Multi-stage speed ratio adjustable planetary reducer

Abstract

The application relates to a multi-stage speed ratio adjustable planetary reducer, which comprises a box body, an input end shaft sleeve, multiple groups of planetary transmission groups and an output shaft arranged along a central axis in sequence, wherein the planetary transmission group comprises a sun gear, a planet wheel, a planet carrier, a gear ring I, a gear ring II and a sliding sleeve, the sliding sleeve is provided with inner spline teeth and outer spline teeth, the sun gear is connected with a connecting sleeve I, the output end of the planet carrier is provided with first outer teeth, the connecting sleeve I is provided with outer teeth I, the sun gear is connected with a connecting sleeve II, the planet carrier is provided with second outer teeth, the connecting sleeve II is provided with outer teeth II, a combination sleeve is further arranged between the connecting sleeve I and the connecting sleeve II, the combination sleeve is provided with connecting outer teeth, the two ends of the combination sleeve are further slidably sleeved with a regulating sleeve I and a regulating sleeve II, the regulating sleeve I is provided with inner teeth I and inner teeth II, and the regulating sleeve II is provided with inner teeth III and inner teeth IV. The multi-stage speed ratio adjustable planetary reducer is more compact in structure and shorter in axial length.

Description

Technical Field

[0001] This application relates to the field of planetary reducer technology, and in particular to a multi-stage adjustable planetary reducer. Background Technology

[0002] A planetary reducer is a power transmission mechanism based on involute planetary gear transmission technology. It achieves speed reduction by having multiple planetary gears rotate around the sun gear. It features light weight, small size, and a wide transmission ratio range (25-4000r / min).

[0003] In the field of planetary gear reducers, increasing the number of reduction stages is a design method that expands the speed ratio range of a transmission system by connecting multiple gears in series. Its core principle is to distribute the total speed ratio across each gear stage, thereby achieving extreme speed reduction or torque amplification effects that a single stage cannot achieve. This type of planetary gear reducer is particularly suitable for scenarios requiring significant speed reduction or torque increase, such as heavy mining equipment, large rolling mills, cranes, or gantry crane sleepers. When adjusting the speed ratio in common multi-stage planetary gear reducers, a shift fork is typically needed to drive the sliding combination sleeve, thereby achieving the engagement and disengagement of different planetary gear sets.

[0004] Regarding the aforementioned technologies, the following drawbacks are considered:

[0005] In common multi-stage planetary reducers, the speed ratio is switched by sliding the combination sleeve. The combination sleeve can only fully engage with the next stage connection sleeve gear when it is completely disengaged from the previous stage connection sleeve gear. Therefore, at least 150-200mm of additional sliding space needs to be reserved for the combination sleeve. This will significantly extend the axial length of the entire reducer, resulting in a larger volume and axial length of the planetary reducer, making it unsuitable for some narrow installation positions. Summary of the Invention

[0006] This application provides a multi-stage adjustable planetary reducer to improve the following technical problems:

[0007] Common multi-stage planetary reducers require at least 150-200mm of additional sliding space for the combination sleeve, which significantly extends the axial length of the entire reducer, resulting in a larger volume and axial length, making it unsuitable for some narrow installation positions.

[0008] This application provides a multi-stage adjustable speed ratio planetary reducer, which adopts the following technical solution:

[0009] A multi-stage adjustable planetary reducer includes a housing and an input end bushing, multiple planetary transmission groups, and an output shaft arranged sequentially along a central axis. The input end bushing and the output shaft are respectively mounted on opposite outer ends of the housing, and the planetary transmission groups are mounted inside the housing. The reducer is characterized by:

[0010] The planetary transmission assembly includes a sun gear, planet gears, a planet carrier, a first gear ring, a second gear ring, and a clearance sleeve. The input end sleeve is fixedly connected to the input end of the nearest sun gear, and the output shaft is fixedly connected to the output end of the nearest planet carrier. The sun gear and the planet gears mesh and drive each other, and the planet gears and the planet carrier drive each other to achieve a speed reduction effect. The planet gears mesh with the internal teeth of the first gear ring. The clearance sleeve has internal splines and external splines and can slide along the central axis. The internal splines of the clearance sleeve mesh with the external teeth of the first gear ring, and the external splines of the clearance sleeve mesh with the internal teeth of the second gear ring. The second gear ring is fixed to the inner peripheral wall of the housing.

