具体实施方式

下面结合附图对本发明作进一步详细的说明。

第一实施例：

参考图1，一种行星式多级传动变速机构，包括输入轴IN、输出轴OUT、第一行星排P1、第二行星排P2与第三行星排P3；

输入轴IN与第一行星排P1连接；输出轴OUT与第二行星排P2连接；

第一行星排P1包括第一太阳轮S1、第一行星架PC1、第一行星轮CA1与第一齿圈R1；第一行星轮CA1活动安装在第一行星架PC1上，第一齿圈R1与第一行星轮CA1相啮合，第一行星轮CA1与第一太阳轮S1相啮合；

第二行星排P2包括第二太阳轮S2、第二行星架PC2、第二行星轮CA2与第二齿圈R2；第二行星轮CA2活动安装在第二行星架PC2上，第二齿圈R2与第二行星轮CA2相啮合，第二行星轮CA2与第二太阳轮S2相啮合；

第三行星排P3包括第三太阳轮S3、第三行星架PC3、第三行星轮CA3与第三齿圈R3；第三行星轮CA3活动安装在第三行星架PC3上，第三齿圈R3与第三行星轮CA3相啮合，第三行星轮CA3与第三太阳轮S3相啮合；

第三太阳轮S3活动的安装在行星架连接轴L3上；第一行星架PC1与第二行星架PC2之间通过行星架连接轴L3固定连接。

输入轴IN与第一太阳轮S1固定连接，第一齿圈R1通过第一连接件L1与第三太阳轮S3固定连接，第三齿圈R3通过第二连接件L2与第二齿圈R2固定连接，输出轴OUT与第二太阳轮S2固定连接；

第一齿圈R1与第一制动器B1连接，即第一制动器B1可对第一齿圈R1进行制动；第二齿圈R2与第二制动器B2连接，即第二制动器B2可对第二齿圈R2进行制动；第二行星架PC2与行星架制动器BL3连接，即行星架制动器BL3可对第二行星架PC2进行制动；第三行星架PC3与第三制动器B3连接，即第三制动器B3可对第三行星架PC3进行制动。

其中，活动安装可理解为转动连接；固定连接可理解为联动连接。

工作原理：齿圈连接太阳轮、齿圈连接齿圈，RS-RR型。

第一制动器B1与第二制动器B2同时接合，分别将第一齿圈R1和第二齿圈R2固定，第一太阳轮S1与输入轴I N固定连接，以相同的方向和转速转动；在第一行星排P1中，第一太阳轮S1输入动力，第一齿圈R1固定，第一行星架PC1与输入轴I N同向转动；在第二行星排P2中，第二行星架PC2通过行星架连接轴L3与第一行星架PC1固定连接，第二行星架PC2输入动力，第二齿圈R2固定，第二太阳轮S2与输出轴OUT固定连接，第二太阳轮S2输出动力至输出轴OUT，输出轴OUT与输入轴I N转动方向相同；动力依次通过第一行星排P1、行星架连接轴L3和第二行星排P2，实现二级传动，输出动力转动方向与输入动力转动方向相同。

第三制动器B3与行星架制动器BL3同时接合，分别将第一行星架PC1、第二行星架PC2、第三行星架PC3固定，第一太阳轮S1与输入轴IN固定连接，以相同的方向和转速转动；在第一行星排P1中，第一太阳轮S1输入动力，第一行星架PC1固定，第一齿圈R1与输入轴IN反向转动；第一齿圈R1与第三太阳轮S3通过第一连接件L1固定连接，在第三行星排P3中，第三太阳轮S3输入动力，第三行星架PC3固定，第三齿圈R3与输入轴IN同向转动；第三齿圈R3与第二齿圈R2通过第二连接件L2固定连接，在第二行星排P2中，第二齿圈R2输入动力，第二行星架PC2固定，第二太阳轮S2与输入轴I N反向转动，第二太阳轮S2与输出轴OUT固定连接，第二太阳轮S2输出动力至输出轴OUT，输出轴OUT与输入轴IN转动方向相反；动力依次通过第一行星排P1、第一连接件L1、第三行星排P3、第二连接件L2和第二行星排P2，实现三级传动，输出动力转动方向与输入动力转动方向相反。

第三制动器B3单独接合，将第三行星架PC3固定，第一行星排P1、第二行星排P2和第三行星排P3组合成一个具有两自由度的行星排组，动力分流为二级传动和三级传动，实现混合传动；第一太阳轮S1与输入轴I N固定连接，以相同的方向和转速转动；在第一行星排P1中，第一太阳轮S1输入动力，动力分流为两路传动，第一路通过第一行星架PC1以二级传动的方式传动，第二路通过第一齿圈R1以三级传动的方式传动；第一路传动，在第一行星排P1中，第一太阳轮S1将动力输出到第一行星架PC1，第一行星架PC1将动力输出到行星架连接轴L3，在第二行星排P2中，行星架连接轴L3将动力输出到第二行星架PC2，第二行星架PC2动力再次分流后分别输出到第二齿圈R2和第二太阳轮S2；第二路传动，在第一行星排P1中，第一太阳轮S1通过第一行星轮CA1将动力输出到第一齿圈R1，第一齿圈R1将动力输出到第一连接件L1，在第三行星排P3中，第一连接件L1将动力输出到第三太阳轮S3，第三太阳轮S3通过第三行星轮CA3将动力输出到第三齿圈R3，第三齿圈R3将动力输出到第二连接件L2，在第二行星排P2中，第二连接件L2将动力输出到第二齿圈R2，第二齿圈R2动力再次分流后分别输出到第二行星架PC2和第二太阳轮S2；具有两自由度的行星排组，实现二级传动并联三级传动的混合传动，动作一个操纵件，消除另一个自由度，可实现固定输入与输出。

第二实施例：

参考图2，一种行星式多级传动变速机构，包括输入轴IN、输出轴OUT、第一行星排P1、第二行星排P2与第三行星排P3；

输入轴IN与第一行星排P1连接；输出轴OUT与第二行星排P2连接；

第一行星排P1包括第一太阳轮S1、第一行星架PC1、第一行星轮CA1与第一齿圈R1；第一行星轮CA1活动安装在第一行星架PC1上，第一齿圈R1与第一行星轮CA1相啮合，第一行星轮CA1与第一太阳轮S1相啮合；

第二行星排P2包括第二太阳轮S2、第二行星架PC2、第二行星轮CA2与第二齿圈R2；第二行星轮CA2活动安装在第二行星架PC2上，第二齿圈R2与第二行星轮CA2相啮合，第二行星轮CA2与第二太阳轮S2相啮合；

第三行星排P3包括第三太阳轮S3、第三行星架PC3、第三行星轮CA3与第三齿圈R3；第三行星轮CA3活动安装在第三行星架PC3上，第三齿圈R3与第三行星轮CA3相啮合，第三行星轮CA3与第三太阳轮S3相啮合；

第二太阳轮S2与第三太阳轮S3均活动的安装在行星架连接轴L3上；第一行星架PC1与第二行星架PC2之间通过行星架连接轴L3固定连接；

输入轴IN与第一太阳轮S1固定连接，第一齿圈R1通过第一连接件L1与第三齿圈R3固定连接，第三太阳轮S3通过第二连接件L2与第二太阳轮S2固定连接，输出轴OUT与第二齿圈R2固定连接；

第一齿圈R1与第一制动器B1连接，即第一制动器B1可对第一齿圈R1进行制动；第二太阳轮S2与第二制动器B2连接，即第二制动器B2可对第二太阳轮S2进行制动；第二行星架PC2与行星架制动器BL3连接，即行星架制动器BL3可对第二行星架PC2进行制动；第三行星架PC3与第三制动器B3连接，即第三制动器B3可对第三行星架PC3进行制动。

工作原理：齿圈连接齿圈、太阳轮连接太阳轮，RR-SS型。

第一制动器B1与第二制动器B2同时接合，分别将第一齿圈R1和第二太阳轮S2固定，第一太阳轮S1与输入轴IN固定连接，以相同的方向和转速转动；在第一行星排P1中，第一太阳轮S1输入动力，第一齿圈R1固定，第一行星架PC1与输入轴IN同向转动；在第二行星排P2中，第二行星架PC2通过行星架连接轴L3与第一行星架PC1固定连接，第二行星架PC2输入动力，第二太阳轮S2固定，第二齿圈R2与输出轴OUT固定连接，第二齿圈R2输出动力至输出轴OUT，输出轴OUT与输入轴IN转动方向相同；动力依次通过第一行星排P1、行星架连接轴L3和第二行星排P2，实现二级传动，输出动力转动方向与输入动力转动方向相同。

第三制动器B3与行星架制动器BL3同时接合，分别将第一行星架PC1、第二行星架PC2、第三行星架PC3固定，第一太阳轮S1与输入轴IN固定连接，以相同的方向和转速转动；在第一行星排P1中，第一太阳轮S1输入动力，第一行星架PC1固定，第一齿圈R1与输入轴IN反向转动；第一齿圈R1与第三齿圈R3通过第一连接件L1固定连接，在第三行星排P3中，第三齿圈R3输入动力，第三行星架PC3固定，第三太阳轮S3与输入轴IN同向转动；第三太阳轮S3与第二太阳轮S2通过第二连接件L2固定连接，在第二行星排P2中，第二太阳轮S2输入动力，第二行星架PC2固定，第二齿圈R2与输入轴IN反向转动，第二齿圈R2与输出轴OUT固定连接，第二齿圈R2输出动力至输出轴OUT，输出轴OUT与输入轴IN转动方向相反；动力依次通过第一行星排P1、第一连接件L1、第三行星排P3、第二连接件L2和第二行星排P2，实现三级传动，输出动力转动方向与输入动力转动方向相反。

第三制动器B3单独接合，将第三行星架PC3固定，第一行星排P1、第二行星排P2和第三行星排P3组合成一个具有两自由度的行星排组，实现二级传动并联三级传动的混合传动；第一太阳轮S1与输入轴IN固定连接，以相同的方向和转速转动；在第一行星排P1中，第一太阳轮S1输入动力，动力分流为两路传动，第一路通过第一行星架PC1以二级传动的方式传动，第二路通过第一齿圈R1以三级传动的方式传动；第一路传动，在第一行星排P1中，第一太阳轮S1将动力输出到第一行星架PC1，第一行星架PC1将动力输出到行星架连接轴L3，在第二行星排P2中，行星架连接轴L3将动力输出到第二行星架PC2，第二行星架PC2动力再次分流后分别输出到第二齿圈R2和第二太阳轮S2；第二路传动，在第一行星排P1中，第一太阳轮S1通过第一行星轮CA1将动力输出到第一齿圈R1，第一齿圈R1将动力输出到第一连接件L1，在第三行星排P3中，第一连接件L1将动力输出到第三齿圈R3，第三齿圈R3通过第三行星轮CA3将动力输出到第三太阳轮S3，第三太阳轮S3将动力输出到第二连接件L2，在第二行星排P2中，第二连接件L2将动力输出到第二太阳轮S2，第二太阳轮S2将动力再次分流后分别输出到第二行星架PC2和第二齿圈R2；具有两自由度的行星排组，实现二级传动并联三级传动的混合传动，动作一个操纵件，消除另一个自由度，可实现固定输入与输出。

第三实施例：

参考图3，一种行星式多级传动变速机构，包括输入轴IN、输出轴OUT、第一行星排P1、第二行星排P2与第三行星排P3；

输入轴IN与第一行星排P1连接；输出轴OUT与第二行星排P2连接；

第一行星排P1包括第一太阳轮S1、第一行星架PC1、第一行星轮CA1与第一齿圈R1；第一行星轮CA1活动安装在第一行星架PC1上，第一齿圈R1与第一行星轮CA1相啮合，第一行星轮CA1与第一太阳轮S1相啮合；

第二行星排P2包括第二太阳轮S2、第二行星架PC2、第二行星轮CA2与第二齿圈R2；第二行星轮CA2活动安装在第二行星架PC2上，第二齿圈R2与第二行星轮CA2相啮合，第二行星轮CA2与第二太阳轮S2相啮合；

第三行星排P3包括第三太阳轮S3、第三行星架PC3、第三行星轮CA3与第三齿圈R3；第三行星轮CA3活动安装在第三行星架PC3上，第三齿圈R3与第三行星轮CA3相啮合，第三行星轮CA3与第三太阳轮S3相啮合；

第二太阳轮S2与第三太阳轮S3均活动安装在行星架连接轴L3上；第一行星架PC1与第二行星架PC2之间通过行星架连接轴L3固定连接；

输入轴IN与第一太阳轮S1固定连接，第一齿圈R1通过第一连接件L1与第三太阳轮S3固定连接，第三齿圈R3通过第二连接件L2与第二太阳轮S2固定连接，输出轴OUT与第二齿圈R2固定连接；

第一齿圈R1与第一制动器B1连接，即第一制动器B1可对第一齿圈R1制动；第二太阳轮S2与第二制动器B2连接，即第二制动器B2可对第二太阳轮S2进行制动；第二行星架PC2与行星架制动器BL3连接，即行星架制动器BL3可对第二行星架PC2进行制动；第三行星架PC3与第三制动器B3连接，即第三制动器B3可对第三行星架PC3进行制动。

工作原理：齿圈连接太阳轮、齿圈连接太阳轮，RS-RS型。

第一制动器B1与第二制动器B2同时接合，分别将第一齿圈R1和第二太阳轮S2固定，第一太阳轮S1与输入轴IN固定连接，以相同的方向和转速转动；在第一行星排P1中，第一太阳轮S1输入动力，第一齿圈R1固定，第一行星架PC1与输入轴IN同向转动；在第二行星排P2中，第二行星架PC2通过行星架连接轴L3与第一行星架PC1固定连接，第二行星架PC2输入动力，第二太阳轮S2固定，第二齿圈R2与输出轴OUT固定连接，第二齿圈R2输出动力至输出轴OUT，输出轴OUT与输入轴IN转动方向相同；动力依次通过第一行星排P1、行星架连接轴L3和第二行星排P2，实现二级传动，输出动力转动方向与输入动力转动方向相同。

第三制动器B3与行星架制动器BL3同时接合，分别将第一行星架PC1、第二行星架PC2、第三行星架PC3固定，第一太阳轮S1与输入轴IN固定连接，以相同的方向和转速转动；在第一行星排P1中，第一太阳轮S1输入动力，第一行星架PC1固定，第一齿圈R1与输入轴IN反向转动；第一齿圈R1与第三太阳轮S3通过第一连接件L1固定连接，在第三行星排P3中，第三太阳轮S3输入动力，第三行星架PC3固定，第三齿圈R3与输入轴IN同向转动；第三齿圈R3与第二太阳轮S2通过第二连接件L2固定连接，在第二行星排P2中，第二太阳轮S2输入动力，第二行星架PC2固定，第二齿圈R2与输入轴I N反向转动，第二齿圈R2与输出轴OUT固定连接，第二齿圈R2输出动力至输出轴OUT，输出轴OUT与输入轴I N转动方向相反；动力依次通过第一行星排P1、第一连接件L1、第三行星排P3、第二连接件L2和第二行星排P2，实现三级传动，输出动力转动方向与输入动力转动方向相反。

第三制动器B3单独接合，将第三行星架PC3固定，第一行星排P1、第二行星排P2和第三行星排P3组合成一个具有两自由度的行星排组，实现二级传动并联三级传动的混合传动；第一太阳轮S1与输入轴IN固定连接，以相同的方向和转速转动；在第一行星排P1中，第一太阳轮S1输入动力，动力分流为两路传动，第一路通过第一行星架PC1以二级传动的方式传动，第二路通过第一齿圈R1以三级传动的方式传动；第一路传动，在第一行星排P1中，第一太阳轮S1将动力输出到第一行星架PC1，第一行星架PC1将动力输出到行星架连接轴L3，在第二行星排P2中，行星架连接轴L3将动力输出到第二行星架PC2，第二行星架PC2动力再次分流后分别输出到第二齿圈R2和第二太阳轮S2；第二路传动，在第一行星排P1中，第一太阳轮S1通过第一行星轮CA1将动力输出到第一齿圈R1，第一齿圈R1将动力输出到第一连接件L1，在第三行星排P3中，第一连接件L1将动力输出到第三太阳轮S3，第三太阳轮S3通过第三行星轮CA3将动力输出到第三齿圈R3，第三齿圈R3将动力输出到第二连接件L2，在第二行星排P2中，第二连接件L2将动力输出到第二太阳轮S2，第二太阳轮S2将动力再次分流后分别输出到第二行星架PC2和第二齿圈R2；具有两自由度的行星排组，实现二级传动并联三级传动的混合传动，动作一个操纵件，消除另一个自由度，可实现固定输入与输出。

第四实施例：

参考图4，一种行星式多级传动变速机构，包括输入轴IN、输出轴OUT、第一行星排P1、第二行星排P2与第三行星排P3；

输入轴IN与第一行星排P1连接；输出轴OUT与第二行星排P2连接；

第一行星排P1包括第一太阳轮S1、第一行星架PC1、第一行星轮CA1与第一齿圈R1；第一行星轮CA1活动安装在第一行星架PC1上，第一齿圈R1与第一行星轮CA1相啮合，第一行星轮CA1与第一太阳轮S1相啮合；

第二行星排P2包括第二太阳轮S2、第二行星架PC2、第二行星轮CA2与第二齿圈R2；第二行星轮CA2活动安装在第二行星架PC2上，第二齿圈R2与第二行星轮CA2相啮合，第二行星轮CA2与第二太阳轮S2相啮合；

第三行星排P3包括第三太阳轮S3、第三行星架PC3、第三行星轮CA3与第三齿圈R3；第三行星轮CA3活动安装在第三行星架PC3上，第三齿圈R3与第三行星轮CA3相啮合，第三行星轮CA3与第三太阳轮S3相啮合；

第一太阳轮S1、第二太阳轮S2与第三太阳轮S3均活动安装在行星架连接轴L3上；第一行星架PC1与第二行星架PC2之间通过行星架连接轴L3固定连接；

输入轴IN与第一齿圈R1固定连接，第一太阳轮S1通过第一连接件L1与第三太阳轮S3固定连接，第三齿圈R3通过第二连接件L2与第二太阳轮S2固定连接，输出轴OUT与第二齿圈R2固定连接；

第一太阳轮S1与第一制动器B1连接，即第一制动器B1可对第一太阳轮S1进行制动；第二太阳轮S2与第二制动器B2连接，即第二制动器B2可对第二太阳轮S2进行制动；第二行星架PC2与行星架制动器BL3连接，即行星架制动器BL3可对第二行星架PC2进行制动；第三行星架PC3与第三制动器B3连接，即第三制动器B3可对第三行星架PC3进行制动。

