Planetary transmission system, speed reducer, drive axle and vehicle

Abstract

The invention relates to a planetary transmission system, a speed reducer, a drive axle and a vehicle. The planetary transmission system comprises a sun gear, a planet carrier, a gear ring, a first gear, a second gear, a first inertia gear and a second inertia gear. The sun gear is in transmission connection with the planet carrier which is in transmission connection with the gear ring; the first gear is fixedly connected with at least one of the sun gear, the planet carrier and the gear ring; the first idle gear and the second idle gear are arranged on the two sides of the first gear correspondingly and engaged with the first gear. And the first idle gear and the second idle gear are respectively meshed with the second gear. According to the planetary transmission system, power is averagely distributed to the first inertia gear and the second inertia gear through the first gear and transmitted to the second gear, so that part of radial acting force of the first gear is counteracted in the transmission process, and the radial acting force borne by the sun gear, the planet carrier and the gear ring is reduced; and the meshing load between the gears is more uniform, so that the NVH performance of the planetary transmission system is improved.

Description

Technical Field

[0001] This application relates to the field of mechanical equipment technology, and in particular to a planetary transmission system, a reducer, a drive axle, and a vehicle. Background Technology

[0002] In current planetary transmission system technologies, during the power transmission process of the planetary transmission mechanism and the second-stage driving gear and the second-stage driven gear through meshing, the central component of the planetary transmission mechanism (sun gear shaft or planet carrier or gear ring) is subjected to radial force from the second-stage gear, causing uneven load distribution in the planetary transmission system, which in turn affects the noise, vibration, and harshness (NVH) performance of the planetary transmission system. Summary of the Invention

[0003] This application provides a planetary transmission system, a reducer, a drive axle, and a vehicle, which can improve the NVH performance of the planetary transmission system.

[0004] According to a first aspect of this application, a planetary transmission system is provided, comprising:

[0005] The system comprises a sun gear, a planet carrier, a ring gear, a first gear, a second gear, a first idler gear, and a second idler gear; the sun gear is driven by the planet carrier, and the planet carrier is driven by the ring gear; the first gear is fixedly connected to at least one of the sun gear, the planet carrier, and the ring gear.

[0006] The first inertial gear and the second inertial gear are respectively disposed on both sides of the first gear and mesh with the first gear;

[0007] The first inert gear and the second inert gear mesh with the second gear, respectively.

[0008] In some embodiments, the line connecting the center of the first inertial gear and the center of the first gear is a first straight line, and the line connecting the center of the first gear and the center of the second inertial gear is a second straight line. The included angle α between the first straight line and the second straight line satisfies the condition: 150°<α≤180°.

[0009] In some embodiments, the pitch circle radius of the first inertial gear and the pitch circle radius of the second inertial gear are equal, and the first inertial gear and the second inertial gear are symmetrically arranged on both sides of the first gear.

[0010] In some embodiments, the planetary transmission system includes: a plurality of planetary gears; the plurality of planetary gears respectively mesh with the sun gear and the ring gear.

[0011] In some embodiments, the planetary transmission system includes:

[0012] A first bearing is disposed on the planet carrier to support the sun gear.

[0013] In some embodiments, the planetary transmission system includes: a first pin, the first pin being connected between the planet carrier and the planet gears.

[0014] In some embodiments, the planetary transmission mechanism transmits power evenly to the first idler gear and the second idler gear via the first gear, and the first idler gear and the second idler gear transmit power to the second gear.

[0015] According to a second aspect of this application, a speed reducer is provided, characterized in that it comprises:

[0016] The first aspect of this application provides a planetary transmission system.

[0017] In some embodiments, the reducer includes: a differential assembly;

[0018] The differential assembly is connected to the second gear drive, and the differential assembly is used to transmit the power of the second gear to the wheels.

[0019] In some embodiments, the reducer includes: a first reducer housing and a second reducer housing, wherein the planetary transmission system and the differential assembly are disposed within the space enclosed by the first reducer housing and the second reducer housing.

[0020] In some embodiments, the reducer includes a second pin, wherein the gear ring of the planetary transmission system is fixed to the second reducer housing via the second pin.

[0021] In some embodiments, the reducer includes a second bearing and a third bearing, the second bearing and the third bearing being respectively disposed at both axial ends of the first gear and connected to the second reducer housing.

