An eccentric shaft metal planetary gear reduction motor for automobiles

Abstract

This invention discloses an eccentric shaft metal planetary gear reducer motor for automobiles, belonging to the technical field of planetary gear reducer motors. It includes a main motor, an outer cooling housing, an oil tank, and a gear cavity. The outer cooling housing is fitted around the outer periphery of the main motor. The gear cavity is fixedly connected to the outer cooling housing and coaxially arranged with the motor shaft of the main motor. The oil tank is fixedly installed on the outer wall of the outer cooling housing. A lubrication assembly is installed inside the gear cavity. This invention cleverly reuses the transmission components of the reducer motor as a volumetric pumping element by incorporating a lubrication assembly consisting of a positioning disc, a second internal gear ring, a double-direction gear ring, and a transmission gear inside the gear cavity. The eccentric meshing of the double-direction gear ring and the second internal gear ring forms a variable-volume closed cavity. The self-powered rotation of the gears enables the intake, pressurization, and discharge of lubricating oil, eliminating the need for a separate oil pump and drive motor. This significantly simplifies the overall structure and reduces manufacturing costs and energy consumption.

Description

Technical Field

[0001] This invention relates to the technical field of planetary gear reducers, and in particular to an eccentric shaft metal planetary gear reducer for automobiles. Background Technology

[0002] Planetary gear reducers are widely used in automobiles due to their advantages such as compact structure, large transmission ratio, and strong load-bearing capacity. Among them, the eccentric shaft planetary gear reducer (also known as differential gear reducer or cycloidal reducer) drives the differential gear to mesh with the internal gear ring through an eccentric disc, which can achieve a large reduction ratio output. It is especially suitable for automotive environments with strict requirements for installation space and torque density.

[0003] During the operation of a geared motor, intense friction and heat are generated in the gear meshing area, requiring continuous lubrication and cooling with lubricating oil. Otherwise, tooth surface scuffing, excessive wear, or even gear seizure will occur. Existing planetary geared motors typically rely on the rotation of the gears themselves to agitate the oil and splash it to each lubrication point. This method is structurally simple, but at low speeds, the gear linear velocity is insufficient, making it difficult to effectively agitate the oil, resulting in insufficient oil supply to the meshing area and dry friction. At high speeds, the resistance to oil agitation increases, causing additional power loss and temperature rise. Summary of the Invention

[0004] The purpose of this section is to outline some aspects of embodiments of the present invention and to briefly describe some preferred embodiments. Simplifications or omissions may be made in this section, as well as in the abstract and title of this application, to avoid obscuring the purpose of these documents; however, such simplifications or omissions should not be construed as limiting the scope of the invention.

[0005] In view of the problems existing in the above and / or existing eccentric shaft metal planetary gear reducers for automobiles, the present invention is proposed.

[0006] Therefore, the problem to be solved by the present invention is how to solve the problem that existing planetary gear reducers usually rely on the rotation of the gears themselves to agitate the oil and splash it to each lubrication point. However, under low-speed conditions, the gear linear velocity is insufficient, and the oil is difficult to be effectively splashed up, resulting in insufficient oil supply to the meshing area and dry friction.

[0007] To solve the above-mentioned technical problems, the present invention provides the following technical solution: an eccentric shaft metal planetary gear reducer motor for automobiles, comprising a main motor, an outer cooling housing, an oil tank, and a gear cavity. The outer cooling housing is sleeved on the outer periphery of the main motor. The gear cavity is fixedly connected to the outer cooling housing and coaxially arranged with the motor shaft of the main motor. The oil tank is fixedly arranged on the outer wall of the outer cooling housing. A lubrication assembly is provided inside the gear cavity. The lubrication assembly includes a positioning disc, a second internal gear ring, a bidirectional gear ring, and a transmission gear. The positioning disc is fixedly connected to the gear cavity. The gear ring is rotatably connected to the gear cavity. The bidirectional gear ring is eccentrically positioned inside the second inner gear ring and rotatably connected to the positioning disk. The bidirectional gear ring and the second inner gear ring mesh with each other and together form a closed cavity. The transmission gear meshes with the bidirectional gear ring. An arc-shaped island is provided inside the positioning disk, which is located inside the closed cavity. An oil inlet groove is opened in the tooth groove of the second inner gear ring. An oil cavity communicating with the closed cavity is opened in the gear cavity. A connecting hole is opened coaxially at the position corresponding to the bidirectional gear on the positioning disk. A circulation pipe for connecting the closed cavity and the connecting hole is opened inside the positioning disk.

