A transmission, powertrain and vehicle
Patent Information
- Application Number
- CN202610740154.7
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2026-05-27
- Publication Date
- 2026-08-18
AI Technical Summary
可以解决相关技术中差速器和减速器组成的总成重量较大，紧凑性不足、结构复杂以及成本高的问题，所述技术方案如下：
传动装置中采用两个简单行星轮系，保持第二行星架固定不动，第一行星轮系的行星架与第二行星轮系的齿圈固定连接，第一行星轮系的太阳轮接收输入的动力，第一行星轮系的齿圈和第二行星轮系的太阳轮作为两个动力输出部件，在车辆转弯或两侧车轮负载不均时，可通过第一行星轮和第二行星轮各自的自适应自转自动调整，第一齿圈与第二太阳轮的转速差异，无需额外的差速器即可实现差速功能，简化了传动装置的结构。而且，通过匹配第一行星轮系和第二行星轮系的齿数比，可以使传动装置同时实现转速大幅降低、扭矩显著增的功能。传动装置通过两个简单行星轮系，同时实现了减速增扭功能和差速功能，传动装置的结构紧凑，无需配置两个独立的差速器和减速器，显著减小了体积和重量，并降低了成本。
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Figure CN122589964A_ABST
Abstract
Description
Technical Field
[0001] This application relates to the field of vehicle technology, and in particular to a transmission device, power system and vehicle. Background Technology
[0002] Differentials and reducers are core functional components of a vehicle's transmission system.
[0003] In related technologies, differentials and reducers are typically arranged in a linked manner to achieve compactness.
[0004] However, because the differential independently performs the differential function and the reducer independently performs the reduction function, the combined assembly is relatively heavy and lacks compactness. Furthermore, the planetary gear train in the reducer generally uses a double-planetary gear structure or two sets of meshing planetary gears, resulting in a complex structure and high cost. Summary of the Invention
[0005] This application provides a transmission device, a power system, and a vehicle. It solves the problems of large weight, insufficient compactness, complex structure, and high cost of assemblies composed of differentials and reducers in related technologies. The technical solution is as follows: On one hand, this application provides a transmission device, including: a housing, and a first planetary gear train and a second planetary gear train, both mounted on the housing; Both the first planetary gear train and the second planetary gear train include: a sun gear, planet gears, a planet carrier, and a ring gear; the planet gears are located around the sun gear and mesh with the sun gear, the ring gears are located around the planet gears and the sun gear as a whole and mesh with the planet gears; the planet gears are also rotatably connected to the planet carrier; In this configuration, the planet carrier in the second planetary gear train is fixedly connected to the housing; the ring gear in the second planetary gear train is fixedly connected to the planet carrier in the first planetary gear train; the sun gear in the first planetary gear train is fixedly connected to the drive unit; the ring gear in the first planetary gear train is fixedly connected to the first connecting shaft; and the sun gear in the second planetary gear train is fixedly connected to the second connecting shaft.
[0006] In some possible implementations, the first planetary gear train and the second planetary gear train are distributed axially in the transmission device; In this configuration, the axes of the sun gear and ring gear in the first planetary gear train and the sun gear in the second planetary gear train are all located on the axis of the transmission device.
[0007] In some possible implementations, the sun gear in the first planetary gear train has a through connecting channel, which is configured to be spaced out around the first connecting shaft; The transmission device further includes: a first connecting part; the first connecting part is fixedly connected to the gear ring in the first planetary gear train on the side axially close to the second planetary gear train; the first connecting part is configured to be fixedly connected to one end of the first connecting shaft; The axis of the connecting channel and the axis of the first connecting part are both located on the axis of the transmission device.
[0008] In some possible implementations, the planet carrier in the first planetary gear train is located on the side of the first connection away from the second planetary gear train in the axial direction of the transmission device; The transmission device further includes a second connecting part; one end of the second connecting part is fixedly connected to the planet carrier in the first planetary gear train, and the other end passes around the outer ring side of the gear ring in the first planetary gear train and the outer ring side of the first connecting part, and is fixedly connected to the gear ring in the second planetary gear train.
[0009] In some possible implementations, the planet carrier in the first planetary gear train includes: a first support portion and a first rotating shaft portion; the first support portion is located on the side of the gear ring in the first planetary gear train away from the second planetary gear train, the first rotating shaft portion is connected to the first support portion and is located within the range of the gear ring in the first planetary gear train, and the planet gears in the first planetary gear train are rotatably sleeved on the first rotating shaft portion; Wherein, the outer ring side of the first support portion protrudes from the outer ring side of the gear ring in the first planetary gear train, and one end of the second connecting portion is fixedly connected to the outer ring side of the first support portion.
[0010] In some possible implementations, in the axial direction of the transmission device, the planet carrier in the second planetary gear train is farther away from the first planetary gear train than the ring gear in the second planetary gear train, and the outer ring side of the planet carrier in the second planetary gear train is fixedly connected to the inner wall of the housing; The second connecting part is fixedly connected at one end away from the planet carrier in the first planetary gear train to the side of the gear ring in the second planetary gear train that is closer to the first planetary gear train.
