Planetary center shaft transmission for bicycle or electric moped

Abstract

The invention relates to a planetary center shaft transmission for a bicycle or an electric moped, comprising a pedal crankshaft (WAn) as input and a transmission output shaft (WAb) as output, and comprising further shafts (W1, W2, W3, W4, W5, W6, W7), and comprising a first transmission shift group (3) and a second transmission shift group (4), the first transmission shift group (3) and the second transmission shift group (4) are coupled to each other in order to achieve a plurality of transmission ratios (G1, G2, G3, G4, G5, G6, G7, G8, G9, G10, G11, G12), in which the first transmission shift group (3) comprises a two-step planetary gear set (StRS), to which a first shift element (B1), a second shift element (B2) and a fifth shift element (F1I, F1II, F1III, F1IV, F1V, F1VI) are assigned. A bicycle or electric moped (1) having a centre shaft transmission is also proposed.

Description

Technical Field

[0001] The invention relates to a planetary bottom-shaft transmission for a bicycle or electric power-assisted vehicle, which has a transmission input shaft or a pedal crankshaft as an input, and a transmission output shaft as an output, has another shaft, has a first transmission shift group with a stepped planetary gear set, and has a second transmission shift group with a first planetary gear set and a second planetary gear set, wherein the planetary gear sets are assigned a plurality of shift elements. The invention also relates to a bicycle or electric power-assisted vehicle having a bottom-shaft transmission. Background Art

[0002] For example, document DE 10 2022 203 243 B3 has disclosed a transmission in a pedal crank housing for a bicycle or electric assisted vehicle. The transmission comprises a stepped planetary gear set and a further planetary gear set, which are arranged coaxially with respect to the pedal crankshaft and are assigned six shifting elements for achieving six transmission ratios. Summary of the invention

[0003] The object of the present invention is to propose a bottom bracket transmission and a bicycle or pedelec having a bottom bracket transmission which has the least possible structural complexity and at the same time has improved properties compared to the prior art.

[0004] This object is achieved according to the invention by the features of patent claims 1 and 13. Advantageous and claimed developments are evident from the subclaims, the description and the drawings.

[0005] Therefore, a planetary bottom bracket transmission for bicycles or electric assisted vehicles is proposed. The bottom bracket transmission has a pedal crankshaft as input, a transmission output shaft as output, and a further shaft, wherein the output is preferably implemented via a sprocket, a pulley or the like. The mid-shaft transmission also includes a first transmission shift group and a second transmission shift group that are connected to each other to achieve multiple gear ratios, wherein the first transmission shift group includes a two-stage stepped planetary gear set to which a first shift element, a second shift element and a fifth shift element are assigned, wherein the second transmission shift group includes a first planetary gear set and a second planetary gear set to which a third shift element, a fourth shift element and a sixth shift element are assigned, wherein a stepped planetary gear carrier as an element of the stepped planetary gear set is connected to the pedal crankshaft or to the sixth shaft as the output shaft of the second transmission shift group, wherein a ring gear as an element of the stepped planetary gear set is connected to the second element of the first planetary gear set or to the transmission output shaft, wherein a second sun gear as an element of the stepped planetary gear set can be fixed to a housing through the first shift element, wherein the first sun gear as an element of the stepped planetary gear set can be fixed to the housing through the second shift element, wherein in order to interlock the stepped planetary gear set A stepped planetary gear set, wherein two elements of the stepped planetary gear set or two shafts connected to the elements of the stepped planetary gear set can be connected to each other through a fifth shifting element, wherein the first element of the first planetary gear set is connected to the first element of the second planetary gear set, wherein the first element of the first planetary gear set and the first element of the second planetary gear set are commonly connected to the stepped planetary gear carrier of the stepped planetary gear set or commonly connected to the transmission output shaft, wherein the third element of the first planetary gear set can be fixed to the housing through a third shifting element, wherein the third element of the second planetary gear set can be fixed to the housing through a fourth shifting element, wherein the third element of the first planetary gear set is connected to the second element of the second planetary gear set, and wherein in order to interlock the first planetary gear set and the second planetary gear set, two shafts connected to the element of the first planetary gear set and the element of the second planetary gear set can be connected to each other through a sixth shifting element.

[0006] In this way, in the proposed intermediate shaft transmission with one provided stepped planetary gear set and two planetary gear sets and only six provided shifting elements, a particularly simple and compact construction is achieved in the intermediate shaft transmission with the above-described connection of the first transmission shift group and the second transmission shift group. In comparison with known transmissions, particularly low component loads are also achieved due to the geometric transmission ratio series in the intermediate shaft transmission, and advantageously a high tooth meshing efficiency is achieved.

[0007] For the mechanical connection of elements (e.g. rotating elements etc.) of two planetary gear sets in two transmission shift groups, preferably not only input shafts and output shafts are used but also further shafts or shaft-like elements, wherein the term "shaft" is to be understood as meaning not only a cylindrical, rotatably mounted machine element for transmitting torque but also a general connecting element for connecting individual gear set elements to one another for the purpose of transmitting torque.

[0008] In the proposed mid-shaft transmission, the axial sequence of the two transmission shift groups can be interchanged. Thus, the first transmission shift group is connected upstream or downstream of the second transmission shift group and between the transmission input shaft or pedal crankshaft and the transmission output shaft of the mid-shaft transmission. If the first transmission shift group is arranged upstream, the transmission input or pedal crankshaft of the mid-shaft transmission connected to the pedal crank can be said to form the input shaft of the first transmission shift group, and the fifth shaft forms the output shaft of the first transmission shift group and is connected to the input of the second transmission shift group. The pedal crankshaft and the first shaft can be formed as one component or as a plurality of components. If the first transmission shift group is arranged downstream, the input shaft of the first transmission shift group is connected to the output of the second transmission shift group, and the fifth shaft of the first transmission shift group is connected to the transmission output shaft. The transmission output shaft and the fifth shaft can be formed as one component or as a plurality of components.

