Two-stage planetary gear assembly and correction tool for assembling two-stage planetary gear assembly

Abstract

The utility model discloses a two-stage planetary gear assembly and a correction tool for assembling the two-stage planetary gear assembly, and the two-stage planetary gear assembly comprises a duplex planetary gear unit which comprises a planetary gear support and at least three duplex gear sets which are arranged in the planetary gear support and are uniformly arranged along the circumferential direction; each duplicate gear set comprises a large gear and a small gear which are coaxially connected; a positioning tooth is formed on each of the large gear and the small gear in each duplicate gear set, and the orthographic projection of the symmetrical center line of the tooth profile of the positioning tooth of each large gear and the tooth profile of the positioning tooth of each small gear in the axial direction coincides with the orthographic projection of the symmetrical center line of the tooth profile of each large gear; the sun gear is arranged on the inner sides of the at least three large gears and meshed with each large gear at the same time, and teeth, meshed with the sun gear, of the at least three large gears are evenly distributed in the circumferential direction of the sun gear; a mounting hole suitable for the sun gear to penetrate through is pre-formed in the planet gear bracket; the fixed gear ring is arranged on the outer sides of the at least three bull gears and is meshed with each bull gear at the same time; and the movable gear ring is arranged on the outer sides of the at least three pinions and is meshed with each pinion at the same time.

Description

Technical Field

[0001] The utility model relates to the technical field of gearboxes, in particular to a two-stage planetary gear assembly and a calibration tool for assembling the same. Background Technique

[0002] The planetary gear reduction structure is generally single-stage or multi-stage transmission. For two-stage and above transmissions, a combined structure of a fixed ring gear and multi-stage planetary gears is mostly adopted. Typically, for a two-stage planetary gear transmission, the first-stage planetary gears are engaged with a fixed ring gear, and the second-stage planetary gears are engaged with a moving ring gear. A sun gear is also provided inside the first-stage planetary gears. After assembly, the sun gear is driven to rotate by an external input shaft, and the sun gear drives the first-stage planetary gears to rotate, so that the second-stage planetary gears that rotate synchronously with the first-stage planetary gears drive the moving ring gear to rotate, thereby driving the output shaft to operate.

[0003] For the above two-stage planetary gear transmission process, in one case of the prior art, for the second-stage planetary gears, a fixed gear is arranged inside them to engage with the second-stage planetary gears, so that the second-stage planetary gears are limited between the moving ring gear and the fixed gear (for each second-stage planetary gear, when the meshing points with the fixed gear and the moving ring gear are symmetrically located on both sides of the rotation center of the planetary gear, the reliable and stable operation of the moving ring gear can be ensured), ensuring the reliable operation of the moving ring gear under the action of the second-stage planetary gears. In this case, on the one hand, an additional fixed gear needs to be designed, which will increase the cost in terms of the overall cost of the product. On the other hand, the second-stage planetary gears need to form an accurate fit with the moving ring gear and the fixed gear at the same time to ensure the smoothness during their operation. Therefore, the more components there are, the higher the requirements for assembly accuracy and product accuracy will be.

[0004] Based on the above situation, in the second alternative implementation case, the setting of the fixed gear is cancelled, so that the second-stage planetary gears only cooperate with the moving ring gear, and no fixed gear is arranged inside them. Thus, the structure can be simplified, the assembly process can be reduced, and the assembly difficulty can be lowered. However, in this case, due to the lack of the positioning function of the fixed gear inside the second-stage planetary gears, and the moving ring gear rotates synchronously with the second-stage planetary gears, if the multiple gears of the second-stage planetary gears without the positioning function of the fixed gear cannot ensure a reliable meshing state with the moving ring gear, it may cause uneven force on the moving ring gear, affecting the stability of the operation of the moving ring gear, and at the same time generating an operating noise between the moving ring gear and the second-stage planetary gears.

[0005] Therefore, for the case where the fixed wheel of the second-stage planetary gear is cancelled as described above, how to ensure that multiple gears of the second-stage planetary gear simultaneously form a reliable meshing state with the moving ring gear (for multiple second-stage planetary gears, their meshing and mating points with the moving ring gear should be evenly arranged in the circumferential direction) is a technical difficulty that needs to be overcome, so as to balance the simplicity of the structure and the reliability of operation. In this regard, for example, the planetary transmission system for an excavator travel motor reducer disclosed in the patent publication No. CN205155102U optimizes the tooth profile structure of the double planetary gear, improves the gear meshing condition, prevents uneven load, improves the transmission smoothness, and reduces the transmission noise. Although the planetary transmission system in this structure can improve the transmission smoothness, it requires precise design of the tooth profile structure of the gear and has high requirements for the production accuracy of the gear (high requirements for controlling the tooth alignment deviation between tooth profiles), so the overall production difficulty is still relatively large. Therefore, regarding the issue of balancing the simplicity of the structure and the reliability of operation, it is also necessary to consider the issue of reducing the production difficulty at the same time.