[0022] In some embodiments, the reducer includes a fourth bearing and a fifth bearing, the fourth bearing and the fifth bearing being respectively disposed at the axial ends of the second gear and connected to the second reducer housing.

[0023] In some embodiments, a first limiting member is provided on the planet carrier of the planetary transmission system, and the first limiting member abuts against the third bearing.

[0024] In some embodiments, the second reducer housing is provided with a second limiting member, which abuts against the second bearing.

[0025] According to a third aspect of this application, a drive axle is provided, the drive axle including the reducer provided in the second aspect of this application.

[0026] According to a fourth aspect of this application, a vehicle is provided, including a reducer provided in a second aspect of this application and / or a drive axle provided in a third aspect of this application.

[0027] The planetary transmission system of this application, through the planetary transmission mechanism and the gear pair consisting of the first gear and the second gear, in the process of transmitting power, offsets part of the radial force of the first gear by the first inert gear and the second inert gear set on both sides of the first gear and meshing with the first gear respectively, so that the radial force from the first gear on the sun gear, planet carrier or gear ring is reduced, and the meshing load of the planetary transmission system is more uniform, thereby improving the NVH performance of the planetary transmission system. Attached Figure Description

[0028] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0029] To gain a more complete understanding of this application and its beneficial effects, the following description will be provided in conjunction with the accompanying drawings, wherein the same reference numerals in the following description denote the same parts.

[0030] Figure 1 This is a schematic diagram of a planetary transmission system structure provided in an exemplary embodiment of this application;

[0031] Figure 2 This is an exploded structural diagram of a planetary transmission system provided in an exemplary embodiment of this application;

[0032] Figure 3 This is a schematic diagram of force analysis of a planetary transmission system provided in an exemplary embodiment of this application;

[0033] Figure 4 This is a schematic cross-sectional view of a speed reducer provided in an exemplary embodiment of this application;

[0034] Figure 5 This is a partial structural cross-sectional schematic diagram of a speed reducer provided in an exemplary embodiment of this application.

[0035] Figure label:

[0036] Planetary carrier: 1; First reducer housing: 2; First bearing: 3; First pin: 4; Planetary gear: 5; Ring gear: 6; Second pin: 7; Second reducer housing: 8; Second bearing: 9; First gear: 10; Third bearing: 11; Sun gear: 12; First limiter: 13; Fourth bearing: 14; Second gear: 15; Differential assembly: 16; Fifth bearing: 17; Second limiter: 18; First idler gear: 19; Second idler gear: 20. Detailed Implementation

[0037] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of them. All other embodiments obtained by those skilled in the art based on the embodiments of this application without creative effort are within the protection scope of this application.

[0038] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains; the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the application; the terms “comprising” and “having”, and any variations thereof, in the specification, claims, and foregoing description of the drawings are intended to cover non-exclusive inclusion.

[0039] In the description of the embodiments of this application, technical terms such as "first" and "second" are used only to distinguish different objects and should not be construed as indicating or implying relative importance or implicitly specifying the number, specific order, or primary and secondary relationship of the indicated technical features. In the description of the embodiments of this application, "multiple" means two or more, unless otherwise explicitly defined.

[0040] In this document, the term "embodiment" means that a particular feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of this application. The appearance of this phrase in various places throughout the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment mutually exclusive with other embodiments. It will be explicitly and implicitly understood by those skilled in the art that the embodiments described herein can be combined with other embodiments.

[0041] In the description of the embodiments in this application, the term "and / or" is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, and B existing alone. Additionally, the character " / " in this document generally indicates that the preceding and following related objects have an "or" relationship.

[0042] In the description of the embodiments of this application, the term "multiple" refers to two or more (including two), similarly, "multiple sets" refers to two or more (including two sets), and "multiple pieces" refers to two or more (including two pieces).

[0043] In the description of the embodiments of this application, unless otherwise expressly specified and limited, the technical terms such as "connected" and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium, or a connection through a network. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this application according to the specific circumstances.

[0044] In current planetary transmission systems, power is typically transmitted from the sun gear shaft to the planet gears. The planet gears drive the secondary drive gear to rotate radially, which then transmits power to the secondary driven gear meshing with it. The power is then transmitted to other components via the secondary driven gear. However, this approach suffers from the reaction force between the secondary drive and driven gears on the planet carrier, causing deformation along the radial direction of the planet carrier. Simultaneously, the sun gear shaft also experiences a radial force at its ends. This force is unbalanced with the additional meshing force provided by the sun gear-planet gear or planet gear-ring gear, resulting in uneven load distribution among the planet gears. This leads to asymmetrical deformation of the planet carrier in the radial direction, affecting the load-sharing capacity of the planetary transmission system. Uneven load-sharing in the planetary transmission system increases the likelihood of wear and noise generation among the components.

