Planetary bottom bracket gear for a bicycle or pedelec

Abstract

A bottom bracket gear in planetary design for a bicycle or a pedelec (1), with a pedal crankshaft (WAn) as input and a transmission output shaft (WAb) as output and further shafts (W1, W2, W3, W4, W5, W6), with at least one stepped planetary gear set (StPS) and one planetary gear set (PS) as a manual transmission, and with at least five switching elements (B1, B2, B3, K1, K2, K3, K4) for realizing several gears (G1, G1.1, G1.2, G1.3, G1.4, G1.5, G2, G2.1, G2.2, G2.3, G3, G4, G5, G6, G7), wherein the pedal crankshaft (WAn) is connectable and / or connected on the drive side to at least one gear set element of the stepped planetary gear set (StPS) and / or the planetary gear set (PS), wherein the transmission output shaft (WAb) is connectable and / or connected on the output side to at least one gear set element of the stepped planetary gear set (StPS) and / or the planetary gear set (PS), and wherein at least two of the shifting elements (B1, B2, B3, K1, K2, K3, K4) are designed as a positive-locking brake and / or freewheel brake. Furthermore, a bicycle or pedelec (1) with a bottom bracket transmission is proposed.

Description

The present invention relates to a bottom bracket transmission of planetary construction for a bicycle or a pedelec having a crank shaft as drive and a transmission output shaft as output and further shafts, having at least one stepped planetary gear set and a planetary gear set as shift transmission, and having 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 publication DE 10 2018 208 387 A1 discloses a multi-speed transmission of planetary construction for a bicycle or a pedelec. For the realization of sixteen gears, the multi-stage transmission comprises three planetary gear sets and one multi-stage planetary gear set as well as eight shift elements.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 pedal bearing transmission comprises at least one stepped planetary gearset and one planetary gearset as a shift transmission and at least five shift elements for realizing a plurality of gears, wherein the pedal crankshaft is connectable and / or connected on the drive side to at least one gearset element of the planetary gearsets, wherein the transmission output shaft is connectable and / or connected on the output side to at least one gearset element of the planetary gearsets, 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 a stepped planetary gear set and a conventional planetary gear set 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 the conventional planetary gear set is designed as a minus planetary gear set, resulting in a particularly space-saving arrangement. It is also conceivable for the planetary gear set 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 crankshaft or transmission input shaft, while the stepped planetary gearset and the conventional planetary gearset are arranged coaxially to the 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 23 show various exemplary 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 or transmission input shaft 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 23, the transmission 4 comprises, for example, a two-stage stepped planetary gearset StPS and a conventional planetary gearset PS, which have at least five shift elements B 1, B 2, B 3, K 1, K 2, K 3, K 4 for realizing a plurality of gears G 1, G 1.1, G 1.2, G 1.3, G 1.4, G 1.5, G 2, G 2.1, G 2. 2, G2.3, G3, G4, G5, G6, G7. The conventional planetary gear set PS is designed as an example as a space-saving minus planetary gear set. The planetary gear set PS has as gear set elements a sun gear SR, a planet carrier PT and a ring gear HR. Depending on the embodiment, the stepped planetary gearset StPS has, as gearset elements, a first sun gear SR 1, a second sun gear SR 2, a stepped planetary carrier SPT, a first ring gear HR 1 and / or a second ring gear HR 2.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 stepped planetary gear set StPS and / or of the planetary gear set PS, 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 stepped planetary gear set StPS and / or of the planetary gear set PS, and wherein at least two of the shift elements B 1, B 2, B 3, K 1, K 2, K 3, K 4 are designed as a form-fit brake and / or freewheel brake.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 bottom bracket transmission according to the invention with reference to FIG. 1 with an additional freewheel F 1 between the crank and the transmission input of the bottom bracket transmission. 