[0008] As a preferred embodiment of the eccentric shaft metal planetary gear reducer motor for automobiles described in this invention, a transmission shaft is further provided inside the gear cavity, the transmission shaft is connected to the motor shaft of the main motor, and the transmission gear is connected to the transmission shaft by a key.

[0009] As a preferred embodiment of the eccentric shaft metal planetary gear reducer motor for automobiles described in this invention, the oil chamber is connected to the closed chamber, one end of the oil chamber corresponds to the position where the second internal gear ring and the bidirectional gear mesh, and the other end extends to the cone point of the arc-shaped island platform, and the circulation pipe corresponds to the end of the arc-shaped island platform away from the oil chamber.

[0010] As a preferred embodiment of the eccentric shaft metal planetary gear reducer motor for automobiles described in this invention, the bidirectional gear ring includes an inner gear ring and an outer gear ring. The outer gear ring is sleeved on the outer circumference of the inner gear ring and is fixedly connected to the inner gear ring. The outer gear ring meshes with a second inner gear ring, and the transmission gear meshes with the inner gear ring.

[0011] In a preferred embodiment of the eccentric shaft metal planetary gear reducer motor for automobiles described in this invention, the oil inlet groove is formed within the tooth groove of the second internal gear ring.

[0012] As a preferred embodiment of the eccentric shaft metal planetary gear reducer motor for automobiles described in this invention, the oil tank is connected to a first oil pipe and a second oil pipe at both ends, the first oil pipe is connected to the oil cavity, and the second oil pipe passes through the outer cooling shell and is connected to the connecting hole.

[0013] As a preferred embodiment of the eccentric shaft metal planetary gear reducer motor for automobiles described in this invention, the oil chamber, the closed chamber, the connecting hole, the internal space of the gear cavity, the first oil pipe, the second oil pipe, and the oil tank together constitute a circulating oil circuit.

[0014] As a preferred embodiment of the eccentric shaft metal planetary gear reducer motor for automobiles described in this invention, the gear cavity is further provided with a transmission component, including a first internal gear ring fixed inside the gear cavity, a rotation hole for mounting a transmission shaft is provided at one end of the gear cavity shaft, an eccentric disk is provided on the outer periphery of the transmission shaft, a differential gear is provided on the outer periphery of the eccentric disk, the differential gear is eccentrically set with the first internal gear ring through the eccentric disk, and the differential gear meshes with the first internal gear ring.

[0015] As a preferred embodiment of the eccentric shaft metal planetary gear reducer motor for automobiles described in this invention, the differential gear has a guide hole inside, a connecting pin is rotatably arranged inside the guide hole, a turntable is arranged at one end of the connecting pin, and an output shaft is fixedly arranged at the center of the turntable.

[0016] As a preferred embodiment of the eccentric shaft metal planetary gear reducer motor for automobiles described in this invention, the number of eccentric discs is three, the guide holes corresponding to the three differential gears are provided with overlapping cavities, the connecting pins are inserted into the interior of the overlapping cavities, the three eccentric discs are linearly arranged on the outer periphery of the drive shaft, and the angles between adjacent eccentric discs are equal.

[0017] The beneficial effects of this invention are:

[0018] 1. By ingeniously reusing the transmission components of the geared motor itself as a positive displacement pumping element through a lubrication assembly consisting of a positioning disc, a second internal gear ring, a double-acting gear ring, and a transmission gear inside the gear cavity, the double-acting gear ring and the second internal gear ring engage eccentrically to form a closed cavity with variable volume. The lubricating oil can be drawn in, pressurized, and discharged using the self-power of the gear rotation, eliminating the need for a separate oil pump and drive motor. This significantly simplifies the overall structure and reduces manufacturing costs and energy consumption.

[0019] 2. The transmission gears and drive shaft are linked, and the pumping flow rate of the lubrication components directly depends on the speed of the main motor. The higher the motor speed, the faster the frequency of change in the volume of the enclosed cavity, and the greater the lubricating oil circulation flow rate. This provides stronger cooling and lubrication under high load and high speed conditions, while automatically reducing the oil supply under low speed and light load conditions to avoid over-lubrication and power waste. This adaptive characteristic effectively solves the problem of insufficient oil supply at low speeds and excessive oil supply at high speeds in traditional fixed-displacement oil pumps, extending the service life of gears and bearings.