[0011] In some possible implementations, the kinematic equations of the first and second planetary gear trains satisfy the following formula: ig10 = Zr1 / Zs1; ig20 = Zr2 / Zs2; ig20 = (1 + ig10) / ig10; Wherein, ig10 represents the transmission ratio between the ring gear and the sun gear in the first planetary gear train; ig20 represents the transmission ratio between the ring gear and the sun gear in the second planetary gear train; Zr1 represents the number of teeth on the ring gear in the first planetary gear train; Zs1 represents the number of teeth on the sun gear in the first planetary gear train; Zr2 represents the number of teeth on the ring gear in the second planetary gear train; and Zs2 represents the number of teeth on the sun gear in the second planetary gear train.
[0012] In some possible implementations, the sun gear, planet gears, and ring gear in the first planetary gear train have the same module; the sun gear, planet gears, and ring gear in the second planetary gear train have the same module. Wherein, the radius of the sun gear in the first planetary gear train is smaller than the radius of the sun gear in the second planetary gear train, and the radius of the planet gears in the first planetary gear train is larger than the radius of the planet gears in the second planetary gear train.
[0013] On the other hand, this application provides a power system, including: a driver, a first connecting shaft, a second connecting shaft, and the aforementioned transmission device; In this configuration, the sun gear in the first planetary gear train is fixedly connected to the driver; the ring gear in the first planetary gear train is fixedly connected to the first connecting shaft; and the sun gear in the second planetary gear train is fixedly connected to the second connecting shaft.
[0014] In another aspect, this application provides a vehicle that integrates the aforementioned power system.
[0015] The beneficial effects of the technical solutions provided in this application include at least the following: The transmission employs two simple planetary gear trains. The second planetary carrier remains stationary, while the planetary carrier of the first planetary gear train is fixedly connected to the ring gear of the second planetary gear train. The sun gear of the first planetary gear train receives the input power. The ring gear of the first planetary gear train and the sun gear of the second planetary gear train serve as two power output components. When the vehicle is turning or the load on both wheels is uneven, the adaptive rotation of the first and second planetary gears automatically adjusts the speed difference. The difference in speed between the first ring gear and the second sun gear eliminates the need for an additional differential, thus simplifying the transmission structure. Furthermore, by matching the gear ratios of the first and second planetary gear trains, the transmission can simultaneously achieve a significant reduction in speed and a significant increase in torque. Through two simple planetary gear trains, the transmission simultaneously achieves speed reduction and torque increase, as well as differential functionality. The transmission has a compact structure, eliminating the need for two separate differentials and reducers, significantly reducing size, weight, and cost. Attached Figure Description
[0016] 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 accompanying 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.
[0017] Figure 1 This is a schematic diagram of the structure of a transmission device provided in an embodiment of this application.
[0018] Figure 2 This is a speed line diagram of a transmission device provided in an embodiment of this application.
[0019] Figure 3 This is a schematic diagram of another transmission device provided in an embodiment of this application.
[0020] Figure 4 This is a schematic diagram of another transmission device provided in the embodiments of this application.
[0021] Figure 5 This is a schematic diagram of another transmission device provided in the embodiments of this application.
[0022] Figure label: 100, First planetary gear train; 110, First sun gear; 111, Drive shaft; L, Connecting channel; 120, First planet gear; 130, First planet carrier; 131, First support part; 132, First rotating shaft part; 140, First gear ring; 200. Second planetary gear train; 210. Second sun gear; 220. Second planetary gear; 230. Second planetary carrier; 231. Second support section; 232. Second shaft section; 240. Second gear ring; 300, housing; Q, receiving cavity; 400, driver; 501, First connecting shaft; 502, Second connecting shaft; 600. First connecting part; 700. Second connecting part. Detailed Implementation
[0023] To make the objectives, technical solutions, and advantages of this application clearer, the embodiments of this application will be described in further detail below with reference to the accompanying drawings.
[0024] On one hand, embodiments of this application provide a transmission device. The transmission device may be a differential, a reducer, or a composite transmission device that combines differential and reduction functions.
[0025] Figure 1 This is a schematic diagram of the structure of a transmission device provided in an embodiment of this application. Figure 1 As shown, the transmission device may include: a housing 300, and a first planetary gear train 100 and a second planetary gear train 200, both mounted on the housing 300. Exemplarily, the housing 300 has a receiving cavity Q, within which both the first planetary gear train 100 and the second planetary gear train 200 are mounted.
[0026] Both the first planetary gear train 100 and the second planetary gear train 200 may include: a sun gear, planet gears, a planet carrier, and a ring gear. The planet gears are located around the sun gear and mesh with it, while the ring gear is located around the planet gears and the sun gear as a whole and meshes with them. The planet gears are also rotatably connected to the planet carrier.
[0027] Here, both the first planetary gear train 100 and the second planetary gear train 200 are simple planetary gear trains. That is, the planetary gears in the first planetary gear train 100 and the second planetary gear train 220 are single-row planetary gears, rather than double-row planetary gears.
[0028] The sun gear, planet gears, planet carrier, and ring gear in the first planetary gear train 100 may include: a first sun gear 110, several first planet gears 120, a first planet carrier 130, and a first ring gear 140. Among them, the first planet gear 120 is a single-row planet gear.