[0011] The output end of the sun gear, which is not connected to the output shaft, is fixedly connected to a first sleeve. The output end of the planet carrier, which is adjacent to the first sleeve, is provided with a first external tooth. The outer peripheral wall of the first sleeve is provided with an external tooth. The input end of the sun gear, which is not connected to the input end sleeve, is fixedly connected to a second sleeve. The input end of the planet carrier, which is adjacent to the second sleeve, is provided with a second external tooth. The outer peripheral wall of the second sleeve is provided with an external tooth.

[0012] A combined sleeve that can rotate freely but cannot be directly transmitted is also provided between the first and second connecting sleeves. The outer peripheral wall of the combined sleeve is provided with connecting external teeth. The first external tooth, the first external tooth, the connecting external tooth, the second external tooth, and the third external tooth are all located on the same circumferential surface. The two ends of the combined sleeve are also slidably fitted with the first adjusting sleeve and the second adjusting sleeve along the central axis. The inner peripheral wall of the first adjusting sleeve is provided with the first internal tooth that meshes with the first external tooth or the first external tooth, and the second internal tooth that meshes with the connecting external tooth. An annular groove 1 is reserved between the first internal tooth and the second internal tooth to avoid the first external tooth. The inner peripheral wall of the second adjusting sleeve is provided with the third internal tooth that meshes with the second external tooth or the second external tooth, and the fourth internal tooth that meshes with the connecting external tooth. An annular groove 2 is reserved between the third internal tooth and the fourth internal tooth to avoid the second external tooth.

[0013] After the external spline teeth are completely disengaged from the internal teeth of the gear ring two, the planetary carrier is in an unlocked state, that is, the planetary carrier has a clearance space to rotate a certain angle along the central axis. When the adjusting sleeve one slides under external force, the internal tooth one can simultaneously engage with the first external tooth and the external tooth one. When the adjusting sleeve two slides under external force, the internal tooth three can simultaneously engage with the second external tooth and the external tooth two.

[0014] In one feasible technical solution of this application, an annular fork groove is provided on the outer peripheral wall of the clearance sleeve, and a fork hole is provided on the housing corresponding to the annular fork groove. An external fork can be inserted into the annular fork groove through the fork hole to drive the clearance sleeve to slide axially and unlock the locking state of the planetary carrier.

[0015] In one feasible technical solution of this application, an annular shift fork groove 2 is provided on the outer peripheral wall of the adjusting sleeve 1, and a shift fork hole 2 is provided on the housing corresponding to the annular shift fork groove 2. An external shift fork can be inserted into the annular shift fork groove 2 through the shift fork hole 2 to drive the adjusting sleeve 1 to slide axially and change the speed ratio.

[0016] In one feasible technical solution of this application, an annular shift fork groove three is provided on the outer peripheral wall of the adjusting sleeve two, and a shift fork hole three is provided on the housing corresponding to the annular shift fork groove three. An external shift fork can be inserted into the annular shift fork groove three through the shift fork hole three to drive the adjusting sleeve two to slide axially and change the speed ratio.

[0017] In one feasible technical solution of this application, an inner bearing is provided between the inner peripheral wall of the combined sleeve and the outer peripheral wall of the connecting sleeve one, a bearing cap is provided at the end of the connecting sleeve one, an inner bearing is provided between the inner peripheral wall of the combined sleeve and the outer peripheral wall of the connecting sleeve two, a bearing cap is provided at the end of the connecting sleeve two, and the bearing cap one and the bearing cap two are in contact with each other.

[0018] In one feasible technical solution of this application, the housing includes a main shell, an end cover one, and an end cover two. The main shell is a cylindrical structure. The end cover one is sealed and installed at the input end of the main shell, and the end cover two is sealed and installed at the output end of the main shell.