[0020] 3. The oil tank, the first oil pipe, the oil chamber, the closed chamber, the circulation pipe, the connecting hole, the internal space of the gear cavity, and the second oil pipe together form a closed-loop circulating oil circuit. During the circulation process, the lubricating oil can actively flow through key friction pairs such as the meshing area between the differential gear and the first internal gear ring, and the sliding interface between the connecting pile and the guide hole, which can quickly carry away the heat generated by friction and dissipate it to the external environment through the outer cooling shell and the oil tank wall. This significantly reduces the temperature rise of the geared motor during continuous operation under high load, prevents the lubricating oil from deteriorating and failing due to high temperature, and thus improves the thermal load capacity and reliability of the whole machine. Attached Figure Description

[0021] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the following description of the embodiments will be briefly introduced. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0022] Figure 1 This is a scene illustration of an eccentric shaft metal planetary gear reducer motor for automobiles.

[0023] Figure 2 Structural explosion of an eccentric shaft metal planetary gear reducer motor for automobiles Figure 1 .

[0024] Figure 3 Structural explosion of an eccentric shaft metal planetary gear reducer motor for automobiles Figure 2 .

[0025] Figure 4 This is a cross-sectional view of the gear cavity of an eccentric shaft metal planetary gear reducer motor for automobiles.

[0026] Figure 5 This is a diagram showing the internal structure of the gear cavity in an eccentric shaft metal planetary gear reducer motor for automobiles.

[0027] Figure 6 This is a structural diagram of the lubrication assembly for an eccentric shaft metal planetary gear reducer motor used in automobiles.

[0028] Figure 7 This is a structural diagram of the transmission assembly inside the gear cavity of an eccentric shaft metal planetary gear reducer motor for automobiles.

[0029] In the diagram: 1. Main motor; 2. Outer cooling housing; 3. Oil tank; 31. First oil pipe; 32. Second oil pipe; 4. Gear cavity; 41. Drive shaft; 42. First internal gear ring; 43. Rotating hole; 44. Eccentric disc; 45. Differential gear; 46. Guide hole; 47. Connecting pin; 48. Turntable; 49. Output shaft; 5. Lubrication assembly; 51. Positioning disc; 52. Second internal gear ring; 53. Bidirectional gear ring; 531. Internal gear ring; 532. External gear ring; 54. Drive gear; 55. Enclosed cavity; 56. Arc-shaped island; 57. Oil inlet groove; 58. Oil cavity; 59. Connecting hole; 510. Circulation pipe. Detailed Implementation

[0030] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, the specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings.

[0031] Many specific details are set forth in the following description in order to provide a full understanding of the invention. However, the invention may also be practiced in other ways different from those described herein, and those skilled in the art can make similar extensions without departing from the spirit of the invention. Therefore, the invention is not limited to the specific embodiments disclosed below.

[0032] Secondly, the term "one embodiment" or "embodiment" as used herein refers to a specific feature, structure, or characteristic that may be included in at least one implementation of the present invention. The phrase "in one embodiment" appearing in different places in this specification does not necessarily refer to the same embodiment, nor is it a single or selective embodiment that is mutually exclusive with other embodiments.

[0033] Example 1, referring to Figures 1 to 7 This is the first embodiment of the present invention. This embodiment provides an eccentric shaft metal planetary gear reducer motor for automobiles. The eccentric shaft metal planetary gear reducer motor for automobiles includes a main motor 1, an outer cooling housing 2, an oil tank 3, and a gear cavity 4. The gear cavity 4 is provided with a lubrication assembly 5. When the main motor 1 is started, the lubrication assembly 5 can actively drive the lubricating oil in the oil tank 3 to circulate, thereby achieving forced lubrication and cooling of the gears inside the gear cavity 4, which greatly improves the service life of the gear assembly.

[0034] Specifically, it includes a main motor 1, an outer cooling housing 2, an oil tank 3, and a gear cavity 4. The outer cooling housing 2 is fitted around the outer periphery of the main motor 1. The outer cooling housing 2 is fixedly connected to the outer shell of the main motor 1 by a flange and bolts, and a cooling air duct is left between the two to remove the heat generated by the main motor 1 during operation. The gear cavity 4 is fixedly connected to the outer cooling housing 2 and is coaxially arranged with the motor shaft of the main motor 1. One end of the gear cavity 4 is rotatably engaged with the end cover of the outer cooling housing 2 through a sealed bearing to ensure coaxiality and prevent lubricating oil leakage. The oil tank 3 is fixedly installed on the outer wall of the outer cooling housing 2 and is fixed by bracket bolts. The oil tank 3 stores lubricating oil inside.

