CN108501672A - Power drive system - Google Patents
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- CN108501672A CN108501672A CN201710105201.1A CN201710105201A CN108501672A CN 108501672 A CN108501672 A CN 108501672A CN 201710105201 A CN201710105201 A CN 201710105201A CN 108501672 A CN108501672 A CN 108501672A
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K1/00—Arrangement or mounting of electrical propulsion units
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location or kind of gearing
- B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location or kind of gearing of change-speed gearing
- B60K17/08—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location or kind of gearing of change-speed gearing of mechanical type
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Abstract
本申请公开了一种动力传动系统，包括电机和减速器。电机的输出轴的轴心为第一中心线。减速器包括太阳轮、内齿圈、双联行星轮以及行星架。太阳轮固定套设在输出轴的外周。内齿圈与太阳轮同轴。双联行星轮的第一齿轮与太阳轮啮合，双联行星轮的第二齿轮与内齿圈啮合。行星架的第一连接部转动连接输出轴，以使输出轴在垂直第一中心线的方向上支撑行星架。行星架的第二连接部绕第一中心线转动。行星架的第三连接部转动连接在第二齿轮的轴心处。输出轴带动太阳轮转动，使得第一齿轮和第二齿轮同步地在太阳轮和内齿圈之间同时自转和公转，第二齿轮带动第三连接部绕第一中心线转动，使得第二连接部转动。所述动力传动系统的减速比提升难度小。
The application discloses a power transmission system, including a motor and a reducer. The axis center of the output shaft of the motor is the first central line. The reducer includes sun gear, ring gear, double planetary gear and planet carrier. The sun gear is fixedly sleeved on the outer periphery of the output shaft. The ring gear is coaxial with the sun gear. The first gear of the double planetary gear meshes with the sun gear, and the second gear of the double planetary gear meshes with the ring gear. The first connecting portion of the planet carrier is rotatably connected to the output shaft, so that the output shaft supports the planet carrier in a direction perpendicular to the first central line. The second connecting portion of the planet carrier rotates around the first center line. The third connecting portion of the planet carrier is rotatably connected to the axis of the second gear. The output shaft drives the sun gear to rotate, so that the first gear and the second gear synchronously rotate and revolve between the sun gear and the ring gear at the same time, and the second gear drives the third connecting part to rotate around the first centerline, so that the second connecting part turn. It is less difficult to increase the reduction ratio of the power transmission system.
Description
技术领域technical field
本申请涉及电动汽车技术领域，尤其涉及一种动力传动系统。The present application relates to the technical field of electric vehicles, in particular to a power transmission system.
背景技术Background technique
现有应用行星轮系传动系统的电动汽车多是采用NGW型行星轮系，即：电机转子轴的输出端与行星轮系减速器的太阳轮连接，内齿圈与壳体连接，根据太阳轮、行星轮和内齿圈的齿轮啮合传动原理，最终通过行星架输出电机的转速和功率。NGW型行星轮系减速器的减速比i1H计算公式为：Most of the existing electric vehicles using the planetary gear transmission system adopt the NGW type planetary gear system, that is, the output end of the motor rotor shaft is connected to the sun gear of the planetary gear reducer, and the inner ring gear is connected to the housing. According to the sun gear , planetary gear and ring gear gear mesh transmission principle, and finally output the speed and power of the motor through the planet carrier. The formula for calculating the reduction ratio i 1H of the NGW planetary gear reducer is:
i1H＝z2/z1+1。i 1H =z 2 /z 1 +1.
其中，z1为太阳轮的齿数；z2为内齿圈的齿数。Among them, z 1 is the number of teeth of the sun gear; z 2 is the number of teeth of the inner ring gear.
为了满足电动汽车整车的加速性能和高速性能，动力系统的发展对电动汽车减速器的减速比提出了更高的需求。由上述减速比i1H计算公式可知，可通过增加内齿圈的齿数或减小太阳轮的齿数来提升减速器的减速比。然而，增加内齿圈的齿数则会增加减速器的径向尺寸，导致减速器难以满足电动汽车动力传动系统部分的安装空间限制要求；减小太阳轮的齿数则容易导致减速器结构稳定性差，从而使减速器在高速重载工况下工作可靠性很差、振动明显、噪声大，因此现有NGW型行星减速器的减速比难以提升。In order to meet the acceleration performance and high-speed performance of the electric vehicle, the development of the power system puts forward higher requirements for the reduction ratio of the electric vehicle reducer. From the calculation formula of the reduction ratio i 1H above, it can be seen that the reduction ratio of the reducer can be increased by increasing the number of teeth of the ring gear or reducing the number of teeth of the sun gear. However, increasing the number of teeth of the inner ring gear will increase the radial size of the reducer, making it difficult for the reducer to meet the installation space requirements of the power transmission system of electric vehicles; reducing the number of teeth of the sun gear will easily lead to poor structural stability of the reducer. As a result, the reducer has poor working reliability, obvious vibration and high noise under high-speed and heavy-load conditions. Therefore, it is difficult to improve the reduction ratio of the existing NGW planetary reducer.
发明内容Contents of the invention
本申请实施例所要解决的技术问题在于，提供一种减速比提升难度小的动力传动系统。The technical problem to be solved by the embodiments of the present application is to provide a power transmission system that is less difficult to increase the reduction ratio.
为了实现上述目的，本申请实施例采用如下技术方案：In order to achieve the above purpose, the embodiment of the present application adopts the following technical solutions:
本申请实施例提供了一种动力传动系统，所述动力传动系统可应用于电动汽车。所述动力传动系统包括电机和减速器。所述电机包括输出轴，所述输出轴的轴心为第一中心线。所述减速器包括太阳轮、内齿圈、双联行星轮以及行星架。所述太阳轮固定套设在所述输出轴的外周。所述内齿圈与所述太阳轮同轴且与所述太阳轮之间形成安装空间。所述双联行星轮设于所述安装空间内。所述双联行星轮包括同轴且彼此固定连接的第一齿轮和第二齿轮。所述第一齿轮与所述太阳轮啮合，所述第二齿轮与所述内齿圈啮合。所述行星架包括彼此固定连接的第一连接部、第二连接部及第三连接部。所述第一连接部设有朝向所述太阳轮的轴孔，所述输出轴的端部穿过所述太阳轮后伸入所述轴孔，所述输出轴的端部与所述第一连接部转动连接，以使所述输出轴在垂直所述第一中心线的方向上支撑所述行星架。所述第二连接部连接在所述第一连接部的背向所述太阳轮的一侧，所述第二连接部绕所述第一中心线转动。所述第三连接部转动连接在所述第二齿轮的轴心处。所述输出轴带动所述太阳轮转动，使得所述第一齿轮和所述第二齿轮同步地在所述太阳轮和所述内齿圈之间同时自转和公转，所述第二齿轮带动所述第三连接部绕所述第一中心线转动，使得所述第二连接部转动以驱动所述电动汽车的车轮转动。An embodiment of the present application provides a power transmission system, and the power transmission system can be applied to an electric vehicle. The power transmission system includes a motor and a reducer. The motor includes an output shaft, and the axis of the output shaft is the first central line. The speed reducer includes a sun gear, an inner ring gear, a double planetary gear and a planet carrier. The sun gear is fixedly sleeved on the outer periphery of the output shaft. The inner ring gear is coaxial with the sun gear and forms an installation space with the sun gear. The double planetary gear is arranged in the installation space. The double planetary gear includes a first gear and a second gear that are coaxial and fixedly connected to each other. The first gear meshes with the sun gear, and the second gear meshes with the ring gear. The planet carrier includes a first connecting portion, a second connecting portion and a third connecting portion fixedly connected to each other. The first connecting portion is provided with a shaft hole facing the sun gear, the end of the output shaft passes through the sun gear and then extends into the shaft hole, and the end of the output shaft is connected to the first The connecting portion is connected in rotation so that the output shaft supports the planetary carrier in a direction perpendicular to the first central line. The second connecting portion is connected to a side of the first connecting portion facing away from the sun gear, and the second connecting portion rotates around the first centerline. The third connecting portion is rotatably connected to the shaft center of the second gear. The output shaft drives the sun gear to rotate, so that the first gear and the second gear synchronously rotate and revolve between the sun gear and the ring gear at the same time, and the second gear drives the The third connecting part rotates around the first center line, so that the second connecting part rotates to drive the wheels of the electric vehicle to rotate.