[0009] In the proposed mid-shaft transmission, any desired design of a multi-stage second transmission shift group can be combined with the first transmission shift group to form a mid-shaft transmission. The second transmission shift group can preferably be designed as a three-ratio transmission or a three-ratio group, and the first transmission shift group can be designed as a three-ratio transmission or a three-ratio group, so that, for example, a nine-ratio transmission is implemented as a mid-shaft transmission. However, it is also possible to implement other numbers of transmission ratios in the transmission shift group, so that the mid-shaft transmission can also achieve more or less than, for example, eight transmission ratios. Depending on the constraints and requirements placed on the mid-shaft transmission, transmission ratios can also be omitted. In this way, the gear set can be optimized for the required speed ratio (ratio step, spread, etc.) or the nature of the shifting operation or the number of shifting elements involved.

[0010] Specifically, for the connection of two transmission shift groups, and in order to achieve a particularly simple and compact construction of the mid-shaft transmission, it can be provided that a stepped planetary gear carrier as an element of a stepped planetary gear set is connected to a pedal crankshaft or to a sixth shaft as an output shaft of a second transmission shift group, wherein a ring gear as an element of a stepped planetary gear set is connected to a second element of a first planetary gear set or to the transmission output shaft via a fifth shaft, wherein when the first shift element is engaged, the second sun gear as an element of the stepped planetary gear set can be fixed to the housing via the first shaft, wherein when the second shift element is engaged, the first sun gear as an element of the stepped planetary gear set can be fixed to the housing via the second shaft, wherein in order to interlock the stepped planetary gear sets, when the fifth shift element is locked, the two elements of the stepped planetary gear sets capable of being connected to each other, wherein the first element of the first planetary gear set is connected to the first element of the second planetary gear set, wherein the first element of the first planetary gear set and the first element of the second planetary gear set are commonly connected to a stepped planetary gear carrier of the stepped planetary gear set or commonly connected to a transmission output shaft, wherein when a third shift element is engaged, the third element of the first planetary gear set can be fixed to the housing via a third shaft, wherein when a fourth shift element is engaged, the third element of the second planetary gear set can be fixed to the housing via a fourth shaft, wherein the third element of the first planetary gear set is connected to the second element of the second planetary gear set via the third shaft, and wherein in order to interlock the first planetary gear set and the second planetary gear set, when the sixth shift element is locked, two shafts connected to the element of the first planetary gear set and the element of the second planetary gear set can be connected to each other.

[0011] Therefore, in the two transmission shift groups of the proposed central shaft transmission, different interlocking variants of the stepped planetary gear set of the fifth shifting element in six different arrangement variants and different interlocking variants of the two planetary gear sets of the sixth shifting element in six different arrangement variants are possible.

[0012] In the case of the present invention, in the proposed central shaft transmission with two transmission shift groups, the shift elements provided can be designed as brakes, flywheel brakes, clutches and / or flywheels. An advantageous design variant of the present invention provides that the first shift element, the second shift element, the third shift element and the fourth shift element are each designed as a positive locking brake, and / or the fifth shift element and the sixth shift element are each designed as a flywheel.

[0013] The shift element designed as a brake is preferably designed as a shape-locking shift element, such as an inexpensive brake or shift dog, etc., such as a toothed brake ring and a corresponding ratchet. Brakes as shift elements have the advantage that they are easily accessible for external actuation. In the case of a clutch designed as a flywheel, it is advantageous that the brake is designed, for example, as a one-way brake to prevent the interlocking of the transmission in the case of a reversal of the direction of rotation at the input or output. As a flywheel, a flywheel preferably made of a flywheel that cannot be actively switched or actuated is used. This has the advantage that a passive shift element does not require a shift actuation. When in a locked direction condition, the flywheel cannot be actuated to transmit torque. Torque is not transmitted in the opposite direction of rotation because the flywheel is not locked when in an overrunning condition. However, it is also conceivable that an active switchable flywheel or an active switchable flywheel brake can also be used.

[0014] A preferred embodiment of the invention can provide that at least one of the provided planetary gear sets is designed as a negative planetary gear set, resulting in a particularly space-saving arrangement. It is also conceivable to design one of the planetary gear sets as a positive planetary gear set.

[0015] Due to the interchange of the planetary gear carrier connection and the ring gear connection to the gear set, the negative planetary gear set can be preferably converted into a positive planetary gear set, and the value of the static speed ratio is increased by 1. The negative planetary gear set has planetary gears rotatably mounted on its planetary gear carrier, the planetary gears meshing with the sun gear and the ring gear of the planetary gear set, so that when the planetary gear carrier remains fixed and the sun gear rotates, the ring gear rotates in a direction opposite to the direction of rotation of the sun gear. The positive planetary gear set has inner planetary gears and outer planetary gears rotatably mounted on its planetary gear carrier, the inner planetary gears and the outer planetary gears meshingly engaged with each other, wherein the sun gear of the planetary gear set meshes with the inner planetary gears, and the ring gear of the planetary gear set meshes with the outer planetary gears, so that when the planetary gear carrier remains fixed and the sun gear rotates, the ring gear rotates in the same direction of rotation as the direction of rotation of the sun gear.

[0016] For a person skilled in the art, this means that in the case of individual gear sets designed as negative planetary gear sets, the first element or gear set element is designed as a sun gear, the second element is designed as a planet carrier or star wheel, and the third element is designed as a ring gear. Furthermore, this means that in the case of individual gear sets designed as positive planetary gear sets, the first element is designed as a sun gear, the second element is designed as a ring gear, and the third element is designed as a planet carrier or star wheel.

[0017] In order to further optimize the control of the proposed mid-shaft transmission, it is provided that at least one torque sensor or the like is provided at the input and / or the output.