[0006] Therefore, on the premise of reducing the production accuracy requirements for gears, regarding the issue of how to reduce the noise during the operation of the double-stage planetary gear reduction structure and improve its operation reliability, it is necessary to further optimize and improve the structure and assembly process of the existing double-stage planetary gear assembly. Summary of the Invention

[0007] The first object of the present invention is to provide a double-stage planetary gear assembly to solve the technical problem of balancing the simplicity of the structure and the reliability of operation on the premise of reducing the production difficulty.

[0008] The second object of the present invention is to provide a calibration tool for assembling a double-stage planetary gear assembly to solve the technical problem of quickly calibrating the meshing position of the gears of each double-gear group of the double-stage planetary gear assembly.

[0009] The double-stage planetary gear assembly of the present invention is realized as follows:

[0010] A double-stage planetary gear assembly, comprising:

[0011] A double planetary gear unit, which includes a planetary gear bracket and at least three double-gear groups evenly arranged in the circumferential direction provided in the planetary gear bracket; each of the double-gear groups includes a large gear and a small gear coaxially connected; a positioning tooth is respectively formed on the large gear and the small gear of each double-gear group, and the symmetry center line of the tooth profile of the positioning teeth of the large gear and the small gear coincides with the orthographic projection along the axial direction; an identification part corresponding to the positioning tooth is provided on the large gear or the small gear of each double-gear group;

[0012] The sun gear is disposed inside at least three large gears and meshes with each large gear simultaneously, and the teeth of at least three large gears meshing with the sun gear are evenly distributed along the circumferential direction of the sun gear; an installation hole adapted for the sun gear to pass through is preset on the planet gear support;

[0013] The fixed gear ring is disposed outside at least three large gears and meshes with each large gear simultaneously;

[0014] The moving gear ring is disposed outside at least three small gears and meshes with each small gear simultaneously.

[0015] In an alternative embodiment of the present utility model, the identification portion is disposed on the large gear; and

[0016] The identification portion is a structure arranged in a concave or convex manner on the axial side end of the large gear facing away from the small gear.

[0017] In an alternative embodiment of the present utility model, the identification portion is disposed at the tooth root of the positioning tooth of the large gear.

[0018] In an alternative embodiment of the present utility model, the planet gear support includes a first support and a second support adapted to be spliced and connected; wherein

[0019] Both the first support and the second support include a circular shaft end plate and a plurality of extension columns at one axial side end of the circular shaft end plate;

[0020] The extension columns between the first support and the second support are adapted to be assembled and connected.

[0021] In an alternative embodiment of the present utility model, the circular shaft end plate of the first support is located on the side of the large gear of each double gear set facing away from the small gear, and the circular shaft end plate of the second support is located on the side of the small gear of each double gear set facing away from the large gear; and

[0022] Each double gear set is supported in the planet gear support by a planet shaft, and two end portions of the planet shaft are fixedly connected to the circular shaft end plates of the first support and the second support respectively.

[0023] In an alternative embodiment of the present utility model, the moving gear ring is connected to the circular shaft end plate of the second support through a positioning shaft.

[0024] In an alternative embodiment of the present utility model, a positioning column for axially positioning the sun gear is further provided on the circular shaft end plate of the second support and protrudes towards the first support.

[0025] In an alternative embodiment of the present utility model, at least a part of the outer circumferential wall surface of the large gear of each double gear set protrudes from the outer circumferential wall surface of the circular shaft end plate of the first support; and

[0026] The outer circumferential wall surface of the pinion gear of each of the double gear sets protrudes at least partially beyond the outer circumferential wall surface of the circular shaft end plate of the second bracket.

[0027] The calibration tool for assembling the two-stage planetary gear assembly of the present utility model is realized as follows:

[0028] A calibration tool for assembling a two-stage planetary gear assembly, comprising: an annular support plate and a plurality of positioning portions provided on the annular support plate for corresponding to the identification portions of each double gear set;

[0029] The plurality of positioning portions are uniformly arranged in the circumferential direction.