在本申请实施例中，所述“轴心”为“一个物体绕着转动或者可以设想绕着转动的一根直线”。定义平行于所述第一中心线的方向为轴向，垂直于所述第一中心线的方向为径向。所述输出轴绕所述第一中心线转动。所述输出轴带动所述太阳轮绕所述第一中心线转动，所述太阳轮的轴心与所述第一中心线共线。所述内齿圈的轴心与所述第一中心线共线，所述内齿圈不转动。所述第一齿轮和所述第二齿轮的轴心为第二中心线，所述第二中心线平行于所述第一中心线。所述第一齿轮和所述第二齿轮沿所述第二中心线排列。所述第一齿轮和所述第二齿轮同步地绕所述第一中心线公转，同时所述第一齿轮和所述第二齿轮同步地绕所述第二中心线自转。由于所述输出轴的端部伸入所述第三连接部的所述轴孔，所述输出轴的端部转动连接所述第三连接部的所述轴孔，因此所述输出轴在轴向上能够相对所述第三连接部转动，在径向(也即垂直所述第一中心线的方向)上能够支撑所述第三连接部。由于所述行星架的所述第一连接部、所述第二连接部及所述第三连接部彼此固定连接，因此所述输出轴能够在径向上支撑所述行星架。由于所述第二连接部绕所述第一中心线转动，因此所述行星架的运动轨迹也是绕所述第一中心线转动的。所述第二齿轮绕所述第一中心线转动时，带动所述第三连接部绕所述第一中心线转动，所述第三连接部的转向和转速分别与所述第二齿轮的公转转向和公转转速相同。所述第二连接部与所述第三连接部同步转动，所述第二连接部的转向和转速也分别与所述第二齿轮的公转转向和公转转速相同。所述第二连接部绕所述第一中心线转动，使得述第二连接部能够驱动所述电动汽车的车轮转动。由于所述第三连接部转动连接在所述第二齿轮的轴心处，因此所述第二齿轮会因其自转动作而相对所述第三连接部转动。In the embodiment of the present application, the "axis" is "a straight line around which an object rotates or conceivably rotates". A direction parallel to the first centerline is defined as an axial direction, and a direction perpendicular to the first centerline is defined as a radial direction. The output shaft rotates about the first centerline. The output shaft drives the sun gear to rotate around the first centerline, and the axis of the sun gear is collinear with the first centerline. The shaft center of the inner ring gear is collinear with the first center line, and the inner ring gear does not rotate. The axes of the first gear and the second gear are a second centerline, and the second centerline is parallel to the first centerline. The first gear and the second gear are arranged along the second centerline. The first gear and the second gear synchronously revolve around the first centerline, while the first gear and the second gear synchronously rotate around the second centerline. Since the end of the output shaft protrudes into the shaft hole of the third connecting portion, and the end of the output shaft is rotatably connected to the shaft hole of the third connecting portion, the output shaft is It can rotate upward relative to the third connecting portion, and can support the third connecting portion in a radial direction (that is, a direction perpendicular to the first central line). Since the first connection portion, the second connection portion and the third connection portion of the planet carrier are fixedly connected to each other, the output shaft can support the planet carrier in the radial direction. Since the second connecting portion rotates around the first centerline, the motion track of the planet carrier also rotates around the first centerline. When the second gear rotates around the first centerline, it drives the third connecting part to rotate around the first centerline, and the steering and rotation speed of the third connecting part are respectively related to the revolution of the second gear. The rotation speed and the revolution speed are the same. The second connecting part rotates synchronously with the third connecting part, and the rotation direction and rotation speed of the second connection part are also the same as the revolution rotation speed and revolution speed of the second gear respectively. The second connecting part rotates around the first center line, so that the second connecting part can drive the wheels of the electric vehicle to rotate. Since the third connecting part is rotatably connected to the axis of the second gear, the second gear will rotate relative to the third connecting part due to its self-rotation.
本申请实施例所述动力传动系统的减速比i计算公式为：The calculation formula of the reduction ratio i of the power transmission system described in the embodiment of the present application is:
其中，Z为所述太阳轮的齿数；Z为所述内齿圈的齿数；Zc为所述双联行星轮的所述第一齿轮的齿数；Zd为所述双联行星轮的所述第二齿轮的齿数。由减速比i计算公式可知，本实施例所述动力传动系统可通过增加Zc/Zd的大小来提升所述动力传动系统的减速比，也即增大所述第一齿轮与所述第二齿轮的齿数比，不需要为了增加减速比而不合理地增加所述内齿圈的齿数或减少所述太阳轮的齿数，使得所述减速器的径向尺寸满足安装空间限制要求且结构稳定性较佳，所述动力传动系统的减速比提升难度小。Wherein, Z is the number of teeth of the sun gear; Z is the number of teeth of the ring gear; Z c is the number of teeth of the first gear of the double planetary gear; Z d is the number of teeth of the double planetary gear The number of teeth of the second gear. It can be seen from the formula for calculating the reduction ratio i that the power transmission system in this embodiment can increase the reduction ratio of the power transmission system by increasing the size of Z c /Z d , that is, increase the first gear and the second gear. The gear ratio of the second gear does not need to unreasonably increase the number of teeth of the inner ring gear or reduce the number of teeth of the sun gear in order to increase the reduction ratio, so that the radial size of the reducer meets the installation space restriction requirements and the structure is stable The performance is better, and the reduction ratio of the power transmission system is less difficult to increase.
由于所述输出轴的所述端部穿过所述太阳轮后伸入所述轴孔，因此所述电机的所述输出轴直接伸入所述减速器以实现动力传递和结构支撑，使得所述电机与所述减速器之间的配合更为紧凑，所述动力传动系统的整体体积更小，从而能够很好地满足电动汽车的安装空间限制要求。所述输出轴对所述行星架的径向结构支撑也提高了所述减速器的结构稳定性，使得所述动力传动系统在高速重载的工况下传动平稳、振动噪声小。Since the end of the output shaft passes through the sun gear and then extends into the shaft hole, the output shaft of the motor directly extends into the reducer to realize power transmission and structural support, so that the The cooperation between the motor and the speed reducer is more compact, and the overall volume of the power transmission system is smaller, so that the limited installation space of the electric vehicle can be well met. The radial structural support of the output shaft to the planet carrier also improves the structural stability of the reducer, so that the power transmission system has stable transmission and low vibration and noise under high-speed and heavy-load working conditions.
本申请实施例所述动力传动系统，可用于将电动汽车的驱动电机动力传送给等速万向节驱动轴总成。本申请实施例所述动力传动系统也可用于电动汽车的轮边或轮毂电机的动力总成系统。The power transmission system described in the embodiment of the present application can be used to transmit the power of the drive motor of the electric vehicle to the constant velocity universal joint drive shaft assembly. The power transmission system described in the embodiments of the present application may also be used in a powertrain system of a wheel or hub motor of an electric vehicle.
可选的，所述输出轴与所述太阳轮之间通过花键固定连接，使得所述输出轴与所述太阳轮之间的动力传动平稳，所能传递的载荷较大。当然，在其他实施方式中，也可通过键连接或者焊接等方式固定连接所述输出轴与所述太阳轮。或者，可一体成型所述输出轴和所述太阳轮，形成太阳轮轴。Optionally, the output shaft and the sun gear are fixedly connected by splines, so that the power transmission between the output shaft and the sun gear is stable and the load that can be transmitted is large. Certainly, in other implementation manners, the output shaft and the sun gear may also be fixedly connected by means of key connection or welding. Alternatively, the output shaft and the sun gear may be integrally formed to form a sun gear shaft.
可选的，所述第二连接部内形成内花键。所述第二连接部可通过花键固定连接等速万向节驱动轴总成，而后通过驱动轴总成驱动电动汽车的车轮转动。或者，所述第二连接部可直接通过转轴连接车轮，所述第二连接部转动以带动车轮转动。在另一种实施方式中，所述第二连接部可形成法兰盘，从而通过法兰连接至驱动轴总成。Optionally, internal splines are formed in the second connecting portion. The second connecting portion can be fixedly connected to the constant velocity universal joint drive shaft assembly through a spline, and then drive the wheels of the electric vehicle to rotate through the drive shaft assembly. Alternatively, the second connecting part may be directly connected to the wheel through a rotating shaft, and the second connecting part rotates to drive the wheel to rotate. In another embodiment, the second connecting portion may form a flange, so as to be connected to the drive shaft assembly through the flange.
可选的，所述双联行星轮的所述第一齿轮和所述第二齿轮一体成型。或者，所述第一齿轮和所述第二齿轮是分体的，所述第一齿轮和所述第二齿轮通过键连接或者焊接等方式彼此固定连接。Optionally, the first gear and the second gear of the double planetary gear are integrally formed. Alternatively, the first gear and the second gear are separated, and the first gear and the second gear are fixedly connected to each other through key connection or welding.