工作原理：太阳轮连接太阳轮、齿圈连接太阳轮，SS-RS型。

第一制动器B1与第二制动器B2同时接合，分别将第一太阳轮S1和第二太阳轮S2固定，第一齿圈R1与输入轴IN固定连接，以相同的方向和转速转动；在第一行星排P1中，第一齿圈R1输入动力，第一太阳轮S1固定，第一行星架PC1与输入轴IN同向转动；在第二行星排P2中，第二行星架PC2通过行星架连接轴L3与第一行星架PC1固定连接，第二行星架PC2输入动力，第二太阳轮S2固定，第二齿圈R2与输出轴OUT固定连接，第二齿圈R2输出动力至输出轴OUT，输出轴OUT与输入轴IN转动方向相同；动力依次通过第一行星排P1、行星架连接轴L3和第二行星排P2，实现二级传动，输出动力转动方向与输入动力转动方向相同。

第三制动器B3与行星架制动器BL3同时接合，分别将第一行星架PC1、第二行星架PC2、第三行星架PC3固定，第一齿圈R1与输入轴IN固定连接，以相同的方向和转速转动；在第一行星排P1中，第一齿圈R1输入动力，第一行星架PC1固定，第一太阳轮S1与输入轴I N反向转动；第一太阳轮S1与第三太阳轮S3通过第一连接件L1固定连接，在第三行星排P3中，第三太阳轮S3输入动力，第三行星架PC3固定，第三齿圈R3与输入轴IN同向转动；第三齿圈R3与第二太阳轮S2通过第二连接件L2固定连接，在第二行星排P2中，第二太阳轮S2输入动力，第二行星架PC2固定，第二齿圈R2与输入轴I N反向转动，第二齿圈R2与输出轴OUT固定连接，第二齿圈R2输出动力至输出轴OUT，输出轴OUT与输入轴I N转动方向相反；动力依次通过第一行星排P1、第一连接件L1、第三行星排P3、第二连接件L2和第二行星排P2，实现三级传动，输出动力转动方向与输入动力转动方向相反。

第三制动器B3单独接合，将第三行星架PC3固定，第一行星排P1、第二行星排P2和第三行星排P3组合成一个具有两自由度的行星排组，实现二级传动并联三级传动的混合传动；第一齿圈R1与输入轴IN固定连接，以相同的方向和转速转动；在第一行星排P1中，第一齿圈R1输入动力，动力分流为两路传动，第一路通过第一行星架PC1以二级传动的方式传动，第二路通过第一太阳轮S1以三级传动的方式传动；第一路传动，在第一行星排P1中，第一齿圈R1将动力输出到第一行星架PC1，第一行星架PC1将动力输出到行星架连接轴L3，在第二行星排P2中，行星架连接轴L3将动力输出到第二行星架PC2，第二行星架PC2动力再次分流后分别输出到第二齿圈R2和第二太阳轮S2；第二路传动，在第一行星排P1中，第一齿圈R1通过第一行星轮CA1将动力输出到第一太阳轮S1，第一太阳轮S1将动力输出到第一连接件L1，在第三行星排P3中，第一连接件L1将动力输出到第三太阳轮S3，第三太阳轮S3通过第三行星轮CA3将动力输出到第三齿圈R3，第三齿圈R3将动力输出到第二连接件L2，在第二行星排P2中，第二连接件L2将动力输出到第二太阳轮S2，第二太阳轮S2将动力再次分流后分别输出到第二行星架PC2和第二齿圈R2；具有两自由度的行星排组，实现二级传动并联三级传动的混合传动，动作一个操纵件，消除另一个自由度，可实现固定输入与输出。

上述四个实施例中，输入轴IN上并列设置n1个行星排构成第一行星排组PZ1；输出轴OUT上并列设置n2个行星排构成第二行星排组PZ2；两个行星排组中的每个行星排设置相应的制动器。

第一行星排组PZ1里的n1个行星排与第二行星排组PZ2里的n2个行星排，两两组合，共有n1×n2种组合，n1×n2种组合里的每一个组合上的一对行星排上所设置的制动器同时制动，可以实现一个二级传动，动力输出的转动方向与动力输入的转动方向相同，可实现n1×n2个二级传动。

第三行星排P3上设置的第三制动器B3制动后，实现一个由第一行星排P1、第二行星排P2和第三行星排P3构成的具有两自由度的行星排组，第一行星排组PZ1上的n1个行星排，与第二行星排组PZ2上的n2个行星排上设置的制动器依次制动后，可消除另一个自由度，实现固定输入与输出，动力输出的转动方向与动力输入的转动方向相同，可实现n1+n2个二级传动并联三级传动的混合传动；第三行星排P3和具有连接关系的第一行星排P1、第二行星排P2，分别组合，共有两种组合方式，每一个组合上的一对行星排上所设置的制动器同时制动，仅实现第一齿圈R1(或第一太阳轮S1)和第二齿圈R2(或第二太阳轮S2)同时制动一种二级传动结果，最终可实现(n1-1)+(n2-1)个具有实际传动效能的混合传动挡位，动力输出的转动方向与动力输入的转动方向相同。

第三制动器B3与行星架制动器BL3同时接合，动力依次通过第一行星排P1、第一连接件L1、第三行星排P3、第二连接件L2和第二行星排P2，实现一个三级传动，输出动力转动方向与输入动力转动方向相反，实现1个挡位。

行星式多级传动变速机构，应用在两个行星排组上，可实现与动力输入转向同向的前进挡位数为n1×n2+(n1-1)+(n2-1)，与动力输入转向反向的后退挡位数为1。

上述行星式多级传动变速机构，是第一行星排组PZ1的行星排数量n1＝1，和第二行星排组PZ2的行星排数量n2＝1的应用示范。

另外，上述实施例中，均允许两种功率流向：第一种，动力从输入轴I N流入，从输出轴OUT流出；第二种，从输出轴OUT流入，从输入轴I N流出。

第一制动器B1、第二制动器B2、第三制动器B3和行星架制动器BL3等制动器均为摩擦式操纵结构。

第五实施例：

参考图5，一种行星式多级传动变速机构，应用第一实施例，在第一实施例的基础上增设第五行星排P5、第四行星排P4和第六行星排P6；布置方式：顺次并列分布第五行星排P5、第一行星排P1、第三行星排P3、第二行星排P2、第四行星排P4和第六行星排P6；

第五行星排P5包括第五太阳轮S5、第五行星架PC5、第五行星轮CA5和第五齿圈R5，第五行星轮CA5活动安装在第五行星架PC5上，第五齿圈R5与第五行星轮CA5相啮合，第五行星轮CA5与第五太阳轮S5相啮合，第五齿圈R5通过第五制动器B5实现制动。

第一行星排P1包括第一太阳轮S1、第一行星架PC1、第一行星轮CA1和第一齿圈R1，第一行星轮CA1活动安装在第一行星架PC1上，第一齿圈R1与第一行星轮CA1相啮合，第一行星轮CA1与第一太阳轮S1相啮合，第一齿圈R1通过第一制动器B1实现制动。

第三行星排P3包括第三太阳轮S3、第三行星架PC3、第三行星轮CA3和第三齿圈R3，第三行星轮CA3活动安装在第三行星架PC3上，第三齿圈R3与第三行星轮CA3相啮合，第三行星轮CA3与第三太阳轮S3相啮合，第三太阳轮S3活动安装在行星架连接轴L3，第三行星架PC3通过第三制动器B3实现制动。

第二行星排P2包括第二太阳轮S2、第二行星架PC2、第二行星轮CA2和第二齿圈R2，第二行星轮CA2活动安装在第二行星架PC2上，第二齿圈R2与第二行星轮CA2相啮合，第二行星轮CA2与第二太阳轮S2相啮合，第二齿圈R2通过第二制动器B2实现制动。

第四行星排P4包括第四太阳轮S4、第四行星架PC4、第四行星轮CA4和第四齿圈R4，第四行星轮CA4活动安装在第四行星架PC4上，第四齿圈R4与第四行星轮CA4相啮合，第四行星轮CA4与第四太阳轮S4相啮合，第四齿圈R4通过第四制动器B4实现制动。

第六行星排P6包括第六太阳轮S6、第六行星架PC6、第六行星轮CA6和第六齿圈R6，第六行星轮CA6活动安装在第六行星架PC6上，第六齿圈R6与第六行星轮CA6相啮合，第六行星轮CA6与第六太阳轮S6相啮合，第六齿圈R6通过第六制动器B6实现制动。

第五太阳轮S5、第一太阳轮S1与输入轴I N固定连接，第五行星架PC5与第一行星架PC1固定连接；第五行星架PC5上设置行星架制动器BL3；行星架制动器BL3可对第五行星架PC5进行制动。

第二太阳轮S2、第四太阳轮S4、第六太阳轮S6与输出轴OUT固定连接；第二齿圈R2通过第四连接件L4与第四行星架PC4固定连接，第四行星架PC4与第六行星架PC6固定连接。

可选的，输入轴I N、第五太阳轮S5、第一太阳轮S1、第三太阳轮S3、第二太阳轮S2、第四太阳轮S4、第六太阳轮S6和输出轴OUT同轴布置；功率流向：动力从输入轴I N流入，从输出轴OUT流出。

第五行星排P5和第一行星排P1构成第一行星排组PZ1，行星排数量n1＝2，第二行星排P2、第四行星排P4和第六行星排P6构成第二行星排组PZ2，行星排数量n2＝3；前进挡数量为n1×n2+(n1-1)+(n2-1)＝2×3+(2-1)+(3-1)＝9，后退挡数量为1；

第三制动器B3与第四制动器B4同时接合，实现前进一挡；

第三制动器B3与第六制动器B6同时接合，实现前进二挡；

第一制动器B1与第四制动器B4同时接合，实现前进三挡；

第一制动器B1与第六制动器B6同时接合，实现前进四挡；

第五制动器B5与第四制动器B4同时接合，实现前进五挡；

第五制动器B5与第六制动器B6同时接合，实现前进六挡；

第一制动器B1与第二制动器B2同时接合，实现前进七挡；

第五制动器B5与第二制动器B2同时接合，实现前进八挡；

第五制动器B5与第三制动器B3同时接合，实现前进九挡；

行星架制动器BL3与第三制动器B3同时接合，实现后退一挡。

相关的计算公式如表1.1所示，各挡位的控制逻辑及传动比如表1.2所示。

表1.1各挡位计算公式：

行星排K值是指行星排的齿圈齿数与太阳轮齿数之比，第一行星排P1的第一齿圈R1与第一太阳轮S1的齿数比值为K1,同理可得：第一行星排P1至第六行星排P6的齿数比值依次为K1至K6；表1.1中K1＝5、K2＝6、K3＝K4＝K5＝3、K6＝6时，输入转速为1，即可得到表1.1所示的各挡位传动比，实现前进九挡后退一挡的变速机构。

如表1.1上的计算公式也揭示了当第三制动器B3制动时，第一行星排P1、第二行星排P2和第三行星排P3组合成的具有两自由度的行星排组在扩大传动比范围时是如何产生作用的。F1挡操纵件B3-B4组合，与F3挡操纵件B1-B4组合转速公式相比，分母多了一个由K1、K2、K3构成的系数(K2+1)×K1×K3，从而减小了转速，增大了传动比；F2挡操纵件B3-B6组合，与F4挡操纵件B1-B6组合转速公式相比，同样分母多了一个由K1、K2、K3构成的系数(K2+1)×K1×K3，从而减小了转速，增大了传动比；F9挡操纵件B5-B3组合，与F8挡操纵件B5-B2组合转速公式相比，多了一个由K1、K2、K3和K5构成的系数[(K1+1)/(K5+1)-1]×K2/K1/K3，当K1>K5时，系数为正数，从而增大了转速，减小了传动比；另一方面，为避免出现循环功率，需要将K1的值设置成大于K5，当第五制动器B5制动时，第一齿圈R1的转向与第一行星架PC1转向相同，在第三制动器B3制动时，可确保动力经第一齿圈R1、第一连接件L1、第三太阳轮S3、第三齿圈R3、第二连接件L2输出到第二齿圈R2时的转向，与第二行星架PC2的转动方向不同，进而避免第二齿圈R2和第二行星架PC2共同输出动力时出现循环功率。

表1.2各挡位控制逻辑及传动比(O表示操纵件接合)

下面结合图5和表1.2对本发明的实例进行详细说明，传动比是指输入轴转速与输出轴转速之比。

第三制动器B3与第四制动器B4同时接合，分别将第三行星架PC3和第四齿圈R4固定，第一太阳轮S1与输入轴I N固定连接，以相同的方向和转速转动；在第一行星排P1中，第一太阳轮S1输入动力，动力分流为两路传动，第一路通过第一行星架PC1以二级传动的方式传动，第二路通过第一齿圈R1以三级传动的方式传动；第一路传动，在第一行星排P1中，第一太阳轮S1将动力输出到第一行星架PC1，第一行星架PC1将动力输出到行星架连接轴L3，在第二行星排P2中，行星架连接轴L3将动力输出到第二行星架PC2，第二行星架PC2动力再次分流后分别输出到第二齿圈R2和第二太阳轮S2；第二路传动，在第一行星排P1中，第一太阳轮S1通过第一行星轮CA1将动力输出到第一齿圈R1，第一齿圈R1将动力输出到第一连接件L1，在第三行星排P3中，第一连接件L1将动力输出到第三太阳轮S3，第三太阳轮S3通过第三行星轮CA3将动力输出到第三齿圈R3，第三齿圈R3将动力输出到第二连接件L2，在第二行星排P2中，第二连接件L2将动力输出到第二齿圈R2，第二齿圈R2通过第四连接件L4与第四行星架PC4固定连接，第二齿圈R2动力再次分流后分别输出到第二行星架PC2、第二太阳轮S2和第四行星架PC4；输出轴OUT为刚性结构，由于第四齿圈R4固定，第四行星架PC4与第四太阳轮S4转速比确定，已限制了行星排组的另一个自由度，最后第二行星架PC2、第二齿圈R2、第四行星架PC4通过第二太阳轮S2和第四太阳轮S4共同输出动力至输出轴OUT，实现前进一挡。

第三制动器B3与第六制动器B6同时接合，分别将第三行星架PC3和第六齿圈R6固定，第一太阳轮S1与输入轴I N固定连接，以相同的方向和转速转动；在第一行星排P1中，第一太阳轮S1输入动力，动力分流为两路传动，第一路通过第一行星架PC1以二级传动的方式传动，第二路通过第一齿圈R1以三级传动的方式传动；第一路传动，在第一行星排P1中，第一太阳轮S1将动力输出到第一行星架PC1，第一行星架PC1将动力输出到行星架连接轴L3，在第二行星排P2中，行星架连接轴L3将动力输出到第二行星架PC2，第二行星架PC2动力再次分流后分别输出到第二齿圈R2和第二太阳轮S2；第二路传动，在第一行星排P1中，第一太阳轮S1通过第一行星轮CA1将动力输出到第一齿圈R1，第一齿圈R1将动力输出到第一连接件L1，在第三行星排P3中，第一连接件L1将动力输出到第三太阳轮S3，第三太阳轮S3通过第三行星轮CA3将动力输出到第三齿圈R3，第三齿圈R3将动力输出到第二连接件L2，在第二行星排P2中，第二连接件L2将动力输出到第二齿圈R2，第二齿圈R2通过第四连接件L4与第四行星架PC4和第六行星架PC6固定连接，第二齿圈R2动力再次分流后分别输出到第二行星架PC2、第二太阳轮S2和第六行星架PC6；输出轴OUT为刚性结构，由于第六齿圈R6固定，第六行星架PC6与第六太阳轮S6转速比确定，已限制了行星排组的另一个自由度，最后第二行星架PC2、第二齿圈R2、第六行星架PC6通过第二太阳轮S2和第六太阳轮S6共同输出动力至输出轴OUT，实现前进二挡。

第一制动器B1与第四制动器B4同时接合，分别将第一齿圈R1和第四齿圈R4固定，第一太阳轮S1与输入轴I N固定连接，以相同的方向和转速转动；在第一行星排P1中，第一太阳轮S1输入动力，由于第一齿圈R1固定，第一行星架PC1与输入轴I N同向转动；第一行星架PC1通过行星架连接轴L3和第二行星架PC2固定连接，在第二行星排P2中，第二行星架PC2输入动力，第二太阳轮S2与第二齿圈R2输出动力，第二太阳轮S2与输出轴OUT固定连接，驱动输出轴OUT转动；第二齿圈R2通过第四连接件L4与第四行星架PC4固定连接，第二齿圈R2驱动第四行星架PC4转动；在第四行星排P4中，第四齿圈R4固定，第四太阳轮S4输出动力；输出轴OUT为刚性结构，最终第二太阳轮S2和第四太阳轮S4共同输出动力至输出轴OUT，实现前进三挡。

第一制动器B1与第六制动器B6同时接合，分别将第一齿圈R1和第六齿圈R6固定，第一太阳轮S1与输入轴I N固定连接，以相同的方向和转速转动；在第一行星排P1中，第一太阳轮S1输入动力，由于第一齿圈R1固定，第一行星架PC1与输入轴I N同向转动；第一行星架PC1通过行星架连接轴L3和第二行星架PC2固定连接，在第二行星排P2中，第二行星架PC2输入动力，第二太阳轮S2与第二齿圈R2输出动力，第二太阳轮S2与输出轴OUT固定连接，驱动输出轴OUT转动；第二齿圈R2通过第四连接件L4与第四行星架PC4和第六行星架PC6固定连接，第二齿圈R2驱动第六行星架PC6转动；在第六行星排P6中，第六齿圈R6固定，第六太阳轮S6输出动力；输出轴OUT为刚性结构，最终第二太阳轮S2和第六太阳轮S6共同输出动力至输出轴OUT，实现前进四挡。

第五制动器B5与第四制动器B4同时接合，分别将第五齿圈R5和第四齿圈R4固定，第五太阳轮S5与输入轴I N固定连接，以相同的方向和转速转动；在第五行星排P5中，第五太阳轮S5输入动力，由于第五齿圈R5固定，第五行星架PC5与第一行星架PC1固定相连，第一行星架PC1与输入轴IN同向转动；第一行星架PC1通过行星架连接轴L3和第二行星架PC2固定连接，在第二行星排P2中，第二行星架PC2输入动力，第二太阳轮S2与第二齿圈R2输出动力，第二太阳轮S2与输出轴OUT固定连接，驱动输出轴OUT转动；第二齿圈R2通过第四连接件L4与第四行星架PC4固定连接，第二齿圈R2驱动第四行星架PC4转动；在第四行星排P4中，第四齿圈R4固定，第四太阳轮S4输出动力；输出轴OUT为刚性结构，最终第二太阳轮S2和第四太阳轮S4共同输出动力至输出轴OUT，实现前进五挡。

