Gear shifting mechanism and speed reducer assembly

Abstract

The gear shifting mechanism is assembled on a target planetary transmission set and comprises a movable gear sleeve, a first fixed gear sleeve and a second fixed gear sleeve, the movable gear sleeve is in shaft connection with a target gear ring and is movably arranged in the axial direction relative to the target gear ring, the first fixed gear sleeve is in shaft connection with a target planet carrier, and the second fixed gear sleeve is in shaft connection with a second planet carrier. And the second fixed gear sleeve is fixedly arranged relative to the target planetary transmission set, and has a first working position connected with the first fixed gear sleeve shaft and a second working position connected with the second fixed gear sleeve shaft in the moving stroke of the movable gear sleeve. The transmission ratio of the target planetary transmission set can be changed by controlling the moving action of the single moving gear sleeve, the gear shifting purpose is achieved, a plurality of clutch devices do not need to be matched for gear shifting, the structure is simple, clamping stagnation is not likely to happen, the error-tolerant rate is high, and stability is good.

Description

Technical Field

[0001] The present invention relates to the technical field of vehicle manufacturing, and in particular to a gear shifting mechanism and a reducer assembly. Background Art

[0002] In the prior art, wheel-side reducers usually use multiple clutch devices to achieve gear shifting. Specifically, multiple clutch devices work together to make the sun gear, ring gear and / or planet carrier in the planetary transmission group fixed or movable, so as to achieve the purpose of switching between different gears. This gear shifting method requires multiple clutch devices to work together. On the one hand, there are disadvantages such as complex clutch structure, large space occupation and high maintenance cost. On the other hand, the fault tolerance rate is low, and it is easy to cause gear shifting failures such as jamming due to improper cooperation of different clutch devices. Summary of the invention

[0003] The present invention aims to provide a shift mechanism and a reducer assembly which have a simple structure, low maintenance cost, are not prone to jamming and have high stability.

[0004] In order to solve the above technical problems, the present invention provides a shift mechanism, comprising:

[0005] The shift mechanism is used to be assembled on a target planetary transmission group, the target planetary transmission group includes a target ring gear and a target planet carrier, and the shift mechanism includes:

[0006] A movable gear sleeve is connected to the target gear ring shaft and is movably arranged in the axial direction relative to the target gear ring, and the movable gear sleeve is provided with engaging teeth;

[0007] A first fixed gear sleeve, connected to the target planet carrier shaft, the first fixed gear sleeve being provided with a first matching tooth;

[0008] A second fixed gear sleeve, fixedly arranged relative to the planetary transmission assembly, the second solid sleeve being provided with second matching teeth;

[0009] Among them, the first fixed gear sleeve, the movable gear sleeve and the second fixed gear sleeve are arranged in sequence along the axial direction, and the movable gear sleeve has a first working position in which the combining tooth is engaged with the first matching tooth to connect the target gear ring to the target planetary carrier shaft during its axial movement stroke; and a second working position in which the combining tooth is engaged with the second matching tooth to fix the target gear ring and the target planetary carrier is rotatable relative to the target gear ring.

[0010] Optionally, the combining tooth includes a plurality of combining keys arranged circumferentially on the movable gear sleeve, the first mating tooth includes a plurality of first mating keys arranged circumferentially on the first fixed gear sleeve, and the second mating tooth includes a plurality of second mating keys arranged circumferentially on the second fixed gear sleeve.

[0011] Optionally, each of the combination keys has a first tooth segment, a middle tooth segment and a second tooth segment which are sequentially arranged along the axial direction;

[0012] The outer periphery of the target gear ring is provided with a plurality of engaging keys arranged along the circumferential direction, and the plurality of intermediate tooth segments are correspondingly engaged with the plurality of engaging keys;

[0013] When the movable gear sleeve is located at the first working position, each of the first tooth segments is correspondingly engaged with each of the first mating keys, and when the movable gear sleeve is located at the second working position, each of the second tooth segments is correspondingly engaged with each of the second mating keys.

[0014] Optionally, in each of the combining keys, the sizes of the first tooth segment and the second tooth segment in the circumferential direction are respectively smaller than those of the middle tooth segment, a first step surface is formed between the middle tooth segment and the first tooth segment on both sides in the circumferential direction, the first step surface extends obliquely toward the direction close to the first fixed tooth sleeve, and a second step surface is formed between the middle tooth segment and the second tooth segment on both sides in the circumferential direction, the second step surface extends obliquely toward the direction close to the second fixed tooth sleeve; and / or,

[0015] The circumferential dimensions of the first tooth segment and the second tooth segment are at least partially gradually increased in a direction away from the middle tooth segment, and the circumferential dimensions of each of the first mating keys and each of the second mating keys are at least partially increased in a direction approaching the middle tooth segment.

[0016] Optionally, the shift mechanism further comprises a hub having a first spline hole axially extending therethrough, the first spline hole being cooperatively connected with a first spline arranged on the outer periphery of the target gear ring, and a plurality of the engaging keys being arranged on the outer periphery of the hub.

[0017] Optionally, each of the combining keys is provided with a first chamfered structure at the end facing the first fixed tooth sleeve and the second fixed tooth sleeve, and each of the first mating teeth and each of the second mating teeth is provided with a second chamfered structure at the end facing the movable tooth sleeve, and the first chamfered structure and the second chamfered structure are adapted to each other.

[0018] Optionally, a first retaining ring is further disposed on the outer periphery of the first fixed gear sleeve, the first retaining ring is spaced apart from the first mating tooth in the axial direction, and is disposed on a side of the first mating tooth away from the movable gear sleeve;

[0019] A second retaining ring is further provided on the outer periphery of the second fixed gear sleeve, the second retaining ring is spaced apart from the second mating tooth in the axial direction, and is provided on a side of the second mating tooth away from the movable gear sleeve;

[0020] The movable gear sleeve is formed with a first limiting surface facing the first retaining ring and a second limiting surface facing the second retaining ring. When the movable retaining ring is located at the first working position, the first limiting surface abuts against the first retaining ring. When the movable retaining ring is located at the second working position, the second limiting surface abuts against the second retaining ring.

