Planetary multi-stage transmission speed change mechanism and vehicle transmission system

Abstract

The planetary multi-stage transmission speed change mechanism comprises an input shaft, an output shaft, a first planet row, a second planet row and a third planet row, the input shaft is connected with the first planet row, and the output shaft is connected with the second planet row; the first planet row is connected with the first brake, the second planet row is connected with the second brake, and the third planet carrier is connected with the third brake. Multi-stage transmission is achieved, the number of parts such as clutches is reduced, the complexity and manufacturing difficulty of a speed change mechanism are remarkably reduced, the number of parts is reduced, the size and weight of a speed changer are reduced, and the operation reliability of the speed change mechanism is improved.

Description

Technical Field

[0001] The utility model relates to the technical field of vehicle transmission, in particular to a planetary multi-stage transmission speed change mechanism and a vehicle transmission system. Background Art

[0002] Currently, automatic transmissions with fixed gear changes used in transportation vehicles mainly include automatic transmissions (AT) and dual-clutch transmissions (DCT). Automatic transmissions (AT) are mainly composed of three components: planetary gears, brakes, and clutches. The combined use of multiple clutches improves the degree of freedom of the transmission and the reuse rate of the planetary gears, allowing the transmission to achieve multiple gear changes within a limited volume. The disadvantage is that the structure is complex, the manufacturing difficulty is high, and the cost is high. To achieve more gears, the structural complexity will increase nonlinearly.

[0003] The dual-clutch transmission (DCT) has clear shifting logic and a simple structure. Its disadvantage is that the reuse rate of the transmission gear set is low. When more gears are designed, the volume of the transmission will expand rapidly. The limited engine compartment volume will restrict the increase in the volume of the transmission.

[0004] Therefore, there is an urgent need for a gearbox with multiple gears, a large transmission ratio range, simple gear control logic, a linear relationship between the increase in gears and the increase in structural complexity, and a high reuse rate of transmission components. Utility Model Content

[0005] The purpose of this utility model is to provide a planetary multi-stage transmission speed change mechanism and a vehicle transmission system to solve the above technical problems. To achieve this purpose, this utility model adopts the following technical solutions:

[0006] A planetary multi-stage transmission speed change mechanism includes an input shaft, an output shaft, a first planetary gear, a second planetary gear, and a third planetary gear; the input shaft is connected to the first planetary gear, and the output shaft is connected to the second planetary gear;

[0007] The first ring gear or the first sun gear of the first planetary row is connected to the first brake; the second ring gear or the second sun gear of the second planetary row is connected to the second brake;

[0008] The first planetary gear includes a first planetary gear; the second planetary gear includes a second planetary gear; the third planetary gear includes a third planetary gear;

[0009] The first planet carrier and the second planet carrier are fixedly connected via a planet carrier connecting shaft; the third sun gear of the third planet row is movably mounted on the planet carrier connecting shaft; the third planet carrier is connected to the third brake; and the second planet carrier is connected to the planet carrier brake.

[0010] In some embodiments, a fixed-axis rotating member (first sun gear / first ring gear) of the first planetary row is fixedly connected to the input shaft, another fixed-axis rotating member (first ring gear / first sun gear) of the first planetary row is fixedly connected to a fixed-axis rotating member (third sun gear / third ring gear) of the third planetary row via a first connecting member; another fixed-axis rotating member (third ring gear / third sun gear) of the third planetary row is fixedly connected to a fixed-axis rotating member (second ring gear / second sun gear) of the second planetary row via a second connecting member; another fixed-axis rotating member (second sun gear / second ring gear) of the second planetary row is fixedly connected to the output shaft.

[0011] In some embodiments, the first planetary gear includes a first sun gear, first planetary gears, and a first ring gear;

[0012] The second planetary gear includes a second sun gear, second planetary gears and a second ring gear;

[0013] The third planetary gear includes a third sun gear, third planetary gears and a third ring gear;

[0014] The third sun gear is movably mounted on the planet carrier connecting shaft;

[0015] The input shaft is fixedly connected to the first sun gear, the first ring gear is fixedly connected to the third sun gear via a first connecting member, the third ring gear is fixedly connected to the second ring gear via a second connecting member, and the output shaft is fixedly connected to the second sun gear;

[0016] The first ring gear is connected to the first brake; the second ring gear is connected to the second brake; the second planetary carrier is connected to the planetary carrier brake; and the third planetary carrier is connected to the third brake.

[0017] Beneficial effects of the utility model:

[0018] 1. The planetary multi-stage transmission speed change mechanism of the present invention adopts a multi-stage transmission method for speed change and torque change. By connecting a three-stage transmission planetary gear in parallel between the two-stage transmission mechanism, three transmission effects are achieved: two-stage transmission, three-stage transmission and a hybrid transmission of two-stage transmission and three-stage transmission in parallel. The gear shifting logic is simple and the gear position has strong scalability. After the planetary gear is expanded into a planetary gear group, the number of transmission gear positions is: forward gear number n1×n2+(n1-1)+(n2-1), reverse gear number 1, and the reuse rate of the planetary gear is greatly improved; at the same time, the hybrid transmission of the two-stage transmission and the three-stage transmission in parallel can achieve an increase in the upper limit and a decrease in the lower limit of the forward gear ratio, thereby expanding the transmission ratio range of the forward gear.

[0019] 2. The main components of the planetary multi-stage transmission speed change mechanism of the utility model are two categories: planetary gears and brakes. Compared with the technical solutions of the prior art that generally adopt three categories of components: planetary gears, brakes and clutches, the clutch component is reduced, which significantly reduces the complexity and manufacturing difficulty of the speed change mechanism, reduces the number of parts, reduces the size and weight of the transmission, and improves the operating reliability of the speed change mechanism, which is a significant improvement.

[0020] 3. The mechanical layout of this utility model is also very suitable for dual power input from the sun gear and the ring gear. The external dual clutch and motor can realize pure oil, pure electric and hybrid power drive, and can be used as a dual clutch transmission or hybrid transmission; the combination of dual clutch and planetary gearbox can also increase the number of forward gears. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 This is a structural diagram of a planetary multi-stage transmission speed change mechanism according to the first embodiment of the present utility model.

[0022] Figure 2 This is a structural diagram of a planetary multi-stage transmission speed change mechanism according to the second embodiment of the present utility model.

[0023] Figure 3 This is a structural diagram of a planetary multi-stage transmission speed change mechanism according to the third embodiment of the present utility model.

[0024] Figure 4 This is a structural diagram of a planetary multi-stage transmission speed change mechanism according to the fourth embodiment of the present utility model.

[0025] Figure 5 This is a structural diagram of a planetary multi-stage transmission speed change mechanism according to the fifth embodiment of the present utility model.

[0026] Figure 6 This is a structural diagram of a planetary multi-stage transmission speed change mechanism according to the sixth embodiment of the present utility model. DETAILED DESCRIPTION

[0027] The present invention will be further described in detail below with reference to the accompanying drawings.

[0028] First embodiment:

[0029] refer to Figure 1 , a planetary multi-stage transmission speed change mechanism, including an input shaft IN, an output shaft OUT, a first planetary row P1, a second planetary row P2 and a third planetary row P3;

[0030] The input shaft IN is connected to the first planetary gear P1; the output shaft OUT is connected to the second planetary gear P2;

[0031] The first planetary gear P1 includes a first sun gear S1, a first planet carrier PC1, a first planetary gear CA1, and a first ring gear R1. The first planetary gear CA1 is movably mounted on the first planet carrier PC1. The first ring gear R1 meshes with the first planetary gear CA1, and the first planetary gear CA1 meshes with the first sun gear S1.

[0032] The second planetary gear P2 includes a second sun gear S2, a second planet carrier PC2, a second planetary gear CA2, and a second ring gear R2. The second planetary gear CA2 is movably mounted on the second planet carrier PC2. The second ring gear R2 meshes with the second planetary gear CA2, and the second planetary gear CA2 meshes with the second sun gear S2.

[0033] The third planetary gear P3 includes a third sun gear S3, a third planet carrier PC3, a third planetary gear CA3, and a third ring gear R3. The third planetary gear CA3 is movably mounted on the third planet carrier PC3. The third ring gear R3 meshes with the third planetary gear CA3, and the third planetary gear CA3 meshes with the third sun gear S3.