第五制动器B5与第六制动器B6同时接合，分别将第五齿圈R5和第六齿圈R6固定，第五太阳轮S5与输入轴I N固定连接，以相同的方向和转速转动；在第五行星排P5中，第五太阳轮S5输入动力，由于第五齿圈R5固定，第五行星架PC5与第一行星架PC1固定相连，第一行星架PC1与输入轴IN同向转动；第一行星架PC1通过行星架连接轴L3和第二行星架PC2固定连接，在第二行星排P2中，第二行星架PC2输入动力，第二太阳轮S2与第二齿圈R2输出动力，第二太阳轮S2与输出轴OUT固定连接，驱动输出轴OUT转动；第二齿圈R2通过第四连接件L4与第四行星架PC4、第六行星架PC6固定连接，第二齿圈R2驱动第六行星架PC6转动；在第六行星排P6中，第六齿圈R6固定，第六太阳轮S6输出动力；输出轴OUT为刚性结构，最终第二太阳轮S2和第六太阳轮S6共同输出动力至输出轴OUT，实现前进六挡。

第一制动器B1与第二制动器B2同时接合，分别将第一齿圈R1和第二齿圈R2固定，第一太阳轮S1与输入轴I N固定连接，以相同的方向和转速转动；在第一行星排P1中，第一太阳轮S1输入动力，由于第一齿圈R1固定，第一行星架PC1与输入轴I N同向转动；第一行星架PC1通过行星架连接轴L3和第二行星架PC2固定连接，在第二行星排P2中，第二行星架PC2输入动力，第二齿圈R2固定，第二太阳轮S2输出动力至输出轴OUT，实现前进七挡。

第五制动器B5与第二制动器B2同时接合，分别将第五齿圈R5和第二齿圈R2固定，第五太阳轮S5与输入轴I N固定连接，以相同的方向和转速转动；在第五行星排P5中，第五太阳轮S5输入动力，由于第五齿圈R5固定，第五行星架PC5与第一行星架PC1固定相连，第一行星架PC1与输入轴IN同向转动；第一行星架PC1通过行星架连接轴L3和第二行星架PC2固定连接，在第二行星排P2中，第二行星架PC2输入动力，第二齿圈R2固定，第二太阳轮S2输出动力至输出轴OUT，实现前进八挡。

第五制动器B5与第三制动器B3同时接合，分别将第五齿圈R5和第三行星架PC3固定，第五太阳轮S5与输入轴I N固定连接，以相同的方向和转速转动；在第五行星排P5中，第五太阳轮S5输入动力，由于第五齿圈R5固定，第五行星架PC5转速确定，并与输入轴IN同向转动；在第一行星排P1中，第一太阳轮S1输入动力，动力分流为两路传动，第一路通过第一行星架PC1以二级传动的方式传动，第二路通过第一齿圈R1以三级传动的方式传动；第一路传动，在第一行星排P1中，第一太阳轮S1将动力输出到第一行星架PC1，第一行星架PC1将动力输出到行星架连接轴L3，在第二行星排P2中，行星架连接轴L3将动力输出到第二行星架PC2，第二行星架PC2动力再次分流后分别输出到第二齿圈R2和第二太阳轮S2；第二路传动，在第一行星排P1中，第一太阳轮S1通过第一行星轮CA1将动力输出到第一齿圈R1，第一齿圈R1将动力输出到第一连接件L1，在第三行星排P3中，第一连接件L1将动力输出到第三太阳轮S3，第三太阳轮S3通过第三行星轮CA3将动力输出到第三齿圈R3，第三齿圈R3将动力输出到第二连接件L2，在第二行星排P2中，第二连接件L2将动力输出到第二齿圈R2，第二齿圈R2动力再次分流后分别输出到第二行星架PC2和第二太阳轮S2；由于第五齿圈R5固定，第五行星架PC5转速确定，已限制了行星排组的另一个自由度，最后第二行星架PC2和第二齿圈R2通过第二太阳轮S2共同输出动力至输出轴OUT，实现前进九挡。

行星架制动器BL3与第三制动器B3同时接合，分别将第五行星架PC5、第一行星架PC1、第二行星架PC2和第三行星架PC3固定，第一太阳轮S1与输入轴I N固定连接，以相同的方向和转速转动；在第一行星排P1中，第一太阳轮S1输入动力，第一行星架PC1固定，第一齿圈R1与输入轴IN反向转动；第一齿圈R1与第三太阳轮S3通过第一连接件L1固定连接，在第三行星排P3中，第三太阳轮S3输入动力，第三行星架PC3固定，第三齿圈R3与输入轴IN同向转动；第三齿圈R3与第二齿圈R2通过第二连接件L2固定连接，在第二行星排P2中，第二齿圈R2输入动力，第二行星架PC2固定，第二太阳轮S2与输入轴IN反向转动，第二太阳轮S2与输出轴OUT固定连接，第二太阳轮S2输出动力至输出轴OUT，实现后退一挡。

上述各挡位的传动比由六个行星排的K值决定，行星排K值是指行星排的齿圈齿数与太阳轮齿数之比，例如K1＝5、K2＝6、K3＝K4＝K5＝3、K6＝6时，即可得到表1.1所示的各挡位传动比，实现前进九挡后退一挡的变速机构，且一挡速比大于5，可降低车辆低速工况时液力变矩器的负载，提高液力变矩器的可靠性，同时大速比可使发动机更多的运行在经济工作区内，提高整机经济性。

由表1.2中各挡位的换挡逻辑可知，每个挡位通过操纵两元件进行控制，可减少摩擦片的滑摩功和热损耗，提高摩擦片的可靠性。

可选的，第一齿圈R1齿数与第一太阳轮S1齿数之比为5。第二齿圈R2齿数与第二太阳轮S2齿数之比为6。第三齿圈R3齿数与第三太阳轮S3齿数之比为3。第四齿圈R4齿数与第四太阳轮S4齿数之比为3。第五齿圈R5齿数与第五太阳轮S5齿数之比为3。第六齿圈R6齿数与第六太阳轮S6齿数之比为6。

可选的，前进一挡的传动比为5.89，前进二挡的传动比为3.73，前进三挡的传动比为2.14，前进四挡的传动比为1.59，前进五挡的传动比为1.43，前进六挡的传动比为1.06，前进七挡的传动比为0.86，前进八挡的传动比为0.57，前进九挡的传动比为0.51；后退一挡的传动比为2.50。

可选的，前进一挡与前进二挡的阶比为1.58，前进二挡与前进三挡的阶比为1.74，前进三挡与前进四挡的阶比为1.35，前进四挡与前进五挡的阶比为1.11，前进五挡与前进六挡的阶比为1.35，前进六挡与前进七挡的阶比为1.24，前进七挡与前进八挡的阶比为1.50，前进八挡与前进九挡的阶比为1.11；最高挡和最低挡的传动比范围为11.49。

本实施例公开了一种车辆传动系统用行星式多级传动变速机构，如图5所示，包括一个输入轴IN、一个输出轴OUT、六个行星排(P1～P6)、七个制动器(BL3、B1～B6)、四个连接件(L1～L4)。

每个行星排均包括：太阳轮(S1～S6)、行星架(PC1～PC6)、行星轮(CA1～CA6)及齿圈(R1～R6)；齿圈与太阳轮同轴分布，行星轮分别通过行星轴和轴承安装在行星架上，且每个行星轮与同行星排上的齿圈内啮合，与同行星排上的太阳轮外啮合。

六个行星排从左到右依次并列分布，且六个太阳轮、输入轴I N与输出轴OUT同轴布置。

本申请中车辆传动系统用行星式多级成传动变速机构，包括六个行星排，七个制动器，行星排均为单行星简单行星排，最高可实现前进九挡后退一挡，前进一挡传动比大于5，挡位多、传动比范围大，阶比小而均匀，可使发动机更多的运行在经济工作区内，提高整机经济性。七个制动器，均为摩擦操纵结构，且通过两元件操纵控制挡位，可减少摩擦片的滑摩功和热损耗，提高摩擦片的可靠性。

第六实施例：

如图6所示，一种行星式多级传动变速机构，应用上述第二实施例，在第二实施例的基础上增设双离合器C1与电机MG等结构。

该传动变速机构包括输入轴IN、双离合器C1、电机MG、第一行星排P1、第三行星排P3、第二行星排P2和输出轴OUT；

输入轴IN与双离合器C1固定连接，双离合器C1上的第一组离合器C11与第四连接件L4固定连接，第四连接件L4上设置第四制动器B4，第四连接件L4上设置有第一行星排P1，第一太阳轮S1与第四连接件L4固定连接；输出轴OUT上设置第二行星排P2，第二齿圈R2与输出轴OUT固定连接；

双离合器C1包括第一组离合器C11和第二组离合器C12；第二组离合器C12设置第一主动齿轮G11，第一主动齿轮G11与第二组离合器C12固定连接；平行的设置电机MG，电机MG的主轴平行于输入轴I N，电机MG的一端与第二组离合器C12连接，另一端与第一齿圈R1连接，第一从动齿轮G12固定安装在电机MG上，并与第一主动齿轮G11相啮合；第二从动齿轮G22与第一齿圈R1固定连接，第二主动齿轮G21固定安装在电机MG上，并与第二从动齿轮G22相啮合。

第一行星排P1包括第一太阳轮S1、第一行星架PC1、第一行星轮CA1和第一齿圈R1，第一行星轮CA1活动安装在第一行星架PC1上，第一齿圈R1与第一行星轮CA1相啮合，第一行星轮CA1与第一太阳轮S1相啮合，第一齿圈R1通过第一制动器B1实现制动，第一太阳轮S1通过第四制动器B4实现制动；

第三行星排P3包括第三太阳轮S3、第三行星架PC3、第三行星轮CA3和第三齿圈R3，第三行星轮CA3活动安装在第三行星架PC3上，第三齿圈R3与第三行星轮CA3相啮合，第三行星轮CA3与第三太阳轮S3相啮合，第三太阳轮S3活动安装在行星架连接轴L3上，第三行星架PC3通过第三制动器B3实现制动；

第二行星排P2包括第二太阳轮S2、第二行星架PC2、第二行星轮CA2和第二齿圈R2，第二行星轮CA2活动安装在第二行星架PC2上，第二齿圈R2与第二行星轮CA2相啮合，第二行星轮CA2与第二太阳轮S2相啮合，第二太阳轮S2活动安装在行星架连接轴L3上，第二太阳轮S2通过第二制动器B2实现制动，第二行星架PC2设置行星架制动器BL3实现制动；

第一组离合器C11和第一太阳轮S1通过第四连接件L4固定连接，第四连接件L4与第四制动器B4连接，第四连接件L4与第一太阳轮S1固定连接，第一太阳轮S1通过第四制动器B4实现制动。

可选的，双离合器C1、输入轴IN、第一太阳轮S1、第三太阳轮S3、第二太阳轮S2和输出轴OUT同轴布置；电机MG与输入轴IN平行轴布置；功率流向：动力从输入轴I N流入，从输出轴OUT流出。

内燃机动力单独驱动可以实现六个前进挡和一个后退挡。具体如下：

第一组离合器C11接合，第一制动器B1与第二制动器B2同时接合，实现前进一挡；

第二组离合器C12接合，第三制动器B3与行星架制动器BL3同时接合，实现前进二挡；

第二组离合器C12接合，第二制动器B2与第四制动器B4同时接合，实现前进三挡；

第一组离合器C11和第二组离合器C12同时接合，第二制动器B2接合，实现前进四挡；

第二组离合器C12接合，第三制动器B3与第四制动器B4同时接合，实现前进五挡；

第一组离合器C11和第二组离合器C12同时接合，第三制动器B3接合，实现前进六挡；

第一组离合器C11接合，第三制动器B3与行星架制动器BL3同时接合，实现后退一挡。

电动机动力单独驱动可以实现三个前进挡，电机反转可以实现三个同样挡位的后退挡。具体如下：

第三制动器B3与行星架制动器BL3同时接合，实现前进一挡；

第二制动器B2与第四制动器B4同时接合，实现前进二挡；

第三制动器B3与第四制动器B4同时接合，实现前进三挡。

相关的计算公式如表2.1和表3.1所示，各挡位的控制逻辑及传动比如表2.2和表3.2所示。

表2.1内燃机动力单独驱动各挡位计算公式

行星排K值是指行星排的齿圈齿数与太阳轮齿数之比，上表K1＝6、K2＝4、K3＝3，齿轮组G11:G12的传动比KG1＝0.4，齿轮组G21:G22的传动比KG2＝4时，输入转速为1，即可得到表2.1所示的各挡位传动比，实现前进六挡后退一挡的变速机构。

表2.2内燃机动力单独驱动各挡位控制逻辑及传动比(O表示操纵件接合)

下面结合图6和表2.2对本发明内燃机动力单独驱动实例进行详细说明，传动比是指输入轴转速与输出轴转速之比。

第一组离合器C11接合，第一制动器B1与第二制动器B2同时接合，分别将第一齿圈R1和第二太阳轮S2固定，第一太阳轮S1与第四连接件L4固定连接，通过第一组离合器C11与输入轴I N固定连接，以相同的方向和转速转动；在第一行星排P1中，第一太阳轮S1输入动力，由于第一齿圈R1固定，第一行星架PC1与输入轴I N同向转动；第一行星架PC1通过行星架连接轴L3和第二行星架PC2固定连接，在第二行星排P2中，第二行星架PC2输入动力，第二太阳轮S2固定，第二齿圈R2输出动力至输出轴OUT，实现前进一挡。

第二组离合器C12接合，第三制动器B3与行星架制动器BL3同时接合，分别将第一行星架PC1、第二行星架PC2和第三行星架PC3固定；第一主动齿轮G11与第二组离合器C12固定连接，通过第二组离合器C12与输入轴I N固定连接，以相同的方向和转速转动；第一从动齿轮G12固定安装在电机MG上，并与第一主动齿轮G11相啮合，与输入轴I N的转动方向相反；第二从动齿轮G22与第一齿圈R1固定连接，第二主动齿轮G21固定安装在电机MG上，并与第二从动齿轮G22相啮合，第二从动齿轮G22与输入轴IN的转动方向相同；第二从动齿轮G22与第一齿圈R1固定连接，第一齿圈R1与输入轴IN同向转动；第一齿圈R1与第三齿圈R3通过第一连接件L1固定连接，在第三行星排P3中，第三齿圈R3输入动力，第三行星架PC3固定，第三太阳轮S3与输入轴IN反向转动；第三太阳轮S3与第二太阳轮S2通过第二连接件L2固定连接，在第二行星排P2中，第二太阳轮S2输入动力，第二行星架PC2固定，第二齿圈R2与输入轴IN同向转动，第二齿圈R2与输出轴OUT固定连接，第二齿圈R2输出动力至输出轴OUT，实现前进二挡。

第二组离合器C12接合，第四制动器B4与第二制动器B2同时接合，分别将第一太阳轮S1和第二太阳轮S2固定；第一主动齿轮G11与第二组离合器C12固定连接，通过第二组离合器C12与输入轴IN固定连接，以相同的方向和转速转动；第一从动齿轮G12固定安装在电机MG上，并与第一主动齿轮G11相啮合，与输入轴IN的转动方向相反；第二从动齿轮G22与第一齿圈R1固定连接，第二主动齿轮G21固定安装在电机MG上，并与第二从动齿轮G22相啮合，第二从动齿轮G22与输入轴IN的转动方向相同；第二从动齿轮G22与第一齿圈R1固定连接，第一齿圈R1与输入轴IN同向转动；在第一行星排P1中，第一齿圈R1输入动力，由于第一太阳轮S1固定，第一行星架PC1与输入轴I N同向转动；第一行星架PC1通过行星架连接轴L3和第二行星架PC2固定连接，在第二行星排P2中，第二行星架PC2输入动力，第二太阳轮S2固定，第二齿圈R2与输入轴IN同向转动，第二齿圈R2输出动力至输出轴OUT，实现前进三挡。

第一组离合器C11和第二组离合器C12同时接合，第二制动器B2接合，第二太阳轮S2固定；第一太阳轮S1与第四连接件L4固定连接，通过第一组离合器C11与输入轴IN固定连接，以相同的方向和转速转动；第一主动齿轮G11与第二组离合器C12固定连接，通过第二组离合器C12与输入轴IN固定连接，以相同的方向和转速转动；第一从动齿轮G12固定安装在电机MG上，并与第一主动齿轮G11相啮合，与输入轴IN的转动方向相反；第二从动齿轮G22与第一齿圈R1固定连接，第二主动齿轮G21固定安装在电机MG上，并与第二从动齿轮G22相啮合，第二从动齿轮G22与输入轴IN的转动方向相同；第二从动齿轮G22与第一齿圈R1固定连接，第一齿圈R1与输入轴IN同向转动；第一太阳轮S1和第一齿圈R1与输入轴IN同向转动，共同输出动力到第一行星架PC1，第一行星架PC1与输入轴IN同向转动；第一行星架PC1通过行星架连接轴L3和第二行星架PC2固定连接，在第二行星排P2中，第二行星架PC2输入动力，第二太阳轮S2固定，第二齿圈R2与输入轴IN同向转动，第二齿圈R2输出动力至输出轴OUT，实现前进四挡。

第二组离合器C12接合，第四制动器B4与第三制动器B3同时接合，分别将第一太阳轮S1和第三行星架PC3固定；第一主动齿轮G11与第二组离合器C12固定连接，通过第二组离合器C12与输入轴IN固定连接，以相同的方向和转速转动；第一从动齿轮G12固定安装在电机MG上，并与第一主动齿轮G11相啮合，与输入轴IN的转动方向相反；第二从动齿轮G22与第一齿圈R1固定连接，第二主动齿轮G21固定安装在电机MG上，并与第二从动齿轮G22相啮合，第二从动齿轮G22与输入轴IN的转动方向相同；第二从动齿轮G22与第一齿圈R1固定连接，第一齿圈R1与输入轴IN同向转动；在第一行星排P1中，第一齿圈R1输入动力，由于第一太阳轮S1固定，第一行星架PC1与输入轴I N同向转动；第一行星架PC1通过行星架连接轴L3和第二行星架PC2固定连接，第二行星架PC2与输入轴I N同向转动；第一齿圈R1与第三齿圈R3通过第一连接件L1固定连接，在第三行星排P3中，第三齿圈R3输入动力，第三行星架PC3固定，第三太阳轮S3与输入轴IN反向转动，第三太阳轮S3与第二太阳轮S2通过第二连接件L2固定连接，第二太阳轮S2与输入轴IN反向转动；在第二行星排P2中，第二行星架PC2和第二太阳轮S2共同输入动力，第二齿圈R2输出动力至输出轴OUT；在行星架和太阳轮共同输入动力，齿圈输出动力时，太阳轮转动方向与行星架相反，可避免出现循环功率，齿圈转动方向与行星架方向相同，从而实现前进五挡。