可选的，所述第三连接部与所述第二齿轮之间通过轴承连接，该轴承的轴承轴心线与所述第二中心线共线。该轴承可同时穿过所述第一齿轮、所述第二齿轮及所述第三连接部，从而更好地将所述双联行星轮的动力传递至所述行星架。Optionally, the third connecting portion is connected to the second gear through a bearing, and the bearing axis of the bearing is collinear with the second centerline. The bearing can pass through the first gear, the second gear and the third connecting portion at the same time, so as to better transmit the power of the double planetary gear to the planet carrier.
可选的，所述输出轴的端部的外周侧与所述轴孔的内周侧之间通过轴承连接，该轴承的轴承轴心线与所述第一中心线共线，从而使所述第一连接部与所述输出轴之间形成轴向上的彼此转动和径向上的彼此支撑。Optionally, the outer peripheral side of the end of the output shaft is connected to the inner peripheral side of the shaft hole through a bearing, and the bearing axis of the bearing is collinear with the first centerline, so that the The first connecting portion and the output shaft form mutual rotation in the axial direction and mutual support in the radial direction.
在一种实施方式中，所述减速器还包括空转太阳轮，所述空转太阳轮转动套设在所述第一连接部的外周，所述空转太阳轮与所述第二齿轮啮合。In one embodiment, the speed reducer further includes an idler sun gear, the idler sun gear is rotatably sleeved on the outer periphery of the first connecting part, and the idler sun gear meshes with the second gear.
在本实施方式中，所述第一连接部可通过所述空转太阳轮对所述双联行星轮进行径向支撑，进一步提高所述减速器的结构稳定性，使得所述动力传动系统在高速重载的工况下，传动平稳，振动噪声小。In this embodiment, the first connecting portion can radially support the double planetary gear through the idling sun gear, further improving the structural stability of the reducer, so that the power transmission system can Under heavy load conditions, the transmission is stable and the vibration and noise are small.
可以理解的是，所述输出轴在通过所述太阳轮对所述双联行星轮的所述第一齿轮进行径向支撑和动力传输的同时，还依次通过所述第一连接部和所述空转太阳轮对所述双联行星轮的所述第二齿轮进行径向支撑，并且所述输出轴对所述行星架进行了径向支撑，使得所述太阳轮与所述双联行星轮之间、所述双联行星轮与所述行星架之间的转动动作平稳、可靠，所述动力传动系统传动平稳、动力输出状态稳定且振动噪声小。It can be understood that, while the output shaft radially supports and transmits power to the first gear of the double planetary gear through the sun gear, it also passes through the first connecting part and the The idling sun gear radially supports the second gear of the double planetary gear, and the output shaft radially supports the planet carrier, so that the distance between the sun gear and the double planetary gear Between, the rotation action between the double planetary wheel and the planet carrier is stable and reliable, the power transmission system has stable transmission, stable power output state and low vibration and noise.
可选的，所述第一连接部的外周侧与所述空转太阳轮的内周侧之间通过轴承连接，该轴承的轴承轴心线与所述第一中心线共线，从而使所述第一连接部与所述空转太阳轮之间形成轴向上的彼此转动和径向上的彼此支撑。Optionally, the outer peripheral side of the first connection part is connected to the inner peripheral side of the idling sun gear through a bearing, and the bearing axis of the bearing is collinear with the first centerline, so that the The first connecting portion and the idling sun gear form mutual rotation in the axial direction and mutual support in the radial direction.
可选的，所述空转太阳轮在轴向上相对所述第一连接部固定。可在所述第一连接部的外周侧上形成定位台阶，所述空转太阳轮的一侧端面抵接所述定位台阶，以实现轴向定位。Optionally, the idling sun gear is axially fixed relative to the first connecting portion. A positioning step may be formed on the outer peripheral side of the first connecting portion, and one end surface of the idler sun gear abuts against the positioning step to achieve axial positioning.
在一种实施方式中，所述双联行星轮的数量为多个，多个所述双联行星轮在所述太阳轮的周向上均匀排布。此时，多个所述双联行星轮均匀地转动连接于所述第三连接部的周向，多个所述双联行星轮等间距地连接在所述太阳轮与所述行星架之间。In one embodiment, there are multiple double planetary gears, and the multiple double planetary gears are evenly arranged in the circumferential direction of the sun gear. At this time, a plurality of the double planetary gears are uniformly rotated and connected in the circumferential direction of the third connecting portion, and a plurality of the double planetary gears are connected between the sun gear and the planet carrier at equal intervals .
在本实施方式中，所述太阳轮同时与多个所述双联行星轮啮合，使得功率被多个所述双联行星轮均匀分流，而后多个所述双联行星轮同时带动所述行星架转动，使得功率最终合流至所述行星架并通过所述行星架输出，因此所述减速器可实现大功率传动，进一步满足现阶段以及未来电动汽车对动力传动系统的重载的要求。In this embodiment, the sun gear meshes with a plurality of the double planetary gears at the same time, so that the power is evenly distributed by the multiple double planetary gears, and then the multiple double planetary gears drive the planetary gears at the same time. The carrier rotates, so that the power is finally merged to the planet carrier and output through the planet carrier, so the reducer can realize high-power transmission, and further meet the heavy load requirements of the current and future electric vehicles on the power transmission system.
可以理解的，多个所述双联行星轮等间距地连接在所述太阳轮与所述行星架之间，能够提高所述减速器传动的稳定性和承载能力，使得所述动力传动系统传动平稳、可靠。It can be understood that a plurality of double planetary gears are equidistantly connected between the sun gear and the planetary carrier, which can improve the stability and bearing capacity of the transmission of the reducer, so that the transmission of the power transmission system Smooth and reliable.
在一种实施方式中，所述第一齿轮的齿数多于所述第二齿轮的齿数。所述第一齿轮的模数与所述第二齿轮的模数相同，则所述第一齿轮的分度圆直径大于所述第二齿轮的分度圆直径。In one embodiment, the number of teeth of the first gear is greater than the number of teeth of the second gear. The module of the first gear is the same as that of the second gear, and the diameter of the pitch circle of the first gear is larger than the diameter of the pitch circle of the second gear.
在本实施方式中，由于所述第一齿轮的齿数多于所述第二齿轮的齿数，因此Zc/Zd＞1，所述动力传动系统的减速器的减速比i比现有技术的减速器的减速比范围大。本申请实施例所述动力传动系统的减速比i的范围可以达到6～15左右，所述输出轴的转速可达到20000r/min以上，满足现阶段以及未来电动汽车对动力传动系统的大减速比及高速的要求。In this embodiment, since the number of teeth of the first gear is more than that of the second gear, Z c /Z d >1, and the reduction ratio i of the reducer of the power transmission system is higher than that of the prior art The reduction ratio range of the reducer is large. The range of reduction ratio i of the power transmission system described in the embodiment of the present application can reach about 6 to 15, and the speed of the output shaft can reach more than 20000r/min, which meets the large reduction ratio of electric vehicles to the power transmission system at the present stage and in the future and high-speed requirements.
在一种实施方式中，所述电机还包括电机壳体，所述减速器还包括减速器壳体，所述电机壳体和所述减速器壳体分别连接于所述内齿圈的相对两侧，以共同围设出减速腔。In one embodiment, the motor further includes a motor housing, and the reducer further includes a reducer housing, and the motor housing and the reducer housing are respectively connected to The opposite sides are used to jointly enclose the deceleration chamber.
所述减速器壳体与所述内齿圈的一侧端面可通过紧固件固定连接。所述电机壳体与所述内齿圈的另一侧端面可通过紧固件固定连接。所述减速器壳体与所述内齿圈的连接方式和所述电机壳体与所述内齿圈的连接方式相同，有利于方便所述动力传动系统的安装、拆卸与互换。当然，在其他实施方式中，所述减速器壳体与所述内齿圈的连接方式和所述电机壳体与所述内齿圈的连接方式也可以不同。The reducer housing and one side end surface of the ring gear can be fixedly connected by fasteners. The motor housing and the other end surface of the ring gear can be fixedly connected by fasteners. The connection mode between the reducer housing and the ring gear is the same as the connection mode between the motor housing and the ring gear, which facilitates the installation, disassembly and interchange of the power transmission system. Certainly, in other embodiments, the connection manner between the reducer housing and the ring gear and the connection manner between the motor housing and the ring gear may also be different.
所述紧固件包括但不限于螺栓、螺钉等。当然，在其他实施方式中，所述减速器壳体与所述内齿圈的一侧端面也可通过键连接或者焊接等方式固定连接。所述电机壳体与所述内齿圈的另一侧端面也可通过键连接或者焊接等方式固定连接。The fasteners include but are not limited to bolts, screws and the like. Certainly, in other implementation manners, the reducer housing and one side end surface of the ring gear may also be fixedly connected by means of key connection or welding. The motor housing and the other end surface of the ring gear can also be fixedly connected by means of key connection or welding.