[0034] The third sun gear S3 is movably mounted on the planet carrier connecting shaft L3; the first planet carrier PC1 and the second planet carrier PC2 are fixedly connected via the planet carrier connecting shaft L3.

[0035] The input shaft IN is fixedly connected to the first sun gear S1, the first ring gear R1 is fixedly connected to the third sun gear S3 via the first connecting member L1, the third ring gear R3 is fixedly connected to the second ring gear R2 via the second connecting member L2, and the output shaft OUT is fixedly connected to the second sun gear S2;

[0036] The first ring gear R1 is connected to the first brake B1, that is, the first brake B1 can brake the first ring gear R1; the second ring gear R2 is connected to the second brake B2, that is, the second brake B2 can brake the second ring gear R2; the second planet carrier PC2 is connected to the planet carrier brake BL3, that is, the planet carrier brake BL3 can brake the second planet carrier PC2; the third planet carrier PC3 is connected to the third brake B3, that is, the third brake B3 can brake the third planet carrier PC3.

[0037] Among them, the movable installation can be understood as a rotating connection; the fixed connection can be understood as a linkage connection.

[0038] Working principle: the ring gear is connected to the sun gear, and the ring gear is connected to the ring gear, RS-RR type.

[0039] The first brake B1 and the second brake B2 are engaged simultaneously, fixing the first ring gear R1 and the second ring gear R2 respectively, and the first sun gear S1 is fixedly connected to the input shaft IN, rotating in the same direction and speed; in the first planetary row P1, the first sun gear S1 inputs power, the first ring gear R1 is fixed, and the first planetary carrier PC1 rotates in the same direction as the input shaft IN; in the second planetary row P2, the second planetary carrier PC2 is fixedly connected to the first planetary carrier PC1 through the planetary carrier connecting shaft L3, the second planetary carrier PC2 inputs power, the second ring gear R2 is fixed, the second sun gear S2 is fixedly connected to the output shaft OUT, and the second sun gear S2 outputs power to the output shaft OUT, and the output shaft OUT rotates in the same direction as the input shaft IN; the power passes through the first planetary row P1, the planetary carrier connecting shaft L3 and the second planetary row P2 in sequence to realize two-stage transmission, and the output power rotation direction is the same as the input power rotation direction.

[0040] The third brake B3 and the planetary carrier brake BL3 are engaged simultaneously, fixing the first planetary carrier PC1, the second planetary carrier PC2, and the third planetary carrier PC3 respectively. The first sun gear S1 is fixedly connected to 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 ring gear R1 rotates in the opposite direction to the input shaft IN. The first ring gear R1 and the third sun gear S3 are fixedly connected through the first connecting member L1. In the third planetary row P3, the third sun gear S3 inputs power, the third planetary carrier PC3 is fixed, and the third ring gear R3 rotates in the same direction as the input shaft IN. Rotation; the third ring gear R3 is fixedly connected to the second ring gear R2 through the second connecting member L2. In the second planetary row P2, the second ring gear R2 inputs power, the second planet carrier PC2 is fixed, the second sun gear S2 rotates in the opposite direction to the input shaft IN, the second sun gear S2 is fixedly connected to the output shaft OUT, and the second sun gear S2 outputs power to the output shaft OUT, and the output shaft OUT rotates in the opposite direction to the input shaft IN; the power passes through the first planetary row P1, the first connecting member L1, the third planetary row P3, the second connecting member L2 and the second planetary row P2 in sequence to realize three-stage transmission, and the output power rotation direction is opposite to the input power rotation direction.

[0041] The third brake B3 is engaged alone to fix the third planetary carrier PC3, 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 power is divided into two-stage transmission and three-stage transmission to realize hybrid transmission; the first sun gear S1 is fixedly connected to 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 is divided into two-way transmission, the first way is transmitted through the first planetary carrier PC1 in the form of a two-stage transmission, and the second way is transmitted through the first ring gear R1 in the form of a three-stage transmission; in the first way transmission, in the first planetary row P1, the first sun gear S1 outputs power to the first planetary carrier PC1, and the first planetary carrier PC1 outputs power to the planetary carrier connecting shaft L3, and in the second planetary row P2, the planetary carrier connecting shaft L3 outputs power to the second planetary carrier PC2, and the second planetary carrier PC2 After the power is split again, it is output to the second ring gear R2 and the second sun gear S2 respectively; for the second transmission, in the first planetary row P1, the first sun gear S1 outputs power to the first ring gear R1 through the first planetary gear CA1, and the first ring gear R1 outputs power to the first connecting member L1. In the third planetary row P3, the first connecting member L1 outputs power to the third sun gear S3, and the third sun gear S3 outputs power to the third ring gear R3 through the third planetary gear CA3. The third ring gear R3 outputs power to the second connecting member L2. In the second planetary row P2, the second connecting member L2 outputs power to the second ring gear R2. After the power of the second ring gear R2 is split again, it is output to the second planet carrier PC2 and the second sun gear S2 respectively; the planetary row group with two degrees of freedom realizes a hybrid transmission of two-stage transmission in parallel with three-stage transmission. Actuating one operating member eliminates another degree of freedom, thereby achieving fixed input and output.

[0042] Second embodiment:

[0043] refer to Figure 2 , a planetary multi-stage transmission speed change mechanism, including an input shaft IN, an output shaft OUT, a first planetary row P1, a second planetary row P2 and a third planetary row P3;

[0044] The input shaft IN is connected to the first planetary gear P1; the output shaft OUT is connected to the second planetary gear P2;

[0045] The first planetary gear P1 includes a first sun gear S1, a first planet carrier PC1, a first planetary gear CA1, and a first ring gear R1. The first planetary gear CA1 is movably mounted on the first planet carrier PC1. The first ring gear R1 meshes with the first planetary gear CA1, and the first planetary gear CA1 meshes with the first sun gear S1.

[0046] The second planetary gear P2 includes a second sun gear S2, a second planet carrier PC2, a second planetary gear CA2, and a second ring gear R2. The second planetary gear CA2 is movably mounted on the second planet carrier PC2. The second ring gear R2 meshes with the second planetary gear CA2, and the second planetary gear CA2 meshes with the second sun gear S2.

[0047] The third planetary gear P3 includes a third sun gear S3, a third planet carrier PC3, a third planetary gear CA3, and a third ring gear R3. The third planetary gear CA3 is movably mounted on the third planet carrier PC3. The third ring gear R3 meshes with the third planetary gear CA3, and the third planetary gear CA3 meshes with the third sun gear S3.

[0048] The second sun gear S2 and the third sun gear S3 are both movably mounted on the planet carrier connecting shaft L3; the first planet carrier PC1 and the second planet carrier PC2 are fixedly connected via the planet carrier connecting shaft L3;

[0049] The input shaft IN is fixedly connected to the first sun gear S1, the first ring gear R1 is fixedly connected to the third ring gear R3 via the first connecting member L1, the third sun gear S3 is fixedly connected to the second sun gear S2 via the second connecting member L2, and the output shaft OUT is fixedly connected to the second ring gear R2;

[0050] The first ring gear R1 is connected to the first brake B1, that is, the first brake B1 can brake the first ring gear R1; the second sun gear S2 is connected to the second brake B2, that is, the second brake B2 can brake the second sun gear S2; the second planet carrier PC2 is connected to the planet carrier brake BL3, that is, the planet carrier brake BL3 can brake the second planet carrier PC2; the third planet carrier PC3 is connected to the third brake B3, that is, the third brake B3 can brake the third planet carrier PC3.

[0051] Working principle: Ring gear connected to ring gear, sun gear connected to sun gear, RR-SS type.

[0052] The first brake B1 and the second brake B2 are engaged simultaneously, fixing the first ring gear R1 and the second sun gear S2 respectively. The first sun gear S1 is fixedly connected to 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 ring gear R1 is fixed, and the first planetary carrier PC1 rotates in the same direction as the input shaft IN; in the second planetary row P2, the second planetary carrier PC2 is fixedly connected to the first planetary carrier PC1 through the planetary carrier connecting shaft L3, the second planetary carrier PC2 inputs power, the second sun gear S2 is fixed, the second ring gear R2 is fixedly connected to the output shaft OUT, and the second ring gear R2 outputs power to the output shaft OUT, and the output shaft OUT rotates in the same direction as the input shaft IN; the power passes through the first planetary row P1, the planetary carrier connecting shaft L3 and the second planetary row P2 in sequence to realize two-stage transmission, and the output power rotation direction is the same as the input power rotation direction.

