Torque direction adjusting mechanism with ultralow rotational inertia

Abstract

The invention provides an ultra-low rotational inertia torque direction adjusting mechanism which comprises a shell, an input shaft and an output shaft are arranged in an inner cavity of the shell, in a planetary gear mechanism of the inner cavity of the shell, the inside and the outside of a planetary gear are meshed with a sun gear and an inner gear ring respectively, and the sun gear is coaxially fixed to the input shaft. The planet carrier is connected with the shell through the first electromagnetic clutch, locking or unlocking of the planet carrier is achieved through connection and disconnection of the first electromagnetic clutch, the planet carrier is connected with the output shaft through the first two-way overrunning clutch, and one-way rotation of the gear ring frame is achieved through the first one-way clutch. And the gear ring frame is connected with the output shaft through a second bidirectional overrunning clutch or a second electromagnetic clutch. The motor has the advantages that controllable reversing of the output shaft of the motor under the high-speed heavy-load condition is achieved, energy loss caused by frequent reversing of the motor is reduced, the problem that reversing is difficult due to the fact that rotational inertia of the motor is too large is solved, and the service life of the motor is prolonged.

Description

Technical Field

[0001] The present invention relates to the technical field of mechanical transmission and control devices, and more specifically, to an ultra-low moment of inertia torque direction adjustment mechanism. Background Art

[0002] In industrial production, motors are often used to provide driving torque. However, in scenarios such as automated equipment (e.g., reciprocating conveying mechanisms), the motor needs to frequently reverse to adapt to the dynamic load requirements. The frequent commutation of the motor will lead to a decrease in the efficiency of the motor and a shortening of its service life; the reverse delay of the electromagnetic torque during the commutation instant may cause mechanical shock, further affecting the system reliability.

[0003] In scenarios with high-speed and high-inertia loads, the torque required for the motor to reverse is large, resulting in difficult commutation. Since motors are usually used in conjunction with speed reducers, the transmission ratio of the speed reducer will amplify the lower angular acceleration at the load end. Therefore, when facing a load with a large moment of inertia and high-speed operation, the torque required for commutation is large. The large moment of inertia will hinder the rapid acceleration and deceleration of the rotor. The torque required for the motor rotor to reverse is too large, resulting in difficult commutation of the motor and affecting the dynamic response ability of the motor. In addition, the too-frequent commutation of the motor will limit the maximum speed of the motor. The motor and the speed reducer form a geared motor. The relative rotation direction of the output shaft and the input shaft of the traditional geared motor is the same. When the output shaft needs to reverse, it is usually necessary to control the motor to reverse, resulting in large energy losses due to the action of inertia and resistance torque. Summary of the Invention

[0004] The purpose of the present invention is to overcome the deficiencies of the prior art and provide an ultra-low moment of inertia torque direction adjustment mechanism to achieve controllable commutation of the output shaft of the motor under high-speed heavy-load conditions, reduce the energy loss during the frequent commutation of the motor, and extend the service life of the motor.

[0005] To achieve the above purpose, the present invention adopts the following technical solutions:

[0006] An ultra-low moment of inertia torque direction adjustment mechanism, comprising a housing with an internal cavity. An input shaft and an output shaft are coaxially arranged in the inner cavity of the housing. The input shaft and the output shaft respectively extend outside the inner cavity of the housing to form an input end and an output end. A planetary gear mechanism is also provided in the inner cavity of the housing. The planetary gear mechanism includes a sun gear, a plurality of planetary gears, a planetary carrier, and a ring gear carrier. The internal gear ring of the ring gear carrier is located outside the sun gear. The plurality of planetary gears are located between the sun gear and the internal gear ring, and the planetary gears are respectively meshed with the sun gear and the internal gear ring inside and outside. The sun gear is coaxially fixed on the input shaft. The planetary carrier is connected to the housing through a first electromagnetic clutch, and the locking or unlocking of the planetary carrier is realized through the on-off of the first electromagnetic clutch. The planetary carrier is connected to the output shaft through a first bi-directional overrunning clutch. The ring gear carrier is connected to the housing through a first one-way clutch, and the one-way rotation of the ring gear carrier is realized through the first one-way clutch. The ring gear carrier is connected to the output shaft through a second bi-directional overrunning clutch or a second electromagnetic clutch.

[0007] As a preferred solution of the above ultra-low moment of inertia torque direction adjustment mechanism, an extension shaft is provided at one end of the planetary carrier close to the output shaft. The inner ring of the first bi-directional overrunning clutch is fixedly sleeved on the extension shaft of the planetary carrier. A hollow first extension shaft sleeve is provided at one end of the planetary carrier close to the input shaft. The input shaft passes through the center of the first extension shaft sleeve. The planetary carrier is rotationally supported on the housing through the first extension shaft sleeve.

[0008] As a preferred solution of the above ultra-low moment of inertia torque direction adjustment mechanism, the outer ring of the first bi-directional overrunning clutch is fixedly connected to the output shaft through a first coupling.