[0021] In order to solve the above technical problems, the present invention further provides a reducer assembly, comprising:

[0022] A housing having a mounting cavity, wherein a first axial hole and a second axial hole are provided on the housing and are arranged opposite to each other in the axial direction, and the first axial hole and the second axial hole are respectively connected to the mounting cavity;

[0023] A first planetary transmission set is installed in the installation cavity, the first planetary transmission set includes a first sun gear, a plurality of first planetary gears, a first ring gear, and a first planet carrier, wherein the first sun gear is connected to an input shaft inserted into the installation cavity from the first shaft hole, the first ring gear is fixed to the housing and sleeved on the periphery of the plurality of first planetary gears, and the first planet carrier is connected to the plurality of first planetary gears;

[0024] a second planetary transmission group, comprising a second planet carrier and a second sun gear, a plurality of second planet gears, and a second ring gear installed in the installation cavity, wherein the second sun gear is connected to the first planet carrier shaft, the second ring gear is sleeved on the periphery of the plurality of second planet gears, one end of the second planet carrier is connected to the plurality of second planet gears, and the other end extends out of the installation cavity from the second shaft hole; and

[0025] As described above, the shifting mechanism is installed in the mounting cavity, wherein the second planetary transmission group constitutes the target planetary transmission group, the second ring gear constitutes the target ring gear, the second planetary carrier constitutes the target planetary carrier, and the second fixed gear sleeve is fixed to the inner side of the casing.

[0026] Optionally, the second gear ring has a first end and a second end which are arranged opposite to each other in the axial direction, the first end is relatively close to the first shaft hole, and the second end is relatively close to the second shaft hole, the second gear ring is provided with a through hole at the first end, and is open at the second end, a first spline is provided on the outer periphery of the first end, and the first spline is used to install the movable gear sleeve, and the second end is provided with an internal gear, and the internal gear is meshed with each of the second planetary gears;

[0027] One end of the second planetary carrier passes through the through hole, and the other end is connected to a plurality of the second planetary gears, and the second planetary carrier, the inner periphery of the second gear ring, and the plurality of the second planetary gears enclose an installation space, and a first bearing is installed in the installation space, and the first bearing acts between the second gear ring and the second planetary carrier.

[0028] Optionally, the second planet carrier comprises a planet carrier cover and a planet mounting frame, the planet carrier cover passes through the through hole, and a limiting ring is convexly provided on the outer circumference, and the planet carrier cover is provided with a second spline on a side of the limiting ring away from the through hole;

[0029] The planetary mounting frame includes a ring frame sleeved on the outer circumference of a plurality of second planetary gears, and a first sleeve and a second sleeve respectively protruding on both sides of the ring frame, the first sleeve is located in the second gear ring and sleeved with the first bearing, the first sleeve is axially penetrated with a second spline hole and abuts against the limit ring, the second spline hole is matched and connected with the second spline, the second sleeve is located outside the second gear ring and sleeved with a second bearing, and the second bearing acts between the second planetary frame and the casing.

[0030] The technical solution provided by the present invention has the following advantages:

[0031] The shift mechanism provided by the present invention is assembled on a target planetary transmission group, and the target transmission planetary transmission group includes a target sun gear, a target planetary gear, a target planetary carrier and a target ring gear, wherein the target sun gear serves as a power input end, and the target planetary carrier serves as a power output end. The shift mechanism includes a moving gear sleeve, a first fixed gear sleeve and a second fixed gear sleeve, wherein the moving gear sleeve is connected to the target ring gear shaft and is movably arranged axially relative to the target ring gear, the first fixed gear sleeve is connected to the target planetary carrier shaft, and the second fixed gear sleeve is fixedly arranged relative to the target planetary transmission group, and in the moving stroke of the moving gear sleeve, there is a first working position connected to the first fixed gear sleeve shaft and a second working position connected to the second fixed gear sleeve shaft, when the moving gear sleeve moves to the first working position, the target ring gear is connected to the target planetary carrier as a whole, and the target planetary transmission group does not play a deceleration role, when the moving gear sleeve moves to the second working position, the target ring gear is fixed, the target planetary carrier is meshed with the target ring gear for transmission, and the target planetary transmission group plays a deceleration role. In the embodiment provided by the present invention, the transmission ratio of the target planetary transmission group can be changed by controlling the movement of a single movable gear sleeve to achieve the purpose of gear shifting. There is no need for multiple clutch devices to cooperate in gear shifting. The structure is simple, not easy to get stuck, has a high fault tolerance rate, and has good stability. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] In order to more clearly illustrate the specific implementation methods of the present invention or the technical solutions in the prior art, the drawings required for use in the specific implementation methods or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are some implementation methods of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0033] Figure 1 A schematic diagram of the three-dimensional structure of a reducer assembly according to an embodiment of the present invention;

[0034] Figure 2 for Figure 1 A cross-sectional view of the middle reducer assembly;

[0035] Figure 3 for Figure 2 The three-dimensional structure exploded view of the reduction transmission mechanism in the middle casing;

[0036] Figure 4 for Figure 3 The assembly diagram of the second gear ring and the shift mechanism;

[0037] Figure 5 for Figure 3 The assembly diagram of the second planetary gear and the second planetary carrier;

[0038] Figure 6 for Figure 2 A schematic diagram of the three-dimensional structure of the middle shift mechanism;

[0039] Figure 7 for Figure 6 A schematic diagram of the three-dimensional structure of the middle shift mechanism from another perspective;

[0040] Figure 8 for Figure 7 A front view of the middle shift mechanism;