[0019] In one feasible technical solution of this application, multiple sets of parallel-arranged outer bearings are provided between the input end bushing and the end cover one, and the end cover one is also provided with a sealing cover one; multiple sets of parallel-arranged outer bearings are provided between the output shaft and the end cover two, and the end cover two is also provided with a sealing cover two.

[0020] In one feasible technical solution of this application, a middle bearing is provided between the outer peripheral wall of the end of the gear ring one and the inner peripheral wall of the housing, and the two middle bearings respectively abut against the two ends of the gear ring two.

[0021] In one feasible technical solution of this application, the gap width between the two ends of the first external tooth and the first external tooth and the connecting external tooth is between 1 and 3 mm, and the gap width between the two ends of the second external tooth and the second external tooth and the connecting external tooth is between 1 and 3 mm.

[0022] In one feasible technical solution of this application, the planetary transmission group has two groups, and the speed ratio value of a single planetary transmission group is A. The value of A is between 3 and 5. The multi-stage adjustable speed ratio planetary reducer can switch between three working modes: speed ratio 1, speed ratio A, and speed ratio A².

[0023] In summary, this application includes at least one of the following beneficial technical effects:

[0024] By driving the adjusting sleeves one and two to slide with external force, the internal gear one can engage with the first external gear or with the external gear one, and the internal gear three can engage with the second external gear or with the external gear two, thereby adjusting the speed ratio of the entire reducer. Furthermore, during the speed ratio adjustment process, the clearance sleeve can be driven to slide first, so that the external spline teeth completely disengage from the internal teeth of the gear ring two, allowing the planetary carrier to switch to the unlocked state. This means the planetary carrier has clearance space to rotate a certain angle along the central axis. By slightly shaking the planetary carrier, the adjustment sleeve one can be ensured to remain in its unlocked state. During the sliding process, the first internal tooth can simultaneously mesh with the first external tooth and the first external tooth. During the sliding process, the second internal tooth can simultaneously mesh with the second external tooth and the second external tooth. After the speed ratio is adjusted, the external force drives the clearance sleeve to reset, that is, the external spline teeth and the internal teeth of the gear ring 2 are fully meshed. The reducer does not need to reserve an additional sliding space of 150-200mm, which will greatly shorten the axial length of the entire reducer, making the planetary reducer smaller in size and axial length, and suitable for some narrow installation positions. Attached Figure Description

[0025] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0026] Figure 1 This is a schematic diagram of the structure of a multi-stage adjustable planetary reducer according to an embodiment of this application, wherein the speed ratio is in the minimum state.

[0027] Figure 2This is a schematic diagram of the structure of a multi-stage adjustable planetary reducer according to an embodiment of this application, wherein the speed ratio is in a medium state.

[0028] Figure 3 This is a schematic diagram of the structure of a multi-stage adjustable planetary reducer according to an embodiment of this application, wherein the speed ratio is at its maximum.

[0029] Figure 4 This is a cross-sectional structural diagram of the clearance sleeve in the embodiments of this application.

[0030] Figure 5 This is a cross-sectional structural diagram of the first sleeve in the embodiment of this application.

[0031] Figure 6 This is a cross-sectional view of the second sleeve in the embodiment of this application.

[0032] Explanation of reference numerals in the attached figures:

[0033] 1. Box body; 11. Main shell; 12. End cover one; 13. End cover two;

[0034] 2. Input end bushing;

[0035] 3. Planetary transmission assembly; 31. Sun gear; 32. Planet gears; 33. Planet carrier; 331. First external gear; 332. Second external gear; 34. Gear ring one; 35. Gear ring two; 36. Clearance sleeve; 361. Internal spline; 362. External spline; 363. Annular shift fork groove one;

[0036] 4. Output shaft;

[0037] 5. Connecting sleeve one; 51. External gear one;

[0038] 6. Connecting sleeve two; 61. External gear two;

[0039] 7. Combination sleeve; 71. Connecting external teeth;

[0040] 8. Adjusting sleeve one; 81. Internal gear one; 82. Internal gear two; 83. Annular groove one; 84. Annular shift fork groove two;

[0041] 9. Adjusting sleeve two; 91. Internal gear three; 92. Internal gear four; 93. Annular groove two; 94. Annular shift fork groove three;

[0042] 10. Inner bearing 1; 20. Bearing cover 1; 30. Inner bearing 2; 40. Bearing cover 2; 50. Outer bearing 1; 60. Cover 1; 70. Outer bearing 2; 80. Cover 2; 90. Middle bearing. Detailed Implementation

[0043] To make the technical problems, technical solutions, and beneficial effects to be solved by this application clearer, the following detailed description is provided in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and are not intended to limit the scope of this application.

