Double-input-mode speed reducer

Abstract

The utility model discloses a double-input-mode speed reducer, which relates to the technical field of speed reducers, and comprises a first input shaft structure, a first planetary gear train structure, a planetary speed reducer structure and a second planetary gear train structure, and the first input shaft structure comprises a first input shaft; the first planetary gear train structure comprises a first sun gear shaft, a first planet gear, a first planet carrier and a gear ring, the first sun gear shaft comprises a first insertion shaft and a sun gear, and a first center hole is formed in one end of the first planet carrier; the planetary reducer structure comprises a planetary reducer and a first cylindrical gear, and the first cylindrical gear is in meshing transmission with the gear ring; the second planetary gear train structure comprises a second sun gear shaft, a second planet gear, a box body and a second planet carrier, the second sun gear shaft comprises a second insertion shaft and a second sun gear, and the second planet gear is suitable for being in meshing transmission with an inner gear ring of the second planet carrier. Through switching of two speed ratio modes, the working efficiency of the speed reducer can be improved, and the reliability is higher.

Description

Technical Field

[0001] The utility model relates to the technical field of reducers, and in particular to a dual-input mode reducer. Background Art

[0002] At present, the planetary reducers used in engineering machinery are mainly single-speed ratio, that is, there is only one transmission speed ratio. During the working process, the reducer itself does not have the function of changing speed. For example, for the winch reducer used in cranes, during the use of the empty hook of the crane, customers hope to have a faster operating speed to improve work efficiency. When the crane is lifting, the reducer needs to run at a low speed for safety reasons. Most of the existing technologies adjust the speed by controlling the motor flow. Due to the flow limit of the hydraulic system, the speed adjustment range is narrow and cannot meet the customer's high-efficiency operation needs.

[0003] In response to market demand, some companies have developed planetary reducers. Since planetary gear transmission is a coaxial transmission, the structure uses several identical planetary gears evenly distributed around the center wheel to share the load. It also reasonably uses the high internal meshing load-bearing capacity and internal gear space volume to reduce the size, make the structure compact, and achieve high load-bearing capacity.

[0004] However, the current planetary reducer has a single speed ratio, which is difficult to meet the actual working conditions. Some machines have high reliability requirements during operation and are not allowed to shut down, such as boiler blowers, cement mixers, etc. Once a power outage occurs, it may cause huge losses. Utility Model Content

[0005] The main purpose of the utility model is to provide a dual-input mode reducer, aiming to solve the technical problems of the existing reducer with a single speed ratio and low reliability.

[0006] In order to achieve the above object, the utility model proposes a dual-input mode reducer, comprising:

[0007] The first input shaft structure comprises a first input shaft, wherein a first stepped hole penetrating along an axial direction is provided at the center of the first input shaft;

[0008] The first planetary gear train structure comprises a first sun gear shaft arranged horizontally, a plurality of first planetary gears evenly distributed and meshed on the outer circumference of the first sun gear shaft, a first planet carrier supporting and mounting the plurality of the first planetary gears, and a gear ring meshing and driving with the plurality of the first planetary gears, the first sun gear shaft comprises a first insertion shaft suitable for being inserted into the first stepped hole and a sun gear coaxially connected to an end of the first insertion shaft away from the first input shaft, and the sun gear is located at the center of the gear ring, and a first center hole is formed at an end of the first planet carrier away from the first insertion shaft;

[0009] A planetary reducer structure, comprising a planetary reducer arranged in parallel on one side of the first input shaft and a first cylindrical gear mounted on the output shaft of the planetary reducer, wherein the first cylindrical gear is meshed with the outer gear ring of the gear ring for transmission;

[0010] The second planetary gear system structure includes a horizontally arranged second sun gear shaft, a plurality of second planetary gears evenly distributed and meshed on the outer circumference of the second sun gear shaft, a housing for supporting and mounting the plurality of second planetary gears, and a second planetary carrier meshed with the plurality of second planetary gears for transmission, the second sun gear shaft includes a second insertion shaft suitable for being inserted into the first center hole and a second sun gear coaxially connected to an end of the second insertion shaft away from the first planetary carrier, and the second planetary gear is suitable for meshing with the inner gear ring of the second planetary carrier for transmission.