[0030] In an alternative embodiment of the present utility model, the identification portion is a positioning blind hole provided on the large gear and / or the pinion gear;

[0031] The positioning portion is a positioning pin adapted to be inserted into the positioning blind hole; an adaptation hole slidably engaged with the positioning pin is provided on the annular support plate;

[0032] An elastic member is provided between the positioning pin and the adaptation hole, so that the positioning pin is adapted to slide relative to the adaptation hole to enter and exit the positioning blind hole.

[0033] In an alternative embodiment of the present utility model, the annular support plate has a through hole adapted for the sun gear to pass through.

[0034] Adopting the above technical solution, the present utility model has the following beneficial effects: For the two-stage planetary gear assembly of the present utility model and the calibration tool for assembling the same, for the double planetary gear unit, by means of the positioning teeth on the large gear and the pinion gear of each double gear set cooperating with the identification portion, the calibration tool can correct the meshing positions with the fixed gear ring and the moving gear ring, so as to ensure that the meshing positions of the pinion gears respectively corresponding to the plurality of double gear sets are uniformly arranged in the circumferential direction, thereby enabling the plurality of pinion gears to generate balanced rotational acting forces on the moving gear ring, preventing the moving gear ring from being subjected to eccentric loading, and thus improving the smoothness of the transmission of the moving gear ring to reduce the transmission noise.

[0035] Furthermore, for the calibration tool, the calibration purpose of the large gear and the pinion gear of the double gear set can be achieved only by simple cooperation with the identification portion in the double gear set, and the operation is convenient and efficient, and the operation difficulty is low. BRIEF DESCRIPTION OF THE DRAWINGS

[0036] Figure 1 It is an exploded structural schematic diagram of the two-stage planetary gear assembly of the present utility model;

[0037] Figure 2 It is an exploded structural schematic diagram of the double planetary gear unit of the two-stage planetary gear assembly of the present utility model;

[0038] Figure 3 Schematic cross-sectional structure diagram of the two-stage planetary gear assembly of the present utility model;

[0039] Figure 4 Schematic structure diagram of the double gear set of the two-stage planetary gear assembly of the present utility model;

[0040] Figure 5 Schematic structure diagram of the positioning teeth of the double gear set of the two-stage planetary gear assembly of the present utility model;

[0041] Figure 6 Schematic structure diagram of the three double gear sets of the two-stage planetary gear assembly of the present utility model in the state where the positioning teeth are corrected in place;

[0042] Figure 7 Schematic structure diagram of the cooperation between the double planetary gear unit and the calibration tooling of the two-stage planetary gear assembly of the present utility model;

[0043] Figure 8 Schematic structure diagram of the calibration tooling for assembling the two-stage planetary gear assembly of the present utility model;

[0044] Figure 9 Schematic cross-sectional structure diagram of the calibration tooling for assembling the two-stage planetary gear assembly of the present utility model;

[0045] Figure 10 Schematic assembly diagram of the sun gear during the assembly process of the two-stage planetary gear assembly of the present utility model;

[0046] Figure 11 Schematic structure diagram when the double planetary gear unit and the moving gear ring of the two-stage planetary gear assembly of the present utility model are assembled in place;

[0047] Figure 12 Schematic structure diagram when the double planetary gear unit and the fixed gear ring of the two-stage planetary gear assembly of the present utility model are assembled in place;

[0048] Figure 13 Schematic structure diagram of the cooperation between the fixed gear ring and the outer housing of the two-stage planetary gear assembly of the present utility model.

[0049] In the figure: outer housing 1, annular step 11, sun gear 2, fixed gear ring 3, moving gear ring 4, large gear 51, small gear 52, first bracket 531, mounting hole 532, second bracket 533, circular shaft end plate 54, extension column 55, positioning column 56, positioning shaft 57, positioning teeth 58, positioning blind hole 59, planetary shaft 510, circular support plate 61, positioning pin 62, mating hole 63, elasticity 64, bolt 65, through hole 66, chamfer K, output shaft 7, bearing 8, groove 91, rib 92, end cover 100. Detailed implementation mode

[0050] In order to make the content of the present utility model easier to be clearly understood, the following further details the present utility model according to specific embodiments and in conjunction with the accompanying drawings.