所述电机壳体设有第一通孔，所述输出轴自所述第一通孔伸入所述减速腔且转动连接所述电机壳体。所述输出轴的外周侧与所述第一通孔的孔壁之间设置轴承，该轴承的轴承轴心线与所述第一中心线共线，从而使所述输出轴得以在轴向上相对所述第一通孔转动，且在径向上被所述第一通孔支撑。The motor housing is provided with a first through hole, and the output shaft extends into the deceleration chamber from the first through hole and is rotatably connected to the motor housing. A bearing is arranged between the outer peripheral side of the output shaft and the hole wall of the first through hole, and the bearing axis of the bearing is collinear with the first center line, so that the output shaft can be axially It rotates relative to the first through hole and is supported by the first through hole in the radial direction.
所述减速器壳体设有第二通孔，所述行星架收容于所述减速腔，所述第二连接部自所述第二通孔伸出所述减速腔且转动连接所述减速器壳体。所述第二连接部的外周侧与所述第二通孔的孔壁之间设置轴承，该轴承的轴承轴心线与所述第一中心线共线，从而使所述第二连接部得以在轴向上相对所述第二通孔转动，且在径向上被所述第二通孔支撑。The reducer casing is provided with a second through hole, the planet carrier is accommodated in the reducer chamber, the second connecting part extends out of the reducer chamber from the second through hole and is rotatably connected to the reducer case. A bearing is arranged between the outer peripheral side of the second connection part and the hole wall of the second through hole, and the bearing axis of the bearing is collinear with the first center line, so that the second connection part can It rotates relative to the second through hole in the axial direction and is supported by the second through hole in the radial direction.
可选的，所述动力传动系统还包括第一密封件和第二密封件，所述第一密封件密封于所述第一通孔的孔壁与所述输出轴之间，所述第二密封件密封于所述第二通孔的孔壁与所述第二连接部之间。Optionally, the power transmission system further includes a first seal and a second seal, the first seal is sealed between the hole wall of the first through hole and the output shaft, the second The sealing element is sealed between the hole wall of the second through hole and the second connection part.
可选的，所述动力传动系统设有连通所述减速腔的进油孔和出油孔，所述进油孔设于所述电机壳体或所述减速器壳体，所述出油孔设于所述电机壳体或所述减速器壳体。所述动力传动系统采用喷油泵方式实现润滑和冷却功能，使得设于所述减速腔内的部件(包括部分所述输出轴、所述太阳轮、所述空转太阳轮、所述双联行星轮及部分所述行星架)润滑和冷却充分，有利于保障所述动力传动系统的工作可靠性，提高了所述动力传动系统的使用寿命。Optionally, the power transmission system is provided with an oil inlet hole and an oil outlet hole communicating with the deceleration chamber, the oil inlet hole is arranged on the motor housing or the reducer housing, and the oil outlet hole The hole is provided in the motor housing or the reducer housing. The power transmission system adopts an oil injection pump to realize lubrication and cooling functions, so that the components (including part of the output shaft, the sun gear, the idling sun gear, and the double planetary gear) arranged in the deceleration chamber and part of the planet carrier) are sufficiently lubricated and cooled, which is conducive to ensuring the reliability of the power transmission system and improving the service life of the power transmission system.
在一种实施方式中，所述电机还包括定子安装架、定子及转子。所述定子安装架连接于所述电机壳体远离所述内齿圈的一侧，以共同围设出电机腔。所述定子安装架与所述电机壳体之间可通过紧固件连接、键连接或者焊接等方式固定连接。所述定子收容于所述电机腔且相对所述定子安装架固定。所述转子套设在所述定子内部，所述转子的轴心处形成所述输出轴。In one embodiment, the motor further includes a stator mounting frame, a stator and a rotor. The stator installation frame is connected to a side of the motor housing away from the ring gear, so as to jointly define a motor cavity. The stator installation frame and the motor housing can be fixedly connected by fasteners, keys or welding. The stator is accommodated in the motor cavity and fixed relative to the stator installation frame. The rotor is sleeved inside the stator, and the output shaft is formed at the center of the rotor.
在本实施方式中，可将所述减速器壳体、所述行星架、所述空转太阳轮、所述内齿圈及所述双联行星轮组装成第一模块，将所述电机壳体、所述太阳轮及所述转子组装成第二模块，将所述定子安装架、所述定子组装成的第三模块。所述第一模块、所述第二模块及所述第三模块的组成明确，单独组装工序简易。同时，所述第一模块、所述第二模块及所述第三模块的模块端面接口可设置成一致接口(例如紧固件连接、焊接或键连接)，从而方便模块之间的拆装与互换。故而，所述动力传动系统具有高度的模块化和集成化，能够降低所述动力传动系统在整车中的空间占有率、拆装和维护成本。In this embodiment, the reducer housing, the planet carrier, the idling sun gear, the ring gear and the double planetary gear can be assembled into a first module, and the motor housing The body, the sun gear and the rotor are assembled into a second module, and the stator mounting frame and the stator are assembled into a third module. The composition of the first module, the second module and the third module is clear, and the individual assembly process is simple. At the same time, the module end face interfaces of the first module, the second module and the third module can be set to a consistent interface (such as fastener connection, welding or key connection), so as to facilitate the disassembly and assembly of the modules. exchange. Therefore, the power transmission system has a high degree of modularization and integration, which can reduce the space occupancy, disassembly and maintenance costs of the power transmission system in the vehicle.
可选的，所述定子安装架的端壁设有支撑槽，所述转子的轴心处形成背向所述输出轴的支撑轴，所述支撑轴转动连接所述支撑槽。也即所述转子相对的两端分别形成所述输出轴和所述支撑轴。所述电机壳体形成一安装口，所述定子安装架自所述安装口安装至所述电机壳体，所述定子安装架的所述端壁封闭所述安装口。Optionally, the end wall of the stator installation frame is provided with a support groove, and a support shaft facing away from the output shaft is formed at the axis of the rotor, and the support shaft is rotatably connected to the support groove. That is, the opposite ends of the rotor form the output shaft and the support shaft respectively. The motor housing forms an installation opening, the stator installation frame is installed to the motor housing from the installation opening, and the end wall of the stator installation frame closes the installation opening.
所述支撑轴的外周侧与所述支撑槽的内周侧之间通过轴承连接，该轴承的轴承轴心线与所述第一中心线共线，从而使所述支撑轴得以在轴向上相对所述支撑槽转动，且在径向上被所述支撑槽支撑。The outer peripheral side of the support shaft is connected to the inner peripheral side of the support groove through a bearing, and the bearing axis of the bearing is collinear with the first center line, so that the support shaft can be axially It rotates relative to the support groove and is supported by the support groove in the radial direction.
在一种实施方式中，所述定子安装架还包括自所述端壁向所述电机腔延伸的支撑壁，所述支撑壁的外周侧与所述电机壳体的内周侧之间过盈配合连接且形成液冷通道。所述液冷通道可为螺旋式通道。通过所述液冷通道可对所述电机腔内的部件(包括所述支撑壁、所述定子及所述转子)进行冷却，有利于保障所述动力传动系统的工作可靠性，提高了所述动力传动系统的使用寿命。In one embodiment, the stator installation frame further includes a support wall extending from the end wall to the motor cavity, and a gap between the outer peripheral side of the support wall and the inner peripheral side of the motor housing are connected with an interference fit and form a liquid cooling channel. The liquid cooling channel may be a spiral channel. The components in the motor cavity (including the support wall, the stator and the rotor) can be cooled through the liquid cooling channel, which is beneficial to ensure the working reliability of the power transmission system and improves the Service life of the drivetrain.
可选的，所述定子固定于所述支撑壁的内周侧。所述定子可与所述支撑壁的内周侧通过过盈配合固定连接。Optionally, the stator is fixed on the inner peripheral side of the supporting wall. The stator can be fixedly connected to the inner peripheral side of the support wall through interference fit.
附图说明Description of drawings
图1是本申请实施例提供的一种动力传动系统的结构示意图。Fig. 1 is a schematic structural diagram of a power transmission system provided by an embodiment of the present application.
图2是图1所示动力传动系统的部分分解图。FIG. 2 is a partially exploded view of the powertrain shown in FIG. 1 .
图3是图1所示动力传动系统应用于电动汽车的示意图。FIG. 3 is a schematic diagram of the application of the power transmission system shown in FIG. 1 to an electric vehicle.
图4是图1中Ⅳ处结构的放大示意图。Fig. 4 is an enlarged schematic view of the structure at IV in Fig. 1 .
图5是图1所示动力传动系统的模块化的结构示意图。FIG. 5 is a schematic structural diagram of the modularization of the power transmission system shown in FIG. 1 .
具体实施方式Detailed ways
下面结合本申请实施例中的附图对本申请实施例进行描述。Embodiments of the present application are described below with reference to the drawings in the embodiments of the present application.