[0011] Optionally, the first input shaft structure also includes a front flange, a first bearing sleeved between the front flange and the first input shaft, a first shaft retaining spring clamped on the first input shaft, and a flange end cover connected to the end face of the front flange, the end face of the first bearing on one side close to the first sun gear shaft abuts against the first protrusion of the first input shaft, the lower end face on the other side is abutted by the first shaft retaining spring, and the top end face on the other side is abutted against the upper end face of the first bearing through the flange end cover.

[0012] Optionally, the first planetary gear train structure also includes a second bearing embedded between the first planetary carrier and the ring gear, a second shaft clamping ring clamped on the first planetary carrier, and a first hole clamping ring clamped on the inner wall of the ring gear; the upper and lower parts of the left end face of the second bearing are limited by the first hole clamping ring and the second shaft clamping ring respectively, and the right end face of the second bearing abuts against the end face of the inner ring gear of the ring gear.

[0013] Optionally, the planetary reducer structure also includes a motor flange mounted on the planetary reducer, a motor flange cover connected to the end of the motor flange, and a fifth bearing sleeved on the output shaft of the planetary reducer. The first cylindrical gear is located inside the motor flange, and the first cylindrical gear and the fifth bearing are fixed by a baffle.

[0014] Optionally, a sixth bearing and a seventh bearing are respectively sleeved on the stepped shafts at both ends of the gear ring, and one end of the sixth bearing away from the gear ring abuts against the motor flange cover, and one end of the seventh bearing away from the gear ring abuts against the inner wall of the motor flange.

[0015] Optionally, the second planetary gear train structure further includes a case cover connected to one end of the case body via a second locking member, and the case cover is located on a side close to the first planet carrier, and an outer diameter of the case cover is greater than an outer diameter of the case body.

[0016] Optionally, a third bearing and a fourth bearing are respectively installed at both ends between the casing and the second planetary carrier, and both ends of the third bearing are respectively abutted against the casing cover and the inner walls of the second planetary carrier, and both ends of the fourth bearing are respectively abutted against the inner walls of the casing and the second planetary carrier.

[0017] Optionally, a first oil seal is provided between the first input shaft and a side of the flange end cover away from the first planetary gear train structure, and a second oil seal is provided between the second planetary carrier and a side of the housing away from the first input shaft structure.

[0018] Optionally, a flat key is provided on the output shaft of the planetary reducer, a keyway corresponding to the position of the flat key is provided on the inner hole of the first cylindrical gear, and the first cylindrical gear and the output shaft of the planetary reducer are fixedly connected via the flat key.

[0019] Optionally, a plurality of second planetary gear shafts evenly distributed horizontally are arranged on the inner wall of the box body, and the second planetary gear is passed through the second planetary gear shafts so that the second planetary gear partly extends out of the box body.

[0020] Compared with the prior art, the beneficial effects of the utility model are as follows:

[0021] In the technical solution of the utility model, the dual-input mode reducer is composed of a first input shaft structure, a first planetary gear train structure, a planetary reducer structure and a second planetary gear train structure. The first insertion shaft of the first sun gear shaft is horizontally inserted into the first stepped hole of the first input shaft, thereby realizing the assembly and power transmission between the first input shaft structure and the first planetary gear train structure; the first cylindrical gear of the planetary reducer structure and the ring gear of the first planetary gear train structure are meshed for transmission, thereby realizing the assembly and power transmission between the planetary reducer structure and the first planetary gear train structure; the axial hole connection between the first planetary carrier of the first planetary gear train structure and the second sun gear shaft of the second planetary gear train structure is realized, thereby realizing the assembly and power transmission between the first planetary gear train structure and the second planetary gear train structure; thus, the input speed ratio is changed through the dual input adjustment of the first input shaft structure and the planetary reducer structure, which can meet the actual working conditions, improve the working efficiency of the reducer, and have higher reliability during operation. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] In order to more clearly illustrate the embodiments of the utility model or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the utility model. For ordinary technicians in this field, other drawings can be obtained based on the structures shown in these drawings without paying creative work.

