Bicycle hub internal gear with nested planetary gear mechanism

Abstract

The application discloses a bicycle hub internal gear changer with nested planetary gear mechanism and belongs to the technical field of planetary gear mechanism transmission. The application overcomes the problems of the existing hub internal gear changer, such as heavy weight, large number of shift mechanisms and scattered arrangement. The application comprises a first nested planetary gear mechanism formed by setting a first planetary gear set in the inner circumference of a second planetary gear set, a second nested planetary gear mechanism formed by setting a third planetary gear set in the inner circumference of a fourth planetary gear set, and a simplified structure of the hub internal gear changer, which can make the size of the internal gear changer smaller. The application comprises one non-rotatable hub shaft, seven rotatable shafts, six shift mechanisms arranged on the hub shaft and concentrated along the axial direction, a small number of shift mechanisms, a compact structure, simple shift logic, and a shift mechanism allowing selective operation to form eight forward gears between the input shaft and the output shaft of the hub internal gear changer.

Description

Technical Field

[0001] This invention belongs to the field of planetary gear mechanism transmission technology, and relates to a hub gearbox, particularly for the power transmission system of a bicycle, specifically a bicycle hub gearbox with a nested planetary gear mechanism. Background Technology

[0002] A bicycle is a means of transportation, and for amateur enthusiasts and professional athletes, it's also a tool for fitness, recreation, and competition. Bicycle manufacturers are constantly improving various bicycle components, one of which has been redesigned: the bicycle wheel hub. The component that allows the hub to have different speeds and torques is the derailleur. Derailleurs are divided into two types: external derailleurs and internal derailleurs. External derailleurs adjust speed and torque by changing the number of teeth on the front and rear sprockets, allowing the bicycle to adapt to different road conditions. External derailleurs have a simpler structure, but their components are exposed, making them susceptible to rain, mud, oil, etc., requiring regular cleaning and maintenance. Furthermore, their shifting is often unstable, generates more noise during shifting, and generally has a shorter lifespan. Internal derailleurs, on the other hand, have a planetary gear mechanism installed inside the rear wheel hub. Riders can select different gear ratios to adjust speed and torque. Compared to external derailleurs, internal derailleurs are smaller, have a longer lifespan, and require less maintenance, leading to their increasing popularity.

[0003] An in-wheel derailleur typically includes a hub axle mounted on the bicycle frame. The hub axle rotatably supports the freewheel and hub shell. The rider's pedaling force is transmitted to the freewheel via the drive sprocket and chain. The hub shell houses multiple planetary gear sets positioned between the freewheel and the hub shell. Power is transmitted from the freewheel to these planetary gear sets, and then to the hub shell. These planetary gear sets can produce multiple specific gear ratios for different power transmission paths, which the rider can select using a shift mechanism.

[0004] In-hub derailleurs with planetary gear mechanisms have been described extensively in the prior art and continue to be developed and improved. For example, Chinese invention patent number 200710126284.9 discloses a bicycle hub assembly in which four planetary gear mechanisms are arranged axially along the hub shaft. Seven shifting mechanisms selectively manipulate the engagement or disengagement of the sun gear, planet carrier, or ring gear of the four planetary gear mechanisms to achieve eight different power transmission paths. These shifting mechanisms employ a ratchet-type overrunning clutch. Increasing the number of shifting mechanisms within the bicycle hub complicates the shifting logic and increases the complexity and weight of the internal derailleur structure. Clearly, these disadvantages limit the widespread application of in-hub derailleurs on bicycles. Summary of the Invention

[0005] The technical problem to be solved by the present invention is to overcome the problems of existing in-wheel derailleurs being heavy and having a large number of gear shifting mechanisms that are scattered. The present invention provides an in-wheel derailleur for bicycles with a nested planetary gear mechanism that has fewer gear shifting mechanisms, a compact structure, a lighter weight, and simpler control logic.