[0041] Fig. 9 for Figure 8 A cross-sectional view at AA in the middle, wherein the movable gear sleeve is located at the first working position;

[0042] Fig.10 for Figure 8 A cross-sectional view at AA in the middle, wherein the movable gear sleeve is located in the second working position;

[0043] Fig.11 for Figure 8 Schematic diagram of the three-dimensional structure of the middle moving gear sleeve;

[0044] Fig.12 for Fig.11 The enlarged schematic diagram of point A in the middle;

[0045] Fig.13for Fig.11 A front view of the middle moving gear sleeve;

[0046] Fig.14 for Fig.13 Sectional view at the middle BB;

[0047] Fig.15 for Fig.11 A schematic diagram of the three-dimensional structure of the first fixed gear sleeve;

[0048] Fig.16 for Fig.15 A front view of the first fixed gear sleeve;

[0049] Fig.17 for Fig.16 Sectional view at CC;

[0050] Fig.18 for Figure 3 A schematic diagram of the three-dimensional structure of the second gear ring;

[0051] Fig.19 for Fig.18 A front view of the second gear ring;

[0052] Fig. 20 for Fig.19 Sectional view at DD in the middle;

[0053] Fig.21 for Figure 3 Schematic diagram of the three-dimensional structure of the middle planet carrier cover;

[0054] Fig. 22 for Figure 3 A schematic diagram of the three-dimensional structure of the middle planetary mounting frame;

[0055] Fig.23 for Fig. 22 A front view of the middle planetary mounting frame;

[0056] Fig.24 for Fig.23 Cross-sectional view at EE in the middle.

[0057] Description of reference numerals:

[0058] 1000-reducer assembly; 100-shift mechanism; 10-movable gear sleeve; 11-combining tooth; 12-combining key; 121-first tooth segment; 122-intermediate tooth segment; 123-second tooth segment; 13-first limiting surface; 14-second limiting surface; 15-first chamfering structure; 20-first fixed gear sleeve; 21-first matching tooth; 22-first matching key; 23-first step surface; 24-first retaining ring; 25-second chamfering structure; 30-second fixed gear sleeve; 31-second matching tooth; 32-second matching key; 33-second step surface; 34-second retaining ring; 40-shaft hub; 41-first spline hole; 42-clamping key; 200-housing; 50-installation cavity; 51-first shaft hole; 52-second shaft hole; 3 00-first planetary transmission group; 60-first sun gear; 61-first planetary gear; 62-first ring gear; 63-first planet carrier; 400-second planetary transmission group / target planetary transmission group; 70-second sun gear / target sun gear; 71-second planetary gear / target planetary gear; 72-second ring gear / target ring gear; 720-installation space; 721-through hole; 722-internal gear; 723-first spline; 73-second planet carrier / target planet carrier; 731-planet carrier cover; 7311-limiting ring; 7312-second spline; 732-planet mounting frame; 80-ring frame; 81-first shaft sleeve; 82-second shaft sleeve; 90-second spline hole; 91-first bearing; 92-second bearing; 93-third bearing. DETAILED DESCRIPTION

[0059] The technical solution of the present invention will be clearly and completely described below in conjunction with the accompanying drawings. Obviously, the described embodiments are part of the embodiments of the present invention, rather than all of the embodiments. The present invention will be described in detail below with reference to the accompanying drawings and in conjunction with the embodiments. It should be noted that the embodiments of the present invention and the features in the embodiments can be combined with each other without conflict.

[0060] It should be noted that the terms "first", "second", etc. in the specification and claims of the present invention and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence.

[0061] See also Figures 1 to 24 The present invention provides a reducer assembly 1000 and a shift mechanism 100 thereof. The reducer assembly 1000 can be applied to vehicle wheel-side deceleration, and can also be applied to other deceleration transmission scenarios. In a preferred embodiment, the reducer assembly 1000 is applied to heavy truck wheel-side deceleration. Preferably, a reducer assembly 1000 is respectively provided on two wheels arranged side by side, so that differential steering between the two wheels can be achieved.

[0062] Please continue reading Figures 1 to 3The reducer assembly 1000 includes a housing 200, which is used to provide mounting support and protection for the reducer assembly 1000. Specifically, a mounting cavity 50 is formed in the housing 200, and a reduction transmission mechanism is installed in the mounting cavity 50. The housing 200 is provided with a first shaft hole 51 and a second shaft hole 52 which are arranged opposite to each other in the axial direction, and the first shaft hole 51 and the second shaft hole 52 are connected to the mounting cavity 50 respectively. The first shaft hole 51 is used for the input shaft to extend into the mounting cavity 50, and the input shaft is driven to rotate by an external main power source, such as a vehicle motor, so as to provide driving force for the reduction transmission mechanism inside the housing 200, and the second shaft hole 52 is used for the output shaft to extend to achieve power output. The reduction transmission mechanism is connected between the input shaft and the output shaft to achieve the reduction output of the power source. A shift mechanism 100 is also arranged in the housing 200, and the shift mechanism 100 can be movably arranged and acts on the reduction transmission mechanism to adjust its gear position.

[0063] In this embodiment, please continue to refer to Figure 2 and Figure 3 The reduction transmission mechanism includes at least one planetary transmission group. The shift mechanism 100 provided in this embodiment is installed in one or more of the at least one planetary transmission group to play the role of clutch shifting of the planetary transmission group. In this embodiment, the planetary transmission group equipped with the shift mechanism 100 is defined as the target planetary transmission group 400. Figures 2 to 5 As shown, the target planetary transmission group 400 includes a target sun gear 70, a target planetary gear 71, a target ring gear 72 and a target planetary carrier 73, wherein a plurality of target planetary gears 71 are provided and are arranged around the outer periphery of the target sun gear 70, the target ring gear 72 is arranged around the periphery of the plurality of target planetary gears 71, and the target planetary carrier 73 is fixed to the plurality of target planetary gears 71. Preferably, the target sun gear 70 serves as a power input end, and the target planetary carrier 73 serves as a power output end.