[0023] Figure 1 It is a schematic diagram of the internal structure of an embodiment of a dual-input mode reducer provided in an embodiment of the utility model;

[0024] Figure 2 It is a schematic diagram of the main structure of an embodiment of a dual-input mode reducer provided in an embodiment of the utility model;

[0025] Figure 3 It is a left-side structural schematic diagram of a dual-input mode reducer provided in an embodiment of the utility model;

[0026] Figure 4 It is a right side structural schematic diagram of the dual-input mode reducer provided in an embodiment of the utility model;

[0027] Figure 5 It is a schematic diagram of the assembly structure of the first input shaft structure and the first planetary gear train structure in the embodiment of the utility model;

[0028] Figure 6 It is a schematic diagram of the assembly structure of the first planetary gear train structure and the planetary reducer structure in the embodiment of the utility model;

[0029] Figure 7 This is a schematic diagram of the structure of the second planetary gear train in the embodiment of the utility model;

[0030] Figure 8 This is a schematic diagram of the assembly structure of the first input shaft and the first sun gear shaft in the embodiment of the utility model;

[0031] Description of reference numerals:

[0032] 1-First input shaft structure;

[0033] 11-front flange; 12-first input shaft; 121-first stepped hole; 122-first convex opening; 123-first slot; 13-first bearing; 14-first shaft retaining ring; 15-flange end cover; 16-first oil seal; 17-first locking member;

[0034] 2-First planetary gear train structure;

[0035] 21-first sun gear shaft; 211-first insertion shaft; 212-first sun gear; 22-first planet carrier; 221-first center hole; 23-first planet gear; 24-gear ring; 241-inner gear ring; 242-outer gear ring; 25-second bearing; 26-second shaft retaining ring; 27-first hole retaining ring;

[0036] 3- Second planetary gear train structure;

[0037] 31-second sun gear shaft; 311-second insertion shaft; 312-second sun gear; 32-second planet carrier; 33-second planet gear; 331-second planet gear shaft; 34-box; 35-box cover; 36-second locking member; 37-third bearing; 38-fourth bearing; 39-second oil seal;

[0038] 4-Planetary reducer structure;

[0039] 41-planetary reducer; 42-first cylindrical gear; 43-motor flange; 44-motor flange cover; 45-fifth bearing; 46-baffle; 47-sixth bearing; 48-seventh bearing; 49-flat key. DETAILED DESCRIPTION

[0040] The following will be combined with the drawings in the embodiments of the utility model to clearly and completely describe the technical solutions in the embodiments of the utility model. Obviously, the described embodiments are only part of the embodiments of the utility model, not all of the embodiments. Based on the embodiments of the utility model, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the utility model.

[0041] It should be noted that if the embodiments of the present invention involve directional indications (such as up, down, left, right, front, back...), the directional indications are only used to explain the relative position relationship, movement status, etc. between the components under a certain specific posture (as shown in the accompanying drawings). If the specific posture changes, the directional indication will also change accordingly.

[0042] In addition, if there are descriptions involving "first", "second", etc. in the embodiments of the utility model, the descriptions of "first", "second", etc. are only used for descriptive purposes and cannot be understood as indicating or suggesting their relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of the features. In addition, the technical solutions between the various embodiments can be combined with each other, but they must be based on the ability of ordinary technicians in the field to implement them. When the combination of technical solutions is contradictory or cannot be implemented, it should be deemed that such a combination of technical solutions does not exist and is not within the scope of protection required by the utility model.

[0043] Currently, the planetary reducers on the market have a single speed ratio, which is difficult to meet the actual working conditions. Some machines have high reliability requirements during operation and are not allowed to stop, such as boiler blowers, cement mixers, etc. Once a power outage causes a shutdown, it may cause huge losses.

[0044] In order to solve the above technical problems, the utility model provides a dual-input mode reducer. Figure 1-4 The figure shows an embodiment of the dual-input mode reducer provided by the utility model.

