pedal crank with pedals, wherein the pedal crankshaft WAn is connected to a transmission input of a transmission 4, indicated only schematically. Furthermore, the bottom bracket transmission comprises a transmission output shaft WAb as output with a chain wheel or belt wheel, not shown in any more detail.As can be seen from the specific exemplary embodiments illustrated in FIGS. 5 to 67, the transmission 4 comprises a first planetary gear set RS 1 and a second planetary gear set RS 2 and a third planetary gear set RS 3, which have at least five shift elements B 1, B 2, B 3, K 1, K 2, K 3 for realizing a plurality of gears G 1, G 1.1, G 1.2, G 1.3, G 2, G 2.1, G 2. 2, G2.3, G3, G4, G5, G5.1, G5.2, G5.3, G6, G6.1, G6.2, G6.3, G7, G7.1, G7.2, G7.3. The planetary gear sets R 1, RS 2, RS 3 each have, as gear set elements, a sun gear SR 1, SR 2, SR 3 and a planetary gear carrier PT 1, PT 2, PT 3 and a ring gear HR 1, HR 2, HR 3.The pedal crankshaft or transmission input shaft WAn can be connected and / or is connected on the drive side to at least one gear set element of the planetary gear sets RS 1, RS 2, RS 3, wherein the transmission output shaft WAb can be connected and / or is connected on the output side to at least one gear set element of the planetary gear sets RS 1, RS 2, RS 3, and wherein at least two of the shift elements B 1, B 2, B 3, K 1, K 2, K 3 are designed as a form-fit brake and / or freewheel brake.The planetary gear sets RS 1, RS 2, RS 3 are designed as space-saving minus planetary gear sets, for example, except for the exemplary embodiment according to FIG. 32, in which the first planetary gear set RS 1 is designed as a plus planetary gear set.FIG. 1 shows an embodiment of the bottom bracket transmission according to the invention, in which a torque sensor 3 is connected or connectable to the pedal crankshaft or to the transmission input shaft WAn. For example, a disk-shaped torque sensor 3 can be arranged at the transmission input. However, the torque sensor 3 can also be implemented in a different manner.FIGS. 2 and 3 each show an embodiment of the bottom bracket transmission according to the invention with an additional electric machine EM on the basis of FIG. 1. The electric machine EM can be connected to the pedal crankshaft WAn, as is indicated in FIG. 2. It is also conceivable for the electric machine EM to be connected to the transmission output shaft WAb, as shown in FIG. 3. The electric machine EM is preferably arranged axially parallel to the pedal crankshaft or transmission input shaft WAn. However, a coaxial arrangement of the electric machine EM with respect to the pedal crankshaft would also be possible. Independently of this, it is advantageous to connect the electric machine EM via a freewheel F 0 or the like, so that no losses are caused by the co-rotating electric machine EM during operation without the electric machine EM.FIG. 4 shows an embodiment of the pedal bearing transmission according to the invention with reference to FIG. 1 with an additional freewheel F 1 between the pedal crank and the transmission input of the transmission 4. In this way, in the event of a pedaling interruption, the freewheel can open and decouple the pedal crank from the inertial masses of the gear wheel set and in particular of the electric machine EM, so that no mass forces can be perceptible at the pedal.For each exemplary embodiment in FIGS. 5 to 67, a shift pattern for the respective exemplary embodiment of the bottom bracket transmission is shown as a multi-speed transmission, so that a total of six or seven gears G 1, G 1.1, G 1.2, G 1.3, G 2, G 2.1, G 2. 2, G2.3, G3, G4, G5, G5.1, G5.2, G5.3, G6, G6.1, G6.2, G6.3, G7, G7.1, G7.2, G7.3. In the shift pattern, the values for the respective gear G 1, G 1.1, G 1.2, G 1.3, G 2, G 2.1, G 2 are. 2, G2.3, G3, G4, G5, G5.1, G5.2, G5.3, G6, G6.1, G6.2, G6.3, G7, G7.1, G7.2, G7.3. In this case, an X or O in the case of a freewheel and a freewheel brake as shift elements in the shift pattern means that the freewheel or the freewheel brake blocks. This works automatically without external actuation. Furthermore, an X or O in the case of a brake and in the case of a clutch as a shift element in the shift pattern means that the brake and the clutch are closed. This functions via a suitable actuator system. An empty field in the case of the freewheel or the freewheel brake as switching elements means in the shift pattern that they do not block. An empty field in the brake and the clutch K 1 means in the shift pattern that they are open.In an exemplary embodiment according to FIG. 5, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2 and to a sun gear SR 3 of the third planetary gear set RS 3, that a ring gear HR 2 of the second planetary gear set RS 2 is connected via a second shaft W 2 to a planet carrier PT 1 of the first planetary gear set RS 1, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a third shaft W3 and via a positively locking shift element B2 designed as a brake and can be connected to the transmission output shaft WAb via a shift element K2 designed as a freewheel and via a positively locking shift element K3 designed as a clutch and via a fourth shaft W4 to a planet carrier PT3 of the third planetary gear set RS3, and a ring gear HR 3 of the third planetary gear set RS 3 being connected to the housing 2 via a fixed housing connection W 0. Overall, in the exemplary embodiment according to the shift pattern in FIG. 5, six gears result.In an exemplary embodiment according to FIG. 6, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connectable via a positively locking shift element K 3 designed as a clutch and via a fourth shaft W 4 to a sun gear SR 3 of the third planetary gear set RS 3, that a ring gear HR 2 of the second planetary gear set RS 2 is connected via a second shaft W 2 to a planet carrier PT 1 of the first planetary gear set RS 1, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a third shaft W3 and via a positively locking shift element B2 designed as a brake and is connected to a planet carrier PT3 of the third planetary gear set RS3, and the ring gear HR1 of the first planetary gear set RS1 can be connected to the transmission output shaft WAb via the third shaft W3 and via a shift element K2 designed as a freewheel, and a ring gear HR 3 of the third planetary gear set RS 3 being connected to the housing 2 via a fixed housing connection W 0. Overall, in the exemplary embodiment according to the shift pattern in FIG. 6, six gears result.In an exemplary embodiment according to FIG. 7, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2, that a ring gear HR 2 of the second planetary gear set RS 2 is connected to a planet carrier PT 1 of the first planetary gear set RS 1 via a second shaft W 2, that a sun gear SR 1 of the first planetary gear set RS 1 can be fixed to the housing 2 via a first shaft W 1 and via a positive-locking shift element B 1 designed as a brake, and can be connected to the pedal crank shaft WAn via a shift element K 1 designed as a freewheel, a ring gear HR1 of the first planetary gear set RS1 is connected via a third shaft W3 to a planet carrier PT3 of the third planetary gear set RS3, the ring gear HR1 of the first planetary gear set RS1 is connectable via the third shaft W3 and via a shifting element K2 designed as a freewheel to the transmission output shaft WAb, and a ring gear HR3 of the third planetary gear set RS3 is connected via a fixed housing connection W0 to the housing 2, and a sun gear SR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B2 designed as a brake and can be connected to the transmission output shaft WAb via a positively locking shift element K3 designed as a clutch. Overall, in the exemplary embodiment according to the shift pattern in FIG. 7, six gears result.In an exemplary embodiment according to FIG. 8, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2 and to a sun gear SR 3 of the third planetary gear set RS 3, that a ring gear HR 2 of the second planetary gear set RS 2 is connected via a second shaft W 2 to a planet carrier PT 1 of the first planetary gear set RS 1, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B2 designed as a brake and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, and a ring gear HR1 of the first planetary gear set RS1 is connected to a planet carrier PT3 of the third planetary gear set RS3 via a third shaft W3, and in that a ring gear HR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fifth shaft W5 and via a shifting element K3 designed as a freewheel and via a fourth shaft W4 and via a positively locking shifting element B1 designed as a brake, and in that a ring gear HR3 of the third planetary gear set RS3 can be connected to the third shaft W3 via a fifth shaft W5 and via a shifting element K3 designed as a freewheel and via a fourth shaft W4 and via a positively locking shifting element K2 designed as a clutch. Overall, in the exemplary embodiment according to the shift pattern in FIG. 8, six gears result.In an exemplary embodiment according to FIG. 9, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2 and to a sun gear SR 3 of the third planetary gear set RS 3, that a ring gear HR 2 of the second planetary gear set RS 2 is connected via a second shaft W 2 to a planet carrier PT 1 of the first planetary gear set RS 1, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B2 designed as a brake and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, and a ring gear HR1 of the first planetary gear set RS1 can be connected to a planet carrier PT3 of the third planetary gear set RS3 via a third shaft W3 and via a shift element K2 designed as a freewheel and via a fifth shaft W5, and a ring gear HR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B1 designed as a brake and can be connected to the third shaft W3 via a positively locking shift element K3 designed as a clutch. Overall, in the exemplary embodiment according to the shift pattern in FIG. 9, six gears result.In an exemplary embodiment according to FIG. 10, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2, that a ring gear HR 2 of the second planetary gear set RS 2 is connected to a planet carrier PT 1 of the first planetary gear set RS 1 via a second shaft W 2, that a sun gear SR 1 of the first planetary gear set RS 1 can be fixed to the housing 2 via a first shaft W 1 and via a positive-locking shift element B 1 designed as a brake, and can be connected to the pedal crank shaft WAn via a shift element K 1 designed as a freewheel, a ring gear HR1 of the first planetary gear set RS1 is connected via a third shaft W3 to a planet carrier PT3 of the third planetary gear set RS3, and a ring gear HR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B2 designed as a brake, a sun gear SR3 of the third planetary gear set RS3 can be connected to the transmission output shaft WAb via a fifth shaft W5 and via a positively locking shift element K2 designed as a freewheel, and in that, in a first blocking variant, the ring gear HR3 of the third planetary gear set RS3 can be connected to the sun gear SR3 of the third planetary gear set RS3 via a positively locking shift element K3 designed as a clutch, wherein, in the context of two further blocking variants, the sun gear SR3 and the planet carrier PT3 of the third planetary gear set and the planet carrier and the ring gear HR3 of the third planetary gear set RS3 can be connected via the positively locking shift element K3 designed as a clutch. Overall, in the exemplary embodiment according to the shift pattern in FIG. 10, six gears result.In an exemplary embodiment according to FIG. 11, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1 and to a sun gear SR 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a planet carrier PT 3 of the third planetary gear set RS 3, that a sun gear SR 1 of the first planetary gear set RS 1 is connected via a first shaft