Variable-speed hub and vehicle

Abstract

The invention discloses a variable-speed hub and a vehicle, and relates to the field of power-assisted riding vehicles. According to the technical scheme, the gear shifting mechanism comprises a first planetary gear assembly, a second planetary gear assembly and a gear shifting adjusting assembly; the first planetary gear assembly comprises a first duplex planetary gear and a second duplex planetary gear, and the second planetary gear assembly comprises a third planetary gear; a second planet carrier of the second planetary gear assembly and a first output gear ring of the first planetary gear assembly are integrally formed; the gear shifting adjusting assembly comprises a gear shifting motor, a driving ring and a gear shifting sleeve. The first planetary gear assembly, the second planetary gear assembly and the gear shifting adjustment assembly are arranged in the limited axial space in the hub shell, variable speed adjustment of ten gears is achieved, automatic gear shifting adjustment can be achieved through the gear shifting motor, and therefore the riding experience can be optimized.

Description

Technical Field

[0001] The present invention relates to the field of power-assisted riding vehicles, and more particularly to a speed-changing hub and a vehicle. Background Art

[0002] The existing Chinese patent with publication number CN117533451A discloses a multi-speed adjustable speed change mechanism, which includes a central shaft, an output housing, an input sleeve, a planetary gear assembly and a shift adjustment assembly; the speed change mechanism can be integrated into a hub motor and can achieve five-speed shifting through a planetary gear assembly integrated with three sun gears.

[0003] If the above-mentioned speed change mechanism is used in a speed change hub, more axial space can be obtained. However, how to further increase the number of gears under limited axial space is a problem to be solved urgently. Summary of the invention

[0004] In view of the shortcomings of the prior art, one of the objects of the present invention is to provide a speed-changing hub, which not only realizes speed adjustment of ten gears by respectively arranging a first planetary gear assembly, a second planetary gear assembly and a shift adjustment assembly in the limited axial space within the hub shell, but also can realize automatic shift adjustment through a shift motor, thereby optimizing the riding experience.

[0005] To achieve the above object, the present invention provides the following technical solutions: A speed-changing hub comprises a middle shaft, a hub shell, an input sleeve, a first planetary gear assembly and a shift adjustment assembly; The first planetary gear assembly comprises a first planet carrier, a first double-coupled planetary gear and a second double-coupled planetary gear respectively arranged on the first planet carrier, an input ring gear meshed with the first double-coupled planetary gear, a first output ring gear meshed with the second double-coupled planetary gear, and a primary sun gear, a secondary sun gear, a third sun gear and a fourth sun gear sequentially arranged along the axial direction; The input gear ring and the input sleeve are linked in the circumferential direction, a first clutch assembly is arranged between the first planet carrier and the hub shell, and a second clutch assembly is arranged between the first output gear ring and the hub shell; The shift adjustment assembly includes a primary pawl and a shift ring gear matched with the primary sun gear, a secondary pawl matched with the secondary sun gear, a third pawl matched with the third sun gear, and a fourth pawl matched with the fourth sun gear; wherein the shift ring gear is linked with the input ring gear in the circumferential direction; In the first to fifth gears, the shift gear ring is separated from the primary sun gear; in the sixth to seventh gears, the shift gear ring is engaged with the primary sun gear and then moves in a circumferential direction; In addition, in the first gear, the first-level pawl engages with the first-level sun gear; in the second gear, the second-level pawl engages with the second-level sun gear; in the third gear, the first-level pawl engages with the first-level sun gear, and the third-level pawl engages with the third-level sun gear; in the fourth gear, the first-level pawl engages with the first-level sun gear, and the fourth-level pawl engages with the fourth-level sun gear; in the fifth gear, the second-level pawl engages with the second-level sun gear, and the fourth-level pawl engages with the fourth-level sun gear; in the sixth gear, the third-level pawl engages with the third-level sun gear; in the seventh gear, the fourth-level pawl engages with the fourth-level sun gear.

[0006] Furthermore, the speed-changing hub also includes one or more planetary gear assemblies connected to the first planetary gear assembly.