[0051] Embodiment 1:

[0052] Please refer to Figures 1 to 13 As shown, this embodiment provides a two-stage planetary gear assembly, including a double planetary gear unit, a sun gear 2, a fixed ring gear 3, a moving ring gear 4, an output shaft 7 connected to the moving ring gear 4, and a housing 1 for accommodating the double planetary gear unit, the sun gear 2, the fixed ring gear 3, and the moving ring gear 4. The moving ring gear 4 is rotationally fitted with the housing 1 through a bearing 8, and the fixed ring gear 3 is fixed in the housing 1.

[0053] Next, specifically, first is the double planetary gear unit, which includes a planetary gear carrier and at least three double gear sets evenly arranged in the circumferential direction in the planetary gear carrier. Here, it can be three double gear sets or four double gear sets. In this embodiment, in combination with the accompanying drawings, the case of designing three double gear sets is used for detailed description.

[0054] Furthermore, each double gear set includes a large gear 51 and a small gear 52 coaxially connected. Here, the outer diameters of the large gear 51 and the small gear 52 are different, and the outer diameter of the large gear 51 is greater than that of the small gear 52. In an optional implementation case, the large gear 51 and the small gear 52 of each double gear set are integrally formed by powder metallurgy. In this embodiment, the module of the large gear 51 and the small gear 52 is not greater than 2, preferably 0.15 to 0.7 (the smaller the module, the more teeth, and the more difficult it is to determine the meshing teeth with the naked eye).

[0055] The sun gear 2 is arranged inside the three large gears 51 and meshes with each large gear 51 at the same time, and the teeth of the three large gears 51 meshing with the sun gear 2 are evenly distributed along the circumferential direction of the sun gear 2. In this regard, considering the need for assembly, a mounting hole 532 suitable for the sun gear 2 to pass through is preset on the planetary gear carrier; the fixed ring gear 3 is arranged outside the three large gears 51 and meshes with each large gear 51 at the same time; the moving ring gear 4 is arranged outside the three small gears 52 and meshes with each small gear 52 at the same time. The external power input drives the sun gear 2 to rotate. The fixed ring gear 3 is fixed inside the housing 1. The double planetary gear unit rotates to drive the moving ring gear 4 to rotate and decelerate, and the output shaft 7 transmits the amplified torque after deceleration.

[0056] In more detail, the planetary gear support adopted in this embodiment includes a first support 531 and a second support 533 suitable for splicing and connecting; wherein the first support 531 and the second support 533 both include a circular shaft end plate 54 and a plurality of extension columns 55 connected to one shaft side end of the circular shaft end plate 54; the first support 531 and the extension columns 55 of the second support 533 are suitable for splicing and connecting. In an optional embodiment, the extension columns 55 of the first support 531 and the second support 533 are connected by rivets to increase axial tension and further improve stability and precision.

[0057] Furthermore, the circular shaft end plate 54 of the first bracket 531 is located on the side of the large gear 51 of each double gear set facing away from the small gear 52, and the circular shaft end plate 54 of the second bracket 533 is located on the side of the small gear 52 of each double gear set facing away from the large gear 51; and each double gear set is supported in the planetary gear bracket through the planetary shaft 510, and the two ends of the planetary shaft 510 are respectively fixedly connected to the circular shaft end plates 54 of the first bracket 531 and the second bracket 533. The two ends of the planetary shaft 510 here can be optionally interference fitted with the circular shaft end plates 54 of the first bracket 531 and the second bracket 533. The mounting hole 532 is arranged on the circumferential shaft end plate of the first bracket 531. Based on this, it is also necessary to explain that in order to improve the reliability and stability of the operating state of the sun gear 2, a positioning column 56 protruding toward the first bracket 531 is also provided on the circular shaft end plate 54 of the second bracket 533 for axially positioning the sun gear 2. The positioning column 56 and the sun gear 2 are in a rotationally matched manner, which does not affect the normal operation of the sun gear 2 and can also play a role in axially positioning it.

[0058] In an optional implementation, the movable gear ring 4 is connected to the circular shaft end plate 54 of the second bracket 533 through the positioning shaft 57. The design of the positioning shaft 57 here can prevent the movable gear ring 4 from having a large axial runout problem when running at high speed. Since the movable gear ring 4 is fixed together with the output shaft 7, the positioning shaft 57 can also be connected to the output shaft 7, which can also prevent the movable gear ring 4 from having a large axial runout problem. When the positioning column 56 and the positioning shaft 57 are designed at the same time, the positioning shaft 57 can be directly assembled with the positioning column 56. Here, it is sufficient to design an axial hole in the positioning column 56 for inserting the positioning shaft 57.