[0035] Specifically, a lubrication assembly 5 is provided inside the gear cavity 4. The lubrication assembly 5 includes a positioning disk 51, a second internal gear ring 52, a double-direction gear ring 53, and a transmission gear 54. The positioning disk 51 is fixedly connected to the gear cavity 4 and is fixedly connected to the inner end face of the gear cavity 4 by multiple circumferentially distributed bolts, which serve to support and limit the position. The second internal gear ring 52 is rotatably connected to the gear cavity 4, and a needle roller bearing is provided between the second internal gear ring 52 and the gear cavity 4, allowing the second internal gear ring 52 to rotate freely relative to the gear cavity 4. The double-direction gear ring 53 is eccentrically disposed inside the second internal gear ring 52 and rotatably connected to the positioning disk 51. Located inside the second internal gear ring 52 and rotatably connected to the positioning disk 51 via a thrust bearing, the eccentric arrangement is the key structural basis for the volume variation. The bidirectional gear ring 53 and the second internal gear ring 52 mesh with each other and jointly form a closed cavity 55. This closed cavity 55 is formed by the meshing of the tooth tips of the bidirectional gear ring 53 and the tooth grooves of the second internal gear ring 52, in conjunction with the sealing effect of the end face of the positioning disk 51. It is a dynamic sealed space with variable volume. The transmission gear 54 meshes with the bidirectional gear ring 53 and is used to drive the bidirectional gear ring 53 to rotate.

[0036] Specifically, the positioning disk 51 has an arc-shaped island 56 inside, which is located within the closed cavity 55. The arc-shaped island 56 serves as a structural filler and flow guide within the closed cavity 55. Its shape design optimizes the volume change rate of the closed cavity 55 during rotation. The arc-shaped island 56 is integrally cast with the positioning disk 51, and its surface is polished to reduce oil flow resistance. The internal gear ring 52 has an oil inlet groove 57 in its tooth groove, and the gear cavity 4 has an oil cavity 58 that communicates with the closed cavity 55. The second internal gear ring 52 has an oil inlet groove 57, and the gear cavity 4 has an oil cavity 58 that communicates with the closed cavity 55. The positioning plate 51 has a circulation pipe 510 that communicates with the closed cavity 55. The oil cavity 58 serves as an oil storage space and is connected to the closed cavity 55 through the oil inlet groove 57 to provide an oil source for the pumping process. The circulation pipe 510 serves as an outlet for high-pressure oil.

[0037] When the bidirectional gear ring 53 rotates eccentrically relative to the second internal gear ring 52, the volume change of the closed cavity 55 will sequentially draw lubricating oil from the oil cavity 58 through the oil inlet groove 57, and then discharge it through the circulation pipe 510 and the connecting hole 59, forming a directional oil flow, thereby achieving efficient lubrication of the gear meshing parts. Due to the eccentric setting, the meshing depth between the bidirectional gear ring 53 and the second internal gear ring 52 will change periodically, which will cause the volume of the closed cavity 55 to increase and decrease periodically. When the volume of the closed cavity 55 increases, negative pressure is generated to draw oil, and when the volume decreases, high pressure is generated to discharge oil, thereby realizing the function of drawing oil from the oil cavity 58 and pumping it out through the circulation pipe 510. The positioning disk 51 is coaxially provided with a connecting hole 59 at the position corresponding to the bidirectional gear, and the inside of the positioning disk 51 is provided with a circulation pipe 510 for connecting the closed cavity 55 and the connecting hole 59.

[0038] Example 2, refer to Figures 2-7 This is the second embodiment of the present invention, which is based on the previous embodiment.

[0039] Specifically, a drive shaft 41 is also provided inside the gear cavity 4. The drive shaft 41 is connected to the motor shaft of the main motor 1, and the drive gear 54 is connected to the drive shaft 41 via a key. Specifically, the input end of the drive shaft 41 is rigidly connected to the motor shaft of the main motor 1 via a coupling. A flat keyway is machined in the middle of the drive shaft 41. The drive gear 54 is fitted onto the drive shaft 41 via a flat key and is axially limited by a shaft retaining ring. The torque of the main motor 1 can be directly transmitted to the drive gear 54 through the drive shaft 41, thereby driving the bidirectional gear ring 53 to rotate, realizing the autonomous operation of the lubrication component 5. The lubrication action is synchronized with the motor speed. The higher the speed, the greater the lubrication flow, forming adaptive lubrication and avoiding the problems of under-lubrication at low speed and over-lubrication at high speed.

[0040] Specifically, the oil cavity 58 is connected to the closed cavity 55. One end of the oil cavity 58 corresponds to the meshing position of the second internal gear ring 52 and the bidirectional gear, and the other end extends to the conical point of the arc-shaped island 56. The circulation pipe 510 corresponds to the end of the arc-shaped island 56 away from the oil cavity 58. The oil cavity 58 extends to the conical point of the arc-shaped island 56, and the connecting hole 59 is located at the end of the closed cavity 55 away from the oil cavity 58. The conical point of the arc-shaped island 56 is the key node for the meshing and separation of the bidirectional gear ring 53 and the second internal gear ring 52. This is because the bidirectional gear ring 53 is eccentrically positioned inside the second internal gear ring 52.