[0007] Furthermore, the speed-changing hub further comprises a second planetary gear assembly disposed at the end of the first planetary gear assembly; The second planetary gear assembly includes a second planet carrier connected to the first output ring gear, a third double-coupled planetary gear disposed on the second planet carrier, a second output ring gear meshing with the third double-coupled planetary gear, and a fifth-stage sun gear and a sixth-stage sun gear sequentially arranged along the axial direction; A third clutch assembly is provided between the second output gear ring and the hub shell; The shift adjustment assembly also includes a five-stage pawl matched with the five-stage sun gear and a six-stage pawl matched with the six-stage sun gear; When the gear is from the eighth gear to the tenth gear, the shift ring gear is engaged with the primary sun gear and then moves in a circumferential direction; In addition, in the eighth gear, the third-level pawl engages with the third-level sun gear, and the fifth-level pawl engages with the fifth-level sun gear; in the ninth gear, the third-level pawl engages with the third-level sun gear, and the sixth-level pawl engages with the sixth-level sun gear; in the tenth gear, the fourth-level pawl engages with the fourth-level sun gear, and the sixth-level pawl engages with the sixth-level sun gear.

[0008] Furthermore, the second clutch assembly includes a second clutch inner ring and a second clutch outer ring; the first output gear ring, the second clutch inner ring and the second planet carrier are integrally formed.

[0009] Furthermore, the first clutch assembly includes a first clutch inner ring and a first clutch outer ring, and the second clutch assembly includes a second clutch inner ring and a second clutch outer ring; the first clutch outer ring and the second clutch outer ring are integrally formed into an integrated outer ring, and the integrated outer ring is fixed to the inner wall of the hub shell.

[0010] Furthermore, an end portion of the second planet carrier extends to form a positioning support ring, and a sliding support member or a rolling support member is provided between the first planet carrier and the positioning support ring.

[0011] Furthermore, the shift adjustment assembly further comprises a shift sleeve rotatably sleeved on the central shaft, and the shift sleeve acts on the shift gear ring and the ratchet pawls at each level; The shift adjustment assembly also includes a drive ring that is circumferentially linked with the shift sleeve, and a shift motor that acts on the drive ring.

[0012] Furthermore, a sliding bearing or a rolling bearing is provided between the driving ring and the second planet carrier.

[0013] Furthermore, the speed-changing hub also includes a gear position detection component; the gear position detection component includes a magnetic ring arranged on the driving ring, and a Hall sensor cooperating with the magnetic ring.

[0014] Another object of the present invention is to provide a vehicle comprising the above-mentioned speed-changing hub.

[0015] In summary, the present invention has the following beneficial effects: 1. The first planetary gear assembly, the second planetary gear assembly and the shift adjustment assembly are arranged in the limited axial space of the hub shell, which not only realizes the speed adjustment of ten gears, but also realizes automatic shift adjustment through the shift motor, thereby optimizing the riding experience; 2. The first planetary gear assembly, the second planetary gear assembly and the shift adjustment assembly not only achieve functional superposition, but also achieve mutual coordination in structure, thereby simplifying the overall structure, optimizing the size and facilitating assembly; 3. Use a shift motor for automatic shift adjustment, and use a gear detection component to detect the gear status. The automatic adjustment is coordinated with the gear detection to ensure smooth gear adjustment and the accuracy of gear adjustment, thereby optimizing the riding experience. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 The structure of the speed hub in Example 1 is shown in FIG. Figure 1 ; Figure 2 The structure of the speed hub in Example 1 is shown in FIG. Figure 2 ; Figure 3 is a schematic structural diagram of the first planetary gear assembly and the second planetary gear assembly in Example 1; Figure 4 Schematic diagram of the structure of the input gear ring and the shift gear ring in Example 1; Figure 5 is a schematic structural diagram of the first planet carrier and the first clutch inner ring in Example 1; Figure 6 Schematic diagram of the structure of the second planet carrier, the first output gear ring and the second clutch inner ring in Example 1; Figure 7is a schematic structural diagram of the shift sleeve in Embodiment 1; Figure 8 This is a schematic diagram of the structure of the middle shaft and the pawls at various levels in Example 1; Fig. 9 is a schematic diagram of the structure of the driving ring in Example 1; Fig.10 This is a schematic diagram of the structure of the limiting ring in Example 1.

[0017] In the figure: 1, middle shaft; 2, hub shell; 3, input sleeve; 41, first-stage sun gear; 42, second-stage sun gear; 43, third-stage sun gear; 44, fourth-stage sun gear; 45, first planet carrier; 451, first planet shaft; 452, first clutch inner ring; 46, first double-coupled planet gear; 47, second double-coupled planet gear; 48, input ring gear; 49, integrated outer ring; 51, fifth-stage sun gear; 52, sixth-stage sun gear; 53, second planet carrier; 531, second planet shaft; 532, first output ring gear; 5 33. Second clutch inner ring; 534. Positioning support ring; 54. Third double planetary gear; 55. Second output ring gear; 61. Shift sleeve; 621. Primary pawl; 622. Secondary pawl; 623. Third pawl; 624. Fourth pawl; 625. Fifth pawl; 626. Sixth pawl; 63. Shift ring gear; 631. Limiting ring; 632. Spring; 64. Driving ring; 641. Driven gear; 65. Shift motor; 651. Driving gear; 661. Magnetic ring; 662. Hall sensor. DETAILED DESCRIPTION

[0018] The present invention is further described in detail below in conjunction with the accompanying drawings.

