Bidirectional planetary gear transmission

Abstract

The invention relates to a bidirectional planetary gear transmission which comprises a first planetary gear structure, a first overrun clutch, a second planetary gear structure, a second overrun clutch, a third planetary gear set and a planetary carrier. The two overrun clutches with the same structure are combined with the two planetary gear structures respectively, gear transmission is carried out between the overrun clutches and the two planetary gear structures through the third planetary gear set, the two overrun clutches are arranged reversely, and the two-way planetary gear transmission compact and reasonable in structure is formed. The two overrun clutches are controlled by changing the steering direction of the sun gear, so that one overrun clutch is locked, and the other overrun clutch is separated, and different transmission routes are switched. According to the transmission, the multiple planetary gear structures are combined with the multiple overrun clutches, so that the space utilization rate is increased, the size of the transmission is reduced, through the planetary gear structures, power can be reasonably distributed, the transmissible torque of the transmission is improved, and the service life of the transmission is prolonged.

Description

Technical Field

[0001] The present invention relates to the technical field of transmissions, and in particular to a bidirectional planetary gear transmission. Background Art

[0002] The bidirectional planetary gear transmission is a widely used industrial product, suitable for various mechanical equipment, including bending machines, gear broaching machines, forklifts, excavators and automobiles, etc. It is mainly used in industrial industries such as machine tools, robots, aerospace, and engineering machinery. In traditional bidirectional planetary gear transmissions, the transmission frame needs to be switched, which leads to a large volume due to the increase in the number of stages, and the internal space utilization rate is not high. In addition, the unreasonable power distribution of gear reduction in the prior art leads to insufficient overall structural strength, and the damage of different gears leads to a short accuracy retention time.

[0003] How to reduce the size of the transmission, increase the torque that the transmission can transmit, and extend the service life of the transmission has become an urgent problem to be solved. Summary of the invention

[0004] The purpose of the present invention is to provide a bidirectional planetary gear transmission, aiming to solve the problems of large size, unreasonable power distribution and short life of traditional transmissions.

[0005] To solve the above technical problems, the present invention provides a bidirectional planetary gear transmission, comprising: a first planetary gear structure, comprising a sun gear, a first planetary gear set and a first outer gear ring that are meshed in sequence; the sun gear is an input end; a first overrunning clutch, which is sleeved on the periphery of the first planetary gear structure, and the inner ring of the first overrunning clutch is integrated with the first outer gear ring; a second planetary gear structure, comprising a second planetary gear set and a second outer gear ring that are meshed with each other; the planetary gears of the second planetary gear set are coaxial with the corresponding planetary gears of the first planetary gear set and can rotate relatively; a second overrunning clutch, which is sleeved on the periphery of the second planetary gear structure, and the inner ring of the second overrunning clutch is integrated with the second outer gear ring; a third planetary gear set, connecting the first planetary gear set and the second planetary gear set; a planet carrier, which serves as an output end; the first planetary gear set, the second planetary gear set and the third planetary gear set are all rotatably mounted on the planet carrier; wherein the first overrunning clutch and the second overrunning clutch have the same structure and are installed in opposite directions to each other.

[0006] Furthermore, the bidirectional planetary gear transmission also includes: multiple planetary shafts, rotatably mounted on the planetary carrier; the first planetary gear set includes multiple first planetary gears, which respectively correspond to and are fixedly mounted on the multiple planetary shafts; the second planetary gear set includes multiple second planetary gears, which respectively correspond to and are rotatably mounted on the multiple planetary shafts.

[0007] Furthermore, the third planetary gear set includes: a plurality of small planetary gears, which correspond to and are fixedly installed on a plurality of planetary shafts respectively; a plurality of transition shafts, which are rotatably installed on the planetary carrier; a plurality of large transition gears, which are meshed with the plurality of small planetary gears; the large transition gears, which correspond to and are fixedly installed on a plurality of transition shafts respectively; a plurality of small transition gears, which correspond to and are fixedly installed on a plurality of transition shafts respectively; and a plurality of small transition gears, which are meshed with a plurality of second planetary gears respectively.

[0008] Furthermore, the plurality of planetary shafts and the plurality of transition shafts are sequentially spaced apart in the circumferential direction, and the connecting lines of the axis centers of the plurality of planetary shafts and the axis centers of the plurality of transition shafts form a regular hexagon.

[0009] Furthermore, the outer diameter of the small planetary gear is smaller than the outer diameter of the first planetary gear; the outer diameter of the transition small gear is smaller than the outer diameter of the transition large gear; the smaller inner diameter of the first outer gear ring and the second outer gear ring is larger than the circumscribed circle diameter of the multiple transition large gears.