[0064] Please continue to refer to Figures 6 to 17The deceleration mechanism provided by the present invention includes a mobile gear sleeve 10, a first fixed gear sleeve 20 and a second fixed gear sleeve 30. The mobile gear sleeve 10 is connected to the target gear ring 72 axially, and the axial connection method includes but is not limited to an integral setting, a fixed connection, a key connection, a spline connection, a hub connection, etc., and the mobile gear sleeve 10 is movably arranged relative to the target gear ring 72 along the axial direction, and a coupling tooth 11 is arranged on the mobile gear sleeve 10. The first fixed gear sleeve 20 is connected to the target planetary carrier 73 axially, specifically, it can be integrally arranged, fastened as a whole, key-connected, etc. with the target planetary carrier 73, and a first matching tooth 21 is arranged on the first fixed gear sleeve 20. The second fixed gear sleeve 30 is fixedly arranged relative to the planetary transmission group, that is, it is arranged non-rotatably or non-movably relative to the planetary transmission group. Specifically, in this embodiment, the second fixed gear sleeve 30 is fixed in the housing 200, preferably integrally arranged with the housing 200, such as connected as a whole or integrally formed, and a second matching tooth 31 is arranged on the second solid sleeve. The tooth shapes of the first mating tooth 21 and the second mating tooth 31 are configured to match the coupling tooth 11 , so that the coupling tooth 11 can smoothly engage with or disengage from one of the first mating tooth 21 and the second mating tooth 31 .

[0065] Specifically, see Fig. 9 and Fig.10 , the first fixed gear sleeve 20, the mobile gear sleeve 10 and the second fixed gear sleeve 30 are arranged in sequence along the axial direction, and the mobile gear sleeve 10 has a first working position in which the coupling tooth 11 is engaged with the first matching tooth 21 in its axial movement stroke, so that the target gear ring 72 is connected to the target planetary carrier 73 axis; and a second working position in which the coupling tooth 11 is engaged with the second matching tooth 31, so that the target gear ring 72 is fixed and the target planetary carrier 73 is rotatable relative to the target gear ring 72. It should be noted that the reducer assembly 1000 also includes a driving mechanism acting on the shifting mechanism 100, so that the shifting mechanism 100 performs a shifting action according to demand. The specific form of the driving mechanism is not limited. In an optional embodiment, the driving mechanism may include a shifting motor that drives the mobile gear sleeve 10 to move, and the shifting motor drives the mobile gear sleeve 10 to move between the first working position and the second working position.

[0066] In this embodiment, when the mobile gear sleeve 10 moves to the first working position, the target gear ring 72 is connected to the target planet carrier 73 as a whole. At this time, the transmission ratio of the target planetary transmission group 400 is approximately 1, and the target planetary transmission group 400 does not play a deceleration role. When the mobile gear sleeve 10 moves to the second working position, the target gear ring 72 is fixed, and the target planet carrier 73 is meshed with the target gear ring 72 for transmission. At this time, the transmission ratio of the target planetary transmission group 400 is less than 1, and the target planetary transmission group 400 plays a deceleration role. In the embodiment provided by the present invention, the transmission ratio of the target planetary transmission group 400 can be changed by controlling the movement of a single mobile gear sleeve 10 to achieve the purpose of shifting, without the need for multiple clutch devices to cooperate with the shifting, and the structure is simple, not easy to get stuck, high fault tolerance, and good stability.

[0067] There are many specific configurations of the combined tooth 11, the first matching tooth 21 and the second matching tooth 31. In a preferred embodiment, in order to achieve the purpose of stable torque transmission and gear shifting during movement, please continue to refer to Figures 11 to 17 As shown in the figure, the coupling tooth 11 includes a plurality of coupling keys 12 arranged circumferentially on the inner ring of the mobile gear sleeve 10, the first mating tooth 21 includes a plurality of first mating keys 22 arranged circumferentially on the outer ring of the first fixed gear sleeve 20, and the second mating tooth 31 includes a plurality of second mating keys 32 arranged circumferentially on the outer ring of the second fixed gear sleeve 30. Preferably, the coupling key 12 is arranged on the inner ring of the mobile gear sleeve 10, and the first mating key 22 and the second mating key 32 are correspondingly arranged on the outer rings of the corresponding first fixed gear sleeve 20 and the second fixed gear sleeve 30. When the mobile gear sleeve 10 moves to the first working position, the first mating tooth 21 is inserted into the mobile gear sleeve 10 and engaged with the coupling tooth 11, and the first fixed gear sleeve 20 and the mobile gear sleeve 10 are axially connected in a non-rotatable manner to stably transmit torque. At this time, the target planet carrier 73 is axially connected to the target gear ring 72, and the target planetary transmission group 400 does not play a deceleration role. When the mobile gear sleeve 10 moves to the second working position, the second mating tooth 31 is inserted into the mobile gear sleeve 10 and engages with the combining tooth 11. The second fixed gear sleeve 30 and the mobile gear sleeve 10 are non-rotatably connected to each other to stably transmit torque. At this time, the target ring gear 72 is fixed to the housing 200 and no longer rotates. The target planetary transmission group 400 plays a deceleration role.