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 23, 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 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 in a brake and 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 crankshaft WAn is connected to a stepped planetary gear carrier SPT of the stepped planetary gear set StPS, that the transmission output shaft WAb is connected to a planetary gear carrier PT of the planetary gear set PS, that a sun gear SR1 of the stepped planetary gear set StPS is connected via a second shaft W2 to a ring gear HR of the planetary gear set PS, that a first ring gear HR1 of the stepped planetary gear set StPS can be fixed to the housing 2 via a third shaft W3 and via a positive-locking shift element B1 designed as a brake and can be connected to the transmission output shaft WAb via a shift element K1 designed as a freewheel, a second ring gear HR2 of the stepped planetary gearset StPS can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B2 designed as a brake, a sun gear SR of the planetary gearset PS 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 order to block the planetary gearset PS, in a first blocking variant, the sun gear SR of the planetary gearset PS can be connected to the planet carrier PT of the planetary gearset PS via a positively locking shift element K2 designed as a clutch, wherein, within the scope of a further blocking variant, the planet carrier PT and the ring gear HR of the planetary gear set PS can be connected to one another via the shift element K 2. 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 crankshaft WAn is connected to a stepped planetary gear carrier SPT of the stepped planetary gear set StPS, that the transmission output shaft WAb is connected to a planetary gear carrier PT of the planetary gear set PS, that a sun gear SR1 of the stepped planetary gear set StPS is connectable to a ring gear HR of the planetary gear set PS via a second shaft W2 and via a shifting element K3 designed as a freewheel and via a fourth shaft W4, and is connectable to the transmission output shaft WAb via a positive shifting element K2 designed as a clutch, a first ring gear HR1 of the stepped planetary gearset StPS can be fixed to the housing 2 via a third shaft W3 and a positive shift element B1 designed as a brake and can be connected to the transmission output shaft WAb via a shift element K1 designed as a freewheel, a second ring gear HR2 of the stepped planetary gearset StPS can be fixed to the housing 2 via a first shaft W1 and a positive shift element B2 designed as a brake, and a sun gear SR of the planetary gearset PS is fixed to the housing 2 via a fixed housing connection W0, and altogether six gears result in the exemplary embodiment according to the shift pattern in FIG. 6.In an exemplary embodiment according to FIG. 7, it is provided that the pedal crank shaft WAn is connected to a planet carrier PT of the planetary gear set PS, that the transmission output shaft WAb is connected to a stepped planet carrier SPT of the stepped planetary gear set StPS, that a sun gear SR1 of the stepped planetary gear set StPS is connected via a third shaft W3 to a ring gear HR of the planetary gear set PS, that a first ring gear HR1 of the stepped planetary gear set StPS can be fixed to the housing 2 via a second shaft W2 and via a positive-locking shift element B2 designed as a brake and can be connected to the pedal crank shaft WAn via a shift element K2 designed as a freewheel, a second ring gear HR2 of the stepped planetary gearset StPS can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shift element B3 designed as a brake, a sun gear SR of the planetary gearset PS can be fixed to the housing 2 via a first shaft W1 and via a shift element B1 designed as a freewheel brake, and, in order to block the planetary gearset PS, within the scope of a first blocking variant, the sun gear SR of the planetary gearset PS can be connected to the planet carrier PT of the planetary gearset PS via a positively locking shift element K1 designed as a clutch, wherein, within the scope of a further blocking variant, the planet carrier PT and the ring gear HR of the planetary gear set PS can be connected to one another via the shift element K 1. 