Planetary gear speed reducer adapting to complex working conditions

Abstract

The utility model relates to the field of speed reducers, and discloses a planetary gear speed reducer adapting to complex working conditions, which comprises a first-stage planetary transmission pair, a second-stage planetary transmission pair, a third-stage planetary transmission pair and a connecting flange, the first-stage planetary transmission pair is used for being connected with a motor, and the third-stage planetary transmission pair is connected with an output gear shaft; the inner surface of the connecting flange is provided with a flat key through a bearing, the flat key is connected with the motor through a torque limiter, the torque limiter comprises a positioning seat, a speed changing ring, a torque input shaft and a torque output shaft, the torque input shaft is sleeved with the positioning seat, and one end of the torque input shaft is fixedly connected with the positioning seat; the torque output shaft is fixedly connected or in transmission connection with the variable speed ring; and a clutch device is arranged between the positioning seat and the variable speed ring. Axial displacement control during torque overload is achieved through the torque limiter, when the output torque exceeds a threshold value, reverse resistance torque generated by the friction plate set enables the speed change ring and the positioning ring to be disengaged, and power transmission is cut off.

Description

Technical Field

[0001] The utility model relates to the field of speed reducers, in particular to a planetary gear speed reducer adapted to complex working conditions. Background Art

[0002] Planetary gear speed reducers are widely used due to their characteristics such as compact structure and high transmission efficiency. However, under complex working conditions (such as instantaneous overload and impact load), traditional speed reducers are prone to gear damage or transmission failure due to over-torque. In the prior art, mechanical torque limiters or electronic sensors are usually used to achieve overload protection, but there are problems such as response delay, complex structure or difficult reset. Under special working conditions such as icebreakers, the speed reducer needs to withstand extremely large torque changes, and traditional speed reducers often have difficulty adapting to such extreme working conditions, easily leading to equipment damage or transmission failure. Therefore, there is an urgent need for a planetary gear speed reducer that can adapt to complex working conditions, has strong torque adaptability, and an overload protection mechanism that can automatically reset and respond quickly, integrated inside the speed reducer to improve reliability and adaptability. Summary of the Invention

[0003] The utility model aims at the deficiencies in the prior art and provides a planetary gear speed reducer adapted to complex working conditions.

[0004] To solve the above technical problems, the utility model is solved by the following technical solutions:

[0005] A planetary gear speed reducer adapted to complex working conditions includes a first-stage planetary transmission pair, a second-stage planetary transmission pair, and a third-stage planetary transmission pair. The first-stage planetary transmission pair, the second-stage planetary transmission pair, and the third-stage planetary transmission pair are sequentially connected for transmission. The first-stage planetary transmission pair is used to connect with the motor, and the third-stage planetary transmission pair is connected with an output gear shaft. Its characteristics are that it also includes a coupling flange. A flat key is installed on the inner surface of the coupling flange through a bearing, and the flat key is connected with the motor through a torque limiter.

[0006] The first-stage planetary transmission pair includes a first-stage sun gear, and the first-stage sun gear is installed with the flat key; the third-stage planetary transmission pair includes a third-stage planetary carrier, and the third-stage planetary carrier is connected with an output gear shaft.

[0007] The torque limiter includes a positioning seat, a speed change ring, a torque input shaft, and a torque output shaft. The positioning seat is sleeved outside the torque input shaft, and one end of the torque input shaft is fixedly connected with the positioning seat. The torque output shaft is fixedly connected or connected for transmission with the speed change ring.

[0008] The positioning seat is fixedly connected to the output shaft of the motor, the speed ring is sleeved and installed on the flat key, and a clutch device is arranged between the positioning seat and the speed ring; when the torque carried on the terminal output gear shaft exceeds the preset value, the clutch device deflects, the positioning seat and the speed ring are disengaged from the transmission, and when the output gear shaft returns to normal or the abnormal situation is eliminated, the positioning seat and the speed ring are rotated through the elastic member to restore the transmission connection. The torque limiter has the function of automatic overload protection. After overload, the positioning seat and the speed ring slip and disengage from the transmission, and the transmission between the motor and the gear box is automatically reset. Especially for icebreakers, because the thickness of ice is different, its resistance changes greatly, so that the load changes are relatively large. Therefore, the torque limiter is adjusted by the preset torque value, and the transmission is stopped when the load is too high, thereby playing a protective role. When it returns to normal or the abnormal situation is eliminated, the master and slave positioning seats and speed rings resume power transmission.