[0068] In order to achieve smooth movement of the movable gear sleeve 10, please refer to Figures 9 to 12, each combining key 12 has a first tooth segment 121, an intermediate tooth segment 122 and a second tooth segment 123 arranged in sequence along the axial direction. The outer periphery of the target gear ring 72 is provided with a plurality of engaging keys 42 arranged along the circumferential direction, and the plurality of intermediate tooth segments 122 are correspondingly engaged with the plurality of engaging keys 42. It should be noted that, in an optional embodiment, the engaging keys 42 may be directly formed on the target gear ring 72, or may not be directly protruded on the outer periphery of the target gear ring 72. In this embodiment, the shifting mechanism 100 also includes a hub 40, which is axially penetrated by a first spline hole 41, the first spline hole 41 is matched and connected with a first spline 723 arranged on the outer periphery of the target gear ring 72, and a plurality of engaging keys 42 are arranged on the outer periphery of the hub 40. At this time, the movable gear sleeve 10 is connected to the target gear ring 72 axis through the shaft hub 40, and the shaft hub 40 is installed relatively immovably relative to the movable gear sleeve 10. At this time, the locking key 42 is correspondingly arranged on the outer periphery of the shaft hub 40, and the movable gear sleeve 10 is correspondingly sleeved on the shaft hub 40, and the straight tooth shape of the intermediate tooth segment 122 and the locking key 42 is matched, so that the two can slide smoothly relative to each other in the axial direction.

[0069] Furthermore, the first tooth segment 121 and the first mating key 22 have toothed structures that can be engaged with each other, and the second tooth segment 123 and the second mating member have toothed structures that can be engaged with each other, so that Fig. 9 and 10 As shown, when the movable gear sleeve 10 is located at the first working position, each first tooth segment 121 is correspondingly engaged with each first matching key 22 , and when the movable gear sleeve 10 is located at the second working position, each second tooth segment 123 is correspondingly engaged with each second matching key 32 .

[0070] Based on the previous embodiment, please continue to refer to Fig.12 In each of the coupling keys 12, the first tooth segment 121 and the second tooth segment 123 are respectively smaller in the circumferential direction than the middle tooth segment 122. This prevents the tooth shape design of the first tooth segment 121 or the second tooth segment 123 from affecting the smoothness of the axial sliding of the movable gear sleeve 10. The middle tooth segment 122 forms a first step surface 23 between the first tooth segment 121 on both sides in the circumferential direction, and the first step surface 23 extends obliquely toward the direction close to the first fixed gear sleeve 20. The middle tooth segment 122 forms a second step surface 33 between the second tooth segment 123 on both sides in the circumferential direction, and the second step surface 33 extends obliquely toward the direction close to the second fixed gear sleeve 30.

[0071] In this way, a tooth groove is formed between two circumferentially adjacent binding keys 12, and at least one first step surface 23, preferably two, is formed at one end of the tooth groove facing the first fixed tooth sleeve 20. The first step surface 23 serves as a limit guide for the first mating tooth 21, so that the first mating tooth 21 will not be inserted too far into the tooth groove to cause the movable tooth sleeve 10 to be stuck, and the binding key 12 can smoothly leave the tooth groove. At least one second step surface 33, preferably two, is formed at one end of the tooth groove facing the second fixed tooth sleeve 30. The second step surface 33 serves as a limit guide for the second mating tooth 31, so that the second mating tooth 31 will not be inserted too far into the tooth groove to cause the movable tooth sleeve 10 to be stuck, and the binding key 12 can smoothly leave the tooth groove.

[0072] In another optional embodiment, the circumferential dimensions of the first tooth segment 121 and the second tooth segment 123 are at least partially gradually increased in the direction away from the middle tooth segment 122, and the circumferential dimensions of each first mating key 22 and each second mating key 32 are at least partially increased in the direction close to the middle tooth segment 122. In this way, each tooth groove and the corresponding first mating key 22 or second mating key 32 have a wedge-shaped structure that matches each other. In this embodiment, when the mobile gear sleeve 10 is located in the first working position, each first mating key 22 wedges into the corresponding tooth groove one by one, and the first fixed gear sleeve 20 has a certain locking force on the mobile gear sleeve 10, so that the mobile gear sleeve 10 is not easy to disengage from the first fixed gear sleeve 20, resulting in failure of torque transmission. When the mobile gear sleeve 10 is located in the second working position, each second mating key 32 wedges into the corresponding tooth groove one by one, and the second fixed gear sleeve 30 has a certain locking force on the mobile gear sleeve 10, so that the mobile gear sleeve 10 is not easy to disengage from the second fixed gear sleeve 30, resulting in failure of torque transmission. It can be understood that the above two embodiments can be implemented separately or in combination.

[0073] Please continue to refer to Fig.12 and Fig.15 In an optional embodiment, the ends of each combination key 12 facing the first fixed tooth sleeve 20 and the second fixed tooth sleeve 30 are respectively provided with a first chamfered structure 15, and the ends of each first matching tooth 21 and each second matching tooth 31 facing the movable tooth sleeve 10 are respectively provided with a second chamfered structure 25, and the first chamfered structure 15 and the second chamfered structure 25 are adapted to each other. It should be noted that the specific shape of the chamfered structure is not limited, and can be a mutually adapted cone or a mutually adapted arc surface. The cooperation of the first chamfered structure 15 and the second chamfered structure 25 reduces the resistance between the first tooth segment 121 when it is inserted into the first matching tooth 21, or the second tooth segment 123 when it is inserted into the second matching tooth 31, and it is easier to insert into each other.

[0074] In a preferred embodiment, when the mobile gear sleeve 10 is located at the first working position, the first matching tooth 21 is wedged into the tooth groove, and its second chamfered structure 25 is correspondingly wedged between the two first step surfaces 23 in the tooth groove. When the mobile gear sleeve 10 is located at the second working position, the second matching tooth 31 is wedged into the tooth groove, and its second chamfered structure 25 is correspondingly wedged between the two second step surfaces 33 in the tooth groove. In this way, on the one hand, the mobile gear sleeve 10 is double-locked in the axial direction to prevent it from shaking during the torque transmission process, and on the other hand, the overall axial size of the shift mechanism 100 is smaller and easier to assemble.