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 of the planetary gear set PS, that the transmission output shaft WAb is connected to a stepped planet carrier SPT of the stepped planetary gear set StPS, that a sun gear SR1 of the stepped planetary gear set StPS is connectable to the pedal crank shaft WAn via a third shaft W3 and via a shifting element K3 designed as a freewheel and via a first shaft W1 and to a ring gear HR of the planetary gear set PS and is connectable to the pedal crank shaft WAn via a positive shifting element K1 designed as a clutch, a first ring gear HR1 of the stepped planetary gearset StPS 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 pedal crankshaft WAn via a shift element K2 designed as a freewheel, a second ring gear HR2 of the stepped planetary gearset StPS 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 a sun gear SR of the planetary gearset PS is fixed to the housing 2 via a fixed housing connection W0. 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 crankshaft WAn is connected to a stepped planetary gear carrier SPT of the stepped planetary gear set StPS, that the transmission output shaft WAb is connected to a planetary gear carrier PT of the planetary gear set PS, that a sun gear SR1 of the stepped planetary gear set StPS is connected via a second shaft W2 to a ring gear HR of the planetary gear set PS, that a first ring gear HR1 of the stepped planetary gear set StPS can be fixed to the housing 2 via a first shaft W1 and via a positive-locking shift element B2 designed as a brake, a second ring gear HR2 of the stepped planetary gearset StPS 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 the transmission output shaft WAb via a shift element K1 designed as a freewheel, a sun gear SR of the planetary gearset PS can be fixed to the housing 2 via a fourth shaft W4 and via a shift element B3 designed as a freewheel brake, and for blocking the planetary gearset PS, within the scope of a first blocking variant, the sun gear SR of the planetary gearset PS can be connected to the planet carrier PT of the planetary gearset PS via a positively locking shift element K2 designed as a clutch, wherein, within the scope of a further blocking variant, the planet carrier PT and the ring gear HR of the planetary gear set PS can be connected to one another via the shift element K 2. 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 crankshaft WAn is connected to a stepped planetary gear carrier SPT of the stepped planetary gear set StPS, that the transmission output shaft WAb is connected to a planetary gear carrier PT of the planetary gear set PS, that a sun gear SR1 of the stepped planetary gear set StPS is connectable to a ring gear HR of the planetary gear set PS via a second shaft W2 and via a shifting element K3 designed as a freewheel and via a fourth shaft W4, and is connectable to the transmission output shaft WAb via a positive shifting element K2 designed as a clutch, a first ring gear HR1 of the stepped planetary gearset StPS can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B2 designed as a brake, a second ring gear HR2 of the stepped planetary gearset StPS 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 the transmission output shaft WAb via a shift element K1 designed as a freewheel, and a sun gear SR of the planetary gearset PS is fixed to the housing 2 via a fixed housing connection W0. 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 crankshaft WAn is connected to a second sun gear SR 2 of the stepped planetary gearset StPS, that the transmission output shaft WAb is connected to a planet carrier PT of the planetary gearset PS, that a first sun gear SR 1 of the stepped planetary gearset StPS is connected to a ring gear HR of the planetary gearset PS via a second shaft W 2, that a stepped planetary carrier SPT of the stepped planetary gearset StPS can be fixed to the housing 2 via a third shaft W 3 and via a positive-locking shift element B 1 designed as a brake, and can be connected to the transmission output shaft WAb via a shift element K 1 designed as a freewheel, a ring gear HR1 of the stepped planetary gearset StPS can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B2 designed as a brake, a sun gear SR of the planetary gearset PS can be fixed to the housing via a fourth shaft W4 and via a shift element B3 designed as a freewheel brake, and for blocking the planetary gearset PS, within the scope of a first blocking variant, the sun gear SR of the planetary gearset PS can be connected to the planet carrier PT of the planetary gearset PS via a positively locking shift element K2 designed as a clutch, wherein, within the scope of a further blocking variant, the planet carrier PT and the ring gear HR of the planetary gear set PS can be connected to one another via the shift element K 2. 