请一并参阅图1至图4，本申请实施例提供了一种动力传动系统100，所述动力传动系统100可应用于电动汽车200。所述动力传动系统100包括电机100a和减速器100b。所述电机100a包括输出轴1，所述输出轴1的轴心为第一中心线101。所述减速器100b包括太阳轮2、内齿圈3、双联行星轮4以及行星架5。所述太阳轮2固定套设在所述输出轴1的外周。所述内齿圈3与所述太阳轮2同轴且与所述太阳轮2之间形成安装空间。所述双联行星轮4设于所述安装空间内。所述双联行星轮4包括同轴且彼此固定连接的第一齿轮41和第二齿轮42。所述第一齿轮41与所述太阳轮2啮合，所述第二齿轮42与所述内齿圈3啮合。所述行星架5包括彼此固定连接的第一连接部51、第二连接部52及第三连接部53。所述第一连接部51设有朝向所述太阳轮2的轴孔531，所述输出轴1的端部102穿过所述太阳轮2后伸入所述轴孔531，所述输出轴1的端部102与所述第一连接部51转动连接，以使所述输出轴1在垂直所述第一中心线101的方向上支撑所述行星架5。所述第二连接部52连接在所述第一连接部51的背向所述太阳轮2的一侧，所述第二连接部52绕所述第一中心线101转动。所述第三连接部53转动连接在所述第二齿轮42的轴心处。所述输出轴1带动所述太阳轮2转动，使得所述第一齿轮41和所述第二齿轮42同步地在所述太阳轮2和所述内齿圈3之间同时自转和公转，所述第二齿轮42带动所述第三连接部53绕所述第一中心线101转动，使得所述第二连接部52转动以驱动所述电动汽车200的车轮201转动。Please refer to FIG. 1 to FIG. 4 together. The embodiment of the present application provides a power transmission system 100 , and the power transmission system 100 can be applied to an electric vehicle 200 . The power transmission system 100 includes a motor 100a and a speed reducer 100b. The motor 100 a includes an output shaft 1 , and the axis of the output shaft 1 is a first central line 101 . The speed reducer 100b includes a sun gear 2 , an inner ring gear 3 , a double planetary gear 4 and a planet carrier 5 . The sun gear 2 is fixedly sleeved on the outer periphery of the output shaft 1 . The ring gear 3 is coaxial with the sun gear 2 and forms an installation space with the sun gear 2 . The duplex planetary gear 4 is arranged in the installation space. The double planetary gear 4 includes a first gear 41 and a second gear 42 that are coaxial and fixedly connected to each other. The first gear 41 meshes with the sun gear 2 , and the second gear 42 meshes with the ring gear 3 . The planet carrier 5 includes a first connecting portion 51 , a second connecting portion 52 and a third connecting portion 53 fixedly connected to each other. The first connecting portion 51 is provided with a shaft hole 531 facing the sun gear 2, the end 102 of the output shaft 1 extends into the shaft hole 531 after passing through the sun gear 2, and the output shaft 1 The end portion 102 of the first connecting portion 51 is rotatably connected, so that the output shaft 1 supports the planetary carrier 5 in a direction perpendicular to the first central line 101 . The second connecting portion 52 is connected to a side of the first connecting portion 51 facing away from the sun gear 2 , and the second connecting portion 52 rotates around the first centerline 101 . The third connecting portion 53 is rotatably connected to the axis of the second gear 42 . The output shaft 1 drives the sun gear 2 to rotate, so that the first gear 41 and the second gear 42 rotate and revolve synchronously between the sun gear 2 and the ring gear 3 , so The second gear 42 drives the third connecting portion 53 to rotate around the first central line 101 , so that the second connecting portion 52 rotates to drive the wheels 201 of the electric vehicle 200 to rotate.
在本申请实施例中，所述“轴心”为“一个物体绕着转动或者可以设想绕着转动的一根直线”。定义平行于所述第一中心线101的方向为轴向，垂直于所述第一中心线101的方向为径向。所述输出轴1绕所述第一中心线101转动。所述输出轴1带动所述太阳轮2绕所述第一中心线101转动，所述太阳轮2的轴心与所述第一中心线101共线。所述内齿圈3的轴心与所述第一中心线101共线，所述内齿圈3不转动。所述第一齿轮41和所述第二齿轮42的轴心为第二中心线401，所述第二中心线401平行于所述第一中心线101。所述第一齿轮41和所述第二齿轮42沿所述第二中心线401排列。所述第一齿轮41和所述第二齿轮42同步地绕所述第一中心线101公转，同时所述第一齿轮41和所述第二齿轮42同步地绕所述第二中心线401自转。由于所述输出轴1的端部102伸入所述第三连接部53的所述轴孔531，所述输出轴1的端部102转动连接所述第三连接部53的所述轴孔531，因此所述输出轴1在轴向上能够相对所述第三连接部53转动，在径向(也即垂直所述第一中心线101的方向)上能够支撑所述第三连接部53。由于所述行星架5的所述第一连接部51、所述第二连接部52及所述第三连接部53彼此固定连接，因此所述输出轴1能够在径向上支撑所述行星架5。由于所述第二连接部52绕所述第一中心线101转动，因此所述行星架5的运动轨迹也是绕所述第一中心线101转动的。所述第二齿轮42绕所述第一中心线101转动时，带动所述第三连接部53绕所述第一中心线101转动，所述第三连接部53的转向和转速分别与所述第二齿轮42的公转转向和公转转速相同。所述第二连接部52与所述第三连接部53同步转动，所述第二连接部52的转向和转速也分别与所述第二齿轮42的公转转向和公转转速相同。所述第二连接部52绕所述第一中心线101转动，使得述第二连接部52能够驱动所述电动汽车200的车轮201转动。由于所述第三连接部53转动连接在所述第二齿轮42的轴心处，因此所述第二齿轮42会因其自转动作而相对所述第三连接部53转动。In the embodiment of the present application, the "axis" is "a straight line around which an object rotates or conceivably rotates". A direction parallel to the first central line 101 is defined as an axial direction, and a direction perpendicular to the first central line 101 is defined as a radial direction. The output shaft 1 rotates around the first centerline 101 . The output shaft 1 drives the sun gear 2 to rotate around the first centerline 101 , and the axis of the sun gear 2 is collinear with the first centerline 101 . The axis of the ring gear 3 is in line with the first centerline 101 , and the ring gear 3 does not rotate. The axes of the first gear 41 and the second gear 42 are the second centerline 401 , and the second centerline 401 is parallel to the first centerline 101 . The first gear 41 and the second gear 42 are arranged along the second central line 401 . The first gear 41 and the second gear 42 revolve synchronously around the first centerline 101 , while the first gear 41 and the second gear 42 synchronously rotate around the second centerline 401 . Since the end 102 of the output shaft 1 extends into the shaft hole 531 of the third connecting portion 53 , the end 102 of the output shaft 1 is rotatably connected to the shaft hole 531 of the third connecting portion 53 , so the output shaft 1 can rotate relative to the third connecting portion 53 in the axial direction, and can support the third connecting portion 53 in the radial direction (that is, the direction perpendicular to the first centerline 101 ). Since the first connection portion 51, the second connection portion 52 and the third connection portion 53 of the planet carrier 5 are fixedly connected to each other, the output shaft 1 can support the planet carrier 5 in the radial direction. . Since the second connecting portion 52 rotates around the first centerline 101 , the motion track of the planet carrier 5 also rotates around the first centerline 101 . When the second gear 42 rotates around the first centerline 101, it drives the third connecting portion 53 to rotate around the first centerline 101, and the steering and rotating speed of the third connecting portion 53 are respectively the same as those of the third connecting portion 53. The revolution direction and revolution speed of the second gear 42 are the same. The second connecting part 52 rotates synchronously with the third connecting part 53 , and the rotation direction and rotation speed of the second connection part 52 are also the same as the revolution rotation speed and revolution speed of the second gear 42 respectively. The second connecting portion 52 rotates around the first central line 101 , so that the second connecting portion 52 can drive the wheels 201 of the electric vehicle 200 to rotate. Since the third connecting portion 53 is rotatably connected to the axis of the second gear 42 , the second gear 42 will rotate relative to the third connecting portion 53 due to its rotation.