[0006] To solve the above-mentioned technical problems, the present invention is implemented using the following technical solution: a bicycle hub-mounted derailleur with nested planetary gear mechanisms, comprising a non-rotatable hub shaft 8, two nested planetary gear mechanisms disposed within a hub housing 11, seven rotatable shafts, and six shifting mechanisms; the two nested planetary gear mechanisms are a first nested planetary gear mechanism T1 and a second nested planetary gear mechanism T2; the first nested planetary gear mechanism T1 includes a first planetary gear set P1 and a second planetary gear set P2; the second nested planetary gear mechanism T2 includes a third planetary gear set P3 and a fourth planetary gear set P4; the first planetary gear set P1 is nested within the inner circumference of the second planetary gear set P2; the first planetary gear set P1 includes a first planetary gear set P3 and a second planetary gear set P4. The first planetary gear set P2 consists of a sun gear P11, a first planet carrier P12, and a first ring gear P13. The first planet carrier P12 guides a first planetary gear P14 on a circular track, and the first planetary gear P14 can rotate on the first planet carrier P12. The first planetary gear P14 meshes externally with the first sun gear P11 and internally with the first ring gear P13. The second planetary gear set P2 includes a second sun gear P21, a second planet carrier P22, and a second ring gear P23. The second planet carrier P22 guides a second planetary gear P24 on a circular track, and the second planetary gear P24 can rotate on the second planet carrier P22. The second planetary gear P24 meshes externally with the second sun gear P21 and internally with the second ring gear P23. The third planetary gear set P3 is nested within the fourth planetary gear set. The inner circumference of gear set P4; the third planetary gear set P3 includes a third sun gear P31, a third planet carrier P32, and a third ring gear P33; the third planet carrier P32 guides the third planetary gear P34 on a circular track, and the third planetary gear P34 can rotate on the third planet carrier P32; the third planetary gear P34 meshes externally with the third sun gear P31 and internally with the third ring gear P33; the fourth planetary gear set P4 includes a fourth sun gear P41, a fourth planet carrier P42, and a fourth ring gear P43; the fourth planet carrier P42 guides the fourth planetary gear P44 on a circular track, and the fourth planetary gear P44 can rotate on the fourth planet carrier P42; the fourth planetary gear P44 meshes externally with the fourth sun gear P41 and internally with the fourth ring gear P43. P43 is internally meshed; the seven rotatable shafts are input shaft 1, output shaft 2, third shaft 3, fourth shaft 4, fifth shaft 5, sixth shaft 6, and seventh shaft 7; input shaft 1 is non-rotatably connected to flywheel 10 and first planetary carrier P12; output shaft 2 is non-rotatably connected to hub housing 11, second ring gear P23, third planetary carrier P32, and fourth planetary carrier P42; third shaft 3 is non-rotatably connected to first sun gear P11; fourth shaft 4 is non-rotatably connected to third ring gear P33 and fourth sun gear P41; fifth shaft 5 is non-rotatably connected to second planetary carrier P22 and fourth ring gear P43; sixth shaft 6 is non-rotatably connected to third sun gear P31.The seventh shaft 7 is connected to the first gear ring P13 and the second sun gear P21 in a non-rotatable manner; the six shifting mechanisms consist of four brakes and two clutches, the four brakes being the first brake C1, the second brake C2, the third brake C3, and the fourth brake C4, and the two clutches being the first clutch C5 and the second clutch C6; the first brake C1 is a operable torque transmission device to selectively connect the sixth shaft 6 to the non-rotatable hub shaft 8; the second brake C2 is a operable torque transmission device to selectively connect the... The fourth shaft 4 is connected to the non-rotatable hub shaft 8; the third brake C3 is a operable torque transmission device to selectively connect the fifth shaft 5 to the non-rotatable hub shaft 8; the fourth brake C4 is a operable torque transmission device to selectively connect the third shaft 3 to the non-rotatable hub shaft 8; the first clutch C5 is a operable torque transmission device to selectively connect the input shaft 1 to the third shaft 3; the second clutch C6 is a operable torque transmission device to selectively connect the input shaft 1 to the fifth shaft 5.