W 1 to a ring gear HR 3 of the third planetary gear set RS 3, a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a second shaft W2 and via a positively locking shift element B2 designed as a brake and is connected to the planet carrier PT2 of the second planetary gear set RS2 and can be connected to the planet carrier PT3 of the third planetary gear set RS3 via a shift element K1 designed as a freewheel, a ring gear HR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a third shaft W3 and via a positively locking shift element B1 designed as a brake, a sun gear SR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fourth shaft W4 and via a shift element B3 designed as a freewheel brake, and in that, in a first blocking variant, the sun gear SR 3 of the third planetary gear set RS 3 can be connected to the planet carrier PT 3 of the third planetary gear set RS 3 via a positively locking shift element K 2 designed as a clutch, wherein, in the context of a further blocking variant, the ring gear HR 3 and the planet carrier PT 3 of the third planetary gear set RS 3 can be connected via the positively locking shift element K 2 designed as a clutch. Overall, in the exemplary embodiment according to the shift pattern in FIG. 11, six gears result.In an exemplary embodiment according to FIG. 12, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1 and to a sun gear SR 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a planet carrier PT 3 of the third planetary gear set RS 3, that a sun gear SR 1 of the first planetary gear set RS 1 is connectable via a first shaft W 1 and via a shift element K 3 designed as a freewheel and via a fourth shaft to a ring gear HR 3 of the third planetary gear set RS 3 and is connectable via a positive shift element K 2 designed as a clutch to the transmission output shaft WAb, a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a second shaft W2 and via a positively locking shift element B2 designed as a brake and is connected to the planet carrier PT2 of the second planetary gear set RS2 and can be connected to the planet carrier PT3 of the third planetary gear set RS3 via a freely running shift element K1, a ring gear HR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a third shaft W3 and via a positively locking shift element B1 designed as a brake, and a sun gear SR3 of the third planetary gear set RS3 is fixed to the housing 2 via a fixed housing connection W0. Overall, in the exemplary embodiment according to the shift pattern in FIG. 12, six gears result.In an exemplary embodiment according to FIG. 13, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1, that the transmission output shaft WAb is connected to a planet carrier PT 2 of the second planetary gear set RS 2 and to a sun gear SR 3 of the third planetary gear set RS 3, that a ring gear HR 1 of the first planetary gear set RS 1 is connected via a third shaft W 3 to a sun gear SR 2 of the second planetary gear set RS 2, a ring gear HR2 of the second planetary gear set RS2 is connected via a first shaft W1 to a planet carrier PT3 of the third planetary gear set RS3 and can be fixed to the housing 2 via a shifting element B1 designed as a freewheel brake and can be connected via a positively locking shifting element K1 designed as a clutch to the pedal crankshaft WAn and the planet carrier PT1 of the first planetary gear set RS1, and a ring gear HR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a second shaft W2 and via a positively locking shifting element B2 designed as a brake, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B3 designed as a brake, and in order to block the first planetary gear set RS1, in a first blocking variant, the sun gear SR1 of the first planetary gear set RS1 can be connected to the planet carrier PT1 of the first planetary gear set RS1 via a positively locking shift element K2 designed as a freewheel, wherein, within the scope of a further blocking variant, the ring gear HR1 and the planet carrier PT1 of the first planetary gear set RS1 can be connected via the shift element K2 designed as a freewheel. Overall, in the exemplary embodiment according to the shift pattern in FIG. 13, six gears result.In an exemplary embodiment according to FIG. 14, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1, that the transmission output shaft WAb is connected to a planet carrier PT 2 of the second planetary gear set RS 2 and to a sun gear SR 3 of the third planetary gear set RS 3, that a ring gear HR 1 of the first planetary gear set RS 1 is connected via a third shaft W 3 to a sun gear SR 2 of the second planetary gear set RS 2, a ring gear HR2 of the second planetary gear set RS2 can be connected to a planet carrier PT3 of the third planetary gear set RS3 via a first shaft W1 and via a positive shift element K3 designed as a clutch, and can be fixed to the housing 2 via a shift element B1 designed as a freewheel brake, and can be connected to the pedal crankshaft WAn and the planet carrier PT1 of the first planetary gear set RS1 via a positive shift element K1 designed as a clutch, and a ring gear HR3 of the third planetary gear set RS3 is fixed to the housing 2 via a fixed housing connection W0, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B2 designed as a brake, and in order to block the first planetary gear set RS1, in a first blocking variant, the sun gear SR1 of the first planetary gear set RS1 can be connected to the planet carrier PT1 of the first planetary gear set RS1 via a positively locking shift element K2 designed as a freewheel, wherein, within the scope of a further blocking variant, the ring gear HR1 and the planet carrier PT1 of the first planetary gear set RS1 can be connected via the shift element K2 designed as a freewheel. Overall, in the exemplary embodiment according to the shift pattern in FIG. 14, six gears result.In an exemplary embodiment according to FIG. 15, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1, that the transmission output shaft WAb is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connectable via a positively locking shift element K 3 designed as a clutch and via a second shaft W 2 to a sun gear SR 3 of the third planetary gear set RS 3, that a ring gear HR 1 of the first planetary gear set RS 1 is connected via a third shaft W 3 to a sun gear SR 2 of the second planetary gear set RS 2, a ring gear HR2 of the second planetary gear set RS2 is connected to a planet carrier PT3 of the third planetary gear set RS3 and can be fixed to the housing 2 via a shifting element B1 designed as a freewheel brake and can be connected to the pedal crankshaft WAn and the planet carrier PT1 of the first planetary gear set RS1 via a positive shifting element K1 designed as a clutch, a ring gear HR3 of the third planetary gear set RS3 is fixed to the housing 2 via a fixed housing connection W0, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a fourth shaft W4 and via a positive shifting element B2 designed as a brake, and in that, in a first blocking variant, the sun gear SR 1 of the first planetary gear set RS 1 can be connected to the planet carrier PT 1 of the first planetary gear set RS 1 via a positively locking shift element K 2 designed as a freewheel, wherein, in the context of a further blocking variant, the ring gear HR 1 and the planet carrier PT 1 of the first planetary gear set RS 1 can be connected via the shift element K 2 designed as a freewheel. Overall, in the exemplary embodiment according to the shift pattern in FIG. 15, six gears result.In an exemplary embodiment according to FIG. 16, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1 and to a sun gear SR 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a planet carrier PT 3 of the third planetary gear set RS 3, that a sun gear SR 1 of the first planetary gear set RS 1 is connected via a first shaft W 1 to a ring gear HR 3 of the third planetary gear set RS 3, a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a second shaft W2 and via a positively locking shift element B1 designed as a brake and is connected to the planet carrier PT2 of the second planetary gear set RS2, a ring gear HR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a third shaft W3 and via a positively locking shift element B2 designed as a brake and can be connected to the planet carrier PT3 of the third planetary gear set RS3 via a shift element K1 designed as a freewheel, and a sun gear SR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fourth shaft W4 and via a shift element B3 designed as a freewheel brake, and in that, in order to block the third planetary gear set RS 3, within the scope of a first blocking variant, the sun gear SR 3 of the third planetary gear set RS 3 can be connected to the planet carrier PT 3 of the third planetary gear set RS 3 via a positively locking shift element K 2 designed as a clutch, wherein, within the scope of a further blocking variant, the planet carrier PT 3 and the ring gear HR 3 of the third planetary gear set RS 3 can be connected to one another via the positively locking shift element K 2 designed as a clutch. Overall, in the exemplary embodiment according to the shift pattern in FIG. 16, six gears result.In an exemplary embodiment according to FIG. 17, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1 and to a sun gear SR 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a planet carrier PT 3 of the third planetary gear set RS 3, that a sun gear SR 1 of the first planetary gear set RS 1 is connectable to the transmission output shaft WAb via a first shaft W 1 and via a shift element K 3 designed as a freewheel and via a fourth shaft W 4 and to a ring gear HR 3 of the third planetary gear set RS 3 and is connectable to the transmission output shaft WAb via a positive shift element K 2 designed as a clutch, a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a second shaft W2 and via a positively locking shift element B1 designed as a brake and is connected to the planet carrier PT2 of the second planetary gear set RS2, a ring gear HR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a third shaft W3 and via a positively locking shift element B2 designed as a brake and can be connected to the planet carrier PT3 of the third planetary gear set RS3 via a shift element K1 designed as a freewheel, and a sun gear SR3 of the third planetary gear set RS3 is fixed to the housing 2 via a fixed housing connection W0. Overall, in the exemplary embodiment according to the shift pattern in FIG. 17, six gears result.In an exemplary embodiment according to FIG. 18, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1, that the transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2 and to a planet carrier PT 3 of the third planetary gear set RS 3, that a ring gear HR 1 of the first planetary gear set RS 1 is connected via a first shaft W 1 to a sun gear SR 3 of the third planetary gear set RS 3, a planet carrier PT2 of the second planetary gear set RS2 is connected via a second shaft W2 to a ring gear HR3 of the third planetary gear set RS3 and can be fixed to the housing 2 via a shifting element B1 designed as a freewheel brake, a ring gear HR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a third shaft W3 and via a positively locking shifting element B2 designed as a brake, and can be connected to the pedal crank shaft WAn and to the planet carrier PT1 of the first planetary gear set RS1 via a positively locking shifting element K1 designed as a clutch, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B3 designed as a brake, and in order to block the first planetary gear set RS1, in a first blocking variant, the sun gear SR1 of the first planetary gear set RS1 can be connected to the planet carrier PT1 of the first planetary gear set RS1 via a positively locking shift element K2 designed as a freewheel, wherein, within the scope of a further blocking variant, the ring gear