[0075] In order to further limit the moving position of the movable gear sleeve 10 to prevent it from moving over the travel and causing it to get stuck, preferably, refer to 9 to Fig.17 The outer periphery of the first fixed gear sleeve 20 is also provided with a first retaining ring 24, which is spaced apart from the first matching teeth 21 in the axial direction and is disposed on the side of the first matching teeth 21 away from the moving gear sleeve 10. The outer periphery of the second fixed gear sleeve 30 is also provided with a second retaining ring 34, which is spaced apart from the second matching teeth 31 in the axial direction and is disposed on the side of the second matching teeth 31 away from the moving gear sleeve 10. The first retaining ring 24 is preferably integrally formed with the first fixed gear sleeve 20, and the second retaining ring 34 is preferably integrally formed with the second fixed gear sleeve 30.

[0076] As shown in the figure, a first limiting surface 13 facing the first retaining ring 24 and a second limiting surface 14 facing the second retaining ring 34 are formed on the mobile gear sleeve 10. Preferably, the first limiting surface 13 is formed on the outer side of the mobile gear sleeve 10 facing the first retaining ring 24 in the radial direction, and the second limiting surface 14 is formed on the outer side of the mobile gear sleeve 10 facing the second retaining ring 34 in the radial direction. When the mobile retaining ring is located at the first working position, the first limiting surface 13 abuts against the first retaining ring 24, and when the mobile retaining ring is located at the second working position, the second limiting surface 14 abuts against the second retaining ring 34. In this embodiment, the travel of the mobile gear sleeve 10 is limited by the limiting cooperation between the mobile gear sleeve 10 and the first retaining ring 24 and the second retaining ring 34, so as to prevent the mobile gear sleeve 10 from moving over the travel during the moving travel, thereby damaging the shift mechanism 100, thereby further improving the stability of the shift mechanism 100.

[0077] Based on the above examples, please refer to Figures 1 to 5 ,and Figure 20 to Figure 24In this embodiment, the reduction transmission mechanism includes a two-stage planetary transmission group, specifically, a first planetary transmission group 300 and a second planetary transmission group 400. The first planetary transmission group 300 is installed in the installation cavity 50, and the first planetary transmission group 300 includes a first sun gear 60, a plurality of first planetary gears 61, a first ring gear 62, and a first planet carrier 63, wherein the first sun gear 60 is connected to the input shaft inserted into the installation cavity 50 from the first shaft hole 51, the first ring gear 62 is fixed to the housing 200 and sleeved on the periphery of the plurality of first planetary gears 61, and the first planet carrier 63 connects the plurality of first planetary gears 61.

[0078] The second planetary transmission group 400 includes a second planetary carrier 73 and a second sun gear 70 installed in the mounting cavity 50, a plurality of second planetary gears 71, and a second ring gear 72, wherein the second sun gear 70 is connected to the first planetary carrier 63 axis, the second ring gear 72 is sleeved on the periphery of the plurality of second planetary gears 71, one end of the second planetary carrier 73 is connected to the plurality of second planetary gears 71, and the other end extends out of the mounting cavity 50 from the second shaft hole 52 as an output shaft. Preferably, a spline is formed on the inner side of the end of the second planetary carrier 73 extending out of the second shaft hole 52 for transmitting torque to the component to be actuated.

[0079] In this embodiment, the input shaft transmits torque to the first sun gear 60, the first planetary gear 61 meshes with the first sun gear 60 for transmission, and outputs torque through the first planet carrier 63 to achieve primary reduction, and the planet carrier is connected to the second sun gear 70 shaft to transmit torque to the second sun gear 70, the second planetary gear 71 meshes with the second sun gear 70 for transmission, and outputs torque through the second planet carrier 73 to achieve secondary reduction. In this way, in this embodiment, two-stage reduction is achieved through the first planetary transmission group 300 and the second planetary transmission group 400, wherein the shift mechanism 100 can be assembled in at least one of the first planetary transmission group 300 and the second planetary transmission group 400.

[0080] Preferably, the speed reducer assembly 1000 further includes the shift mechanism 100 in any of the above embodiments, and the shift mechanism 100 is installed in the mounting cavity 50, wherein the second fixed gear sleeve 30 is fixed to the inner side of the housing 200. As shown in the figure, the shift mechanism 100 is assembled on the second planetary transmission group 400, that is, the second planetary transmission group 400 constitutes the target planetary transmission group 400, the second gear ring 72 constitutes the target gear ring 72 in the above embodiment, and the second planet carrier 73 constitutes the target planet carrier 73 in the above embodiment. When the mobile gear sleeve 10 in the shift mechanism 100 is located in its first working position, the second planet carrier 73 is connected to the second gear ring 72 shaft as a whole, at this time, the first planetary transmission group 300 is reduced in speed, the second planetary transmission group 400 does not play a deceleration role, and the speed reducer assembly 1000 is in the first gear position. When the movable gear sleeve 10 in the shift mechanism 100 is in its second working position, the second ring gear 72 is fixedly connected to the housing 200. At this time, the second ring gear 72 does not rotate, and the second sun gear 70 rotates, driving the second planetary gear 71 to engage in transmission, and the second planetary carrier 73 outputs torque. The first planetary transmission group 300 and the second planetary transmission group 400 both play a deceleration role, and the reducer assembly 1000 is in the second gear.

[0081] In this embodiment, the transmission ratio of the second planetary transmission group 400 can be changed by controlling the movement of a single movable gear sleeve 10 to achieve the purpose of shifting. There is no need for multiple clutch devices to cooperate in shifting. The structure is simple, not easy to get stuck, has a high fault tolerance rate, and good stability.