[0007] The six shifting mechanisms described in the technical solution are set on the non-rotatable hub shaft 8 and arranged sequentially along the axial direction. When viewed from the input shaft 1, they are, in order, the fourth brake C4, the first clutch C5, the second clutch C6, the third brake C3, the second brake C2, and the first brake C1.

[0008] In the technical solution, the first brake C1, the second brake C2, the third brake C3, and the fourth brake C4 are configured as a shifting mechanism that can be used according to the operation requirements, especially a mechanical and / or electric ratchet clutch; the first clutch C5 and the second clutch C6 are configured as a shifting mechanism that can be used according to the operation requirements, especially a mechanical and / or electric jaw clutch.

[0009] The phrase "cannot be connected relative to each other" should be understood as two components being connected by a spline or rigidity, so that the two components have equal angular velocities when they rotate.

[0010] The term "clutch" should be understood in particular as a unit configured to selectively engage or disengage two rotatably mounted shafts without relative rotation. Similarly, the term "brake" should be understood in particular as a unit configured to selectively engage or disengage a rotatable shaft and a non-rotatable shaft, particularly the inner transmission hub shaft, without relative rotation.

[0011] Compared with the prior art, the beneficial effects of the present invention are:

[0012] This invention radially nests the first planetary gear mechanism into the sun gear of the second planetary gear mechanism, making the ring gear of the first planetary gear mechanism and the sun gear of the second planetary gear mechanism non-rotatably connected to form a nested planetary gear mechanism. Four planetary gear mechanisms can be nested into two nested planetary gear mechanisms, which greatly simplifies the structure of the in-hub transmission. The size of the in-hub transmission can be made smaller, effectively reducing the weight of the in-hub transmission. At the same time, the number of shifting mechanisms is reduced and they are arranged sequentially along the axial direction of the hub shaft, making the in-hub transmission more compact and further reducing its weight. The shifting logic is simple, making the production cost of the in-hub transmission lower. Attached Figure Description

[0013] The invention will now be further described with reference to the accompanying drawings:

[0014] Figure 1 This is a schematic view of a bicycle in-hub transmission with a nested planetary gear mechanism according to an embodiment of the present invention;

[0015] In the picture:

[0016] 1. Input axis;

[0017] 2. Output shaft;

[0018] 3. Third axis;

[0019] 4. Fourth axis;

[0020] 5. Fifth axis;

[0021] 6. The sixth axis;

[0022] 7. The seventh axis;

[0023] 8. Hub axles;

[0024] 9. Chain;

[0025] 10. Flywheel;

[0026] 11. Wheel hub shell;

[0027] 12. Ball bearings;

[0028] 13. Ball bearings;

[0029] 14. Ball bearings;

[0030] C1 First brake;

[0031] C2 Second Brake;

[0032] C3 Third brake;

[0033] C4 Fourth Brake;

[0034] C5 First Clutch;

[0035] C6 Second Clutch;

[0036] T1 First nested planetary gear mechanism;

[0037] T2 Second nested planetary gear mechanism;

[0038] P1 First planetary gear set;

[0039] P2 Second planetary gear set;

[0040] P3 Third Planetary Gear Set;

[0041] P4 Fourth Planetary Gear Set;

[0042] P11 First Sun Gear;

[0043] P12 First planetary support;

[0044] P13 First gear ring;

[0045] P14 First planetary gear;

[0046] P21 Second Sun Gear;

[0047] P22 Second planetary support;

[0048] P23 Second gear ring;

[0049] P24 Second planetary gear;

[0050] P31 Third Sun Gear;

[0051] P32 Third planetary support;

[0052] P33 Third gear ring;

[0053] P34 Third planetary gear;

[0054] P41 Fourth Sun Wheel;

[0055] P42 Fourth Planetary Carrier;

[0056] P43 Fourth gear ring;