[0009] As a preferred solution of the above ultra-low moment of inertia torque direction adjustment mechanism, a disc is fixedly provided at one end of the planetary carrier close to the input shaft. One end of the first electromagnetic clutch is fixed on the disc and the other end is fixed on the housing.

[0010] As a preferred solution of the above ultra-low moment of inertia torque direction adjustment mechanism, a hollow second extension shaft sleeve is provided at one end of the ring gear carrier close to the output shaft. The output shaft passes through the center of the second extension shaft sleeve. When the ring gear carrier is connected to the output shaft through a second bi-directional overrunning clutch, the inner ring of the second bi-directional overrunning clutch is fixedly sleeved on the second extension shaft sleeve, and the outer ring of the second bi-directional overrunning clutch is fixedly connected to the output shaft through a second coupling.

[0011] As a preferred solution of the above ultra-low moment of inertia torque direction adjustment mechanism, the inner ring of the first one-way clutch is fixedly sleeved on the second extension shaft sleeve and the outer ring is fixed on the housing.

[0012] As a preferred solution of the above ultra-low moment of inertia torque direction adjustment mechanism, the adjustment mechanism further includes an energy feedback module for realizing the transmission of torque from the output shaft to the input shaft.

[0013] As a preferred embodiment of the above ultra-low moment of inertia torque direction adjustment mechanism, the energy feedback module includes a first energy feedback planetary gear assembly. The ring gear carrier is connected to the output shaft through a second electromagnetic clutch. A transition member is fixed inside the ring gear carrier, and the transition member is connected to the output shaft through a second one-way clutch. The first energy feedback planetary gear assembly includes a first energy feedback sun gear, a plurality of first energy feedback planetary gears, a first energy feedback planetary carrier, and a first energy feedback internal gear ring. The plurality of first energy feedback planetary gears are located between the first energy feedback sun gear and the first energy feedback internal gear ring, and the first energy feedback planetary gears are respectively meshed with the first energy feedback sun gear and the first energy feedback internal gear ring inside and outside. The first energy feedback internal gear ring is fixed inside the ring gear carrier, the first energy feedback sun gear is connected to the output shaft through a third one-way clutch, and the first energy feedback planetary carrier is connected to the housing through a third electromagnetic clutch.

[0014] As a preferred embodiment of the above ultra-low moment of inertia torque direction adjustment mechanism, the energy feedback module includes a second energy feedback planetary gear assembly. The ring gear carrier is connected to the output shaft through a second electromagnetic clutch. The second energy feedback planetary gear assembly includes a second energy feedback sun gear, a plurality of second energy feedback planetary gears, a second energy feedback planetary carrier, and a second energy feedback internal gear ring. The plurality of second energy feedback planetary gears are located between the second energy feedback sun gear and the second energy feedback internal gear ring, and the second energy feedback planetary gears are respectively meshed with the second energy feedback sun gear and the second energy feedback internal gear ring inside and outside. The second energy feedback internal gear ring is fixed inside the ring gear carrier, the second energy feedback sun gear is connected to the output shaft through a fourth one-way clutch, and the second energy feedback planetary carrier is connected to the housing through a fifth one-way clutch.

[0015] As a preferred embodiment of the above ultra-low moment of inertia torque direction adjustment mechanism, the ring gear carrier is detachably connected to each internal gear ring.

[0016] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0017] 1. An ultra-low moment of inertia torque direction adjustment mechanism provided by the present invention introduces a planetary gear mechanism, locks or unlocks the planetary carrier by controlling the on-off of the current of the first electromagnetic clutch, realizes the one-way rotation of the ring gear carrier through the first one-way clutch, and at the same time introduces a bidirectional overrunning clutch. By utilizing the characteristics of the bidirectional overrunning clutch, the change of the mechanical structure connection relationship is comprehensively realized, and then it is realized that the motor only needs to rotate in the same direction to flexibly adjust the direction of the output torque according to needs, realizes the high-speed controllable commutation of the output shaft of the motor under heavy load conditions, reduces the energy loss in the frequent commutation process, prolongs the service life of the motor, and is especially suitable for scenarios where large torque needs to be transmitted and the motor needs to commutate frequently under the conditions of high requirements for installation space and weight.

[0018] 2. The ultra-low moment of inertia torque direction adjustment mechanism provided by the present invention can be equipped with an energy feedback module on the basic structure. It can not only actively output torque through the motor, but also recover the energy at the load end through the added energy feedback module. At the same time, the rotation direction of the motor during the recovery process will not change with the change of the load input torque direction, thereby increasing the energy recovery efficiency.

[0019] 3. The ultra-low moment of inertia torque direction adjustment mechanism provided by the present invention has a compact structure and is equipped with a planetary gear mechanism. It can reduce the occupied space and play a role in speed reduction and torque increase at the same time. The function of the planetary reducer is integrated into the electric control torque direction adjustment mechanism, and there is no need to additionally set a speed reduction mechanism on the motor output shaft. Moreover, the electromagnetic clutch and the planetary gear mechanism are ingeniously embedded together in the structure, avoiding the problem of too long stroke caused by the series connection of the torque direction adjustment mechanism in the structure, and can be applied to fields with limited space. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 is the structural schematic diagram of Embodiment 1 of the present invention.