HR1 and the planet carrier PT1 of the first planetary gear set RS1 can be connected via the shift element K2 designed as a freewheel. Overall, in the exemplary embodiment according to the shift pattern in FIG. 18, six gears result.In an exemplary embodiment according to FIG. 19, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1, that the transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2 and to a planet carrier PT 3 of the third planetary gear set RS 3, that a ring gear HR 1 of the first planetary gear set RS 1 is connectable via a fourth shaft W 4 and via a positive shift element K 3 designed as a clutch and via a first shaft W 1 to a sun gear SR 3 of the third planetary gear set RS 3, a sun gear SR3 of the third planetary gear set RS3 is connectable to the pedal crank shaft WAn via a first shaft W1 and via a shifting element K2 designed as a freewheel, a planet carrier PT2 of the second planetary gear set RS2 is connected to a ring gear HR3 of the third planetary gear set RS3 via a second shaft W2 and is fixable to the housing 2 via a shifting element B1 designed as a freewheel brake, a ring gear HR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a third shaft W3 and via a positive shift element B2 designed as a brake, and can be connected to the pedal crankshaft WAn and to the planet carrier PT1 of the first planetary gear set RS1 via a positive shift element K1 designed as a clutch, and a sun gear SR1 of the first planetary gear set RS1 is fixed to the housing 2 via a fixed housing connection W0. Overall, in the exemplary embodiment according to the shift pattern in FIG. 19, six gears result.In an exemplary embodiment according to FIG. 20, it is provided that the pedal crankshaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1 and to a sun gear SR 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connectable via a shifting element K 2 designed as a freewheel to a planet carrier PT 3 of the third planetary gear set RS 3, that a sun gear SR 1 of the first planetary gear set RS 1 is connected via a first shaft W 1 to a ring gear HR 3 of the third planetary gear set RS 3 and is connectable via a positive shifting element K 1 designed as a clutch to the transmission output shaft WAb, a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a second shaft W2 and via a positively locking shift element B1 designed as a brake and is connected to the planet carrier PT2 of the second planetary gear set RS2, a ring gear HR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a third shaft W3 and via a positively locking shift element B2 designed as a brake and can be connected to the planet carrier PT3 of the third planetary gear set RS3 via a shift element K3 designed as a freewheel and via a fourth shaft W4, and a sun gear SR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fifth shaft W5 and via a positively locking shift element B3 designed as a brake. Overall, in the exemplary embodiment according to the shift pattern in FIG. 20, seven gears are obtained, alternative sixth gears G 6.1, G 6.2, G 6.3 and alternative seventh gears G 7.1, G 7.2, G 7.3 being provided.In an exemplary embodiment according to FIG. 21, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a planet carrier PT 3 of the third planetary gear set RS 3, that a ring gear HR 2 of the second planetary gear set RS 2 is connected via a second shaft W 2 to a planet carrier PT 1 of the first planetary gear set RS 1, that a sun gear SR 2 of the second planetary gear set RS 2 is connected via a fourth shaft W 4 to a sun gear SR of three of the third planetary gear set RS 3, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a third shaft W3 and via a positively locking shift element B2 designed as a brake and can be connected to a planet carrier PT3 of the third planetary gear set RS3 and to the transmission output shaft WAb via a positively locking shift element K2 designed as a clutch, the ring gear HR1 of the first planetary gear set RS1 is connectable via the third shaft W3 and via a shifting element K3 designed as a freewheel to the sun gear SR2 of the second planetary gear set R2 and to the sun gear SR3 of the third planetary gear set RS3, and a ring gear HR3 of the third planetary gear set RS2 is connected to the housing 2 via a fixed housing connection W0. Overall, in the exemplary embodiment according to the shift pattern in FIG. 21, six gears result.In an exemplary embodiment according to FIG. 22, it is provided that the pedal crankshaft WAn is connected to a planet gear carrier PT 1 and can be connected via a positively locking shift element K 1 designed as a clutch and via a third shaft W 3 to a planet gear carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a ring gear HR 3 of the third planetary gear set RS 3, that a sun gear SR 1 of the first planetary gear set RS 1 is connected via a second shaft W 2 to a ring gear HR 2 of the second planetary gear set RS 2 and to a planet gear carrier PT 3 of the third planetary gear set RS 3, a sun gear SR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B2 designed as a brake and can be connected to the planet carrier PT2 of the second planetary gear set RS2 via a shift element K3 designed as a freewheel and via the third shaft W3, a sun gear SR2 of the second planetary gear set RS2 is fixed to the housing 2 via a fixed housing connection W0, and a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake, and in that, in order to block the first planetary gear set RS 1, within the scope of a first blocking variant, the sun gear SR 1 and the planet carrier PT 1 of the first planetary gear set RS 1 can be connected via a shifting element K 2 designed as a freewheel, wherein a further blocking variant provides that the planet carrier PT 1 and the ring gear HR 1 can be connected to one another via the shifting element K 2. Overall, in the exemplary embodiment according to the shift pattern in FIG. 22, six gears result.In an exemplary embodiment according to FIG. 23, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1, that the transmission output shaft WAb is connected to a planet carrier PT 3 of the third planetary gear set RS 3, that a ring gear HR 1 of the first planetary gear set RS 1 is connected via a second shaft W 2 to a sun gear SR 2 of the second planetary gear set RS 2 and to a ring gear HR 3 of the third planetary gear set RS 3, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake, and can be connected to a planet carrier PT2 of the second planetary gear set RS2 via a shift element K3 designed as a freewheel and a third shaft W3, the planet carrier PT2 of the second planetary gear set RS2 can be connected to the transmission output shaft WAb via a third shaft W3 and via a shift element K1 designed as a freewheel, and a ring gear HR2 of the second planetary gear set RS2 is fixed to the housing 2 via a fixed housing connection W0, a sun gear SR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B2 designed as a brake, and for blocking the third planetary gear set RS3, within the scope of a first blocking variant, the sun gear SR3 and the planet carrier PT3 of the third planetary gear set RS3 can be connected via a positively locking shift element K2 designed as a clutch, wherein, in a further blocking variant, the planet carrier PT3 and the ring gear HR3 of the third planetary gear set RS3 can be connected via the positively locking shift element K2 designed as a clutch. Overall, in the exemplary embodiment according to the shift pattern in FIG. 23, six gears result.In an exemplary embodiment according to FIG. 24, it is provided that the pedal crank shaft WAn is connected to a sun gear SR 1 of the first planetary gear set RS 1 and to a planet carrier PT 2 of the second planetary gear set RS 2, wherein the transmission output shaft WAb is connected to a ring gear HR 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 can be fixed to the housing 2 via a first shaft W 1 and via a positive shift element B 1 designed as a brake and is connected to a ring gear HR 2 of the second planetary gear set RS 2, a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a second shaft W2 and via a positively locking shift element B2 designed as a brake and can be connected to a planet carrier PT3 of the third planetary gear set RS3 via a shift element K2 designed as a freewheel and a third shaft W3, and the planet carrier PT3 of the third planetary gear set RS3 can be connected to a sun gear SR2 of the second planetary gear set RS2 via a third shaft W3 and via a positively locking shift element K3 designed as a clutch and a fourth shaft W4, the sun gear SR2 of the second planetary gear set RS2 can be connected to the transmission output shaft WAb via the fourth shaft W4 and via a shifting element K1 designed as a freewheel, and a sun gear SR3 of the third planetary gear set RS3 is fixed to the housing 2 via a fixed housing connection W0. Overall, in the exemplary embodiment according to the shift pattern in FIG. 24, six gears result.In an exemplary embodiment according to FIG. 25, it is provided that the pedal crankshaft WAn is connected to a planet carrier PT 3 of the third planetary gear set RS 3, that the transmission output shaft WAb is connected to a sun gear SR 3 of the third planetary gear set RS 3, that a sun gear SR 1 of the first planetary gear set and a sun gear SR 2 of the second planetary gear set RS 2 can be fixed to the housing 2 via a first shaft W 1 and via a positive shift element B 1 designed as a brake, and can be connected to the pedal crankshaft WAn via a positive shift element K 1 designed as a clutch, a planet carrier PT1 of the first planetary gear set RS1 can be fixed to the housing 2 via a second shaft W2 and via a positively locking shift element B3 designed as a brake, a ring gear HR1 of the first planetary gear set RS1 is connected to a planet carrier PT2 of the second planetary gear set RS2 and to a ring gear HR3 of the third planetary gear set RS3 via a third shaft W3, and a ring gear HR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B2 designed as a brake, and can be connected to the transmission output shaft WAb via a shift element K2 designed as a freewheel. Overall, in the exemplary embodiment according to the shift pattern in FIG. 25, six gears are obtained, three alternative fifth gears G 5.1, G 5.2, G 5.3 being provided.In an exemplary embodiment according to FIG. 26, it is provided that the pedal crankshaft WAn is connected to a planet carrier PT 3 of the third planetary gear set RS 3, that the transmission output shaft WAb is connected to a sun gear SR 3 of the third planetary gear set RS 3, that a sun gear SR 2 of the second planetary gear set RS 2 can be fixed to the housing 2 via a first shaft W 1 and via a positive shift element B 1 designed as a brake, and can be connected to the pedal crankshaft WAn via a positive shift element K 1 designed as a clutch, and can be connected to a sun gear SR 1 of the first planetary gear set RS 1 via a positive shift element K 3 designed as a clutch, and via a second shaft W 2, a planet carrier PT1 of the first planetary gear set RS1 is fixed to the housing 2 via a fixed housing connection W0, a ring gear HR1 of the first planetary gear set RS1 is connected to a planet carrier PT2 of the second planetary gear set RS2 and to a ring gear HR3 of the third planetary gear set RS3 via a third shaft W3, and a ring gear HR2 of the second planetary gear set RS2 is fixable to the housing 2 via a fourth shaft W4 and via a positive shift element B2 designed as a brake and is connectable to the transmission output shaft WAb via a shift element K2 designed as a freewheel. Overall, in the exemplary embodiment according to the shift pattern in FIG. 26, six gears are obtained, three alternative fifth gears G 5.1, G 5.2, G 5.3 being provided.In an exemplary embodiment according to FIG. 27, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 3 of the third planetary