[0057] P44 Fourth planetary wheel. Implementation

[0058] The present invention will now be described in detail with reference to the accompanying drawings:

[0059] Figure 1An embodiment of a bicycle in-hub derailleur with nested planetary gear mechanisms is shown. This in-hub derailleur has two nested planetary gear mechanisms: a first planetary gear set P1 nested within the inner circumference of a second planetary gear set P2 to form a first nested planetary gear mechanism T1; and a third planetary gear set P3 nested within the inner circumference of a fourth planetary gear set P4 to form a second nested planetary gear mechanism T2. All four planetary gear sets P1, P2, P3, and P4 have negative gear ratios. Six shifting mechanisms C1, C2, C3, C4, C5, and C6 are sequentially arranged along the hub axis. These shifting mechanisms are selectively operated to establish eight different power transmission paths, each producing a specific gear ratio, thus providing the in-hub derailleur with eight forward gears V1, V2, V3, V4, V5, V6, V7, and V8.

[0060] An in-hub derailleur with a nested planetary gear mechanism is configured to connect the bicycle freewheel 10 to a drive wheel (not shown in detail) of the bicycle. The gear ratio between the freewheel and the drive wheel can be adjusted using the in-hub derailleur.

[0061] The power input side of the bicycle in-hub derailleur with nested planetary gear mechanism has an input shaft 1, which is rotatably mounted on a hub shaft 8 equipped with ball bearings 13, and is non-rotatably connected to a flywheel 10 driven by a chain 9. The input shaft is configured to introduce driving torque into the in-hub derailleur.

[0062] Additionally, the power output side of the bicycle in-hub derailleur with nested planetary gear mechanism has an output shaft 2, which is non-rotatably connected to the hub housing 11, the second ring gear P23, the third planetary carrier P32, and the fourth planetary carrier P42. The hub housing is rotatably mounted on the input shaft 1, which is equipped with ball bearings 12, and is also rotatably mounted on the hub shaft 8, which is equipped with ball bearings 14. The output shaft is configured to transmit driving torque from the in-hub derailleur to the hub housing, which is non-rotatably connected to a drive wheel (not shown in detail).

[0063] The first planetary gear set P1 is located on the power input side. The first planetary gear set P1 has a single-stage planetary gear set. The single-stage planetary gear set includes a first sun gear P11, a first planet carrier P12, and a first ring gear P13. The planet carrier P12 guides planet gears P14 on a circular track. Planet gears P14 externally mesh with the sun gear P11 and internally mesh with the ring gear P13. Planet gears P14 can rotate circumferentially on the planet carrier P12. The characteristic coefficient of the first planetary gear set P1 is the fixed transmission ratio K1 = -4.00.

[0064] The second planetary gear set P2 is centrally located on the input side. The second planetary gear set P2 has a single-stage planetary gear set. This single-stage planetary gear set includes a second sun gear P21, a second planet carrier P22, and a second ring gear P23. The planet carrier P22 guides planet gears P24 on a circular track. Planet gears P24 externally mesh with the sun gear P21 and internally mesh with the ring gear P23. Planet gears P24 can rotate circumferentially on the planet carrier P22. The characteristic coefficient of the second planetary gear set P2 is the fixed transmission ratio K2 = -1.45.

[0065] The third planetary gear set P3 is centrally located on the output side. The third planetary gear set P3 is a single-stage planetary gear set. This single-stage planetary gear set includes a third sun gear P31, a third planet carrier P32, and a third ring gear P33. The planet carrier P32 guides planet gears P34 on a circular track. Planet gears P34 externally mesh with the sun gear P31 and internally mesh with the ring gear P33. Planet gears P34 can rotate circumferentially on the planet carrier P32. The characteristic coefficient of the third planetary gear set P3 is the fixed transmission ratio K3 = -3.15.