[0018] For electric drive assistance in the proposed mid-shaft transmission, at least one electric motor or the like can be connected or can be connected or fixedly or detachably coupled to the input or to the pedal crankshaft or the transmission input shaft and / or to the output or to the transmission output shaft. The electric motor can preferably be arranged axially parallel to the pedal crankshaft or the transmission input shaft, while the planetary gear set is arranged coaxially relative to the pedal crankshaft or the transmission input shaft.

[0019] Another aspect of the invention is a bicycle or electric assisted bicycle having a bottom bracket transmission as described above. This leads to the advantages already described and further advantages. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] The present invention will be discussed in more detail below based on the accompanying drawings.

[0021] in:

[0022] Figure 1 A schematic diagrammatic view of a bottom bracket transmission on a bicycle or electric assisted vehicle according to the present invention is shown, the bottom bracket transmission having a first transmission shift group having a stepped planetary gear set with a first interlocking variation, the first transmission shift group being connected upstream of a second transmission shift group having two planetary gear sets with a first interlocking variation

[0023] Figure 2 A schematic diagrammatic view of a mid-axle transmission according to the invention is shown, having a first transmission shift group with a stepped planetary gear set with a first interlocking variant, which is connected downstream of a second transmission shift group with two planetary gear sets with a first interlocking variant

[0024] Figure 3 A schematic diagrammatic view of a mid-axle transmission according to the invention is shown, having a first transmission shift group with a stepped planetary gear set with a second interlocking variant, which is connected upstream of a second transmission shift group with two planetary gear sets with a first interlocking variant

[0025] Figure 4 A schematic diagrammatic view of a mid-axle transmission according to the invention is shown, having a first transmission shift group with a stepped planetary gear set with a third interlocking variant, which is connected upstream of a second transmission shift group with two planetary gear sets with a first interlocking variant

[0026] Figure 5A schematic diagrammatic view of a mid-axle transmission according to the invention is shown, having a first transmission shift group with a stepped planetary gear set with a fourth interlocking variant, which is connected upstream of a second transmission shift group with two planetary gear sets with a first interlocking variant

[0027] Figure 6 A schematic diagrammatic view of a mid-axle transmission according to the invention is shown, having a first transmission shift group with a stepped planetary gear set with a fifth interlocking variant, which is connected upstream of a second transmission shift group with two planetary gear sets with a first interlocking variant

[0028] Figure 7 A schematic diagrammatic view of a midshaft transmission according to the invention is shown, having a first transmission shift group with a stepped planetary gear set with a sixth interlocking variant, which is connected upstream of a second transmission shift group with two planetary gear sets with a first interlocking variant

[0029] Figure 8 A schematic diagrammatic view of a mid-axle transmission according to the invention is shown, having a second transmission shift group with two planetary gear sets with a second interlocking variant, which is connected downstream of a first transmission shift group with a stepped planetary gear set with a first interlocking variant

[0030] Fig. 9 A schematic diagrammatic view of a central shaft transmission according to the invention is shown, having a second transmission shift group with two planetary gear sets with a third interlocking variant, which is connected downstream of a first transmission shift group with a stepped planetary gear set with a first interlocking variant

[0031] Fig.10 A schematic diagrammatic view of a mid-axle transmission according to the invention is shown, having a second transmission shift group with two planetary gear sets with a fourth interlocking variant, which is connected downstream of a first transmission shift group with a stepped planetary gear set with a first interlocking variant

[0032] Fig.11 A schematic diagrammatic view of a central shaft transmission according to the invention is shown, having a second transmission shift group with two planetary gear sets with a fifth interlocking variant, which is connected downstream of a first transmission shift group with a stepped planetary gear set with a first interlocking variant

[0033] Fig.12 A schematic diagrammatic view of a central shaft transmission according to the invention is shown, having a second transmission shift group with two planetary gear sets with a sixth interlocking variant, which is connected downstream of a first transmission shift group with a stepped planetary gear set with a first interlocking variant

[0034] Fig.13 A schematic diagrammatic view of a mid-axle transmission according to the invention is shown, with a first transmission shift group, in which the stepped planets of the stepped planetary gear set are shown in mirror-inverted form, the first transmission shift group being connected downstream of a second transmission shift group

[0035] Fig.14 Shift diagram showing nine engageable gear ratios with a mid-axle transmission

[0036] Fig.15 Shown according to Figure 1 Schematic diagrammatic view of a mid-shaft transmission, wherein a torque sensor is shown by way of example at the input

[0037] Fig.16 Shown according to Fig.15 Schematic diagram of a mid-shaft transmission, wherein the electric machine is arranged at the input by way of example

[0038] Fig.17 Shown according to Fig.15 A schematic diagrammatic view of a mid-shaft transmission of , wherein the electric machine is arranged at the output in an exemplary manner; and

[0039] Fig.18 Shown according to Fig.15 Schematic diagrammatic view of a bottom bracket transmission with the flywheel located upstream of the pedal crankshaft. DETAILED DESCRIPTION

[0040] Figures 1 to 18 Various design variants and embodiments of the planetary mid-shaft transmission according to the invention and the shifting diagrams are shown purely by way of example. Figure 1 By way of example, a bicycle or pedelec 1 , which is only schematically shown, is shown with a bottom bracket transmission.

[0041] The bottom bracket transmission is shown in a housing or bottom bracket housing 2, which has a pedal crank with a pedal as a pedal crankshaft WAn, wherein the pedal crankshaft WAn is connected to the input of one of the transmission shift groups 3, 4. The bottom bracket transmission also includes a transmission output shaft WAb as an output, which has a sprocket or pulley (not shown in more detail) connected to the output of one of the transmission shift groups 3, 4. The bottom bracket transmission comprises a multi-ratio first transmission shift group 3 and a multi-ratio second transmission shift group 4, wherein the first transmission shift group 3 has a two-stage stepped planetary gear set StRS, which is assigned a first shift element B1 as a positive locking brake, a second shift element B2 as a positive locking brake and a fifth shift element F1 I 、F1 II 、 F1 III 、F1 IV 、F1 V 、F1 VI as a flywheel, and wherein the second transmission shifting group 4 has a first planetary gear set RS1 and a second planetary gear set RS2, which are assigned a third shifting element B3 as a positive locking brake, a fourth shifting element B4 as a positive locking brake, and a sixth shifting element F2 I 、F2 II 、F2 III 、F2 IV 、F2 V 、F2 VI The two transmission shift groups 3 , 4 form, so to speak, two sub-transmissions which can be interconnected in any desired sequence between the pedal crankshaft WAn and the transmission output shaft WAb with respect to the direction of the power flow.