第一组离合器C11和第二组离合器C12同时接合，第三制动器B3接合，第三行星架PC3固定；第一太阳轮S1与第四连接件L4固定连接，通过第一组离合器C11与输入轴IN固定连接，以相同的方向和转速转动；第一主动齿轮G11与第二组离合器C12固定连接，通过第二组离合器C12与输入轴IN固定连接，以相同的方向和转速转动；第一从动齿轮G12固定安装在电机MG上，并与第一主动齿轮G11相啮合，与输入轴IN的转动方向相反；第二从动齿轮G22与第一齿圈R1固定连接，第二主动齿轮G21固定安装在电机MG上，并与第二从动齿轮G22相啮合，第二从动齿轮G22与输入轴IN的转动方向相同；第二从动齿轮G22与第一齿圈R1固定连接，第一齿圈R1与输入轴IN同向转动；第一太阳轮S1和第一齿圈R1与输入轴IN同向转动，共同输出动力到第一行星架PC1，第一行星架PC1与输入轴IN同向转动；第一行星架PC1通过行星架连接轴L3和第二行星架PC2固定连接，第二行星架PC2与输入轴IN同向转动；第一齿圈R1与第三齿圈R3通过第一连接件L1固定连接，在第三行星排P3中，第三齿圈R3输入动力，第三行星架PC3固定，第三太阳轮S3与输入轴IN反向转动，第三太阳轮S3与第二太阳轮S2通过第二连接件L2固定连接，第二太阳轮S2与输入轴I N反向转动；在第二行星排P2中，第二行星架PC2和第二太阳轮S2共同输入动力，第二齿圈R2输出动力至输出轴OUT；在行星架和太阳轮共同输入动力，齿圈输出动力时，太阳轮转动方向与行星架相反，可避免出现循环功率，齿圈转动方向与行星架方向相同，从而实现前进六挡。

第一组离合器C11接合，第三制动器B3与行星架制动器BL3同时接合，分别将第一行星架PC1、第二行星架PC2和第三行星架PC3固定；第一太阳轮S1与第四连接件L4固定连接，通过第一组离合器C11与输入轴I N固定连接，以相同的方向和转速转动；在第一行星排P1中，第一太阳轮S1输入动力，第一行星架PC1固定，第一齿圈R1与输入轴I N反向转动；第一齿圈R1与第三齿圈R3通过第一连接件L1固定连接，在第三行星排P3中，第三齿圈R3输入动力，第三行星架PC3固定，第三太阳轮S3与输入轴I N同向转动；第三太阳轮S3与第二太阳轮S2通过第二连接件L2固定连接，在第二行星排P2中，第二太阳轮S2输入动力，第二行星架PC2固定，第二齿圈R2与输入轴I N反向转动，第二齿圈R2与输出轴OUT固定连接，第二齿圈R2输出动力至输出轴OUT，实现后退一挡。

表3.1电机MG动力单独驱动计算公式

行星排K值是指行星排的齿圈齿数与太阳轮齿数之比，上表K1＝6、K2＝4、K3＝3，齿轮组G21:G22的传动比KG2＝4时，电机MG输入转速为1，即可得到表3.1所示的各挡位传动比，实现三个挡位的变速机构。

表3.2电机MG动力单独驱动各挡位控制逻辑及传动比(O表示操纵件接合)

下面结合图6和表3.2对本发明电机动力单独驱动实例进行详细说明，传动比是指输入轴转速与输出轴转速之比。

第三制动器B3与行星架制动器BL3同时接合，分别将第一行星架PC1、第二行星架PC2和第三行星架PC3固定；第二主动齿轮G21固定安装在电机MG上，并与第二从动齿轮G22相啮合，第二从动齿轮G22转动方向与电机MG转动方向相反；第二从动齿轮G22与第一齿圈R1固定连接，第一齿圈R1与电机MG反向转动；第一齿圈R1与第三齿圈R3通过第一连接件L1固定连接，在第三行星排P3中，第三齿圈R3输入动力，第三行星架PC3固定，第三太阳轮S3与电机MG同向转动；第三太阳轮S3与第二太阳轮S2通过第二连接件L2固定连接，在第二行星排P2中，第二太阳轮S2输入动力，第二行星架PC2固定，第二齿圈R2与电机MG反向转动，第二齿圈R2与输出轴OUT固定连接，第二齿圈R2输出动力至输出轴OUT，实现第一挡。

第四制动器B4与第二制动器B2同时接合，分别将第一太阳轮S1和第二太阳轮S2固定；第二主动齿轮G21固定安装在电机MG上，并与第二从动齿轮G22相啮合，第二从动齿轮G22转动方向与电机MG转动方向相反；第二从动齿轮G22与第一齿圈R1固定连接，第一齿圈R1与电机MG反向转动；在第一行星排P1中，第一齿圈R1输入动力，由于第一太阳轮S1固定，第一行星架PC1与电机MG反向转动；第一行星架PC1通过行星架连接轴L3和第二行星架PC2固定连接，在第二行星排P2中，第二行星架PC2输入动力，第二太阳轮S2固定，第二齿圈R2与电机MG反向转动，第二齿圈R2输出动力至输出轴OUT，实现第二挡。

第四制动器B4与第三制动器B3同时接合，分别将第一太阳轮S1和第三行星架PC3固定；第二主动齿轮G21固定安装在电机MG上，并与第二从动齿轮G22相啮合，第二从动齿轮G22与电机MG转动方向相反；第二从动齿轮G22与第一齿圈R1固定连接，第一齿圈R1与电机MG转动方向相反；在第一行星排P1中，第一齿圈R1输入动力，由于第一太阳轮S1固定，第一行星架PC1与电机MG反向转动；第一行星架PC1通过行星架连接轴L3和第二行星架PC2固定连接，第二行星架PC2与电机MG转动方向相反；第一齿圈R1与第三齿圈R3通过第一连接件L1固定连接，在第三行星排P3中，第三齿圈R3输入动力，第三行星架PC3固定，第三太阳轮S3与电机MG同向转动，第三太阳轮S3与第二太阳轮S2通过第二连接件L2固定连接，第二太阳轮S2与电机MG同向转动；在第二行星排P2中，第二行星架PC2和第二太阳轮S2共同输入动力，第二齿圈R2与电机MG转动方向相反，第二齿圈R2输出动力至输出轴OUT；在行星架和太阳轮共同输入动力，齿圈输出动力时，太阳轮转动方向与行星架相反，可避免出现循环功率，齿圈转动方向与行星架方向相同，从而实现第三挡。

电机MG可以控制正向、反向转动，从而可以实现前进和后退各三个挡位。

上述各挡位的传动比由两对齿轮组的传动比和三个行星排的K值决定。本例齿轮组的传动比为：齿轮组G11:G12的传动比KG1＝0.4，齿轮组G21:G22的传动比KG2＝4；行星排K值是指行星排的齿圈齿数与太阳轮齿数之比，本例为：K1＝6、K2＝4、K3＝3，即可得到表2.2和表3.2所示的各挡位传动比，实现内燃机动力独立驱动前进六挡后退一挡的变速机构，以及电机动力独立驱动前进和后退各三个挡位的变速机构。

可选的，换挡时，仅第一组离合器C11接合，电机MG与内燃机并联，将电机MG作为发电机用于发电，一方面以平衡发动机所受的载荷，使发动机在换挡阶段能提供足够的驱动力，另一方面将发动机与变速箱之间因转速差而无法用于驱动的动力用于发电，为动力电池充电，换挡的平顺性也得到极大的改善；正常行驶时，第一组离合器C11和第二组离合器C12同时接合，电机MG与内燃机混联驱动，电机MG辅助内燃机工作，输出传动比不变，提升输出总功率，增加输出扭矩；

可选的，仅第一组离合器C11接合，电机MG与内燃机并联驱动，电机MG用于调速和调扭，可实现无级变速，实现ECVT变速箱的功能，可减少离合器摩擦片的滑摩功和热损耗，提升动力使用效率，提高摩擦片的可靠性。

可选的，内燃机前置，设置后轮驱动电机，仅第一组离合器C11接合，电机MG与内燃机并联，将电机MG作为发电机用于发电，所发电力用于后轮电机的驱动，从而将内燃机的动力在前、后轮进行重新分配，实现四轮驱动。

可选的，第一从动齿轮G12与第一主动齿轮G11齿数之比为0.4。第二从动齿轮G22与第二主动齿轮G21齿数之比为4。第一齿圈R1齿数与第一太阳轮S1齿数之比为6。第二齿圈R2齿数与第二太阳轮S2齿数之比为4。第三齿圈R3齿数与第三太阳轮S3齿数之比为3。

可选的，内燃机动力独立驱动，前进一挡的传动比为5.60，前进二挡的传动比为2.13，前进三挡的传动比为1.49，前进四挡的传动比为1.18，前进五挡的传动比为0.88，前进六挡的传动比为0.76；后退一挡的传动比为8.00。进一步地，内燃机动力独立驱动，前进一挡与前进二挡的阶比为2.63，前进二挡与前进三挡的阶比为1.43，前进三挡与前进四挡的阶比为1.27，前进四挡与前进五挡的阶比为1.34，前进五挡与前进六挡的阶比为1.16；最高挡和最低挡的传动比范围为7.38。

可选的，电机动力独立驱动，第一挡的传动比为5.33，第二挡的传动比为3.73，第三挡的传动比为2.2；电机可以控制正向、反向转动，从而可以实现前进和后退各三个挡位。进一步地，电机动力独立驱动，前进一挡与前进二挡的阶比为1.43，前进二挡与前进三挡的阶比为1.7；最高挡和最低挡的传动比范围为2.43。

本实施例公开了一种车辆传动系统用行星式多级传动变速机构，如图6所示，包括一个双离合器C1、一个电机MG、一个输入轴I N、一个输出轴OUT、三个行星排(P1～P3)、五个制动器(BL3、B1～B4)、四个连接件(L1～L4)。

每个行星排均包括：太阳轮(S1～S3)、行星架(PC1～PC3)、行星轮(CA1～CA3)及齿圈(R1～R3)；齿圈与太阳轮同轴分布，行星轮分别通过行星轴和轴承安装在行星架上，且每个行星轮与同行星排上的齿圈内啮合，与同行星排上的太阳轮外啮合。

双离合器C1和三个行星排从左到右依次并列分布，且双离合器C1、三个太阳轮、输入轴I N与输出轴OUT同轴布置。电机MG与输入轴IN平行轴布置。

功率流向：动力从输入轴IN流入，从输出轴OUT流出。电机MG并联驱动时，电机MG的动力从第一齿圈R1流入，从输出轴OUT流出。

本申请中车辆传动系统用行星式多级传动变速机构，包括三个行星排，五个制动器，行星排均为单行星简单行星排，最高可实现前进六挡后退一挡，前进一挡传动比大于5，可实现油、电混合驱动，可使发动机更多的运行在经济工作区内，提高整机经济性。五个制动器，均为摩擦操纵结构，且通过两元件操纵控制挡位，可减少摩擦片的滑摩功和热损耗，提高摩擦片的可靠性。

第七实施例：

一种车辆传动系统，包括第一实施例至第六实施例任一的行星式多级传动变速机构。

综上，本发明的车辆传动系统结构简单、传动比范围大、传递扭矩能力强、挡位可扩展性强，相较于现有的传动系统能够更好的适应车辆的传动需求。

以上公开的仅是本发明的一些实施方式。对于本领域的普通技术人员来说，在不脱离本发明创造构思的前提下，还可以做出若干变形和改进，这些都属于本发明的保护范围。

The specific embodiment

The present invention is described in further detail below in conjunction with the accompanying drawings.

The first embodiment:

Referring to FIG. 1, a planetary multi-stage transmission transmission mechanism comprises input shaft IN, output shaft OUT, the first planetary row P1, the second planetary row P2 and the third planetary row P3;

The input shaft IN is connected with the first planetary row P1; The output shaft OUT is connected with the second planetary row P2;

The first planetary row P1 comprises the first sun gear S1, the first planetary carrier PC1, the first planetary wheel CA1 and the first gear ring R1; the first planetary wheel CA1 is movably mounted on the first planetary carrier PC1, the first gear ring R1 is meshed with the first planetary wheel CA1, and the first planetary wheel CA1 is meshed with the first sun wheel S1;

the second planet row P2 comprises a second sun gear S2, a second planet carrier PC2, a second planet wheel CA2 and a second gear ring R2; the second planet wheel CA2 is movably mounted on the second planet carrier PC2, the second gear ring R2 is meshed with the second planet wheel CA2, and the second planet wheel CA2 is meshed with the second sun wheel S2;

the third planet row P3 comprises the third sun gear S3, the third planet carrier PC3, the third planet wheel CA3 and the third gear ring R3; the third planet wheel CA3 is movably installed on the third planet carrier PC3, the third gear ring R3 is meshed with the third planet wheel CA3, and the third planet wheel CA3 is meshed with the third sun wheel S3;

the third sun gear S3 is movably arranged on the planet carrier connecting shaft L3; The first planetary carrier PC1 and the second planetary carrier PC2 are fixedly connected through the planetary carrier connecting shaft L3.

input shaft IN is fixedly connected with the first sun gear S1, the first gear ring R1 is fixedly connected with the third sun gear S3 through the first connecting piece L1, the third gear ring R3 is fixedly connected with the second gear ring R2 through the second connecting piece L2, and the output shaft OUT is fixedly connected with the second sun gear S2;

The first gear ring R1 is connected with the first brake B1, that is, the first brake B1 can brake the first gear ring R1; The second gear ring R2 is connected with the second brake B2, that is, the second brake B2 can brake the second gear ring R2; the second planetary carrier PC2 is connected with the planetary carrier brake BL3, that is, the planetary carrier brake BL3 can brake the second planetary carrier PC2; The third planetary carrier PC3 is connected with the third brake B3, that is, the third brake B3 can brake the third planetary carrier PC3.

Among them, the movable installation can be understood as a rotating connection; A fixed connection can be understood as a linkage connection.

Working principle: ring gear is connected to the sun gear, ring gear is connected to ring gear, RS-RR type.

The first brake B1 is engaged with the second brake B2 at the same time, the first gear ring R1 and the second gear ring R2 are fixed respectively, and the first sun gear S1 is fixedly connected with input shaft N, and rotates in the same direction and speed; In the first planetary row P1, the first sun gear S1 inputs power, the first gear ring R1 is fixed, and the first planetary carrier PC1 rotates in the same direction with the input shaft I N; in the second planetary row P2, the second planetary carrier PC2 is fixedly connected with the first planetary carrier PC1 through the planetary carrier connecting shaft L3, the second planetary carrier PC2 input power, the second gear ring R2 is fixed, the second sun gear S2 is fixedly connected with the output shaft OUT, the second sun gear S2 outputs power to the output shaft OUT, and the output shaft OUT is the same as the input shaft I N rotation direction; The power passes through the first planetary row P1, the planetary carrier connecting shaft L3 and the second planetary row P2 in turn, realizes the two-stage transmission, and the direction of rotation of the output power is the same as that of the input power.

The third brake B3 is engaged with the planetary carrier brake BL3 at the same time, the first planetary carrier PC1, the second planetary carrier PC2 and the third planetary carrier PC3 are fixed respectively, and the first sun gear S1 is fixedly connected with the input shaft IN and rotates in the same direction and speed; In the first planetary row P1, the first sun gear S1 inputs power, the first planetary carrier PC1 is fixed, and the first gear ring R1 rotates in the opposite direction with the input shaft IN; The first gear ring R1 is fixedly connected with the third sun gear S3 through the first connecting piece L1, and in the third planetary row P3, the third sun gear S3 input power, the third planet carrier PC3 is fixed, and the third gear ring R3 rotates in the same direction with the input shaft IN; The third gear ring R3 is fixedly connected with the second gear ring R2 through the second connecting piece L2, in the second planetary row P2, the second gear ring R2 input power, the second planetary carrier PC2 is fixed, the second sun gear S2 and the input shaft I N rotate in the opposite direction, the second sun gear S2 is fixedly connected with the output shaft OUT, the second sun gear S2 outputs power to the output shaft OUT, and the output shaft OUT is opposite to the input shaft IN rotation direction; The power passes through the first planetary row P1, the first connecting piece L1, the third planetary row P3, the second connecting piece L2 and the second planetary row P2 in turn, realizes three-stage transmission, and the direction of rotation of output power is opposite to the direction of rotation of input power.

The third brake B3 is individually engaged, the third planetary carrier PC3 is fixed, the first planetary row P1, the second planetary row P2 and the third planetary row P3 are combined into a planetary row group with two degrees of freedom, and the power is divided into a two-stage transmission and a three-stage transmission, and a mixed transmission is realized; The first sun gear S1 is fixedly connected with the input shaft I N and rotates in the same direction and speed; In the first planetary row P1, the first sun gear S1 inputs power, and the power shunt is a two-way transmission, the first road is transmitted in the mode of two-stage transmission through the first planetary carrier PC1, and the second road is transmitted in the mode of three-stage transmission through the first ring gear R1; In the first planetary row P1, the first sun gear S1 will output power to the first planet carrier PC1, the first planet carrier PC1 will output power to the planet carrier connecting shaft L3, in the second planet row P2, the planet carrier connecting shaft L3 will output power to the second planet carrier PC2, and the second planet carrier PC2 power is respectively output to the second gear ring R2 and the second sun gear S2 after the second planet carrier PC2 power is shunted again; The second way transmission, in the first planetary row P1, the first sun gear S1 outputs power to the first gear ring R1 through the first planet wheel CA1, the first gear ring R1 will output power to the first connecting piece L1, in the third planet row P3, the first connecting piece L1 will output power to the third sun gear S3, the third sun gear S3 will output power to the third gear ring R3 through the third planet wheel CA3, the third gear ring R3 will output power to the second connecting piece L2, in the second planet row P2, the second connecting piece L2 outputs power to the second gear ring R2, and the second gear ring R2 power is output to the second planetary carrier PC2 and the second sun gear S2 respectively after the second gear R2 power is shunted again; The planetary row group with two degrees of freedom realizes the hybrid transmission of two-stage transmission in parallel and three-stage transmission, and activates one control piece to eliminate another degree of freedom, so as to realize fixed input and output.