[0009] Preferably, the clutch device includes an elastic member and a friction plate group, the elastic member is a torsion spring, and both ends of the elastic member are respectively connected to the torque output shaft and the clutch device housing, or the two ends of the elastic member are respectively connected to the torque output shaft and the torque input shaft, for providing axial preload.

[0010] Preferably, the friction plate group includes active friction plates and driven friction plates that are alternately arranged, the active friction plates are fixedly connected to the positioning seat, and the driven friction plates are fixedly connected to the speed change ring. The wear-resistant design of the friction plate group and the adjustable preload of the elastic member ensure the long-term stable operation of the clutch device. Usually, there are multiple active friction plates and driven friction plates that are alternately arranged.

[0011] Preferably, a first strike plate is fixed to the positioning seat, and a second strike plate is fixed to the torque input shaft. When the clutch device is transmitting normally, the first strike plate and the second strike plate are staggered. When the clutch device is deflected, the first strike plate and the second strike plate are pressed against each other. The outer ring of the torque input shaft is toothed and meshes with the inner ring of the positioning seat.

[0012] Preferably, the torsion clutch device includes an elastic member, a mating slot, and a ball. The mating slot is a circular mating slot arranged on the end face of the torque input shaft or a mating slot arranged on the outer wall. The ball is fixedly connected to the speed change ring or the torque output shaft through a frame. When the input torque is lower than the set threshold, the speed change ring is axially pressed toward the positioning seat under the action of the elastic member, so that the ball is pressed into the mating slot, and the torque input shaft rotates to drive the ball through the mating slot to rotate the torque output shaft. When the input torque exceeds the threshold, the ball deflects and leaves the mating slot, so that the transmission between the torque input shaft and the speed change ring or the torque output shaft is cut off.

[0013] Preferably, a torque sensor is provided at the end of the output gear shaft for real-time monitoring of the torque value of the output gear shaft. The torque sensor at the end of the output gear shaft can monitor the torque value in real time, providing data support for the control system to facilitate the confirmation of overload and return to the normal state.

[0014] Preferably, the first-stage planetary transmission pair includes a first-stage sun gear, a first-stage planet carrier, and first-stage planet gears; the second-stage planetary transmission pair includes a second-stage sun gear, a second-stage planet carrier, and second-stage planet gears; the third-stage planetary transmission pair includes a third-stage sun gear, a third-stage planet carrier, and third-stage planet gears. The first-stage planet gears are arranged on the first-stage planet carrier and mesh with the first-stage sun gear. The second-stage sun gear meshes with the first-stage planet carrier and the second-stage planet gears respectively. The second-stage planet gears are arranged on the second-stage planet carrier and mesh with the second-stage sun gear. The third-stage sun gear meshes with the second-stage planet carrier and the third-stage planet gears respectively. The third-stage planet gears are arranged on the third-stage planet carrier and drive the third-stage planet carrier to rotate. The third-stage planet carrier is connected to the output gear shaft and drives the output gear shaft to rotate.

[0015] The present utility model has significant technical effects due to the adoption of the above technical solutions:

[0016] By optimizing the structure of the clutch device, the present utility model significantly improves the torque adaptability of the planetary gear reducer under complex working conditions, is particularly suitable for extreme working condition scenarios such as icebreakers, and has broad application prospects. In scenarios with strong torque, through the design of the clutch device, the reducer can automatically interrupt power transmission under extreme working conditions to avoid equipment damage;

[0017] The structure of the present utility model utilizes the dynamic protection mechanism of the torque limiter to achieve axial displacement control when torque overload occurs. When the output torque exceeds the threshold value, the reverse resistance torque generated by the friction plate group causes the speed change ring to disengage from the positioning ring, cutting off power transmission. Compared with the traditional frequency converter speed regulation method, this solution has higher transmission efficiency and realizes a faster and more stable torque response ability. Brief Description of the Drawings

[0018] Figure 1 is the structural schematic diagram of the present utility model;

[0019] Figure 2 is the structural schematic diagram of the output side of the torque limiter;

[0020] Figure 3 is the structural schematic diagram of the input side of the torque limiter;

[0021] Figure 4 is the front view of the input end of the torque limiter;

[0022] Figure 5 is Figure 4 the sectional view of the torque limiter A-A in

[0023] The names of the parts indicated by the numerical labels in the above drawings are as follows: 11, motor; 12, output gear shaft; 211, primary sun gear; 212, primary planet carrier; 213, primary planet gear; 221, secondary sun gear; 222, secondary planet carrier; 223, secondary planet gear; 231, tertiary planet carrier; 232, tertiary sun gear; 233, tertiary planet gear; 3, connecting flange; 31, flat key; 5, torque limiter; 51, positioning ring; 52, speed change ring; 53, torque input shaft; 54, torque output shaft; 55, first impact plate; 56, second impact plate; 62, friction plate group; 621, active friction plate; 622, driven friction plate. DETAILED DESCRIPTION