[0053] The third brake B3 and the planetary carrier brake BL3 are engaged simultaneously, fixing the first planetary carrier PC1, the second planetary carrier PC2, and the third planetary carrier PC3 respectively. The first sun gear S1 is fixedly connected to 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 ring gear R1 rotates in the opposite direction to the input shaft IN. The first ring gear R1 and the third ring gear R3 are fixedly connected by the first connecting member L1. In the third planetary row P3, the third ring gear R3 inputs power, the third planetary carrier PC3 is fixed, and the third sun gear S3 rotates in the same direction as the input shaft IN. The third sun gear S3 is fixedly connected to the second sun gear S2 through the second connecting member L2. In the second planetary row P2, the second sun gear S2 inputs power, the second planet carrier PC2 is fixed, the second ring gear R2 rotates in the opposite direction to the input shaft IN, and the second ring gear R2 is fixedly connected to the output shaft OUT. The second ring gear R2 outputs power to the output shaft OUT, and the output shaft OUT rotates in the opposite direction to the input shaft IN. The power passes through the first planetary row P1, the first connecting member L1, the third planetary row P3, the second connecting member L2 and the second planetary row P2 in sequence to realize three-stage transmission. The output power rotation direction is opposite to that of the input power.

[0054] The third brake B3 is engaged alone to fix the third planetary carrier PC3, 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, realizing a hybrid transmission of two-stage transmission in parallel with three-stage transmission; the first sun gear S1 is fixedly connected to 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 is divided into two transmission paths, the first path is transmitted through the first planetary carrier PC1 in a two-stage transmission mode, and the second path is transmitted through the first ring gear R1 in a three-stage transmission mode; in the first transmission path, in the first planetary row P1, the first sun gear S1 outputs power to the first planetary carrier PC1, and the first planetary carrier PC1 outputs power to the planetary carrier connecting shaft L3. In the second planetary row P2, the planetary carrier connecting shaft L3 outputs power to the second planetary carrier PC2, and the power of the second planetary carrier PC2 is then After the second diversion, the power is output to the second ring gear R2 and the second sun gear S2 respectively; for the second transmission, in the first planetary row P1, the first sun gear S1 outputs power to the first ring gear R1 through the first planetary gear CA1, and the first ring gear R1 outputs power to the first connecting member L1. In the third planetary row P3, the first connecting member L1 outputs power to the third ring gear R3, and the third ring gear R3 outputs power to the third sun gear S3 through the third planetary gear CA3. The third sun gear S3 outputs power to the second connecting member L2. In the second planetary row P2, the second connecting member L2 outputs power to the second sun gear S2, and the second sun gear S2 diverts the power again and outputs it to the second planet carrier PC2 and the second ring gear R2 respectively; the planetary row group with two degrees of freedom realizes a hybrid transmission of two-stage transmission in parallel with three-stage transmission. By actuating one operating member, the other degree of freedom is eliminated, thereby achieving fixed input and output.

[0055] Third embodiment:

[0056] refer to Figure 3 , a planetary multi-stage transmission speed change mechanism, including an input shaft IN, an output shaft OUT, a first planetary row P1, a second planetary row P2 and a third planetary row P3;

[0057] The input shaft IN is connected to the first planetary gear P1; the output shaft OUT is connected to the second planetary gear P2;

[0058] The first planetary gear P1 includes a first sun gear S1, a first planet carrier PC1, a first planetary gear CA1, and a first ring gear R1. The first planetary gear CA1 is movably mounted on the first planet carrier PC1. The first ring gear R1 meshes with the first planetary gear CA1, and the first planetary gear CA1 meshes with the first sun gear S1.

[0059] The second planetary gear P2 includes a second sun gear S2, a second planet carrier PC2, a second planetary gear CA2, and a second ring gear R2. The second planetary gear CA2 is movably mounted on the second planet carrier PC2. The second ring gear R2 meshes with the second planetary gear CA2, and the second planetary gear CA2 meshes with the second sun gear S2.

[0060] The third planetary gear P3 includes a third sun gear S3, a third planet carrier PC3, a third planetary gear CA3, and a third ring gear R3. The third planetary gear CA3 is movably mounted on the third planet carrier PC3. The third ring gear R3 meshes with the third planetary gear CA3, and the third planetary gear CA3 meshes with the third sun gear S3.

[0061] The second sun gear S2 and the third sun gear S3 are both movably mounted on the planet carrier connecting shaft L3; the first planet carrier PC1 and the second planet carrier PC2 are fixedly connected via the planet carrier connecting shaft L3;

[0062] The input shaft IN is fixedly connected to the first sun gear S1, the first ring gear R1 is fixedly connected to the third sun gear S3 via the first connecting member L1, the third ring gear R3 is fixedly connected to the second sun gear S2 via the second connecting member L2, and the output shaft OUT is fixedly connected to the second ring gear R2;

[0063] The first ring gear R1 is connected to the first brake B1, that is, the first brake B1 can brake the first ring gear R1; the second sun gear S2 is connected to the second brake B2, that is, the second brake B2 can brake the second sun gear S2; the second planet carrier PC2 is connected to the planet carrier brake BL3, that is, the planet carrier brake BL3 can brake the second planet carrier PC2; the third planet carrier PC3 is connected to the third brake B3, that is, the third brake B3 can brake the third planet carrier PC3.

[0064] Working principle: Ring gear connected to sun gear, ring gear connected to sun gear, RS-RS type.

[0065] The first brake B1 and the second brake B2 are engaged simultaneously, fixing the first ring gear R1 and the second sun gear S2 respectively. The first sun gear S1 is fixedly connected to 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 ring gear R1 is fixed, and the first planetary carrier PC1 rotates in the same direction as the input shaft IN; in the second planetary row P2, the second planetary carrier PC2 is fixedly connected to the first planetary carrier PC1 through the planetary carrier connecting shaft L3, the second planetary carrier PC2 inputs power, the second sun gear S2 is fixed, the second ring gear R2 is fixedly connected to the output shaft OUT, and the second ring gear R2 outputs power to the output shaft OUT, and the output shaft OUT rotates in the same direction as the input shaft IN; the power passes through the first planetary row P1, the planetary carrier connecting shaft L3 and the second planetary row P2 in sequence to realize two-stage transmission, and the output power rotation direction is the same as the input power rotation direction.

[0066] The third brake B3 and the planetary carrier brake BL3 are engaged simultaneously, fixing the first planetary carrier PC1, the second planetary carrier PC2, and the third planetary carrier PC3 respectively. The first sun gear S1 is fixedly connected to 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 ring gear R1 rotates in the opposite direction to the input shaft IN. The first ring gear R1 and the third sun gear S3 are fixedly connected through the first connecting member L1. In the third planetary row P3, the third sun gear S3 inputs power, the third planetary carrier PC3 is fixed, and the third ring gear R3 rotates in the same direction as the input shaft IN. Rotation; the third ring gear R3 is fixedly connected to the second sun gear S2 through the second connecting member L2. In the second planetary row P2, the second sun gear S2 inputs power, the second planetary carrier PC2 is fixed, the second ring gear R2 rotates in the opposite direction to the input shaft IN, and the second ring gear R2 is fixedly connected to the output shaft OUT. The second ring gear R2 outputs power to the output shaft OUT, and the output shaft OUT rotates in the opposite direction to the input shaft IN; the power passes through the first planetary row P1, the first connecting member L1, the third planetary row P3, the second connecting member L2 and the second planetary row P2 in sequence to realize three-stage transmission, and the output power rotation direction is opposite to the input power rotation direction.