[0010] Furthermore, the plurality of planetary shafts and the plurality of transition shafts are mounted on the planetary carrier via needle bearings; and the second planetary gear is mounted on the corresponding planetary shaft via needle bearing sleeves.

[0011] Furthermore, the number of the first planetary gear, the second planetary gear, the small planetary gear, the transition large gear and the transition small gear are all three.

[0012] Furthermore, the overrunning clutch is a roller overrunning clutch.

[0013] Furthermore, the bidirectional planetary gear transmission also includes: a case body, which defines a tubular installation space, and the case body includes an inlet and an outlet; the first planetary gear structure is installed in the installation space corresponding to the inlet; the planetary carrier is installed in the installation space corresponding to the outlet; the outer rings of the first overrunning clutch and the second overrunning clutch are integrated with the side wall of the case body.

[0014] Furthermore, the bidirectional planetary gear transmission also includes: a blocking plate, which is clamped between the first outer gear ring and the second outer gear ring and is used to isolate the first outer gear ring and the second outer gear ring.

[0015] Implementing the embodiments of the present invention will have the following beneficial effects:

[0016] 1. The overrunning clutch is combined with the planetary gear structure. By setting the inner ring of the first overrunning clutch and the first outer gear ring as one body, and setting the inner ring of the second overrunning clutch and the second outer gear ring as one body, and using the housing as the common outer ring of the first overrunning clutch and the second overrunning clutch, the volume of the gear transmission structure is greatly reduced and the gear installation stability is increased.

[0017] 2. By utilizing the combination of overrunning clutches and planetary gear structures that are set in pairs and in opposite directions, and utilizing the particularity of the planetary gear structure, the clutch states of the two corresponding gear rings are controlled by two overrunning clutches, and the rotation direction of the input end is changed to enable the output end to have different speed ratios and torque outputs. A high speed ratio and a small torque are used during rapid return motion, and a low speed ratio and a large torque are used during operation, thereby improving the overall transmission efficiency and enhancing the load-bearing capacity and stability.

[0018] 3. The output of the sun gear is transmitted to the second planetary gear structure by the third planetary gear set, rather than by a single gear. This reduces the volume of the structure and makes the power distribution inside the transmission more reasonable, increasing the torque that can be transmitted by the transmission and extending the service life of the transmission. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the embodiments of the present invention 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 present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0020] Figure 1 A schematic diagram of the internal structure of a bidirectional planetary gear transmission provided by an embodiment of the present disclosure;

[0021] Figure 2 A schematic diagram of the external structure of a bidirectional planetary gear transmission provided in one embodiment of the present disclosure;

[0022] Figure 3 For along Figure 2 A schematic diagram of the cross-sectional structure in the direction indicated by AA;

[0023] Figure 4 For along Figure 2 A schematic diagram of the cross-sectional structure in the direction indicated by BB;

[0024] Figure 5 For along Figure 2 A schematic diagram of the cross-sectional structure in the direction indicated by CC;

[0025] Figure 6 A schematic diagram of the meshing of a first planetary gear structure provided in an embodiment of the present disclosure;

[0026] Figure 7 A schematic diagram of the connection and meshing between the third planetary gear set and the first planetary gear structure provided in one embodiment of the present disclosure;

[0027] Figure 8 A schematic diagram of the connection and meshing between the second planetary gear structure and the third planetary gear set provided in one embodiment of the present disclosure;

[0028] Fig. 9 A schematic diagram of the overall meshing of a first planetary gear structure, a second planetary gear structure and a third planetary gear set provided in an embodiment of the present disclosure.

[0029] Reference numerals:

[0030] 100, bidirectional planetary gear transmission; 110, first planetary gear structure; 111, sun gear; 112, first planetary gear set; 1121, first planetary gear; 113, first outer ring gear; 120, first overrunning clutch; 121, roller; 122, spring; 123, first inner ring; 124, outer ring; 130, second planetary gear structure; 131, second planetary gear set; 1311, second planetary gear; 132, second outer ring gear; 140, second overrunning clutch; 141, second inner ring; 150, third planetary gear set; 151, small planetary gear; 152, transition shaft; 153, transition large gear; 154, transition small gear; 160, planet carrier; 170, planetary shaft; 180, housing; 181, installation space; 182, inlet; 183, outlet; 190, baffle; 200, needle roller bearing. DETAILED DESCRIPTION

[0031] In order to facilitate the understanding of the present invention, the present invention will be described more fully below with reference to the relevant drawings. The preferred embodiments of the present invention are given in the drawings. However, the present invention can be implemented in many different forms and is not limited to the embodiments described herein. On the contrary, the purpose of providing these embodiments is to make the understanding of the disclosure of the present invention more thorough and comprehensive.