gear set RS 3, that the transmission output shaft WAb is connected to a sun gear SR 3 of the third planetary gear set RS 3, that a sun gear SR 1 of the first planetary gear set RS 1 and a sun gear SR 2 of the second planetary gear set RS 2 can be fixed to the housing 2 via a first shaft W 1 and via a positive shift element B 1 designed as a brake and can be connected to the pedal crank shaft WAn via a positive shift element K 1 designed as a clutch, a planet carrier PT1 of the first planetary gear set RS1 is fixed to the housing 2 via a fixed housing connection W0, a ring gear HR1 of the first planetary gear set RS1 is fixable to the housing 2 via a second shaft W2 and via a positively locking shift element K3 designed as a clutch and via a third shaft W3 to a planet carrier PT2 of the second planetary gear set RS2 and to a ring gear HR3 of the third planetary gear set RS3, and a ring gear HR2 of the second planetary gear set RS2 is fixable to the housing 2 via a fourth shaft W4 and via a positively locking shift element B2 designed as a brake and is connectable to the transmission output shaft WAb via a shift element K2 designed as a freewheel. Overall, in the exemplary embodiment according to the shift pattern in FIG. 27, six gears are obtained, three alternative fifth gears G 5.1, G 5.2, G 5.3 being provided.In an exemplary embodiment according to FIG. 28, it is provided that the crank shaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1, that the transmission output shaft WAb is connected to a sun gear SR 1 of the first planetary gear set RS 1, that a ring gear HR 1 of the first planetary gear set is connectable via a first shaft W 1 to a planet carrier PT 2 of the second planetary gear set RS 2 and to a ring gear HR 3 of the third planetary gear set RS 3, that a sun gear SR 2 of the second planetary gear set RS 2 and a sun gear SR 3 of the third planetary gear set RS 3 are fixable to the housing 2 via a second shaft W 2 and via a positive-locking shift element B 1 designed as a brake, a ring gear HR2 of the second planetary gear set RS2 can be fixed on the housing two via a third shaft W3 and via a positive shift element B2 designed as a brake and can be connected to the pedal crankshaft WAn via a positive shift element K1 designed as a clutch, and a planet carrier PT3 of the third planetary gear set RS3 can be fixed on the housing 2 via a fourth shaft W4 and via a positive shift element B3 designed as a brake and can be connected to the transmission output shaft WAb via a shift element K2 designed as a freewheel. Overall, in the exemplary embodiment according to the shift pattern in FIG. 28, six gears are obtained, three alternative sixth gears G 6.1, G 6.2, G 6.3 being provided.In an exemplary embodiment according to FIG. 29, it is provided that the pedal crankshaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that a transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2, that a sun gear SR 1 of the first planetary gear set RS 1 can be fixed to the housing 2 via a first shaft W 1 and via a positive-locking shift element B 1 designed as a brake and can be connected to the pedal crankshaft WAn via a positive-locking shift element K 1 designed as a clutch, a planet carrier PT1 of the first planetary gear set RS1 is connected via a second shaft W2 to a ring gear HR2 of the second planetary gear set RS2 and to a ring gear HR3 of the third planetary gear set RS3, a ring gear HR1 of the first planetary gear set RS1 is fixable to the housing 2 via a third shaft W3 and via a positive shift element B2 designed as a brake and is connected to a planet carrier PT3 of the third planetary gear set RS3 and is connectable to the transmission output shaft WAb via a shift element K2 designed as a freewheel, and a sun gear SR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B3 designed as a brake. Overall, in the exemplary embodiment according to the shift pattern in FIG. 29, six gears are obtained, three alternative sixth gears G 6.1, G 6.2, G 6.3 being provided.In an exemplary embodiment according to FIG. 30, it is provided that the pedal crankshaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that a transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2, that a sun gear SR 1 of the first planetary gear set RS 1 can be fixed to the housing 2 via a first shaft W 1 and via a positive-locking shift element B 3 designed as a brake and can be connected to the pedal crankshaft WAn via a positive-locking shift element K 1 designed as a clutch, a ring gear HR1 of the first planetary gear set RS1 is connected via a third shaft W3 to a ring gear HR2 of the second planetary gear set RS2 and to a planet carrier PT3 of the third planetary gear set RS3, a planet carrier PT1 of the first planetary gear set RS1 is fixable to the housing 2 via a second shaft W2 and via a positive shift element B2 designed as a brake and is connected to a ring gear HR3 of the third planetary gear set RS3, and a sun gear SR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B1 designed as a brake and can be connected to the transmission output shaft WAb via a shift element K2 designed as a freewheel. Overall, in the exemplary embodiment according to the shift pattern in FIG. 30, six gears are obtained, three alternative fifth gears G 5.1, G 5.2, G 5.3 being provided.In an exemplary embodiment according to FIG. 31, it is provided that the pedal crankshaft WAn is connected to a planet carrier PT 3 of the third planetary gear set RS 3, that the transmission output shaft WAb is connected to a sun gear SR 3 of the third planetary gear set RS 3, that a sun gear SR 1 of the first planetary gear set RS 1 can be fixed to the housing 2 via a first shaft W 1 and via a positive-locking shift element B 1 designed as a brake, a ring gear HR1 of the first planetary gear set RS1 and a sun gear SR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a third shaft W3 and via a positively locking shift element B2 designed as a brake and can be connected to the pedal crankshaft WAn via a positively locking shift element K1 designed as a clutch, and a planet carrier PT1 of the first planetary gear set RS1 is connected via a second shaft W2 to a planet carrier PT2 of the second planetary gear set RS2 and to a ring gear HR3 of the third planetary gear set RS3, and a ring gear HR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B3 designed as a brake and can be connected to the transmission output shaft WAb via a shift element K2 designed as a freewheel. Overall, in the exemplary embodiment according to the shift pattern in FIG. 31, six gears are obtained, three alternative sixth gears G 6.1, G 6.2, G 6.3 being provided.In an exemplary embodiment according to FIG. 32, it is provided that the first planetary gear set RS 1 is designed as a plus planetary gear set, while the two other planetary gear sets RS 2 and RS 3 are designed as usual minus planetary gear sets. It is provided that the pedal crank shaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1 and to a planet carrier PT 3 of the third planetary gear set RS 3, that the transmission output shaft WAb is connected to a sun gear SR 3 of the third planetary gear set, that a sun gear SR 1 of the first planetary gear set RS 1 and a sun gear SR 2 of the second planetary gear set RS 2 can be fixed to the housing 2 via a first shaft W 1 and via a positive shift element B 1 designed as a brake, that a ring gear HR 1 of the first planetary gear set RS 1 can be fixed to the housing 2 via a second shaft W 2 and via a positive shift element B 2 designed as a brake, a ring gear HR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B3 designed as a brake and can be connected to the transmission output shaft WAb via a shift element K2 designed as a freewheel, a planet carrier PT2 of the second planetary gear set RS2 can be connected to a ring gear HR3 of the third planetary gear set via a third shaft W3, and for blocking the first planetary gear set RS1, within the scope of a first blocking variant, the sun gear SR1 can be connected to the planet carrier PT1 of the first planetary gear set RS1 via a shift element K1 designed as a freewheel, two further blocking variants being possible, in which, on the one hand, the sun gear SR1 and the ring gear HR1 and, on the other hand, the planet carrier PT1 and the ring gear HR1 can be connected in each case via the shifting element K1. Overall, in the exemplary embodiment according to the shift pattern in FIG. 32, six gears result.In an exemplary embodiment according to FIG. 33, it is provided that the pedal crank shaft WAn is connected to a ring gear HR 1 of the first planetary gear set RS 1, that the transmission output shaft WAb is connected to a sun gear SR 3 of the third planetary gear set RS 3, that a planet carrier PT 2 of the second planetary gear set RS 2 is connected via a fourth shaft W 4 to a ring gear HR 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected via a first shaft W 1 to a planet carrier PT 3 of the third planetary gear set RS 3, a sun gear SR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a third shaft W3 and via a positively locking shift element B1 designed as a brake and can be connected to a sun gear SR1 of the first planetary gear set RS1 via a shift element K3 designed as a freewheel and via a second shaft W2, a ring gear HR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a fifth shaft W5 and via a positively locking shift element B2 designed as a brake and can be connected to the transmission output shaft WAb via a shift element K2 designed as a freewheel, and in that, in order to block the first planetary gear set RS 1, within the scope of a first blocking variant, the ring gear HR 1 can be connected to the sun gear SR 1 of the first planetary gear set RS 1 via a positively locking shift element K 1 designed as a clutch, wherein, within the scope of further blocking variants, on the one hand, the sun gear SR 1 and the planet carrier PT 1 and, on the other hand, the planet carrier PT 1 and the ring gear HR 1 can each be connected via the shift element K 1. Overall, in the exemplary embodiment according to the shift pattern in FIG. 33, six gears result.In an exemplary embodiment according to FIG. 34, it is provided that the pedal crank shaft WAn is connected to a ring gear HR 1 of the first planetary gear set RS 1, that the transmission output shaft WAb is connected to a sun gear SR 3 of the third planetary gear set RS 3, that a planetary gear carrier PT 2 of the second planetary gear set RS 2 is connected to a ring gear HR 3 of the third planetary gear set RS 3 via a fourth shaft W 4, a planet carrier PT3 of the third planetary gear set RS3 can be connected to a planet carrier PT1 of the first planetary gear set RS1 via a first shaft W1 and via a shifting element K3 designed as a freewheel and a second shaft W2 and can be connected to the pedal crankshaft WAn via a positively locking shifting element K1 designed as a clutch, and a sun gear SR1 of the first planetary gear set RS1 and a sun gear SR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a third shaft W3 and via a positively locking shifting element B1 designed as a brake, and a ring gear HR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a fifth shaft W5 and via a positively locking shift element B2 designed as a brake and can be connected to the transmission output shaft WAb via a shift element K2 designed as a freewheel. Overall, in the exemplary embodiment according to the shift pattern in FIG. 34, six gears result.In an exemplary embodiment according to FIG. 35, it is provided that the pedal crankshaft WAn can be connected via a shifting element K 3 designed as a freewheel and via a second shaft W 2 to a ring gear HR 1 of the first planetary gear set RS 1, that the transmission output shaft WAb is connected to a sun gear SR 3 of the third planetary gear set RS 3, that a planetary gear carrier PT 2 