[0045] See also Figure 1 , 5 As shown, in a specific solution of the utility model, the dual-input mode reducer includes a first input shaft structure 1, a first planetary gear train structure 2, a planetary reducer structure 4 and a second planetary gear train structure 3, wherein:

[0046] The first input shaft structure 1 includes a first input shaft 12. A first stepped hole 121 is opened in the center of the first input shaft 12 and penetrates along the axial direction. The first input shaft 12 receives external power input and a first stepped hole 121 is opened in the center of the first input shaft 12. The first stepped hole 121 is connected to other components to transmit power.

[0047] The first planetary gear train structure 2 includes a first sun gear shaft 21, a first planet carrier 22, a first planet gear 23 and a ring gear 24, wherein:

[0048] The first sun gear shaft 21 is arranged horizontally, and multiple first planetary gears 23 are evenly distributed and meshed on the outer circumference of the first sun gear shaft 21. The first planetary carrier 22 supports and installs multiple first planetary gears 23, and the ring gear 24 meshes with the multiple first planetary gears 23 for transmission. The first sun gear shaft 21 includes a first insertion shaft 211 and a sun gear 212. The first insertion shaft 211 is suitable for being inserted in the first stepped hole 121. The sun gear 212 is coaxially connected to the end of the first insertion shaft 211 away from the first input shaft 12, and the sun gear 212 is located at the center of the ring gear 24. The first planetary carrier 22 is provided with a first center hole 221 at one end away from the first insertion shaft 211.

[0049] See also Figure 6 As shown, the planetary reducer structure 4 includes a planetary reducer 41 and a first cylindrical gear 42. The planetary reducer 41 is arranged in parallel on one side of the first input shaft 12. The first cylindrical gear 42 is installed on the output shaft of the planetary reducer 41. The first cylindrical gear 42 is meshed with the outer ring gear 242 of the ring gear 24 for transmission.

[0050] See also Figure 7As shown, the second planetary gear system structure 3 includes a second sun gear shaft 31, a second planetary carrier 32, a second planetary gear 33 and a box body 34. The second sun gear shaft 31 is horizontally arranged, and a plurality of second planetary gears 33 are evenly distributed and meshed with the outer circumference of the second sun gear shaft 31. The box body 34 supports and installs a plurality of second planetary gears 33. The second planetary carrier 32 meshes with the plurality of second planetary gears 33 for transmission. The second sun gear shaft 31 includes a second insertion shaft 311 and a second sun gear 312. The second insertion shaft 311 is suitable for being inserted in the first center hole 221. The second sun gear 312 is coaxially connected to the end of the second insertion shaft 311 away from the first planetary carrier 22, and the second planetary gear 33 is suitable for meshing with the inner gear ring of the second planetary carrier 32 for transmission.

[0051] In the present embodiment, the first insertion shaft 211 of the first sun gear shaft 21 is horizontally inserted into the first stepped hole 121 of the first input shaft 12, thereby realizing the assembly and power transmission between the first input shaft structure 1 and the first planetary gear train structure 2; the first cylindrical gear 42 of the planetary reducer structure 4 is meshed with the ring gear 24 of the first planetary gear train structure 2, thereby realizing the assembly and power transmission between the planetary reducer structure 4 and the first planetary gear train structure 2; the axial hole connection between the first planetary carrier 22 of the first planetary gear train structure 2 and the second sun gear shaft 31 of the second planetary gear train structure 3 is realized, thereby realizing the assembly and power transmission between the first planetary gear train structure 2 and the second planetary gear train structure 3; thus, through the dual input adjustment of the first input shaft structure 1 and the planetary reducer structure 4, the input speed ratio is changed, which can meet the actual working conditions, improve the working efficiency of the reducer, and have higher reliability during operation.

[0052] Furthermore, the first input shaft structure 1 further includes a front flange 11, a first bearing 13, a first shaft retaining spring 14 and a flange end cover 15, wherein:

[0053] The first bearing 13 is sleeved between the front flange 11 and the first input shaft 12. The first shaft is clamped on the first input shaft 12 by a retaining spring 14. The flange end cover 15 is connected to the end face of the front flange 11. The end face of the first bearing 13 on one side close to the first sun gear shaft 21 abuts against the first protrusion 122 of the first input shaft 12, and the lower end face on the other side is abutted by the first shaft retaining spring 14, and the top end face on the other side abuts against the upper end face of the first bearing 13 through the flange end cover 15.