[0067] The third brake B3 is engaged alone to fix the third planetary carrier PC3, 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, realizing a hybrid transmission of two-stage transmission in parallel with three-stage transmission; the first sun gear S1 is fixedly connected to 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 is divided into two transmission paths, the first path is transmitted through the first planetary carrier PC1 in a two-stage transmission mode, and the second path is transmitted through the first ring gear R1 in a three-stage transmission mode; in the first transmission path, in the first planetary row P1, the first sun gear S1 outputs power to the first planetary carrier PC1, and the first planetary carrier PC1 outputs power to the planetary carrier connecting shaft L3. In the second planetary row P2, the planetary carrier connecting shaft L3 outputs power to the second planetary carrier PC2, and the power of the second planetary carrier PC2 is then After the second diversion, the power is output to the second ring gear R2 and the second sun gear S2 respectively; for the second transmission, in the first planetary row P1, the first sun gear S1 outputs power to the first ring gear R1 through the first planetary gear CA1, and the first ring gear R1 outputs power to the first connecting member L1. In the third planetary row P3, the first connecting member L1 outputs power to the third sun gear S3, and the third sun gear S3 outputs power to the third ring gear R3 through the third planetary gear CA3. The third ring gear R3 outputs power to the second connecting member L2. In the second planetary row P2, the second connecting member L2 outputs power to the second sun gear S2, and the second sun gear S2 diverts the power again and outputs it to the second planet carrier PC2 and the second ring gear R2 respectively; the planetary row group with two degrees of freedom realizes a hybrid transmission of two-stage transmission in parallel with three-stage transmission. By actuating one operating member, the other degree of freedom is eliminated, thereby achieving fixed input and output.

[0068] Fourth embodiment:

[0069] refer to Figure 4 , a planetary multi-stage transmission speed change mechanism, including an input shaft IN, an output shaft OUT, a first planetary row P1, a second planetary row P2 and a third planetary row P3;

[0070] The input shaft IN is connected to the first planetary gear P1; the output shaft OUT is connected to the second planetary gear P2;

[0071] The first planetary gear P1 includes a first sun gear S1, a first planet carrier PC1, a first planetary gear CA1, and a first ring gear R1. The first planetary gear CA1 is movably mounted on the first planet carrier PC1. The first ring gear R1 meshes with the first planetary gear CA1, and the first planetary gear CA1 meshes with the first sun gear S1.

[0072] The second planetary gear P2 includes a second sun gear S2, a second planet carrier PC2, a second planetary gear CA2, and a second ring gear R2. The second planetary gear CA2 is movably mounted on the second planet carrier PC2. The second ring gear R2 meshes with the second planetary gear CA2, and the second planetary gear CA2 meshes with the second sun gear S2.

[0073] The third planetary gear P3 includes a third sun gear S3, a third planet carrier PC3, a third planetary gear CA3, and a third ring gear R3. The third planetary gear CA3 is movably mounted on the third planet carrier PC3. The third ring gear R3 meshes with the third planetary gear CA3, and the third planetary gear CA3 meshes with the third sun gear S3.

[0074] 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 planet carrier PC1 and the second planet carrier PC2 are fixedly connected via the planet carrier connecting shaft L3;

[0075] The input shaft IN is fixedly connected to the first ring gear R1, the first sun gear S1 is fixedly connected to the third sun gear S3 via the first connecting member L1, the third ring gear R3 is fixedly connected to the second sun gear S2 via the second connecting member L2, and the output shaft OUT is fixedly connected to the second ring gear R2;

[0076] The first sun gear S1 is connected to the first brake B1, that is, the first brake B1 can brake the first sun gear S1; the second sun gear S2 is connected to the second brake B2, that is, the second brake B2 can brake the second sun gear S2; the second planet carrier PC2 is connected to the planet carrier brake BL3, that is, the planet carrier brake BL3 can brake the second planet carrier PC2; the third planet carrier PC3 is connected to the third brake B3, that is, the third brake B3 can brake the third planet carrier PC3.

[0077] Working principle: sun gear connected to sun gear, ring gear connected to sun gear, SS-RS type.

[0078] The first brake B1 and the second brake B2 are engaged simultaneously, fixing the first sun gear S1 and the second sun gear S2 respectively, and the first ring gear R1 is fixedly connected to the input shaft IN, rotating in the same direction and speed; in the first planetary row P1, the first ring gear R1 inputs power, the first sun gear S1 is fixed, and the first planetary carrier PC1 rotates in the same direction as the input shaft IN; in the second planetary row P2, the second planetary carrier PC2 is fixedly connected to the first planetary carrier PC1 through the planetary carrier connecting shaft L3, the second planetary carrier PC2 inputs power, the second sun gear S2 is fixed, the second ring gear R2 is fixedly connected to the output shaft OUT, and the second ring gear R2 outputs power to the output shaft OUT, and the output shaft OUT rotates in the same direction as the input shaft IN; the power passes through the first planetary row P1, the planetary carrier connecting shaft L3 and the second planetary row P2 in sequence to realize two-stage transmission, and the output power rotation direction is the same as the input power rotation direction.

[0079] The third brake B3 and the planetary carrier brake BL3 are engaged simultaneously, fixing the first planetary carrier PC1, the second planetary carrier PC2, and the third planetary carrier PC3 respectively. The first ring gear R1 is fixedly connected to the input shaft IN and rotates in the same direction and speed. In the first planetary row P1, the first ring gear R1 inputs power, the first planetary carrier PC1 is fixed, and the first sun gear S1 rotates in the opposite direction to the input shaft IN. The first sun gear S1 and the third sun gear S3 are fixedly connected by the first connecting member L1. In the third planetary row P3, the third sun gear S3 inputs power, the third planetary carrier PC3 is fixed, and the third ring gear R3 rotates in the same direction as the input shaft IN. Rotation; the third ring gear R3 is fixedly connected to the second sun gear S2 through the second connecting member L2. In the second planetary row P2, the second sun gear S2 inputs power, the second planetary carrier PC2 is fixed, the second ring gear R2 rotates in the opposite direction to the input shaft IN, and the second ring gear R2 is fixedly connected to the output shaft OUT. The second ring gear R2 outputs power to the output shaft OUT, and the output shaft OUT rotates in the opposite direction to the input shaft IN; the power passes through the first planetary row P1, the first connecting member L1, the third planetary row P3, the second connecting member L2 and the second planetary row P2 in sequence to realize three-stage transmission, and the output power rotation direction is opposite to the input power rotation direction.

[0080] The third brake B3 is engaged separately to fix the third planetary carrier PC3, 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, realizing a hybrid transmission of two-stage transmission and three-stage transmission in parallel; the first ring gear R1 is fixedly connected to the input shaft IN and rotates in the same direction and speed; in the first planetary row P1, the first ring gear R1 inputs power, and the power is divided into two transmission paths, the first path is transmitted through the first planetary carrier PC1 in a two-stage transmission mode, and the second path is transmitted through the first sun gear S1 in a three-stage transmission mode; in the first transmission path, in the first planetary row P1, the first ring gear R1 outputs power to the first planetary carrier PC1, and the first planetary carrier PC1 outputs power to the planetary carrier connecting shaft L3. In the second planetary row P2, the planetary carrier connecting shaft L3 outputs power to the second planetary carrier PC2, and the power of the second planetary carrier PC2 is divided again After the flow, they are output to the second ring gear R2 and the second sun gear S2 respectively; for the second transmission, in the first planetary row P1, the first ring gear R1 outputs power to the first sun gear S1 through the first planetary gear CA1, and the first sun gear S1 outputs power to the first connecting member L1, and in the third planetary row P3, the first connecting member L1 outputs power to the third sun gear S3, and the third sun gear S3 outputs power to the third ring gear R3 through the third planetary gear CA3, and the third ring gear R3 outputs power to the second connecting member L2, and in the second planetary row P2, the second connecting member L2 outputs power to the second sun gear S2, and the second sun gear S2 diverts the power again and outputs it to the second planet carrier PC2 and the second ring gear R2 respectively; the planetary row group with two degrees of freedom realizes a hybrid transmission of two-stage transmission in parallel with three-stage transmission. Actuating one operating member eliminates another degree of freedom, thereby achieving fixed input and output.

[0081] In the above four embodiments, n1 planetary gears are arranged in parallel on the input shaft IN to form the first planetary gear set PZ1; n2 planetary gears are arranged in parallel on the output shaft OUT to form the second planetary gear set PZ2; and each planetary gear in the two planetary gear sets is provided with a corresponding brake.