[0082] Please continue reading Figures 2 to 4 and Figure 20 to Figure 24 The second gear ring 72 has a first end and a second end which are arranged opposite to each other in the axial direction, the first end is relatively close to the first shaft hole 51, and the second end is relatively close to the second shaft hole 52. The second gear ring 72 has a through hole 721 at the first end and is open at the second end. The outer periphery of the first end is provided with a first spline 723, and the first spline 723 is used to install the mobile gear sleeve 10. Specifically, the first spline 723 can be directly spline-connected with the mobile gear sleeve 10, or can be spline-connected with the first spline hole 41 and the shaft hub 40 as shown in the figure. The shaft hub 40 plays a role in adjusting the diameter difference between the second gear ring 72 and the first fixed gear sleeve 20 and the second fixed gear sleeve 30, and also makes the second planet carrier 73 easy to assemble. The second end is provided with an internal gear 722, which meshes with each second planetary gear 71.

[0083] Furthermore, one end of the second planetary carrier 73 passes through the through hole 721, and the other end is connected to multiple second planetary gears 71, and the second planetary carrier 73, the inner periphery of the second ring gear 72, and the multiple second planetary gears 71 enclose an installation space 720, and a first bearing 91 is installed in the installation space 720, and the first bearing 91 acts between the second ring gear 72 and the second planetary carrier 73.

[0084] In this embodiment, the sleeve-type second gear ring 72 is used to assemble the second planetary carrier 73, so that the shift mechanism 100 is installed by using the space near the second shaft hole 52 in the installation cavity 50, so that the reducer assembly 1000 has a compact structure and reasonable force. In addition, the first bearing 91 is installed by using the space between the second gear ring 72 and the second planetary carrier 73. When the reducer assembly 1000 is in the second gear, the first bearing 91 plays a role in supporting the second planetary carrier 73 to rotate relative to the second gear ring 72 and reducing the rotational friction, so that the reduction transmission mechanism can stably transmit torque in the second gear. In the first gear, the first bearing 91 is integrated with the second planetary carrier 73 and the second gear ring 72, and does not affect the integrated rotation of the second planetary carrier 73 and the second gear ring 72.

[0085] Further, the second planet carrier 73 includes a planet carrier cover 731 and a planet mounting frame 732. The planet carrier cover 731 passes through the through hole 721 and is provided with a stop ring 7311 protruding from the outer circumference. The planet carrier cover 731 is provided with a second spline 7312 on the side of the stop ring 7311 away from the through hole 721. The planet mounting frame 732 includes a ring frame 80 sleeved on the outer circumference of the plurality of second planetary gears 71, and a first shaft sleeve 81 and a second shaft sleeve 82 protruding from both sides of the ring frame 80, respectively. The first shaft sleeve 81 is located in the second gear ring 72 and is sleeved with a first bearing 91. The first shaft sleeve 81 is axially penetrated with a second spline hole 90 and abuts against the side of the stop ring 7311 facing the second shaft hole 52. Preferably, the two are fixedly connected by bolts to strengthen the connection between the planet carrier cover 731 and the planet mounting frame 732. The second spline hole 90 is connected with the second spline 7312 to realize the spline connection between the planet carrier cover 731 and the planet mounting frame 732, so that the torque can be transmitted more reliably. The second shaft sleeve 82 is located outside the second gear ring 72 and is sleeved with a second bearing 92, which acts between the second planet carrier 73 and the housing 200. The second bearing 92 supports the rotation of the second planet carrier 73 so that it can stably transmit torque.

[0086] Preferably, if Figure 3As shown, the second planetary carrier 73 is provided with a third bearing 93 on the outer periphery of the end portion near the second shaft hole 52, and the third bearing 93 acts between the second planetary carrier 73 and the housing 200. When the reduction transmission mechanism is in the first gear, the movable gear sleeve 10 is located at the first working position, and the second gear sleeve is connected to the second planetary carrier 73 as a whole. At this time, the second planetary carrier 73 is rotatably supported by the third bearing 93 and the second bearing 92 between the two ends in the axial direction and the housing 200, respectively, and can rotate stably. When the reduction transmission mechanism is in the second gear, the movable gear sleeve 10 is located at the second working position, and the second gear sleeve is fixed to the housing 200. In addition to being rotatably supported by the second bearing 92 and the third bearing 93, the second planetary carrier 73 is also rotatably supported by the first bearing 91 relative to the second gear sleeve, which reduces the rotation resistance between the second planetary gear 71 and the second gear sleeve, and improves the transmission stability and transmission efficiency.

[0087] Obviously, the embodiments described above are only some embodiments of the present invention, rather than all embodiments. Based on the embodiments of the present invention, ordinary technicians in this field can make other different forms of changes or modifications without creative work, which should fall within the scope of protection of the present invention.

Claims

1. A gear shifting mechanism, characterized in that: The shift mechanism is used to be assembled on a target planetary transmission group, the target planetary transmission group includes a target ring gear and a target planet carrier, and the shift mechanism includes: A movable gear sleeve is connected to the target gear ring shaft and is movably arranged in the axial direction relative to the target gear ring, and the movable gear sleeve is provided with engaging teeth; A first fixed gear sleeve, connected to the target planet carrier shaft, the first fixed gear sleeve being provided with a first matching tooth; A second fixed gear sleeve, fixedly arranged relative to the planetary transmission assembly, the second solid sleeve being provided with second matching teeth; Among them, the first fixed gear sleeve, the movable gear sleeve and the second fixed gear sleeve are arranged in sequence along the axial direction, and the movable gear sleeve has a first working position in which the combining tooth is engaged with the first matching tooth to connect the target gear ring to the target planetary carrier shaft during its axial movement stroke; and a second working position in which the combining tooth is engaged with the second matching tooth to fix the target gear ring and the target planetary carrier is rotatable relative to the target gear ring.

2. The shift mechanism according to claim 1, characterized in that: The combining tooth includes a plurality of combining keys arranged circumferentially on the movable gear sleeve, the first mating tooth includes a plurality of first mating keys arranged circumferentially on the first fixed gear sleeve, and the second mating tooth includes a plurality of second mating keys arranged circumferentially on the second fixed gear sleeve.