[0059] In addition, in order to enable the large gear 51 to better adapt to the fixed ring gear 3, and the small gear 52 to better adapt to the movable ring gear 4, at least part of the outer circular wall surface of the large gear 51 of each double gear set protrudes from the outer circular wall surface of the circular shaft end plate 54 of the first bracket 531; and at least part of the outer circular wall surface of the small gear 52 of each double gear set protrudes from the outer circular wall surface of the circular shaft end plate 54 of the second bracket 533.

[0060] Based on the above situation, it should be further explained that in order to unify the meshing transmission reference between the large gear 51 and the small gear 52 in each double gear set, a positioning tooth 58 is respectively formed on the large gear 51 and the small gear 52 in each double gear set, and the symmetric center line of the tooth profile of the positioning teeth 58 of the large gear 51 and the small gear 52 coincides with the positive projection along the axial direction. Based on this, the remaining teeth of the large gear 51 and the small gear 52 can be evenly arranged at equal angles in the circumferential direction according to the design parameters.

[0061] Based on the above structure, an identification part corresponding to the positioning tooth 58 is provided on the large gear 51 or the small gear 52 of each double gear set; in this way, the position of the positioning tooth 58 can be clearly found through the identification part. The design of the identification part here is mainly to improve the assembly accuracy and assembly efficiency of the double planetary gear unit with the fixed gear ring 3 and the moving gear ring 4.

[0062] In this regard, taking an optional implementation situation as an example in combination with the attached drawings,

[0063] The identification part is only provided on the large gear 51; regarding the shape of the identification part, it can be understood that it can be a structure arranged in a concave or convex manner on the shaft side end of the large gear 51 facing away from the small gear 52.

[0064] Regarding the specific design position of the identification part, the identification part is provided at the tooth root of the positioning tooth 58 of the large gear 51.

[0065] Next, it should be explained that for the two-stage planetary gear assembly of this embodiment, its specific assembly method includes the following steps:

[0066] Step S1: Assemble each double gear set with the planetary gear bracket in place. In this process, the three planetary shafts 510 are respectively passed through the double gear set, and the first bracket 531 and the second bracket 533 are respectively fixed at both ends of the three planetary shafts 510. In this embodiment, the first bracket 531 and the second bracket 533 are used to form the support for the double gear set, so that the double planetary gear unit can be formed as a whole to facilitate the assembly with the fixed gear ring 3 and the moving gear ring 4, improving the assembly efficiency and assembly accuracy.

[0067] Step S2: Use a calibration tooling to position the identification parts of each double gear set so that the identification parts of at least three double gear sets are evenly distributed in the circumferential direction, thereby calibrating the meshing positions of the large gear 51 and the small gear 52 of each double gear set with the fixed gear ring 3 and the moving gear ring 4 respectively.

[0068] Step S3: After the position correction of the large gears 51 and small gears 52 of each double-gear set with the fixed gear ring 3 and the moving gear ring 4 respectively, insert the sun gear 2 into the mounting hole 532 of the planetary gear bracket until the sun gear 2 meshes with each large gear 51 simultaneously, and then remove the alignment tooling.

[0069] During this process, since the large gears 51 of the three double-gear sets have corrected the positions of the positioning teeth 58 under the action of the alignment tooling, therefore, during the process of inserting the sun gear 2, the tooth surface meshing of the large gears 51 of the three double-gear sets with the sun gear 2 can enter the correct meshing angle simultaneously, with high assembly efficiency and high precision in meshing angle positioning. When the sun gear 2 is inserted, based on the relative angles between the large gears 51 of the three double-gear sets being determined, therefore, after removing the alignment tooling, although each large gear 51 in the three double-gear sets will rotate by a certain angle, the relative angles of the large gears 51 of the three double-gear sets remain unchanged, thus ensuring the accuracy of the assembly positions of the three double-gear sets with the moving gear ring 4 and the fixed gear ring 3, that is, the meshing points of the three small gears 52 with the moving gear ring 4 are evenly distributed along the circumferential direction. Similarly, the meshing points of the three large gears 51 with the fixed gear ring 3 are evenly distributed along the circumferential direction.

[0070] Step S4: Assemble the double-planet gear unit with the moving gear ring 4 and the fixed gear ring 3 in place in sequence. During this process, first assemble the double-planet gear unit with the moving gear ring 4. Since the moving gear ring 4 is assembled in the outer housing 1, insert the double-planet gear unit into the outer housing 1 so that the small gears 52 of the double-planet gear unit can mesh with the moving gear ring 4. At this time, during the insertion process, when the tooth profile surface of the small gear 52 contacts the tooth surface of the moving gear ring 4, appropriately adjust the insertion direction and angle of the double-planet gear unit, and the tooth surface meshing of the small gears 52 of the three double-gear sets with the moving gear ring 4 can enter the correct meshing angle simultaneously, with high assembly efficiency and high precision in meshing angle positioning.