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 crankshaft WAn is connected to a second sun gear SR 2 of the stepped planetary gearset StPS, that the transmission output shaft WAb is connected to a planet carrier PT of the planetary gearset PS, that a first sun gear SR 1 of the stepped planetary gearset StPS is connectable via a second shaft W 2 and via a shift element K 3 designed as a freewheel and via a fourth shaft W 4 to a ring gear HR of the planetary gearset PS, and is connectable via a positive shift element K 2 designed as a clutch to the transmission output shaft WAb, a stepped planetary gear carrier SPT of the stepped planetary gear set StPS 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 the transmission output shaft WAb via a shift element K1 designed as a freewheel, a ring gear HR1 of the stepped planetary gear set StPS 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 a sun gear SR of the planetary gear set PS is fixed to the housing 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 crankshaft WAn is connected to a first sun gear SR 1 of the stepped planetary gearset StPS, that the transmission output shaft WAb is connected to a planet carrier PT of the planetary gearset PS, that a second sun gear SR 2 of the stepped planetary gearset StPS is connectable via a second shaft W 2 and via a shift element K 3 designed as a freewheel and via a fourth shaft W 4 to a ring gear HR of the planetary gearset PS, and is connectable via a positive shift element K 1 designed as a clutch to the transmission output shaft WAb, the stepped planetary gear carrier SPT of the stepped planetary gear set StPS can be fixed to the housing 2 via the first shaft W1 and via a positively locking shift element B1 designed as a brake, and can be connected to a ring gear HR of the planetary gear set PS via a shift element K2 designed as a freewheel and via a fourth shaft W4, a ring gear HR1 of the stepped planetary gear set StPS 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 a sun gear SR of the planetary gear set PS is fixed to the housing via a fixed housing connection W0. 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 crankshaft WAn is connected to a first sun gear SR 1 of the stepped planetary gearset StPS, that the transmission output shaft WAb is connected to a planet carrier PT of the planetary gearset PS, that a second sun gear SR 2 of the stepped planetary gearset StPS is connectable via a second shaft W 2 and via a shift element K 3 designed as a freewheel and via a fourth shaft W 4 to a ring gear HR of the planetary gearset PS, and is connectable via a positive shift element K 1 designed as a clutch to the transmission output shaft WAb, a stepped planetary gear carrier SPT of the stepped planetary gear set StPS can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake, the ring gear HR1 of the stepped planetary gear set StPS can be fixed to the housing 2 via the third shaft W3 and via a positively locking shift element B2 designed as a brake, and can be connected to a ring gear HR of the planetary gear set PS via a shift element K2 designed as a freewheel and via a fourth shaft W4, and a sun gear SR of the planetary gear set PS is fixed to the housing via a fixed housing connection W0. 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 crankshaft WAn is connected to a first sun gear SR 1 of the stepped planetary gearset StPS, that the transmission output shaft WAb is connected to a planet carrier PT of the planetary gearset PS, that a second sun gear SR 2 of the stepped planetary gearset StPS is connectable via a second shaft W 2 and via a shift element K 3 designed as a freewheel and via a fifth shaft W 5 to a ring gear HR of the planetary gearset PS, and is connectable via a positive shift element K 1 designed as a clutch to the transmission output shaft WAb, a stepped planetary gear carrier SPT of the stepped planetary gear set StPS 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 a first ring gear HR1 of the stepped planetary gear set StPS can be fixed to the housing 2 via a third shaft W3 and via a positively locking shift element B2 designed as a brake, a second ring gear HR2 of the stepped planetary gearset StPS is connectable via a fourth shaft W4 and via a shift element K2 designed as a free wheel and via a fifth shaft W5 to a ring gear HR of the planetary gearset PS, and a sun gear SR of the planetary gearset PS is fixed to the housing via a fixed housing connection W0. 