[0021] Figure 2 is the three-dimensional internal structure diagram of the ring gear frame in Embodiment 1 of the present invention.

[0022] Figure 3 is the three-dimensional internal structure diagram of the housing in Embodiment 1 of the present invention.

[0023] Figure 4 is Figure 3 a three-dimensional diagram from another perspective.

[0024] Figure 5 is Figure 3 the three-dimensional exploded view of

[0025] Figure 6 is Figure 3 the three-dimensional half-sectional view of

[0026] Figure 7 is the structural schematic diagram of Embodiment 2 of the present invention.

[0027] Figure 8 is the structural schematic diagram of Embodiment 3 of the present invention.

[0028] In the figure, 1 is the housing; 2 is the input shaft; 3 is the output shaft; 4 is the sun gear; 5 is the planetary gear; 6 is the planet carrier; 7 is the ring gear carrier; 8 is the internal ring gear; 9 is the first electromagnetic clutch; 10 is the first bi-directional overrunning clutch; 11 is the first one-way clutch; 12 is the second bi-directional overrunning clutch; 13 is the second electromagnetic clutch; 14 is the extension shaft; 15 is the first coupling; 16 is the disc; 17 is the first extension shaft sleeve; 18 is the second extension shaft sleeve; 19 is the second coupling; 20 is the transition piece; 21 is the second one-way clutch; 22 is the first energy-feeding sun gear; 23 is the first energy-feeding planetary gear; 24 is the first energy-feeding planet carrier; 25 is the first energy-feeding internal ring gear; 26 is the third one-way clutch; 27 is the third electromagnetic clutch; 28 is the second energy-feeding sun gear; 29 is the second energy-feeding planetary gear; 30 is the second energy-feeding planet carrier; 31 is the second energy-feeding internal ring gear; 32 is the fourth one-way clutch; 33 is the fifth one-way clutch. Detailed implementation manners

[0029] To make the objectives, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the embodiments of the present invention. Obviously, the described embodiments are some, but not all, of the embodiments of the present invention. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts shall fall within the protection scope of the present invention.

[0030] Embodiment 1

[0031] Please refer to Figures 1 to 6, this embodiment provides a torque direction adjustment mechanism with ultra-low moment of inertia, including a housing 1 with an internal cavity. An input shaft 2 and an output shaft 3 are coaxially arranged in the inner cavity of the housing 1. The input shaft 2 and the output shaft 3 extend out of the inner cavity of the housing 1 respectively to form an input end and an output end. The input end of the input shaft 2 is connected to an external power component such as a motor, and the output end of the output shaft 3 is connected to a driven component that needs to frequently reverse. A planetary gear mechanism is also provided in the inner cavity of the housing 1. The planetary gear mechanism includes a sun gear 4, several planetary gears 5, a planet carrier 6, and a ring gear carrier 7. An internal gear ring 8 is detachably connected to the ring gear carrier 7. The internal gear ring 8 and the ring gear carrier 7 can be detachably connected by means of screw connection, which is convenient for installation, disassembly, and independent replacement, saving costs. The internal gear ring 8 of the ring gear carrier 7 is located outside the sun gear 4. Several planetary gears 5 are located between the sun gear 4 and the internal gear ring 8, and the planetary gears 5 are meshed with the sun gear 4 and the internal gear ring 8 respectively inside and outside. The sun gear 4 is coaxially fixed on the input shaft 2. The planet carrier 6 is connected to the housing 1 through a first electromagnetic clutch 9. The locking or unlocking of the planet carrier 6 is achieved by the on-off of the current of the first electromagnetic clutch 9. The planet carrier 6 is connected to the output shaft 3 through a first bidirectional overrunning clutch 10. The ring gear carrier 7 is connected to the housing 1 through a first one-way clutch 11. The one-way rotation of the ring gear carrier 7 is achieved through the first one-way clutch 11. The ring gear carrier 7 is connected to the output shaft 3 through a second bidirectional overrunning clutch 12 or a second electromagnetic clutch 13.

[0032] Among them, an extension shaft 14 is provided at one end of the planet carrier 6 close to the output shaft 3. The inner ring of the first bidirectional overrunning clutch 10 is fixedly sleeved on the extension shaft 14 of the planet carrier 6, and the outer ring of the first bidirectional overrunning clutch 10 is fixedly connected to the output shaft 3 through a first coupling 15. A disc 16 is provided at one end of the planet carrier 6 close to the input shaft 2. One end of the first electromagnetic clutch 9 is fixed on the disc 16 and the other end is fixed on the housing 1. A hollow first extension shaft sleeve 17 is provided on the disc 16. The input shaft 2 passes through the center of the first extension shaft sleeve 17. The planet carrier 6 is rotationally supported on the housing 1 through the first extension shaft sleeve 17.