本申请实施例所述动力传动系统100的减速比i计算公式为：The formula for calculating the reduction ratio i of the power transmission system 100 in the embodiment of the present application is:
其中，Za为所述太阳轮2的齿数；Zb为所述内齿圈3的齿数；Zc为所述双联行星轮4的所述第一齿轮41的齿数；Zd为所述双联行星轮4的所述第二齿轮42的齿数。由减速比i计算公式可知，本实施例所述动力传动系统100可通过增加Zc/Zd的大小来提升所述动力传动系统100的减速比，也即增大所述第一齿轮41与所述第二齿轮42的齿数比，不需要为了增加减速比而不合理地增加所述内齿圈3的齿数或减少所述太阳轮2的齿数，使得所述减速器100b的径向尺寸满足安装空间限制要求且结构稳定性较佳，所述动力传动系统100的减速比提升难度小。由于所述输出轴1的所述端部102穿过所述太阳轮2后伸入所述轴孔531，因此所述电机100a的所述输出轴1直接伸入所述减速器100b以实现动力传递和结构支撑，使得所述电机100a与所述减速器100b之间的配合更为紧凑，所述动力传动系统100的整体体积更小，从而能够很好地满足电动汽车的安装空间限制要求。所述输出轴1对所述行星架5的径向结构支撑也提高了所述减速器100b的结构稳定性，使得所述动力传动系统100在高速重载的工况下传动平稳、振动噪声小。Wherein, Z a is the number of teeth of the sun gear 2; Z b is the number of teeth of the ring gear 3; Z c is the number of teeth of the first gear 41 of the double planetary gear 4; Z d is the number of teeth of the first gear 41 of the double planetary gear 4; The number of teeth of the second gear 42 of the double planetary gear 4. It can be seen from the formula for calculating the reduction ratio i that the power transmission system 100 in this embodiment can increase the reduction ratio of the power transmission system 100 by increasing the size of Z c /Z d , that is, increasing the first gear 41 and The gear ratio of the second gear 42 does not need to unreasonably increase the number of teeth of the ring gear 3 or reduce the number of teeth of the sun gear 2 in order to increase the reduction ratio, so that the radial dimension of the speed reducer 100b satisfies Due to limited installation space and good structural stability, it is less difficult to increase the reduction ratio of the power transmission system 100 . Since the end 102 of the output shaft 1 passes through the sun gear 2 and then extends into the shaft hole 531, the output shaft 1 of the motor 100a directly extends into the reducer 100b to realize power. Transmission and structural support make the cooperation between the motor 100a and the reducer 100b more compact, and the overall volume of the power transmission system 100 is smaller, so that it can well meet the installation space restriction requirements of electric vehicles. The radial structural support of the output shaft 1 to the planet carrier 5 also improves the structural stability of the reducer 100b, making the power transmission system 100 stable in transmission and low in vibration and noise under high-speed and heavy-load working conditions .
本申请实施例所述动力传动系统100，可用于将电动汽车200的驱动电机动力传送给等速万向节驱动轴总成。本申请实施例所述动力传动系统100也可用于电动汽车200的轮边或轮毂电机的动力总成系统。The power transmission system 100 described in the embodiment of the present application can be used to transmit the driving motor power of the electric vehicle 200 to the constant velocity universal joint drive shaft assembly. The power transmission system 100 described in the embodiment of the present application may also be used in a powertrain system of a wheel or hub motor of the electric vehicle 200 .
可选的，所述输出轴1与所述太阳轮2之间通过花键固定连接，使得所述输出轴1与所述太阳轮2之间的动力传动平稳，所能传递的载荷较大。当然，在其他实施方式中，也可通过键连接或者焊接等方式固定连接所述输出轴1与所述太阳轮2。或者，可一体成型所述输出轴1和所述太阳轮2，形成太阳轮轴。Optionally, the output shaft 1 and the sun gear 2 are fixedly connected by splines, so that the power transmission between the output shaft 1 and the sun gear 2 is stable and the load that can be transmitted is large. Certainly, in other embodiments, the output shaft 1 and the sun gear 2 may also be fixedly connected by means of key connection or welding. Alternatively, the output shaft 1 and the sun gear 2 can be integrally formed to form a sun gear shaft.
可选的，所述第二连接部52内形成内花键。所述第二连接部52可通过花键固定连接等速万向节驱动轴总成，而后通过驱动轴总成驱动电动汽车200的车轮201转动。或者，所述第二连接部52可直接通过转轴连接车轮201，所述第二连接部52转动以带动车轮201转动。在另一种实施方式中，所述第二连接部52可形成法兰盘，从而通过法兰连接至驱动轴总成。Optionally, internal splines are formed in the second connecting portion 52 . The second connecting portion 52 can be fixedly connected to the constant velocity universal joint drive shaft assembly through a spline, and then drive the wheel 201 of the electric vehicle 200 to rotate through the drive shaft assembly. Alternatively, the second connecting portion 52 may be directly connected to the wheel 201 through a rotating shaft, and the second connecting portion 52 rotates to drive the wheel 201 to rotate. In another embodiment, the second connecting portion 52 may form a flange, so as to be connected to the drive shaft assembly through a flange.
可选的，所述双联行星轮4的所述第一齿轮41和所述第二齿轮42一体成型。或者，所述第一齿轮41和所述第二齿轮42是分体的，所述第一齿轮41和所述第二齿轮42通过键连接或者焊接等方式彼此固定连接。Optionally, the first gear 41 and the second gear 42 of the double planetary gear 4 are integrally formed. Alternatively, the first gear 41 and the second gear 42 are separated, and the first gear 41 and the second gear 42 are fixedly connected to each other through key connection or welding.
可选的，所述第三连接部53与所述第二齿轮42之间通过轴承61连接，该轴承61的轴承轴心线与所述第二中心线401共线。该轴承61可同时穿过所述第一齿轮41、所述第二齿轮42及所述第三连接部53，从而更好地将所述双联行星轮4的动力传递至所述行星架5。Optionally, the third connecting portion 53 is connected to the second gear 42 through a bearing 61 , and the bearing axis of the bearing 61 is collinear with the second centerline 401 . The bearing 61 can pass through the first gear 41, the second gear 42 and the third connecting portion 53 at the same time, so as to better transmit the power of the double planetary gear 4 to the planet carrier 5 .
可选的，所述输出轴1的端部102的外周侧与所述轴孔531的内周侧之间通过轴承62连接，该轴承62的轴承轴心线与所述第一中心线101共线，从而使所述第一连接部51与所述输出轴1之间形成轴向上的彼此转动和径向上的彼此支撑。Optionally, the outer peripheral side of the end 102 of the output shaft 1 is connected to the inner peripheral side of the shaft hole 531 through a bearing 62, and the bearing axis of the bearing 62 is the same as the first central line 101. line, so that the first connecting portion 51 and the output shaft 1 form mutual rotation in the axial direction and mutual support in the radial direction.
请一并参阅图1、图2以及图4，作为一种可选实施例，所述减速器100b还包括空转太阳轮7，所述空转太阳轮7转动套设在所述第一连接部51的外周，所述空转太阳轮7与所述第二齿轮42啮合。Please refer to FIG. 1 , FIG. 2 and FIG. 4 together. As an optional embodiment, the reducer 100 b further includes an idler sun gear 7 , and the idler sun gear 7 is rotatably sleeved on the first connecting portion 51 The outer periphery of the idling sun gear 7 meshes with the second gear 42 .
在本实施例中，所述第一连接部51可通过所述空转太阳轮7对所述双联行星轮4进行径向支撑，进一步提高所述减速器100b的结构稳定性，使得所述动力传动系统100在高速重载的工况下，传动平稳，振动噪声小。In this embodiment, the first connecting part 51 can radially support the double planetary gear 4 through the idling sun gear 7, further improving the structural stability of the reducer 100b, so that the power The transmission system 100 has stable transmission and low vibration and noise under high-speed and heavy-load working conditions.
可以理解的是，所述输出轴1在通过所述太阳轮2对所述双联行星轮4的所述第一齿轮41进行径向支撑和动力传输的同时，还依次通过所述第一连接部51和所述空转太阳轮7对所述双联行星轮4的所述第二齿轮42进行径向支撑，并且所述输出轴1对所述行星架5进行了径向支撑，使得所述太阳轮2与所述双联行星轮4之间、所述双联行星轮4与所述行星架5之间的转动动作平稳、可靠，所述动力传动系统100传动平稳、动力输出状态稳定且振动噪声小。It can be understood that, while the output shaft 1 radially supports and transmits power to the first gear 41 of the double planetary gear 4 through the sun gear 2, it also sequentially passes through the first connection part 51 and the idling sun gear 7 radially support the second gear 42 of the double planetary gear 4, and the output shaft 1 radially supports the planet carrier 5, so that the The rotation action between the sun gear 2 and the double planetary gear 4 and between the double planetary gear 4 and the planet carrier 5 is stable and reliable, and the power transmission system 100 has a stable transmission, a stable power output state and Vibration noise is small.