[0054] Specifically, see Figure 5 , 6 As shown in FIG. 8 , in a specific solution of the utility model, the first input shaft structure 1 is composed of a front flange 11, a first bearing 13, a first shaft retaining ring 14 and a flange end cover 15. The front flange 11 is provided with an inner stop at one end close to the first planetary gear train structure 2. The first input shaft 12 is passed through

[0055] The first bearing 13 is rotatably mounted on a side of the front flange 11 close to the first planetary gear train structure 2, wherein the axial right end top surface limit of the first bearing 13 is completed by the inner stop of the front flange 11, and the axial right end bottom surface limit of the first bearing 13 is completed by the first protrusion 122 of the first input shaft 12. A first retaining groove 123 suitable for accommodating a first shaft retaining spring 14 is provided on the outer circumference of the left end of the first input shaft 12 close to the first bearing 13. The left end top surface of the first bearing 13 is also abutted by the end shaft portion of the flange end cover 15, and the flange end cover 15 is fixedly connected to the left end surface of the front flange 11 by the first locking member 17, thereby limiting the axial movement of the first bearing 13.

[0056] Furthermore, the first planetary gear train structure 2 further includes a second bearing 25, a second shaft clamping ring 26 and a first hole clamping ring 27, wherein:

[0057] The second bearing 25 is embedded and installed between the first planetary carrier 22 and the ring gear 24. The second shaft is clamped on the first planetary carrier 22 with a clamping ring 26, and the first hole is clamped on the inner wall of the ring gear 24 with a clamping ring 27. The upper and lower parts of the left end face of the second bearing 25 are respectively limited by the first hole clamping ring 27 and the second shaft clamping ring 26, and the right end face of the second bearing 25 abuts against the end face of the inner ring gear 241 of the ring gear 24.

[0058] Specifically, see Figure 5 , 6As shown, in the specific scheme of the utility model, the first planetary gear system structure 2 is composed of a first sun gear shaft 21, a first planet carrier 22, a first planetary gear 23, a gear ring 24, a second bearing 25, a second shaft clamp 26 and a first hole clamp 27. A plurality of evenly distributed first planetary gears 23 are meshed on the outer circumference of the first sun gear shaft 21, and the first planetary gears 23 are horizontally rotatably connected through the first planet carrier 22. A plurality of evenly distributed pin shaft holes are opened on the first planet carrier 22, and pin shafts penetrating the first planetary gears 23 are installed in the pin shaft holes, so that the first planetary gears 23 are rotatably connected on the first planet carrier 22, and the top of the first planetary gear 23 is meshed with the inner gear ring of the gear ring 24 through the opening on the first planet carrier 22 for transmission, and the bottom of the first planetary gear 23 is connected to the first sun gear shaft 21 inside the first planet carrier 22. Meshing transmission; considering the coaxial assembly of the first planetary carrier 22 and the ring gear 24, a second bearing 25 is assembled between the first planetary carrier 22 and the left end of the ring gear 24, the bottom surface of the right end of the second bearing 25 is limited by the outer step of the first planetary carrier 22, and the top surface of the right end of the second bearing 25 is limited by the inner step of the ring gear 24. A groove suitable for placing the second shaft clamping ring 26 is opened on the outer circumferential surface of the first planetary carrier 22 near the left end of the second bearing 25, and a groove suitable for placing the first hole clamping ring 27 is opened on the inner wall circumferential surface of the ring gear 24 near the left end of the second bearing 25. The bottom surface of the left end of the second bearing 25 is axially limited by the second shaft clamping ring 26, and the top surface of the left end of the second bearing 25 is axially limited by the first hole clamping ring 27; thereby, the axial limitation of the second bearing 25 is achieved, thereby preventing the axial movement of the second bearing 25.