[0033] The ring gear carrier 7 is of a cylindrical structure. A hollow second extension shaft sleeve 18 is provided at one end of the ring gear carrier 7 close to the output shaft 3. The output shaft 3 passes through the center of the second extension shaft sleeve 18. When the ring gear carrier 7 is connected to the output shaft 3 through the second bidirectional overrunning clutch 12, the inner ring of the second bidirectional overrunning clutch 12 is fixedly sleeved on the second extension shaft sleeve 18, and the outer ring of the second bidirectional overrunning clutch 12 is fixedly connected to the output shaft 3 through a second coupling 19. The inner ring of the first one-way clutch 11 is fixedly sleeved on the second extension shaft sleeve 18 and the outer ring is fixed on the housing 1. There are no restrictions on the shape, material, and installation method of the housing 1. It can be designed accordingly according to the size and dimensions of the actual installation space, as long as it can meet the installation and fixing functions of the corresponding components.

[0034] One end of the bi-directional overrunning clutch is the driving end and the other end is the driven end. The bi-directional overrunning clutch has the following characteristics: when the driving end rotates forward (backward), it can drive the driven end to rotate forward (backward); when the driving end stops or does not rotate, the driven end can rotate freely in both directions; when the driving end drives the driven end to operate, the driven end can overrun the driving end in the same direction, that is, the driven end can rotate independently at a speed higher than that of the driving end until its speed decreases and it automatically engages with the driving end. In this embodiment, the inner rings of the two bi-directional overrunning clutches are the driving ends and the outer rings are the driven ends. The two bi-directional overrunning clutches can only transmit the torque of the inner rings to the outer rings connected to the output shaft 3, and the torque of the output shaft 3 cannot be transmitted from the outer rings to the inner rings.

[0035] Assume that the first one-way clutch 11 cannot rotate in the clockwise direction and can only rotate freely in the counterclockwise direction. Due to the action of the first one-way clutch 11, the ring gear carrier 7 can only rotate unidirectionally in the counterclockwise direction and is fixed to the housing 1 in the clockwise direction and cannot rotate. The following describes the various operating conditions of the adjustment mechanism when the ring gear carrier 7 is connected to the output shaft 3 through the second bi-directional overrunning clutch 12.

[0036] In the first operating condition, the input shaft 2 and the output shaft 3 transmit torque in the same direction:

[0037] The first electromagnetic clutch 9 is de-energized and the planet carrier 6 is unlocked. The torque of the input shaft 2 is sequentially transmitted through the sun gear 4, the planet gears 5, the planet carrier 6 in the planetary gear mechanism, and then through the first bi-directional overrunning clutch 10 and the second bi-directional overrunning clutch 12 to the output shaft 3.

[0038] Specifically, when transmitting torque in the same direction, the input shaft 2 inputs torque in the clockwise direction. After passing through the sun gear 4, the sun gear 4 drives each planet gear 5 to rotate counterclockwise. Since the planet carrier 6 is in the unlocked state, each counterclockwise rotating planet gear 5 will drive the planet carrier 6 to revolve clockwise around the sun gear 4 at the same time. The planet gears 5 with rotation and revolution will drive the ring gear carrier 7 to have a tendency to rotate clockwise, and the ring gear carrier 7 is locked in the clockwise direction, so the ring gear carrier 7 remains stationary at this time. The torque in the clockwise direction is output through the planet carrier 6, and then the clockwise torque is transmitted to the output shaft 3 through the driving end of the first bi-directional overrunning clutch 10. Due to the characteristics of the bi-directional overrunning clutch, when the driving end stops or does not rotate, the driven end can rotate freely in both directions. At this time, the inner driving end of the second bi-directional overrunning clutch 12 is connected to the stationary ring gear carrier 7, and the outer driven end is connected to the output shaft 3. Due to the characteristics of the second bi-directional overrunning clutch 12, the clockwise rotation of the output shaft 3 will not affect the ring gear carrier 7 at this time, thus realizing the transmission of torque in the same direction between the input shaft 2 and the output shaft 3.

[0039] In the second operating condition, the input shaft 2 and the output shaft 3 transmit torque in the opposite direction:

[0040] The first electromagnetic clutch 9 is energized, and the planet carrier 6 is locked by being connected to the housing 1 through the electromagnetic clutch. The torque of the input shaft 2 is sequentially transmitted through the sun gear 4, planet gears 5, and ring gear carrier 7 in the planetary gear mechanism and then transmitted to the second overrunning clutch 12 connected thereto, and then output through the output shaft 3.

[0041] Specifically, when transmitting torque in the reverse direction, the input shaft 2 inputs torque in the clockwise direction. Since the planet carrier 6 is locked and in a stationary state, the torque is sequentially transmitted through the sun gear 4, planet gears 5, and ring gear carrier 7 and then through the second overrunning clutch 12 to transmit the torque to the output shaft 3. Due to the conversion effect of the planetary gear mechanism, the torque output by the output shaft 3 at this time is in the counterclockwise direction. Due to the characteristics of the first overrunning clutch 10, the counterclockwise torque of the output shaft 3 will not affect the planet carrier 6, thus realizing the reverse transmission of torque between the input shaft 2 and the output shaft 3.