[0029] The sun gear, planet gears, planet carrier, and ring gear in the second planetary gear train 200 may include: a second sun gear 210, several second planet gears 220, a second planet carrier 230, and a second ring gear 240. Among them, the second planet gear 220 is a single-row planet gear.
[0030] It is understandable that, in addition to cooperating with each other, some of the rotating components of the first planetary gear train 100 and the second planetary gear train 200 can be supported on the housing 300 by bearings, thereby achieving the positioning of the first planetary gear train 100 and the second planetary gear train 200 within the housing 300.
[0031] In this configuration, the planet carrier in the second planetary gear train 200 is fixedly connected to the housing 300. The ring gear in the second planetary gear train 200 is fixedly connected to the planet carrier in the first planetary gear train 100, and the sun gear in the first planetary gear train 100 is fixedly connected to the drive unit 400. The ring gear in the first planetary gear train 100 is fixedly connected to the first connecting shaft 501. The sun gear in the second planetary gear train 200 is fixedly connected to the second connecting shaft 502.
[0032] For example, the driver 400 can be a motor, the first connecting shaft 501 can be the left half-shaft of the axle, and the second connecting shaft 502 can be the right half-shaft of the axle. The left half-shaft is fixedly connected to the left wheel of the vehicle, and the right half-shaft is fixedly connected to the right wheel of the vehicle.
[0033] Here, the second planetary carrier 230 and the housing 300 can be mutually limited by means of bolt fixing, spline limiting, or step limiting, so that the second planetary carrier 230 remains fixed relative to the housing 300. The second ring gear 240 and the first planetary carrier 130 can be fixedly connected to each other by means of bolt fixing or welding. The first sun gear 110 can be directly or indirectly fixedly connected to the driver 400 and receive the rotational power output by the driver 400. The first ring gear 140 can be directly or indirectly fixedly connected to the first connecting shaft 501 and output rotational power to the first connecting shaft 501. The second sun gear 210 can be directly or indirectly fixedly connected to the second connecting shaft 502 and output rotational power to the second connecting shaft 502.
[0034] The driver 400 drives the first sun gear 110 to rotate, which in turn drives several first planet gears 120 to rotate around their own axes. Simultaneously, since the first planet carrier 130 is fixedly connected to the ring gear of the second planetary gear train 200, and the planet carrier of the second planetary gear train 200 is fixed to the housing 300, the rotation of the first planet gears 120 will drive the first planet carrier 130 to revolve around the axis of the first sun gear 110. The revolve of the first planet carrier 130 drives the second ring gear 240 of the second planetary gear train 200 to rotate synchronously, which in turn drives several second planet gears 220 meshing with it to rotate. Because the second planet carrier 230 is fixed, the rotation of the second planet gears 220 is converted into the rotation of the second sun gear 210, thereby driving the second connecting shaft 502 to output power. At the same time, the first planet gears 120 mesh with the first ring gear 140, and the rotation of the first planet gears 120 will also drive the first ring gear 140 to rotate, which in turn drives the first connecting shaft 501 fixed to it to output power. Ultimately, the power of the drive 400 is output from the first ring gear 140 and the second sun gear 210 through the first planetary gear train 100 and the second planetary gear train 200 of the transmission device.
[0035] When the vehicle turns, the speed difference between the first ring gear 140 and the second sun gear 210 can be adjusted by the adaptive rotation of the first planetary gear 120 and the second planetary gear 220, thereby realizing the differential function of the first ring gear 140 and the second sun gear 210; moreover, when the load on one side of the connecting shaft changes (such as when one side of the wheel slips), the power loss can be reduced by the power distribution mechanism of the planetary gear system.
[0036] In the first planetary gear train 100, when the first sun gear 110 drives the first planet gear 120, the first planet gear 120 simultaneously rotates on its own axis and revolves around the sun, decomposing the single input power into two output paths, reducing the speed and increasing the torque, thus achieving the first stage of speed reduction and torque increase. In the second planetary gear train 200, the second ring gear 240 is driven to rotate by the first planet carrier 130, and the second sun gear 210 outputs power, further reducing the speed and increasing the torque, thus achieving the second stage of speed reduction and torque increase. By matching the gear ratio of the first planetary gear train 100 and the second planetary gear train 200, the transmission device can achieve a larger transmission ratio and a significant increase in torque.
[0037] Figure 2 This is a speed line diagram of a transmission device provided in an embodiment of this application. Figure 2 In the diagram, the horizontal axis represents the components of the first planetary gear train 100 and the second planetary gear train 200, while the vertical axis represents the rotational speed.
[0038] Figure 2 In this diagram, S1 represents the first sun gear 110, C1 represents the first planet carrier 130, R1 represents the first ring gear 140, S2 represents the second sun gear 210, C2 represents the second planet carrier 230, and R2 represents the second ring gear 240. Since the second sun gear 210 and the first ring gear 140 are two power output elements, their rotational speeds are defined as 1. Because the second planet carrier 230 is fixed and its rotational speed is 0, and the first planet carrier 130 is fixedly connected to the second ring gear 240, their rotational speeds are the same. According to the transmission relationship, the second ring gear 240 has a negative rotational speed.