Second embodiment:

Referring to FIG. 2, a planetary multi-stage transmission transmission mechanism comprises input shaft IN, output shaft OUT, the first planetary row P1, the second planetary row P2 and the third planetary row P3;

The input shaft IN is connected with the first planetary row P1; The output shaft OUT is connected with the second planetary row P2;

The first planetary row P1 comprises the first sun gear S1, the first planetary carrier PC1, the first planetary wheel CA1 and the first gear ring R1; the first planetary wheel CA1 is movably mounted on the first planetary carrier PC1, the first gear ring R1 is meshed with the first planetary wheel CA1, and the first planetary wheel CA1 is meshed with the first sun wheel S1;

the second planet row P2 comprises a second sun gear S2, a second planet carrier PC2, a second planet wheel CA2 and a second gear ring R2; the second planet wheel CA2 is movably mounted on the second planet carrier PC2, the second gear ring R2 is meshed with the second planet wheel CA2, and the second planet wheel CA2 is meshed with the second sun wheel S2;

the third planet row P3 comprises the third sun gear S3, the third planet carrier PC3, the third planet wheel CA3 and the third gear ring R3; the third planet wheel CA3 is movably installed on the third planet carrier PC3, the third gear ring R3 is meshed with the third planet wheel CA3, and the third planet wheel CA3 is meshed with the third sun wheel S3;

the second sun gear S2 and the third sun gear S3 are both movably mounted on the planetary carrier connecting shaft L3; The first planetary carrier PC1 and the second planetary carrier PC2 are fixedly connected through the planetary carrier connecting shaft L3;

input shaft IN is fixedly connected with the first sun gear S1, the first gear ring R1 is fixedly connected with the third gear ring R3 through the first connecting piece L1, the third sun gear S3 is fixedly connected with the second sun gear S2 through the second connecting piece L2, and the output shaft OUT is fixedly connected with the second gear ring R2;

The first gear ring R1 is connected with the first brake B1, that is, the first brake B1 can brake the first gear ring R1; The second sun gear S2 is connected with the second brake B2, that is, the second brake B2 can brake the second sun gear S2; the second planetary carrier PC2 is connected with the planetary carrier brake BL3, that is, the planetary carrier brake BL3 can brake the second planetary carrier PC2; The third planetary carrier PC3 is connected with the third brake B3, that is, the third brake B3 can brake the third planetary carrier PC3.

Working principle: ring gear is connected to ring gear, sun gear is connected to sun gear, RR-SS type.

The first brake B1 is engaged with the second brake B2 simultaneously, the first gear ring R1 and the second sun gear S2 are fixed respectively, and the first sun gear S1 is fixedly connected with input shaft IN and rotates in the same direction and speed; In the first planetary row P1, the first sun gear S1 inputs power, the first gear ring R1 is fixed, and the first planetary carrier PC1 rotates in the same direction with the input shaft IN; in the second planetary row P2, the second planetary carrier PC2 is fixedly connected with the first planetary carrier PC1 through the planetary carrier connecting shaft L3, the second planetary carrier PC2 input power, the second sun gear S2 is fixed, the second gear ring R2 is fixedly connected with the output shaft OUT, the second gear ring R2 outputs power to the output shaft OUT, and the output shaft OUT and the input shaft IN rotate in the same direction; The power passes through the first planetary row P1, the planetary carrier connecting shaft L3 and the second planetary row P2 in turn, realizes the two-stage transmission, and the direction of rotation of the output power is the same as that of the input power.

The third brake B3 is engaged with the planetary carrier brake BL3 at the same time, the first planetary carrier PC1, the second planetary carrier PC2 and the third planetary carrier PC3 are fixed respectively, and the first sun gear S1 is fixedly connected with the input shaft IN and rotates in the same direction and speed; In the first planetary row P1, the first sun gear S1 inputs power, the first planetary carrier PC1 is fixed, and the first gear ring R1 rotates in the opposite direction with the input shaft IN; The first gear ring R1 is fixedly connected with the third gear ring R3 through the first connecting piece L1, and in the third planetary row P3, the third gear ring R3 input power, the third planet carrier PC3 is fixed, and the third sun gear S3 rotates in the same direction with the input shaft IN; the third sun gear S3 and the second sun gear S2 are fixedly connected through the second connecting piece L2, in the second planetary row P2, the second sun gear S2 input power, the second planetary carrier PC2 is fixed, the second gear ring R2 rotates in reverse with the input shaft IN, the second gear ring R2 is fixedly connected with the output shaft OUT, the second gear ring R2 outputs the power to the output shaft OUT, and the output shaft OUT is opposite to the input shaft IN rotation direction; The power passes through the first planetary row P1, the first connecting piece L1, the third planetary row P3, the second connecting piece L2 and the second planetary row P2 in turn, realizes three-stage transmission, and the direction of rotation of output power is opposite to the direction of rotation of input power.

The third brake B3 is individually engaged, the third planetary carrier PC3 is fixed, and the first planetary row P1, the second planetary row P2 and the third planetary row P3 are combined into a planetary row group with two degrees of freedom, and the mixed transmission of two-stage transmission parallel three-stage transmission is realized; The first sun gear S1 is fixedly connected with the input shaft IN and rotates in the same direction and speed; In the first planetary row P1, the first sun gear S1 inputs power, and the power shunt is a two-way transmission, the first road is transmitted in the mode of two-stage transmission through the first planetary carrier PC1, and the second road is transmitted in the mode of three-stage transmission through the first ring gear R1; In the first planetary row P1, the first sun gear S1 will output power to the first planet carrier PC1, the first planet carrier PC1 will output power to the planet carrier connecting shaft L3, in the second planet row P2, the planet carrier connecting shaft L3 will output power to the second planet carrier PC2, and the second planet carrier PC2 power is respectively output to the second gear ring R2 and the second sun gear S2 after the second planet carrier PC2 power is shunted again; The second way transmission, in the first planetary row P1, the first sun gear S1 outputs power to the first gear ring R1 through the first planet wheel CA1, the first gear ring R1 will output power to the first connecting piece L1, in the third planetary row P3, the first connecting piece L1 will output power to the third gear ring R3, the third gear gear R3 will output power to the third sun gear S3 through the third planet wheel CA3, the third sun gear S3 will output power to the second connecting piece L2, in the second planet row P2, the second connecting piece L2 outputs power to the second sun gear S2, and the second sun gear S2 outputs the power to the second planetary carrier PC2 and the second gear ring R2 respectively after the power is shunted again; The planetary row group with two degrees of freedom realizes the hybrid transmission of two-stage transmission in parallel and three-stage transmission, and activates one control piece to eliminate another degree of freedom, so as to realize fixed input and output.

3rd embodiment:

Referring to FIG. 3, a planetary multistage transmission variable speed mechanism comprises input shaft IN, output shaft OUT, the first planetary row P1, the second planetary row P2 and the third planetary row P3;

The input shaft IN is connected with the first planetary row P1; The output shaft OUT is connected with the second planetary row P2;

The first planetary row P1 comprises the first sun gear S1, the first planetary carrier PC1, the first planetary wheel CA1 and the first gear ring R1; the first planetary wheel CA1 is movably mounted on the first planetary carrier PC1, the first gear ring R1 is meshed with the first planetary wheel CA1, and the first planetary wheel CA1 is meshed with the first sun wheel S1;

the second planet row P2 comprises a second sun gear S2, a second planet carrier PC2, a second planet wheel CA2 and a second gear ring R2; the second planet wheel CA2 is movably mounted on the second planet carrier PC2, the second gear ring R2 is meshed with the second planet wheel CA2, and the second planet wheel CA2 is meshed with the second sun wheel S2;

the third planet row P3 comprises the third sun gear S3, the third planet carrier PC3, the third planet wheel CA3 and the third gear ring R3; the third planet wheel CA3 is movably installed on the third planet carrier PC3, the third gear ring R3 is meshed with the third planet wheel CA3, and the third planet wheel CA3 is meshed with the third sun wheel S3;

the second sun gear S2 and the third sun gear S3 are both movably mounted on the planetary carrier connecting shaft L3; The first planetary carrier PC1 and the second planetary carrier PC2 are fixedly connected through the planetary carrier connecting shaft L3;

input shaft IN is fixedly connected with the first sun gear S1, the first gear ring R1 is fixedly connected with the third sun gear S3 through the first connecting piece L1, the third gear ring R3 is fixedly connected with the second sun gear S2 through the second connecting piece L2, and the output shaft OUT is fixedly connected with the second gear ring R2;

The first gear ring R1 is connected with the first brake B1, that is, the first brake B1 can brake the first gear ring R1; The second sun gear S2 is connected with the second brake B2, that is, the second brake B2 can brake the second sun gear S2; the second planetary carrier PC2 is connected with the planetary carrier brake BL3, that is, the planetary carrier brake BL3 can brake the second planetary carrier PC2; The third planetary carrier PC3 is connected with the third brake B3, that is, the third brake B3 can brake the third planetary carrier PC3.

Working principle: ring gear is connected to the sun gear, ring gear is connected to the sun gear, RS-RS type.

The first brake B1 is engaged with the second brake B2 simultaneously, the first gear ring R1 and the second sun gear S2 are fixed respectively, and the first sun gear S1 is fixedly connected with input shaft IN and rotates in the same direction and speed; In the first planetary row P1, the first sun gear S1 inputs power, the first gear ring R1 is fixed, and the first planetary carrier PC1 rotates in the same direction with the input shaft IN; in the second planetary row P2, the second planetary carrier PC2 is fixedly connected with the first planetary carrier PC1 through the planetary carrier connecting shaft L3, the second planetary carrier PC2 input power, the second sun gear S2 is fixed, the second gear ring R2 is fixedly connected with the output shaft OUT, the second gear ring R2 outputs power to the output shaft OUT, and the output shaft OUT and the input shaft IN rotate in the same direction; The power passes through the first planetary row P1, the planetary carrier connecting shaft L3 and the second planetary row P2 in turn, realizes the two-stage transmission, and the direction of rotation of the output power is the same as that of the input power.

The third brake B3 is engaged with the planetary carrier brake BL3 at the same time, the first planetary carrier PC1, the second planetary carrier PC2 and the third planetary carrier PC3 are fixed respectively, and the first sun gear S1 is fixedly connected with the input shaft IN and rotates in the same direction and speed; In the first planetary row P1, the first sun gear S1 inputs power, the first planetary carrier PC1 is fixed, and the first gear ring R1 rotates in the opposite direction with the input shaft IN; The first gear ring R1 is fixedly connected with the third sun gear S3 through the first connecting piece L1, and in the third planetary row P3, the third sun gear S3 input power, the third planet carrier PC3 is fixed, and the third gear ring R3 rotates in the same direction with the input shaft IN; The third gear ring R3 is fixedly connected with the second sun gear S2 through the second connecting piece L2, in the second planetary row P2, the second sun gear S2 input power, the second planet carrier PC2 is fixed, the second gear ring R2 rotates in reverse with the input shaft IN, the second gear ring R2 is fixedly connected with the output shaft OUT, the second gear ring R2 outputs the power to the output shaft OUT, and the output shaft OUT is opposite to the direction of rotation of the input shaft IN; The power passes through the first planetary row P1, the first connecting piece L1, the third planetary row P3, the second connecting piece L2 and the second planetary row P2 in turn, realizes three-stage transmission, and the direction of rotation of output power is opposite to the direction of rotation of input power.

The third brake B3 is individually engaged, the third planetary carrier PC3 is fixed, and the first planetary row P1, the second planetary row P2 and the third planetary row P3 are combined into a planetary row group with two degrees of freedom, and the mixed transmission of two-stage transmission parallel three-stage transmission is realized; The first sun gear S1 is fixedly connected with the input shaft IN and rotates in the same direction and speed; In the first planetary row P1, the first sun gear S1 inputs power, and the power shunt is a two-way transmission, the first road is transmitted in the mode of two-stage transmission through the first planetary carrier PC1, and the second road is transmitted in the mode of three-stage transmission through the first ring gear R1; In the first planetary row P1, the first sun gear S1 will output power to the first planet carrier PC1, the first planet carrier PC1 will output power to the planet carrier connecting shaft L3, in the second planet row P2, the planet carrier connecting shaft L3 will output power to the second planet carrier PC2, and the second planet carrier PC2 power is respectively output to the second gear ring R2 and the second sun gear S2 after the second planet carrier PC2 power is shunted again; The second way transmission, in the first planetary row P1, the first sun gear S1 outputs power to the first gear ring R1 through the first planet wheel CA1, the first gear ring R1 will output power to the first connecting piece L1, in the third planet row P3, the first connecting piece L1 will output power to the third sun gear S3, the third sun gear S3 will output power to the third gear ring R3 through the third planet wheel CA3, the third gear ring R3 will output power to the second connecting piece L2, in the second planet row P2, the second connecting piece L2 outputs power to the second sun gear S2, and the second sun gear S2 outputs the power to the second planetary carrier PC2 and the second gear ring R2 respectively after the power is shunted again; The planetary row group with two degrees of freedom realizes the hybrid transmission of two-stage transmission in parallel and three-stage transmission, and activates one control piece to eliminate another degree of freedom, so as to realize fixed input and output.

Fourth embodiment:

Referring to FIG. 4, a planetary multistage transmission variable speed mechanism comprises input shaft IN, output shaft OUT, the first planetary row P1, the second planetary row P2 and the third planetary row P3;

The input shaft IN is connected with the first planetary row P1; The output shaft OUT is connected with the second planetary row P2;

The first planetary row P1 comprises the first sun gear S1, the first planetary carrier PC1, the first planetary wheel CA1 and the first gear ring R1; the first planetary wheel CA1 is movably mounted on the first planetary carrier PC1, the first gear ring R1 is meshed with the first planetary wheel CA1, and the first planetary wheel CA1 is meshed with the first sun wheel S1;

the second planet row P2 comprises a second sun gear S2, a second planet carrier PC2, a second planet wheel CA2 and a second gear ring R2; the second planet wheel CA2 is movably mounted on the second planet carrier PC2, the second gear ring R2 is meshed with the second planet wheel CA2, and the second planet wheel CA2 is meshed with the second sun wheel S2;

the third planet row P3 comprises the third sun gear S3, the third planet carrier PC3, the third planet wheel CA3 and the third gear ring R3; the third planet wheel CA3 is movably installed on the third planet carrier PC3, the third gear ring R3 is meshed with the third planet wheel CA3, and the third planet wheel CA3 is meshed with the third sun wheel S3;

the first sun gear S1, the second sun gear S2 and the third sun gear S3 are all movably mounted on the planet carrier connecting shaft L3; The first planetary carrier PC1 and the second planetary carrier PC2 are fixedly connected through the planetary carrier connecting shaft L3;

input shaft IN is fixedly connected with first gear ring R1, first sun gear S1 is fixedly connected with third sun gear S3 by first connecting piece L1, third gear ring R3 is fixedly connected with second sun gear S2 by second connecting piece L2, and output shaft OUT is fixedly connected with second gear ring R2;

The first sun gear S1 is connected with the first brake B1, that is, the first brake B1 can brake the first sun wheel S1; The second sun gear S2 is connected with the second brake B2, that is, the second brake B2 can brake the second sun gear S2; the second planetary carrier PC2 is connected with the planetary carrier brake BL3, that is, the planetary carrier brake BL3 can brake the second planetary carrier PC2; The third planetary carrier PC3 is connected with the third brake B3, that is, the third brake B3 can brake the third planetary carrier PC3.

Working principle: the sun gear is connected to the sun gear, and the ring gear is connected to the sun gear, SS-RS type.

The first brake B1 is engaged with the second brake B2 at the same time, the first sun gear S1 and the second sun gear S2 are fixed respectively, and the first gear ring R1 is fixedly connected with input shaft IN and rotates in the same direction and speed; In the first planetary row P1, the first gear ring R1 inputs power, the first sun gear S1 is fixed, and the first planetary carrier PC1 rotates in the same direction with the input shaft IN; in the second planetary row P2, the second planetary carrier PC2 is fixedly connected with the first planetary carrier PC1 through the planetary carrier connecting shaft L3, the second planetary carrier PC2 input power, the second sun gear S2 is fixed, the second gear ring R2 is fixedly connected with the output shaft OUT, the second gear ring R2 outputs power to the output shaft OUT, and the output shaft OUT and the input shaft IN rotate in the same direction; The power passes through the first planetary row P1, the planetary carrier connecting shaft L3 and the second planetary row P2 in turn, realizes the two-stage transmission, and the direction of rotation of the output power is the same as that of the input power.

The third brake B3 is engaged with the planetary carrier brake BL3 simultaneously, the first planetary carrier PC1, the second planetary carrier PC2 and the third planetary carrier PC3 are fixed respectively, and the first gear ring R1 is fixedly connected with the input shaft IN and rotates in the same direction and speed; In the first planetary row P1, the first gear ring R1 inputs power, the first planet carrier PC1 is fixed, and the first sun gear S1 rotates in reverse with input shaft I N; The first sun gear S1 and the third sun gear S3 are fixedly connected through the first connecting piece L1, and in the third planetary row P3, the third sun gear S3 input power, the third planet carrier PC3 is fixed, and the third gear ring R3 rotates in the same direction with input shaft IN; The third gear ring R3 is fixedly connected with the second sun gear S2 through the second connecting piece L2, in the second planetary row P2, the second sun gear S2 input power, the second planet carrier PC2 is fixed, the second gear ring R2 rotates in reverse with the input shaft IN, the second gear ring R2 is fixedly connected with the output shaft OUT, the second gear ring R2 outputs the power to the output shaft OUT, and the output shaft OUT is opposite to the direction of rotation of the input shaft IN; The power passes through the first planetary row P1, the first connecting piece L1, the third planetary row P3, the second connecting piece L2 and the second planetary row P2 in turn, realizes three-stage transmission, and the direction of rotation of output power is opposite to the direction of rotation of input power.

The third brake B3 is individually engaged, the third planetary carrier PC3 is fixed, and the first planetary row P1, the second planetary row P2 and the third planetary row P3 are combined into a planetary row group with two degrees of freedom, and the mixed transmission of two-stage transmission parallel three-stage transmission is realized; The first gear ring R1 is fixedly connected with the input shaft IN and rotates in the same direction and speed; In the first planetary row P1, the first gear ring R1 inputs power, and the power shunt is a two-way transmission, the first is transmitted in the mode of two-stage transmission through the first planetary carrier PC1, and the second is transmitted in the mode of three-stage transmission through the first sun gear S1; In the first planetary row P1, the first gear ring R1 will output power to the first planet carrier PC1, the first planet carrier PC1 will power output to the planet carrier connecting shaft L3, in the second planet row P2, the planet carrier connecting shaft L3 will output power to the second planet carrier PC2, and the second planet carrier PC2 power is respectively output to the second gear ring R2 and the second sun gear S2 after the second planet carrier PC2 power is shunted again; The second way transmission, in the first planetary row P1, the first gear ring R1 outputs power to the first sun gear S1 through the first planet gear CA1, the first sun gear S1 outputs power to the first connecting piece L1, in the third planet row P3, the first connecting piece L1 outputs power to the third sun gear S3, the third sun gear S3 outputs power to the third gear ring R3 through the third planet gear CA3, the third gear ring R3 outputs power to the second connecting piece L2, in the second planet row P2, the second connecting piece L2 outputs power to the second sun gear S2, and the second sun gear S2 outputs the power to the second planetary carrier PC2 and the second gear ring R2 respectively after the power is shunted again; The planetary row group with two degrees of freedom realizes the hybrid transmission of two-stage transmission in parallel and three-stage transmission, and activates one control piece to eliminate another degree of freedom, so as to realize fixed input and output.