[0042] When the ring gear carrier 7 is connected to the output shaft 3 through the second electromagnetic clutch 13, it is only necessary to control the second electromagnetic clutch 13 to disconnect under the above first working condition to separate the ring gear carrier 7 from the output shaft 3, and the ring gear carrier 7 is fixed; control the second electromagnetic clutch 13 to be connected under the above second working condition, and the ring gear carrier 7 will transmit the counterclockwise torque to the output shaft 3.

[0043] Embodiment 2

[0044] Refer to Figure 7 , on the basis of the above adjustment mechanism, an energy feedback module is added in this embodiment for realizing the transmission of torque from the output shaft 3 to the input shaft 2, and the ring gear carrier 7 is connected to the output shaft 3 through the second electromagnetic clutch 13. A transition member 20 is also fixed in the ring gear carrier 7, and the transition member 20 is connected to the output shaft 3 through the second one-way clutch 21. The energy feedback module includes a first energy feedback planetary gear assembly, and the first energy feedback planetary gear assembly includes a first energy feedback sun gear 22, a plurality of first energy feedback planetary gears 23, a first energy feedback planet carrier 24, and a first energy feedback internal gear ring 25. The plurality of first energy feedback planetary gears 23 are located between the first energy feedback sun gear 22 and the first energy feedback internal gear ring 25, and the inner and outer parts of the first energy feedback planetary gears 23 are respectively meshed with the first energy feedback sun gear 22 and the first energy feedback internal gear ring 25. The first energy feedback internal gear ring 25 can be detachably connected to the ring gear carrier 7 by means of screw connection. The first energy feedback sun gear 22 is connected to the output shaft 3 through the third one-way clutch 26, and the first energy feedback planet carrier 24 is connected to the housing 1 through the third electromagnetic clutch 27.

[0045] Among them, the second one-way clutch 21 and the third one-way clutch 26 are installed in opposite directions, so that the one-way rotation directions of the second one-way clutch 21 and the third one-way clutch 26 are opposite. In this embodiment, it is assumed that the second one-way clutch 21 can only rotate freely in the clockwise direction, while the third one-way clutch 26 can only rotate freely in the counterclockwise direction. Due to the action of the second one-way clutch 21, the ring gear carrier 7 can only rotate unidirectionally in the clockwise direction. Due to the action of the third one-way clutch 26, the first energy-feeding sun gear 22 can only rotate unidirectionally in the counterclockwise direction.

[0046] This embodiment adds a third electromagnetic clutch 27 and a pair of second one-way clutch 21 and third one-way clutch 26 installed in opposite directions, which can realize that the input in a single direction of the input shaft 2 is selectively switched into the torque in any one of the two directions by controlling the on-off of the electromagnetic clutch. And when the input shaft 2 connected to the external motor does not provide torque and the output shaft 3 is used as the power source for providing torque in this embodiment, the torques in the two directions can be uniformly converted into the torque in a single direction of the input shaft 2, so that the energy recovery efficiency during reverse energy feeding can be greatly improved. The torque controllable adjustment mechanism with energy feeding function in this embodiment can realize the following four working conditions:

[0047] Working condition 1: The input shaft 2 and the output shaft 3 are in the same direction and the input shaft 2 actively outputs:

[0048] At this time, both the first electromagnetic clutch 9 and the third electromagnetic clutch 27 are in the disengaged state, and both the planet carrier 6 and the first energy-recovery planet carrier 24 are in the unlocked state and can rotate freely. The first one-way clutch 11 installed between the housing 1 and the ring gear carrier 7 (locked in the clockwise direction and free to rotate counterclockwise) is in the locked state, and the ring gear carrier 7 is connected to the housing 1 and remains stationary. The input shaft 2 inputs a clockwise torque, which is transmitted to the output shaft 3 via the planetary gear 5, the planet carrier 6, and the first bi-directional overrunning clutch 10. It should be explained that when the clockwise torque is transmitted to the planetary gear 5, it will inevitably drive the ring gear carrier 7 to rotate clockwise. According to the characteristics of the bi-directional overrunning clutch, when the driving end drives the driven end to operate, the driven end can overrun the driving end in the same direction, that is, the driven end can rotate independently at a speed higher than that of the driving end until its speed decreases and it automatically engages with the driving end. At this time, the planet carrier 6 is connected to the driving end of the first bi-directional overrunning clutch 10, driving the driven end of the first bi-directional overrunning clutch 10 to rotate clockwise. The driven end of the first bi-directional overrunning clutch 10 is connected to the output shaft 3, and the output shaft 3 is also connected to one end of the second electromagnetic clutch 13. At this time, the second electromagnetic clutch 13 is in the disengaged state. At this time, the output shaft 3 rotates clockwise, the second one-way clutch 21 can rotate freely clockwise, which is equivalent to idling, and the third one-way clutch 26 cannot rotate freely clockwise. Then, at this time, the third one-way clutch 26 fixes the first energy-recovery sun gear 22 and the output shaft 3 together to rotate clockwise. Since the ring gear carrier 7 is fixed, the first energy-recovery planet carrier 24 outputs a clockwise torque, which has no effect and is equivalent to idling.