[0032] It should be noted that when an element is referred to as being "fixed to" another element, it may be directly on the other element or there may be a central element. When an element is considered to be "connected to" another element, it may be directly connected to the other element or there may be a central element at the same time. The terms "vertical", "horizontal", "left", "right" and similar expressions used herein are for illustrative purposes only.

[0033] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as those commonly understood by those skilled in the art of the present invention. The terms used herein in the specification of the present invention are only for the purpose of describing specific embodiments and are not intended to limit the present invention. The term "and / or" used herein includes any and all combinations of one or more related listed items.

[0034] A planetary gear transmission is a transmission that uses a planetary gear mechanism to achieve speed change. The planetary gear mechanism is named because it is similar to the solar system. Its center is the sun gear, and there are several planetary gears rotating around the sun gear. There is a common planet carrier between the planetary gears. Outside the planetary gears, there is a large outer ring gear. A planetary gear transmission is a kind of gearbox. It is composed of a planetary outer ring gear, a sun gear, a planetary gear (also called a satellite gear) and a gear axle. According to the motion relationship between the outer ring gear, the sun gear and the planetary gear, it can achieve the input shaft and the output shaft to be separated from the rigid transmission relationship, the input shaft and the output shaft to drive in the same direction or in the opposite direction, and the input and output shaft transmission ratio changes. The planetary gear mechanism has three moving parts that can rotate relative to each other: the sun gear, the planet carrier and the outer ring gear.

[0035] An overrunning clutch is a device that utilizes the speed change or rotation direction change of the master and slave parts and has a self-clutching function, and is mainly used for power transmission and separation between the prime mover and the working machine or between the driving shaft and the driven shaft inside the machine. The roller overrunning clutch provided in the embodiment of the present disclosure includes an inner ring, an outer ring, and a brake assembly arranged between the inner ring and the outer ring, wherein the brake assembly includes rollers, springs, bearings and other components. When the inner ring rotates clockwise, the roller moves counterclockwise to the narrow side of the groove under the action of centrifugal force, and is stuck between the outer ring and the inner ring. The outer ring is driven to rotate by the friction force of the roller. At this time, the overrunning clutch is in a working state. Since the outer ring is fixed to the box body and does not rotate in the embodiment of the present disclosure, when the inner ring and the outer ring are stuck, the inner ring stops rotating, and the planetary gear structure drives the inner ring to rotate. The sun gear is the driving gear, which drives the planetary gear to rotate, and then drives the planetary carrier to rotate along the same direction as the sun gear.

[0036] In the disclosed embodiment, the bidirectional planetary gear transmission 100 uses two overrunning clutches installed in opposite directions. When the sun gear 111 rotates clockwise, the first overrunning clutch 120 is locked. Since the second overrunning clutch 140 is installed in the opposite direction to the first overrunning clutch 120, the second overrunning clutch 140 is in a disengaged state and does not participate in the work. The sun gear 111 is meshed with the first planetary gear 1121, and the first planetary gear 1121 drives the output end planetary carrier 160 to rotate and output the speed and torque. At this time, the direction of the output end planetary carrier 160 is the same as that of the sun gear 111, which is clockwise. When the sun gear 111 rotates counterclockwise, the first overrunning clutch 120 is disengaged, and the second overrunning clutch 140 is locked. The second overrunning clutch 140 has the same structure as the first overrunning clutch 120, and the inner ring is meshed with the planetary gear structure. The sun gear 111 rotates to transfer power to the second planetary gear 1311 through gear transmission. The second planetary gear 1311 drives the planetary carrier 160 to rotate and output in the same direction as the sun gear 111, so that no matter whether the sun gear rotates clockwise or counterclockwise, the output direction of the planetary carrier 160 is always the same as the sun gear 111. At the same time, due to the difference between the transmission path between the first overrunning clutch 120 and the planetary carrier 160 and the transmission path between the second overrunning clutch 140 and the planetary carrier 160, the speed and torque transmitted from the sun gear 111 to the output end planetary carrier 160 are different in the clockwise and counterclockwise situations. That is, the bidirectional planetary gear transmission 100 in the disclosed embodiment can achieve different speeds in the forward and reverse directions. When the sun gear 111 rotates clockwise, the first overrunning clutch 120 is locked and the second overrunning clutch 140 is disengaged; when the sun gear 111 rotates counterclockwise, the first overrunning clutch 120 is disengaged and the second overrunning clutch 140 is locked. The outer ring gear of the planetary gear structure corresponding to the overrunning clutch in the disengaged state only rotates with the planet carrier, and the outer ring gear of the planetary gear structure corresponding to the overrunning clutch in the locked state is fixed, and the planet carrier rotates. The rotation direction of the planet carrier is consistent with the rotation direction of the sun gear, that is, the output rotation direction is the same as the input rotation direction.