3. The shift mechanism according to claim 2, characterized in that: Each of the combination keys comprises a first tooth segment, a middle tooth segment and a second tooth segment which are sequentially arranged along the axial direction; The outer periphery of the target gear ring is provided with a plurality of engaging keys arranged along the circumferential direction, and the plurality of intermediate tooth segments are correspondingly engaged with the plurality of engaging keys; When the movable gear sleeve is located at the first working position, each of the first tooth segments is correspondingly engaged with each of the first mating keys, and when the movable gear sleeve is located at the second working position, each of the second tooth segments is correspondingly engaged with each of the second mating keys.

4. The shift mechanism according to claim 3, characterized in that: In each of the combining keys, the sizes of the first tooth segment and the second tooth segment in the circumferential direction are respectively smaller than those of the middle tooth segment, the middle tooth segment forms a first step surface between the first tooth segment and both sides in the circumferential direction, the first step surface extends obliquely toward the first fixed tooth sleeve, the middle tooth segment forms a second step surface between the second tooth segment and both sides in the circumferential direction, the second step surface extends obliquely toward the second fixed tooth sleeve; and / or, The circumferential dimensions of the first tooth segment and the second tooth segment are at least partially gradually increased in a direction away from the middle tooth segment, and the circumferential dimensions of each of the first mating keys and each of the second mating keys are at least partially increased in a direction approaching the middle tooth segment.

5. The shift mechanism according to claim 3, characterized in that: The shift mechanism further comprises a hub, wherein the hub is axially provided with a first spline hole, the first spline hole is cooperatively connected with a first spline arranged on the outer periphery of the target gear ring, and a plurality of the engaging keys are arranged on the outer periphery of the hub.

6. The shift mechanism according to any one of claims 2 to 5, characterized in that: The ends of each of the combining keys facing the first fixed tooth sleeve and the second fixed tooth sleeve are respectively provided with a first chamfered structure, and the ends of each of the first mating teeth and each of the second mating teeth facing the movable tooth sleeve are respectively provided with a second chamfered structure, and the first chamfered structure and the second chamfered structure are adapted to each other.

7. The shift mechanism according to any one of claims 1 to 5, characterized in that: A first retaining ring is further disposed on the outer periphery of the first fixed gear sleeve, the first retaining ring being spaced apart from the first mating tooth in the axial direction and being disposed on a side of the first mating tooth away from the movable gear sleeve; A second retaining ring is further provided on the outer periphery of the second fixed gear sleeve, the second retaining ring is spaced apart from the second mating tooth in the axial direction, and is provided on a side of the second mating tooth away from the movable gear sleeve; The movable gear sleeve is formed with a first limiting surface facing the first retaining ring and a second limiting surface facing the second retaining ring. When the movable retaining ring is located at the first working position, the first limiting surface abuts against the first retaining ring. When the movable retaining ring is located at the second working position, the second limiting surface abuts against the second retaining ring.

8. A reducer assembly, characterized in that: include: A housing having a mounting cavity, wherein a first axial hole and a second axial hole are provided on the housing and are arranged opposite to each other in the axial direction, and the first axial hole and the second axial hole are respectively connected to the mounting cavity; A first planetary transmission set is installed in the installation cavity, the first planetary transmission set includes a first sun gear, a plurality of first planetary gears, a first ring gear, and a first planet carrier, wherein the first sun gear is connected to an input shaft inserted into the installation cavity from the first shaft hole, the first ring gear is fixed to the housing and sleeved on the periphery of the plurality of first planetary gears, and the first planet carrier is connected to the plurality of first planetary gears; a second planetary transmission group, comprising a second planet carrier and a second sun gear, a plurality of second planet gears, and a second ring gear installed in the installation cavity, wherein the second sun gear is connected to the first planet carrier shaft, the second ring gear is sleeved on the periphery of the plurality of second planet gears, one end of the second planet carrier is connected to the plurality of second planet gears, and the other end extends out of the installation cavity from the second shaft hole; and The shift mechanism according to any one of claims 1 to 7, wherein the shift mechanism is installed in the mounting cavity, wherein the second planetary transmission group constitutes the target planetary transmission group, the second ring gear constitutes the target ring gear, the second planetary carrier constitutes the target planetary carrier, and the second fixed gear sleeve is fixed to the inner side of the casing.

9. The reducer assembly according to claim 8, characterized in that: The second gear ring has a first end and a second end which are arranged opposite to each other in the axial direction, the first end is relatively close to the first shaft hole, and the second end is relatively close to the second shaft hole, the second gear ring is provided with a through hole at the first end, and is open at the second end, the outer periphery of the first end is provided with a first spline, the first spline is used to install the moving gear sleeve, and the second end is provided with an internal gear, and the internal gear is meshed with each of the second planetary gears; One end of the second planetary carrier passes through the through hole, and the other end is connected to a plurality of the second planetary gears, and the second planetary carrier, the inner periphery of the second gear ring, and the plurality of the second planetary gears enclose an installation space, and a first bearing is installed in the installation space, and the first bearing acts between the second gear ring and the second planetary carrier.

10. The reducer assembly according to claim 9, characterized in that: The second planet carrier comprises a planet carrier cover and a planet mounting frame, the planet carrier cover passes through the through hole, and a limiting ring is convexly provided on the outer circumference, and the planet carrier cover is provided with a second spline on a side of the limiting ring away from the through hole; The planetary mounting frame includes a ring frame sleeved on the outer circumference of a plurality of second planetary gears, and a first sleeve and a second sleeve respectively protruding on both sides of the ring frame, the first sleeve is located in the second gear ring and sleeved with the first bearing, the first sleeve is axially penetrated with a second spline hole and abuts against the limit ring, the second spline hole is matched and connected with the second spline, the second sleeve is located outside the second gear ring and sleeved with a second bearing, and the second bearing acts between the second planetary frame and the casing.

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