[0059] Furthermore, the planetary reducer structure 4 further includes a motor flange 43, a motor flange cover 44 and a fifth bearing 45, wherein:

[0060] The motor flange 43 is installed on the planetary reducer 41, the motor flange cover 44 is connected to the end of the motor flange 43, the fifth bearing 45 is sleeved on the output shaft of the planetary reducer 41, the first cylindrical gear 42 is located inside the motor flange 43, and the first cylindrical gear 42 and the fifth bearing 45 are limited and fixed by a baffle 46.

[0061] Specifically, see Figure 6As shown, in the specific scheme of the utility model, the planetary reducer structure 4 is composed of a planetary reducer 41, a first cylindrical gear 42, a motor flange 43, a motor flange cover 44 and a fifth bearing 45. The motor flange 43 is installed on the shell end face of the planetary reducer 41, so that the output shaft of the planetary reducer 41 is located in the motor flange 43, and the first cylindrical gear 42 is installed on the output shaft of the planetary reducer 41, and the first cylindrical gear 42 is meshed and connected with the outer ring gear 242 of the ring gear 24. Considering the stability of the meshing transmission of the first cylindrical gear 42, the right end of the output shaft of the planetary reducer 41 also needs to be supported and rotated by the fifth bearing 45 and the motor flange cover 44, wherein the motor flange cover 44 is connected to the end face of the motor flange 43 by a bolt connector, and the inner wall of the motor flange cover 44 is also provided with a mounting groove suitable for placing the fifth bearing 45, and the fifth bearing 45 is rotatably installed on the output shaft of the planetary reducer 41, thereby supporting the stable meshing of the first cylindrical gear 42.

[0062] Furthermore, a sixth bearing 47 and a seventh bearing 48 are respectively sleeved on the stepped shafts at both ends of the gear ring 24, and one end of the sixth bearing 47 away from the gear ring 24 abuts against the motor flange cover 44, and one end of the seventh bearing 48 away from the gear ring 24 abuts against the inner wall of the motor flange 43.

[0063] Specifically, see Figure 6 As shown, in the specific scheme of the utility model, considering the stability of the meshing transmission of the gear ring 24, a sixth bearing 47 and a seventh bearing 48 are respectively sleeved on the stepped shafts at both ends of the gear ring 24, the left end face of the sixth bearing 47 is limited and fixed by the gear ring 24, the right end face of the sixth bearing 47 is limited by the stopper of the motor flange cover 44, the right end face of the seventh bearing 48 is limited and fixed by the gear ring 24, and the left end face of the seventh bearing 48 is limited by another stopper of the motor flange 43.

[0064] Furthermore, the second planetary gear train structure 3 also includes a box cover 35 , which is connected to one end of the box body 34 through a second locking member 36 , and is located on a side close to the first planetary carrier 22 , and an outer diameter of the box cover 35 is greater than an outer diameter of the box body 34 .

[0065] Specifically, see Figure 7 As shown, in a specific solution of the present invention, the box cover 35 is connected to one end of the box body 34 through a second locking member 36 , and the box cover 35 is located inside the second planet carrier 32 .

[0066] Furthermore, a third bearing 37 and a fourth bearing 38 are respectively installed at both ends between the box body 34 and the second planetary carrier 32, and both ends of the third bearing 37 are respectively abutted against the inner walls of the box cover 35 and the second planetary carrier 32, and both ends of the fourth bearing 38 are respectively abutted against the inner walls of the box body 34 and the second planetary carrier 32.

[0067] Specifically, see Figure 7 As shown, in the specific scheme of the utility model, since the second planetary carrier 32 is meshed with the second planetary gear 33 in the box body 34 for transmission, in order to ensure the smooth movement of the second planetary gear train structure 3, a third bearing 37 and a fourth bearing 38 are respectively installed on the box body 34 at both ends of the second planetary gear 33, wherein the two ends of the third bearing 37 are respectively abutted against the inner wall of the box cover 35 and the second planetary carrier 32, so that the third bearing 37 does not move axially, and the two ends of the fourth bearing 38 are respectively abutted against the inner wall of the box body 34 and the second planetary carrier 32, so that the fourth bearing 38 does not move axially.