[0049] Condition 2: The input shaft 2 and the output shaft 3 are in opposite directions and the input shaft 2 outputs actively:

[0050] At this time, the first electromagnetic clutch 9 is closed, connecting the planet carrier 6 and the housing 1 at both ends. Therefore, the planet carrier 6 is also locked and fixed. The clockwise torque input via the input shaft 2 is changed to a counterclockwise torque via the sun gear 4, the planet gears 5, and the ring gear carrier 7. Then, by energizing the second electromagnetic clutch 13 to make the second electromagnetic clutch 13 in a closed transmission state, the ring gear carrier 7 is combined with the output shaft 3. At this time, a counterclockwise torque is output from the ring gear carrier 7 to the output shaft 3. The first one-way clutch 11 (locked and immovable in the clockwise direction, free to rotate in the counterclockwise direction) installed between the housing 1 and the ring gear carrier 7 is in a free rotation state, and the ring gear carrier 7 also rotates counterclockwise. According to the characteristics of the bi-directional overrunning clutch: when the driving end stops or does not rotate, the driven end can achieve bi-directional free rotation. At this time, the driving end of the first bi-directional overrunning clutch 10 connected to the planet carrier 6 is stationary, and the output shaft 3 can rotate freely in both directions. The second one-way clutch 21 (free to rotate in the clockwise direction, fixed to the ring gear carrier 7 in the counterclockwise direction through the transition member 20) rotates counterclockwise together with the ring gear carrier 7. The first one-way clutch 11 (locked and immovable in the clockwise direction, free to rotate in the counterclockwise direction) can rotate freely counterclockwise. The third one-way clutch 26 (fixed to the first energy-feeding sun gear 22 in the clockwise direction, free to rotate in the counterclockwise direction) rotates freely and is not connected to the first energy-feeding sun gear 22.

[0051] Condition 3: The output shaft 3 rotates clockwise and the input torque plays an energy-feeding role:

[0052] When the output shaft 3 rotates clockwise and inputs torque, the second one-way clutch 21 (free to rotate in the clockwise direction, fixed to the ring gear carrier 7 in the counterclockwise direction) idles. The third one-way clutch 26 (fixed to the first energy-feeding sun gear 22 in the clockwise direction, free to rotate in the counterclockwise direction) is fixedly connected to the first energy-feeding sun gear 22. At this time, the third electromagnetic clutch 27 is closed, and the first energy-feeding planet carrier 24 is locked and fixed. The clockwise torque outputs a counterclockwise torque via the first energy-feeding sun gear 22, the first energy-feeding planet gears 23, and the ring gear carrier 7. The first one-way clutch 11 (locked and immovable in the clockwise direction, free to rotate in the counterclockwise direction) can rotate freely counterclockwise and transmits the counterclockwise torque of the ring gear carrier 7 to the planet gears 5. At this time, the first electromagnetic clutch 9 is closed, and the planet carrier 6 and the housing 1 are connected and locked stationary. The counterclockwise torque is changed in direction via the planet gears 5 and the sun gear 4 and outputs a clockwise torque to the input shaft 2 connected to the external motor. At this time, the driving end of the first bi-directional overrunning clutch 10 is stationary and the driven end can rotate freely. The second electromagnetic clutch 13 is not energized and is in an open state.

[0053] Condition 4: The output shaft 3 rotates counterclockwise and the input torque plays an energy-feeding role:

[0054] The output shaft rotates counterclockwise to input torque. The third one-way clutch 26 (fixed to the first energy-recovery sun gear 22 in the clockwise direction and free to rotate in the counterclockwise direction) idles. The second one-way clutch 21 (free to rotate in the clockwise direction and fixed to the ring gear carrier 7 in the counterclockwise direction) drives the ring gear carrier 7 to rotate counterclockwise together through the transition member 20 mounted thereon. At this time, the third electromagnetic clutch 27 is disengaged, and the first energy-recovery planet carrier 24 is unlocked and free to rotate. The counterclockwise torque is output as a clockwise torque through the planet gear 5 and the sun gear 4 in sequence. The first one-way clutch 11 (locked and immovable in the clockwise direction and free to rotate in the counterclockwise direction) can rotate freely counterclockwise and transmits the counterclockwise torque of the ring gear carrier 7 to the planet gear 5. At this time, the first electromagnetic clutch 9 is closed, and the planet carrier 6 and the housing 1 are locked and stationary. The counterclockwise torque is reversed through the planet gear 5 and the sun gear 4 and the clockwise torque is output to the input shaft 2 connected to the external motor. At this time, the driving end of the first bi-directional overrunning clutch 10 is stationary and the driven end can rotate freely, and the second electromagnetic clutch 13 is de-energized and in the disengaged state.