[0066] The fourth planetary gearbox P4 is located on the output side. The fourth planetary gear set P4 is a single-stage planetary gear set. This single-stage planetary gear set includes a fourth sun gear P41, a fourth planet carrier P42, and a fourth ring gear P43. The planet carrier P42 guides planet gears P44 on a circular track. Planet gears P44 externally mesh with the sun gear P41 and internally mesh with the ring gear P43. Planet gears P44 can rotate circumferentially on the planet carrier P42. The characteristic coefficient of the fourth planetary gear set P4 is a fixed planetary gear ratio K4 = -2.64.

[0067] Six shifting mechanisms are mounted on the non-rotatable hub shaft 8 and arranged sequentially along the axial direction. Viewed from the input shaft 1, they are, in order: fourth brake C4, first clutch C5, second clutch C6, third brake C3, second brake C2, and first brake C1. When the first brake C1 is actuated, it connects the non-rotatable hub shaft 8 to the sixth shaft 6; when the second brake C2 is actuated, it connects the non-rotatable hub shaft 8 to the fourth shaft 4; when the third brake C3 is actuated, it connects the non-rotatable hub shaft 8 to the fifth shaft 5; when the fourth brake C4 is actuated, it connects the non-rotatable hub shaft 8 to the third shaft 3; when the first clutch C5 is actuated, it connects the input shaft 1 to the third shaft 3; and when the second clutch C6 is actuated, it connects the input shaft 1 to the fifth shaft 5.

[0068] like Figure 1The invention shown is a bicycle in-hub gearbox with nested planetary gear mechanisms, comprising a non-rotatable hub shaft 8, four planetary gear sets (P1, P2, P3, P4) consisting of two nested planetary gear mechanisms (T1, T2) disposed within a hub housing 11, seven rotatable shafts (1, 2, 3, 4, 5, 6, 7), and six shift mechanisms (C1, C2, C3, C4, C5, C6). The shift mechanisms selectively engage or disengage to obtain eight different gear ratios between the input shaft 1 and the output shaft 2, thereby enabling eight forward gears. The input shaft 1, connected to the flywheel 10 and the first planetary carrier P12, is detachably connected to the third shaft 3 via a first clutch C5. The third shaft 3 is connected to the first sun gear P11 and is detachably connected to the hub shaft 8 via a fourth brake C4. The fifth shaft 5, connected to the second planetary carrier P22 and the fourth ring gear P43, is connected to the input shaft 8 via a second clutch C6. Shaft 1 is detachably connected, and the fifth shaft 5 is detachably connected to the hub shaft 8 via the third brake C3; the fourth shaft 4, which is connected to the third ring gear P33 and the fourth sun gear P41, is detachably connected to the hub shaft 8 via the second brake C2; ​​the sixth shaft 6, which is connected to the third sun gear P31, is connected to the hub shaft 8 via the first brake C1; the seventh shaft 7 is connected to the first ring gear P13 and the second sun gear P21; the output shaft 2 is connected to the second ring gear P23, the hub housing 11, the fourth planetary carrier P42, and the third planetary carrier P32.

[0069] Table 1 shows the data based on... Figure 1 This paper presents an exemplary shifting logic, gear ratios, and ratio intervals for an in-hub bicycle derailleur with a nested planetary gear mechanism. Each gear requires only two shift mechanisms to engage. The shifting diagram exemplifies how the gear ratios for each gear are determined, as well as the shift jump or ratio interval (the ratio of the gear ratios between adjacent gears) to the next higher gear can be identified. The gear ratio range for the in-hub derailleur is 3.45. In Table 1, the symbol "×" below each shift mechanism indicates that the shift mechanism is engaged in the corresponding gear, while the absence of the "×" indicates that the shift mechanism is disengaged in the corresponding gear.