[0042] Regardless of the specific design variant, it is provided in the mid-shaft transmission that the stepped planetary gear carrier SPT as an element of the stepped planetary gear set StRS1 is connected to the pedal crankshaft WAn or to the sixth shaft W6 as the output shaft of the second transmission shift group 4, wherein the ring gear HR1.1 as an element of the stepped planetary gear set StRS is connected to the second element of the first planetary gear set RS1 or to the transmission output shaft WAb, wherein the second sun gear SR1.2 as an element of the stepped planetary gear set StRS can be fixed to the housing 2 or a static component, etc. via the first shift element B1, wherein the first sun gear SR1.1 as an element of the stepped planetary gear set StRS can be fixed to the housing 2 via the second shift element B2, wherein in order to interlock the stepped planetary gear set StRS, two elements of the stepped planetary gear set StRS are connected via the fifth shift element F1 I 、F1 II、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII capable of being connected to each other, wherein the first element of the first planetary gear set RS1 is connected to the first element of the second planetary gear set RS2, wherein the first element of the first planetary gear set RS1 and the first element of the second planetary gear set RS2 are commonly connected to the stepped planetary gear carrier SPT of the stepped planetary gear set StRS or are commonly connected to the transmission output shaft WAb, wherein the third element of the first planetary gear set RS1 can be fixed to the housing 2 via the third shift element B3, wherein the third element of the second planetary gear set RS2 can be fixed to the housing 2 via the fourth shift element B4, wherein the third element of the first planetary gear set RS1 is connected to the second element of the second planetary gear set RS2, and wherein in order to interlock the first planetary gear set RS1 and the second planetary gear set RS2, the two shafts connected to the elements of the first planetary gear set RS1 and the second planetary gear set RS2 are connected via the sixth shift element F2 I 、F2 II 、F2 III 、F2 IV 、F2 V 、F2 VI Able to connect to each other.

[0043] Figures 1 to 13 and Figures 15 to 18 The planetary gear sets RS1, RS2 provided in are each designed as a space-saving negative planetary gear set. Here, in each of the planetary gear sets RS1, RS2, a sun gear SR1, SR2 is provided as a first element, a star gear or planetary gear carrier PT1, PT2 is provided as a second element, and a ring gear HR1, HR2 is provided as a third element.

[0044] Figure 1 1 shows a design variant of a mid-shaft transmission, in which a first transmission shift group 3 is connected upstream of a second transmission shift group 4. Figure 1In the first design variant, it is provided that the stepped planetary gear carrier SPT as an element of the stepped planetary gear set StRS1 is connected to the pedal crankshaft WAn, wherein the ring gear HR1.1 as an element of the stepped planetary gear set StRS is connected to the planetary gear carrier PT1 of the first planetary gear set RS1 via the fifth shaft W5 as the input shaft of the second transmission shift group 4, wherein when the first shift element B1 is engaged, the second sun gear SR1.2 as an element of the stepped planetary gear set StRS can be fixed to the housing 2 via the first shaft W1, wherein when the second shift element B2 is engaged, the first sun gear SR1.1 as an element of the stepped planetary gear set StRS can be fixed to the housing 2 via the second shaft W2, wherein in order to interlock the stepped planetary gear set StRS in the first interlocking variant, when the fifth shift element F1 in the first arrangement variant is engaged. I When locked, the ring gear HR1.1 connected to the fifth shaft W5 can be connected to the first sun gear SR1.1 of the stepped planetary gear set StRS, which is connected to the second shaft W2, wherein the sun gear SR1 of the first planetary gear set RS1 is connected to the sun gear SR2 of the second planetary gear set RS2, wherein the sun gear SR1 of the first planetary gear set RS1 and the sun gear SR2 of the second planetary gear set RS2 are commonly connected to the transmission output shaft WAb, wherein when the third shift element B3 is engaged, the ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via the third shaft W3, wherein when the fourth shift element B4 is engaged, the ring gear HR2 of the second planetary gear set RS2 can be fixed to the housing 2 via the fourth shaft W4, wherein the ring gear HR1 of the first planetary gear set RS1 is connected to the planetary gear carrier PT2 of the second planetary gear set RS2 via the third shaft W3, and wherein in order to interlock the first planetary gear set RS1 and the second planetary gear set RS2 in the first interlocking variant, when the sixth shift element F2 in the first arrangement variant is engaged. I When locked, the fourth shaft W4 connected to the ring gear HR2 can be connected to the transmission output shaft WAb connected to the first sun gear SR1 and to the second sun gear SR2.