[0041] When the bidirectional gear ring 53 rotates to the cone position of the arc-shaped island 56, the tooth tip of the bidirectional gear ring 53 gradually separates from the tooth groove of the second internal gear ring 52, and the meshing gap between the two reaches its maximum. The oil chamber 58 extends to this position, which corresponds to the instant when the volume of the closed chamber 55 increases. The increase in the volume of the closed chamber 55 reduces its internal pressure, forming a negative pressure zone. Under the action of negative pressure, the oil stored in the oil chamber 58 is quickly drawn into the closed chamber 55, thus completing the oil suction process. By utilizing the spatial effect at the moment of gear separation, the change in geometric position is converted into fluid power, realizing automatic oil intake without the need for an external oil suction pump.

[0042] Correspondingly, the connecting hole 59 is located at the end of the closed cavity 55 away from the oil cavity 58. This position corresponds to the area where the bidirectional toothed ring 53 and the second internal toothed ring 52 re-mesh. As the bidirectional toothed ring 53 continues to rotate, the tooth tip gradually slides into the tooth groove of the second internal toothed ring 52, and the volume of the closed cavity 55 gradually decreases. The oil is compressed. Since one side of the oil cavity 58 is blocked by the arc-shaped island 56 and the tooth surface, the pressurized oil can only flow towards the lower pressure connecting hole 59. When the oil is squeezed to the position of the connecting hole 59, the pressure reaches its peak, thus being forced into the connecting hole 59 and discharged. This "one suction, one discharge" layout design ensures the unidirectional and continuous flow of the oil.

[0043] Specifically, the bidirectional gear ring 53 includes an inner gear ring 531 and an outer gear ring 532. The outer gear ring 532 is sleeved on the outer periphery of the inner gear ring 531 and is fixedly connected to the inner gear ring 531. The two can be fixed together by a key connection to ensure concentricity and reliability of torque transmission. The outer gear ring 532 meshes with the second inner gear ring 52, and the transmission gear 54 meshes with the inner gear ring 531. The use of an inner and outer double gear ring structure allows the bidirectional gear ring 53 to simultaneously serve as a power receiving end and a pumping action execution end.

[0044] Specifically, the drive shaft 41 drives the drive gear 54 to rotate, and the drive gear 54 meshes with the internal gear ring 531, thereby driving the bidirectional gear ring 53 to rotate as a whole. During the rotation of the bidirectional gear ring 53, its outer gear ring 532 meshes with the second internal gear ring 52. Due to the eccentric setting of the bidirectional gear ring 53, the meshing gap between the outer gear ring 532 and the second internal gear ring 52 changes periodically, thereby driving the flow of oil. The gear components in the geared motor transmission system are reused as the core components of the lubrication pump, achieving the effect of multiple uses in one machine. It completes the dual functions of power transmission and lubrication circulation within a limited space.

[0045] Specifically, the oil inlet groove 57 is opened in the groove of the second inner toothed ring 52. When the bidirectional toothed ring 53 rotates to the moment it separates from the second inner toothed ring 52, the space in the groove is directly connected to the closed cavity 55. Since the oil inlet groove 57 is located in the groove, the oil in the oil cavity 58 can be directly sucked into the closed cavity 55 along the extension direction of the groove with almost no turns. This greatly reduces the local resistance loss of the oil flow and avoids the phenomenon of bubbles and cavitation caused by the sudden change in the flow direction of the oil at the oil inlet, thereby ensuring the smoothness and efficiency of the oil suction process.

[0046] Specifically, the two ends of the oil tank 3 are respectively connected to a first oil pipe 31 and a second oil pipe 32. The first oil pipe 31 is connected to the oil cavity 58, and the second oil pipe 32 passes through the outer cooling shell 2 and is connected to the connecting hole 59. The oil pipe connecting the oil tank 3 and the oil cavity 58 is the first oil pipe 31, which is responsible for transporting the room temperature lubricating oil in the oil tank 3 to the oil suction area of ​​the lubrication component 5. The oil pipe connecting the oil tank 3 and the connecting hole 59 is the second oil pipe 32, which is responsible for guiding the lubricating oil after pumping and pressurization back to the oil tank 3. Furthermore, the oil cavity 58, the closed cavity 55, the connecting hole 59, the gear cavity 4, the two oil pipes and the oil tank 3 together form a circulating oil circuit. Based on the pumping effect of the aforementioned lubrication component 5, the lubrication component 5 works continuously when the geared motor is running.