of the second planetary gear set RS 2 is connected via a fourth shaft W 4 to a ring gear HR 3 of the third planetary gear set RS 3, a planet carrier PT3 of the third planetary gear set RS3 is connectable via a first shaft W1 to a planet carrier PT1 of the first planetary gear set RS1 and is connectable via a positively locking shift element K1 designed as a clutch to the pedal crankshaft WAn, a sun wheel SR1 of the first planetary gear set RS1 and a sun wheel SR2 of the second planetary gear set RS2 being fixable to the housing 2 via a third shaft W3 and via a positively locking shift element B1 designed as a brake, and a ring gear HR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a fifth shaft W5 and via a positively locking shift element B2 designed as a brake and can be connected to the transmission output shaft WAb via a shift element K2 designed as a freewheel. Overall, in the exemplary embodiment according to the shift pattern in FIG. 35, six gears result.In an exemplary embodiment according to FIG. 36, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1, that the transmission output shaft WAb is connected to a ring gear HR 3 of the third planetary gear set RS 3, that a ring gear HR 1 of the first planetary gear set RS 1 is connected via a first shaft W 1 to a planet carrier PT 3 of the third planetary gear set RS 3, that a ring gear HR 2 of the second planetary gear set RS 2 is connected via a fifth shaft W 5 to a sun gear SR 3 of the third planetary gear set RS 3, a sun gear SR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a third shaft W3 and via a positively locking shift element B1 designed as a brake and can be connected to a sun gear SR1 of the first planetary gear set RS1 via a positively locking shift element K3 designed as a clutch and via a second shaft W2, a planet carrier PT2 of the second planetary gear set RS2 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B2 designed as a brake and can be connected to the transmission output shaft WAb via a shift element K1 designed as a freewheel, and in that, in order to block the first planetary gear set RS 1 within the scope of a first blocking variant, the sun gear SR 1 can be connected to the ring gear HR 1 of the first planetary gear set RS 1 via a shifting element K 2 designed as a freewheel, wherein within the scope of further blocking variants, on the one hand, the sun gear SR 1 and the planet carrier PT 1 and, on the other hand, the ring gear HR 1 and the planet carrier PT 1 can be connected to one another via the shifting element K 2. Overall, in the exemplary embodiment according to the shift pattern in FIG. 36, six gears result.In an exemplary embodiment according to FIG. 37, it is provided that the pedal crankshaft WAn is connectable via a positively locking shift element K 3 designed as a clutch and via a second shaft W 2 to a planet carrier PT 1 of the first planetary gear set RS 1, that the transmission output shaft WAb is connected to a ring gear HR 3 of the third planetary gear set RS 3, that a ring gear HR 1 of the first planetary gear set RS 1 is connected via a first shaft W 1 to a planet carrier PT 3 of the third planetary gear set RS 3 and is connectable via a shift element K 2 designed as a freewheel to the pedal crankshaft WAn, a ring gear HR2 of the second planetary gear set RS2 is connected via a fifth shaft W5 to a sun gear SR3 of the third planetary gear set RS3, a sun gear SR1 of the first planetary gear set RS1 and a sun gear SR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a third shaft W3 and via a positively locking shift element B1 designed as a brake, and a planet carrier PT2 of the second planetary gear set RS2 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B2 designed as a brake, and can be connected to the transmission output shaft WAb via a shift element K1 designed as a freewheel.Overall, in the exemplary embodiment according to the shift pattern in FIG. 37, six gears result.In its own exemplary embodiment according to FIG. 38, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1, that the transmission output shaft WAb is connected to a ring gear HR 3 of the third planetary gear set RS 3, that a planet carrier PT 3 of the third planetary gear set RS 3 is connectable via a first shaft W 1 and via a positive-locking shift element K 3 designed as a clutch and via a second shaft W 2 to a ring gear HR 1 of the first planetary gear set RS 1 and is connectable via a shift element K 2 designed as a freewheel to the pedal crank shaft WAn, a ring gear HR2 of the second planetary gear set RS2 is connected via a fifth shaft W5 to a sun gear SR3 of the third planetary gear set RS3, a sun gear SR1 of the first planetary gear set RS1 and a sun gear SR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a third shaft W3 and via a positively locking shift element B1 designed as a brake, and a planet carrier PT2 of the second planetary gear set RS2 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B2 designed as a brake, and can be connected to the transmission output shaft WAb via a shift element K1 designed as a freewheel. Overall, in the exemplary embodiment according to the shift pattern in FIG. 38, six gears result.In an exemplary embodiment according to FIG. 39, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a planet carrier PT 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected via a third shaft W 3 to a ring gear HR 2 of the second planetary gear set RS 2, that a sun gear SR 2 of the second planetary gear set RS 2 is connected via a fourth shaft W 4 to a ring gear HR 3 of the third planetary gear set RS 3, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a second shaft W2 and via a positively locking shift element B2 designed as a brake and can be connected to a sun gear SR3 of the third planetary gear set RS3 via a shift element K3 designed as a freewheel, and in that, in order to block the third planetary gear set RS 3, within the scope of a first blocking variant, the sun gear SR 3 of the third planetary gear set RS can be connected to the planet carrier PT 3 of the third planetary gear set RS 3 via a positively locking shift element K 2 designed as a clutch, wherein, within the scope of further blocking variants, on the one hand the sun gear SR 3 and the ring gear HR 3 of the third planetary gear set and on the other hand the planet carrier PT 3 and the ring gear HR 3 of the third planetary gear set can be connected via the shift element K 2. Overall, in the exemplary embodiment according to the shift pattern in FIG. 39, six gears result.In an exemplary embodiment according to FIG. 40, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a planet carrier PT 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected to a ring gear HR 2 of the second planetary gear set RS 2 via a third shaft W 3, a sun gear SR2 of the second planetary gear set RS2 can be connected via a fourth shaft W4 and via a shifting element K3 designed as a freewheel and via a fifth shaft W5 to a ring gear HR3 of the third planetary gear set RS3 and can be connected via a positively locking shifting element K2 designed as a clutch to the transmission output shaft WAb, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shifting element B1 designed as a brake and can be connected via a shifting element K1 designed as a freewheel to the pedal crank shaft WAn, and a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a second shaft W2 and via a positively locking shift element B2 designed as a brake and is connected to a sun gear SR3 of the third planetary gear set RS3. Overall, in the exemplary embodiment according to the shift pattern in FIG. 40, six gears result.In an exemplary embodiment according to FIG. 41, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connectable via a shifting element K 3 designed as a freewheel and via a fifth shaft W 5 to a planet carrier PT 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected via a third shaft W 3 to a ring gear HR 2 of the second planetary gear set RS 2, a sun gear SR2 of the second planetary gear set RS2 is connected via a fourth shaft W4 to a ring gear HR3 of the third planetary gear set RS3 and can be connected to the transmission output shaft WAb via a positively locking shift element K2 designed as a clutch, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake and can be connected to the pedal crank shaft WAn via a shift element K1 designed as a freewheel, and a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a second shaft W2 and via a positively locking shift element B2 designed as a brake and is connected to a sun gear SR3 of the third planetary gear set RS3. Overall, in the exemplary embodiment according to the shift pattern in FIG. 41, six gears result.In an exemplary embodiment according to FIG. 42, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1, that the transmission output shaft WAb is connected to a ring gear HR 1 of the first planetary gear set, that a sun gear SR 1 of the first planetary gear set RS 1 is connected via a first shaft W 1 to a sun gear SR 2 of the second planetary gear set RS 2, that a planet carrier PT 2 of the second planetary gear set RS 2 is connected via a second shaft W 2 to a planet carrier PT 3 of the third planetary gear set RS 3, a sun gear SR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B1 designed as a brake and can be connected via a shift element K3 designed as a freewheel and a third shaft W3 to a ring gear HR2 of the second planetary gear set RS2, and the ring gear HR2 of the second planetary gear set RS2 can be connected via the third shaft W3 and via a positively locking shift element K1 designed as a clutch to the pedal crankshaft WAn, and in that a ring gear HR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fifth shaft W5 and via a positively locking shift element B2 designed as a brake and can be connected to the transmission output shaft WAb via a shift element K2 designed as a freewheel. Overall, in the exemplary embodiment according to the shift pattern in FIG. 42, six gears result.In an exemplary embodiment according to FIG. 43, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connectable via a shifting element K 3 designed as a freewheel and via a second shaft W 2 to a planet carrier PT 3 of the third planetary gear set RS 3 and to a ring gear HR 1 of the first planetary gear set RS 1, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected via a third shaft W 3 to a ring gear HR 2 of the second planetary gear set RS 2, a sun gear SR2 of the second planetary gear set RS2 is connected via a fourth shaft W4 to a sun gear SR3 of the third planetary gear set RS3 and can be connected to the transmission output shaft WAb via a positively locking shift element K2 designed as a clutch, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B2 designed as a brake and can be connected to the pedal crank shaft WAn via a shift element K1 designed as a freewheel, and a ring gear HR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fifth shaft W5 and via a positively locking shift element B1 designed as a brake. Overall, in the exemplary embodiment according to the shift pattern in FIG. 43, six gears result.In an exemplary embodiment according to FIG. 44, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a planet carrier PT 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected to a ring gear HR 2 of the second planetary gear set RS 2 via a third shaft W 3, a sun gear SR2 of the second planetary gear set RS2 is connected via a fourth shaft W4 to a ring gear HR3 of the third planetary gear set RS3 and is connectable via a shifting element K2 designed as a free wheel and via a second shaft W2 to a ring gear HR1 of the first planetary gear set RS1, the ring gear HR1 of the first planetary gear set RS1 is connectable via the second shaft W2 and via a positive shifting element K3 designed as a clutch and a fifth shaft W5 to a