[0055] Embodiment 3

[0056] Refer to Figure 8 In this embodiment, an energy feedback module is added on the basis of the adjusting mechanism in Embodiment 1 to realize the transmission of torque from the output shaft 3 to the input shaft 2, and the ring gear carrier 7 is connected to the output shaft 3 through the second electromagnetic clutch 13. In this embodiment, the energy feedback module includes a second energy-recovery planetary gear assembly. The second energy-recovery planetary gear assembly includes a second energy-recovery sun gear 28, a plurality of second energy-recovery planetary gears 29, a second energy-recovery planet carrier 30, and a second energy-recovery internal gear ring 31. A plurality of second energy-recovery planetary gears 29 are located between the second energy-recovery sun gear 28 and the second energy-recovery internal gear ring 31, and the inner and outer parts of the second energy-recovery planetary gears 29 are respectively meshed with the second energy-recovery sun gear 28 and the second energy-recovery internal gear ring 31. The second energy-recovery internal gear ring 31 can be detachably mounted in the ring gear carrier 7 by means of screw connection. The second energy-recovery sun gear 28 is connected to the output shaft 3 through the fourth one-way clutch 32, and the second energy-recovery planet carrier 30 is connected to the housing 1 through the fifth one-way clutch 33.

[0057] The torque controllable adjusting mechanism with energy feedback function in this embodiment can realize four working conditions. The working processes of Working Condition 1 and Working Condition 2 are similar to those in Embodiment 3. The main difference lies in the different working processes during energy feedback in Working Condition 3 and Working Condition 4. In this embodiment:

[0058] Working Condition 3: The output shaft 3 rotates clockwise to input torque to play an energy feedback role:

[0059] When a clockwise torque is input to the output shaft 3, the fourth one-way clutch 32 (locked in the clockwise direction and free to rotate counterclockwise) is fixedly connected to the second energy-feeding sun gear 28, driving the second energy-feeding sun gear 28 to rotate clockwise. The second energy-feeding planet carrier 30 also has a tendency to move clockwise. The fifth one-way clutch 33 (locked in the clockwise direction and free to rotate counterclockwise) fixedly connects the second energy-feeding planet carrier 30 to the housing 1, and the second energy-feeding planet carrier 30 is locked and remains stationary. The second energy-feeding sun gear 28 drives the second energy-feeding planet gear 29 to rotate counterclockwise, and the second energy-feeding planet gear 29 drives the ring gear carrier 7 to rotate counterclockwise together. The first one-way clutch 11 (locked in the clockwise direction and free to rotate counterclockwise) can rotate freely and will not lock the ring gear carrier 7. The first electromagnetic clutch 9 is energized and closed to fix the planet carrier 6 to the housing 1. After reversing through the planet gear 5 and the sun gear 4, the clockwise torque is transmitted to the input shaft 2. At this time, the second electromagnetic clutch 13 is in the off state, and the driving end of the first bi-directional overrunning clutch 10 is stationary while the driven end can rotate counterclockwise.

[0060] Condition 4: The output shaft 3 rotates counterclockwise and the input torque functions as energy feeding:

[0061] When a counterclockwise torque is input to the output shaft 3, the fourth one-way clutch 32 (locked in the clockwise direction and free to rotate counterclockwise) can rotate freely and will not drive the second energy-feeding sun gear 28 to rotate. The second electromagnetic clutch 13 is energized and closed to engage the output shaft 3 with the ring gear carrier 7, thereby transmitting the counterclockwise torque on the output shaft 3 to the ring gear carrier 7. The first one-way clutch 11 (locked in the clockwise direction and free to rotate counterclockwise) can rotate freely and will not fix the ring gear carrier 7. The first electromagnetic clutch 9 is energized and closed to fix the planet carrier 6 to the housing 1. The counterclockwise torque of the ring gear carrier 7 forms a clockwise torque after reversing through the planet gear 5 and the sun gear 4, and the clockwise torque is transmitted from the sun gear 4 to the input shaft 2.

[0062] The above are only the preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent replacements, and improvements made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. An ultra-low moment of inertia torque direction adjustment mechanism, comprising a housing (1) with a cavity therein, wherein an input shaft (2) and an output shaft (3) are coaxially arranged in the inner cavity of the housing (1), and the input shaft (2) and the output shaft (3) extend out of the inner cavity of the housing (1) to form an input end and an output end, respectively, and characterized in that: A planetary gear mechanism is also provided in the inner cavity of the housing (1), the planetary gear mechanism comprising a sun gear (4), a plurality of planetary gears (5), a planet carrier (6), and a ring gear carrier (7). An inner ring gear (8) of the ring gear carrier (7) is located outside the sun gear (4), a plurality of planetary gears (5) are located between the sun gear (4) and the inner ring gear (8), and the inner and outer sides of the planetary gears (5) are respectively meshed with the sun gear (4) and the inner ring gear (8). The sun gear (4) is coaxially fixed on the input shaft (2), and the planet carrier (6) is connected to the input shaft (2) via a first electromagnetic clutch (9). The gear ring carrier (7) is connected to the housing (1), and the planet carrier (6) is locked or unlocked by turning on and off a first electromagnetic clutch (9). The planet carrier (6) is connected to the output shaft (3) via a first two-way overrunning clutch (10). The gear ring carrier (7) is connected to the housing (1) via a first one-way clutch (11). The one-way rotation of the gear ring carrier (7) is achieved via the first one-way clutch (11). The gear ring carrier (7) is connected to the output shaft (3) via a second two-way overrunning clutch (12) or a second electromagnetic clutch (13).