[0019] This specific embodiment is merely an explanation of the present invention and is not a limitation of the present invention. After reading this specification, those skilled in the art may make non-creative modifications to the present embodiment as needed. However, as long as they are within the scope of the claims of the present invention, they are protected by the patent law. Embodiment 1:

[0020] A speed hub, referring to Figures 1 to 10 , which includes a middle shaft 1, a hub shell 2, an input sleeve 3, a first planetary gear assembly, a second planetary gear assembly and a shift adjustment assembly; the hub shell 2 is rollingly supported on the middle shaft 1, and the first planetary gear assembly, the second planetary gear assembly and the shift adjustment assembly are all located in the hub shell 2; one end of the input sleeve 3 extends into the hub shell 2, and the other end extends out of the hub shell 2; when the speed-changing hub is installed on a vehicle, the middle shaft 1 is fixed, and the hub shell 2 is used to output torque and drive the wheels to rotate.

[0021] Reference Figure 1Specifically, a bearing is arranged between the input sleeve 3 and the middle shaft 1, and bearings are respectively arranged between the hub shell 2, the input sleeve 3 and the middle shaft 1; that is, one end of the hub shell 2 is rollingly supported on the middle shaft 1, and the other end is rollingly supported on the input sleeve 3.

[0022] Reference Figures 1 to 10 The first planetary gear assembly includes a first planet carrier 45, a first double-coupled planetary gear 46 and a second double-coupled planetary gear 47 respectively arranged on the first planet carrier 45, an input ring gear 48 meshing with the first double-coupled planetary gear 46, a first output ring gear 532 meshing with the second double-coupled planetary gear 47, and a first-stage sun gear 41, a second-stage sun gear 42, a third-stage sun gear 43 and a fourth-stage sun gear 44 arranged in sequence along the axial direction; specifically, a first planetary shaft 451 is provided on the first planet carrier 45, and a first planetary shaft 452 is provided on the second planetary shaft 453. A double-coupled planetary gear 46 and a second double-coupled planetary gear 47 are both sleeved on the first planetary shaft 451; the first double-coupled planetary gear 46 includes a primary planetary gear and a secondary planetary gear, the primary planetary gear is respectively meshed with the primary sun gear 41 and the input ring gear 48, and the secondary planetary gear is meshed with the secondary sun gear 42; the second double-coupled planetary gear 47 includes a third planetary gear and a fourth planetary gear, the third planetary gear is meshed with the third sun gear 43, and the fourth planetary gear is respectively meshed with the fourth sun gear 44 and the first output ring gear 532.

[0023] Reference Figures 1 to 10 Specifically, the end of the input gear ring 48 extends radially inward to form an input end plate, and an input ring is provided at the radial inner end of the input end plate; the input sleeve 3 and the input end plate are fixedly connected by fasteners, and the input sleeve 3 and the input gear ring 48 are linked in the circumferential direction; a first clutch assembly is provided between the first planetary carrier 45 and the hub shell 2, and a second clutch assembly is provided between the first output gear ring 532 and the hub shell 2; specifically, the first clutch assembly includes a first clutch inner ring 452 integrally formed on the outer side wall of the first planetary carrier 45, and a first clutch outer ring; the first clutch inner ring 452 is axially opposite to the third-stage planetary gear, that is, the first clutch inner ring 452 is located radially outside the third-stage planetary gear; the second clutch assembly includes an integrally formed The second clutch inner ring 533 and the second clutch outer ring are on the outer side wall of the first output gear ring 532; in this embodiment, the first clutch outer ring and the second clutch outer ring are integrally formed as an integrated outer ring 49, and the integrated outer ring 49 is fixed to the inner side wall of the hub shell 2; the integrated design between the first planetary carrier 45, the first clutch assembly, the first output gear ring 532 and the second clutch assembly is conducive to reducing the number of parts and assembly procedures, facilitating assembly and optimizing radial dimensions; in this embodiment, the first clutch assembly and the second clutch assembly are both ratchet pawl clutch assemblies, which have the advantages of high structural strength and good stability; of course, in other optional embodiments, the first clutch assembly and the second clutch assembly may also adopt other clutch assemblies, which are not limited here.