[0044] It should be noted that when a component is referred to as being "fixed to" or "set on" another component, it can be directly on or indirectly on that other component. When a component is referred to as being "connected to" another component, it can be directly connected to or indirectly connected to that other component.

[0045] It should be understood that the terms "length", "width", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this application.

[0046] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0047] The following is in conjunction with the appendix Figure 1-6 This application will be described in further detail.

[0048] This application discloses a multi-stage adjustable speed ratio planetary reducer. (Refer to...) Figure 1-6 The multi-stage adjustable speed ratio planetary reducer includes a housing 1 and an input end bushing 2, multiple planetary transmission groups 3 and an output shaft 4 arranged sequentially along the central axis. The input end bushing 2 and the output shaft 4 are respectively installed at the opposite outer ends of the housing 1, and the planetary transmission groups 3 are installed inside the housing 1. It is suitable for scenarios that require a significant reduction in speed or a significant increase in torque, such as heavy mining equipment, large rolling mills, cranes or gantry rails.

[0049] The planetary transmission assembly 3 includes a sun gear 31, planet gears 32, a planet carrier 33, a first gear ring 34, a second gear ring 35, and a clearance sleeve 36. The input end sleeve 2 is fixedly connected to the input end of the nearest sun gear 31, and the output shaft 4 is fixedly connected to the output end of the nearest planet carrier 33. The sun gear 31 and planet gears 32 mesh and drive each other, and the planet gears 32 and planet carrier 33 drive each other to achieve a speed reduction effect. The planet gears 32 mesh with the internal teeth of the first gear ring 34. The clearance sleeve 36 has internal spline teeth 361 and external spline teeth 362 and can slide along the central axis. The internal spline teeth 361 of the clearance sleeve 36 mesh with the external teeth of the first gear ring 34, and the external spline teeth 362 of the clearance sleeve 36 mesh with the internal teeth of the second gear ring 35. The second gear ring 35 is fixed on the inner peripheral wall of the housing 1.

[0050] The output end of the sun gear 31, which is not connected to the output shaft 4, is fixedly connected to a first sleeve 5. The output end of the planet carrier 33 adjacent to the first sleeve 5 is provided with a first external tooth 331. The outer peripheral wall of the first sleeve 5 is provided with an external tooth 51. The input end of the sun gear 31, which is not connected to the input end sleeve 2, is fixedly connected to a second sleeve 6. The input end of the planet carrier 33 adjacent to the second sleeve 6 is provided with a second external tooth 332. The outer peripheral wall of the second sleeve 6 is provided with an external tooth 61.

[0051] Between connecting sleeve 1 (5) and connecting sleeve 2 (6), there is also a combined sleeve 7 that can rotate freely but cannot be directly transmitted. The outer peripheral wall of the combined sleeve 7 is provided with connecting external teeth 71. The first external tooth 331, external tooth 1 (51), connecting external tooth 71, external tooth 2 (61), and second external tooth 332 are all located on the same circumferential surface. At both ends of the combined sleeve 7, adjusting sleeve 1 (8) and adjusting sleeve 2 (9) are slidably fitted along the central axis. The inner peripheral wall of adjusting sleeve 1 (8) is provided with a tooth that interacts with the first external tooth 331 or external tooth 2 (61). 51 has an internal tooth 81 for meshing transmission and an internal tooth 82 for meshing transmission with the connecting external tooth 71. An annular groove 83 is reserved between the internal tooth 81 and the internal tooth 82 to avoid the external tooth 51. The inner peripheral wall of the adjusting sleeve 9 has an internal tooth 91 for meshing transmission with the second external tooth 332 or the external tooth 61 and an internal tooth 92 for meshing transmission with the connecting external tooth 71. An annular groove 93 is reserved between the internal tooth 91 and the internal tooth 92 to avoid the external tooth 61.