[0037] Combination Figures 1 to 9As shown, the present invention discloses a bidirectional planetary gear transmission 100, comprising a first planetary gear structure 110, a first overrunning clutch 120, a second planetary gear structure 130, a second overrunning clutch 140, a third planetary gear set 150 and a planet carrier 160. The first planetary gear structure 110 comprises a sun gear 111, a first planetary gear set 112 and a first outer gear ring 113 which are meshed in sequence. The sun gear 111 is an input end. The first overrunning clutch 120 is sleeved on the periphery of the first planetary gear structure 110, the side wall of the housing 180 forms an outer ring 124 of the first overrunning clutch 120, and the first outer gear ring 113 simultaneously constitutes a first inner ring 123 (inner rotor) of the first overrunning clutch 120. The second planetary gear structure 130 comprises a second planetary gear set 131 and a second outer gear ring 132 which are meshed with each other. The planetary gears of the second planetary gear set 131 are coaxial with the planetary gears of the first planetary gear set 112, and can rotate relatively. The second overrunning clutch 140 is sleeved on the periphery of the second planetary gear structure 130. The inner ring of the second overrunning clutch 140 is integrated with the second outer gear ring 132, that is, the second outer gear ring 132 also constitutes the second inner ring 141 (inner rotor) of the second overrunning clutch 140. The first overrunning clutch 120 and the second overrunning clutch 140 are coaxially arranged in parallel and spaced apart, and in the direction from the inlet 182 to the outlet 183, the clutch directions of the first overrunning clutch 120 and the second overrunning clutch 140 are opposite. For example, when the sun gear 111 rotates clockwise, the first overrunning clutch 120 is locked and the second overrunning clutch 140 is disengaged. On the contrary, when the sun gear 111 rotates counterclockwise, the first overrunning clutch 120 is disengaged and the second overrunning clutch 140 is locked. The third planetary gear set 150 connects the first planetary gear set 112 and the second planetary gear set 131. The planet carrier 160 serves as the output end, and the first planetary gear set 112, the second planetary gear set 131 and the third planetary gear set 150 are all rotatably mounted on the planet carrier 160. When the sun gear 111 rotates clockwise, the first overrunning clutch 120 is locked, the second overrunning clutch 140 is disengaged, and the first outer gear ring 113 is fixed. The movement of the sun gear 111 drives the first planetary gear 1121 to rotate and then drives the planet carrier 160 to output. When the sun gear 111 rotates counterclockwise, the first overrunning clutch 120 is disengaged, the first outer gear ring 113 is not fixed, the second overrunning clutch 140 is locked, and the second outer gear ring 132 is fixed. The movement of the sun gear 111 drives the first planetary gear 1121 to rotate, the first planetary gear 1121 drives the gear in the third planetary gear to rotate, and the gear of the third planetary gear set 150 drives the second planetary gear 1311 to rotate. Since the second outer gear ring 132 is locked and fixed, the second planetary gear 1311 drives the planet carrier 160 to rotate and output.

[0038] Combination Figure 1 , Figure 3 , Figure 6 and Figure 8 As shown, in some embodiments, the bidirectional planetary gear transmission 100 further includes a plurality of planetary shafts 170. The planetary shafts 170 are used to support and install the first planetary gear 1121, the small planetary gear 151 and the second planetary gear 1311. One end of the planetary shaft 170 is rotatably mounted on the planetary frame 160, and the other end is rotatably mounted on the housing 180. The first planetary gear set 112 includes a plurality of first planetary gears 1121, and the plurality of first planetary gears 1121 are respectively corresponding to and fixedly mounted on the plurality of planetary shafts 170. The plurality of planetary shafts 170 are triangular in shape and parallel to each other. The second planetary gear set 131 includes a plurality of second planetary gears 1311, and the number of the second planetary gears 1311 is the same as the number of the first planetary gears 1121 and is rotatably mounted on the plurality of planetary shafts 170 in a one-to-one correspondence. The second planetary gear 1311 is rotatably mounted on the planetary shaft 170, while the first planetary gear 1121 is fixedly mounted on the planetary shaft 170. When the sun gear 111 drives the first planetary gear 1121 to rotate, it will not directly drive the second planetary gear 1311 to rotate. When the first outer gear ring 113 is fixed, the first planetary gear 1121 can directly drive the planetary carrier 160 to rotate and output through the planetary shaft 170. When the first overrunning clutch 120 is disengaged, the first outer gear ring 113 is not fixed. At this time, the sun gear 111 needs to drive the first planetary gear 1121 to rotate, and the first planetary gear 1121 drives the gear of the third planetary gear set 150 to rotate, so as to drive the second planetary gear 1311 to rotate through the rotation of the gear of the third planetary gear set 150. When the second outer gear ring 132 is fixed, the second planetary gear 1311 drives the planetary carrier 160 to rotate and output, thereby realizing the change of the speed ratio.