[0024] Reference Figures 1 to 10 , the second planetary gear assembly is connected to the end of the first planetary gear assembly, so that torque can be easily transmitted; based on the first planetary gear assembly, the second planetary gear assembly can increase the number of gears, thereby optimizing the riding experience; in order to further increase the number of gears, planetary gear assemblies can also be further added at the end of the second planetary gear assembly, which is not limited here; specifically, the second planetary gear assembly includes a second planet carrier 53 connected to the first output ring gear 532, a third double-coupled planetary gear 54 arranged on the second planet carrier 53, a second output ring gear 55 meshing with the third double-coupled planetary gear 54, and a five-stage sun gear 51 and a six-stage sun gear 52 arranged in sequence along the axial direction; specifically, the second planet carrier 53 is connected to the end of the first output ring gear 532, and the second planet carrier 53, the first output ring gear 532 and the second clutch inner ring 533 are integrally formed, thereby reducing the number of parts and assembly processes, and improving the stability of the transmission; in this embodiment, the second planetary gear assembly adopts a double-coupled planetary gear, thereby increasing the number of gears; in other optional embodiments, the second planetary gear assembly can also adopt a single planetary gear, which is not limited here.

[0025] Reference Figures 1 to 10 , the second planetary carrier 53 is connected to the first output ring gear 532 to achieve torque transmission between the first planetary gear assembly and the second planetary gear assembly; in this embodiment, the first output ring gear 532 is meshed with the four-stage planetary gear, which is also convenient for connecting the first output ring gear 532 with the second planetary carrier 53; if more planetary gear assemblies are added, the planetary carrier of the newly added planetary gear assembly is connected to the second output ring gear to achieve torque transmission.

[0026] Reference Figures 1 to 10 A second planetary shaft 531 is provided on the second planetary carrier 53, and the third double-coupled planetary gear 54 is sleeved on the second planetary shaft 531; the third double-coupled planetary gear 54 includes a five-stage planetary gear and a six-stage planetary gear, the five-stage planetary gear is meshed with the five-stage sun gear 51, and the six-stage planetary gear is meshed with the six-stage sun gear 52 and the second output ring gear 55 respectively; that is, the second output ring gear 55 is located at the end of the second planetary gear assembly; a third clutch assembly is provided between the second output ring gear 55 and the hub shell 2; specifically, in this embodiment, the second output ring gear 55 and the clutch inner ring of the third clutch assembly are integrally formed, thereby reducing the number of parts and assembly procedures, and facilitating assembly.

[0027] Reference Figures 1 to 10Specifically, in this embodiment, the first double-coupled planetary gear 46, the second double-coupled planetary gear 47 and the third double-coupled planetary gear 54 have the same size and shape, which can facilitate parts management and assembly, and effectively avoid misassembly, thereby improving production efficiency; the first-stage sun gear 41, the second-stage sun gear 42, the third-stage sun gear 43, the fourth-stage sun gear 44, the fifth-stage sun gear 51 and the sixth-stage sun gear 52 are arranged in sequence along the axial direction, and the first-stage sun gear 41 is close to the input sleeve 3.

[0028] Reference Figures 1 to 10 Specifically, the shift adjustment assembly in this embodiment includes a first-stage pawl 621, a second-stage pawl 622, a third-stage pawl 623, a fourth-stage pawl 624, a fifth-stage pawl 625 and a sixth-stage pawl 626 which are sequentially embedded in the middle shaft 1 along the axial direction; the first-stage to sixth-stage pawls are respectively matched with the first-stage to sixth-stage sun gears; the shift adjustment assembly also includes a shift gear ring 63, a limit ring 631, a spring 632, a shift sleeve 61, a drive ring 64 and a shift motor 65; the shift sleeve 61 is provided with release holes respectively matched with the pawls at each stage, and the pawls are released by rotating the shift sleeve 61. The claw pops out to release or is pressed to retract; the shift ring gear 63 is embedded in the inner wall of the input ring, and the shift ring gear 63 and the input ring are linked in the circumferential direction, and the shift ring gear 63 can move axially relative to the input ring; the shift ring gear 63 cooperates with the primary sun gear 41, that is, the shift ring gear 63 and the primary sun gear 41 include a separation state and a engagement state; the shift ring gear 63 can move axially to engage with the primary sun gear 41, thereby realizing the circumferential linkage between the two; the spring 632 and the limit ring 631 are used to control the movement of the shift ring gear 63, and this structure belongs to the prior art and will not be elaborated here.