[0045] To address at least one of the aforementioned problems, this application provides a planetary transmission system, comprising:

[0046] Sun gear 12, planet carrier 1, ring gear 6, first gear 10, second gear 15, first idler gear 19, and second idler gear 20;

[0047] The sun gear 12 is connected to the planet carrier 1 in a driving connection, and the planet carrier 1 is connected to the ring gear 6 in a driving connection.

[0048] The first gear 10 is fixedly connected to at least one of the sun gear 12, the planet carrier 1, and the ring gear 6; the first inert gear 19 and the second inert gear 20 are respectively disposed on both sides of the first gear 10 and mesh with the first gear 10; the first inert gear 19 and the second inert gear 20 mesh with the second gear 15 respectively.

[0049] like Figure 1As shown, the planetary transmission system includes a sun gear 12, a planet carrier 1, a ring gear 6, a first gear 10, a second gear 15, a first inertial gear 19, and a second inertial gear 20.

[0050] In this system, the sun gear 12 serves as the power input shaft for the planetary transmission system. Typically, one end of the sun gear 12 is connected to the input shaft of the motor, which drives the sun gear 12 to rotate radially. The other end of the sun gear 12 is connected to the planet carrier 1, which in turn is connected to the ring gear 6, which can be fixed to the housing. The first gear 10 is splined and interference-fitted onto at least one of the sun gear 12, the planet carrier 1, or the ring gear 6. As the sun gear 12, the planet carrier 1, or the ring gear 6 rotates radially, they drive the first gear 10 to rotate radially as well.

[0051] Optionally, the planetary transmission system includes a plurality of planetary gears 5; the plurality of planetary gears 5 respectively mesh with the sun gear 12 and the ring gear 6.

[0052] To more clearly see the relationships between the various components of a planetary transmission system, such as... Figure 2 This is an exploded structural diagram of the planetary transmission system of this application. The planetary transmission system includes multiple planetary gears 5, which are fixedly mounted on the planet carrier 1 and mesh with the sun gear 12. While the sun gear 12 drives the multiple planetary gears 5 to revolve around the sun gear 12, the multiple planetary gears 5 rotate together with the planet carrier 1.

[0053] Simultaneously, the ring gear 6 meshes with multiple planetary gears 5. As the multiple planetary gears 5 revolve around the sun gear 12, they roll along the inner wall of the ring gear 6, ensuring that the rotation direction of the planet carrier 1 is synchronized with that of the sun gear. With the ring gear 6 stationary, the sun gear 12 acts as the driving element, driving the planetary gears 5 to rotate around its axis. Simultaneously, the planetary gears 5 drive the planet carrier 1 to revolve around the sun gear 12 along its axis. The combined effect of the planetary gears' revolution and rotation enables torque distribution and speed regulation among the sun gear 12, the ring gear 6, and the planet carrier 1.

[0054] On both sides of the first gear 10, a first idler gear 19 and a second idler gear 20 are provided, wherein the first idler gear 19 and the second idler gear 20 are located on both sides of the first gear 10 and mesh with the first gear 10; similarly, the first idler gear 19 and the second idler gear 20 are distributed on both sides of the second gear 15 and mesh with the second gear 15. During the radial rotation of the first gear 10, the first gear 10 drives the first idler gear 19 and the second idler gear 20 to rotate, and then drives the second gear 15 to rotate through the first idler gear 19 and the second idler gear 20.

[0055] In the planetary transmission system of this application, during the transmission of power through the planetary transmission mechanism and the gear pair consisting of the first gear 10 and the second gear 12, the first inertial gear 19 and the second inertial gear 20, which are respectively set on both sides of the first gear 10 and mesh with the first gear 10, offset part of the radial force of the first gear 10. This reduces the radial force from the first gear 10 on the sun gear 12, the planet carrier 1, or the ring gear 6, making the meshing load of the planetary transmission system more uniform and thus improving the NVH performance of the planetary transmission system.