[0039] Combination Figure 1 , Figure 3 , Figure 6 , Figure 7 As shown in FIG8 , in some embodiments, the third planetary gear set 150 includes a plurality of

[0040] A small planetary gear, a plurality of transition shafts 152, a plurality of transition large gears 153 and a plurality of transition small gears 154. The number of small planetary gears 151 is the same as that of the first planetary gears 1121, and they are coaxial with the first planetary gears 1121. The small planetary gears 151 are fixedly integrated with the planetary shaft 170 and rotate with the rotation of the first planetary gear 1121. The plurality of transition shafts 152 are arranged in parallel with the planetary shaft 170 and are rotatably mounted on the planetary carrier 160. The plurality of transition large gears 153 are fixedly mounted on the transition shaft 152 and mesh with the plurality of small planetary gears 151. The sun gear 111 drives the first planetary gear 1121 to rotate. The first planetary gear 1121 and the small planetary gear 151 are both fixed to the planetary shaft 170. Therefore, the rotation of the first planetary gear 1121 drives the planetary shaft 170 to rotate, and drives the small planetary gear 151 to rotate. The small planetary gear 151 meshes with the transition large gear 153, and thus drives the transition large gear 153 to rotate. The transition large gear 153 and the transition small gear 154 are both fixedly mounted on the transition shaft 152. Therefore, the rotation of the transition large gear 153 drives the transition shaft 152 to rotate, and then drives the transition small gear 154 to rotate. The plurality of transition small gears 154 are correspondingly meshed with the plurality of second planetary gears 1311. Therefore, the rotation of the transition small gear 154 drives the second planetary gear 1311 to rotate. When the second outer gear ring 132 is fixed, the rotation of the second planetary gear 1311 can drive the planet carrier 160 to rotate and output.

[0041] Combination Figure 1 , Figure 3 , Figure 6 , Figure 7 , Figure 8 and Fig. 9 As shown, in some embodiments, multiple planetary shafts 170 and multiple transition shafts are sequentially arranged at intervals along the circumferential direction and are spatially staggered to prevent interference between gears. The axis centers of the multiple planetary shafts 170 and the axis centers of the multiple transition shafts 152 form a regular hexagon. The axis centers of the multiple planetary shafts 170 and the axis centers of the multiple transition shafts 152 are respectively located at the vertices of the regular hexagon, so that the internal space of the box 180 is fully utilized.

[0042] Combination Figures 6 to 9 As shown, in some embodiments, the outer diameter of the small planetary wheel 151 is smaller than the outer diameter of the first planetary wheel 1121 .

[0044] The small planetary gear 151 is coaxially arranged with the first planetary gear 1121, and the outer diameter of the small planetary gear 151 is set smaller than the outer diameter of the first planetary gear 1121 to prevent the diameter of the circumscribed circle of the plurality of small planetary gears 151 from being too large, which would increase the overall size of the housing 180. Similarly, the outer diameter of the transition pinion 154 is smaller than the outer diameter of the transition large gear 153, and the smaller inner diameter of the first outer gear ring 113 and the second outer gear ring 132 is larger than the diameter of the circumscribed circle of the plurality of transition large gears 153.

[0045] It is understandable that the number of teeth of the transition pinion 154 , the transition gear 153 , and the asteroid wheel 151 can be adjusted as needed to obtain different speed ratio outputs.

[0046] Combination Figure 1 and Figure 3 As shown, in some embodiments, multiple planetary shafts 170 and multiple transition shafts 152 are mounted on the planetary carrier 160 through needle bearings 200. The second planetary gear 1311 is sleeved and mounted on the corresponding planetary shaft 170 through the needle bearing 200. One end of the planetary shaft 170 and the transition shaft 152 are mounted on the planetary carrier 160 through the needle bearing 200, and the other end is mounted on the housing 180 through the needle bearing 200 to support the rotation of the planetary shaft 170 and the transition shaft 152.