[0047] During the oil suction stage, the lubricating oil in the oil tank 3 flows into the oil chamber 58 through the first oil pipe 31 under negative pressure, and is then sucked into the closed chamber 55. During the oil discharge stage, the lubricating oil is pressurized in the closed chamber 55 and enters the second oil pipe 32 through the circulation pipe 510 and the connecting hole 59. The connecting hole 59 leads directly to the inside of the gear cavity 4, and the oil can fully wet the meshing parts such as the differential gear 45 and the first internal gear ring 42, providing forced lubrication and cooling. Then, the oil is guided back to the oil tank 3 through the second oil pipe 32 for sedimentation and cooling before entering the next cycle.

[0048] The closed-loop circulation oil circuit design enables active circulation of lubricating oil. Compared with traditional splash lubrication, it can more effectively remove the heat generated by gear meshing and dissipate it through the external cooling housing 2. This significantly reduces the temperature rise of the geared motor under high load conditions and extends the service life of the lubricating oil and gears. At the same time, the oil tank 3 allows for convenient addition of lubricating oil, and the oil tank 3 is equipped with a filter component for filtering the oil.

[0049] Specifically, the oil chamber 58, the closed chamber 55, the connecting hole 59, the internal space of the gear cavity 4, the first oil pipe 31, the second oil pipe 32, and the oil tank 3 together constitute a circulating oil circuit. After the main motor 1 starts, the transmission shaft 41 drives the transmission gear 54 to rotate. The transmission gear 54 drives the bidirectional gear ring 53 to rotate eccentrically, causing the closed chamber 55 to alternately expand and contract. During expansion, lubricating oil from the first oil pipe 31 of the oil tank 3 is drawn from the oil chamber 58 through the oil inlet groove 57. During contraction, the lubricating oil is pressed into the connecting hole 59 through the circulation pipe 510, and then flows back to the oil tank 3 through the second oil pipe 32. The entire cycle is driven by the gear movement itself, without the need for external energy. Moreover, the continuous flow of lubricating oil can promptly remove the heat generated by gear friction, significantly extending the service life of the geared motor.

[0050] Specifically, the gear cavity 4 also houses a transmission assembly, including a first internal gear ring 42 fixed inside the gear cavity 4. A rotating hole 43 for mounting a transmission shaft 41 is provided at one end of the gear cavity 4. An eccentric disk 44 is provided on the outer periphery of the transmission shaft 41, and a differential gear 45 is provided on the outer periphery of the eccentric disk 44. The differential gear 45 is eccentrically positioned with the first internal gear ring 42 via the eccentric disk 44, and meshes with the first internal gear ring 42. The first internal gear ring 42 is fixed to the inner wall of the gear cavity 4 by a locating pin, serving as the internal gear ring 531 in the planetary gear transmission. The transmission shaft 41 serves as the power input end, and its axis coincides with the centerline of the gear cavity 4. The eccentric disk 44 is mounted on the transmission shaft 41 and rotates synchronously with the transmission shaft 41, with an eccentricity between its axis and the axis of the transmission shaft 41.

[0051] The differential gear 45 is mounted on the outer circumference of the eccentric disk 44 via a needle roller bearing. When the drive shaft 41 drives the eccentric disk 44 to rotate, the differential gear 45 will revolve due to the eccentricity. Since the differential gear 45 meshes with the fixed first internal gear ring 42, it will also rotate on its own axis while revolving. This planetary gear transmission structure features a compact structure, a large transmission ratio, and strong load-bearing capacity, effectively achieving the function of speed reduction and torque increase. It should be noted that the drive shaft 41 is the power source shaft for the aforementioned lubrication assembly 5.

[0052] Specifically, the differential gear 45 has a guide hole 46 inside, and a connecting pin 47 is rotatably arranged inside the guide hole 46. A turntable 48 is arranged at one end of the connecting pin 47, and an output shaft 49 is fixedly arranged at the center of the turntable 48. In the planetary gear transmission principle, the differential gear 45 revolves eccentrically under the drive of the eccentric disk 44, and rotates on its own axis under the meshing action with the first internal gear ring 42. Specifically, the guide hole 46 is distributed along the circumference of the differential gear 45, and the axial direction of the guide hole 46 is parallel to the axial direction of the differential gear 45. The connecting pin 47 is inserted into the guide hole 46 and can slide relative to the hole wall within the guide hole 46.