In the above four embodiments, n1 planetary rows are arranged in parallel on the input shaft IN to form the first planetary row group PZ1; n2 planetary rows are arranged in parallel on the output shaft OUT to form a second planetary row group PZ2; Each of the two planetary rows is equipped with a corresponding brake.

The n1 planetary rows in the first planetary row group PZ1 and the n2 planetary rows in the second planetary row group PZ2 are combined in pairs, and there are n1×n2 combinations, and a pair of brakes on the planetary rows on each combination of n1×n2 combinations brake at the same time, can realize a two-stage transmission, and the rotation direction of power output is the same as the rotation direction of power input, and n1×n2 two-stage transmissions can be realized.

After braking the third brake B3 that is arranged on the third planetary row P3, realize a planetary row group with two degrees of freedom that is made up of the first planetary row P1, the second planetary row P2 and the third planetary row P3, the n1 planetary row on the first planetary row group PZ1, after braking sequentially with the brake that is arranged on the n2 planetary rows on the second planetary row group PZ2, another degree of freedom can be eliminated, the fixed input and output are realized, and the rotation direction of power output is the same as the rotation direction of power input, and n1+ can be realizedn2 two-stage transmissions, parallel three-stage transmissions, mixed transmissions; The third planet row P3 and the first planet row P1, the second planet row P2 with the connection relationship are combined separately, and there are two combinations in total, and the brakes that are arranged on a pair of planetary rows on each combination brake at the same time, only realize the first gear ring R1 (or the first sun gear S1) and the second gear ring R2 (or the second sun gear S2) brake a kind of two-stage transmission result simultaneously, and finally realize (n1-1) + (n2-1) mixed transmission gears with actual transmission efficiency, The direction of rotation of the power take-off is the same as that of the power input.

The third brake B3 is connected with the planetary carrier brake BL3 at the same time, and the power passes through the first planetary row P1, the first connecting piece L1, the third planetary row P3, the second connecting piece L2 and the second planetary row P2 in turn, realizes a three-stage transmission, and the output power rotation direction is opposite to the input power rotation direction, and realizes 1 gear.

The planetary multi-stage transmission transmission mechanism is applied to two planetary rows, and the forward gears in the same direction as the power input steering can be n1×n2+(n1-1)+(n2-1), and the number of backward gears in the opposite direction of the power input steering is 1.

The above-mentioned planetary multi-stage transmission transmission mechanism is an application demonstration of the number of planetary rows n1=1 of the first planetary row group PZ1 and the planetary row number n2=1 of the second planetary row group PZ2.

In addition, in the above embodiment, two power flow directions are allowed: first, power flows in from the input shaft N and flows out from the output shaft OUT; In the second case, it flows in from the output shaft OUT and out from the input shaft N .

Brakes such as the first brake B1, the second brake B2, the third brake B3 and the planetary carrier brake BL3 are all friction type control structures.

Fifth embodiment:

Referring to Fig. 5, a planetary type multi-stage transmission transmission mechanism, applying the first embodiment, on the basis of the first embodiment, the fifth planetary row P5, the fourth planetary row P4 and the sixth planetary row P6 are added; Arrangement: the fifth planet row P5, the first planet row P1, the third planet row P3, the second planet row P2, the fourth planet row P4 and the sixth planet row P6 are distributed in sequence;

The fifth planetary row P5 comprises the fifth sun gear S5, the fifth planetary carrier PC5, the fifth planetary wheel CA5 and the fifth ring gear R5, the fifth planet wheel CA5 is movably installed on the fifth planet carrier PC5, the fifth ring gear R5 is meshed with the fifth planet wheel CA5, the fifth planetary wheel CA5 is meshed with the fifth sun gear S5, and the fifth ring gear R5 realizes braking through the fifth brake B5.

The first planetary row P1 comprises the first sun gear S1, the first planetary carrier PC1, the first planetary wheel CA1 and the first ring gear R1, the first planet wheel CA1 is movably mounted on the first planet carrier PC1, the first ring gear R1 is meshed with the first planet wheel CA1, the first planetary wheel CA1 is meshed with the first sun wheel S1, and the first ring gear R1 realizes braking through the first brake B1.

The third planet row P3 comprises the third sun gear S3, the third planet carrier PC3, the third planet wheel CA3 and the third gear ring R3, the third planet wheel CA3 is movably installed on the third planet carrier PC3, the third gear ring R3 is meshed with the third planet wheel CA3, the third planet gear CA3 is meshed with the third sun gear S3, the third sun gear S3 is movably installed on the planet carrier connecting shaft L3, and the third planet carrier PC3 realizes braking through the third brake B3.

The second planet row P2 comprises the second sun gear S2, the second planet carrier PC2, the second planet wheel CA2 and the second ring gear R2, the second planet wheel CA2 is movably installed on the second planet carrier PC2, the second ring gear R2 is meshed with the second planet wheel CA2, the second planet wheel CA2 is meshed with the second sun gear S2, and the second ring gear R2 realizes braking through the second brake B2.

The fourth planet row P4 comprises the fourth sun gear S4, the fourth planet carrier PC4, the fourth planet wheel CA4 and the fourth gear ring R4, the fourth planet wheel CA4 is movably installed on the fourth planet carrier PC4, the fourth gear ring R4 is meshed with the fourth planet wheel CA4, the fourth planet wheel CA4 is meshed with the fourth sun wheel S4, and the fourth gear ring R4 realizes braking through the fourth brake B4.

The sixth planet row P6 comprises the sixth sun gear S6, the sixth planet carrier PC6, the sixth planet wheel CA6 and the sixth gear ring R6, the sixth planet wheel CA6 is movably installed on the sixth planet carrier PC6, the sixth gear ring R6 is meshed with the sixth planet wheel CA6, the sixth planetary wheel CA6 is meshed with the sixth sun wheel S6, and the sixth gear ring R6 realizes braking through the sixth brake B6.

The fifth sun gear S5, the first sun gear S1 are fixedly connected with input shaft N N, and the fifth planetary carrier PC5 is fixedly connected with the first planetary carrier PC1; The fifth planet carrier PC5 is provided with planet carrier brake BL3; The planetary carrier brake BL3 can brake the fifth planetary carrier PC5.

The second sun gear S2, the fourth sun gear S4, the sixth sun gear S6 are fixedly connected with the output shaft OUT; The second gear ring R2 is fixedly connected with the fourth planetary carrier PC4 through the fourth connecting piece L4, and the fourth planetary carrier PC4 is fixedly connected with the sixth planetary carrier PC6.

optional, input shaft N, the fifth sun gear S5, the first sun gear S1, the third sun gear S3, the second sun gear S2, the fourth sun gear S4, the sixth sun gear S6 and the output shaft OUT coaxial arrangement; Power flow direction: Power flows in from the input shaft N and out from the output shaft OUT.

The fifth planetary row P5 and the first planetary row P1 constitute the first planetary array PZ1, the number of planetary rows n1=2, the second planetary row P2, the fourth planetary row P4 and the sixth planetary row P6 constitute the second planetary row group PZ2, and the number of planetary rows n2=3; The number of forward gears is n1×n2 + (n1-1) + (n2-1) = 2×3 + (2-1) + (3-1) = 9, and the number of backward gears is 1;

The 3rd brake B3 and the 4th brake B4 are engaged at the same time, and the forward one gear is realized;

The third brake B3 and the sixth brake B6 are engaged at the same time to realize the forward second gear;

The first brake B1 and the fourth brake B4 are engaged at the same time to realize three forward gears;

The first brake B1 and the sixth brake B6 are engaged at the same time, and realize four forward gears;

The fifth brake B5 and the fourth brake B4 are engaged at the same time to realize five forward gears;

The fifth brake B5 and the sixth brake B6 are engaged at the same time to realize the forward six gears;

The first brake B1 and the second brake B2 are engaged at the same time, and realize the forward seven gears;

The fifth brake B5 is engaged with the second brake B2 at the same time, and realizes eight forward gears;

The fifth brake B5 and the third brake B3 are engaged at the same time to realize the forward nine gears;

The planetary carrier brake BL3 and the third brake B3 are engaged at the same time to achieve a backward gear.

The relevant calculation formula is shown in Table 1.1, and the control logic and transmission of each gear are shown in Table 1.2.

Table 1.1 Calculation formula for each gear:

The ratio of the number of teeth of the first ring gear R1 of the first planetary row P1 to the number of teeth of the first sun gear S1 is K1, and the ratio of the number of teeth of the first planetary row P1 to the sixth planetary row P6 is K1 to K6; When K1=5, K2=6, K3=K4=K5=3, K6=6 in Table 1.1, the input speed is 1, and the transmission ratio of each gear shown in Table 1.1 can be obtained, and the transmission mechanism of nine gears forward and one gear backward is realized.

As shown in Table 1.1, the calculation formula also reveals how the planetary row with two degrees of freedom composed of the first planetary row P1, the second planetary row P2 and the third planetary row P3 when the third brake B3 brakes brakes and expands the transmission ratio range. F1 gear control part B3-B4 combination, compared with the F3 gear control part B1-B4 combination speed formula, the denominator has an additional coefficient (K2+1) composed of K1, K2, K3 ×K1×K3, thereby reducing the speed and increasing the transmission ratio; Compared with the B1-B6 combination speed formula of F4 gear control parts, the same denominator has an additional coefficient (K2+1) composed of K1, K2 and K3 ×K1×K3, thereby reducing the speed and increasing the transmission ratio; F9 gear control part B5-B3 combination, compared with the F8 gear control part B5-B2 combination speed formula, has an additional coefficient [(K1+1)/(K5+1)-1]×K2/K1/K3 composed of K1, K2, K3 and K5, when K1>K5, the coefficient is positive, thereby increasing the speed and reducing the transmission ratio; On the other hand, in order to avoid circulating power, the value of K1 needs to be set to be greater than K5, when the fifth brake B5 brakes, the steering of the first gear ring R1 is the same as the first planetary carrier PC1 steering, and when the third brake B3 is braking, the steering when the power is output to the second gear ring R2 through the first gear ring R1, the first connecting piece L1, the third sun gear S3, the third ring gear R3, the second connecting piece L2 is different from the rotation direction of the second planetary carrier PC2, In addition, the cyclic power occurs when the second gear ring R2 and the second planetary carrier PC2 jointly output power.

Table 1.2 Control logic and transmission ratio of each gear (O indicates the engagement of the control part)

The examples of the present invention are described in detail below in conjunction with Figure 5 and Table 1.2, and the transmission ratio refers to the ratio of the speed of the input shaft to the speed of the output shaft.

The 3rd brake B3 is engaged with the 4th brake B4 simultaneously, the 3rd planet carrier PC3 and the 4th gear ring R4 are fixed respectively, and the first sun gear S1 is fixedly connected with input shaft I N, and rotates in the same direction and speed; In the first planetary row P1, the first sun gear S1 inputs power, and the power shunt is a two-way transmission, the first road is transmitted in the mode of two-stage transmission through the first planetary carrier PC1, and the second road is transmitted in the mode of three-stage transmission through the first ring gear R1; In the first planetary row P1, the first sun gear S1 will output power to the first planet carrier PC1, the first planet carrier PC1 will output power to the planet carrier connecting shaft L3, in the second planet row P2, the planet carrier connecting shaft L3 will output power to the second planet carrier PC2, and the second planet carrier PC2 power is respectively output to the second gear ring R2 and the second sun gear S2 after the second planet carrier PC2 power is shunted again; The second way transmission, in the first planetary row P1, the first sun gear S1 outputs power to the first gear ring R1 through the first planet wheel CA1, the first gear ring R1 will output power to the first connecting piece L1, in the third planet row P3, the first connecting piece L1 will output power to the third sun gear S3, the third sun gear S3 will output power to the third gear ring R3 through the third planet wheel CA3, the third gear ring R3 will output power to the second connecting piece L2, in the second planet row P2, the second connecting piece L2 outputs power to the second ring gear R2, the second ring gear R2 is fixedly connected with the fourth planetary carrier PC4 through the fourth connecting piece L4, and the second ring gear R2 power is respectively output to the second planetary carrier PC2, the second sun gear S2 and the fourth planetary carrier PC4 after the power is shunted again; The output shaft OUT is a rigid structure, because the fourth gear ring R4 is fixed, the speed ratio of the fourth planetary carrier PC4 and the fourth sun gear S4 is determined, another degree of freedom of the planetary row group has been limited, and finally the second planetary carrier PC2, the second ring gear R2, the fourth planetary carrier PC4 jointly output power to the output shaft OUT through the second sun gear S2 and the fourth sun gear S4, and realize the forward first gear.

The 3rd brake B3 is engaged with the 6th brake B6 at the same time, the 3rd planetary carrier PC3 and the 6th gear ring R6 are fixed respectively, and the first sun gear S1 is fixedly connected with the input shaft I N, and rotates in the same direction and speed; In the first planetary row P1, the first sun gear S1 inputs power, and the power shunt is a two-way transmission, the first road is transmitted in the mode of two-stage transmission through the first planetary carrier PC1, and the second road is transmitted in the mode of three-stage transmission through the first ring gear R1; In the first planetary row P1, the first sun gear S1 will output power to the first planet carrier PC1, the first planet carrier PC1 will output power to the planet carrier connecting shaft L3, in the second planet row P2, the planet carrier connecting shaft L3 will output power to the second planet carrier PC2, and the second planet carrier PC2 power is respectively output to the second gear ring R2 and the second sun gear S2 after the second planet carrier PC2 power is shunted again; The second way transmission, in the first planetary row P1, the first sun gear S1 outputs power to the first gear ring R1 through the first planet wheel CA1, the first gear ring R1 will output power to the first connecting piece L1, in the third planet row P3, the first connecting piece L1 will output power to the third sun gear S3, the third sun gear S3 will output power to the third gear ring R3 through the third planet wheel CA3, the third gear ring R3 will output power to the second connecting piece L2, in the second planet row P2, the second connecting piece L2 outputs power to the second gear ring R2, the second gear ring R2 is fixedly connected with the fourth planetary carrier PC4 and the sixth planetary carrier PC6 through the fourth connecting piece L4, and the second gear ring R2 power is output to the second planetary carrier PC2, the second sun gear S2 and the sixth planetary carrier PC6 respectively after the second gear ring R2 power is shunted again; The output shaft OUT is a rigid structure, because the sixth gear ring R6 is fixed, the speed ratio of the sixth planetary carrier PC6 and the sixth sun gear S6 is determined, another degree of freedom of the planetary row group has been limited, and finally the second planetary carrier PC2, the second ring gear R2, the sixth planetary carrier PC6 jointly output power to the output shaft OUT through the second sun gear S2 and the sixth sun gear S6, and realize the forward second gear.

The first brake B1 is engaged with the 4th brake B4 simultaneously, the first gear ring R1 and the 4th gear ring R4 are fixed respectively, and the first sun gear S1 is fixedly connected with input shaft I N, and rotates in the same direction and speed; In the first planetary row P1, the first sun gear S1 inputs power, and because the first gear ring R1 is fixed, the first planetary carrier PC1 rotates in the same direction with the input shaft I N; The first planetary carrier PC1 is fixedly connected by the planetary carrier connecting shaft L3 and the second planetary carrier PC2, in the second planetary row P2, the second planetary carrier PC2 input power, the second sun gear S2 and the second gear ring R2 output power, and the second sun gear S2 is fixedly connected with the output shaft OUT, and the output shaft is driven to rotate; the second gear ring R2 is fixedly connected with the fourth planetary carrier PC4 through the fourth connecting piece L4, and the second gear ring R2 drives the fourth planetary carrier PC4 to rotate; In the fourth planetary row P4, the fourth gear ring R4 is fixed, and the fourth sun gear S4 outputs power; The output shaft OUT is a rigid structure, and finally the second sun gear S2 and the fourth sun gear S4 jointly output power to the output shaft OUT to achieve three forward gears.

The first brake B1 is engaged with the sixth brake B6 at the same time, the first gear ring R1 and the sixth gear ring R6 are fixed respectively, and the first sun gear S1 is fixedly connected with input shaft I N, and rotates in the same direction and speed; In the first planetary row P1, the first sun gear S1 inputs power, and because the first gear ring R1 is fixed, the first planetary carrier PC1 rotates in the same direction with the input shaft I N; The first planetary carrier PC1 is fixedly connected by the planetary carrier connecting shaft L3 and the second planetary carrier PC2, in the second planetary row P2, the second planetary carrier PC2 input power, the second sun gear S2 and the second gear ring R2 output power, and the second sun gear S2 is fixedly connected with the output shaft OUT, and the output shaft is driven to rotate; the second gear ring R2 is fixedly connected with the fourth planetary carrier PC4 and the sixth planetary carrier PC6 through the fourth connecting piece L4, and the second gear ring R2 drives the sixth planetary carrier PC6 to rotate; In the sixth planetary row P6, the sixth gear ring R6 is fixed, and the sixth sun gear S6 outputs power; The output shaft OUT is a rigid structure, and finally the second sun gear S2 and the sixth sun gear S6 jointly output power to the output shaft OUT to achieve four forward gears.

The fifth brake B5 is engaged with the fourth brake B4 simultaneously, the fifth gear ring R5 and the fourth gear ring R4 are fixed respectively, and the fifth sun gear S5 is fixedly connected with input shaft I N, and rotates in the same direction and speed; In the fifth planetary row P5, the fifth sun gear S5 input power, because the fifth gear ring R5 is fixed, the fifth planetary carrier PC5 is fixedly connected with the first planetary carrier PC1, and the first planetary carrier PC1 rotates in the same direction with the input shaft IN; The first planetary carrier PC1 is fixedly connected by the planetary carrier connecting shaft L3 and the second planetary carrier PC2, in the second planetary row P2, the second planetary carrier PC2 input power, the second sun gear S2 and the second gear ring R2 output power, and the second sun gear S2 is fixedly connected with the output shaft OUT, and the output shaft is driven to rotate; the second gear ring R2 is fixedly connected with the fourth planetary carrier PC4 through the fourth connecting piece L4, and the second gear ring R2 drives the fourth planetary carrier PC4 to rotate; In the fourth planetary row P4, the fourth gear ring R4 is fixed, and the fourth sun gear S4 outputs power; The output shaft OUT is a rigid structure, and finally the second sun gear S2 and the fourth sun gear S4 jointly output power to the output shaft OUT to achieve five forward gears.