[0029] Reference Figures 1 to 10 , the drive ring 64 is sleeved on the end of the shift sleeve 61, and the drive ring 64 and the shift sleeve 61 are linked in the circumferential direction; that is, the drive ring 64 can drive the shift sleeve 61 to rotate, thereby performing gear shifting adjustment; the shift motor 65 is fixedly sleeved on the central shaft 1, and the shift motor 65 is used to control the drive ring 64 to rotate; specifically, the shift motor 65 is provided with a driving gear 651, and the drive ring 64 is provided with a driven gear 641 meshing with the driving gear 651; then, the shift motor 65 controls the rotation of the shift sleeve 61 through the gear assembly and the drive ring 64 to realize automatic gear shifting adjustment.

[0030] Reference Figures 1 to 10Preferably, the speed hub also includes a gear detection component; the gear detection component includes a magnetic ring 661 embedded in the end of the drive ring 64, and a Hall sensor 662 cooperating with the magnetic ring 661; the Hall sensor 662 is fixed on the gear shift motor 65, specifically a Hall sensor; that is, by detecting the rotation angle of the magnetic ring 661 through the Hall sensor 662, the rotation angle of the shift sleeve 61 can be obtained, so that the state between the shift sleeve 61 and the pawls at each level can be fed back, and then the gear can be determined; in this embodiment, the shift motor 65 is used for automatic gear shift adjustment, and the gear detection component is used to detect the gear state, then the automatic adjustment is coordinated with the gear detection, which can ensure the smooth adjustment of the gear, and can also ensure the accuracy of the gear adjustment, thereby optimizing the riding experience.

[0031] Reference Figures 1 to 10 In this embodiment, one end of the first planet carrier 45 is supported on the input ring, and the other end is supported on the second planet carrier 53; specifically, the end of the second planet carrier 53 extends to form a positioning support ring 534; sliding friction support members are respectively provided between the first planet carrier 45 and the input ring and the positioning support ring 534, thereby improving the stability of the first planet carrier 45 and optimizing the axial size and radial size; one end of the second planet carrier 53 is supported on the shift sleeve 61 through a sliding ring, and the other end is supported on the drive ring 64 through a sliding friction support member, thereby improving the stability of the second planet carrier 53 and optimizing the axial size and radial size. And it can optimize the axial size and radial size; wherein, the sliding ring is located between the fourth-stage sun gear 44 and the fifth-stage sun gear 51; in other optional embodiments, the sliding friction support can also be replaced by a rolling support, such as a ball; for example, a plurality of balls arranged along the circumferential direction are embedded in the first planetary carrier, and the balls are in contact with the second planetary carrier 53, thereby realizing rolling support; in this embodiment, between the first planetary gear assembly and the second planetary gear assembly, not only torque transmission is formed, but also positioning support is formed, thereby realizing multi-level coordination of the two planetary gear assemblies, thereby being able to increase the number of gears in a limited axial space.

[0032] In this embodiment, the first planetary gear assembly and the second planetary gear assembly cooperate with each other and use three double-linked planetary gears to achieve speed adjustment of ten gears. In addition, the axial size is small, which is convenient for arrangement in the hub shell.

[0033] Here’s how it works: In the first gear, the primary pawl 621 bounces up to engage with the primary sun gear 41, so that the primary sun gear 41 is fixed; at this time, the shift ring gear 63 is separated from the primary sun gear 41, and the other pawls of each level are in a retracted state.

[0034] The torque transmission path of the first gear is: input sleeve 3, input ring gear 48, first double planetary gear 46, first planetary carrier 45, first clutch assembly to hub shell 2; wherein, the rotation speed of hub shell 2 is lower than the rotation speed of input sleeve 3, so the first gear is a speed reduction transmission.

[0035] In the second gear, the secondary pawl 622 bounces up to engage with the secondary sun gear 42, so that the secondary sun gear 42 is fixed; at this time, the shift ring gear 63 is separated from the primary sun gear 41, and the remaining pawls of each level are in a retracted state.

[0036] The second gear torque transmission path is: input sleeve 3, input ring gear 48, first double planetary gear 46, first planetary carrier 45, first clutch assembly to hub shell 2; wherein, the rotation speed of hub shell 2 is lower than the rotation speed of input sleeve 3, so the second gear is a speed reduction transmission.