[0047] Combination Figures 6 to 9 As shown, in some embodiments, the number of the first planetary gear 1121, the second planetary gear 1311, the small planetary gear 151, the transition gear 153 and the transition gear 154 are all three. Among them, the first planetary gear 1121, the small planetary gear 151 and the second planetary gear 1311 are coaxially mounted on the planetary shaft 170. The first planetary gear 1121, the second planetary gear 1311, the small planetary gear 151, the transition gear 153 and the transition gear 154 are uniformly distributed on the same pitch circle in the radial direction, and the spacing between each other is the same. The transition gear 153 and the transition gear 154 are coaxially fixedly mounted on the transition shaft 152. The first planetary gear 1121 and the small planetary gear 151 are both fixedly mounted on the planetary gear, and the second planetary gear 1311 is rotatably mounted on the planetary shaft 170 through the needle bearing 200. So that the sun gear 111 drives the first planetary gear 1121 to rotate, and the first planetary gear 1121 will not directly drive the second planetary gear 1311 to rotate when driving the planetary shaft 170 to rotate. The second planetary gear 1311 is rotated by the sun gear 111 to drive the first planetary gear 1121 to rotate, the first planetary gear 1121 drives the planetary shaft 170 to rotate, the planetary shaft 170 drives the asteroid wheel 151 to rotate, the asteroid wheel 151 drives the transition large gear 153 to rotate, the transition large gear 153 drives the transition shaft 152 and then drives the transition small gear 154 to rotate, and the transition small gear 154 is meshed with the second planetary gear 1311 to drive the second planetary gear 1311 to rotate, thereby realizing speed ratio transmission.

[0048] Combination Figures 1 to 5 As shown, in some embodiments, the overrunning clutch is a roller 121 overrunning clutch. The housing 180, the first outer gear ring 113 (or the second outer gear ring 132), the bearing, the roller 121, the retaining spring and the spring 122 constitute the first overrunning clutch 120 (the second overrunning clutch 140). The retaining spring is clamped on the first outer gear ring 113 and the second outer gear ring 132 on one side of the bearing to limit the axial movement of the bearing.

[0049] Combination Figures 1 to 3 As shown, in some embodiments, the bidirectional planetary gear transmission 100 further includes a housing 180. The housing 180 defines a tubular installation space 181, and the housing 180 includes an inlet 182 and an outlet 183. The first planetary gear structure 110 is installed in the installation space 181 corresponding to the inlet 182. The sun gear 111 is a driving gear. The planet carrier 160 is installed in the installation space 181 corresponding to the outlet 183, and the planet carrier 160 is an output end. The outer ring 124 of the first overrunning clutch 120 and the second overrunning clutch 140 is integrated with the side wall of the housing 180, that is, the outer ring 124 of the first overrunning clutch 120 and the second overrunning clutch 140 formed by the inner wall of the housing 180 is fixed.

[0050] The box body 180 at the inlet 182 can be connected to the motor by screws, and the sun gear 111 can be fixedly connected to the motor shaft to obtain power.

[0051] Combination Figures 1 to 3 As shown, in some embodiments, the bidirectional planetary gear transmission 100 further includes a stopper 190.

[0052] piece

[0053] 190 is sandwiched between the first outer gear ring 113 and the second outer gear ring 132 to isolate the first outer gear ring 113 from the second outer gear ring 132 .

[0054] Exemplarily, the bidirectional planetary gear transmission 100 provided in the embodiment of the present disclosure can be installed according to the following steps:

[0055] Step 1: first, put the needle bearing 200 onto the ends of the planetary shaft 170 and the transition shaft 152 , and then install the needle bearing 200 into the planetary carrier 160 , and then install the needle bearing 200 into the inner hole of the second planetary gear 1311 .

[0056] Step 2: Place the second planetary gear 1311 equipped with the needle bearing 200 and the transition gear 153 in the position to be installed. Note that you should not press-fit them at this time.

[0057] Step three: put the first planetary gear 1121 into the position to be installed, and install the planetary shaft 170. Note that the first planetary gear 1121 must be positioned with the aid of a tooling with the same parameters as the first outer gear ring 113 to ensure that the tooth positions of each set of first planetary gears 1121 and the asteroid gear 151 are consistent, and then press them into place with a press. The press-fit connection here needs to be carried out by interference fit.

[0058] Step 4: Press-fit the second planetary gear 1311. Since the transition large gear 153 and the second planetary gear 1311 do not need to be positioned, directly insert the transition small gear 154 and the second planetary gear 1311 at the same time, press the transition small gear 154 and the second planetary gear 1311 into place together, and finally install the retaining spring.

[0059] Step 5: Assemble the second overrunning clutch 140. First, install the bearing on the housing 180 and fix it with a circlip, install the spring 122 and the roller 121 into the second outer gear ring 132 and fix it with a circlip. Install the first overrunning clutch 120 in the same way.

[0060] Step 6: Install the sun gear 111 and the motor base assembly. Install the bearing into the motor base and fix it with a circlip, install the sun gear 111, fix it with a circlip 3, and then insert the sealing ring.