[0039] Based on the above settings, and according to the speed curve diagram and the lever principle of speed ratio, the rotational speed SR of the first sun gear 110, which serves as the input element, can be calculated. Figure 2 As shown, SR is located on the longitudinal axis. Compared to the first ring gear 140 and the second sun gear 210, which rotate at a speed of 1, the distance between SR and the transverse axis is significantly greater than the speed of the first ring gear 140 at 1. The value of SR is the transmission ratio of this transmission device. Therefore, the transmission device achieves a large transmission ratio and a significant increase in torque. The transmission ratio of this transmission device can reach a level comparable to that of a parallel shaft reducer.
[0040] In summary, the transmission system employs two simple planetary gear trains. The second planetary carrier remains stationary, while the planetary carrier of the first planetary gear train is fixedly connected to the ring gear of the second planetary gear train. The sun gear of the first planetary gear train receives the input power. The ring gear of the first planetary gear train and the sun gear of the second planetary gear train serve as two power output components. When the vehicle is turning or the load on both wheels is uneven, the adaptive rotation of the first and second planetary gears automatically adjusts the speed difference. The difference in speed between the first ring gear and the second sun gear eliminates the need for an additional differential, thus simplifying the transmission system's structure. Furthermore, by matching the gear ratios of the first and second planetary gear trains, the transmission system can simultaneously achieve a significant reduction in speed and a significant increase in torque. Through two simple planetary gear trains, the transmission system simultaneously achieves speed reduction and torque increase, as well as differential functionality. The compact structure of the transmission system eliminates the need for two independent differentials and reducers, significantly reducing size, weight, and cost.
[0041] Figure 3 This is a schematic diagram of another transmission device provided in an embodiment of this application. For example... Figure 3 As shown, in some possible implementations, the first planetary gear train 100 and the second planetary gear train 200 are distributed axially in the transmission device.
[0042] In this system, the axes of the sun gear in the first planetary gear train 100, the ring gear, and the sun gear in the second planetary gear train 200 are all located on the axis of the transmission device. That is, the axes of the input (first sun gear 110) and the two outputs (first ring gear 140 and second sun gear 210) of the transmission device are all located on the axis of the transmission device.
[0043] In this way, the input and output shafts of the transmission are arranged coaxially, which not only effectively reduces the space occupied by the transmission in the radial direction and improves the compactness of the transmission, thus freeing up layout space for other components on the vehicle; but also reduces eccentric loss in the power transmission process and improves the transmission efficiency of the transmission.
[0044] Furthermore, the first planetary gear train 100 and the second planetary gear train 200 themselves can ensure internal balance of radial forces. The first planetary gear train 100 and the second planetary gear train 200 are distributed axially in the transmission device, with the first sun gear 110, the first ring gear 140, and the second sun gear 210 arranged coaxially. During torque transmission, this reduces the imbalance of axial forces within the transmission device, thereby improving the balance of axial and radial forces. This balance of axial and radial forces not only reduces the risk and degree of deformation of the two planetary gears, but also, due to the smaller axial force, allows for the use of more efficient deep groove ball bearings or cylindrical roller bearings in the rotating components within the transmission device, eliminating the need for less efficient tapered bearings. This improves the transmission efficiency of the transmission device and reduces its vibration and noise.
[0045] For example, the transmission device is installed between the first connecting shaft 501 and the second connecting shaft 502, such that the first planetary gear train 100 is distributed close to the first connecting shaft 501, and the second planetary gear train 502 is distributed close to the second connecting shaft 502. In the axial direction of the transmission device, clearance holes can be provided on both sides of the housing 300. The first connecting shaft 501 can pass through the corresponding clearance hole and be fixedly connected to the first gear ring 140, and the second connecting shaft 502 can pass through the corresponding clearance hole and be fixedly connected to the second sun gear 210.
[0046] In some embodiments, the axes of the first sun gear 110, the first planet carrier 130, the first ring gear 140, the second sun gear 210, the second planet carrier 230, and the second ring gear 240 are all located on the same axis, which is also the axis of the transmission device. In this way, all core transmission components are arranged along the same axis, further compressing the radial dimension of the transmission device and improving its radial compactness. In summary, a coaxial transmission device with only one axis can achieve a significant improvement in space utilization.
[0047] Continue to refer to Figure 3 As shown, in some possible implementations, the sun gear in the first planetary gear train 100 has a through connecting channel L (i.e., the first sun gear 110 has a through connecting channel L), and the connecting channel L is configured to be spaced around the periphery of the first connecting shaft 501. That is, there is a gap between the first connecting shaft 501 and the inner wall of the connecting channel L.
[0048] For example, a drive shaft 111 is coaxially fixed on the first sun gear 110. The drive shaft 111 protrudes from the first gear ring 140 on the side away from the second planetary gear train 200. Both the drive shaft 111 and the first sun gear 110 have the aforementioned connection channel L.
[0049] The transmission device may further include a first connecting portion 600. The first connecting portion 600 is fixedly connected to the gear ring 140 in the first planetary gear train 100 on the side axially close to the second planetary gear train 200. The first connecting portion 600 is configured to be fixedly connected to one end of the first connecting shaft 501. By placing the first connecting portion 600 on the side of the first gear ring 140 close to the second planetary gear train 200, the axial space between the first planetary gear train 100 and the second planetary gear train 200 is fully utilized, avoiding additional axial extension and further reducing the overall axial dimension of the transmission device.