[0082] The n1 planetary gears in the first planetary gear set PZ1 and the n2 planetary gears in the second planetary gear set PZ2 are combined in pairs, with a total of n1×n2 combinations. The brakes set on a pair of planetary gears in each of the n1×n2 combinations are braked simultaneously to realize a two-stage transmission. The rotation direction of the power output is the same as the rotation direction of the power input, and n1×n2 two-stage transmissions can be realized.

[0083] When the third brake B3 on the third planetary gear P3 is applied, a two-degree-of-freedom planetary gear set is formed, consisting of the first, second, and third planetary gears P1, P2, and P3. Sequentially applying the brakes on the n1 planetary gears of the first planetary gear set PZ1 and the n2 planetary gears of the second planetary gear set PZ2 eliminates another degree of freedom, achieving fixed input and output. The direction of rotation of the power output is the same as that of the power input, thus realizing a hybrid transmission with n1+n2 two-stage transmissions connected in parallel to a three-stage transmission. The third planetary gear P3 is combined with the connected first and second planetary gears P1 and P2 in two possible combinations. In each combination, the brakes on a pair of planetary gears are applied simultaneously, achieving a two-stage transmission result in which only the first ring gear R1 (or first sun gear S1) and the second ring gear R2 (or second sun gear S2) are braked simultaneously. Ultimately, (n1-1)+(n2-1) hybrid transmission gears with practical transmission efficiency are realized, with the power output direction being the same as that of the power input.

[0084] The third brake B3 and the planetary carrier brake BL3 are engaged at the same time, and the power passes through the first planetary gear P1, the first connecting member L1, the third planetary gear P3, the second connecting member L2 and the second planetary gear P2 in sequence, realizing a three-stage transmission. The output power rotation direction is opposite to the input power rotation direction, realizing one gear.

[0085] The planetary multi-stage transmission speed change mechanism is applied to two planetary gear sets, which can realize the number of forward gears in the same direction as the power input direction is n1×n2+(n1-1)+(n2-1), and the number of reverse gears in the opposite direction of the power input direction is 1.

[0086] The above-mentioned planetary multi-stage transmission speed change mechanism is an application demonstration in which the number of planetary gears n1 of the first planetary gear set PZ1 is 1, and the number of planetary gears n2 of the second planetary gear set PZ2 is 1.

[0087] In addition, in the above embodiments, two power flows are allowed: the first is that power flows in from the input shaft IN and flows out from the output shaft OUT; the second is that power flows in from the output shaft OUT and flows out from the input shaft IN.

[0088] The first brake B1, the second brake B2, the third brake B3 and the planetary carrier brake BL3 are all friction-type operating structures.

[0089] Fifth embodiment:

[0090] refer to Figure 5A planetary multi-stage transmission speed change mechanism adopts the first embodiment and adds a fifth planetary row P5, a fourth planetary row P4 and a sixth planetary row P6 on the basis of the first embodiment; the arrangement is as follows: the fifth planetary row P5, the first planetary row P1, the third planetary row P3, the second planetary row P2, the fourth planetary row P4 and the sixth planetary row P6 are sequentially arranged in parallel;

[0091] The fifth planetary gear P5 includes the fifth sun gear S5, the fifth planet carrier PC5, the fifth planetary gear CA5 and the fifth ring gear R5. The fifth planetary gear CA5 is movably mounted on the fifth planet carrier PC5. The fifth ring gear R5 is engaged with the fifth planetary gear CA5. The fifth planetary gear CA5 is engaged with the fifth sun gear S5. The fifth ring gear R5 is braked by the fifth brake B5.

[0092] The first planetary row P1 includes a first sun gear S1, a first planetary carrier PC1, a first planetary gear CA1 and a first ring gear R1. The first planetary gear CA1 is movably mounted on the first planetary carrier PC1. The first ring gear R1 is meshed with the first planetary gear CA1. The first planetary gear CA1 is meshed with the first sun gear S1. The first ring gear R1 is braked by a first brake B1.

[0093] The third planetary row P3 includes a third sun gear S3, a third planet carrier PC3, a third planetary gear CA3 and a third ring gear R3. The third planetary gear CA3 is movably mounted on the third planet carrier PC3. The third ring gear R3 is engaged with the third planetary gear CA3. The third planetary gear CA3 is engaged with the third sun gear S3. The third sun gear S3 is movably mounted on the planet carrier connecting shaft L3. The third planet carrier PC3 is braked by the third brake B3.

[0094] The second planetary row P2 includes a second sun gear S2, a second planetary carrier PC2, a second planetary gear CA2 and a second ring gear R2. The second planetary gear CA2 is movably mounted on the second planetary carrier PC2. The second ring gear R2 is engaged with the second planetary gear CA2. The second planetary gear CA2 is engaged with the second sun gear S2. The second ring gear R2 is braked by the second brake B2.

[0095] The fourth planetary gear P4 includes a fourth sun gear S4, a fourth planet carrier PC4, a fourth planetary gear CA4 and a fourth ring gear R4. The fourth planetary gear CA4 is movably mounted on the fourth planet carrier PC4. The fourth ring gear R4 is engaged with the fourth planetary gear CA4. The fourth planetary gear CA4 is engaged with the fourth sun gear S4. The fourth ring gear R4 is braked by the fourth brake B4.

[0096] The sixth planetary gear P6 includes the sixth sun gear S6, the sixth planet carrier PC6, the sixth planetary gear CA6 and the sixth ring gear R6. The sixth planetary gear CA6 is movably mounted on the sixth planet carrier PC6. The sixth ring gear R6 is engaged with the sixth planetary gear CA6. The sixth planetary gear CA6 is engaged with the sixth sun gear S6. The sixth ring gear R6 is braked by the sixth brake B6.

[0097] The fifth sun gear S5 and the first sun gear S1 are fixedly connected to the input shaft IN, and the fifth planet carrier PC5 is fixedly connected to the first planet carrier PC1. A planet carrier brake BL3 is provided on the fifth planet carrier PC5. The planet carrier brake BL3 can brake the fifth planet carrier PC5.

[0098] The second sun gear S2, the fourth sun gear S4, and the sixth sun gear S6 are fixedly connected to the output shaft OUT; the second ring gear R2 is fixedly connected to the fourth planet carrier PC4 through the fourth connecting member L4, and the fourth planet carrier PC4 is fixedly connected to the sixth planet carrier PC6.

[0099] Optionally, the input shaft IN, 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 are coaxially arranged; power flow direction: power flows into the input shaft IN and flows out of the output shaft OUT.

[0100] The fifth planetary gear P5 and the first planetary gear P1 form the first planetary gear group PZ1, with the number of planetary gears n1 = 2. The second planetary gear P2, the fourth planetary gear P4, and the sixth planetary gear P6 form the second planetary gear group PZ2, with the number of planetary gears 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 reverse gears is 1.

[0101] The third brake B3 and the fourth brake B4 are engaged simultaneously to achieve first forward gear;

[0102] The third brake B3 and the sixth brake B6 are engaged simultaneously to achieve the second forward gear;

[0103] The first brake B1 and the fourth brake B4 are engaged simultaneously to achieve third forward gear;

[0104] The first brake B1 and the sixth brake B6 are engaged simultaneously to achieve the fourth forward gear;

[0105] The fifth brake B5 and the fourth brake B4 are engaged simultaneously to achieve the fifth forward gear;

[0106] The fifth brake B5 and the sixth brake B6 are engaged simultaneously to achieve the sixth forward gear;

[0107] The first brake B1 and the second brake B2 are engaged simultaneously to achieve the seventh forward gear;

[0108] The fifth brake B5 and the second brake B2 are engaged simultaneously to achieve the eighth forward gear;

[0109] The fifth brake B5 and the third brake B3 are engaged simultaneously to achieve the ninth forward gear;

[0110] The planetary carrier brake BL3 and the third brake B3 are engaged simultaneously to achieve one reverse gear.

[0111] The relevant calculation formulas are shown in Table 1.1, and the control logic and transmission ratio of each gear are shown in Table 1.2.