[0061] Step 7: Install the sun gear 111 and the motor base assembly to the housing 180. Install the bearing to the inlet 182 of the housing 180, insert the sun gear 111 and the motor base assembly into engagement, connect and install the overrunning clutch at the corresponding gear position, and fix the motor base to the housing 180 with screws.

[0062] Step 8: Install the end cover of outlet 183. Install the bearing on the planet carrier 160 and then install the end cover, connect it with screws and finally insert the sealing ring.

[0063] Exemplarily, the working principle of the bidirectional planetary gear transmission 100 provided by the embodiment of the present disclosure is as follows:

[0064] The housing 180, the first outer gear ring 113, the bearing, the roller 121, the retaining spring and the spring 122 form the first overrunning clutch 120. The housing 180, the second outer gear ring 132, the bearing, the roller 121, the retaining spring and the spring 122 form the second overrunning clutch 140. The first overrunning clutch 120 and the second overrunning clutch 140 are arranged in parallel and opposite directions in the axial direction and separated by the baffle 190. The sun gear 111 is meshed with the first planetary gear 1121, the first planetary gear 1121 is coaxially fixed with the asteroid gear 151, the asteroid gear 151 is meshed with the transition gear 153, the transition gear 153 is coaxially fixed with the transition pinion 154, and the transition pinion 154 is meshed with the second planetary gear 1311. The second planetary gear 1311 is mounted on the planetary shaft 170 through the needle bearing 200.

[0065] When the sun gear 111 rotates clockwise, the sun gear 111 drives the first planetary gear to rotate, and the first planetary gear drives the first outer gear ring 113 to rotate in the opposite direction, the first overrunning clutch 120 is locked, the first outer gear ring 113 is fixed and does not rotate, and the first planetary gear 1121 drives the planet carrier 160 to rotate clockwise. The speed ratio calculation formula at this time is:

[0066] I=1+Z 齿圈1 / Z 太阳 ; where Z 齿圈1 is the number of teeth of the first outer gear ring 113; Z 太阳 is the number of teeth of the sun gear 111.

[0067] When the sun gear 111 rotates counterclockwise, the clutch states of the two clutches are opposite, the second overrunning clutch 140 is locked, and the first overrunning clutch 120 is disengaged, and the output end obtains a larger speed ratio and output torque. The speed ratio calculation formula at this time is:

[0068] i=Z 行1 / Z 太阳 ×Z 过大 / Z 行小 ×Z 行2 / Z 过小 ×Z 圈2 / Z 行2 +1; among them, Z 行1 is the number of teeth of the first planetary gear; Z 太阳 is the number of teeth of the sun gear 111; Z 过大 The number of teeth of the transition gear is 153; Z 行小 The number of teeth of the asteroid wheel is 151; Z 行2 is the number of teeth of the second planetary gear 1311; Z 过小 Transition pinion 154 teeth; Z 圈2 The number of teeth of the second outer gear ring 132. In the present invention, the clutch 1 and the clutch 2 must be used in pairs, and the front and rear positions can be reversed, but the directions must be opposite.

[0069] The above description and the accompanying drawings sufficiently illustrate the embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The embodiments represent only possible variations, and unless explicitly required, individual components and functions are optional, and the order of operations may vary. Portions and features of some embodiments may be included in or replace portions and features of other embodiments. Moreover, the words used in this application are only used to describe the embodiments and are not used to limit the claims. As used in the description of the embodiments and the claims, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. Similarly, the term "and / or" as used in this application refers to any and all possible combinations of one or more associated listings. In addition, when used in this application, the term "comprise" and its variant "including"

[0070] The terms "comprises" and / or "comprising" refer to the presence of stated features, integers, steps, operations, elements, and / or components, but not to the

[0071] The existence or addition of one or more other features, integral bodies, steps, operations, elements, components and / or groups thereof is excluded. In the absence of further restrictions, the elements defined by the statement "comprising a ..." do not exclude the existence of other identical elements in the process, method or device comprising the elements. Herein, each embodiment may focus on the differences from other embodiments, and the same and similar parts between the embodiments may refer to each other. For the methods, products, etc. disclosed in the embodiments, if they correspond to the method part disclosed in the embodiments, the relevant parts may refer to the description of the method part.

[0072] The above-described embodiments only express several implementation methods of the present invention, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the invention patent. The technical features of the above-described embodiments can be arbitrarily combined. In order to make the description concise, all possible combinations of the technical features in the above-described embodiments are not described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification. It should be pointed out that, for a person of ordinary skill in the art, several variations and improvements can be made without departing from the concept of the present invention, and these all belong to the protection scope of the present invention. Therefore, the protection scope of the patent of the present invention shall be based on the attached claims.