[0050] For example, the first connecting part 600 is a spoke or a spoke plate. The first connecting part 600 can be welded and fixed to the side of the first gear ring 140 near the second planetary gear train 200. The axis of the first connecting part 600 can be fixedly connected to the first connecting shaft 501.
[0051] The axis of the connecting channel L and the axis of the first connecting part 600 are both located on the axis of the transmission device. This ensures that the first gear ring 140 and the first sun gear 110 are arranged coaxially.
[0052] In this way, the first connecting part 600 can serve as a connector between the first gear ring 140 and the first connecting shaft 501. The first connecting shaft 501 can rotate independently of the first sun gear 110 in the connecting channel L, enabling the first gear ring 140 to output power outward. At the same time, the driver 400 can be connected to the first sun gear 110 on the outer periphery of the connecting channel L, realizing the coaxial arrangement of input and output on the same side of the transmission device (first planetary gear train 100). The nested arrangement of the connecting channel L of the first sun gear 110 and the first connecting shaft 501 enables compact power transmission within a limited axial space and reduces the overall radial dimension. This improves the compactness of the overall structure after connection.
[0053] For example, when the transmission device, driver 400, and axle are assembled, the driver 400 can be sleeved and fixed on the outside of the drive shaft 111, and the left half-shaft of the axle can pass through the connecting channel L and be fixedly connected to the first connecting part 600. The driver 400 drives the first sun gear 110 to rotate, which is transmitted to the first ring gear 140 through the first planetary gear train 100. The rotation of the first ring gear 140 drives the first connecting part 600 to rotate synchronously, and the first connecting part 600 drives the first connecting shaft 501 to rotate synchronously, thereby transmitting power to the wheel at the end of the first connecting shaft 501 away from the first connecting part 600.
[0054] Figure 4 This is a schematic diagram of another transmission device provided in an embodiment of this application. For example... Figure 4As shown, in some possible implementations, in the axial direction of the transmission device, the planet carrier in the first planetary gear train 100 is located on the side of the first connecting portion 600 away from the second planetary gear train 200. That is, the first connecting portion 600 is fixed to the side of the first gear ring 140 close to the second planetary gear train 200, while the first planet carrier 130 is arranged on the side of the first connecting portion 600 away from the second planetary gear train 200.
[0055] Since the first connecting portion 600 mainly functions as a spoke, that is, as a spoke of the first gear ring 140, its axial dimension can be relatively small, or even completely share the axial dimension with the first gear ring 140. However, the first planetary carrier 130 typically requires a rotating shaft to rotatably support the first planetary gear 120, resulting in its axial dimension being much larger than that of the first connecting portion 600. By arranging the first connecting portion 600 on the side of the first gear ring 140 closer to the second planetary gear train 200, and arranging the first planetary carrier 130 on the side away from the second planetary gear train 200, the axial space between the first planetary gear train 100 and the second planetary gear train 200 can be significantly reduced, improving the compactness of the transmission device. Furthermore, the first planetary carrier 130 can share the axial space with the output shaft of the first sun gear 110, thereby improving the axial compactness of the transmission device. In addition, after the transmission device is arranged on the axle, the first planetary carrier 130 can also share axial space with the first connecting shaft 501, thereby improving the overall compactness of the transmission device and the axle.
[0056] The transmission device may further include a second connecting portion 700. One end of the second connecting portion 700 is fixedly connected to the planet carrier in the first planetary gear train 100, and the other end passes around the outer ring side of the gear ring in the first planetary gear train 100 and the outer ring side of the first connecting portion 600, and is then fixedly connected to the gear ring in the second planetary gear train 200. Here, the fixing method between the second connecting portion 700 and the first planet carrier 130 and the second gear ring 240 is not limited, and the connection can be made by bolting, welding, or integral molding.
[0057] For example, the second connecting portion 700 can be a ring structure, or it can be a plurality of connecting rods spaced circumferentially along the first gear ring 140, with each connecting rod having its two ends fixedly connected to the first planetary carrier 130 and the second gear ring 240, respectively. The circumferential distribution of the second connecting portion 700 can reduce eccentric loss during power transmission.
[0058] In this way, by bypassing the first gear ring 140 and the first connecting part 600 through the second connecting part 700, a fixed connection is achieved between the second connecting part 700 and the first gear ring 140 and the first planetary carrier 130. Furthermore, the second connecting part 700 enables the power connection and linkage between the first planetary gear train 100 and the second planetary gear train 200. At the same time, direct contact and interference between the rotating components such as the first gear ring 140, the first planetary carrier 130, the second gear ring 240, the first connecting part 600, and the second connecting part 700 are avoided, ensuring that the first gear ring 140 and the first planetary carrier 130 rotate independently, and realizing the independence and coordination of the movement of the first gear ring 140, the first planetary carrier 130, and the first planetary gear 120.