[0053] When the differential gear 45 revolves, the connecting pile 47 is constrained by the turntable 48 and forced to maintain its original spatial position, thus producing reciprocating sliding within the guide hole 46. One end of the connecting pile 47 is connected to a turntable 48, which is located on one side of the differential gear 45, and the axis of the turntable 48 coincides with the axis of the transmission shaft 41. The connecting pile 47 passes through the clearance hole on the side wall of the differential gear 45 and is fixedly connected to the turntable 48. Since the sliding of the connecting pile 47 within the guide hole 46 cancels out the revolution component of the differential gear 45, the turntable 48 only receives the rotation component of the differential gear 45, thus enabling the turntable 48 to rotate on a fixed axis.

[0054] The output shaft 49 is fixedly set at the center of the turntable 48 and rotates synchronously with the turntable 48, eventually outputting the decelerated torque in a stable manner. As a preferred embodiment, the number of guide holes 46 is set to three and evenly distributed along the circumference of the differential gear 45. The multi-hole arrangement can make the driving force of the connecting pile 47 on the turntable 48 more uniform, avoid excessive force on a single connection point, and thus improve the smoothness of the rotation of the output shaft 49.

[0055] Furthermore, to reduce the frictional resistance when the connecting pile 47 slides within the guide hole 46, a bushing can be provided between the connecting pile 47 and the wall of the guide hole 46, converting sliding friction into rolling friction, further improving transmission efficiency and extending the service life of the components. This embodiment, through the above structure, transforms the complex planar motion of the differential gear 45 into the simple fixed-axis rotation of the output shaft 49, ensuring the stability and reliability of the power output of the geared motor.

[0056] Specifically, there are three eccentric disks 44, and the guide holes 46 corresponding to the three differential gears 45 are provided with overlapping cavities. The connecting pile 47 is inserted into the interior of the overlapping cavity. The three eccentric disks 44 are linearly arranged on the outer periphery of the transmission shaft 41, and the angle between adjacent eccentric disks 44 is equal. The three differential gears 45 share the load, and each surface of the overlapping cavity can jointly push the connecting pile 47 to move, which improves the peak torque, impact resistance and stability of the geared motor. In terms of lubrication, the rotation of multiple differential gears 45 is also conducive to stirring the lubricating oil to all parts of the gear cavity 4. With the above-mentioned circulating oil circuit, all-round lubrication of all gear pairs is achieved.

[0057] When in use, after the main motor 1 is powered on, its motor shaft drives the transmission shaft 41 to rotate. The transmission shaft 41 drives the differential gear 45 to make planetary oscillation in the first internal gear ring 42 through the eccentric disc 44. The oscillation of the differential gear 45 is converted into the low-speed, high-torque rotation of the output shaft 49 through the connecting pile 47 and the turntable 48, realizing the function of deceleration and torque increase.

[0058] On the other hand, the drive shaft 41 drives the drive gear 54 to rotate via a key connection. The drive gear 54 drives the bidirectional gear ring 53 to rotate eccentrically relative to the second internal gear ring 52, causing the volume of the closed cavity 55 to change periodically. This draws the lubricating oil in the oil tank 3 into the closed cavity 55 through the first oil pipe 31, the oil chamber 58, and the oil inlet groove 57, and then back into the oil tank 3 through the circulation pipe 510, the connecting hole 59, and the second oil pipe 32, forming a continuous circulating lubrication.

[0059] During the circulation process, the lubricating oil continuously flows through the gear meshing area and bearing parts, carrying away frictional heat and wear particles. It is then filtered, cooled, and reused. The entire system does not rely on an external oil pump, achieving self-driven and self-circulating lubrication. This not only reduces energy consumption but also improves lubrication reliability under harsh operating conditions such as frequent start-stop cycles and high / low temperatures, extending the life of gears and bearings. At the same time, the continuous circulation of oil inside the gear cavity 4 effectively reduces the operating noise and vibration of the geared motor.

[0060] It should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit it. Although the present invention has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications or equivalent substitutions can be made to the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention, and all such modifications or substitutions should be covered within the scope of the claims of the present invention.