[0052] After the external spline tooth 362 is completely disengaged from the internal tooth of the gear ring 35, the planetary carrier 33 is in the unlocked state, that is, the planetary carrier 33 has a clearance space to rotate a certain angle along the central axis. When the adjusting sleeve 8 slides under external force, the internal tooth 81 can simultaneously engage with the first external tooth 331 and the external tooth 51. When the adjusting sleeve 9 slides under external force, the internal tooth 91 can simultaneously engage with the second external tooth 332 and the external tooth 61.

[0053] The gap width between the two ends of external tooth 51 and the first external tooth 331 and the connecting external tooth 71 is between 1 and 3 mm. The gap width between the two ends of external tooth 61 and the second external tooth 332 and the connecting external tooth 71 is between 1 and 3 mm. The planetary transmission group 3 has two groups, and the speed ratio value of a single planetary transmission group 3 is A. The value of A is between 3 and 5. This multi-stage adjustable speed ratio planetary reducer can switch between three working modes: speed ratio value 1, speed ratio value A, and speed ratio value A². In this embodiment, the value of A is specifically 3.2. The value of A can be changed by adjusting the gear ratio of each group in the planetary transmission group 3.

[0054] To facilitate the sliding of the clearance sleeve 36 along the central axis by external force, an annular fork groove 363 is provided on the outer peripheral wall of the clearance sleeve 36. A fork hole corresponding to the annular fork groove 363 is provided on the housing 1. An external fork can be inserted into the annular fork groove 363 through the fork hole to drive the clearance sleeve 36 to slide axially and unlock the locking state of the planetary carrier 33.

[0055] To facilitate the sliding of the adjusting sleeve 8 along the central axis by external force, an annular shift fork groove 84 is provided on the outer peripheral wall of the adjusting sleeve 8, and a shift fork hole 2 is provided on the housing 1 corresponding to the annular shift fork groove 84. The external shift fork can be inserted into the annular shift fork groove 84 through the shift fork hole 2 to drive the adjusting sleeve 8 to slide axially and change the speed ratio.

[0056] To facilitate the sliding of the adjusting sleeve 2 9 along the central axis by external force, an annular shift fork groove 3 94 is provided on the outer peripheral wall of the adjusting sleeve 2 9, and a shift fork hole 3 is provided on the housing 1 corresponding to the annular shift fork groove 3 94. The external shift fork can be inserted into the annular shift fork groove 3 94 through the shift fork hole 3 to drive the adjusting sleeve 2 9 to slide axially and change the speed ratio.

[0057] To ensure that the combined sleeve 7 can rotate smoothly along the central axis, an inner bearing 10 is provided between the inner peripheral wall of the combined sleeve 7 and the outer peripheral wall of the connecting sleeve 5, a bearing cap 20 is provided at the end of the connecting sleeve 5, an inner bearing 30 is provided between the inner peripheral wall of the combined sleeve 7 and the outer peripheral wall of the connecting sleeve 6, and a bearing cap 40 is provided at the end of the connecting sleeve 6. The bearing cap 20 and the bearing cap 40 fit together.

[0058] To facilitate the quick installation of various components inside the enclosure 1 and to facilitate the later disassembly of the enclosure 1 for replacement of internal components, the enclosure 1 includes a main shell 11, an end cover 12, and an end cover 13. The main shell 11 has a cylindrical structure. The end cover 12 is sealed and installed at the input end of the main shell 11, and the end cover 13 is sealed and installed at the output end of the main shell 11.

[0059] To reduce the rotational resistance of the input end bushing 2 and the output shaft 4 during operation, multiple sets of parallel-arranged outer bearings 50 are provided between the input end bushing 2 and the end cover 12, and a cover 60 is also provided on the end cover 12; multiple sets of parallel-arranged outer bearings 70 are provided between the output shaft 4 and the end cover 13, and a cover 80 is also provided on the end cover 13.