[0070] Table 1

[0071]

[0072] As shown in Table 1, the first forward gear V1 is obtained by closing the second brake C2 and the first clutch C5; the second forward gear V2 is obtained by closing the second brake C2 and the fourth brake C4; the third forward gear V3 is obtained by closing the second brake C2 and the second clutch C6; the fourth forward gear V4 is obtained by closing the fourth brake C4 and the second clutch C6; the fifth forward gear V5 is obtained by closing the first clutch C5 and the second clutch C6; the sixth forward gear V6 is obtained by closing the first brake C1 and the second clutch C6; the seventh forward gear V7 is obtained by closing the first brake C1 and the first clutch C5; and the eighth forward gear V8 is obtained by closing the first brake C1 and the fourth brake C4.

[0073] In sequential shifting, two adjacent gears each require only one shift mechanism to disengage and one to engage, while the engagement of the other shift mechanism remains unchanged. This means that a single shift mechanism is shared when shifting into adjacent gears. For example, shifting sequentially from first forward gear V1 to the adjacent second forward gear V2 involves engaging the second brake C2 and the first clutch C5 to achieve first forward gear V1. When shifting into second forward gear V2, the first clutch C5 disengages and the fourth brake C4 engages, while the engagement of the second brake C2 remains unchanged. Shifting into non-adjacent gears also allows for shifting while sharing a single shift mechanism; this type of shifting is called skip shifting. For example, shifting sequentially from first forward gear V1 to the non-adjacent third forward gear V3 involves engaging the second brake C2 and the first clutch C5 to achieve first forward gear V1. When shifting into third forward gear V3, the first clutch C5 disengages and the second clutch C6 engages, while the engagement of the second brake C2 remains unchanged. Furthermore, it can be seen that the internal transmission can achieve small shift jumps and a dense range of gear ratios during shifting.

[0074] According to the present invention, even in the same in-wheel hub transmission schematic diagram, different gear ratio intervals can be obtained depending on the different shift logic, thereby enabling applications to specific variant schemes.

[0075] According to the present invention, the first brake C1, the second brake C2, the third brake C3, and the fourth brake C4 are configured as a shifting mechanism capable of operation, particularly force-locking brakes, such as pawl clutches, roller overrunning clutches, backstops, and one-way clutches, preferably mechanical and / or electric pawl clutches. The first clutch C5 and the second clutch C6 are configured as a shifting mechanism capable of operation, particularly force-locking clutches, such as jaw clutches, plate friction clutches, centrifugal clutches, and electromagnetic clutches, preferably, especially mechanical and / or electric jaw clutches.

[0076] Within the scope of an advantageous improvement of the invention, in order to drive additional bicycle loads, a motor can be installed on each axle, preferably on the input shaft 1 or the output shaft 2, as a generator and / or as an additional drive device.

[0077] Although only selected embodiments have been chosen to illustrate the invention, those skilled in the art will make various changes and modifications without departing from the scope of the invention as defined by the appended claims. Furthermore, the foregoing description of embodiments according to the invention is merely illustrative and not intended to limit the scope of the invention as defined by the appended claims and their equivalents.