[0056] In some embodiments, the line connecting the center of the first inertial gear 19 and the center of the first gear 10 is a first straight line, and the line connecting the center of the first gear 10 and the center of the second inertial gear 20 is a second straight line. The included angle α between the first straight line and the second straight line satisfies the condition: 150°<α≤180°.

[0057] like Figure 3 As shown, the line connecting the center Q1 of the first idler gear 19 and the center Q3 of the first gear 10 is the first straight line L1, and the line connecting the center Q3 of the first gear 10 and the center Q2 of the second idler gear 20 is the second straight line L2. To ensure that the resultant force of the first idler gear 19 and the second idler gear 20 on the first gear 10 in the radial direction will approach zero, the included angle α between the first straight line L1 and the second straight line L2 needs to be as close as possible to 180°, and at least not less than 150°. Therefore, the included angle α needs to satisfy the condition: 150° < α ≤ 180°.

[0058] In some embodiments, the pitch circle radius of the first inertial gear 19 and the pitch circle radius of the second inertial gear 20 are equal, and the first inertial gear 19 and the second inertial gear 20 are respectively symmetrically arranged on both sides of the first gear 10.

[0059] To ensure that the resultant force of the first idler gear 19 and the second idler gear 20 on the first gear 10 will approach zero, and to make the deformation of the planetary carrier 1 in the radial direction more symmetrical, thereby improving the uneven load on the upper planetary gear from the source, the first idler gear 19 and the second idler gear 20 need to be two idler gears with the same pitch circle radius, and the first idler gear 19 and the second idler gear 20 should be symmetrically arranged on both sides of the first gear 10. Here, "same pitch circle radius" means that the module (a parameter of gear tooth size) and the pressure angle (the inclination angle of the gear tooth profile) of the first idler gear 19 and the second idler gear 20 are both equal.

[0060] Meanwhile, the first inertial gear 19 and the second inertial gear 20 are symmetrically arranged on both sides of the second gear 15. Optionally, the second gear 15 and the first gear 10 can also mesh and transmit power.

[0061] Furthermore, the introduction of the first inertial gear 19 and the second inertial gear 20 can serve as a power split, which can reduce the size of the second gear 15, especially for high torque situations, where the size of the second gear 15 can be further reduced.

[0062] In some embodiments, the planetary transmission system includes a first bearing 3 disposed on the planet carrier 1 to support the sun gear 12.

[0063] A first bearing 3 is provided on the planetary carrier 1. The first bearing 3 is used to support and position the sun gear 12 on the planetary carrier 1, ensuring that the sun gear 12 is stable in the axial position and preventing the sun gear 12 from axial displacement or tilting due to force or vibration. Preferably, the first bearing 3 of this application is a four-point angular contact bearing. Through the cooperation between the inner ring of the four-point angular contact bearing and the planetary carrier 1, the axial position of the sun gear 12 is precisely defined, ensuring that the sun gear 12 always maintains the correct meshing relationship with the planet gears 5 and the ring gear 6. At the same time, the rolling friction between the inner ring of the four-point angular contact bearing and the sun gear 12 replaces the sliding friction, reducing the risk of wear during operation and extending the service life of the sun gear 12.

[0064] In some embodiments, the planetary transmission system includes a first pin 4, which is connected between the planet carrier 1 and the planetary gears 5.

[0065] Optionally, a first pin 4 is provided between the planet carrier 1 and the planet gear 5. The first pin 4 is connected to the planet carrier 1 and the planet gear 5 by a snap-fit, or is interference-fitted with the planet carrier 1 and the planet gear 5 to fix the planet gear 5 on the planet carrier 1 and prevent relative displacement between the planet gear 5 and the planet carrier 1 during operation.

[0066] In some embodiments, the planetary transmission mechanism 30 transmits power evenly through the first gear 10 to the first idler gear 19 and the second idler gear 20, and the first idler gear 19 and the second idler gear 20 transmit power to the second gear 15.

[0067] Specifically, the planetary carrier 1 transmits power evenly to the first inertial gear 19 and the second inertial gear 20 via the first gear 10, and the first inertial gear 19 and the second inertial gear 20 transmit power to the second gear 15.