[0060] In order to reduce the rotational resistance of the gear ring 34 during operation, a middle bearing 90 is provided between the outer peripheral wall of the end of the gear ring 34 and the inner peripheral wall of the housing 1, and the two middle bearings 90 respectively abut against the two ends of the gear ring 35.

[0061] In this embodiment, the two planetary transmission groups 3 are respectively named the first-level planetary transmission group 3 and the second-level planetary transmission group 3. The internal components are distinguished by adding "first-level" or "second-level" before their names, such as... Figure 1 As shown, the planetary reducer has a minimum speed ratio of 1, and the power transmission route is as follows: input end bushing 2, first-stage sun gear 31, connecting sleeve 1 5, adjusting sleeve 1 8, combined sleeve 7, adjusting sleeve 2 9, second-stage planetary carrier 33, output shaft 4; Figure 2 As shown, the planetary reducer has a medium speed ratio, specifically 3.2. The power transmission route is as follows: input end bushing 2, first-stage sun gear 31, first-stage planetary gears 32, first-stage planetary carrier 33, adjusting sleeve 1 8, combination sleeve 7, adjusting sleeve 2 9, second-stage planetary carrier 33, output shaft 4; Figure 3 As shown, the planetary reducer has a maximum speed ratio of 10.24, and the power transmission route is as follows: input end bushing 2, first-stage sun gear 31, first-stage planetary gear 32, first-stage planetary carrier 33, adjusting bushing 1 8, combined bushing 7, adjusting bushing 2 9, connecting bushing 2 6, second-stage sun gear 31, second-stage planetary gear 32, second-stage planetary carrier 33, and output shaft 4.

[0062] The beneficial technical effects of the multi-stage adjustable planetary reducer in this application are roughly as follows:

[0063] By driving the adjusting sleeves 8 and 9 to slide with external force, the internal gear 81 can mesh with the first external gear 331 or with the external gear 51, and the internal gear 91 can mesh with the second external gear 332 or with the external gear 61, thereby adjusting the speed ratio of the entire reducer. During the speed ratio adjustment process, the clearance sleeve 36 can be driven to slide with external force first, so that the external spline tooth 362 completely disengages from the internal teeth of the gear ring 35, allowing the planetary carrier 33 to switch to the unlocked state. That is, the planetary carrier 33 has clearance space to rotate a certain angle along the central axis. By slightly shaking the planetary carrier 33, it can be confirmed that... During the sliding process, the inner tooth 81 of the adjusting sleeve 8 can simultaneously mesh with the first outer tooth 331 and the outer tooth 51. During the sliding process, the inner tooth 91 of the adjusting sleeve 9 can simultaneously mesh with the second outer tooth 332 and the outer tooth 61. After the speed ratio is adjusted, the external force drives the clearance sleeve 36 to reset, that is, the outer spline tooth 362 and the inner tooth of the gear ring 35 are fully meshed. The reducer does not need to reserve an additional sliding space of 150-200mm inside, so the axial length of the entire reducer will be greatly shortened, making the planetary reducer smaller in size and axial length, which can be used in some narrow installation positions.

[0064] The above description is merely a preferred embodiment of this application and is not intended to limit this application. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A multi-stage adjustable speed ratio planetary reducer, comprising a housing and an input end bushing, two sets of planetary transmission groups, and an output shaft arranged sequentially along a central axis, characterized in that: The planetary transmission assembly includes a sun gear, planet gears, a planet carrier, a first gear ring, a second gear ring, and a clearance sleeve. The input end sleeve is fixedly connected to the input end of the nearest sun gear, and the output shaft is fixedly connected to the output end of the nearest planet carrier. The sun gear and planet gears mesh for transmission, and the planet gears and planet carrier are connected for transmission. The planet gears mesh with the internal teeth of the first gear ring. The clearance sleeve has internal splines and external splines. The internal splines mesh with the first gear ring, and the external splines mesh with the second gear ring. The second gear ring is fixed to the housing. The output end of the sun gear, which is not connected to the output shaft, is fixedly connected to a first sleeve. The output end of the planet carrier adjacent to the first sleeve is provided with a first external tooth. The outer peripheral wall of the first sleeve is provided with an external tooth. The input end of the sun gear, which is not connected to the input end sleeve, is fixedly connected to a second sleeve. The input end of the planet carrier adjacent to the second sleeve is provided with a second external tooth. The outer peripheral wall of the second sleeve is provided with an external tooth. A combination sleeve is also provided between the first and second connecting sleeves. The outer peripheral wall of the combination sleeve is provided with connecting external teeth. The two ends of the combination sleeve are also slidably fitted with the first and second adjusting sleeves. The inner peripheral wall of the first adjusting sleeve is provided with the first and second internal teeth. An annular groove 1 is reserved between the first and second internal teeth. The inner peripheral wall of the second adjusting sleeve is provided with the third and fourth internal teeth. An annular groove 2 is reserved between the third and fourth internal teeth. After the external spline teeth are completely disengaged from the internal teeth of the gear ring 2, the planetary carrier is in the unlocked state.