可选的，所述第一连接部51的外周侧与所述空转太阳轮7的内周侧之间通过轴承63连接，该轴承63的轴承轴心线与所述第一中心线101共线，从而使所述第一连接部51与所述空转太阳轮7之间形成轴向上的彼此转动和径向上的彼此支撑。Optionally, the outer peripheral side of the first connecting portion 51 is connected to the inner peripheral side of the idling sun gear 7 through a bearing 63, and the bearing axis of the bearing 63 is collinear with the first centerline 101 , so that the first connecting portion 51 and the idling sun gear 7 form axial mutual rotation and radial mutual support.
可选的，所述空转太阳轮7在轴向上相对所述第一连接部51固定。可在所述第一连接部51的外周侧上形成定位台阶532，所述空转太阳轮7的一侧端面抵接所述定位台阶532，以实现轴向定位。Optionally, the idling sun gear 7 is axially fixed relative to the first connecting portion 51 . A positioning step 532 can be formed on the outer peripheral side of the first connecting portion 51 , and one end surface of the idler sun gear 7 abuts against the positioning step 532 to achieve axial positioning.
请一并参阅图1、图2以及图4，作为一种可选实施例，所述双联行星轮4的数量为多个，多个所述双联行星轮4在所述太阳轮2的周向上均匀排布。此时，多个所述双联行星轮4均匀地转动连接于所述第三连接部53的周向，多个所述双联行星轮4等间距地连接在所述太阳轮2与所述行星架5之间。Please refer to Fig. 1, Fig. 2 and Fig. 4 together. As an optional embodiment, the number of the double planetary gears 4 is multiple, and a plurality of the double planetary gears 4 are on the side of the sun gear 2. Evenly distributed around the circumference. At this time, a plurality of the double planetary gears 4 are uniformly rotated and connected to the circumferential direction of the third connecting portion 53, and a plurality of the double planetary gears 4 are connected at equal intervals between the sun gear 2 and the Between the planet carrier 5.
在本实施例中，所述太阳轮2同时与多个所述双联行星轮4啮合，使得功率被多个所述双联行星轮4均匀分流，而后多个所述双联行星轮4同时带动所述行星架5转动，使得功率最终合流至所述行星架5并通过所述行星架5输出，因此所述减速器100b可实现大功率传动，进一步满足现阶段以及未来电动汽车对动力传动系统100的重载的要求。In this embodiment, the sun gear 2 meshes with multiple double planetary gears 4 at the same time, so that the power is evenly distributed by multiple double planetary gears 4, and then multiple double planetary gears 4 simultaneously Drive the planetary carrier 5 to rotate, so that the power is finally merged to the planetary carrier 5 and output through the planetary carrier 5, so the reducer 100b can realize high-power transmission, and further meet the needs of electric vehicles at this stage and in the future. System 100's heavy load requirements.
可以理解的，多个所述双联行星轮4等间距地连接在所述太阳轮2与所述行星架5之间，能够提高所述减速器100b传动的稳定性和承载能力，使得所述动力传动系统100传动平稳、可靠。It can be understood that a plurality of double planetary gears 4 are equidistantly connected between the sun gear 2 and the planetary carrier 5, which can improve the stability and carrying capacity of the transmission of the reducer 100b, so that the The transmission of the power transmission system 100 is stable and reliable.
请一并参阅图1和图2，作为一种可选实施例，所述第一齿轮41的齿数多于所述第二齿轮42的齿数。所述第一齿轮41的模数与所述第二齿轮42的模数相同，则所述第一齿轮41的分度圆直径大于所述第二齿轮42的分度圆直径。Please refer to FIG. 1 and FIG. 2 together. As an optional embodiment, the number of teeth of the first gear 41 is greater than the number of teeth of the second gear 42 . The modulus of the first gear 41 is the same as that of the second gear 42 , so the pitch circle diameter of the first gear 41 is larger than the pitch circle diameter of the second gear 42 .
在本实施例中，由于所述第一齿轮41的齿数多于所述第二齿轮42的齿数，因此Zc/Zd＞1，所述动力传动系统100的减速器100b的减速比i比现有技术的减速器的减速比范围大。本申请实施例所述动力传动系统100的减速比i的范围可以达到6～15左右，所述输出轴1的转速可达到20000r/min以上，满足现阶段以及未来电动汽车对动力传动系统的大减速比及高速的要求。In this embodiment, since the number of teeth of the first gear 41 is greater than the number of teeth of the second gear 42, Z c /Z d >1, and the reduction ratio i of the speed reducer 100b of the power transmission system 100 is The speed reducer of the prior art has a wide range of reduction ratios. The range of the reduction ratio i of the power transmission system 100 in the embodiment of the present application can reach about 6-15, and the speed of the output shaft 1 can reach more than 20,000 r/min, which meets the requirements of the current and future electric vehicles on the power transmission system. Reduction ratio and high speed requirements.
请一并参阅图1、图2以及图4，作为一种可选实施例，所述电机100a还包括电机壳体8，所述减速器100b还包括减速器壳体9，所述电机壳体8和所述减速器壳体9分别连接于所述内齿圈3的相对两侧，以共同围设出减速腔10。Please refer to Fig. 1, Fig. 2 and Fig. 4 together, as an optional embodiment, the motor 100a also includes a motor housing 8, and the speed reducer 100b also includes a speed reducer housing 9, and the motor The casing 8 and the reducer casing 9 are respectively connected to opposite sides of the ring gear 3 to jointly define a reduction cavity 10 .
所述减速器壳体9与所述内齿圈3的一侧端面可通过紧固件固定连接。所述电机壳体8与所述内齿圈3的另一侧端面可通过紧固件固定连接。所述减速器壳体9与所述内齿圈3的连接方式和所述电机壳体8与所述内齿圈3的连接方式相同，有利于方便所述动力传动系统100的安装、拆卸与互换。当然，在其他实施方式中，所述减速器壳体9与所述内齿圈3的连接方式和所述电机壳体8与所述内齿圈3的连接方式也可以不同。The reducer housing 9 can be fixedly connected to one side end surface of the ring gear 3 by a fastener. The motor housing 8 and the other end surface of the ring gear 3 can be fixedly connected by fasteners. The connection mode between the reducer housing 9 and the ring gear 3 is the same as the connection mode between the motor housing 8 and the ring gear 3 , which facilitates the installation and disassembly of the power transmission system 100 with interchangeable. Certainly, in other embodiments, the connection manner between the reducer housing 9 and the ring gear 3 and the connection manner between the motor housing 8 and the ring gear 3 may also be different.
所述紧固件包括但不限于螺栓、螺钉等。当然，在其他实施方式中，所述减速器壳体9与所述内齿圈3的一侧端面也可通过键连接或者焊接等方式固定连接。所述电机壳体8与所述内齿圈3的另一侧端面也可通过键连接或者焊接等方式固定连接。The fasteners include but are not limited to bolts, screws and the like. Certainly, in other implementation manners, the reducer housing 9 and one side end surface of the ring gear 3 may also be fixedly connected by means of key connection or welding. The motor housing 8 and the other end surface of the ring gear 3 can also be fixedly connected by means of key connection or welding.
所述电机壳体8设有第一通孔81，所述输出轴1自所述第一通孔81伸入所述减速腔10且转动连接所述电机壳体8。所述输出轴1的外周侧与所述第一通孔81的孔壁之间设置轴承64，该轴承64的轴承轴心线与所述第一中心线101共线，从而使所述输出轴1得以在轴向上相对所述第一通孔81转动，且在径向上被所述第一通孔81支撑。The motor housing 8 is provided with a first through hole 81 , and the output shaft 1 extends into the deceleration chamber 10 through the first through hole 81 and is rotatably connected to the motor housing 8 . A bearing 64 is arranged between the outer peripheral side of the output shaft 1 and the hole wall of the first through hole 81, and the bearing axis line of the bearing 64 is collinear with the first center line 101, so that the output shaft 1 can rotate relative to the first through hole 81 in the axial direction, and is supported by the first through hole 81 in the radial direction.
所述减速器壳体9设有第二通孔91，所述行星架5收容于所述减速腔10，所述第二连接部52自所述第二通孔91伸出所述减速腔10且转动连接所述减速器壳体9。所述第二连接部52的外周侧与所述第二通孔91的孔壁之间设置轴承65，该轴承65的轴承轴心线与所述第一中心线101共线，从而使所述第二连接部52得以在轴向上相对所述第二通孔91转动，且在径向上被所述第二通孔91支撑。The reducer housing 9 is provided with a second through hole 91, the planet carrier 5 is accommodated in the deceleration chamber 10, and the second connecting portion 52 extends out of the deceleration chamber 10 from the second through hole 91 And the reducer housing 9 is rotatably connected. A bearing 65 is arranged between the outer peripheral side of the second connecting portion 52 and the hole wall of the second through hole 91, and the bearing axis of the bearing 65 is collinear with the first centerline 101, so that the The second connecting portion 52 can rotate relative to the second through hole 91 in the axial direction, and is supported by the second through hole 91 in the radial direction.