[0071] For the assembly process of the fixed gear ring 3 and the outer housing 1, in terms of the axial direction of the fixed gear ring 3, there is an annular step 11 on the inner wall of the outer housing 1 for abutting against one axial end of the fixed gear ring 3. And in terms of the circumferential positioning of the fixed gear ring 3, it is achieved through at least one concave-convex fitting structure between the inner wall of the outer housing 1 and the fixed gear ring 3. The concave-convex fitting structure can be a groove 91 formed on the inner wall of the outer housing 1 and a rib 92 formed on the outer side wall of the fixed gear ring 3, thereby reliably fixing the fixed gear ring 3 in the outer housing 1 and preventing it from rotating with the operation of the three double-gear sets.

[0072] It is also necessary to note here that for the entire two-stage planetary gear assembly involved in this embodiment, it further includes an end cover 100 that cooperates with the outer housing 1. After the assembly of the fixed ring gear 3 is completed in step S4, before the end cover 100 is assembled, an appropriate amount of lubricating grease can be injected into the gaps between the three double-gear sets, between the planet gears and the large ring gear 51 of the ring gear and the fixed ring gear 3, and between the pinion gear 52 and the moving ring gear 4. After the end cover 100 is assembled, a running-in process is carried out for a certain period of time to evenly distribute the lubricating grease on the meshing tooth surfaces.

[0073] In summary, for the two-stage planetary gear assembly of this embodiment, through the positioning tooth 58 matching recognition parts designed on the large gear 51 and the pinion gear 52 in each double-gear set, the meshing positions with the fixed ring gear 3 and the moving ring gear 4 can be corrected by the calibration tooling, so as to ensure that the meshing positions of the pinion gears 52 corresponding to the multiple double-gear sets with the moving ring gear 4 are evenly arranged in the circumferential direction. Thus, the multiple pinion gears 52 generate balanced rotational acting forces on the moving ring gear 4, preventing the moving ring gear 4 from being subjected to uneven loading, thereby improving the transmission smoothness of the moving ring gear 4 and reducing the transmission noise. For the assembly process of the two-stage planetary gear assembly of this embodiment, after the double planetary gear unit is assembled with the sun gear 2, it is integrally assembled with the moving ring gear 4 and the fixed ring gear 3. This not only has a high assembly efficiency but also can avoid the problem of low installation accuracy and the need for repeated adjustment caused by installing each double-gear set separately.

[0074] Embodiment 2:

[0075] Please refer to Figures 1 to 13 As shown, based on the two-stage planetary gear assembly of Embodiment 1, this embodiment provides a calibration tooling for assembling the two-stage planetary gear assembly, which is applicable to assembling the two-stage planetary gear assembly of Embodiment 1. The calibration tooling includes: an annular support plate 61 and a plurality of positioning parts provided on the annular support plate 61 for corresponding to the recognition parts of each double-gear set; the plurality of positioning parts are evenly arranged in the circumferential direction.

[0076] Here, taking the case of using three double-gear sets in combination with a two-stage planetary gear assembly as an example, it is only necessary to design three positioning portions on the annular support plate 61. At this time, the central angle formed by every two adjacent positioning portions among these three positioning portions is 120° (when four positioning portions are designed corresponding to four double-gear sets, the central angle formed by every two adjacent positioning portions is 90°; that is to say, as long as the sum of the central angles formed by every two adjacent positioning portions among multiple positioning portions is 360°, the usage requirements of this embodiment are met). Accordingly, when the three positioning portions respectively correspond to the identification portions of each double-gear set, the positioning teeth 58 on the large gears 51 of the three double-gear sets form an equilateral triangle structure, that is, the central angle formed by every two adjacent positioning teeth 58 is 120°. In this way, when the small gears 52 of the three double-gear sets are simultaneously engaged with the moving gear ring 4, the three small gears 52 can form a balanced acting force on the moving gear ring 4, so that the moving gear ring 4 is uniformly stressed during operation, thereby improving the reliability and stability of the operation of the moving gear ring 4.