Claims

1. A bicycle hub internal gear change with a nested planetary gear mechanism characterised in that: It includes a non-rotatable hub shaft (8), two nested planetary gear mechanisms set in the hub housing (11), seven rotatable shafts and six shifting mechanisms; The two nested planetary gear mechanisms are the first nested planetary gear mechanism (T1) and the second nested planetary gear mechanism (T2). The first nested planetary gear mechanism (T1) includes a first planetary gear set (P1) and a second planetary gear set (P2). The second nested planetary gear mechanism (T2) includes a third planetary gear set (P3) and a fourth planetary gear set (P4); The first planetary gear set (P1) is nested within the inner circumference of the second planetary gear set (P2); The first planetary gear set (P1) includes a first sun gear (P11), a first planet carrier (P12), and a first ring gear (P13); the first planet carrier (P12) guides the first planet gear (P14) on a circular track, and the first planet gear (P14) can rotate circumferentially on the first planet carrier (P12); the first planet gear (P14) meshes externally with the first sun gear (P11) and internally with the first ring gear (P13); The second planetary gear set (P2) includes a second sun gear (P21), a second planet carrier (P22), and a second ring gear (P23); the second planet carrier (P22) guides the second planet gear (P24) on a circular track, and the second planet gear (P24) can rotate on the second planet carrier (P22); the second planet gear (P24) meshes externally with the second sun gear (P21) and internally with the second ring gear (P23); The third planetary gear set (P3) is nested within the inner circumference of the fourth planetary gear set (P4); The third planetary gear set (P3) includes a third sun gear (P31), a third planet carrier (P32), and a third ring gear (P33); the third planet carrier (P32) guides the third planet gear (P34) on a circular track, and the third planet gear (P34) can rotate on the third planet carrier (P32); the third planet gear (P34) meshes externally with the third sun gear (P31) and internally with the third ring gear (P33); The fourth planetary gear set (P4) includes a fourth sun gear (P41), a fourth planet carrier (P42), and a fourth ring gear (P43); the fourth planet carrier (P42) guides the fourth planet gear (P44) on a circular track, and the fourth planet gear (P44) can rotate on the fourth planet carrier (P42); the fourth planet gear (P44) meshes externally with the fourth sun gear (P41) and internally with the fourth ring gear (P43); The seven rotatable axes are the input axis (1), the output axis (2), the third axis (3), the fourth axis (4), the fifth axis (5), the sixth axis (6), and the seventh axis (7). The input shaft (1) is connected to the flywheel (10) and the first planetary carrier (P12) in a manner that prevents them from rotating relative to each other; The output shaft (2) is connected to the hub housing (11), the second gear ring (P23), the third planetary carrier (P32), and the fourth planetary carrier (P42) in a manner that prevents them from rotating relative to each other. The third shaft (3) is connected to the first sun gear (P11) in a way that prevents them from rotating relative to each other; The fourth shaft (4) is connected to the third gear ring (P33) and the fourth sun gear (P41) in a way that prevents them from rotating relative to each other. The fifth shaft (5) is connected to the second planetary carrier (P22) and the fourth gear ring (P43) in a way that prevents them from rotating relative to each other; The sixth shaft (6) is connected to the third sun gear (P31) in a way that prevents them from rotating relative to each other; The seventh shaft (7) is connected to the first gear ring (P13) and the second sun gear (P21) in a way that prevents them from rotating relative to each other; The six shifting mechanisms consist of four brakes and two clutches. The four brakes are the first brake (C1), the second brake (C2), the third brake (C3), and the fourth brake (C4). The two clutches are the first clutch (C5) and the second clutch (C6). The first brake (C1) is a steerable torque transmission device for selectively connecting the sixth shaft (6) to the non-rotatable hub shaft (8); The second brake (C2) is a steerable torque transmission device for selectively connecting the fourth shaft (4) to the non-rotatable hub shaft (8); The third brake (C3) is a steerable torque transmission device for selectively connecting the fifth shaft (5) to the non-rotatable hub shaft (8); The fourth brake (C4) is a steerable torque transmission device for selectively connecting the third shaft (3) to the non-rotatable hub shaft (8); The first clutch (C5) is a steerable torque transmission device for selectively connecting the input shaft (1) to the third shaft (3); The second clutch (C6) is a steerable torque transmission device for selectively connecting the input shaft (1) to the fifth shaft (5).

2. The bicycle hub-mounted derailleur with a nested planetary gear mechanism according to claim 1, characterized in that: The six shifting mechanisms are set on the non-rotatable hub shaft (8) and arranged sequentially along the axial direction. When viewed from the input shaft (1), they are the fourth brake (C4), the first clutch (C5), the second clutch (C6), the third brake (C3), the second brake (C2), and the first brake (C1).

3. The bicycle hub-mounted derailleur with a nested planetary gear mechanism according to claim 1, characterized in that: The first brake (C1), the second brake (C2), the third brake (C3), and the fourth brake (C4) are mechanical and / or electric ratchet clutches; The first clutch (C5) and the second clutch (C6) are mechanical and / or electric jaw clutches.

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