[0037] In the third gear, the third-stage pawl 623 pops up to engage with the third-stage sun gear 43, so that the third-stage sun gear 43 is fixed; and the first-stage pawl 621 pops up to engage with the first-stage sun gear 41, so that the first-stage sun gear 41 is fixed; at this time, the shift ring gear 63 is separated from the first-stage sun gear 41, and the remaining pawls of each stage are in a retracted state.

[0038] The third gear torque transmission path is: input sleeve 3, input ring gear 48, first duplex planetary gear 46 to first planetary carrier 45, first planetary carrier 45, second duplex planetary gear 47, first output ring gear 532, second clutch assembly to hub shell 2; the rotation speed of hub shell 2 is greater than the rotation speed of first planetary carrier 45, and the first clutch assembly is in an overrunning state; wherein, the rotation speed of hub shell 2 is less than the rotation speed of input sleeve 3, so the third gear is a downshift transmission.

[0039] In the fourth gear, the fourth-level pawl 624 pops up to engage with the fourth-level sun gear 44, so that the fourth-level sun gear 44 is fixed; and the first-level pawl 621 pops up to engage with the first-level sun gear 41, so that the first-level sun gear 41 is fixed; at this time, the shift ring gear 63 is separated from the first-level sun gear 41, and the remaining levels of pawls are in a retracted state.

[0040] The fourth gear torque transmission path is: input sleeve 3, input ring gear 48, first duplex planetary gear 46 to first planetary carrier 45, first planetary carrier 45, second duplex planetary gear 47, first output ring gear 532, second clutch assembly to hub shell 2; the rotation speed of hub shell 2 is greater than the rotation speed of first planetary carrier 45, and the first clutch assembly is in an overrunning state; wherein, the rotation speed of hub shell 2 is less than the rotation speed of input sleeve 3, so the fourth gear is a speed reduction transmission.

[0041] In the fifth gear, the fifth-level pawl 625 pops up to engage with the fifth-level sun gear 51, so that the fifth-level sun gear 51 is fixed; and the secondary pawl 622 pops up to engage with the secondary sun gear 42, so that the secondary sun gear 42 is fixed; at this time, the shift ring gear 63 is separated from the primary sun gear 41, and the remaining levels of pawls are in a retracted state.

[0042] The fifth gear torque transmission path is: input sleeve 3, input ring gear 48, first double planetary gear 46 to first planetary carrier 45, first planetary carrier 45, second double planetary gear 47, first output ring gear 532, second clutch assembly to hub shell 2; the rotation speed of hub shell 2 is greater than the rotation speed of first planetary carrier 45, and the first clutch assembly is in an overtaking state; wherein, the rotation speed of hub shell 2 is greater than the rotation speed of input sleeve 3, so the fifth gear is an up-speed transmission.

[0043] In the sixth gear, the third-stage pawl 623 bounces up and engages with the third-stage sun gear 43, so that the third-stage sun gear 43 is fixed; and the shift ring gear 63 engages with the first-stage sun gear 41 and then moves in a circumferential direction; at this time, the remaining stages of the pawls are in a retracted state.

[0044] The torque transmission path of the sixth gear is: input sleeve 3, input ring gear 48 to the first planetary carrier 45, first planetary carrier 45, second double planetary gear 47, first output ring gear 532, second clutch assembly to hub shell 2; the rotation speed of hub shell 2 is greater than the rotation speed of first planetary carrier 45, and the first clutch assembly is in an overtaking state; wherein, the rotation speed of hub shell 2 is greater than the rotation speed of input sleeve 3, so the sixth gear is an up-speed transmission.

[0045] In the seventh gear, the fourth-stage pawl 624 bounces up and engages with the fourth-stage sun gear 44, so that the fourth-stage sun gear 44 is fixed; and the shift ring gear 63 engages with the first-stage sun gear 41 and then moves in a circumferential direction; at this time, the remaining stages of the pawls are in a retracted state.

[0046] The seventh gear torque transmission path is: input sleeve 3, input ring gear 48 to first planetary carrier 45, first planetary carrier 45, second double planetary gear 47, first output ring gear 532, second clutch assembly to hub shell 2; the rotation speed of hub shell 2 is greater than the rotation speed of first planetary carrier 45, and the first clutch assembly is in overtaking state; wherein, the rotation speed of hub shell 2 is greater than the rotation speed of input sleeve 3, so the seventh gear is a speed-up transmission.

[0047] In the eighth gear, the fifth-stage pawl 625 pops up to engage with the fifth-stage sun gear 51, so that the fifth-stage sun gear 51 is fixed; the third-stage pawl 623 pops up to engage with the third-stage sun gear 43, so that the third-stage sun gear 43 is fixed; and the shift ring gear 63 engages with the first-stage sun gear 41 and then moves in a circumferential direction; at this time, the remaining stages of the pawls are in a retracted state.