[0077] In this regard, taking an optional implementation case as an example with reference to the accompanying drawings, the identification portion is a positioning blind hole 59 provided on the large gear 51 and / or the small gear 52; the positioning portion is a positioning pin 62 adapted to be inserted into the positioning blind hole 59; and an adapter hole 63 for slidingly mating with the positioning pin 62 is provided on the annular support plate 61. Here, in order to improve the convenience of inserting the positioning pin 62 into the positioning blind hole 59, a chamfer K can be provided at the opening of the positioning blind hole 59.

[0078] On the basis of the above structure, further, an elastic member 64 is provided between the positioning pin 62 and the adapter hole 63, so that the positioning pin 62 is adapted to slide relative to the adapter hole 63 to enter and exit the positioning blind hole 59. The elastic member 64 here can optionally be a spring. For the positioning pin 62, it is preferably in a T shape, so that one end of it always remains in the adapter hole 63, and the problem that the positioning pin 62 is disengaged from the adapter hole 63 will not occur. For the adapter hole 63 here, it can be a through hole extending along the axial direction of the annular support plate 61. The end of the adapter hole 63 facing away from the large gear 51 has a large-diameter opening for facilitating the installation of the positioning pin 62 and the elastic member 64. Here, a bolt 65 can be used to form a stop for one end of the elastic member 64, and the end of the adapter hole 63 facing the large gear 51 has a small-diameter opening for facilitating the positioning pin 62 to partially extend out of the adapter hole 63 to form a positioning fit with the positioning hole on the large gear 51.

[0079] In addition, it should be noted that the annular support plate 61 has a through hole 66 adapted for the sun gear 2 to pass through. That is to say, the cooperation between the sun gear 2 and the multiple large gears 51 is achieved when the positioning blind hole 59 of the large gear 51 and the positioning pin 62 are assembled in place. That is, the sun gear 2 is installed on the premise that the positions of the positioning teeth 58 of the multiple large gears 51 are accurately positioned by the calibration tooling. At this time, not only can the reliable meshing between the sun gear 2 and the multiple large gears 51 be quickly achieved, but also the accuracy of the meshing point position formed by the large gear 51 and the sun gear 2 can be improved.

[0080] Regarding the calibration tooling of this embodiment, its specific usage process is as follows:

[0081] The double planetary gear unit is placed on the calibration tooling so that the end face of the large gear 51 provided with the positioning blind hole 59 faces the end of the annular support plate 61 provided with the positioning pin 62. At this time, when the positioning blind hole 59 of the large gear 51 is not aligned with the positioning pin 62, the axial end face of the large gear 51 will form a pressing force on the positioning pin 62, causing the positioning pin 62 to be pressed and compress the elastic member 64, thereby enabling the entire positioning pin 62 to be received in the mating hole 63. At this time, manually rotate the large gears 51 of the three double gear sets in sequence. When the positioning blind hole 59 of each large gear 51 is aligned with the positioning pin 62 of the annular support plate 61, under the thrust of the elastic member 64, the positioning pin 62 enters the positioning hole. At this time, the calibration tooling completes the identification and positioning process of the positioning teeth 58 of the large gears 51 of the double gear set.

[0082] The above specific embodiments have further detailed the purpose, technical solution, and beneficial effects of the present invention. It should be understood that the above are only specific embodiments of the present invention and are not used to limit the present invention. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention shall be included within the protection scope of the present invention.

[0083] In the description of the present invention, it should be understood that the terms indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation to the present invention.

[0084] In the present utility model, unless otherwise clearly defined and limited, terms such as "installation", "connection", "linkage", "fixation", etc. shall be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or an integral one; it may be a mechanical connection or an electrical connection; it may be a direct connection or an indirect connection through an intermediate medium, and it may be the communication inside two elements or the interaction relationship between two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present utility model can be understood according to specific circumstances.

[0085] In the description of the present utility model, it should be noted that the orientation or positional relationship indicated by terms such as "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings, or the orientation or positional relationship in which the utility model product is usually placed during use. It is only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation to the present utility model. In addition, terms such as "first", "second", "third", etc. are only used for distinguishing descriptions and cannot be understood as indicating or implying relative importance.

[0086] In addition, terms such as "horizontal", "vertical", "overhanging", etc. do not mean that the components are required to be absolutely horizontal or overhanging, but may be slightly inclined. For example, "horizontal" only means that its direction is more horizontal relative to "vertical", and does not mean that the structure must be completely horizontal, but may be slightly inclined.