[0024] The utility model is further described in detail below in conjunction with the accompanying drawings and embodiments. Example

[0025] A planetary gear reducer that adapts to complex working conditions, such as Figures 1-5 As shown, it includes a primary planetary transmission pair, a secondary planetary transmission pair, and a tertiary planetary transmission pair, which are sequentially connected in transmission, the primary planetary transmission pair is used to connect with the motor 11, and the tertiary planetary transmission pair is connected with the output gear shaft 12, characterized in that it also includes a connecting flange 3, the inner surface of the connecting flange 3 is equipped with a flat key 31 through a bearing, and the flat key 31 is connected to the motor 11 through a torque limiter 5.

[0026] The first-stage planetary transmission pair includes a first-stage sun gear 211, which is installed with a flat key 31; the third-stage planetary transmission pair includes a third-stage planet carrier 231, which is connected to the output gear shaft 12;

[0027] The torque limiter 5 includes a positioning seat 51, a speed ring 52, a torque input shaft 53 and a torque output shaft 54. The positioning seat 51 is sleeved outside the torque input shaft 53 and one end of the torque input shaft 53 is fixedly connected to the positioning seat 51. The torque output shaft 54 ​​is fixedly connected or transmission-connected to the speed ring 52.

[0028] The locating seat 51 is fixedly connected to the output shaft of the motor 11, the speed ring 52 is sleeved and installed on the flat key 31, and a clutch device is provided between the locating seat 51 and the speed ring 52; when the torque carried on the terminal output gear shaft 12 exceeds a preset value, the clutch device deflects, and the transmission between the locating seat 51 and the speed ring 52 is disengaged. When the output gear shaft 12 returns to normal or the abnormal situation is eliminated, the locating seat 51 and the speed ring 52 are rotated through the elastic member to restore the transmission connection.

[0029] The clutch device includes an elastic member and a friction plate group 62. The elastic member is a torsion spring, and both ends of the elastic member are respectively connected to the torque output shaft 54 and the clutch device housing, or both ends of the elastic member are respectively connected to the torque output shaft 54 and the torque input shaft 53, and are used to provide an axial pre-tightening force. The elastic member can adopt a disc spring to provide an axial pre-tightening force to ensure that the friction plate group 62 is closely attached under normal working conditions.

[0030] The friction plate group 62 includes alternately arranged active friction plates 621 and driven friction plates 622. The active friction plates 621 are fixedly connected to the positioning seat 51, and the driven friction plates 622 are fixedly connected to the speed change ring 52. Usually, multiple active friction plates 621 and multiple driven friction plates 622 are provided respectively to increase the reliability of transmission.

[0031] A first striker 55 is fixed on the positioning seat 51, and a second striker 56 is fixed on the torque input shaft 53. When the clutch device is transmitting power normally, the first striker 55 and the second striker 56 are staggered. When the clutch device deflects, the first striker 55 and the second striker 56 abut against each other. The outer circle of the torque input shaft 53 is serrated and meshes with the inner circle of the positioning seat 51.

[0032] A torque sensor is provided at the end of the output gear shaft 12 for real-time monitoring of the torque value of the output gear shaft 12.

[0033] The first-level planetary transmission pair includes a first-level sun gear 211, a first-level planet carrier 212, and first-level planet gears 213. The second-level planetary transmission pair includes a second-level sun gear 221, a second-level planet carrier 222, and second-level planet gears 223. The third-level planetary transmission pair includes a third-level sun gear 232, a third-level planet carrier 231, and third-level planet gears 233. The first-level planet gears 213 are arranged on the first-level planet carrier 212, and the first-level planet gears 213 mesh with the first-level sun gear 211. The second-level sun gear 221 meshes with the first-level planet carrier 212 and the second-level planet gears 223 respectively. The second-level planet gears 223 are arranged on the second-level planet carrier 222, and the second-level planet gears 223 mesh with the second-level sun gear 221. The third-level sun gear 232 meshes with the second-level planet carrier 222 and the third-level planet gears 233 respectively. The third-level planet gears 233 are arranged on the third-level planet carrier 231 and drive the third-level planet carrier 231 to rotate. The third-level planet carrier 231 is connected to the output gear shaft 12 and drives the output gear shaft 12 to rotate.