[0048] The eighth-gear torque transmission path is: input sleeve 3, input ring gear 48 to first planetary carrier 45, first planetary carrier 45, second double-coupled planetary gear 47 to first output ring gear 532, first output ring gear 532, second planetary carrier 53, third double-coupled planetary gear 54, second output ring gear 55, third clutch assembly to hub shell 2; the rotation speed of hub shell 2 is greater than the rotation speed of first planetary carrier 45 and first output ring gear 532, and first clutch assembly and second clutch assembly are both in overrunning state; wherein, the rotation speed of hub shell 2 is greater than the rotation speed of input sleeve 3, so the eighth gear is a speed-up transmission.

[0049] In the ninth gear, the sixth-stage pawl 626 pops up to engage with the sixth-stage sun gear 52, so that the sixth-stage sun gear 52 is fixed; the third-stage pawl 623 pops up to engage with the third-stage sun gear 43, so that the third-stage sun gear 43 is fixed; and the shift ring gear 63 engages with the first-stage sun gear 41 and then moves in a circumferential direction; at this time, the pawls of the remaining stages are all in a retracted state.

[0050] The torque transmission path of the ninth gear is: input sleeve 3, input ring gear 48 to first planetary carrier 45, first planetary carrier 45, second double planetary gear 47 to first output ring gear 532, first output ring gear 532, second planetary carrier 53, third double planetary gear 54, second output ring gear 55, third clutch assembly to hub shell 2; the rotation speed of hub shell 2 is greater than the rotation speed of first planetary carrier 45 and first output ring gear 532, and the first clutch assembly and the second clutch assembly are both in overrunning state; among them, the rotation speed of hub shell 2 is greater than the rotation speed of input sleeve 3, so the ninth gear is a speed-up transmission.

[0051] In the tenth gear, the sixth-stage pawl 626 pops up to engage with the sixth-stage sun gear 52, so that the sixth-stage sun gear 52 is fixed; the fourth-stage pawl 624 pops up to engage with the fourth-stage sun gear 44, so that the fourth-stage sun gear 44 is fixed; and the shift ring gear 63 engages with the first-stage sun gear 41 and then moves in a circumferential direction; at this time, the pawls of the remaining stages are all in a retracted state.

[0052] The torque transmission path of the tenth gear is: input sleeve 3, input ring gear 48 to first planetary carrier 45, first planetary carrier 45, second double planetary gear 47 to first output ring gear 532, first output ring gear 532, second planetary carrier 53, third double planetary gear 54, second output ring gear 55, third clutch assembly to hub shell 2; the rotation speed of hub shell 2 is greater than the rotation speed of first planetary carrier 45 and first output ring gear 532, and the first clutch assembly and the second clutch assembly are both in overrunning state; wherein, the rotation speed of hub shell 2 is greater than the rotation speed of input sleeve 3, so the tenth gear is a speed-up transmission.

[0053] In this embodiment, the first planetary gear assembly, the second planetary gear assembly and the shift adjustment assembly are respectively arranged in the limited axial space in the hub shell 2, which not only realizes the speed adjustment of ten gears, but also can realize automatic shift adjustment through the shift motor, thereby optimizing the riding experience.

[0054] In this embodiment, the first to fourth gears are downshifting transmission, and the fifth to tenth gears are upshifting transmission, which makes it convenient to start while riding and optimizes the riding experience; in other optional embodiments, the transmission ratio of each gear can be adjusted as needed, which is not limited here; in addition, the structure can also increase the number of gears by continuing to add planetary gear assemblies, thereby reducing the difficulty of technical improvements and reducing improvement costs.

[0055] In this embodiment, the first planetary gear assembly, the second planetary gear assembly and the shift adjustment assembly are not only superimposed in function, but also coordinated in structure, thereby simplifying the overall structure, optimizing the size and facilitating assembly. Embodiment 2:

[0056] A vehicle, see Figures 1 to 10 , which includes the above-mentioned speed-changing hub; the vehicle is a riding vehicle, including a bicycle, a power-assisted bicycle, an electric motorcycle, a tricycle, etc.