2. The multi-stage adjustable planetary reducer according to claim 1, characterized in that, The outer peripheral wall of the clearance sleeve is also provided with an annular shift fork groove, and the housing is provided with a shift fork hole corresponding to the annular shift fork groove. The external shift fork can be inserted into the annular shift fork groove through the shift fork hole to drive the clearance sleeve to slide axially and unlock the locking state of the planetary carrier.

3. The multi-stage adjustable planetary reducer according to claim 1, characterized in that, The outer peripheral wall of the adjusting sleeve is provided with an annular shift fork groove 2, and the housing is provided with a shift fork hole 2 corresponding to the annular shift fork groove 2. The external shift fork can be inserted into the annular shift fork groove 2 through the shift fork hole 2 to drive the adjusting sleeve 1 to slide axially and change the speed ratio.

4. The multi-stage adjustable planetary reducer according to claim 1, characterized in that, The outer peripheral wall of the adjusting sleeve 2 is provided with an annular shift fork groove 3, and the housing is provided with a shift fork hole 3 corresponding to the annular shift fork groove 3. The external shift fork can be inserted into the annular shift fork groove 3 through the shift fork hole 3 to drive the adjusting sleeve 2 to slide axially and change the speed ratio.

5. The multi-stage adjustable planetary reducer according to claim 1, characterized in that, An inner bearing is provided between the inner peripheral wall of the combined sleeve and the outer peripheral wall of the connecting sleeve one. A bearing cover is provided at the end of the connecting sleeve one. An inner bearing is provided between the inner peripheral wall of the combined sleeve and the outer peripheral wall of the connecting sleeve two. A bearing cover is provided at the end of the connecting sleeve two. The bearing cover one and the bearing cover two are in contact with each other.

6. The multi-stage adjustable planetary reducer according to claim 1, characterized in that, The enclosure includes a main shell, end cover one, and end cover two. The main shell is a cylindrical structure. End cover one is sealed and installed at the input end of the main shell, and end cover two is sealed and installed at the output end of the main shell.

7. The multi-stage adjustable planetary reducer according to claim 6, characterized in that, Multiple sets of parallel-arranged outer bearings are provided between the input end bushing and the end cover one, and a sealing cover one is also provided on the end cover one; multiple sets of parallel-arranged outer bearings are provided between the output shaft and the end cover two, and a sealing cover two is also provided on the end cover two.

8. The multi-stage adjustable planetary reducer according to claim 1, characterized in that, A central bearing is provided between the outer peripheral wall of the end of gear ring one and the inner peripheral wall of the housing, and two central bearings abut against the two ends of gear ring two respectively.

9. The multi-stage adjustable planetary reducer according to claim 1, characterized in that, The gap width between the two ends of external tooth one and the first external tooth and the connecting external tooth is between 1 and 3 mm, and the gap width between the two ends of external tooth two and the second external tooth and the connecting external tooth is between 1 and 3 mm.

10. The multi-stage adjustable planetary reducer according to claim 1, characterized in that, The planetary gear set has two sets, and the speed ratio of each planetary gear set is A. The value of A is between 3 and 5. This multi-stage adjustable speed ratio planetary reducer can switch between three working modes: speed ratio 1, speed ratio A, and speed ratio A².

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