2. The ultra-low moment of inertia torque direction adjustment mechanism according to claim 1, characterized in that: An extension shaft (14) is provided at one end of the planet carrier (6) close to the output shaft (3); the inner ring of the first two-way overrunning clutch (10) is fixedly sleeved on the extension shaft (14) of the planet carrier (6); a hollow first extension sleeve (17) is provided at one end of the planet carrier (6) close to the input shaft (2); the input shaft (2) passes through the center of the first extension sleeve (17); and the planet carrier (6) is rotatably supported on the housing (1) through the first extension sleeve (17).

3. The ultra-low moment of inertia torque direction adjustment mechanism according to claim 2, characterized in that: The outer ring of the first bidirectional overrunning clutch (10) is fixedly connected to the output shaft (3) via a first coupling (15).

4. The ultra-low moment of inertia torque direction adjustment mechanism according to claim 2, characterized in that: A disc (16) is fixedly provided at one end of the planet carrier (6) close to the input shaft (2); one end of the first electromagnetic clutch (9) is fixed on the disc (16) and the other end is fixed on the housing (1).

5. The ultra-low moment of inertia torque direction adjustment mechanism according to claim 1, characterized in that: A hollow second extension sleeve (18) is provided at one end of the gear ring frame (7) close to the output shaft (3), and the output shaft (3) passes through the center of the second extension sleeve (18). When the gear ring frame (7) and the output shaft (3) are connected via the second two-way overrunning clutch (12), the inner ring of the second two-way overrunning clutch (12) is fixedly sleeved on the second extension sleeve (18), and the outer ring of the second two-way overrunning clutch (12) is fixedly connected to the output shaft (3) via the second coupling (19).

6. The ultra-low moment of inertia torque direction adjustment mechanism according to claim 5, characterized in that: The inner ring of the first one-way clutch (11) is fixedly sleeved on the second extension sleeve (18), and the outer ring is fixed on the outer shell (1).

7. The ultra-low moment of inertia torque direction adjustment mechanism according to claim 1, characterized in that: The regulating mechanism also includes an energy feedback module, which is used to transmit torque from the output shaft (3) to the input shaft (2).

8. The ultra-low moment of inertia torque direction adjustment mechanism according to claim 7, characterized in that: The energy feedback module comprises a first energy feedback planetary gear assembly, a ring gear frame (7) and an output shaft (3) are connected via a second electromagnetic clutch (13), a transition piece (20) is fixed inside the ring gear frame (7), and the transition piece (20) is connected to the output shaft (3) via a second one-way clutch (21), the first energy feedback planetary gear assembly comprises a first energy feedback sun gear (22), a plurality of first energy feedback planetary gears (23), a first energy feedback planetary frame (24), a first energy feedback inner ring gear (25), and a plurality of first energy feedback The planetary gear (23) is located between the first energy feeding sun gear (22) and the first energy feeding inner gear ring (25), and the first energy feeding planetary gear (23) is meshed with the first energy feeding sun gear (22) and the first energy feeding inner gear ring (25) at the inside and outside respectively, the first energy feeding inner gear ring (25) is fixed in the gear ring carrier (7), the first energy feeding sun gear (22) is connected to the output shaft (3) via a third one-way clutch (26), and the first energy feeding planetary carrier (24) is connected to the housing (1) via a third electromagnetic clutch (27).

9. The ultra-low moment of inertia torque direction adjustment mechanism according to claim 7, characterized in that: The energy feedback module comprises a second energy feeding planetary gear assembly, wherein the ring gear carrier (7) is connected to the output shaft (3) via a second electromagnetic clutch (13), the second energy feeding planetary gear assembly comprises a second energy feeding sun gear (28), a plurality of second energy feeding planetary gears (29), a second energy feeding planetary carrier (30), and a second energy feeding inner ring gear (31), wherein the plurality of second energy feeding planetary gears (29) are located between the second energy feeding sun gear (28) and the second energy feeding inner ring gear (31), and the second energy feeding planetary gears (29) are meshed with the second energy feeding sun gear (28) and the second energy feeding inner ring gear (31) at the inside and outside thereof, respectively, the second energy feeding inner ring gear (31) is fixed in the ring gear carrier (7), the second energy feeding sun gear (28) is connected to the output shaft (3) via a fourth one-way clutch (32), and the second energy feeding planetary carrier (30) is connected to the housing (1) via a fifth one-way clutch (33).

10. An ultra-low moment of inertia torque direction adjustment mechanism as claimed in claim 8 or 9, characterized in that: The gear ring frame (7) is detachably connected to each inner gear ring.

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