[0068] like Figure 3The diagram shown illustrates the force analysis between the first gear 10, the second gear 15, the first idler gear 19, and the second idler gear 20 in this application. By comparing the force analysis results of the driving gear and driven gear in related technologies using simulation software and experimental data, the main differences between the planetary transmission system of this application and related technical solutions can be identified. These differences lie in:

[0069] With the symmetrical introduction of first idler gears 19 and 20 on both sides of the first gear 10 and the first driven gear, when the included angle α between the first straight line L1 and the second straight line L2 is close to 180 degrees, the resultant force of the first idler gears 19 and 20 on the first gear 10 in the radial direction will approach zero. This makes the radial force on the sun gear, planet carrier, and ring gear more uniform, thereby improving the load distribution of the planetary gear carrier in the upper planetary transmission system from the source. In addition, the introduction of the first idler gears 19 and 20 has a power splitting effect, resulting in a significant reduction in the size of the first driven gear, especially for high torque conditions.

[0070] According to a second aspect of this application, a speed reducer is provided, characterized in that it comprises:

[0071] The first aspect of this application provides a planetary transmission system in a reducer, including a planetary transmission system that provides transmission power, wherein the planetary transmission system achieves power reduction and torque amplification of the reducer through gear meshing.

[0072] In some embodiments, the reducer includes a differential assembly 16; the differential assembly 16 is drive-connected to a second gear 15, and the differential assembly 16 is used to transmit power from the second gear 15 to the wheels.

[0073] like Figure 4 The diagram shown is a cross-sectional view of a speed reducer provided in this application. The speed reducer includes a differential assembly 16 and a planetary transmission system. The differential assembly 16 is connected to the second gear 15 of the planetary transmission system. After receiving the transmission power for the second gear 15, the differential assembly 16 moves, outputting the power to the wheel axle and further transmitting it to the wheel.

[0074] The reducer of this application has a first idler gear 19 and a second idler gear 20 respectively meshing with the first gear 10 and the second gear 15. During the process of the sun gear 12 driving the planet carrier 1 to move in the radial direction of the planet carrier 1, the power is transmitted from the first gear 10 to the second gear 15. The power is then evenly distributed to the first idler gear 19 and the second idler gear 20 through the first gear 10. Then, the two equal powers are transmitted to the second gear 15 through the first idler gear 19 and the second idler gear 20, and the power is further output to the wheel axle. This reduces the radial force borne by the sun gear 12, the planet carrier 1 and the ring gear 6 in the reducer, making the meshing load between the gears more uniform and improving the NVH performance of the reducer.

[0075] In some embodiments, the reducer includes: a first reducer housing 2 and a second reducer housing 8, wherein the planetary transmission system and the differential assembly 16 are disposed within the space enclosed by the first reducer housing 2 and the second reducer housing 8.

[0076] The reducer also includes a first reducer housing 2 and a second reducer housing 8. The planetary transmission system and the differential assembly 16 are disposed within the space enclosed by the first reducer housing 2 and the second reducer housing 8. The first reducer housing 2 and the second reducer housing 8 provide precise mounting bases for the gears, bearings, and other transmission components of the planetary transmission system and the differential assembly 16 through internal reinforcing ribs and boss structures, ensuring the relative positional accuracy of the shaft components. Furthermore, the longitudinal positioning of the reducer transmission components is achieved through bearing seat holes and locating pins, which withstand the periodic impact loads generated by gear meshing and ensure the overall rigidity of the reducer. At the same time, the first reducer housing 2 and the second reducer housing 8 form a closed lubrication space, through which oil guide grooves achieve gear splash lubrication, prevent lubricating oil leakage, and also prevent the intrusion of external impurities, thereby protecting the transmission components of the reducer.

[0077] Optionally, the second reducer housing 8 can also serve as the housing of the planetary transmission system, with the gear ring 6 fixed on the second reducer housing 8.

[0078] In some embodiments, the reducer includes a second pin 7, and the gear ring 6 of the planetary transmission system is fixed to the second reducer housing 8 by the second pin 7.

[0079] Optional, such as Figure 5 As shown, the reducer includes a second pin 7, and the gear ring 6 of the planetary transmission system is fixed to the second reducer housing 8 via the second pin 7.

[0080] In some embodiments, the reducer includes a second bearing 9 and a third bearing 11, which are respectively disposed at the axial ends of the first gear 10 of the planetary transmission system and connected to the second reducer housing 8.