Claims

1. A speed-changing hub, characterized in that: It includes a middle shaft, a hub shell, an input sleeve, a first planetary gear assembly and a shift adjustment assembly; The first planetary gear assembly comprises a first planet carrier, a first double-coupled planetary gear and a second double-coupled planetary gear respectively arranged on the first planet carrier, an input ring gear meshed with the first double-coupled planetary gear, a first output ring gear meshed with the second double-coupled planetary gear, and a primary sun gear, a secondary sun gear, a third sun gear and a fourth sun gear sequentially arranged along the axial direction; The input gear ring and the input sleeve are linked in the circumferential direction, a first clutch assembly is arranged between the first planet carrier and the hub shell, and a second clutch assembly is arranged between the first output gear ring and the hub shell; The shift adjustment assembly includes a primary pawl and a shift ring gear matched with the primary sun gear, a secondary pawl matched with the secondary sun gear, a third pawl matched with the third sun gear, and a fourth pawl matched with the fourth sun gear; wherein the shift ring gear is linked with the input ring gear in the circumferential direction; In the first to fifth gears, the shift gear ring is separated from the primary sun gear; in the sixth to seventh gears, the shift gear ring is engaged with the primary sun gear and then moves in a circumferential direction; In addition, in the first gear, the first-level pawl engages with the first-level sun gear; in the second gear, the second-level pawl engages with the second-level sun gear; in the third gear, the first-level pawl engages with the first-level sun gear, and the third-level pawl engages with the third-level sun gear; in the fourth gear, the first-level pawl engages with the first-level sun gear, and the fourth-level pawl engages with the fourth-level sun gear; in the fifth gear, the second-level pawl engages with the second-level sun gear, and the fourth-level pawl engages with the fourth-level sun gear; in the sixth gear, the third-level pawl engages with the third-level sun gear; in the seventh gear, the fourth-level pawl engages with the fourth-level sun gear.

2. The speed-changing hub according to claim 1, characterized in that: The speed-changing hub also includes one or more planetary gear assemblies connected to the first planetary gear assembly.

3. The speed-changing hub according to claim 1, characterized in that: The speed-changing hub also includes a second planetary gear assembly disposed at the end of the first planetary gear assembly; The second planetary gear assembly includes a second planet carrier connected to the first output ring gear, a third double-coupled planetary gear disposed on the second planet carrier, a second output ring gear meshing with the third double-coupled planetary gear, and a fifth-stage sun gear and a sixth-stage sun gear sequentially arranged along the axial direction; A third clutch assembly is provided between the second output gear ring and the hub shell; The shift adjustment assembly also includes a five-stage pawl matched with the five-stage sun gear and a six-stage pawl matched with the six-stage sun gear; When the gear is from the eighth gear to the tenth gear, the shift ring gear is engaged with the primary sun gear and then moves in a circumferential direction; In addition, in the eighth gear, the third-level pawl engages with the third-level sun gear, and the fifth-level pawl engages with the fifth-level sun gear; in the ninth gear, the third-level pawl engages with the third-level sun gear, and the sixth-level pawl engages with the sixth-level sun gear; in the tenth gear, the fourth-level pawl engages with the fourth-level sun gear, and the sixth-level pawl engages with the sixth-level sun gear.

4. The speed-changing hub according to claim 3, characterized in that: The second clutch assembly includes a second clutch inner ring and a second clutch outer ring; the first output gear ring, the second clutch inner ring and the second planet carrier are integrally formed.

5. The speed-changing hub according to claim 1, characterized in that: The first clutch assembly includes a first clutch inner ring and a first clutch outer ring, and the second clutch assembly includes a second clutch inner ring and a second clutch outer ring; the first clutch outer ring and the second clutch outer ring are integrally formed into an integrated outer ring, and the integrated outer ring is fixed to the inner side wall of the hub shell.

6. The speed-changing hub according to claim 3, characterized in that: The end of the second planet carrier extends to form a positioning support ring, and a sliding support member or a rolling support member is arranged between the first planet carrier and the positioning support ring.

7. The speed-changing hub according to claim 3, characterized in that: The shift adjustment assembly also includes a shift sleeve rotatably sleeved on the central shaft, and the shift sleeve acts on the shift gear ring and various levels of ratchet; The shift adjustment assembly also includes a drive ring that is circumferentially linked with the shift sleeve, and a shift motor that acts on the drive ring.

8. The speed-changing hub according to claim 7, characterized in that: A sliding bearing or a rolling bearing is arranged between the drive ring and the second planet carrier.

9. The speed-changing hub according to claim 7, characterized in that: The speed-changing hub also includes a gear position detection component; the gear position detection component includes a magnetic ring arranged on a driving ring, and a Hall sensor matched with the magnetic ring.

10. A vehicle, characterized in that: A speed-changing hub comprising the speed-changing hub described in any one of claims 1 to 9.

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