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 crankshaft WAn is connected to a first sun gear SR 1 of the stepped planetary gearset StPS, that the transmission output shaft WAb is connected to a planet carrier PT of the planetary gearset PS, that a second sun gear SR 2 of the stepped planetary gearset StPS is connectable via a second shaft W 2 and via a shifting element K 3 designed as a freewheel and via a fourth shaft W 4 to a ring gear HR of the planetary gearset PS, and is connectable via the second shaft W 2 and via a positive shifting element K 1 designed as a clutch to the transmission output shaft WAb, a stepped planetary gear carrier SPT of the stepped planetary gear set StPS can be fixed to the housing 2 via a first shaft W1 and via a positively locking shift element B1 designed as a brake, the ring gear HR1 of the stepped planetary gear set StPS can be fixed to the housing 2 via the third shaft W3 and via a positively locking shift element B2 designed as a brake, and can be connected to a ring gear HR of the planetary gear set PS via a third shaft W3 and via a shift element K2 designed as a freewheel and via a fourth shaft W4, and a sun gear SR of the planetary gear set PS is fixed to the housing via a fixed housing connection W0. 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 crankshaft WAn is connected to a first sun gear SR 1 of the stepped planetary gearset StPS, that the transmission output shaft WAb is connected to a planet carrier PT of the planetary gearset PS, that a second sun gear SR 2 of the stepped planetary gearset StPS is connectable via a third shaft W 3 and via a shift element K 3 designed as a freewheel and via a fourth shaft W 4 to a ring gear HR of the planetary gearset PS, and is connectable via a positive shift element K 1 designed as a clutch to the transmission output shaft WAb, the stepped planetary gear carrier SPT of the stepped planetary gear set StPS can be fixed to the housing 2 via the first shaft W1 and via a positively locking shift element B1 designed as a brake, and can be connected to a ring gear HR of the planetary gear set PS via a first shaft W1 and via a freely rotating shift element K2 and via a fourth shaft W4, a ring gear HR1 of the stepped planetary gear set StPS 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 a sun gear SR of the planetary gear set PS is fixed to the housing 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 crankshaft WAn is connected to a planet carrier PT of the planetary gear set PS, that the transmission output shaft WAb is connected to a first sun gear SR 1 of the stepped planetary gear set StPS, that a second sun gear SR 2 of the stepped planetary gear set StPS is connectable via a third shaft W 3 and via a shift element K 2 designed as a freewheel and via a first shaft W 1 to a ring gear HR of the planetary gear set PS, the stepped planetary gear carrier SPT of the stepped planetary gear set StPS can be connected to the pedal crankshaft WAn via the second shaft W2 and via a shifting element K1 designed as a freewheel and can be connected to the ring gear HR of the planetary gear set PS via the second shaft W2 and via a positively locking shifting element K3 designed as a clutch, and a first shaft W1, a sun gear SR of the planetary gear set PS is fixed to the housing 2 via a fixed housing connection W0, and a first ring gear HR1 of the stepped planetary gear set StPS can be fixed to the housing 2 via a fifth shaft W5 and via a positively locking shifting element B2 designed as a brake, a second ring gear HR2 of the stepped planetary gearset StPS can be fixed to the housing 2 via a fourth shaft W4 and via a positive shift element B1 designed as a brake. 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 crankshaft WAn is connected to a ring gear HR of the planetary gear set PS, that the transmission output shaft WAb can be connected via a positively locking shift element K 3 designed as a clutch and via a third shaft W 3 to a second sun gear SR 2 of the stepped planetary gear set StPS, that a first sun gear SR 1 of the stepped planetary gear set StPS can be connected via a first shaft W 1 and via a shift element K 1 designed as a freewheel to the transmission output shaft WAb, the first sun gear SR1 of the stepped planetary gearset StPS can be connected to the pedal crankshaft WAn via the first shaft W1 and via a shifting element K2 designed as a freewheel, a stepped planetary carrier SPT of the stepped planetary gearset StPS is connected to a planetary carrier PT of the planetary gearset PS via a second shaft W2, a first ring gear HR1 of the stepped planetary gearset StPS can be fixed to the housing 2 