sun gear SR3 of the third planetary gear set RS3, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B2 designed as a brake and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, and a sun gear SR3 of the third planetary gear set RS3 can be fixed to the housing 2 via the fifth shaft W5 and via a positively locking shift element B1 designed as a brake. Overall, in the exemplary embodiment according to the shift pattern in FIG. 44, six gears result.In an exemplary embodiment according to FIG. 45, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a sun gear SR 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected to a ring gear HR 2 of the second planetary gear set RS 2 via a third shaft W 3, a sun gear SR2 of the second planetary gear set RS2 can be connected via a fourth shaft W4 and via a positively locking shift element K3 designed as a clutch and via a second shaft W2 to a ring gear HR1 of the first planetary gear set RS1 and to a planet carrier PT3 of the third planetary gear set RS3, and can be connected via a freely locking shift element K2 to the transmission output shaft WAb, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B2 designed as a brake, and can be connected to the pedal crank shaft WAn via a freely locking shift element K1, and a ring gear HR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fifth shaft W5 and via a positive shift element B1 designed as a brake. Overall, in the exemplary embodiment according to the shift pattern in FIG. 45, six gears result.In an exemplary embodiment according to FIG. 46, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 3 of the third planetary gear set RS 3, that the transmission output shaft WAb is connected to a sun gear SR 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected via a third shaft W 3 to a ring gear HR 2 of the second planetary gear set RS 2, that a planet carrier PT 2 of the second planetary gear set RS 2 is connected via a fifth shaft W 5 to a ring gear HR 3 of the third planetary gear set RS 3, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake, and can be connected via a positively locking shift element K3 designed as a clutch and via a fourth shaft W4 to a sun gear SR2 of the second planetary gear set RS2, and a sun gear SR2 of the second planetary gear set RS2 can be connected via a fourth shaft W4 and via a shift element K1 designed as a freewheel to the pedal crankshaft WAn, and a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a second shaft W2 and via a positively locking shift element B2 designed as a brake and can be connected to the transmission output shaft WAb via a shift element K2 designed as a freewheel. Overall, in the exemplary embodiment according to the shift pattern in FIG. 46, six gears result.In an exemplary embodiment according to FIG. 47, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected via a third shaft W 3 to a ring gear HR 3 of the third planetary gear set RS 3, that a ring gear HR 2 of the second planetary gear set RS 2 is connected via a fourth shaft W 4 to a planet carrier PT 3 of the third planetary gear set RS 3, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, and a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a second shaft W2 and via a positively locking shift element B2 designed as a brake and can be connected to a sun gear SR3 of the third planetary gear set RS3 via a positively locking shift element K3 designed as a clutch and via a fifth shaft W5, the sun gear SR3 of the third planetary gear set RS3 can be connected to the transmission output shaft WAb via a fifth shaft W5 and via a shifting element K2 designed as a free wheel. Overall, in the exemplary embodiment according to the shift pattern in FIG. 47, six gears result.In an exemplary embodiment according to FIG. 48, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1, that the transmission output shaft WAb is connected to a sun gear SR 1 of the first planetary gear set RS 1, that a ring gear HR 1 of the first planetary gear set RS 1 is connected via a first shaft W 1 to a planet carrier PT 2 of the second planetary gear set RS 2, that a sun gear SR 2 of the second planetary gear set RS 2 is connected via a third shaft W 3 to a ring gear HR 3 of the third planetary gear set, a sun gear SR3 of the third planetary gear set RS3 can be fixed to the housing via a fourth shaft W4 and via a positively locking shift element B1 designed as a brake and can be connected via a positively locking shift element K3 designed as a clutch and via a second shaft W2 to a ring gear HR2 of the second planetary gear set RS2, and the ring gear HR2 of the second planetary gear set RS2 can be connected via a second shaft W2 and via a shift element K1 designed as a freewheel to the pedal crankshaft WAn, and a planet carrier PT3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fifth shaft W5 and via a positively locking shift element B2 designed as a brake and can be connected to the transmission output shaft WAb via a shift element K2 designed as a freewheel.Overall, in the exemplary embodiment according to the shift pattern in FIG. 48, six gears result.In an exemplary embodiment according to FIG. 49, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2 and to a sun gear SR 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected via a third shaft W 3 to a ring gear HR 2 of the second planetary gear set RS 2, that a ring gear HR 3 of the third planetary gear set RS 3 can be fixed to the housing 2 via a fourth shaft W 4 and via a positive-locking shift element B 1 designed as a brake, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B2 designed as a brake and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a second shaft W2 and via a positively locking shift element B3 designed as a brake and can be connected to a planet carrier PT3 of the third planetary gear set RS3 via a shift element K3 designed as a freewheel and via a fifth shaft W5, and in that, in order to block the third planetary gear set RS 3, within the scope of a first blocking variant, the sun gear SR 3 of the third planetary gear set RS 3 can be connected to the ring gear HR 3 of the third planetary gear set RS 3 via a shifting element K 2 designed as a freewheel, wherein, within the scope of further blocking variants, on the one hand the sun gear SR 3 and the planet carrier PT 3 of the third planetary gear set RS 3 and on the other hand the planet carrier PT 3 and the ring gear HR 3 of the third planetary gear set RS 3 can be connected to one another via the shifting element K 2. Altogether, six gears are thus obtained in the exemplary embodiment according to the shift pattern in FIG. 49.In an exemplary embodiment according to FIG. 50, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2 and to a sun gear SR 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected via a third shaft W 3 to a ring gear HR 2 of the second planetary gear set RS 2, that a ring gear HR 3 of the third planetary gear set RS 3 can be fixed to the housing 2 via a fourth shaft W 4 and via a positive-locking shift element B 1 designed as a brake, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B2 designed as a brake and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, and a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a second shaft W2 and via a positively locking shift element B3 designed as a brake and can be connected to a planet carrier PT3 of the third planetary gear set RS3 via a shift element K3 designed as a freewheel and via a fifth shaft W5, and can be connected to the transmission output shaft WAb via a shift element K2 designed as a freewheel. Altogether, six gears are thus obtained in the exemplary embodiment according to the shift pattern in FIG. 50.In an exemplary embodiment according to FIG. 51, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2 and to a sun gear SR 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected via a third shaft W 3 to a ring gear HR 2 of the second planetary gear set RS 2, a ring gear HR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B1 designed as a brake and can be connected via a shift element K3 designed as a freewheel and via a second shaft W2 to a ring gear HR1 of the first planetary gear set RS1, and the ring gear HR1 of the first planetary gear set RS1 can be connected via a second shaft W2 and via a shift element K2 designed as a freewheel to a planet carrier PT3 of the third planetary gear set RS3, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B2 designed as a brake and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, and a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via the second shaft W2 and via a positively locking shift element B3 designed as a brake. Altogether, six gears are thus obtained in the exemplary embodiment according to the shift pattern in FIG. 51.In an exemplary embodiment according to FIG. 52, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2 and to a sun gear SR 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected via a third shaft W 3 to a ring gear HR 2 of the second planetary gear set RS 2, a ring gear HR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fourth shaft W4 and via a shifting element K3 designed as a free wheel and via a fifth shaft W5 and via a positively locking shifting element B3 designed as a brake, the fifth shaft W5 can be connected to the transmission output shaft WAb via a shifting element K2 designed as a free wheel, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shifting element B2 designed as a brake, and can be connected to the pedal crank shaft WAn via a shifting element K1 designed as a free wheel, and a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via the second shaft W2 and via a positively locking shift element B1 designed as a brake and is connected to a planet carrier PT3 of the third planetary gear set RS3. Altogether, six gears are thus obtained in the exemplary embodiment according to the shift pattern in FIG. 52.In an exemplary embodiment according to FIG. 53, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2 and to a sun gear SR 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected via a third shaft W 3 to a ring gear HR 2 of the second planetary gear set RS 2, a ring gear HR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fourth shaft W4 and via a shift element K3 designed as a freewheel and via a fifth shaft W5 and via a positively locking shift element B3 designed as a brake, and the fifth shaft W5 can be connected via a shift element K2 designed as a freewheel and via a second shaft W2 to a planet carrier PT3 of the third planetary gear set RS3 and to a ring gear HR1 of the first planetary gear set RS1, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B2 designed as a brake and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, and a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via the second shaft W2 and via a positively locking shift element B1 designed as a brake and is connected to a planet carrier PT3 of the third planetary gear set RS3. Altogether, six gears are thus obtained in the exemplary embodiment according to the shift pattern in FIG. 53.In an exemplary embodiment according to FIG. 54, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2 and is connectable via a shifting element K 3 designed as a freewheel and via a fourth shaft W 4 to a sun gear SR 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected via a third shaft W 3 to a ring gear HR 2 of the second planetary gear set RS 2, a ring gear HR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fifth shaft W5 and via a positively locking shift element B3 designed as a brake, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake, and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, and a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via the second shaft W2 and via a positively locking shift element B2 designed as a brake