The 5th brake B5 and the 6th brake B6 are engaged simultaneously, the 5th gear ring R5 and the 6th gear ring R6 are fixed respectively, and the 5th sun gear S5 is fixedly connected with input shaft I N, and rotates in the same direction and speed; In the fifth planetary row P5, the fifth sun gear S5 input power, because the fifth gear ring R5 is fixed, the fifth planetary carrier PC5 is fixedly connected with the first planetary carrier PC1, and the first planetary carrier PC1 rotates in the same direction with the input shaft IN; The first planetary carrier PC1 is fixedly connected by the planetary carrier connecting shaft L3 and the second planetary carrier PC2, in the second planetary row P2, the second planetary carrier PC2 input power, the second sun gear S2 and the second gear ring R2 output power, and the second sun gear S2 is fixedly connected with the output shaft OUT, and the output shaft is driven to rotate; the second gear ring R2 is fixedly connected with the fourth planetary carrier PC4 and the sixth planetary carrier PC6 through the fourth connecting piece L4, and the second gear ring R2 drives the sixth planetary carrier PC6 to rotate; In the sixth planetary row P6, the sixth gear ring R6 is fixed, and the sixth sun gear S6 outputs power; The output shaft OUT is a rigid structure, and finally the second sun gear S2 and the sixth sun gear S6 jointly output power to the output shaft OUT to achieve six forward gears.

The first brake B1 is engaged with the second brake B2 at the same time, the first gear ring R1 and the second gear ring R2 are fixed respectively, and the first sun gear S1 is fixedly connected with input shaft N, and rotates in the same direction and speed; In the first planetary row P1, the first sun gear S1 inputs power, and because the first gear ring R1 is fixed, the first planetary carrier PC1 rotates in the same direction with the input shaft I N; The first planetary carrier PC1 is fixedly connected by the planetary carrier connecting shaft L3 and the second planetary carrier PC2, in the second planetary row P2, the second planetary carrier PC2 inputs power, the second gear ring R2 is fixed, and the second sun gear S2 outputs power to the output shaft OUT, realizes forward seven gears.

The fifth brake B5 is engaged with the second brake B2 simultaneously, the fifth gear ring R5 and the second gear ring R2 are fixed respectively, and the fifth sun gear S5 is fixedly connected with input shaft I N, and rotates in the same direction and speed; In the fifth planetary row P5, the fifth sun gear S5 input power, because the fifth gear ring R5 is fixed, the fifth planetary carrier PC5 is fixedly connected with the first planetary carrier PC1, and the first planetary carrier PC1 rotates in the same direction with the input shaft IN; The first planetary carrier PC1 is fixedly connected by the planetary carrier connecting shaft L3 and the second planetary carrier PC2, in the second planetary row P2, the second planetary carrier PC2 inputs power, the second gear ring R2 is fixed, and the second sun gear S2 outputs power to the output shaft OUT, and realizes eight forward gears.

The 5th brake B5 is engaged with the 3rd brake B3 simultaneously, the 5th gear ring R5 and the 3rd planet carrier PC3 are fixed respectively, and the 5th sun gear S5 is fixedly connected with input shaft I N, and rotates in the same direction and speed; In the fifth planetary row P5, the fifth sun gear S5 input power, because the fifth gear ring R5 is fixed, the fifth planetary carrier PC5 speed is determined, and rotates in the same direction with the input shaft IN; In the first planetary row P1, the first sun gear S1 inputs power, and the power shunt is a two-way transmission, the first road is transmitted in the mode of two-stage transmission through the first planetary carrier PC1, and the second road is transmitted in the mode of three-stage transmission through the first ring gear R1; In the first planetary row P1, the first sun gear S1 will output power to the first planet carrier PC1, the first planet carrier PC1 will output power to the planet carrier connecting shaft L3, in the second planet row P2, the planet carrier connecting shaft L3 will output power to the second planet carrier PC2, and the second planet carrier PC2 power is respectively output to the second gear ring R2 and the second sun gear S2 after the second planet carrier PC2 power is shunted again; The second way transmission, in the first planetary row P1, the first sun gear S1 outputs power to the first gear ring R1 through the first planet wheel CA1, the first gear ring R1 will output power to the first connecting piece L1, in the third planet row P3, the first connecting piece L1 will output power to the third sun gear S3, the third sun gear S3 will output power to the third gear ring R3 through the third planet wheel CA3, the third gear ring R3 will output power to the second connecting piece L2, in the second planet row P2, the second connecting piece L2 outputs power to the second gear ring R2, and the second gear ring R2 power is output to the second planetary carrier PC2 and the second sun gear S2 respectively after the second gear R2 power is shunted again; Because the fifth gear ring R5 is fixed, the speed of the fifth planetary carrier PC5 is determined, another degree of freedom of the planetary row group has been limited, and finally the second planetary carrier PC2 and the second gear ring R2 jointly output power to the output shaft OUT through the second sun gear S2, and realize the forward nine gears.

Planetary carrier brake BL3 is engaged with the third brake B3 simultaneously, the fifth planetary carrier PC5, the first planetary carrier PC1, the second planetary carrier PC2 and the third planetary carrier PC3 are fixed respectively, and the first sun gear S1 is fixedly connected with input shaft I N, and rotates in the same direction and speed; In the first planetary row P1, the first sun gear S1 inputs power, the first planetary carrier PC1 is fixed, and the first gear ring R1 rotates in the opposite direction with the input shaft IN; The first gear ring R1 is fixedly connected with the third sun gear S3 through the first connecting piece L1, and in the third planetary row P3, the third sun gear S3 input power, the third planet carrier PC3 is fixed, and the third gear ring R3 rotates in the same direction with the input shaft IN; The third gear ring R3 is fixedly connected with the second gear ring R2 through the second connecting piece L2, in the second planetary row P2, the second gear ring R2 input power, the second planet carrier PC2 is fixed, the second sun gear S2 and the input shaft IN rotate in the opposite direction, the second sun gear S2 is fixedly connected with the output shaft OUT, and the second sun gear S2 outputs power to the output shaft OUT, and realizes a backward gear.

The transmission ratio of each gear is determined by the K value of the six planetary rows, and the K value of the planetary row refers to the ratio of the number of ring gear teeth of the planetary row to the number of sun gear teeth, for example, when K1=5, K2=6, K3=K4=K5=3, K6=6, The transmission ratio of each gear shown in Table 1.1 can be obtained, and the transmission mechanism of nine gears forward and one gear backward is realized, and the speed ratio of one gear is greater than 5, which can reduce the load of the torque converter when the vehicle is at low speed, improve the reliability of the torque converter, and at the same time, the large speed ratio can make the engine run more in the economic working area, and improve the economy of the whole machine.

From the shift logic of each gear in Table 1.2, it can be seen that each gear is controlled by manipulating two elements, which can reduce the slippery work and heat loss of the friction plate, and improve the reliability of the friction plate.

Optionally, the ratio of the number of teeth of the first gear ring R1 to the number of teeth of the first sun gear S1 is 5. The ratio of the number of teeth of the second ring gear R2 to the number of teeth of the second sun gear S2 is 6. The ratio of the number of teeth of the third gear ring R3 to the number of teeth of the third sun gear S3 is 3. The ratio of the number of teeth of the fourth gear ring R4 to the number of teeth of the fourth sun gear S4 is 3. The ratio of the number of teeth of the fifth ring gear R5 to the number of teeth of the fifth sun gear S5 is 3. The ratio of the number of teeth of the sixth gear ring R6 to the number of teeth of the sixth sun gear S6 is 6.

Optional, the ratio of the forward first gear is 5.89, the ratio of the forward second gear is 3.73, the ratio of the forward third gear is 2.14, the ratio of the forward four gears is 1.59, the ratio of the forward five gears is 1.43, the ratio of the forward six gears is 1.06, the ratio of the forward seven gears is 0.86, the ratio of the forward eight gears is 0.57, the ratio of the forward nine gears is 0.51, and the ratio of the backward first gear is 2.50.

Optional, The step ratio of the forward first gear to the forward second gear is 1.58, the step ratio of the forward second gear to the forward third gear is 1.74, the step ratio of the forward third gear to the forward fourth gear is 1.35, the step ratio of the forward four gear to the forward fifth gear is 1.11, the step ratio of the forward five gear to the forward six gear is 1.35, the step ratio of the forward six gear to the forward seven gear is 1.24, the step ratio of the forward seven gear to the forward eight gear is 1.50, the step ratio of the forward eight gear and the forward nine gear is 1.11, and the transmission ratio range of the highest gear and the lowest gear is 11.49.

The embodiment discloses a planetary multistage transmission transmission mechanism for vehicle transmission system, as shown in Figure 5, comprises an input shaft IN, an output shaft OUT, six planetary rows (P1~P6), seven brakes (BL3, B1~B6), and four connectors (L1~L4).

Each planetary row includes: sun gear (S1~S6), planet carrier (PC1~PC6), planetary wheel (CA1~CA6) and ring gear (R1~R6); The ring gear is coaxially distributed with the sun gear, and the planetary wheel is installed on the planetary carrier through the planetary shaft and the bearing respectively, and each planetary wheel is meshed with the ring gear on the counter star row and meshed with the sun wheel on the peer star row.

The six planetary rows are arranged side by side from left to right, and the six sun gears, input shaft I N and output shaft OUT are coaxially arranged.

In the present application, the vehicle transmission system is used for planetary multi-stage transmission transmission mechanism, comprising six planetary rows, seven brakes, and the planetary rows are all single planetary simple planetary rows, and the highest can realize nine forward gears and one backward gear, and the forward one gear transmission ratio is greater than 5, and the gear is many, the transmission ratio range is large, and the step ratio is small and uniform, so that the engine can run more in the economic working area, and the whole machine economy is improved. The seven brakes, all of which are friction-controlled structures, and control the gear through two-element operation, can reduce the slippery work and heat loss of the friction plate, and improve the reliability of the friction plate.

Sixth embodiment:

As shown in Fig. 6, a planetary type multi-stage transmission transmission mechanism, the second embodiment is applied, and structures such as double clutch C1 and motor MG are added on the basis of the second embodiment.

This transmission transmission mechanism comprises input shaft IN, double clutch C1, motor MG, the first planetary row P1, the third planetary row P3, the second planetary row P2 and the output shaft OUT;

input shaft IN is fixedly connected with double clutch C1, the first group of clutches C11 on double clutch C1 is fixedly connected with the 4th connecting piece L4, the 4th connecting piece L4 is provided with the 4th brake B4, the 4th connecting piece L4 is provided with the first planetary row P1, and the first sun gear S1 is fixedly connected with the 4th connecting piece L4; The second planetary row P2 is arranged on the output shaft OUT, and the second gear ring R2 is fixedly connected with the output shaft OUT;

The dual clutch C1 comprises the first group of clutches C11 and the second group of clutches C12; The second group of clutches C12 is provided with the first driving gear G11, and the first driving gear G11 is fixedly connected with the second group of clutches C12; Parallel setting motor MG, the main shaft of motor MG is parallel to input shaft N, one end of motor MG is connected with the second group of clutches C12, the other end is connected with the first gear ring R1, and the first driven gear G12 is fixedly mounted on motor MG and is meshed with the first driving gear G11; The second driven gear G22 is fixedly connected with the first gear ring R1, and the second driving gear G21 is fixedly mounted on the motor MG and is meshed with the second driven gear G22.

The first planetary row P1 comprises a first sun gear S1, a first planetary carrier PC1, a first planet wheel CA1 and a first ring gear R1, the first planet wheel CA1 is movably mounted on the first planet carrier PC1, the first ring gear R1 is meshed with the first planet wheel CA1, the first planet wheel CA1 is meshed with the first sun wheel S1, the first gear ring R1 realizes braking through the first brake B1, and the first sun gear S1 realizes braking through the fourth brake B4;

The third planet row P3 comprises the third sun gear S3, the third planet carrier PC3, the third planet wheel CA3 and the third gear ring R3, the third planet wheel CA3 is movably arranged on the third planet carrier PC3, the third gear ring R3 is meshed with the third planet wheel CA3, the third planet gear CA3 is meshed with the third sun wheel S3, the third sun gear S3 is movably installed on the planet carrier connecting shaft L3, and the third planet carrier PC3 realizes braking through the third brake B3;

The second planet row P2 comprises a second sun gear S2, a second planet carrier PC2, a second planet wheel CA2 and a second ring gear R2, the second planet wheel CA2 is movably arranged on the second planet carrier PC2, the second ring gear R2 is meshed with the second planet wheel CA2, the second planet gear CA2 is meshed with the second sun gear S2, the second sun gear S2 is movably mounted on the planet carrier connecting shaft L3, and the second sun gear S2 realizes braking through the second brake B2, the second planetary carrier PC2 is provided with a planetary carrier brake BL3 to realize braking;

The first group of clutches C11 and the first sun gear S1 are fixedly connected by the fourth connecting piece L4, the fourth connecting piece L4 is connected with the fourth brake B4, the fourth connecting piece L4 is fixedly connected with the first sun gear S1, and the first sun gear S1 realizes braking through the fourth brake B4.

Optional, double clutch C1, input shaft IN, first sun gear S1, third sun gear S3, second sun gear S2 and output shaft OUT coaxial arrangement; Motor MG and input shaft IN parallel shaft arrangement; Power flow direction: Power flows in from the input shaft N and out from the output shaft OUT.

The internal combustion engine power is driven separately and can achieve six forward and one reverse gears. The details are as follows:

The first group of clutches C11 is engaged, and the first brake B1 and the second brake B2 are engaged at the same time, and the forward first gear is realized;

the second group of clutches C12 is engaged, and the third brake B3 is engaged with the planetary carrier brake BL3 at the same time, and the forward second gear is realized;

The second group of clutches C12 is engaged, and the second brake B2 and the fourth brake B4 are engaged simultaneously to realize three forward gears;

The first group of clutches C11 and the second group of clutches C12 are engaged at the same time, and the second brake B2 is engaged to realize four forward gears;

The second group of clutches C12 is engaged, and the third brake B3 and the fourth brake B4 are engaged at the same time, and the forward five gears are realized;

The first group of clutches C11 and the second group of clutches C12 are engaged at the same time, and the third brake B3 is engaged to achieve six forward gears;

The first group of clutches C11 is engaged, and the third brake B3 is engaged at the same time with the planetary carrier brake BL3 to achieve a backward first gear.

The motor power can be driven separately to achieve three forward gears, and the motor reversal can achieve three reverse gears of the same gear. The details are as follows:

The third brake B3 is engaged with the planetary carrier brake BL3 at the same time to realize the forward first gear;

The second brake B2 and the fourth brake B4 are engaged at the same time to realize the forward second gear;

The third brake B3 and the fourth brake B4 are engaged at the same time to realize the forward three gears.

The relevant calculation formulas are shown in Table 2.1 and Table 3.1, and the control logic and transmission of each gear are shown in Table 2.2 and Table 3.2.

Table 2.1 Calculation formula for each gear of the internal combustion engine power driven separately

Planetary row K value refers to the ratio of the number of ring gear teeth of planetary row to the number of sun gear teeth, K1 = 6, K2 = 4, K3 = 3 in the above table, the transmission ratio KG1 = 0.4 of gear set G11: G12, and the transmission ratio KG2 = 4 of gear set G21: G22, when the input speed is 1, the transmission ratio of each gear shown in Table 2.1 can be obtained, and the transmission mechanism of six gears forward and one gear backward is realized.

Table 2.2 Internal combustion engine power is driven separately to control the control logic and transmission ratio of each gear (O indicates the engagement of the control parts)

The following is described in detail in conjunction with Figure 6 and Table 2.2 of the present invention internal combustion engine power separate drive example, and the transmission ratio refers to the ratio of input shaft speed to output shaft speed.

The first group of clutches C11 is engaged, the first brake B1 is engaged with the second brake B2 simultaneously, the first gear ring R1 and the second sun gear S2 are fixed respectively, the first sun gear S1 is fixedly connected with the fourth connecting piece L4, is fixedly connected with input shaft N by the first group of clutches C11, rotates in the same direction and at the same speed; In the first planetary row P1, the first sun gear S1 inputs power, and because the first gear ring R1 is fixed, the first planetary carrier PC1 rotates in the same direction with the input shaft I N; The first planetary carrier PC1 is fixedly connected by the planetary carrier connecting shaft L3 and the second planetary carrier PC2, in the second planetary row P2, the second planetary carrier PC2 inputs power, the second sun gear S2 is fixed, and the second gear ring R2 outputs power to the output shaft OUT, and realizes the forward first gear.

the second group of clutches C12 is engaged, and the third brake B3 is engaged with the planetary carrier brake BL3 at the same time, and the first planetary carrier PC1, the second planetary carrier PC2 and the third planetary carrier PC3 are fixed respectively; The first driving gear G11 is fixedly connected with the second group of clutches C12, and is fixedly connected with input shaft I N by the second group of clutches C12, and rotates in the same direction and speed; The first driven gear G12 is fixedly mounted on the motor MG and is meshed with the first driving gear G11, and is opposite to the direction of rotation of input shaft N; the second driven gear G22 is fixedly connected with the first gear ring R1, and the second driving gear G21 is fixedly mounted on the motor MG and is meshed with the second driven gear G22, and the rotation direction of the second driven gear G22 is the same as that of input shaft IN; The second driven gear G22 is fixedly connected with the first gear ring R1, and the first gear ring R1 rotates in the same direction with input shaft IN; The first gear ring R1 is fixedly connected with the third gear ring R3 through the first connecting piece L1, and in the third planetary row P3, the third gear ring R3 input power, the third planet carrier PC3 is fixed, and the third sun gear S3 rotates in reverse with input shaft IN; The third sun gear S3 and the second sun gear S2 are fixedly connected through the second connecting piece L2, in the second planetary row P2, the second sun gear S2 input power, the second planetary carrier PC2 is fixed, the second gear ring R2 rotates in the same direction with the input shaft IN, the second gear ring R2 is fixedly connected with the output shaft OUT, and the second gear ring R2 outputs power to the output shaft OUT, and realizes the forward second gear.

the second group of clutches C12 is engaged, and the 4th brake B4 is engaged with the 2nd brake B2 simultaneously, and the first sun gear S1 and the second sun gear S2 are fixed respectively; The first driving gear G11 is fixedly connected with the second group of clutches C12, and is fixedly connected with the input shaft IN through the second group of clutches C12, and rotates in the same direction and speed; The first driven gear G12 is fixedly mounted on the motor MG and is meshed with the first driving gear G11 and is opposite to the direction of rotation of input shaft IN; the second driven gear G22 is fixedly connected with the first gear ring R1, and the second driving gear G21 is fixedly mounted on the motor MG and is meshed with the second driven gear G22, and the rotation direction of the second driven gear G22 is the same as that of input shaft IN; The second driven gear G22 is fixedly connected with the first gear ring R1, and the first gear ring R1 rotates in the same direction with input shaft IN; In the first planetary row P1, the first gear ring R1 inputs power, and because the first sun gear S1 is fixed, the first planetary carrier PC1 rotates in the same direction with the input shaft I N; The first planetary carrier PC1 is fixedly connected by the planetary carrier connecting shaft L3 and the second planetary carrier PC2, in the second planetary row P2, the second planetary carrier PC2 input power, the second sun gear S2 is fixed, the second gear ring R2 rotates in the same direction with the input shaft IN, and the second gear ring R2 outputs power to the output shaft OUT, and realizes three forward gears.