Claims

1. A bidirectional planetary gear transmission, characterized in that: include: A first planetary gear structure (110) comprises a sun gear (111), a first planetary gear set (112) and a first outer gear ring (113) which are meshed in sequence; the sun gear (111) is an input end; A first overrunning clutch (120) is sleeved on the periphery of the first planetary gear structure (110), wherein the inner ring of the first overrunning clutch (120) is integrated with the first outer gear ring (113); A second planetary gear structure (130) comprises a second planetary gear set (131) and a second outer gear ring (132) meshing with each other; the planetary gears of the second planetary gear set (131) are coaxial with the planetary gears of the first planetary gear set (112) and can rotate relative to each other; A second overrunning clutch (140) is sleeved on the outer periphery of the second planetary gear structure (130), wherein the inner ring of the second overrunning clutch (140) is integrated with the second outer gear ring (132); A third planetary gear set (150) connecting the first planetary gear set (112) and the second planetary gear set (131); A planet carrier (160) serves as an output end; the first planetary gear set (112), the second planetary gear set (131) and the third planetary gear set (150) are all rotatably mounted on the planet carrier (160); The first overrunning clutch (120) and the second overrunning clutch (140) have the same structure and are installed in opposite directions.

2. The bidirectional planetary gear transmission according to claim 1, characterized in that: Also includes: A plurality of planet shafts (170) rotatably mounted on the planet carrier (160); The first planetary gear set (112) comprises a plurality of first planetary gears (1121). (1121) Respectively corresponding to and fixedly mounted on the plurality of planetary shafts (170); The second planetary gear set (131) comprises a plurality of second planetary gears (1311), wherein the second planetary gears (1311) are Don't Correspondingly and rotatably mounted on the plurality of planetary shafts (170).

3. The bidirectional planetary gear transmission according to claim 2, characterized in that: The third planetary gear set (150) include: A plurality of small planetary wheels (151), respectively corresponding to and fixedly mounted on the plurality of planetary shafts (170); A plurality of transition shafts (152) rotatably mounted on the planet carrier (160); A plurality of transition large gears (153) mesh with the plurality of small planetary gears (151); the transition large gears (153) Respectively corresponding to and fixedly mounted on the plurality of transition shafts (152); A plurality of transition pinions (154) are respectively corresponding to and fixedly mounted on the plurality of transition shafts (152); the plurality of transition pinions (154) are correspondingly meshed with the plurality of second planetary gears (1311).

4. The bidirectional planetary gear transmission according to claim 3, characterized in that: The plurality of planetary shafts (170) and the plurality of transition shafts (152) are arranged in sequence and spaced apart along the circumferential direction, and the axis centers of the plurality of planetary shafts (170) and the axis centers of the plurality of transition shafts (152) form a regular hexagon.

5. The bidirectional planetary gear transmission according to claim 3, characterized in that: The outer diameter of the small planetary wheel (151) is smaller than the outer diameter of the first planetary wheel (1121); The outer diameter of the transition pinion (154) is smaller than the outer diameter of the transition large gear (153); The smaller inner diameter of the first outer gear ring (113) and the second outer gear ring (132) is larger than the diameter of the circumscribed circle of the plurality of transition large gears (153).

6. The bidirectional planetary gear transmission according to any one of claims 2 to 5, characterized in that: The plurality of planetary shafts (170) and the plurality of transition shafts (152) are both mounted on the planetary carrier (160) via needle bearings (200); The second planetary gear (1311) is sleeved and mounted on the corresponding planetary shaft (170) via a needle bearing (200).

7. The bidirectional planetary gear transmission according to any one of claims 2 to 5, characterized in that: The number of the first planetary gear (1121), the second planetary gear (1311), the small planetary gear (151), the transition large gear (153) and the transition small gear (154) are all three.

8. The bidirectional planetary gear transmission according to any one of claims 2 to 5, characterized in that: The overrunning clutch is a roller (121) type overrunning clutch.

9. The bidirectional planetary gear transmission according to any one of claims 2 to 5, characterized in that: Also includes: A housing (180) defines a tubular installation space (181), wherein the housing (180) includes an inlet (182) and an outlet (183); the first planetary gear structure (110) is installed in the installation space (181) corresponding to the inlet (182); The planet carrier (160) is installed in the installation space (181) corresponding to the outlet (183); The outer rings of the first overrunning clutch (120) and the second overrunning clutch (140) are connected to the housing (180) The side walls are integrated.

10. The bidirectional planetary gear transmission according to claim 9, characterized in that: Also includes: The baffle (190) is sandwiched between the first outer gear ring (113) and the second outer gear ring (132) to isolate The first outer gear ring (113) and the second outer gear ring (132).

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