and is connected to a planet carrier PT3 of the third planetary gear set RS3 and can be connected to the transmission output shaft WAb via a shift element K2 designed as a freewheel. Altogether, six gears are thus obtained in the exemplary embodiment according to the shift pattern in FIG. 54.In an exemplary embodiment according to FIG. 55, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2 and is connectable via a shifting element K 2 designed as a freewheel and via a fourth shaft W 4 to a sun gear SR 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected via a third shaft W 3 to a ring gear HR 2 of the second planetary gear set RS 2, a ring gear HR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fifth shaft W5 and via a positively locking shift element B3 designed as a brake and can be connected to the transmission output shaft WAb via a shift element K3 designed as a freewheel, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, and a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via the second shaft W2 and via a positively locking shift element B2 designed as a brake and is connected to a planet carrier PT3 of the third planetary gear set RS3. Altogether, six gears are thus obtained in the exemplary embodiment according to the shift pattern in FIG. 55.In an exemplary embodiment according to FIG. 56, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2 and is connectable via a shifting element K 2 designed as a freewheel and via a fourth shaft W 4 to a sun gear SR 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected via a third shaft W 3 to a ring gear HR 2 of the second planetary gear set RS 2, a ring gear HR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fifth shaft W5 and via a positively locking shift element B3 designed as a brake, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake, and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via the second shaft W2 and via a positively locking shift element B2 designed as a brake, and is connected to a planet carrier PT3 of the third planetary gear set RS3, and in that, in order to block the third planetary gear set RS 3, within the scope of a first blocking variant, the ring gear HR 3 of the third planetary gear set RS 3 can be connected to the sun gear SR 3 of the third planetary gear set RS 3 via a shifting element K 3 designed as a freewheel, wherein, within the scope of further blocking variants, on the one hand the sun gear SR 3 and the planet carrier PT 3 of the third planetary gear set and on the other hand the planet carrier PT 3 and the ring gear HR 3 of the third planetary gear set can be connected to one another via the shifting element K 3. Altogether, six gears are thus obtained in the exemplary embodiment according to the shift pattern in FIG. 56.In an exemplary embodiment according to FIG. 57, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected to a ring gear HR 2 of the second planetary gear set RS 2 via a third shaft W 3, that a sun gear SR 1 of the first planetary gear set RS 1 can be fixed to the housing 2 via a first shaft W 1 and via a positive-locking shift element B 1 designed as a brake, and can be connected to the pedal crank shaft WAn via a shift element K 1 designed as a freewheel, a ring gear HR1 of the first planetary gear set RS1 is connected via a second shaft W2 to a planet carrier PT3 of the third planetary gear set RS3 and can be connected via a shift element K2 designed as a freewheel to the transmission output shaft WAb, a sun gear SR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fourth shaft W4 and via a positive shift element B2 designed as a brake and can be connected to the transmission output shaft WAb via a shift element K3 designed as a freewheel, and a ring gear HR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fifth shaft W5 and via a positive shift element B3 designed as a brake. Altogether, six gears are thus obtained in the exemplary embodiment according to the shift pattern in FIG. 57, three alternative first gears G 1.1, G 1.2, G 1.3 and three alternative second gears G 2.1, G 2.2, G 2.3 being provided.In an exemplary embodiment according to FIG. 58, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a sun gear SR 2 of the second planetary gear set RS 2, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected to a ring gear HR 2 of the second planetary gear set RS 2 via a third shaft W 3, that a sun gear SR 1 of the first planetary gear set RS 1 can be fixed to the housing 2 via a first shaft W 1 and via a positive-locking shift element B 1 designed as a brake, and can be connected to the pedal crank shaft WAn via a shift element K 1 designed as a freewheel, a ring gear HR1 of the first planetary gear set RS1 is connected via a second shaft W2 to a planet carrier PT3 of the third planetary gear set RS3, a sun gear SR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B2 designed as a brake, and can be connected to the transmission output shaft WAb via a shift element K2 designed as a freewheel, and a ring gear HR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fifth shaft W5 and via a positively locking shift element B3 designed as a brake, and in that, in order to block the third planetary gear set RS 3, within the scope of a first blocking variant, the sun gear SR 3 of the third planetary gear set RS 3 can be connected to the ring gear HR 3 of the third planetary gear set RS 3 via a shifting element K 3 designed as a freewheel, wherein, within the scope of further blocking variants, on the one hand the sun gear SR 3 and the planet carrier PT 3 of the third planetary gear set and on the other hand the planet carrier PT 3 and the ring gear HR 3 can be connected to one another via the shifting element K 3. Altogether, six gears are thus obtained in the exemplary embodiment according to the shift pattern in FIG. 58, wherein three alternative fifth gears G 5.1, G 5.2, G 5.3 and three alternative sixth gears G 6.1, G 6.2, G 6.3 are provided.In an exemplary embodiment according to FIG. 59, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1, that the transmission output shaft WAb is connected to a sun gear SR 3 of the third planetary gear set RS 3, that a ring gear HR 1 of the first planetary gear set RS 1 is connected via a second shaft W 2 to a planet carrier PT 3 of the third planetary gear set RS 3, that a planet carrier PT 2 of the second planetary gear set RS 2 is connected via a fourth shaft W 4 to a ring gear HR 3 of the third planetary gear set RS 3, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake, a sun gear SR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a third shaft W3 and via a positively locking shift element B2 designed as a brake, and can be connected to the sun gear SR1 of the first planetary gear set RS1 via a shift element K1 designed as a freewheel and via the first shaft W1, and can be connected to the pedal crank shaft WAn via a shift element K2 designed as a freewheel, and a ring gear HR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a fifth shaft W5 and via a positively locking shift element B3 designed as a brake and can be connected to the transmission output shaft WAb via a shift element K3 designed as a freewheel. Altogether, six gears are thus obtained in the exemplary embodiment according to the shift pattern in FIG. 59.In an exemplary embodiment according to FIG. 60, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1, that the transmission output shaft WAb is connected to a ring gear HR 2 of the second planetary gear set RS 2, that a ring gear HR 1 of the first planetary gear set RS 1 is connected to a planet carrier PT 2 of the second planetary gear set RS 2 via a second shaft W 2 and is connectable to a planet carrier PT 3 of the third planetary gear set RS 3 via a shift element K 3 designed as a freewheel and a fourth shaft W 4, a sun gear SR2 of the second planetary gear set RS2 is connected via a third shaft W3 to a ring gear H3 of the third planetary gear set RS2, the sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake, a sun gear SR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fifth shaft W5 and via a shift element B2 designed as a freewheel brake and can be connected to the transmission output shaft WAb via a positively locking shift element K1 designed as a clutch, a planet carrier PT3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B3 designed as a brake, and in order to block the first planetary gear set RS1, within the scope of a first blocking variant, the sun gear SR1 of the first planetary gear set RS1 can be connected to the ring gear HR1 of the first planetary gear set RS1 via a shift element K2 designed as a freewheel, wherein, within the scope of further blocking variants, on the one hand the sun gear SR1 and the planet carrier PT1 of the first planetary gear set RS1 and, on the other hand, the planet carrier PT1 and the ring gear HR1 of the third planetary gear set RS1 can be connected to one another via the shift element K2. Overall, seven gears are thus obtained in the exemplary embodiment according to the shift pattern in FIG. 60.In an exemplary embodiment according to FIG. 61, it is provided that the pedal crank shaft WAn is connected to a ring gear HR 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a ring gear HR 3 of the third planetary gear set, that a ring gear HR 1 of the first planetary gear set RS 1 is connected to a sun gear SR 2 of the second planetary gear set RS 2 via a second shaft W 2, a planet carrier PT2 of the second planetary gear set RS2 is connected via a fourth shaft W4 to a planet carrier PT3 of the third planetary gear set RS3 and can be connected via a positively locking shift element K3 designed as a clutch and via a third shaft W3 to a planet carrier PT1 of the first planetary gear set RS1, and a sun gear SR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fifth shaft W5 and via a positively locking shift element B1 designed as a brake, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B2 designed as a brake and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, the planet carrier PT1 of the first planetary gear set RS1 can be fixed to the housing 2 via the third shaft W3 and via a shift element B3 designed as a freewheel brake, and for blocking the third planetary gear set RS3 within the scope of a first blocking variant the sun gear SR3 can be connected to the ring gear HR3 of the third planetary gear set RS3 via a shift element K2 designed as a freewheel, wherein, within the scope of further blocking variants, on the one hand the sun gear SR 3 and the planet carrier PT 3 of the third planetary gear set RS 3 and on the other hand the planet carrier PT 3 and the ring gear HR 3 of the third planetary gear set RS 3 can be connected to one another via the shift element K 2. Overall, seven gears are thus obtained in the embodiment according to the shift pattern in FIG. 61.In an exemplary embodiment according to FIG. 62, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 1 of the first planetary gear set RS 1, that the transmission output shaft WAb is connected to a planet carrier PT 3 of the third planetary gear set RS 3, that a ring gear HR 1 of the first planetary gear set RS 1 is connected via a second shaft W 2 to a ring gear HR 3 of the third planetary gear set RS 3, that a ring gear HR 2 of the second planetary gear set RS 2 is connected via a fifth shaft W 5 to a sun gear SR 3 of the third planetary gear set RS 3, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake, a sun gear SR2 of the second planetary gear set RS2 can be fixed to the housing 2 via a third shaft W3 and via a positively locking shift element B2 designed as a brake, and can be connected to the ring gear HR1 of the first planetary gear set RS1 and to the ring gear HR3 of the third planetary gear set RS3 via a shift element K3 designed as a freewheel, a planet carrier PT2 of the second planetary