The first group of clutches C11 and the second group of clutches C12 are engaged at the same time, and the second brake B2 is engaged, and the second sun gear S2 is fixed; The first sun gear S1 is fixedly connected with the fourth connecting piece L4, and is fixedly connected with input shaft IN by the first group of clutches C11, and rotates in the same direction and speed; The first driving gear G11 is fixedly connected with the second group of clutches C12, and is fixedly connected with the input shaft IN through the second group of clutches C12, and rotates in the same direction and speed; The first driven gear G12 is fixedly mounted on the motor MG and is meshed with the first driving gear G11 and is opposite to the direction of rotation of input shaft IN; the second driven gear G22 is fixedly connected with the first gear ring R1, and the second driving gear G21 is fixedly mounted on the motor MG and is meshed with the second driven gear G22, and the rotation direction of the second driven gear G22 is the same as that of input shaft IN; The second driven gear G22 is fixedly connected with the first gear ring R1, and the first gear ring R1 rotates in the same direction with input shaft IN; The first sun gear S1 and the first gear ring R1 rotate in the same direction with the input shaft IN, and jointly output power to the first planetary carrier PC1, and the first planetary carrier PC1 rotates in the same direction with the input shaft IN; The first planetary carrier PC1 is fixedly connected by the planetary carrier connecting shaft L3 and the second planetary carrier PC2, in the second planetary row P2, the second planetary carrier PC2 input power, the second sun gear S2 is fixed, the second ring gear R2 rotates in the same direction with the input shaft IN, and the second ring gear R2 outputs power to the output shaft OUT, and realizes four forward gears.

the second group of clutches C12 is engaged, and the 4th brake B4 is engaged with the 3rd brake B3 simultaneously, and the first sun gear S1 and the 3rd planet carrier PC3 are fixed respectively; The first driving gear G11 is fixedly connected with the second group of clutches C12, and is fixedly connected with the input shaft IN through the second group of clutches C12, and rotates in the same direction and speed; The first driven gear G12 is fixedly mounted on the motor MG and is meshed with the first driving gear G11 and is opposite to the direction of rotation of input shaft IN; the second driven gear G22 is fixedly connected with the first gear ring R1, and the second driving gear G21 is fixedly mounted on the motor MG and is meshed with the second driven gear G22, and the rotation direction of the second driven gear G22 is the same as that of input shaft IN; The second driven gear G22 is fixedly connected with the first gear ring R1, and the first gear ring R1 rotates in the same direction with input shaft IN; In the first planetary row P1, the first gear ring R1 inputs power, and because the first sun gear S1 is fixed, the first planetary carrier PC1 rotates in the same direction with the input shaft I N; The first planetary carrier PC1 is fixedly connected by the planetary carrier connecting shaft L3 and the second planetary carrier PC2, and the second planetary carrier PC2 rotates in the same direction with the input shaft I N; The first gear ring R1 is fixedly connected with the third gear ring R3 through the first connecting piece L1, in the third planetary row P3, the third gear ring R3 input power, the third planet carrier PC3 is fixed, the third sun gear S3 rotates in reverse with the input shaft IN, the third sun gear S3 and the second sun gear S2 are fixedly connected through the second connecting piece L2, and the second sun gear S2 rotates in reverse with input shaft IN; In the second planetary row P2, the second planetary carrier PC2 and the second sun gear S2 jointly input power, and the second gear ring R2 outputs power to the output shaft OUT; When the planet carrier and the sun gear jointly input power, and the gear ring outputs power, the sun wheel rotates in the opposite direction to the planet carrier, which can avoid the occurrence of circulating power, and the gear ring rotates in the same direction as the planet carrier, so as to achieve five forward gears.

The first group of clutches C11 and the second group of clutches C12 are engaged at the same time, and the third brake B3 is engaged, and the third planetary carrier PC3 is fixed; The first sun gear S1 is fixedly connected with the fourth connecting piece L4, and is fixedly connected with input shaft IN by the first group of clutches C11, and rotates in the same direction and speed; The first driving gear G11 is fixedly connected with the second group of clutches C12, and is fixedly connected with the input shaft IN through the second group of clutches C12, and rotates in the same direction and speed; The first driven gear G12 is fixedly mounted on the motor MG and is meshed with the first driving gear G11 and is opposite to the direction of rotation of input shaft IN; the second driven gear G22 is fixedly connected with the first gear ring R1, and the second driving gear G21 is fixedly mounted on the motor MG and is meshed with the second driven gear G22, and the rotation direction of the second driven gear G22 is the same as that of input shaft IN; The second driven gear G22 is fixedly connected with the first gear ring R1, and the first gear ring R1 rotates in the same direction with input shaft IN; The first sun gear S1 and the first gear ring R1 rotate in the same direction with the input shaft IN, and jointly output power to the first planetary carrier PC1, and the first planetary carrier PC1 rotates in the same direction with the input shaft IN; The first planetary carrier PC1 is fixedly connected with the second planetary carrier PC2 through the planetary carrier connecting shaft L3, and the second planetary carrier PC2 rotates in the same direction with the input shaft IN; The first gear ring R1 is fixedly connected with the third gear ring R3 through the first connecting piece L1, in the third planetary row P3, the third gear ring R3 input power, the third planet carrier PC3 is fixed, the third sun gear S3 rotates in reverse with the input shaft IN, the third sun gear S3 and the second sun gear S2 are fixedly connected through the second connecting piece L2, and the second sun gear S2 rotates in reverse with input shaft N; In the second planetary row P2, the second planetary carrier PC2 and the second sun gear S2 jointly input power, and the second gear ring R2 outputs power to the output shaft OUT; When the planet carrier and the sun gear jointly input power, and the ring gear outputs power, the direction of rotation of the sun wheel is opposite to that of the planet carrier, which can avoid the occurrence of circulating power, and the direction of rotation of the ring gear is the same as the direction of the planet carrier, so as to achieve six forward gears.

The first group of clutches C11 is engaged, and the 3rd brake B3 is engaged with the planetary carrier brake BL3 simultaneously, and the first planetary carrier PC1, the second planetary carrier PC2 and the 3rd planetary carrier PC3 are fixed respectively; The first sun gear S1 is fixedly connected with the fourth connecting piece L4, is fixedly connected with input shaft I N by the first group of clutches C11, and rotates in the same direction and speed; In the first planetary row P1, the first sun gear S1 inputs power, the first planet carrier PC1 is fixed, and the first gear ring R1 rotates in reverse with input shaft N N; The first gear ring R1 is fixedly connected with the third gear ring R3 through the first connecting piece L1, and in the third planetary row P3, the third gear ring R3 input power, the third planet carrier PC3 is fixed, and the third sun gear S3 rotates in the same direction with the input shaft I N; The third sun gear S3 and the second sun gear S2 are fixedly connected by the second connecting piece L2, in the second planetary row P2, the second sun gear S2 input power, the second planetary carrier PC2 is fixed, the second gear ring R2 and the input shaft I N rotate in the opposite direction, the second gear ring R2 is fixedly connected with the output shaft OUT, and the second gear ring R2 outputs power to the output shaft OUT, realizes the first gear backward.

Table 3.1 Calculation formula for individual drive of motor MG power

Planetary row K value refers to the ratio of the number of ring gear teeth of planetary row to the number of sun gear teeth, K1 = 6, K2 = 4, K3 = 3 in the above table, when the transmission ratio KG2 = 4 of the gear set G21: G22, the input speed of the motor MG is 1, and the transmission ratio of each gear shown in Table 3.1 can be obtained, and the transmission mechanism of three gears is realized.

Table 3.2 Motor MG power drive individually, control logic and transmission ratio of each gear (O indicates the engagement of the control part)

The following is combined with Figure 6 and Table 3.2 to describe in detail the motor power of the present invention separately driving example, and the transmission ratio refers to the ratio of the input shaft speed to the output shaft speed.

the third brake B3 is engaged with the planetary carrier brake BL3 at the same time, and the first planetary carrier PC1, the second planetary carrier PC2 and the third planetary carrier PC3 are fixed respectively; the second driving gear G21 is fixedly mounted on the motor MG and is meshed with the second driven gear G22, and the second driven gear G22 rotates in opposite directions with the motor MG rotation direction; The second driven gear G22 is fixedly connected with the first gear ring R1, and the first gear ring R1 rotates in the opposite direction with motor MG; The first gear ring R1 is fixedly connected with the third gear ring R3 through the first connecting piece L1, and in the third planetary row P3, the third gear ring R3 inputs power, the third planet carrier PC3 is fixed, and the third sun gear S3 rotates in the same direction with motor MG; The third sun gear S3 and the second sun gear S2 are fixedly connected through the second connecting piece L2, in the second planetary row P2, the second sun gear S2 input power, the second planetary carrier PC2 is fixed, the second gear ring R2 rotates in reverse with the motor MG, the second gear ring R2 is fixedly connected with the output shaft OUT, and the second gear ring R2 outputs power to the output shaft OUT, and realizes the first gear.

The 4th brake B4 is engaged with the 2nd brake B2 simultaneously, and the first sun gear S1 and the second sun gear S2 are fixed respectively; the second driving gear G21 is fixedly mounted on the motor MG and is meshed with the second driven gear G22, and the second driven gear G22 rotates in opposite directions with the motor MG rotation direction; The second driven gear G22 is fixedly connected with the first gear ring R1, and the first gear ring R1 rotates in the opposite direction with motor MG; In the first planetary row P1, the first gear ring R1 inputs power, and because the first sun gear S1 is fixed, the first planetary carrier PC1 rotates in the opposite direction with the motor MG; The first planetary carrier PC1 is fixedly connected by the planetary carrier connecting shaft L3 and the second planetary carrier PC2, in the second planetary row P2, the second planetary carrier PC2 inputs power, the second sun gear S2 is fixed, the second ring gear R2 rotates in the opposite direction with the motor MG, and the second ring gear R2 outputs power to the output shaft OUT, and realizes the second gear.

The 4th brake B4 is engaged with the 3rd brake B3 at the same time, and the first sun gear S1 and the 3rd planet carrier PC3 are fixed respectively; the second driving gear G21 is fixedly mounted on the motor MG and is meshed with the second driven gear G22, and the second driven gear G22 is opposite to the motor MG in the direction of rotation; the second driven gear G22 is fixedly connected with the first gear ring R1, and the first gear ring R1 is opposite to the motor MG in the direction of rotation; In the first planetary row P1, the first gear ring R1 inputs power, and because the first sun gear S1 is fixed, the first planetary carrier PC1 rotates in the opposite direction with the motor MG; The first planetary carrier PC1 is fixedly connected with the second planetary carrier PC2 through the planetary carrier connecting shaft L3, and the second planetary carrier PC2 is in opposite direction of rotation with the motor MG; The first gear ring R1 is fixedly connected with the third gear ring R3 through the first connecting piece L1, in the third planetary row P3, the third gear ring R3 input power, the third planet carrier PC3 is fixed, the third sun gear S3 rotates in the same direction with the motor MG, the third sun gear S3 is fixedly connected with the second sun gear S2 through the second connecting piece L2, and the second sun gear S2 rotates in the same direction with the motor MG; In the second planetary row P2, the second planetary carrier PC2 and the second sun gear S2 jointly input power, and the second ring gear R2 is opposite to the direction of rotation of motor MG, and the second ring gear R2 outputs power to output shaft OUT; When the planetary carrier and the sun gear jointly input power, and the gear ring outputs power, the sun wheel rotates in the opposite direction to the planet carrier, which can avoid circulating power, and the gear ring rotates in the same direction as the planetary carrier, so as to achieve the third gear.

The MG motor can control forward and reverse rotation, so that three gears can be realized, forward and backward.

The transmission ratios of the above gears are determined by the transmission ratios of the two pairs of gear sets and the K value of the three planetary rows. The transmission ratio of the gear set in this example is: the transmission ratio KG1=0.4 of the gear set G11:G12, and the transmission ratio KG2=4 of the gear set G21:G22; The K value of the planetary row refers to the ratio of the number of ring gear teeth of the planetary row to the number of sun gear teeth, in this example: K1 = 6, K2 = 4, K3 = 3, you can get the transmission ratio of each gear shown in Table 2.2 and Table 3.2, and realize the transmission mechanism of the internal combustion engine power independent drive forward six gears and backward one gear, and the motor power independently drives the transmission mechanism of three gears forward and backward.

Optionally, when shifting gears, only the first group of clutches C11 is engaged, and the motor MG is connected in parallel with the internal combustion engine, and the motor MG is used as a generator for power generation, on the one hand, the load on the engine is balanced, so that the engine can provide sufficient driving force in the shift stage, on the other hand, the power that cannot be used for driving due to the speed difference between the engine and the gearbox is used for power generation, and the power battery is charged, and the smoothness of gear shift is also greatly improved; During normal driving, the first group of clutches C11 and the second group of clutches C12 are engaged at the same time, the motor MG and the internal combustion engine are mixed drive, and the motor MG assists the internal combustion engine to work, and the output transmission ratio remains unchanged, so that the total output power is increased and the output torque is increased;

Optional, only the first group of clutches C11 is engaged, the motor MG is driven in parallel with the internal combustion engine, and the motor MG is used for speed regulation and torsion, which can realize stepless speed change, realize the function of ECVT gearbox, reduce the slippery work and heat loss of the clutch friction plate, improve the power use efficiency, and improve the reliability of the friction plate.

Optional, the internal combustion engine is front-mounted, the rear-wheel drive motor is arranged, only the first group of clutches C11 is engaged, the motor MG is connected in parallel with the internal combustion engine, the motor MG is used as a generator for power generation, and the generated power is used for the drive of the rear wheel motor, so that the power of the internal combustion engine is redistributed in the front and rear wheels to achieve four-wheel drive.

Optionally, the ratio of the number of teeth of the first driven gear G12 and the first driving gear G11 is 0.4. The ratio of the number of teeth of the second driven gear G22 and the second driving gear G21 is 4. The ratio of the number of teeth of the first ring gear R1 to the number of teeth of the first sun gear S1 is 6. The ratio of the number of teeth of the second ring gear R2 to the number of teeth of the second sun gear S2 is 4. The ratio of the number of teeth of the third gear ring R3 to the number of teeth of the third sun gear S3 is 3.

Optional, the internal combustion engine power is driven independently, the transmission ratio of the forward first gear is 5.60, the transmission ratio of the forward second gear is 2.13, the transmission ratio of the forward third gear is 1.49, the transmission ratio of the forward fourth gear is 1.18, the transmission ratio of the forward fifth gear is 0.88, the transmission ratio of the forward six gear is 0.76, and the transmission ratio of the backward first gear is 8.00. Further, the internal combustion engine power is driven independently, and the step ratio of the forward first gear and the forward second gear is 2.63, the step ratio of the forward second gear and the forward third gear is 1.43, the step ratio of the forward third gear and the forward fourth gear is 1.27, the step ratio of the forward fourth gear to the forward fifth gear is 1.34, the step ratio of the forward fifth gear and the forward sixth gear is 1.16, and the transmission ratio range of the highest gear and the lowest gear is 7.38.

Optional, the motor power is driven independently, the transmission ratio of the first gear is 5.33, the transmission ratio of the second gear is 3.73, and the transmission ratio of the third gear is 2.2; Further, the motor power is driven independently, and the step ratio of the forward first gear and the forward second gear is 1.43, the step ratio of the forward second gear and the forward third gear is 1.7, and the transmission ratio range of the highest gear and the lowest gear is 2.43.

The embodiment discloses a planetary multi-stage transmission transmission mechanism for vehicle transmission system, as shown in Figure 6, and comprises a double clutch C1, a motor MG, an input shaft N input, an output shaft OUT, three planetary rows (P1~P3), five brakes (BL3, B1~B4), and four connectors (L1~L4).

Each planetary row includes: sun gear (S1~S3), planet carrier (PC1~PC3), planetary wheel (CA1~CA3) and ring gear (R1~R3); The ring gear is coaxially distributed with the sun gear, and the planetary wheel is installed on the planetary carrier through the planetary shaft and the bearing respectively, and each planetary wheel is meshed with the ring gear on the counter star row and meshed with the sun wheel on the peer star row.

The dual clutch C1 and the three planetary rows are distributed side by side from left to right, and the dual clutch C1, three sun gears, the input shaft I N and the output shaft OUT are coaxially arranged. The motor MG is arranged parallel to the input shaft IN.

Power flow direction: Power flows in from the input shaft IN and out from the output shaft. When the motor MG is driven in parallel, the power of the motor MG flows in from the first ring gear R1 and flows out from the output shaft.

In the present application, the vehicle transmission system is used for planetary multi-stage transmission transmission mechanism, comprises three planetary rows, five brakes, the planetary rows are single planetary simple planetary rows, the highest forward six gears can be realized, the forward one gear transmission ratio is greater than 5, the oil, electric hybrid drive can be realized, the engine can be run more in the economic working area, and the economy of the whole machine is improved. The five brakes are all friction-controlled structures, and the gear is controlled by two-element operation, which can reduce the slippery work and thermal loss of the friction pads and improve the reliability of the friction pads.

Seventh embodiment:

A vehicle transmission system comprises a planetary multistage transmission transmission mechanism from the first embodiment to any of the sixth embodiments.

To sum up, the vehicle transmission system of the present invention is simple in structure, the transmission ratio range is large, the transmission torque capacity is strong, the gear scalability is strong, and can better adapt to the transmission demand of the vehicle than the existing transmission system.

The above disclosed are only some embodiments of the present invention. For a person skilled in the art, under the premise of not departing from the idea of the present invention, a number of deformations and improvements can also be made, which all belong to the scope of protection of the present invention.