[0112] Table 1.1 Calculation formula for each gear:

[0113]

[0114] The K value of a planetary gear set refers to the ratio of the number of teeth on the planetary gear ring to the number of teeth on the sun gear. The tooth ratio of the first ring gear R1 of the first planetary gear set P1 to the first sun gear S1 is K1. Similarly, the tooth ratios of the first planetary gear set P1 to the sixth planetary gear set P6 are K1 to K6, respectively. When K1 = 5, K2 = 6, K3 = K4 = K5 = 3, and K6 = 6 in Table 1.1, and the input speed is 1, the transmission ratios of each gear shown in Table 1.1 can be obtained, realizing a transmission mechanism with nine forward gears and one reverse gear.

[0115] The calculation formula in Table 1.1 also reveals how the two-degree-of-freedom planetary gear set composed of the first planetary gear set P1, the second planetary gear set P2 and the third planetary gear set P3 works to expand the transmission ratio range when the third brake B3 is applied. Compared with the speed formula of the F3 gear operating parts B1-B4 combination, the F1 gear operating parts B3-B4 combination has an additional coefficient (K2+1)×K1×K3 composed of K1, K2 and K3 in the denominator, thereby reducing the speed and increasing the transmission ratio; compared with the speed formula of the F4 gear operating parts B1-B6 combination, the F2 gear operating parts B3-B6 combination has an additional coefficient (K2+1)×K1×K3 composed of K1, K2 and K3 in the denominator, thereby reducing the speed and increasing the transmission ratio; compared with the speed formula of the F8 gear operating parts B5-B2 combination, the F9 gear operating parts B5-B3 combination has an additional coefficient [(K1+1) / (K5+1)-1]×K2 / K1 / K3, when K1>K5, the coefficient is a positive number, which increases the speed and reduces 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 is braked, the direction of the first ring gear R1 is the same as the direction of the first planetary carrier PC1. When the third brake B3 is braked, it can ensure that the direction of power output to the second ring gear R2 through the first ring gear R1, the first connecting member L1, the third sun gear S3, the third ring gear R3, and the second connecting member L2 is different from the rotation direction of the second planetary carrier PC2, thereby avoiding circulating power when the second ring gear R2 and the second planetary carrier PC2 jointly output power.

[0116] Table 1.2 Control logic and transmission ratio of each gear (O means the control part is engaged)

[0117]

[0118] The following combination Figure 5 The examples of the present invention are described in detail in Table 1.2. The transmission ratio refers to the ratio of the input shaft speed to the output shaft speed.

[0119] The third brake B3 and the fourth brake B4 are engaged at the same time, fixing the third planet carrier PC3 and the fourth ring gear R4 respectively, and the first sun gear S1 is fixedly connected to the input shaft IN, rotating in the same direction and speed; in the first planetary row P1, the first sun gear S1 inputs power, and the power is divided into two transmission paths, the first path is transmitted through the first planetary row PC1 in a two-stage transmission mode, and the second path is transmitted through the first ring gear R1 in a three-stage transmission mode; in the first transmission path, in the first planetary row P1, the first sun gear S1 outputs power to the first planetary row PC1, and the first planetary row PC1 outputs power to the planetary row connecting shaft L3, and in the second planetary row P2, the planetary row connecting shaft L3 outputs power to the second planetary row PC2, and the power of the second planetary row PC2 is divided again and output to the second ring gear R2 and the second sun gear S2 respectively; in the second transmission path, in the first planetary row P1, the first sun gear S1 outputs power to the first ring gear R1 through the first planetary gear CA1, and the first The ring gear R1 outputs power to the first connecting member L1. In the third planetary row P3, the first connecting member L1 outputs power to the third sun gear S3. The third sun gear S3 outputs power to the third ring gear R3 through the third planetary gear CA3. The third ring gear R3 outputs power to the second connecting member L2. In the second planetary row P2, the second connecting member L2 outputs power to the second ring gear R2. The second ring gear R2 is fixedly connected to the fourth planet carrier PC4 through the fourth connecting member L4. The power of the second ring gear R2 is split again and output to the second planet carrier PC2, the second sun gear S2 and the fourth planet carrier PC4 respectively; the output shaft OUT is a rigid structure. Since the fourth ring gear R4 is fixed, the speed ratio between the fourth planet carrier PC4 and the fourth sun gear S4 is determined, which has restricted another degree of freedom of the planetary row group. Finally, the second planet carrier PC2, the second ring gear R2, and the fourth planet carrier PC4 jointly output power to the output shaft OUT through the second sun gear S2 and the fourth sun gear S4 to achieve first forward gear.

[0120] The third brake B3 and the sixth brake B6 are engaged at the same time, fixing the third planet carrier PC3 and the sixth ring gear R6 respectively, and the first sun gear S1 is fixedly connected to the input shaft IN, rotating in the same direction and speed; in the first planetary row P1, the first sun gear S1 inputs power, and the power is divided into two transmission paths, the first path is transmitted through the first planetary row PC1 in a two-stage transmission mode, and the second path is transmitted through the first ring gear R1 in a three-stage transmission mode; in the first transmission path, in the first planetary row P1, the first sun gear S1 outputs power to the first planetary row PC1, and the first planetary row PC1 outputs power to the planetary row connecting shaft L3, and in the second planetary row P2, the planetary row connecting shaft L3 outputs power to the second planetary row PC2, and the power of the second planetary row PC2 is divided again and output to the second ring gear R2 and the second sun gear S2 respectively; in the second transmission path, in the first planetary row P1, the first sun gear S1 outputs power to the first ring gear R1 through the first planetary gear CA1, and the first ring gear R1 The power is output to the first connecting member L1. In the third planetary row P3, the first connecting member L1 outputs power to the third sun gear S3. The third sun gear S3 outputs power to the third ring gear R3 through the third planetary gear CA3. The third ring gear R3 outputs power to the second connecting member L2. In the second planetary row P2, the second connecting member L2 outputs power to the second ring gear R2. The second ring gear R2 is fixedly connected to the fourth planet carrier PC4 and the sixth planet carrier PC6 through the fourth connecting member L4. The power of the second ring gear R2 is split again and output to the second planet carrier PC2, the second sun gear S2 and the sixth planet carrier PC6 respectively; the output shaft OUT is a rigid structure. Since the sixth ring gear R6 is fixed, the speed ratio between the sixth planet carrier PC6 and the sixth sun gear S6 is determined, which has restricted another degree of freedom of the planetary row group. Finally, the second planet carrier PC2, the second ring gear R2, and the sixth planet carrier PC6 jointly output power to the output shaft OUT through the second sun gear S2 and the sixth sun gear S6, realizing the second forward gear.

[0121] The first brake B1 and the fourth brake B4 are engaged simultaneously, respectively fixing the first ring gear R1 and the fourth ring gear R4. The first sun gear S1 is fixedly connected to the input shaft IN, rotating in the same direction and speed. In the first planetary row P1, the first sun gear S1 inputs power. Since the first ring gear R1 is fixed, the first planet carrier PC1 rotates in the same direction as the input shaft IN. The first planet carrier PC1 is fixedly connected to the second planet carrier PC2 via the planetary carrier connecting shaft L3. In the second planetary row P2, the second planet carrier PC2 inputs power, and the second sun gear S2 and the second ring gear R2 output power. The second sun gear S2 is fixedly connected to the output shaft OUT, driving the output shaft OUT to rotate. The second ring gear R2 is fixedly connected to the fourth planetary row PC4 via the fourth connecting member L4, and the second ring gear R2 drives the fourth planetary row PC4 to rotate. In the fourth planetary row P4, the fourth ring gear R4 is fixed, and the fourth sun gear S4 outputs power. The output shaft OUT is a rigid structure. Ultimately, the second sun gear S2 and the fourth sun gear S4 jointly output power to the output shaft OUT, achieving the third forward gear.