[0081] Optionally, the reducer also includes a second bearing 9 and a third bearing 11. The second bearing 9 and third bearing 11 preferably use tapered roller bearings. Tapered roller bearings have a large load-bearing capacity, can operate stably under heavy and impact loads, and have good self-aligning performance, automatically adjusting shaft misalignment to ensure uniform bearing stress. This helps reduce wear and fatigue of the second bearing 9 and third bearing 11, extending their service life. The second bearing 9 and third bearing 11 are respectively located at both ends of the first gear 10 in the planetary transmission system. The first gear 10 is fixed to the second reducer housing 8 via the second bearing 9 and third bearing 11. The second bearing 9 and third bearing 11 cooperate with the second reducer housing 8, enabling the first gear 10 to withstand axial and radial loads at both ends, achieving high-load, high-precision rotational support, ensuring the stability of the first gear 10 during movement, and reducing frictional loss. Simultaneously, preload adjustment controls the axial movement range of the first gear 10, avoiding vibration or noise caused by axial misalignment.

[0082] In some embodiments, the reducer includes a fourth bearing 14 and a fifth bearing 17, which are respectively disposed at both axial ends of the second gear 15 and connected to the second reducer housing 8.

[0083] Optionally, the reducer includes a fourth bearing 14 and a fifth bearing 17. The fourth bearing 14 and fifth bearing 17 preferably use tapered roller bearings, which help reduce wear and fatigue, extending their service life. The fourth bearing 14 and fifth bearing 17 are respectively located at both ends of the second gear 15 in the planetary transmission system, and are connected to the second reducer housing 8 and / or the first reducer housing 2 via bearing seats. The second reducer housing 8 and / or the first reducer housing 2 support the fourth bearing 14 and fifth bearing 17 via the bearing seats, providing rigid support to ensure the stability of the second gear 15 during operation and reducing frictional losses. By cooperating with the second reducer housing 8 and / or the first reducer housing 2, the fourth bearing 14 and fifth bearing 17 enable the two ends of the second gear 15 to withstand axial and radial loads, achieving high-load, high-precision rotary support.

[0084] In some embodiments, a first limiting member 13 is provided on the planet carrier 1 of the planetary transmission system, and the first limiting member 13 abuts against the third bearing 11.

[0085] Optionally, the reducer includes a first limiting member 13, which is typically a snap ring. The first limiting member 13 is arranged on the planet carrier 1 of the planetary transmission system and abuts against the third bearing 11. The first limiting member 13 can limit the third bearing 11, control the axial movement range of the planet carrier 1, and avoid vibration or noise caused by axial displacement.

[0086] In some embodiments, the second reducer housing 8 is provided with a second limiting member 18, which abuts against the second bearing 9.

[0087] Optionally, the reducer also includes a second limiting member 18, which is typically a hexagonal screw. The second limiting member 18 is disposed on the second reducer housing 8 and abuts against the second bearing 9. The second limiting member 18 can limit the movement of the second bearing 9, preventing the second bearing 9 from vibrating or shifting during the operation of the reducer, thereby ensuring the support and limiting of the entire internal structure of the reducer.

[0088] According to a third aspect of this application, a drive axle is provided, the drive axle including the reducer provided in the third aspect of this application.

[0089] The drive axle includes the aforementioned reducer. The drive axle increases the driving force of the vehicle through the reducer and converts the longitudinal rotation of the drive shaft into the lateral rotation of the drive wheels, thereby changing the direction of power transmission. Furthermore, the reducer reduces the rotational speed to increase torque.

[0090] During operation, the drive axle of this application improves NVH performance due to the enhanced stability of the reducer.

[0091] According to a third aspect of this application, a vehicle is provided, the vehicle including a reducer provided in the second aspect of this application, and / or a drive axle provided in the second aspect.

[0092] The reducer works in conjunction with other components in the vehicle to achieve efficient matching between the vehicle's power source and the actuator by reducing the rotational speed and increasing the torque.

[0093] A drive axle is used in vehicles. The drive axle is connected to the vehicle's wheel axles via half-shafts to transmit power to the wheels, thus driving the vehicle.

[0094] The vehicle can be a gasoline-powered vehicle, a plug-in hybrid electric vehicle, or a new energy vehicle, etc., and this application does not make any specific restrictions on this.

[0095] When the vehicle of this application is driven by the reducer and / or drive axle, the NVH performance of the reducer and / or drive axle is improved, thus enabling it to adapt to more complex road surfaces, improve vehicle stability during driving, and reduce vehicle noise during driving.