[0068] Furthermore, a first oil seal 16 is provided between the first input shaft 12 and the side of the flange end cover 15 away from the first planetary gear train structure 2 , and a second oil seal 39 is provided between the second planet carrier 32 and the side of the housing 34 away from the first input shaft structure 1 .

[0069] Specifically, see Figure 5 As shown, in a specific scheme of the utility model, a first oil seal 16 is arranged between the first input shaft 12 and the side of the flange end cover 15 away from the first planetary gear train structure 2, and a second oil seal 39 is arranged between the second planetary carrier 32 and the side of the housing 34 away from the first input shaft structure 1. The first oil seal 16 and the second oil seal 39 can effectively seal the lubricating oil inside the mechanical equipment to prevent the lubricating oil from leaking to the outside of the equipment, thereby protecting the mechanical bearings of the equipment and reducing mechanical failures.

[0070] Furthermore, a flat key 49 is provided on the output shaft of the planetary reducer 41 , and a keyway corresponding to the position of the flat key 49 is provided on the inner hole of the first cylindrical gear 42 . The first cylindrical gear 42 and the output shaft of the planetary reducer 41 are fixedly connected via the flat key 49 .

[0071] Specifically, see Figure 6 As shown, in the specific scheme of the utility model, the planetary reducer 41 and the first cylindrical gear 42 are connected by a flat key 49. The flat key connection has a simple structure, is easy to assemble and disassemble, and has good centering performance. However, since the key connection cannot withstand axial force, it cannot play a role in axially fixing the parts on the shaft.

[0072] Furthermore, a plurality of second planetary gear shafts 331 evenly distributed horizontally are arranged on the inner wall of the box body 34 , and the second planetary gears 33 are passed through the second planetary gear shafts 331 so that the second planetary gears 33 partially extend out of the box body 34 .

[0073] Specifically, see Figure 7As shown, in the specific scheme of the utility model, the second planetary gear 33 is installed on the second planetary gear shaft 331 on the housing 34 and meshes with the second sun gear shaft 31; the second sun gear 312 of the second sun gear shaft 31 is fixed at the center of the housing 34 and meshes with the planetary gear; the second planetary carrier 32 is fixed on the outer ring of the housing 34 and meshes with the gear of the second planetary gear 33.

[0074] Although the utility model is disclosed as above, the protection scope of the utility model is not limited thereto. Those skilled in the art may make various changes and modifications without departing from the spirit and scope of the disclosure, and these changes and modifications will fall within the protection scope of the utility model.

Claims

1. A dual-input mode reducer, characterized in that: include: A first input shaft structure (1) comprises a first input shaft (12), wherein a first stepped hole (121) penetrating along an axial direction is provided at the center of the first input shaft (12); A first planetary gear train structure (2), comprising a first sun gear shaft (21) arranged horizontally, a plurality of first planetary gears (23) evenly distributed and meshed on the outer circumference of the first sun gear shaft (21), a first planet carrier (22) supporting and mounting the plurality of first planetary gears (23), and a ring gear (24) meshed and driven with the plurality of first planetary gears (23), wherein the first sun gear shaft (21) comprises a first insertion shaft (211) suitable for being inserted into the first stepped hole (121) and a sun gear (212) coaxially connected to an end of the first insertion shaft (211) away from the first input shaft (12), and the sun gear (212) is located at the center of the ring gear (24), and a first center hole (221) is provided at an end of the first planet carrier (22) away from the first insertion shaft (211); A planetary reducer structure (4), comprising a planetary reducer (41) arranged in parallel on one side of the first input shaft (12) and a first cylindrical gear (42) mounted on the output shaft of the planetary reducer (41), wherein the first cylindrical gear (42) is meshed with an outer ring gear (242) of the ring gear (24) for transmission; The second planetary gear train structure (3) comprises a second sun gear shaft (31) arranged horizontally, a plurality of second planetary gears (33) evenly distributed and meshed on the outer circumference of the second sun gear shaft (31), a housing (34) supporting and mounting the plurality of second planetary gears (33), and a second planet carrier (32) meshed with the plurality of second planetary gears (33), wherein the second sun gear shaft (31) comprises a second insertion shaft (311) suitable for being inserted into the first center hole (221) and a second sun gear (312) coaxially connected to an end of the second insertion shaft (311) away from the first planet carrier (22), and the second planetary gears (33) are suitable for meshing with the inner gear ring of the second planet carrier (32) for transmission.