[0087] In the present utility model, unless otherwise clearly defined and limited, the first feature being above or below the second feature may include the direct contact between the first and second features, or may include the situation where the first and second features are not in direct contact but in contact through additional features therebetween. Moreover, the first feature being above, over and on the second feature includes that the first feature is directly above and obliquely above the second feature, or merely indicates that the horizontal height of the first feature is higher than that of the second feature. The first feature being below, under and beneath the second feature includes that the first feature is directly below and obliquely below the second feature, or merely indicates that the horizontal height of the first feature is lower than that of the second feature.

Claims

1. A two-stage planetary gear assembly, characterized in that: include: A double planetary gear unit, comprising a planetary gear carrier and at least three double gear sets arranged evenly in the circumferential direction in the planetary gear carrier; each of the double gear sets comprises a large gear and a small gear connected coaxially; a positioning tooth is formed on the large gear and the small gear in each double gear set respectively, and the symmetrical center lines of the tooth profiles of the positioning teeth of the large gear and the small gear coincide with the orthographic projections along the axial direction; an identification portion corresponding to the positioning tooth is provided on the large gear or the small gear of each double gear set; A sun gear, which is arranged on the inner side of at least three large gears and meshes with each large gear at the same time, and the teeth of at least three large gears meshing with the sun gear are evenly distributed along the circumferential direction of the sun gear; the planetary gear support is preset with a mounting hole suitable for the sun gear to pass through; A fixed gear ring, which is arranged outside at least three large gears and meshes with each large gear at the same time; The movable ring gear is arranged outside at least three pinion gears and meshes with each pinion gear at the same time.

2. The double-stage planetary gear assembly according to claim 1, characterized in that: The identification part is arranged on the large gear; and The identification part is a structure arranged on the shaft side end of the large gear facing away from the small gear and arranged in a concave or convex manner.

3. The double-stage planetary gear assembly according to claim 2, characterized in that: The identification part is arranged at the tooth root of the positioning tooth of the large gear.

4. The double-stage planetary gear assembly according to any one of claims 1 to 3, characterized in that: The planetary gear support comprises a first support and a second support suitable for being spliced ​​together; wherein The first bracket and the second bracket each include a circular shaft end plate and a plurality of extension columns connected to one shaft side end of the circular shaft end plate; The extension columns of the first bracket and the second bracket are suitable for being assembled and connected.

5. The double-stage planetary gear assembly according to claim 4, characterized in that: The circular shaft end plate of the first bracket is located on the side of the large gear of each double gear set facing away from the small gear, and the circular shaft end plate of the second bracket is located on the side of the small gear of each double gear set facing away from the large gear; as well as Each of the double gear sets is supported in the planetary gear support through a planetary shaft, and two ends of the planetary shaft are respectively fixedly connected to the circular shaft end plates of the first support and the second support.

6. The double-stage planetary gear assembly according to claim 5, characterized in that: The movable gear ring is connected to the circular shaft end plate of the second bracket through a positioning shaft.

7. The double-stage planetary gear assembly according to claim 5, characterized in that: The circular shaft end plate of the second bracket is also provided with a positioning column protruding toward the first bracket and used for axial positioning of the sun gear.

8. The double-stage planetary gear assembly according to claim 5, characterized in that: At least part of the outer circumferential wall surface of the large gear of each of the double gear sets protrudes from the outer circumferential wall surface of the circular shaft end plate of the first bracket; as well as At least part of the outer circumferential wall surface of the pinion of each of the dual gear sets protrudes from the outer circumferential wall surface of the circular shaft end plate of the second bracket.

9. A calibration tool for assembling a double-stage planetary gear assembly, characterized in that: Suitable for assembling a double-stage planetary gear assembly as claimed in any one of claims 1 to 8, comprising: a circular ring-shaped support plate and a plurality of positioning parts provided on the circular ring-shaped support plate for corresponding to the identification parts of each double gear set; The plurality of positioning portions are evenly arranged along the circumferential direction.

10. The calibration tool for assembling a double-stage planetary gear assembly according to claim 9, characterized in that: The identification part is a positioning blind hole provided on the large gear and / or the small gear; The positioning portion is a positioning pin suitable for being inserted into the positioning blind hole; the annular support plate is provided with an adapter hole that is slidably matched with the positioning pin; An elastic member is provided between the positioning pin and the matching hole, so that the positioning pin is suitable for sliding relative to the matching hole to enter and exit the positioning blind hole.

11. The calibration tool for assembling a double-stage planetary gear assembly according to claim 9 or 10, characterized in that: The annular support plate is provided with a through hole suitable for the sun gear to pass through.

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