[0034] Working principle:

[0035] Normal working condition: The first striker 55 and the second striker 56 are staggered, and the power is transmitted between the first striker 55 and the second striker 56 through static friction. The positioning seat maintains a linkage state with the speed change ring 52, and the torque input shaft 53 and the torque output shaft 54 are in linkage.

[0036] Overload condition: Under complex working conditions, when the torque carried by the output gear shaft 12 exceeds the preset value, the friction plate group 62 in the clutch device begins to slip, the elastic member is twisted and compressed, and the positioning seat 51 and the speed change ring 52 produce circumferential relative rotation, and the power transmission is interrupted. As one embodiment, the positioning seat 51 is fixed with a first collision plate 55, and the torque input shaft 53 is fixed with a second collision plate 56. The clutch device deflects, the first collision plate 55 and the second collision plate 56 are pressed against each other, and the transmission between the torque input shaft 53 and the torque output shaft 54 ​​stops.

[0037] Restoration condition: When the torque returns to normal or the abnormal condition is eliminated, the elastic member releases the elastic potential energy and rotates, so that the first collision plate 55 and the second collision plate 56 return to the original state of the staggered state, and the friction plate group 62 returns to the state of static friction transmission. Power transmission is restored. The positioning seat maintains the linkage state with the speed change ring 52, thereby ensuring the linkage between the torque input shaft 53 and the torque output shaft 54, and the power is transmitted normally through the torque limiter. Example

[0038] The same as the first embodiment, but different in that: the clutch device includes an elastic member, a matching slot, and a ball. (This embodiment is not shown in the drawings, but is a conventional means for people in this field to set a torque limiter, and will not be described in detail here.) The matching slot is a circular matching slot set on the end face of the torque input shaft 53 or a matching slot set on the outer wall, and the ball is fixedly connected to the speed change ring 52 or the torque output shaft 54 ​​through a skeleton; when the input torque is lower than the set threshold, the speed change ring 52 is axially pressed toward the positioning seat 51 under the action of the elastic member, so that the ball is pressed into the matching slot, and the torque input shaft 53 rotates to drive the ball through the matching slot to rotate the torque output shaft 54; when the input torque exceeds the threshold, the ball deflects and leaves the matching slot, so that the transmission of the torque input shaft 53 and the speed change ring 52 or the torque output shaft 54 ​​is cut off, and the speed change ring 52 is disengaged from the positioning seat 51, forming a torque cut-off protection. The elastic member is generally a compression spring. Under normal working conditions, the speed change ring 52 is axially positioned on the seat 51, and the shapes of the ball and the matching slot match each other so that they can rotate relatively statically, so that the speed change ring 52 is pressed against the positioning seat 51, and the two achieve the purpose of transmission linkage. When the torque exceeds the preset value, the resistance on the output side of the matching slot is too large relative to the ball, and it cannot carry the load after rotation. The matching slot will produce a relative circumferential deflection relative to the ball, and the ball will thus escape from the matching slot. The two cannot be normally linked, and at the same time, the elastic member is driven to twist in a compressed state to accumulate elastic potential energy of circumferential rotation. When the reducer restores normal torque or stops working, the elastic member will rotate and drive the ball to roll back into the matching slot to achieve linkage.

[0039] In the description of the present utility model, it should be understood that the orientation or positional relationship indicated by the terms "center", "length", "width", "thickness", "upper", "lower", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings, and 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, and therefore should not be construed as a limitation to the present utility model. In addition, the terms "first" and "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present utility model, the meaning of "a plurality of" is two or more unless otherwise specifically defined.

[0040] In summary, the above are only the preferred embodiments of the present utility model, and all equivalent changes and modifications made according to the scope of the patent application of the present utility model shall fall within the scope covered by the patent of the present utility model.