[0122] The first brake B1 and the sixth brake B6 are simultaneously engaged, respectively fixing the first ring gear R1 and the sixth ring gear R6. The first sun gear S1 is fixedly connected to the input shaft IN, rotating in the same direction and speed. In the first planetary gear P1, the first sun gear S1 receives power. Since the first ring gear R1 is fixed, the first planet carrier PC1 rotates in the same direction as the input shaft IN. The first planet carrier PC1 is fixedly connected to the second planet carrier PC2 via the planetary carrier connecting shaft L3. In the second planetary gear P2, the second planet carrier PC2 receives power, and the second sun gear S2 and the second ring gear R2 output power. The second sun gear S2 is fixedly connected to the output shaft OUT, driving the output shaft OUT to rotate. The second ring gear R2 is fixedly connected to the fourth planet carrier PC4 and the sixth planet carrier PC6 via the fourth connecting member L4. The second ring gear R2 drives the sixth planet carrier PC6 to rotate. In the sixth planetary gear P6, the sixth ring gear R6 is fixed, and the sixth sun gear S6 outputs power. The output shaft OUT is a rigid structure. Ultimately, the second sun gear S2 and the sixth sun gear S6 jointly output power to the output shaft OUT, achieving the fourth forward gear.

[0123] The fifth brake B5 and the fourth brake B4 are engaged at the same time, fixing the fifth ring gear R5 and the fourth ring gear R4 respectively. The fifth sun gear S5 is fixedly connected to the input shaft IN and rotates in the same direction and speed. In the fifth planetary gear P5, the fifth sun gear S5 inputs power. Since the fifth ring gear R5 is fixed, the fifth planetary carrier PC5 is fixedly connected to the first planetary carrier PC1. The first planetary carrier PC1 rotates in the same direction as the input shaft IN. The first planetary carrier PC1 is fixedly connected to the second planetary carrier PC2 through the planetary carrier connecting shaft L3. In the second planetary gear P2, the second planetary carrier PC1 rotates in the same direction as the input shaft IN. The planet carrier PC2 inputs power, the second sun gear S2 and the second ring gear R2 output power, the second sun gear S2 is fixedly connected to the output shaft OUT, driving the output shaft OUT to rotate; the second ring gear R2 is fixedly connected to the fourth planet carrier PC4 through the fourth connecting member L4, and the second ring gear R2 drives the fourth planet carrier PC4 to rotate; in the fourth planetary row P4, the fourth ring gear 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, realizing the fifth forward gear.

[0124] The fifth brake B5 and the sixth brake B6 are engaged at the same time, fixing the fifth ring gear R5 and the sixth ring gear R6 respectively. The fifth sun gear S5 is fixedly connected to the input shaft IN and rotates in the same direction and speed. In the fifth planetary gear P5, the fifth sun gear S5 inputs power. Since the fifth ring gear R5 is fixed, the fifth planetary carrier PC5 is fixedly connected to the first planetary carrier PC1. The first planetary carrier PC1 rotates in the same direction as the input shaft IN. The first planetary carrier PC1 is fixedly connected to the second planetary carrier PC2 through the planetary carrier connecting shaft L3. In the second planetary gear P2, the second planetary carrier PC 2 input power, the second sun gear S2 and the second ring gear R2 output power, and the second sun gear S2 is fixedly connected to the output shaft OUT, driving the output shaft OUT to rotate; the second ring gear R2 is fixedly connected to the fourth planet carrier PC4 and the sixth planet carrier PC6 through the fourth connecting member L4, and the second ring gear R2 drives the sixth planet carrier PC6 to rotate; in the sixth planetary row P6, the sixth ring gear 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 the sixth forward gear.

[0125] The first brake B1 and the second brake B2 are engaged simultaneously, fixing the first ring gear R1 and the second ring gear R2 respectively. The first sun gear S1 is fixedly connected to 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. Since the first ring gear R1 is fixed, the first planet carrier PC1 rotates in the same direction as the input shaft IN. The first planet carrier PC1 is fixedly connected to the second planet carrier PC2 through the planetary carrier connecting shaft L3. In the second planetary row P2, the second planet carrier PC2 inputs power, the second ring gear R2 is fixed, and the second sun gear S2 outputs power to the output shaft OUT, realizing the seventh forward gear.

[0126] The fifth brake B5 and the second brake B2 are engaged simultaneously, fixing the fifth ring gear R5 and the second ring gear R2 respectively, and the fifth sun gear S5 is fixedly connected to the input shaft IN, rotating in the same direction and speed; in the fifth planetary row P5, the fifth sun gear S5 inputs power, and since the fifth ring gear R5 is fixed, the fifth planet carrier PC5 is fixedly connected to the first planet carrier PC1, and the first planet carrier PC1 rotates in the same direction as the input shaft IN; the first planet carrier PC1 is fixedly connected to the second planet carrier PC2 through the planetary carrier connecting shaft L3. In the second planetary row P2, the second planet carrier PC2 inputs power, the second ring gear R2 is fixed, and the second sun gear S2 outputs power to the output shaft OUT, realizing the eighth forward gear.

[0127] The fifth brake B5 and the third brake B3 are engaged simultaneously, fixing the fifth ring gear R5 and the third planet carrier PC3 respectively, and the fifth sun gear S5 is fixedly connected to the input shaft IN, rotating in the same direction and speed; in the fifth planetary row P5, the fifth sun gear S5 inputs power, and since the fifth ring gear R5 is fixed, the speed of the fifth planetary carrier PC5 is determined, and it rotates in the same direction as the input shaft IN; in the first planetary row P1, the first sun gear S1 inputs power, and the power is split into two transmission paths, the first path is transmitted through the first planetary carrier PC1 in a two-stage transmission mode, and the second path is transmitted through the first ring gear R1 in a three-stage transmission mode; in the first transmission path, in the first planetary row P1, the first sun gear S1 outputs power to the first planetary carrier PC1, and the first planetary carrier PC1 outputs power to the planetary carrier connecting shaft L3. In the second planetary row P2, the planetary carrier connecting shaft L3 outputs power to the second planetary carrier PC2, and the power of the second planetary carrier PC2 is split again and divided The power is output to the second ring gear R2 and the second sun gear S2 respectively; in the second transmission, in the first planetary row P1, the first sun gear S1 outputs power to the first ring gear R1 through the first planetary gear CA1, and the first ring gear R1 outputs power to the first connecting member L1. In the third planetary row P3, the first connecting member L1 outputs power to the third sun gear S3, and the third sun gear S3 outputs power to the third ring gear R3 through the third planetary gear CA3. The third ring gear R3 outputs power to the second connecting member L2. In the second planetary row P2, the second connecting member L2 outputs power to the second ring gear R2. The power of the second ring gear R2 is diverted again and output to the second planet carrier PC2 and the second sun gear S2 respectively; since the fifth ring gear R5 is fixed, the speed of the fifth planet carrier PC5 is determined, which has limited another degree of freedom of the planetary row group. Finally, the second planetary carrier PC2 and the second ring gear R2 jointly output power to the output shaft OUT through the second sun gear S2 to achieve ninth forward gear.

[0128] The planetary carrier brake BL3 and the third brake B3 are engaged simultaneously, respectively fixing the fifth planetary carrier PC5, the first planetary carrier PC1, the second planetary carrier PC2, and the third planetary carrier PC3. The first sun gear S1 is fixedly connected to 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 ring gear R1 rotates in the opposite direction to the input shaft IN. The first ring gear R1 and the third sun gear S3 are fixedly connected by the first connecting member L1. In the third planetary row P3, the third sun gear S3 inputs power, the third planetary carrier PC3 is fixed, and the third ring gear R3 rotates in the same direction as the input shaft IN. The third ring gear R3 and the second ring gear R2 are fixedly connected by the second connecting member L2. In the second planetary row P2, the second ring gear R2 inputs power, the second planetary carrier PC2 is fixed, and the second sun gear S2 rotates in the opposite direction to the input shaft IN. The second sun gear S2 is fixedly connected to the output shaft OUT and outputs power to the output shaft OUT, achieving first reverse gear.

[0129] The transmission ratios of the above-mentioned gears are determined by the K values ​​of the six planetary gears. The K value of the planetary gear refers to the ratio of the number of teeth on the planetary gear ring to the number of teeth on the sun gear. For example, when K1=5, K2=6, K3=K4=K5=3, and K6=6, the transmission ratios of the gears shown in Table 1.1 can be obtained, realizing a transmission mechanism with nine forward gears and one reverse gear, and the first gear ratio is greater than 5, which can reduce the load on the torque converter when the vehicle is operating at low speeds and improve the reliability of the torque converter. At the same time, the large speed ratio can make the engine operate more in the economic working area, thereby improving the economy of the entire machine.