gear set RS2 can be fixed to the housing 2 via a fourth shaft W4 and via a shift element B3 designed as a freewheel brake, and that, in order to block the first planetary gear set RS 1, in the context of a first blocking variant, the sun gear SR 1 can be connected to the ring gear HR 1 of the first planetary gear set RS 1 via a shift element K 2 designed as a freewheel, and in order to block the first planetary gear set RS 1, wherein, in the context of further blocking variants, on the one hand the sun gear SR 1 and the planetary gear carrier PT 1 of the first planetary gear set RS 1 and, on the other hand, the planetary gear carrier PT 1 and the ring gear HR 1 of the first planetary gear set RS 1 can be connected to one another via the shift element K 2. Overall, seven gears are thus obtained in the exemplary embodiment according to the shift pattern in FIG. 62.In an exemplary embodiment according to FIG. 63, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a planet carrier PT 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected via a third shaft W 3 to a ring gear HR 2 of the second planetary gear set RS 2, that a sun gear SR 2 of the second planetary gear set RS 2 is connected via a fourth shaft W 4 to a ring gear HR 3 of the third planetary gear set RS 3, a sun gear SR3 of the third planetary gear set RS3 can be fixed to the housing 2 via a fifth shaft W5 and via a shifting element B1 designed as a freewheel brake, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shifting element B2 designed as a brake, and can be connected to the pedal crankshaft WAn via a shifting element K1 designed as a freewheel, a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a second shaft W2 and via a positively locking shifting element B3 designed as a brake, and can be connected to the transmission output shaft WAb via a shifting element K3 designed as a freewheel, and in that, in order to block the third planetary gear set RS 3, within the scope of a first blocking variant, the sun gear SR 3 of the third planetary gear set RS 3 can be connected to the planet carrier PT 3 of the third planetary gear set RS 3 via a positively locking shift element K 2 designed as a clutch, wherein, within the scope of a further blocking variant, the planet carrier PT 3 and the ring gear HR 3 of the third planetary gear set RS 3 can be connected to one another via the shift element K 2. Overall, seven gears are thus obtained in the embodiment according to the shift pattern in FIG. 63.In an exemplary embodiment according to FIG. 64, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a planet carrier PT 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected to a ring gear HR 2 of the second planetary gear set RS 2 via a third shaft W 3, a sun gear SR2 of the second planetary gear set RS2 can be connected via a fourth shaft W4 and via a shifting element K4 designed as a free wheel and via a fifth shaft W5 to a ring gear HR3 of the third planetary gear set RS3, and can be connected via a positively locking shifting element K2 designed as a clutch to the transmission output shaft WAb, and a sun gear SR3 of the third planetary gear set RS3 is fixed to the housing 2 via a fixed housing connection W0, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, and a ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a second shaft W2 and via a positively locking shift element B2 designed as a brake and can be connected to the transmission output shaft WAb via a shift element K3 designed as a freewheel. Overall, seven gears are thus obtained in the exemplary embodiment according to the shift pattern in FIG. 64.In an exemplary embodiment according to FIG. 65, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a planet carrier PT 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected to a ring gear HR 2 of the second planetary gear set RS 2 via a third shaft W 3, a sun gear SR2 of the second planetary gear set RS2 can be connected via a fourth shaft W4 and via a shifting element K3 designed as a free wheel and via a fifth shaft W5 to a ring gear HR3 of the third planetary gear set RS3, and can be connected via a positively locking shifting element K2 designed as a clutch to the transmission output shaft WAb, the ring gear HR3 of the third planetary gear set RS3 can be connected via the fifth shaft W5 and via a shifting element K4 designed as a free wheel and via a second shaft W2 to a ring gear HR1 of the first planetary gear set, and a sun gear SR3 of the third planetary gear set RS3 is fixed to the housing 2 via a fixed housing connection W0, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, and the ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via the second shaft W2 and via a positively locking shift element B2 designed as a brake. Overall, seven gears are thus obtained in the exemplary embodiment according to the shift pattern in FIG. 65.In an exemplary embodiment according to FIG. 66, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a ring gear HR 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected to a ring gear HR 2 of the second planetary gear set RS 2 via a third shaft W 3, a sun gear SR2 of the second planetary gear set RS2 can be connected via a fourth shaft W4 and via a positively locking shift element K3 designed as a clutch and via a fifth shaft W5 to a planet carrier PT3 of the third planetary gear set RS3, and can be connected via a freely running shift element K2 to the transmission output shaft WAb, and a sun gear SR3 of the third planetary gear set RS3 is fixed to the housing 2 via a fixed housing connection W0, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, and the ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via the second shaft W2 and via a positively locking shift element B2 designed as a brake and can be connected to the planet carrier PT3 of the third planetary gear set RS3 via a shift element K4 designed as a freewheel. Overall, seven gears are thus obtained in the exemplary embodiment according to the shift pattern in FIG. 66.In an exemplary embodiment according to FIG. 67, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT 2 of the second planetary gear set RS 2, that the transmission output shaft WAb is connected to a sun gear SR 3 of the third planetary gear set RS 3, that a planet carrier PT 1 of the first planetary gear set RS 1 is connected to a ring gear HR 2 of the second planetary gear set RS 2 via a third shaft W 3, a sun gear SR2 of the second planetary gear set RS2 is connectable via a fourth shaft W4 and via a positively locking shift element K3 designed as a clutch and via a second shaft W2 to a planet carrier PT3 of the third planetary gear set RS3 and to a ring gear HR1 of the first planetary gear set RS1, and is connectable via a freely locking shift element K2 to the transmission output shaft WAb, and a ring gear HR3 of the third planetary gear set RS3 is fixed to the housing 2 via a fifth shaft W5 and via a positively locking shift element B2 designed as a brake, a sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B3 designed as a brake and can be connected to the pedal crankshaft WAn via a shift element K1 designed as a freewheel, and the ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via the second shaft W2 and via a positively locking shift element B1 designed as a brake and is connected to the planet carrier PT3 of the third planetary gear set RS3 which is in. Overall, seven gears are thus obtained in the embodiment according to the shift pattern in FIG. 67.Reference numerals denote reference numerals1 Bicycle or Pedelec 2 housing or bottom bracket housing 3 torque sensor 4 multi-stage transmission EM electric machine F 0 freewheel for electric machine F 1 additional freewheel SR 1 sun gear as gear set element of the first planetary gear set PT 1 planet carrier as gear set element of the first planetary gear set HR 1 ring gear as gear set element of the first planetary gear set SR 2 sun gear as gear set element of the second planetary gear set PT 2 planet carrier as gear set element of the second planetary gear set HR 2 ring gear as gear set element of the second planetary gear set SR 3 sun gear as gear set element of the third planetary gear set PT 3 planet carrier as gear set element of the third planetary gear set HR 3 ring gear as gear set element of the third planetary gear set RS 1 first planetary gear set RS 2 of the second Planetary gear set RS3 Third planetary gear set WAn Transmission input shaft or pedal crankshaft WAb Transmission output shaft W1 First shaft W2 Second shaft W3 Third shaft W4 Fourth shaft W5 Fifth shaft WO Fixed housing connection G1 First gear G1.1 First gear G1.2 Alternative first gear G1.3 Alternative first gear G2 Second gear G2.1 Second gear G2.2 Alternative second gear G2.3 Alternative second gear G3 Third gear G4 Fourth gear G5 Fifth gear G5.1 Fifth gear G5.2 Alternative fifth gear G5.3 Alternative fifth gear G6 Sixth gear G6.1 Sixth gear G6.2 Alternative sixth gear G6.3 Alternative sixth gear G7 Seventh gear G7.1 Seventh gear G7.2 Alternative seventh gear G7.3 Alternative seventh gear B1 Shift element B2 Shift element B3 Shift element K1 Shift element K2 Shift element K3 Shift elementReferences included in the specificationThis list of documents cited by the applicant has been produced in an automated manner and is only included for the better information of the reader. The list is not part of the German patent application or utility model application. The DPMA does not take any adhesion for any faults or omissions.Patent Literature citedDE 10 2022 203 241 B3

[0002]

Claims

Bottom bracket transmission in planetary construction for a bicycle or a pedelec (1), having a crank shaft (WAn) as drive and a transmission output shaft (WAb) as output and further shafts (W1, W2, W3, W4, W5), having three planetary gear sets (RS1, RS2, RS3) as shift transmission (4) and having at least five shift elements (B1, B2, B3, K1, K2, K3) for realizing a plurality of gears (G1, G1.1, G1.2, G1.3, G2, G2.1, G2. 2, G2.3, G3, G4, G5, G5.1, G5.2, G5.3, G6, G6.1, G6.2, G6.3, G7, G7.1, G7.2, G7.3), wherein the pedal crankshaft (WAn) is connectable and / or connected on the drive side to at least one gear set element of the planetary gear sets (RS1, RS2, RS3), wherein the transmission output shaft (WAb) is connectable and / or connected on the output side to at least one gear set element of the planetary gear sets (RS1, RS2, RS3), and wherein at least two of the shift elements (B1, B2, B3, K1, K2, K3) are designed as a form-fit brake and / or a freewheel brake.Bottom bracket transmission according to Claim 1, 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) is designed as a minus planetary gear set.Bottom bracket 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) is designed as a plus planetary gear set.Pedal transmission according to one of the preceding claims, characterized in that a torque sensor (3) is connected to the pedal crankshaft (WAn).Pedal transmission according to one of the preceding claims, characterized in that at least one electric machine (EM) is connected or can be connected to the pedal crankshaft (WAn) or to the transmission output shaft (WAb).Pedal bearing transmission according to Claim 5, characterized in that the electric machine (EM) is arranged axially parallel to the pedal crankshaft (WAn).Pedal transmission according to either of Claims 5 and 6, characterized in that the electric machine (EM) can be connected via a freewheel (F0) to the pedal crankshaft (WAn) or to the transmission output shaft (WAb).Pedal transmission according to one of the preceding claims, characterized in that the pedal crank can be connected to the transmission input of the transmission (4) via a freewheel (F1).Bicycle or pedelec (1) with the bottom bracket transmission according to one of the preceding claims.

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