[0059] Figure 5 This is a schematic diagram of another transmission device provided in an embodiment of this application. For example... Figure 5 As shown, in some possible implementations, the planet carrier in the first planetary gear train 100 may include a first support portion 131 and a first rotating shaft portion 132. The first support portion 131 is located on the side of the gear ring in the first planetary gear train 100 away from the second planetary gear train 200. The first rotating shaft portion 132 is connected to the first support portion 131 and is located within the range of the gear ring in the first planetary gear train 100. The planet gears in the first planetary gear train 100 are rotatably fitted onto the first rotating shaft portion 132.
[0060] Here, the first support portion 131 is located on the side of the first gear ring 140 away from the second planetary gear train 200, and maintains a gap with the first gear ring 140. The first rotating shaft portion 132 is parallel to the axis of the transmission device. One end of the first rotating shaft portion 132 is fixedly connected to the first support portion 131, and the other end extends into the first gear ring 140 to provide rotational support for the first planetary gear 120. Exemplarily, the first support portion 131 is in the shape of a spoke.
[0061] The first support portion 131 maintains a gap with the first gear ring 140 to avoid motion interference between the two. The first rotating shaft portion 132 extends into the first gear ring 140 to support the first planetary gear 120 and improve the axial compactness of the transmission device.
[0062] The outer ring side of the first support portion 131 protrudes from the outer ring side of the gear ring in the first planetary gear train 100, and one end of the second connecting portion 700 is fixedly connected to the outer ring side of the first support portion 131. That is, the outer ring side of the first support portion 131 protrudes from the outer ring side of the first gear ring 140.
[0063] In this way, the outer ring side of the first support portion 131 protrudes from the outer ring side of the first gear ring 140, providing sufficient and convenient connection space for the second connecting portion 700. The second connecting portion 700 does not require a complex connection structure, thus simplifying the structure of the second connecting portion 700.
[0064] Continue to refer to Figure 5 As shown, in some possible implementations, in the axial direction of the transmission device, the planet carrier in the second planetary gear train 200 is farther away from the first planetary gear train 100 than the ring gear in the second planetary gear train 200, and the outer ring side of the planet carrier in the second planetary gear train 200 is fixedly connected to the inner wall of the housing 300.
[0065] Exemplarily, the second planetary carrier 230 includes a second support portion 231 and a second rotating shaft portion 232. The second support portion 231 is located on the side of the second gear ring 240 opposite to the first planetary gear train 100 and maintains a gap with the second gear ring 240. The second rotating shaft portion 232 is parallel to the axis of the transmission device, one end of the second rotating shaft portion 232 is fixedly connected to the second support portion 231, and the other end extends into the area surrounded by the second gear ring 240 to provide rotational support for the second planetary gear 220. The second support portion 231 may be spoke-shaped, with its outer ring side fixedly connected to the inner wall of the housing 300.
[0066] The second connecting part 700 is fixedly connected at one end away from the planet carrier in the first planetary gear train 100 to the side of the gear ring in the second planetary gear train 200 that is close to the first planetary gear train 100.
[0067] In this way, the second connecting part 700 and the second planetary carrier 230 can avoid each other, preventing motion interference between them and achieving independence and coordination of movement of the second connecting part 700, the second planetary gear 220, and the second planetary carrier 230. Simultaneously, the path of the second connecting part 700 extending from the first planetary gear train 100 to the second gear ring 240 is short, thereby compressing the axial space and preventing the second planetary carrier 230 from occupying the axial space between the first planetary gear train 100 and the second planetary gear train 200. The axial spacing between the first planetary gear train 100 and the second planetary gear train 200 can be smaller, allowing for a more compact axial arrangement.
[0068] In some possible implementations, the kinematic equations of the first planetary gear train 100 and the second planetary gear train 200 satisfy the following formula: ig10=Zr1 / Zs1; formula (1) ig20=Zr2 / Zs2; formula (2) ig20=(1+ig10) / ig10; formula (3) Wherein, ig10 represents the transmission ratio between the ring gear and the sun gear in the first planetary gear train 100, that is, the transmission ratio between the first ring gear 140 and the first sun gear 110. ig20 represents the transmission ratio between the ring gear and the sun gear in the second planetary gear train 200, that is, the transmission ratio between the second ring gear 240 and the second sun gear 210. Zr1 represents the number of teeth on the ring gear in the first planetary gear train 100, and the number of teeth on the first ring gear 140. Zs1 represents the number of teeth on the sun gear in the first planetary gear train 100, that is, the number of teeth on the first sun gear 110. Zr2 represents the number of teeth on the ring gear in the second planetary gear train 200, that is, the number of teeth on the second ring gear 240. Zs2 represents the number of teeth on the sun gear in the second planetary gear train 200, that is, the number of teeth on the second sun gear 210.
[0069] Assuming the input torque of the first sun gear 110 is Ts1, based on the above kinematic equations, the output torque Tr1 of the first ring gear 140 and the output torque Tc1 of the first planetary carrier 130 can be obtained, and the calculation formulas are as follows: Tr1 = ig10 * Ts1; Tc1 = -(1 + ig10) * Ts1; Since the second gear ring 240 is fixedly connected to the first planetary carrier 130, the formula for calculating the torque Tr2 of the second gear ring 240 is as follows: Tr2=Tc1=-(1+ig10)*Ts1; Based on the torque of the second ring gear 240, the output torque Ts2 of the second sun gear 210 can be obtained, and the calculation formula is as follows: Ts2=Tr2 / ig20=-(1+ig10)*Ts1 / ig20; When the output torque Tr1 of the first ring gear 140 is equal to the output torque Ts2 of the second sun gear 210, and their directions are opposite (to ensure rotation in the same direction), then the following formula is satisfied: ig10*Ts1=(1+ig10)*Ts1 / ig20; The simplified formula is: ig20 = (1 + ig10) / ig10.