[0045] Figure 2 1 shows a design variant of a mid-shaft transmission, in which a first transmission shift group 3 is connected downstream of a second transmission shift group 4. Figure 2In the first design variant, it is provided that the stepped planetary gear carrier SPT as an element of the stepped planetary gear set StRS1 is connected to the sixth shaft W6 as the output shaft of the second transmission shift group 4, wherein the ring gear HR1.1 as an element of the stepped planetary gear set StRS is connected to the transmission output shaft WAb, wherein when the first shift element B1 is engaged, the second sun gear SR1.2 as an element of the stepped planetary gear set StRS can be fixed to the housing 2 via the first shaft W1, wherein when the second shift element B2 is engaged, the first sun gear SR1.1 as an element of the stepped planetary gear set StRS can be fixed to the housing 2 via the second shaft W2, wherein in order to interlock the stepped planetary gear set StRS in the first interlocking variant, when the fifth shift element F1 in the first arrangement variant is engaged. I When locked, the ring gear HR1.1 connected to the transmission output shaft WAb can be connected to the first sun gear SR1.1 of the stepped planetary gear set StRS, which is connected to the second shaft W2, wherein the sun gear SR1 of the first planetary gear set RS1 is connected to the sun gear SR2 of the second planetary gear set RS2, wherein the sun gear SR1 of the first planetary gear set RS1 and the sun gear SR2 of the second planetary gear set RS2 are commonly connected to the stepped planetary gear carrier SPT of the stepped planetary gear set StRS, wherein when the third shift element B3 is engaged When the fourth shift element B4 is engaged, the ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via the third shaft W3, wherein when the fourth shift element B4 is engaged, the ring gear HR2 of the second planetary gear set RS2 can be fixed to the housing 2 via the fourth shaft W4, wherein the ring gear HR1 of the first planetary gear set RS1 is connected to the planet gear carrier PT2 of the second planetary gear set RS2 via the third shaft W3, and wherein in order to interlock the first planetary gear set RS1 and the second planetary gear set RS2 in the case of the first interlocking variant, when the sixth shift element F2 in the first arrangement variant is engaged I When locked, the fourth shaft W4 connected to the ring gear HR2 can be connected to the sixth shaft W6 connected to the first sun gear SR1 and to the second sun gear SR2.

[0046] and Figure 1 In contrast, Figure 3 The second interlocking variant of the stepped planetary gear set StRS in the first transmission shift group 3 connected upstream of the second transmission shift group 4 is shown. In the case of the second interlocking variant, when the fifth shift element F1 in the second arrangement variant is II When locked, the second sun gear SR1.2 connected to the first shaft W1 is connected to the stepped planetary gear carrier SPT of the first stepped planetary gear set StR1, which is connected to the pedal crankshaft WAn.

[0047] and Figure 1 In contrast, Figure 4 The third interlocking variant of the stepped planetary gear set StRS in the first transmission shift group 3 connected upstream of the second transmission shift group 4 is shown. In the case of the third interlocking variant, when the fifth shift element F1 in the third arrangement variant is III When locked, the first sun gear SR1.1 connected to the second shaft W2 is connected to the stepped planetary gear carrier SPT of the first stepped planetary gear set StR1, which is connected to the pedal crankshaft WAn.

[0048] and Figure 1 In contrast, Figure 5 The fourth interlocking variant of the stepped planetary gear set StRS in the first transmission shift group 3 connected upstream of the second transmission shift group 4 is shown. In the case of the fourth interlocking variant, when the fifth shift element F1 in the fourth arrangement variant is IV When locked, the ring gear HR1.1 connected to the fifth shaft W5 is connected to the stepped planetary gear carrier SPT of the first stepped planetary gear set StR1, which is connected to the pedal crankshaft WAn.

[0049] and Figure 1 In contrast, Figure 6 The fifth interlocking variant of the stepped planetary gear set StRS in the first transmission shift group 3 connected upstream of the second transmission shift group 4 is shown. In the case of the fifth interlocking variant, when the fifth shifting element F1 in the fifth arrangement variant is V When locked, the second sun gear SR1.2 connected to the first shaft W1 is connected to the first sun gear SR1.1 of the first stepped planetary gear set StR1, and the first sun gear is connected to the second shaft W2.

[0050] and Figure 1 In contrast, Figure 7 The sixth interlocking variant of the stepped planetary gear set StRS1 in the first transmission shift group 3 connected upstream of the second transmission shift group 4 is shown. In the case of the sixth interlocking variant, when the fifth shift element F1 in the sixth arrangement variant is VI When locked, the second sun gear SR1.2 connected to the first shaft W1 is connected to the ring gear HR1.1 of the first stepped planetary gear set StR1, which is connected to the fifth shaft W5.

[0051] and Figure 1 In contrast, Figure 8The second interlocking variant of the first planetary gear set RS1 and the planetary gear set RS2 in the second transmission shift group 4 connected downstream of the first transmission shift group 3 is shown. In the case of the second interlocking variant, when the sixth shift element F2 in the second arrangement variant is II When locked, the third shaft W3 connected to the ring gear HR1 of the first planetary gear set RS1 and to the planetary gear carrier PT2 of the second planetary gear set RS2 is connected to the transmission output shaft WAb, which is connected to the sun gear SR1 of the first planetary gear set RS1 and to the sun gear SR2 of the second planetary gear set RS2.

[0052] and Figure 1 In contrast, Fig. 9 The third interlocking variant of the first planetary gear set RS1 and the planetary gear set RS2 in the second transmission shift group 4 connected downstream of the first transmission shift group 3 is shown. In the case of the third interlocking variant, when the sixth shift element F2 in the third arrangement variant is III When locked, the fifth shaft W5 connected to the planetary gear carrier PT1 of the first planetary gear set RS1 is connected to the transmission output shaft WAb connected to the sun gear SR1 of the first planetary gear set RS1 and to the sun gear SR2 of the second planetary gear set RS2.

[0053] and Figure 1 In contrast, Fig.10 The fourth interlocking variant of the first planetary gear set RS1 and the planetary gear set RS2 in the second transmission shift group 4 connected downstream of the first transmission shift group 3 is shown. In the case of the fourth interlocking variant, when the sixth shift element F2 in the fourth arrangement variant is IV When locked, the third shaft W3 connected to the ring gear HR1 of the first planetary gear set RS1 and to the planet carrier PT2 of the second planetary gear set RS2 is connected to the fourth shaft W4 connected to the ring gear HR2 of the second planetary gear set RS2.

[0054] and Figure 1 In contrast, Fig.11 The fifth interlocking variant of the first planetary gear set RS1 and the planetary gear set RS2 in the second transmission shift group 4 connected downstream of the first transmission shift group 3 is shown. In the case of the fifth interlocking variant, when the sixth shift element F2 in the fifth arrangement variant is V When locked, the third shaft W3 connected to the ring gear HR1 of the first planetary gear set RS1 and to the planet carrier PT2 of the second planetary gear set RS2 is connected to the fifth shaft W5 connected to the planet carrier PT1 of the first planetary gear set RS1.