[0096] In the description of this application, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more features. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0097] In the above embodiments, the descriptions of each embodiment have different focuses. For parts not described in detail in a certain embodiment, please refer to the relevant descriptions in other embodiments.

[0098] The embodiments, implementation methods, and related technical features of this application can be combined and substituted for each other without conflict.

[0099] The above are merely preferred embodiments of this application and are not intended to limit this application in any way. Any simple modifications, equivalent changes, and alterations made to the above embodiments based on the technical essence of this application without departing from the scope of the technical solution of this application shall still fall within the scope of the technical solution of this application.

Claims

1. A planetary transmission system, characterized in that, include: Sun gear (12), planet carrier (1), ring gear (6), first gear (10), second gear (15), first inertial gear (19) and second inertial gear (20); The sun gear (12) is connected to the planet carrier (1) in a transmission connection, and the planet carrier (1) is connected to the gear ring (6) in a transmission connection. The first gear (10) is fixedly connected to at least one of the sun gear (12), the planet carrier (1) and the gear ring (6); The first inertial gear (19) and the second inertial gear (20) are respectively disposed on both sides of the first gear (10) and mesh with the first gear (10); The first inertial gear (19) and the second inertial gear (20) mesh with the second gear (15), respectively.

2. The planetary transmission system according to claim 1, characterized in that, The line connecting the center of the first inertial gear (19) and the center of the first gear (10) is a first straight line, and the line connecting the center of the first gear (10) and the center of the second inertial gear (20) is a second straight line. The angle α between the first straight line and the second straight line satisfies the condition: 150°<α≤180°.

3. The planetary transmission system according to claim 1, characterized in that, The pitch circle radius of the first inertial gear (19) and the pitch circle radius of the second inertial gear (20) are equal, and the first inertial gear (19) and the second inertial gear (20) are respectively symmetrically arranged on both sides of the first gear (10).

4. The planetary transmission system according to claim 3, characterized in that, include: Multiple planetary gears (5); the multiple planetary gears (5) respectively mesh with the sun gear (12) and the gear ring (6).

5. The planetary transmission system according to claim 4, characterized in that, include: A first bearing (3) is disposed on the planet carrier (1) to support the sun gear (12).

6. The planetary transmission system according to claim 4, characterized in that, include: The first pin (4) is connected between the planet carrier (1) and the planetary gear (5).

7. The planetary transmission system according to any one of claims 1 to 6, characterized in that: The planetary transmission mechanism (30) transmits power evenly through the first gear (10) to the first inertial gear (19) and the second inertial gear (20), and the first inertial gear (19) and the second inertial gear (20) transmit power to the second gear (15).

8. A speed reducer, characterized in that, include: The planetary transmission system according to any one of claims 1 to 9.

9. The reducer according to claim 8, characterized in that, include: Differential assembly (16); the differential assembly (16) is connected to the second gear (15) for transmitting the power of the second gear (15) to the wheels.

10. The reducer according to claim 9, characterized in that, include: The first reducer housing (2) and the second reducer housing (8) are arranged in the space enclosed by the first reducer housing (2) and the second reducer housing (8). The planetary transmission system and the differential assembly (16) are arranged in the space enclosed by the first reducer housing (2) and the second reducer housing (8).

11. The reducer according to claim 10, characterized in that, include: The second pin (7) is used to fix the gear ring (6) of the planetary transmission system to the second reducer housing (8).

12. The reducer according to claim 11, characterized in that, include: The second bearing (9) and the third bearing (11) are respectively disposed at both ends of the axial direction of the first gear (10) and connected to the second reducer housing (8).

13. The reducer according to claim 12, characterized in that, include: The fourth bearing (14) and the fifth bearing (17) are respectively disposed at both ends of the axial direction of the second gear (15) and connected to the second reducer housing (8).

14. The reducer according to claim 12, characterized in that, The planetary carrier (1) is provided with a first limiting member (13), which abuts against the third bearing (11).

15. The reducer according to claim 12, characterized in that, The second reducer housing (8) is provided with a second limiting member (18), which abuts against the second bearing (9).

16. A drive axle, characterized in that, Includes the speed reducer as described in any one of claims 8 to 15.

17. A vehicle, characterized in that, Includes the reducer as described in any one of claims 8 to 15, and / or the drive axle as described in claim 16.

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