2. The dual-input mode reducer according to claim 1, characterized in that: The first input shaft structure (1) further comprises a front flange (11), a first bearing (13) sleeved between the front flange (11) and the first input shaft (12), a first shaft retaining spring (14) clamped on the first input shaft (12), and a flange end cover (15) connected to the end face of the front flange (11); the end face of the first bearing (13) on one side close to the first sun gear shaft (21) abuts against a first protrusion (122) of the first input shaft (12), the lower end face on the other side abuts against the first sun gear shaft via the first shaft retaining spring (14), and the top end face on the other side abuts against an upper end face of the first bearing (13) via the flange end cover (15).

3. The dual-input mode reducer according to claim 2, characterized in that: The first planetary gear train structure (2) further comprises a second bearing (25) embedded between the first planet carrier (22) and the gear ring (24), a second shaft clamping ring (26) clamped on the first planet carrier (22), and a first hole clamping ring (27) clamped on the inner wall of the gear ring (24); the upper and lower parts of the left end surface of the second bearing (25) are respectively limited by the first hole clamping ring (27) and the second shaft clamping ring (26), and the right end surface of the second bearing (25) abuts against the end surface of the inner gear ring (241) of the gear ring (24).

4. The dual-input mode reducer according to claim 2, characterized in that: The planetary reducer structure (4) further comprises a motor flange (43) mounted on the planetary reducer (41), a motor flange cover (44) connected to the end of the motor flange (43), and a fifth bearing (45) sleeved on the output shaft of the planetary reducer (41); the first cylindrical gear (42) is located inside the motor flange (43), and the first cylindrical gear (42) and the fifth bearing (45) are fixed by a baffle (46).

5. The dual-input mode reducer according to claim 4, characterized in that: A sixth bearing (47) and a seventh bearing (48) are respectively sleeved on the stepped shafts at both ends of the gear ring (24), and one end of the sixth bearing (47) away from the gear ring (24) abuts against the motor flange cover (44), while one end of the seventh bearing (48) away from the gear ring (24) abuts against the inner wall of the motor flange (43).

6. The dual-input mode reducer according to claim 3, characterized in that: The second planetary gear train structure (3) further comprises a box cover (35) connected to one end of the box body (34) via a second locking member (36), and the box cover (35) is located on a side close to the first planet carrier (22), and the outer diameter of the box cover (35) is greater than the outer diameter of the box body (34).

7. The dual-input mode reducer according to claim 6, characterized in that: A third bearing (37) and a fourth bearing (38) are respectively installed at the two ends between the housing (34) and the second planetary carrier (32), and the two ends of the third bearing (37) are respectively abutted against the housing cover (35) and the inner wall of the second planetary carrier (32), and the two ends of the fourth bearing (38) are respectively abutted against the inner wall of the housing (34) and the second planetary carrier (32).

8. The dual-input mode reducer according to claim 6, characterized in that: A first oil seal (16) is provided between the first input shaft (12) and a side of the flange end cover (15) away from the first planetary gear train structure (2), and a second oil seal (39) is provided between the second planet carrier (32) and a side of the housing (34) away from the first input shaft structure (1).

9. The dual-input mode reducer according to claim 1, characterized in that: A flat key (49) is provided on the output shaft of the planetary reducer (41), a keyway corresponding to the position of the flat key (49) is provided on the inner hole of the first cylindrical gear (42), and the first cylindrical gear (42) and the output shaft of the planetary reducer (41) are fixedly connected via the flat key (49).

10. The dual-input mode reducer according to any one of claims 1 to 9, characterized in that: A plurality of second planetary gear shafts (331) evenly distributed horizontally are arranged on the inner wall of the box body (34), and the second planetary gear (33) is passed through the second planetary gear shaft (331) so that the second planetary gear (33) partially extends out of the box body (34).

Images