[0055] and Figure 1 In contrast, Fig.12 The sixth interlocking variant of the first planetary gear set RS1 and the planetary gear set RS2 in the second transmission shift group 4 connected downstream of the first transmission shift group 3 is shown. In the case of the sixth interlocking variant, when the sixth shifting element F2 in the sixth arrangement variant is VI When locked, the fourth shaft W4 connected to the ring gear HR2 of the second planetary gear set RS2 is connected to the fifth shaft W5 connected to the planet carrier PT1 of the first planetary gear set RS1.

[0056] Fig.13 Based on Figure 1 The embodiment of FIG. 1 shows a mirror-inverted stepped planet in a stepped planetary gear set StRS, in which two stages of the stepped planet have been axially interchanged. This means that, when viewed axially, the second sun gear SR1.2 is arranged in a first plane and the first sun gear SR1.1 together with the ring gear HR1.1 is arranged in a second plane.

[0057] Fig.14 The shift diagram of a central shaft transmission with a first transmission shift group 3 as a three-ratio transmission and a second transmission shift group 4 as a three-ratio transmission is shown. This means that 3x3, i.e. nine transmission ratios G1, G2, G3, G4, G5, G6, G7, G8, G9 can be realized. The shift diagram indicates the shift elements B1, B2, B3, B4, F1 I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F2 I 、F2 II 、F2 III 、F2 IV 、F2 V 、F2 VI For each gear ratio G1, G2, G3, G4, G5, G6, G7, G8, G9. Here, for the flywheel F1 as the shift element I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F2 I 、F2 II 、F2 III 、F2 IV 、F2 V 、F2 VI, the X in the shift diagram indicates that the flywheel is locked. This occurs automatically without external actuation. In addition, for brakes B1, B2, B3, B4 as shift elements, the X in the shift diagram indicates that brakes B1, B2, B3, B4 are engaged. This is performed by a suitable actuator device. Here, for flywheel F1 I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F2 I 、F2 II 、F2 III 、F2 IV 、F2 V 、F2 VI , empty field means that these flywheels are not locked. For brakes B1, B2, B3, B4, empty field means that these brakes are disengaged.

[0058] Specifically, from Fig.14 As can be seen from the shift diagram, in order to achieve or engage the first transmission ratio G1, the fifth shift element F1 designed as a flywheel I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI and the sixth shifting element F2 designed as a flywheel I 、F2 II 、F2 III 、F2 IV 、F2 V 、F2 VI , locked; wherein, in order to achieve the second transmission ratio G2, the first shift element B1 designed as a brake is engaged, and the sixth shift element F2 designed as a flywheel I 、F2 II 、F2 III 、F2 IV 、F2 V 、F2 VI wherein, in order to achieve the third transmission ratio G3, the second shift element B2 is designed as a brake and is engaged, and the sixth shift element F2 is designed as a flywheel I 、F2 II 、F2 III 、F2 IV 、F2 V 、F2 VI wherein, in order to achieve the fourth gear ratio G4, the fourth shift element B4 designed as a brake is engaged, and the fifth shift element F1 designed as a flywheel I 、F1II 、F1 III 、F1 IV 、F1 V 、F1 VI wherein, in order to achieve the fifth transmission ratio G5, the first shifting element B1 designed as a brake and the fourth shifting element B4 designed as a brake are engaged; wherein, in order to achieve the sixth transmission ratio G6, the second shifting element B2 designed as a brake and the fourth shifting element B4 designed as a brake are engaged; wherein, in order to achieve the seventh transmission ratio G7, the third shifting element B3 designed as a brake is engaged, and the fifth shifting element F1 designed as a flywheel is engaged I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI Locked; in order to achieve the eighth transmission ratio G8, the first shift element B1 designed as a brake and the third shift element B3 designed as a brake are engaged; and / or, wherein in order to achieve the ninth transmission ratio G9, the second shift element B2 designed as a brake and the third shift element B3 designed as a brake are engaged.

[0059] Fig.15 Shown according to Figure 1 An embodiment of a mid-shaft transmission according to the invention in which the torque sensor 5 is connected or connectable to the pedal crankshaft or connected or connectable to the transmission input shaft WAn. For example, a disc-shaped torque sensor 5 can be arranged at the transmission input. However, the torque sensor 5 can also be of some other design.

[0060] Fig.16 and Fig.17 Each shows a method based on the Fig.15 Embodiment of a mid-shaft transmission with an additional electric motor EM. The electric motor EM can be connected to the pedal crankshaft WAn, such as Fig.16 It is also conceivable that the motor EM is connected to the transmission output shaft WAb, such as Fig.17 As shown. The electric motor EM is preferably arranged axially parallel to the pedal crankshaft or the transmission input shaft WAn. However, the electric motor EM can also be arranged coaxially with respect to the pedal crankshaft. Regardless of this, it is advantageous for the electric motor EM to be connected via a flywheel F0 or the like so that during operation without the electric motor EM, no losses are generated due to the rotation of the electric motor EM therewith.

[0061] Fig.18 It shows that according to the present invention Fig.15Embodiment of a bottom bracket transmission with an additional flywheel F between the pedal cranks and the transmission input of the bottom bracket transmission. In this way, when pedaling is interrupted, the flywheel can open the pedal cranks and decouple the pedal cranks from the inertia mass of the transmission gear set, in particular the inertia mass of the electric motor EM, so that no inertia forces are felt at the pedals.