[0070] Therefore, when the kinematic equations of the first planetary gear train 100 and the second planetary gear train 200 satisfy formulas (1)-(3), it can be guaranteed that the first ring gear 140 and the second sun gear 210 can output rotational power with the same torque and in the same direction, thereby realizing the equal distribution of torque of the transmission device, ensuring the torque balance of the two output ends, and improving the handling and safety of the vehicle.
[0071] like Figure 1 , Figures 3-5In some possible implementations, the sun gear, planet gears, and ring gear in the first planetary gear train 100 have the same module. The sun gear, planet gears, and ring gear in the second planetary gear train 200 also have the same module.
[0072] In this system, the radius of the sun gear in the first planetary gear train 100 is smaller than the radius of the sun gear in the second planetary gear train 200, and the radius of the planet gears in the first planetary gear train 100 is larger than the radius of the planet gears in the second planetary gear train 200.
[0073] The radius of the first sun gear 110 is smaller than the radius of the second sun gear 210, and the radius of the first planet gear 120 is larger than the radius of the second planet gear 220.
[0074] In this way, by ensuring that the radius of the first sun gear 110 is smaller than that of the second sun gear 210, and the radius of the first planetary gear 120 is larger than that of the second planetary gear 220, and considering that their respective planetary gear trains have the same internal module, the tooth count relationship of the sun gear, planet gears, and ring gear in the two planetary gear trains can be precisely controlled. The smaller sun gear and larger planet gear in the first planetary gear train 100 complement the larger sun gear and smaller planet gear in the second planetary gear train 200, ensuring that the transmission ratios of the two planetary gear trains are equal, resulting in identical torque. This achieves equal torque distribution in the transmission device, ensuring torque balance at both output ends and improving vehicle handling and safety.
[0075] On the other hand, embodiments of this application provide a power system. Figure 1 , Figures 3-5 A structural diagram of the power system is also shown. (For example...) Figure 1 , Figures 3-5 As shown, the power system may include: a driver 400, a first connecting shaft 501, a second connecting shaft 502, and the aforementioned transmission device. The power system may be an axle; exemplarily, the axle may be an electric drive axle.
[0076] In the first planetary gear train 100, the sun gear is fixedly connected to the driver 400. The ring gear in the first planetary gear train 100 is fixedly connected to the first connecting shaft 501. In the second planetary gear train 200, the sun gear is fixedly connected to the second connecting shaft 502.
[0077] For example, the driver 400 can be a drive motor, the first connecting shaft 501 can be the left half-shaft of the axle, and the second connecting shaft 502 can be the right half-shaft of the axle. The left half-shaft is fixedly connected to the left wheel of the vehicle, and the right half-shaft is fixedly connected to the right wheel of the vehicle.
[0078] The drive motor can be mounted on the transmission shaft 111 which is fixedly connected to the first sun gear 110. The drive motor rotates, and through the transmission shaft 111, it drives the first sun gear 110 to rotate, thereby inputting power into the transmission device.
[0079] The power system provided in this application embodiment employs the aforementioned transmission device, which utilizes two simple planetary gear trains. The second planetary carrier remains stationary, while the planetary carrier of the first planetary gear train is fixedly connected to the ring gear of the second planetary gear train. The sun gear of the first planetary gear train receives the input power. The ring gear of the first planetary gear train and the sun gear of the second planetary gear train serve as two power output components. When the vehicle is turning or the load on both wheels is uneven, the adaptive rotation of the first and second planetary gears automatically adjusts the speed difference. The difference in speed between the first ring gear and the second sun gear eliminates the need for an additional differential, thus simplifying the transmission device's structure. Furthermore, by matching the gear ratios of the first and second planetary gear trains, the transmission device can simultaneously achieve a significant reduction in speed and a significant increase in torque. The transmission device, through two simple planetary gear trains, simultaneously achieves speed reduction and torque increase as well as differential functionality. Its compact structure eliminates the need for two independent differentials and reducers, significantly reducing size, weight, and cost.
[0080] Furthermore, embodiments of this application provide a vehicle that integrates the aforementioned power system. The vehicle can be either an electric vehicle or a traditional gasoline-powered vehicle.
[0081] The vehicle provided in this application embodiment, by adopting the above-mentioned power system and transmission device, allows the two simple planetary gear trains in the transmission device to simultaneously achieve differential function and deceleration and torque increase function. Moreover, the transmission device has a simple structure and high compactness, which improves the compactness of the power system in the vehicle.
[0082] In this application, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance. The term "multiple" refers to two or more unless otherwise expressly defined.
[0083] The above description is merely an optional embodiment of this application and is not intended to limit this application. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.