via a fourth shaft W4 and via a positively locking shifting element B2 designed as a brake, a second ring gear HR2 of the stepped planetary gearset StPS can be fixed to the housing 2 via a fifth shaft W5 and via a positively locking shift element B1 designed as a brake, and a sun gear SR of the planetary gearset PS is fixed to the housing 2 via a fixed housing connection W0. Thus, in the 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 stepped planetary gear carrier SPT of the stepped planetary gear set StPS, that the transmission output shaft WAb is connected to a ring gear HR of the planetary gear set PS, that a sun gear SR of the planetary gear set PS is fixed to the housing 2 via a fixed housing connection W0, that a sun gear SR1 of the stepped planetary gear set StPS is connectable to a planetary gear carrier PT of the planetary gear set PS via a first shaft W1 and via a positive-locking shift element K3 designed as a clutch and via a second shaft W2, the sun gear SR1 of the stepped planetary gearset StPS can be connected to the transmission output shaft WAb via the first shaft W1 and via a shifting element K1 designed as a freewheel, the second ring gear HR of the second stepped planetary gearset StPS can be fixed to the housing via the fifth shaft W5 and via a positively locking shifting element B1 designed as a brake, and can be connected to a planet carrier PT of the planetary gearset PS via a shifting element K2 designed as a freewheel and via a second shaft W2, and a first ring gear HR1 of the stepped planetary gearset StPS can be fixed to the housing via a fourth shaft W4 and via a positively locking shifting element B2 designed as a brake. Thus, in the embodiment according to the shift pattern in FIG. 20, six gears result.In an exemplary embodiment according to FIG. 21, it is provided that the pedal crankshaft WAn is connected to a stepped planetary gear carrier SPT of the stepped planetary gear set StPS, that the transmission output shaft WAb is connectable via a shifting element K 2 designed as a freewheel and via a second shaft W 2 to a planetary gear carrier PT of the planetary gear set PS, that the transmission output shaft WAb is connectable via a positively locking shifting element K 3 designed as a clutch and via a first shaft W 1 to a first sun gear SR 1 of the stepped planetary gear set StPS, that a ring gear HR of the planetary gear set PS is fixed to the housing 2 via a fixed housing connection W 0, a sun gear SR of the planetary gear set PS is connected via a third shaft W3 to a second sun gear SR2 of the stepped planetary gear set StPS, the planet carrier PT of the planetary gear set PS is connectable via the second shaft W2 and via a shifting element K1 designed as a freewheel to the pedal crankshaft WAn, a first ring gear HR1 of the stepped planetary gear set StPS is fixable to the housing via a fourth shaft W4 and via a positive shifting element B1 designed as a brake, and a second ring gear HR2 of the stepped planetary gear set StPS is fixable to the housing 2 via a fifth shaft W5 and via a positive shifting element B2 designed as a brake. Thus, in the 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 ring gear HR of the planetary gear set PS, that the transmission output shaft WAb is connectable via a shifting element K 2 designed as a freewheel and via a sixth shaft W 6 to a first sun gear SR 1 of the stepped planetary gear set StPS, that the transmission output shaft WAb is connectable via a positively locking shifting element K 1 designed as a clutch and via a third shaft W 3 to a second sun gear SR 2 of the stepped planetary gear set StPS, that a planetary gear carrier PT of the planetary gear set PS is connected via a first shaft W 1 to a stepped planetary gear carrier SPT of the stepped planetary gear set StPS, a sun gear SR of the planetary gear set PS 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 can be connected to a second ring gear HR2 of the stepped planetary gear set StPS via a shift element K3 designed as a freewheel and via a fourth shaft W4, and a first ring gear HR1 of the stepped planetary gear set StPS can be fixed to the housing 2 via a fifth shaft W5 and via a positively locking shift element B2 designed as a brake. Thus, in the 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 crankshaft WAn is connected to a planet carrier PT of the planetary gear set PS, that the transmission output shaft WAb is connected to a first sun gear SR 1 of the stepped planetary gear set StPS, that a second sun gear SR 2 of the stepped planetary gear