此时，所述太阳轮2、所述空转太阳轮7及所述双联行星轮4也收容于所述减速腔10。At this time, the sun gear 2 , the idling sun gear 7 and the double planetary gear 4 are also accommodated in the reduction chamber 10 .
可选的，所述动力传动系统100还包括第一密封件111和第二密封件112，所述第一密封件111密封于所述第一通孔81的孔壁与所述输出轴1之间，所述第二密封件112密封于所述第二通孔91的孔壁与所述第二连接部52之间。Optionally, the power transmission system 100 further includes a first seal 111 and a second seal 112, the first seal 111 is sealed between the hole wall of the first through hole 81 and the output shaft 1 Between, the second sealing member 112 is sealed between the hole wall of the second through hole 91 and the second connecting portion 52 .
可选的，所述动力传动系统100设有连通所述减速腔10的进油孔121和出油孔122，所述进油孔121设于所述电机壳体8或所述减速器壳体9，所述出油孔122设于所述电机壳体8或所述减速器壳体9。所述动力传动系统100采用喷油泵方式实现润滑和冷却功能，使得设于所述减速腔10内的部件(包括部分所述输出轴1、所述太阳轮2、所述空转太阳轮7、所述双联行星轮4及部分所述行星架5)润滑和冷却充分，有利于保障所述动力传动系统100的工作可靠性，提高了所述动力传动系统100的使用寿命。Optionally, the power transmission system 100 is provided with an oil inlet hole 121 and an oil outlet hole 122 communicating with the reduction chamber 10, and the oil inlet hole 121 is arranged on the motor housing 8 or the reducer housing Body 9 , the oil outlet hole 122 is provided in the motor housing 8 or the reducer housing 9 . The power transmission system 100 adopts an oil injection pump to realize lubrication and cooling functions, so that the components (including part of the output shaft 1, the sun gear 2, the idling sun gear 7, the The duplex planetary gear 4 and part of the planet carrier 5) are sufficiently lubricated and cooled, which is conducive to ensuring the reliability of the power transmission system 100 and improving the service life of the power transmission system 100.
请一并参阅图1、图2、图4以及图5，作为一种可选实施例，所述电机100a还包括定子安装架13、定子14及转子15。所述定子安装架13连接于所述电机壳体8远离所述内齿圈3的一侧，以共同围设出电机腔16。所述定子安装架13与所述电机壳体8之间可通过紧固件连接、键连接或者焊接等方式固定连接。所述定子14收容于所述电机腔16且相对所述定子安装架13固定。所述转子15套设在所述定子14内部，所述转子15的轴心处形成所述输出轴1。Please refer to FIG. 1 , FIG. 2 , FIG. 4 and FIG. 5 together. As an optional embodiment, the motor 100 a further includes a stator mounting frame 13 , a stator 14 and a rotor 15 . The stator mounting frame 13 is connected to a side of the motor housing 8 away from the ring gear 3 to jointly define a motor cavity 16 . The stator mounting frame 13 and the motor housing 8 can be fixedly connected by fasteners, keys or welding. The stator 14 is accommodated in the motor chamber 16 and fixed relative to the stator mounting frame 13 . The rotor 15 is sleeved inside the stator 14 , and the output shaft 1 is formed at the center of the rotor 15 .
在本实施例中，可将所述减速器壳体9、所述行星架5、所述空转太阳轮7、所述内齿圈3及所述双联行星轮4组装成第一模块1001，将所述电机壳体8、所述太阳轮2及所述转子15组装成第二模块1002，将所述定子安装架13、所述定子14组装成的第三模块1003。所述第一模块1001、所述第二模块1002及所述第三模块1003的组成明确，单独组装工序简易。同时，所述第一模块1001、所述第二模块1002及所述第三模块1003的模块端面接口可设置成一致接口(例如紧固件连接、焊接或键连接)，从而方便模块之间的拆装与互换。故而，所述动力传动系统100具有高度的模块化和集成化，能够降低所述动力传动系统100在整车中的空间占有率、拆装和维护成本。In this embodiment, the reducer housing 9, the planet carrier 5, the idling sun gear 7, the ring gear 3 and the double planetary gear 4 can be assembled into a first module 1001, The motor housing 8 , the sun gear 2 and the rotor 15 are assembled into a second module 1002 , and the stator mounting frame 13 and the stator 14 are assembled into a third module 1003 . The composition of the first module 1001 , the second module 1002 and the third module 1003 is clear, and the individual assembly process is simple. At the same time, the module end interfaces of the first module 1001, the second module 1002, and the third module 1003 can be set to a consistent interface (such as fastener connection, welding or key connection), so as to facilitate the connection between modules Disassembly and exchange. Therefore, the power transmission system 100 has a high degree of modularization and integration, which can reduce the space occupancy, disassembly and maintenance costs of the power transmission system 100 in the vehicle.
可选的，所述定子安装架13的端壁131设有支撑槽132，所述转子15的轴心处形成背向所述输出轴1的支撑轴151，所述支撑轴151转动连接所述支撑槽132。也即所述转子15相对的两端分别形成所述输出轴1和所述支撑轴151。所述电机壳体8形成一安装口，所述定子安装架13自所述安装口安装至所述电机壳体8，所述定子安装架13的所述端壁131封闭所述安装口。Optionally, the end wall 131 of the stator mounting frame 13 is provided with a support groove 132, and the center of the rotor 15 forms a support shaft 151 facing away from the output shaft 1, and the support shaft 151 is rotatably connected to the Support groove 132 . That is, the opposite ends of the rotor 15 respectively form the output shaft 1 and the support shaft 151 . The motor housing 8 forms a mounting opening, the stator mounting frame 13 is installed to the motor housing 8 from the mounting port, and the end wall 131 of the stator mounting frame 13 closes the mounting port .
所述支撑轴151的外周侧与所述支撑槽132的内周侧之间通过轴承66连接，该轴承66的轴承轴心线与所述第一中心线101共线，从而使所述支撑轴151得以在轴向上相对所述支撑槽132转动，且在径向上被所述支撑槽132支撑。The outer peripheral side of the support shaft 151 and the inner peripheral side of the support groove 132 are connected by a bearing 66, the bearing axis of the bearing 66 is collinear with the first center line 101, so that the support shaft 151 can rotate relative to the support slot 132 in the axial direction, and is supported by the support slot 132 in the radial direction.
请一并参阅图1和图5，作为一种可选实施例，所述定子安装架13还包括自所述端壁131向所述电机腔16延伸的支撑壁132，所述支撑壁132的外周侧与所述电机壳体8的内周侧之间过盈配合连接且形成液冷通道17。所述液冷通道17可为螺旋式通道。Please refer to FIG. 1 and FIG. 5 together. As an optional embodiment, the stator installation frame 13 further includes a support wall 132 extending from the end wall 131 to the motor chamber 16, and the support wall 132 The outer peripheral side is connected with an interference fit with the inner peripheral side of the motor housing 8 and forms a liquid cooling channel 17 . The liquid cooling channel 17 can be a spiral channel.
在本实施例中，通过所述液冷通道17可对所述电机腔16内的部件(包括所述支撑壁132、所述定子14及所述转子15)进行冷却，有利于保障所述动力传动系统100的工作可靠性，提高了所述动力传动系统100的使用寿命。In this embodiment, the components in the motor chamber 16 (including the support wall 132, the stator 14 and the rotor 15) can be cooled through the liquid cooling channel 17, which is beneficial to ensure the power The working reliability of the transmission system 100 improves the service life of the power transmission system 100 .
可选的，所述定子14固定于所述支撑壁132的内周侧。所述定子14可与所述支撑壁132的内周侧通过过盈配合固定连接。Optionally, the stator 14 is fixed on the inner peripheral side of the support wall 132 . The stator 14 can be fixedly connected to the inner peripheral side of the support wall 132 through interference fit.
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| CN116488396A (en) * | 2023-05-29 | 2023-07-25 | 湖北万润新能源科技股份有限公司 | Planetary reduction electric drive |
| CN116494743A (en) * | 2023-06-12 | 2023-07-28 | 中国重汽集团济南动力有限公司 | Electric drive axle system and automobile |
| CN116494743B (en) * | 2023-06-12 | 2024-04-16 | 中国重汽集团济南动力有限公司 | Electric drive axle system and car |
| CN117128291A (en) * | 2023-09-18 | 2023-11-28 | 上汽通用汽车有限公司 | Speed change device and vehicle |
| WO2026158037A1 (en) * | 2025-01-27 | 2026-07-30 | 华为技术有限公司 | Powertrain comprising two-stage planetary coaxial reducer and electric vehicle |
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Application publication date: 20180907 |
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