Claims
1. A transmission device, characterized in that, include: Housing (300), and a first planetary gear train (100) and a second planetary gear train (200) both mounted on the housing (300); Both the first planetary gear train (100) and the second planetary gear train (200) include: a sun gear, planet gears, a planet carrier, and a ring gear; the planet gears are located around the sun gear and mesh with the sun gear, the ring gears are located around the planet gears and the sun gear as a whole and mesh with the planet gears; the planet gears are also rotatably connected to the planet carrier; In this configuration, the planet carrier in the second planetary gear train (200) is fixedly connected to the housing (300); the gear ring in the second planetary gear train (200) is fixedly connected to the planet carrier in the first planetary gear train (100); the sun gear in the first planetary gear train (100) is fixedly connected to the drive (400); the gear ring in the first planetary gear train (100) is fixedly connected to the first connecting shaft (501); and the sun gear in the second planetary gear train (200) is fixedly connected to the second connecting shaft (502).
2. The transmission device according to claim 1, characterized in that, The first planetary gear train (100) and the second planetary gear train (200) are distributed axially in the transmission device; The axes of the sun gear and the ring gear in the first planetary gear train (100) and the sun gear in the second planetary gear train (200) are all located on the axis of the transmission device.
3. The transmission device according to claim 2, characterized in that, The sun gear in the first planetary gear train (100) has a through connecting channel (L), which is configured to be spaced around the periphery of the first connecting shaft (501). The transmission device further includes: a first connecting part (600); the first connecting part (600) is fixedly connected to the gear ring in the first planetary gear train (100) on the side axially close to the second planetary gear train (200); the first connecting part (600) is configured to be fixedly connected to one end of the first connecting shaft (501); The axis of the connecting channel (L) and the axis of the first connecting part (600) are both located on the axis of the transmission device.
4. The transmission device according to claim 3, characterized in that, In the axial direction of the transmission device, the planet carrier in the first planetary gear train (100) is located on the side of the first connecting part (600) away from the second planetary gear train (200); The transmission device further includes a second connecting part (700); one end of the second connecting part (700) is fixedly connected to the planet carrier in the first planetary gear train (100), and the other end passes around the outer ring side of the gear ring in the first planetary gear train (100) and the outer ring side of the first connecting part (600) and is fixedly connected to the gear ring in the second planetary gear train (200).
5. The transmission device according to claim 4, characterized in that, The planet carrier in the first planetary gear train (100) includes a first support portion (131) and a first rotating shaft portion (132); the first support portion (131) is located on the side of the gear ring in the first planetary gear train (100) away from the second planetary gear train (200), the first rotating shaft portion (132) is connected to the first support portion (131) and is located within the range of the gear ring in the first planetary gear train (100), and the planet gears in the first planetary gear train (100) are rotatably sleeved on the first rotating shaft portion (132); The outer ring side of the first support part (131) protrudes from the outer ring side of the gear ring in the first planetary gear train (100), and one end of the second connecting part (700) is fixedly connected to the outer ring side of the first support part (131).
6. The transmission device according to claim 4, characterized in that, In the axial direction of the transmission device, the planet carrier in the second planetary gear train (200) is farther away from the first planetary gear train (100) than the gear ring in the second planetary gear train (200), and the outer ring side of the planet carrier in the second planetary gear train (200) is fixedly connected to the inner wall of the housing (300); The second connecting part (700) is located away from the planet carrier in the first planetary gear train (100) and is fixedly connected to the side of the gear ring in the second planetary gear train (200) that is close to the first planetary gear train (100).
7. The transmission device according to any one of claims 1-6, characterized in that, The kinematic equations of the first planetary gear train (100) and the second planetary gear train (200) satisfy the following formula: ig10 = Zr1 / Zs1; ig20 = Zr2 / Zs2; ig20 = (1 + ig10) / ig10; Wherein, ig10 represents the transmission ratio between the ring gear and the sun gear in the first planetary gear train (100); ig20 represents the transmission ratio between the ring gear and the sun gear in the second planetary gear train (200); Zr1 represents the number of teeth on the ring gear in the first planetary gear train (100); Zs1 represents the number of teeth on the sun gear in the first planetary gear train (100); Zr2 represents the number of teeth on the ring gear in the second planetary gear train (200); and Zs2 represents the number of teeth on the sun gear in the second planetary gear train (200).
8. The transmission device according to any one of claims 1-6, characterized in that, The sun gear, planet gears and ring gear in the first planetary gear train (100) have the same module; the sun gear, planet gears and ring gear in the second planetary gear train (200) have the same module. Wherein, the radius of the sun gear in the first planetary gear train (100) is smaller than the radius of the sun gear in the second planetary gear train (200), and the radius of the planet gear in the first planetary gear train (100) is larger than the radius of the planet gear in the second planetary gear train (200).
9. A power system, characterized in that, include: The driver (400), the first connecting shaft (501), the second connecting shaft (502), and the transmission device according to any one of claims 1-8; In this configuration, the sun gear in the first planetary gear train (100) is fixedly connected to the driver (400); the ring gear in the first planetary gear train (100) is fixedly connected to the first connecting shaft (501); and the sun gear in the second planetary gear train (200) is fixedly connected to the second connecting shaft (502).
10. A vehicle, characterized in that, The vehicle integrates the power system as described in claim 9.