set StPS is connectable to the pedal crankshaft WAn via a first shaft W 1 and via a shift element K 1 designed as a freewheel, that a ring gear HR of the planetary gear set PS is connected to a stepped planetary gear carrier SPT of the stepped planetary gear set StPS via a third shaft W 3, a sun gear SR of the planetary gear set PS can be fixed to the housing 2 via a second shaft W2 and via a positively locking shift element B1 designed as a brake, a first ring gear HR1 of the stepped planetary gear set StPS can be fixed to the housing 2 via a sixth shaft W6 and via a positively locking shift element K3 designed as a clutch, and via a fourth shaft W4 and a positively locking shift element B2 designed as a brake, a second ring gear HR2 of the stepped planetary gearset StPS can be fixed to the housing 2 via a fifth shaft W5 and via a shift element K4 designed as a free wheel and via the fourth shaft W4 and the positively locking shift element B2 designed as a brake, and can be connected to the first ring gear HR1 of the stepped planetary gearset StPS via the positively locking shift element K3 designed as a clutch and the sixth shaft W6, and in that, in order to block the planetary gearset PS, the sun gear SR of the planetary gearset PS can be connected to the ring gear HR of the planetary gearset PS via a shift element K2 designed as a free wheel, as part of a first blocking variant, wherein, within the scope of further block variants, on the one hand, the sun gear SR and the planet carrier PT of the planetary gear set PS and, on the other hand, the planet carrier PT and the ring gear HR of the planetary gear set PS can be connected to one another via the shift element K 2. Thus, in the exemplary embodiment according to the shift pattern in FIG. 23, seven gears are obtained, wherein five alternative first gears G 1.1, G 1.2, G 1.3, G 1.4, G 1.5 and three alternative second gears G 2.1, G 2.2, G 2.3 can be realized.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 or first sun gear as gear set element of the stepped planetary gear set SR 2 second sun gear as gear set element of the stepped planetary gear set PT 1 stepped planetary gear carrier as gear set element of the stepped planetary gear set HR 1 ring gear or first ring gear as gear set element of the stepped planetary gear set HR 2 second ring gear as gear set element of the stepped planetary gear set SR sun gear as gear set element of the planetary gear set PT planetary gear carrier as gear set element of the planetary gear set HR ring gear as gear set element of the planetary gear set PS planetary gear set StPS two-stage gear Stepped planetary gearset 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 W6 Sixth shaft W0 Fixed housing connection G1 First gear G1.1 First gear G1.2 Alternative first gear G1.3 Alternative first gear G1.4 Alternative first gear G1.5 Alternative first gear G2 Second gear G2.1 Second gear G2.2 Alternative second gear G2.3 Alternative second gear G2.4 Alternative second gear G2.5 Alternative second gear G3 Third gear G4 Fourth gear G5 Fifth gear G6 Sixth gear G7 seventh gear B 1 shift element B 2 shift element B 3 shift element K 1 shift element K 2 shift element K 3 shift element K 4 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 2018 208 387 A1

[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, W6), having at least one stepped planetary gearset (StPS) and a planetary gearset (PS) as shift transmission, and having at least five shift elements (B1, B2, B3, K1, K2, K3, K4) for realizing a plurality of gears (G1, G1.1, G1.2, G1.3, G1.4, G1.5, G2, G2.1, G2. 2, G2.3, G3, G4, G5, G6, G7), wherein the pedal crankshaft (WAn) is connectable and / or connected on the drive side to at least one gear set element of the stepped planetary gear set (StPS) and / or of the planetary gear set (PS), wherein the transmission output shaft (WAb) is connectable and / or connected on the output side to at least one gear set element of the stepped planetary gear set (StPS) and / or of the planetary gear set (PS), and wherein at least two of the shift elements (B1, B2, B3, K1, K2, K3, K4) are designed as a positive brake and / or a free-wheel brake.Bottom bracket transmission according to one of the preceding claims, characterized in that the planetary gear set (PS) is designed as a minus planetary gear set.Bottom bracket transmission according to one of the preceding claims, characterized in that the planetary gear set (PS) 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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