[0062] Reference numerals

[0063] 1 Bicycle or electric assisted bicycle

[0064] 2 Shell or bottom bracket shell

[0065] 3 First transmission shift group

[0066] 4 Second transmission shift group

[0067] 5. Torque sensor

[0068] EM Motor

[0069] F0 Flywheel for electric motor

[0070] F Additional flywheel

[0071] SR1 Sun gear of the first planetary gear set

[0072] PT1 Planetary gear carrier for the first planetary gear set

[0073] HR1 Ring gear of the first planetary gear set

[0074] SR2 Sun gear of the second planetary gear set

[0075] PT2 Planetary gear carrier for the second planetary gear set

[0076] HR2 Ring gear of the second planetary gear set

[0077] SR1.1 The first sun gear of the stepped planetary gear set has a relatively small number of teeth

[0078] SR1.2 Second sun gear with relatively large number of teeth of stepped planetary gear set

[0079] HR1.1 Ring gear of stepped planetary gear set

[0080] SPT Stepped planetary gear carrier for stepped planetary gear sets

[0081] RS1 1st planetary gear set

[0082] RS2 Second planetary gear set

[0083] StRS stepped planetary gear set

[0084] WAn transmission input shaft or pedal crankshaft

[0085] WAb transmission output shaft

[0086] W1 first axis

[0087] W2 Second Axis

[0088] W3 Third Axis

[0089] W4 fourth axis

[0090] W5 Fifth Axis

[0091] W6 Sixth Axis

[0092] G1 first gear ratio

[0093] G2 second gear ratio

[0094] G3 third gear ratio

[0095] G4 fourth gear ratio

[0096] G5 fifth gear ratio

[0097] G6 6th gear ratio

[0098] G7 seventh gear ratio

[0099] G8 eighth gear ratio

[0100] G9 ninth gear ratio

[0101] B1 First shifting element, designed as a brake

[0102] B2 Second shifting element, designed as a brake

[0103] B3 Third shifting element, designed as a brake

[0104] B4 Fourth shifting element, designed as a brake

[0105] F1 I The fifth shifting element, designed as a flywheel, is in the first arrangement position

[0106] F1 II The fifth shifting element, designed as a flywheel, is in the second arrangement position

[0107] F1 III The fifth shifting element, designed as a flywheel, is in the third arrangement position

[0108] F1 IV The fifth shifting element, designed as a flywheel, is in the fourth arrangement position

[0109] F1 V The fifth shifting element, designed as a flywheel, is in the fifth arrangement position

[0110] F1 VI The fifth shifting element, designed as a flywheel, is in the sixth arrangement position

[0111] F2 I The sixth shifting element, designed as a flywheel, is in the first arrangement position

[0112] F2 II The sixth shifting element, designed as a flywheel, is in the second arrangement position

[0113] F2 III The sixth shifting element, designed as a flywheel, is in the third arrangement position

[0114] F2 IV The sixth shifting element, designed as a flywheel, is in the fourth arrangement position

[0115] F2 V The sixth shifting element, designed as a flywheel, is in the fifth arrangement position

[0116] F2 VI The sixth shifting element, designed as a flywheel, is in a sixth arrangement position.

Claims

1. A planetary mid-shaft transmission for a bicycle or an electric power-assisted vehicle (1), the mid-shaft transmission having a pedal crankshaft (WAn) as an input and a transmission output shaft (WAb) as an output, and having other shafts (W1, W2, W3, W4, W5, W6), and having a first transmission shift group (3) and a second transmission shift group (4), the first transmission shift group (3) and the second transmission shift group (4) being coupled to each other to achieve a plurality of gear ratios (G1, G2, G3, G4, G5, G6, G7, G8, G9, G10, G11, G12), The first transmission shift group (3) includes a two-stage stepped planetary gear set (StRS), and the two-stage stepped planetary gear set (StRS) is assigned a first shift element (B1), a second shift element (B2) and a fifth shift element (F1 I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI ), The second transmission shifting group (4) includes a first planetary gear set (RS1) and a second planetary gear set (RS2), and the first planetary gear set (RS1) and the second planetary gear set (RS2) are assigned a third shifting element (B3), a fourth shifting element (B4) and a sixth shifting element (F2 I 、F2 II 、F2 III 、F2 IV 、F2 V 、F2 VI ), wherein a stepped planetary gear carrier (SPT) as an element of the stepped planetary gear set (StRS1) is connected to the pedal crankshaft (WAn) or to a sixth shaft (W6) as an output shaft of the second transmission shift group (4), wherein the ring gear (HR1.1) as an element of the stepped planetary gear set (StRS) is connected to the second element of the first planetary gear set (RS1) or to the transmission output shaft (WAb), wherein the second sun gear (SR1.2) as an element of the stepped planetary gear set (StRS) can be fixed to the housing (2) via a first shifting element (B1), wherein a first sun gear (SR1.1) as an element of the stepped planetary gear set (StRS) can be fixed to the housing (2) via a second shifting element (B2), in, In order to interlock the stepped planetary gear set (StRS), two elements of the stepped planetary gear set (StRS) are connected via the fifth shift element (F1 I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI ) can be connected to each other, wherein the first element of the first planetary gear set (RS1) is connected to the first element of the second planetary gear set (RS2), wherein the first element of the first planetary gear set (RS1) and the first element of the second planetary gear set (RS2) are commonly connected to the stepped planetary gear carrier (SPT) of the stepped planetary gear set (StRS) or commonly connected to the transmission output shaft (WAb), The third element of the first planetary gear set (RS1) can be fixed to the housing (2) via a third shift element (B3), wherein the third element of the second planetary gear set (RS2) can be fixed to the housing (2) via a fourth shift element (B4), wherein the third element of the first planetary gear set (RS1) is connected to the second element of the second planetary gear set (RS2), and In order to interlock the first planetary gear set (RS1) and the second planetary gear set (RS2), two shafts connected to the elements of the first planetary gear set (RS1) and the second planetary gear set (RS2) are connected via a sixth shift element (F2 I 、F2 II 、F2 III 、F2 IV 、F2 V 、F2 VI ) can be connected to each other.

2. The mid-shaft transmission according to claim 1, characterized in that: The first transmission shift group (3) is connected upstream or downstream of the second transmission shift group (4).