Claims

1. An eccentric shaft metal planetary gear reduction motor for an automobile, characterized by: The system includes a main motor (1), an outer cooling housing (2), an oil tank (3), and a gear cavity (4). The outer cooling housing (2) is fitted around the outer periphery of the main motor (1). The gear cavity (4) is fixedly connected to the outer cooling housing (2) and coaxially arranged with the motor shaft of the main motor (1). The oil tank (3) is fixedly arranged on the outer wall of the outer cooling housing (2). A lubrication assembly (5) is provided inside the gear cavity (4). The lubrication assembly (5) includes a positioning plate (51), a second internal gear ring (52), a double-acting gear ring (53), and a transmission gear (54). The positioning plate (51) is fixedly connected to the gear cavity (4). The second internal gear ring (52) is rotatably connected to the gear cavity (4). The double-acting gear ring (53) is eccentrically arranged on the second internal gear ring (52). The gear (54) is rotatably connected to the positioning disk (51). The bidirectional gear ring (53) and the second internal gear ring (52) mesh with each other and together form a closed cavity (55). The transmission gear (54) meshes with the bidirectional gear ring (53). An arc-shaped island (56) is provided inside the positioning disk (51). The arc-shaped island (56) is located inside the closed cavity (55). An oil inlet groove (57) is opened in the tooth groove of the second internal gear ring (52). An oil cavity (58) is opened in the gear cavity (4) and communicates with the closed cavity (55). A connecting hole (59) is opened coaxially at the position corresponding to the bidirectional gear (53) of the positioning disk (51). A circulation pipe (510) is opened inside the positioning disk (51) to connect the closed cavity (55) and the connecting hole (59).

2. The eccentric shaft metal planetary gear reduction motor for an automobile according to claim 1, characterized by: The gear cavity (4) is also provided with a transmission shaft (41), which is connected to the motor shaft of the main motor (1). The transmission gear (54) is connected to the transmission shaft (41) by a key.

3. The automotive eccentric shaft metal planetary gear reducer motor as described in claim 1 or 2, characterized in that: The oil chamber (58) is connected to the closed chamber (55). One end of the oil chamber (58) corresponds to the position where the second internal gear ring (52) and the bidirectional gear mesh, and the other end extends to the cone position of the arc-shaped island (56). The circulation pipe (510) corresponds to the end of the arc-shaped island (56) away from the oil chamber (58).

4. The automotive eccentric shaft metal planetary gear reducer motor as described in claim 2, characterized in that: The bidirectional gear ring (53) includes an inner gear ring (531) and an outer gear ring (532). The outer gear ring (532) is sleeved on the outer periphery of the inner gear ring (531) and is fixedly connected to the inner gear ring (531). The outer gear ring (532) meshes with the second inner gear ring (52), and the transmission gear (54) meshes with the inner gear ring (531).

5. The automotive eccentric shaft metal planetary gear reducer motor as described in claim 1 or 4, characterized in that: The oil inlet groove (57) is located in the groove of the second internal gear ring (52).

6. The automotive eccentric shaft metal planetary gear reducer motor as described in claim 1, characterized in that: The oil tank (3) is connected to a first oil pipe (31) and a second oil pipe (32) at both ends. The first oil pipe (31) is connected to the oil cavity (58), and the second oil pipe (32) passes through the outer cooling shell (2) and is connected to the connecting hole (59).

7. The automotive eccentric shaft metal planetary gear reducer motor as described in claim 3, characterized in that: The oil chamber (58), the closed chamber (55), the connecting hole (59), the internal space of the gear cavity (4), the first oil pipe (31), the second oil pipe (32), and the oil tank (3) together constitute a circulating oil circuit.

8. The automotive eccentric shaft metal planetary gear reducer motor as described in claim 1, characterized in that: The gear cavity (4) is also provided with a transmission assembly, including a first internal gear ring (42) fixed inside the gear cavity (4). A rotating hole (43) for mounting the transmission shaft (41) is provided at the center of one end of the gear cavity (4). An eccentric disk (44) is provided on the outer periphery of the transmission shaft (41). A differential gear (45) is provided on the outer periphery of the eccentric disk (44). The differential gear (45) is eccentrically set with the first internal gear ring (42) through the eccentric disk (44), and the differential gear (45) meshes with the first internal gear ring (42).

9. The automotive eccentric shaft metal planetary gear reducer motor as described in claim 8, characterized in that: The differential gear (45) has a guide hole (46) inside, and a connecting pin (47) is rotatably arranged inside the guide hole (46). A turntable (48) is arranged at one end of the connecting pin (47), and an output shaft (49) is fixedly arranged at the center of the turntable (48).

10. The automotive eccentric shaft metal planetary gear reducer motor as described in claim 8, characterized in that: The number of eccentric disks (44) is three, and the guide holes (46) corresponding to the three differential gears (45) are provided with overlapping cavities. The connecting pile (47) is inserted into the interior of the overlapping cavity. The three eccentric disks (44) are linearly arranged on the outer periphery of the transmission shaft (41), and the angles between adjacent eccentric disks (44) are equal.

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