Claims

1. A planetary gear reducer adapted to complex working conditions, comprising a primary planetary transmission pair, a secondary planetary transmission pair, and a tertiary planetary transmission pair, wherein the primary planetary transmission pair, the secondary planetary transmission pair, and the tertiary planetary transmission pair are sequentially connected in transmission, the primary planetary transmission pair is used to be connected to a motor (11), and the tertiary planetary transmission pair is connected to an output gear shaft (12), characterized in that: It also includes a connecting flange (3), the inner surface of the connecting flange (3) is provided with a flat key (31) via a bearing, and the flat key (31) is connected to the motor (11) via a torque limiter (5). The first-stage planetary transmission pair comprises a first-stage sun gear (211), which is mounted on a flat key (31); the third-stage planetary transmission pair comprises a third-stage planet carrier (231), which is connected to an output gear shaft (12); The torque limiter (5) comprises a positioning seat (51), a speed change ring (52), a torque input shaft (53) and a torque output shaft (54); the positioning seat (51) is sleeved outside the torque input shaft (53) and one end of the torque input shaft (53) is fixedly connected to the positioning seat (51); and the torque output shaft (54) is fixedly connected or transmission-connected to the speed change ring (52); The positioning seat (51) is fixedly connected to the output shaft of the motor (11); the speed change ring (52) is sleeved and installed on the flat key (31); and a clutch device is provided between the positioning seat (51) and the speed change ring (52); when the torque carried by the terminal output gear shaft (12) exceeds a preset value, the clutch device deflects, and the positioning seat (51) and the speed change ring (52) are disengaged from the transmission; when the output gear shaft (12) returns to normal or the abnormal condition is eliminated, the positioning seat (51) and the speed change ring (52) are rotated through the elastic member to restore the transmission connection.

2. A planetary gear reducer adapted to complex working conditions according to claim 1, characterized in that: The clutch device comprises an elastic member and a friction plate group (62), the elastic member being a torsion spring, the two ends of the elastic member being respectively connected to the torque output shaft (54) and the clutch device housing, or the two ends of the elastic member being respectively connected to the torque output shaft (54) and the torque input shaft (53), for providing an axial preload.

3. A planetary gear reducer adapted to complex working conditions according to claim 2, characterized in that: The friction plate group (62) comprises active friction plates (621) and driven friction plates (622) which are alternately arranged; the active friction plates (621) are fixedly connected to the positioning seat (51), and the driven friction plates (622) are fixedly connected to the speed change ring (52).

4. A planetary gear reducer adapted to complex working conditions according to claim 3, characterized in that: A first striker (55) is fixed to the positioning seat (51), and a second striker (56) is fixed to the torque input shaft (53). When the clutch device is normally transmitting, the first striker (55) and the second striker (56) are staggered. When the clutch device is deflected, the first striker (55) and the second striker (56) are pressed against each other. The outer ring of the torque input shaft (53) is toothed and meshes with the inner ring of the positioning seat (51).

5. The planetary gear reducer adapted to complex working conditions according to claim 1, characterized in that: The clutch device comprises an elastic member, a matching slot, and a ball bearing. The matching slot is a circular matching slot provided on the end surface of the torque input shaft (53) or a matching slot provided on the outer wall. The ball bearing is fixedly connected to the speed change ring (52) or the torque output shaft (54) through a frame. When the input torque is lower than a set threshold value, the speed change ring (52) is axially pressed toward the positioning seat (51) under the action of the elastic member, so that the ball bearing is pressed into the matching slot. The torque input shaft (53) rotates through the matching slot to drive the ball bearing and rotate the torque output shaft (54). When the input torque exceeds the threshold value, the ball bearing deflects and leaves the matching slot, so that the transmission between the torque input shaft (53) and the speed change ring (52) or the torque output shaft (54) is cut off.

6. A planetary gear reducer adapted to complex working conditions according to any one of claims 2 to 5, characterized in that: A torque sensor is provided at the end of the output gear shaft (12) for real-time monitoring of the torque value of the output gear shaft (12).

7. The planetary gear reducer adapted to complex working conditions according to claim 1, characterized in that: The first-stage planetary transmission pair comprises a first-stage sun gear (211), a first-stage planet carrier (212), and a first-stage planetary gear (213); the second-stage planetary transmission pair comprises a second-stage sun gear (221), a second-stage planet carrier (222), and a second-stage planetary gear (223); the third-stage planetary transmission pair comprises a third-stage sun gear (232), a third-stage planet carrier (231), and a third-stage planetary gear (233); the first-stage planetary gear (213) is arranged on the first-stage planet carrier (212); the first-stage planetary gear (213) meshes with the first-stage sun gear (211); and the second-stage sun gear (221) is respectively The second planetary gear (223) is meshed with the first planetary carrier (212) and the second planetary gear (223), the second planetary gear (223) is arranged on the second planetary carrier (222), the second planetary gear (223) is meshed with the second sun gear (221), the third sun gear (232) is respectively meshed with the second planetary carrier (222) and the third planetary gear (233), the third planetary gear (233) is arranged on the third planetary carrier (231) and drives the third planetary carrier (231) to rotate, and the third planetary carrier (231) is connected to the output gear shaft (12) and drives the output gear shaft (12) to rotate.

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