3. The mid-shaft transmission according to claim 1 or 2, characterized in that: The stepped planetary gear carrier (SPT) as an element of the stepped planetary gear set (StRS1) is connected to the pedal crankshaft (WAn) or to the sixth shaft (W6) as an output shaft of the second transmission shift group (4), wherein the ring gear (HR1.1) as an element of the stepped planetary gear set (StRS) is connected to the second element of the first planetary gear set (RS1) or to the transmission output shaft (WAb) via a fifth shaft (W5), wherein the second sun gear (SR1.2) as an element of the stepped planetary gear set (StRS) can be fixed to the housing (2) via the first shaft (W1) when the first shift element (B1) is engaged, wherein the first sun gear (SR1.1) as an element of the stepped planetary gear set (StRS) can be fixed to the housing (2) via a second shaft (W2) when the second shift element (B2) is engaged, In order to interlock the stepped planetary gear set (StRS), when the fifth shifting element (F1 I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI ) is locked, the two elements of the stepped planetary gear set (StRS) can be connected to each other, wherein the first element of the first planetary gear set (RS1) is connected to the first element of the second planetary gear set (RS2), wherein the first element of the first planetary gear set (RS1) and the first element of the second planetary gear set (RS2) are commonly connected to the stepped planetary gear carrier (SPT) of the stepped planetary gear set (StRS) or commonly connected to the transmission output shaft (WAb), wherein when the third shift element (B3) is engaged, the third element of the first planetary gear set (RS1) can be fixed to the housing (2) via a third shaft (W3), wherein when the fourth shift element (B4) is engaged, the third element of the second planetary gear set (RS2) can be fixed to the housing (2) via a fourth shaft (W4), wherein the third element of the first planetary gear set (RS1) is connected to the second element of the second planetary gear set (RS2) via the third shaft (W3), and In order to interlock the first planetary gear set (RS1) and the second planetary gear set (RS2), when the sixth shift element (F2 I 、F2 II 、F2 III 、F2 IV 、F2 V 、F2 VI ) is locked, the two shafts (WAb, W3, W4, W5) connected to the elements of the first planetary gear set (RS1) and the second planetary gear set (RS2) can be connected to each other.

4. A mid-shaft transmission according to any one of the preceding claims, characterised in that The first shift element (B1), the second shift element (B2), the third shift element (B3) and the fourth shift element (B4) are each designed as a positive-locking brake, and / or The fifth shifting element (F1 I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI ) and the sixth shift element (F2 I 、F2 II 、F2 III 、F2 IV 、F2 V 、F2 VI ) are each designed as a flywheel.

5. A mid-shaft transmission according to any one of the preceding claims, characterised in that The first planetary gear set (RS1) and / or the second planetary gear set (RS2) are each designed as a negative planetary gear set.

6. The mid-shaft transmission according to claim 5, characterized in that: In the case of a negative planetary gear set, the first element is designed as a sun gear (SR1, SR2), the second element is designed as a planet gear carrier (PT1, PT2), and the third element is designed as a ring gear (HR1, HR2).

7. A mid-shaft transmission according to any one of the preceding claims, characterised in that The first planetary gear set (RS1) and / or the second planetary gear set (RS2) are each designed as a spur planetary gear set.

8. The mid-shaft transmission according to claim 7, characterized in that: In the case of a spurious planetary gear set, the first element is designed as a sun gear (SR1, SR2), the second element is designed as a ring gear (HR1, HR2), and the third element is designed as a planet carrier (PT1, PT2).

9. A mid-shaft transmission according to any one of the preceding claims, characterised in that A torque sensor (5) is connected to the pedal crankshaft (WAn).

10. A mid-shaft transmission according to any one of the preceding claims, characterised in that At least one electric machine (EM) is connected or connectable to the pedal crankshaft (WAn) or to the transmission output shaft (WAb).

11. The mid-shaft transmission according to claim 10, characterized in that: The electric motor (EM) is arranged axially parallel to the pedal crankshaft (WAn).

12. A mid-shaft transmission according to any one of the preceding claims, characterised in that In order to achieve or engage the first transmission ratio (G1), the fifth shifting element (F1) designed as a flywheel I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI ) and the sixth shifting element (F2 I 、F2 II 、F2 III 、F2 IV 、F2 V 、F2 VI )locking; In order to achieve the second transmission ratio (G2), the first shifting element (B1) designed as a brake is engaged and the sixth shifting element (F2) designed as a flywheel is engaged. I 、F2 II 、F2 III 、F2 IV 、F2 V 、F2 VI )locking; In order to achieve the third transmission ratio (G3), the second shifting element (B2) designed as a brake is engaged, and the sixth shifting element (F2) designed as a flywheel is engaged. I 、F2 II 、F2 III 、F2 IV 、F2 V 、F2 VI )locking; In order to achieve the fourth transmission ratio (G4), the fourth shifting element (B4) designed as a brake is engaged, and the fifth shifting element (F1) designed as a flywheel is engaged. I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI )locking; wherein, in order to achieve a fifth transmission ratio (G5), the first shifting element (B1) designed as a brake and the fourth shifting element (B4) designed as a brake are engaged; wherein, in order to achieve a sixth transmission ratio (G6), the second shifting element (B2) designed as a brake and the fourth shifting element (B4) designed as a brake are engaged; In order to achieve the seventh gear ratio (G7), the third shifting element (B3) designed as a brake is engaged and the fifth shifting element (F1) designed as a flywheel is engaged. I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI )locking; wherein, in order to achieve an eighth transmission ratio (G8), the first shifting element (B1) designed as a brake and the third shifting element (B3) designed as a brake are engaged; and / or To achieve the ninth gear ratio (G9), the second shifting element (B2) designed as a brake and the third shifting element (B3) designed as a brake are engaged.

13. A bicycle or an electric assisted vehicle (1) having a bottom bracket transmission according to any one of the preceding claims.

Images