[0130] From the shifting 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 sliding friction work and heat loss of the friction plate and improve the reliability of the friction plate.

[0131] Optionally, 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 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 ring gear R3 to the number of teeth of the third sun gear S3 is 3. The ratio of the number of teeth of the fourth ring gear 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 ring gear R6 to the number of teeth of the sixth sun gear S6 is 6.

[0132] Optionally, the transmission ratio of the first forward gear is 5.89, the transmission ratio of the second forward gear is 3.73, the transmission ratio of the third forward gear is 2.14, the transmission ratio of the fourth forward gear is 1.59, the transmission ratio of the fifth forward gear is 1.43, the transmission ratio of the sixth forward gear is 1.06, the transmission ratio of the seventh forward gear is 0.86, the transmission ratio of the eighth forward gear is 0.57, and the transmission ratio of the ninth forward gear is 0.51; the transmission ratio of the first reverse gear is 2.50.

[0133] Optionally, the step ratio of the first forward gear to the second forward gear is 1.58, the step ratio of the second forward gear to the third forward gear is 1.74, the step ratio of the third forward gear to the fourth forward gear is 1.35, the step ratio of the fourth forward gear to the fifth forward gear is 1.11, the step ratio of the fifth forward gear to the sixth forward gear is 1.35, the step ratio of the sixth forward gear to the seventh forward gear is 1.24, the step ratio of the seventh forward gear to the eighth forward gear is 1.50, and the step ratio of the eighth forward gear to the ninth forward gear is 1.11; the transmission ratio range between the highest gear and the lowest gear is 11.49.

[0134] This embodiment discloses a planetary multi-stage transmission speed change mechanism for a vehicle transmission system. Figure 5 As shown, it includes an input shaft IN, an output shaft OUT, six planetary gears (P1-P6), seven brakes (BL3, B1-B6), and four connecting parts (L1-L4).

[0135] Each planetary gear row includes: sun gear (S1~S6), planet carrier (PC1~PC6), planet gear (CA1~CA6) and ring gear (R1~R6); the ring gear is coaxial with the sun gear, and the planet gears are respectively mounted on the planet carrier through planet shafts and bearings, and each planet gear is internally meshed with the ring gear on the same planetary gear row and externally meshed with the sun gear on the same planetary gear row.

[0136] The six planetary gears are arranged in parallel from left to right, and the six sun gears, the input shaft IN and the output shaft OUT are arranged coaxially.

[0137] The vehicle transmission system in this application utilizes a planetary multi-stage transmission mechanism, including six planetary gears and seven brakes. Each planetary gear is a simple single-planet gear, capable of achieving up to nine forward gears and one reverse gear. The forward gear ratio is greater than 5, resulting in a wide range of gears, a wide ratio range, and small and uniform step ratios. This allows the engine to operate more efficiently within its operating range, improving overall vehicle efficiency. The seven brakes are all friction-operated, and the gear position is controlled by two elements, reducing frictional work and heat loss on the friction plates and improving their reliability.

[0138] Sixth embodiment:

[0139] like Figure 6 As shown, a planetary multi-stage transmission speed change mechanism is applied to the above-mentioned second embodiment, and a dual clutch C1 and a motor MG are additionally provided on the basis of the second embodiment.

[0140] The transmission speed change mechanism includes an input shaft IN, a dual clutch C1, a motor MG, a first planetary gear P1, a third planetary gear P3, a second planetary gear P2 and an output shaft OUT;

[0141] The input shaft IN is fixedly connected to the dual clutch C1. The first clutch C11 of the dual clutch C1 is fixedly connected to the fourth connecting member L4. The fourth connecting member L4 is provided with a fourth brake B4. The fourth connecting member L4 is provided with a first planetary gear P1. The first sun gear S1 is fixedly connected to the fourth connecting member L4. The output shaft OUT is provided with a second planetary gear P2. The second ring gear R2 is fixedly connected to the output shaft OUT.

[0142] The dual clutch C1 includes a first clutch group C11 and a second clutch group C12; the second clutch group C12 is provided with a first driving gear G11, and the first driving gear G11 is fixedly connected to the second clutch group C12; the motor MG is arranged in parallel, and the main shaft of the motor MG is parallel to the input shaft IN. One end of the motor MG is connected to the second clutch group C12, and the other end is connected to the first ring gear R1. The first driven gear G12 is fixedly mounted on the motor MG and meshes with the first driving gear G11; the second driven gear G22 is fixedly connected to the first ring gear R1, and the second driving gear G21 is fixedly mounted on the motor MG and meshes with the second driven gear G22.

[0143] The first planetary gear P1 includes a first sun gear S1, a first planet carrier PC1, a first planetary gear CA1, and a first ring gear R1. The first planetary gear CA1 is movably mounted on the first planet carrier PC1. The first ring gear R1 meshes with the first planetary gear CA1, and the first planetary gear CA1 meshes with the first sun gear S1. The first ring gear R1 is braked by a first brake B1, and the first sun gear S1 is braked by a fourth brake B4.

[0144] The third planetary gear P3 includes a third sun gear S3, a third planet carrier PC3, a third planetary gear CA3, and a third ring gear R3. The third planetary gear CA3 is movably mounted on the third planet carrier PC3. The third ring gear R3 meshes with the third planetary gear CA3. The third planetary gear CA3 meshes with the third sun gear S3. The third sun gear S3 is movably mounted on the planet carrier connecting shaft L3. The third planet carrier PC3 is braked by a third brake B3.

[0145] The second planetary row P2 includes a second sun gear S2, a second planetary carrier PC2, a second planetary gear CA2, and a second ring gear R2. The second planetary gear CA2 is movably mounted on the second planetary carrier PC2. The second ring gear R2 meshes with the second planetary gear CA2. The second planetary gear CA2 meshes with the second sun gear S2. The second sun gear S2 is movably mounted on the planetary carrier connecting shaft L3. The second sun gear S2 is braked by the second brake B2. The second planetary carrier PC2 is provided with a planetary carrier brake BL3 to achieve braking.

[0146] The first clutch group C11 and the first sun gear S1 are fixedly connected via the fourth connecting member L4. The fourth connecting member L4 is connected to the fourth brake B4. The fourth connecting member L4 is fixedly connected to the first sun gear S1. The first sun gear S1 is braked by the fourth brake B4.

[0147] Optionally, the dual clutch C1, input shaft IN, first sun gear S1, third sun gear S3, second sun gear S2 and output shaft OUT are coaxially arranged; the motor MG is arranged parallel to the input shaft IN; power flow direction: power flows into the input shaft IN and flows out of the output shaft OUT.

[0148] The internal combustion engine can achieve six forward gears and one reverse gear.

[0149] The first clutch C11 is engaged, and the first brake B1 and the second brake B2 are engaged simultaneously, achieving first forward gear;

[0150] The second clutch group C12 is engaged, and the third brake B3 and the planetary carrier brake BL3 are engaged simultaneously to achieve the second forward gear;

[0151] The second clutch C12 is engaged, and the second brake B2 and the fourth brake B4 are engaged simultaneously to achieve third forward gear;

[0152] The first clutch group C11 and the second clutch group C12 are engaged simultaneously, and the second brake B2 is engaged to achieve the fourth forward gear;

[0153] The second clutch C12 is engaged, and the third brake B3 and the fourth brake B4 are engaged simultaneously to achieve the fifth forward gear;

[0154] The first clutch group C11 and the second clutch group C12 are engaged simultaneously, and the third brake B3 is engaged to achieve the sixth forward gear;

[0155] The first clutch C11 is engaged, and the third brake B3 and the planetary carrier brake BL3 are engaged at the same time to achieve one reverse gear.

[0156] The motor can achieve three forward gears when driven alone, and three reverse gears with the same gears when the motor is reversed.

[0157] The third brake B3 and the planetary carrier brake BL3 are engaged simultaneously to achieve first forward gear;

[0158] The second brake B2 and the fourth brake B4 are engaged simultaneously to achieve the second forward gear;

[0159] The third brake B3 and the fourth brake B4 are engaged simultaneously to realize the third forward gear.

[0160] The relevant calculation formulas are shown in Table 2.1 and Table 3.1, and the control logic and transmission ratio of each gear are shown in Table 2.2 and Table 3.2.

[0161] Table 2.1 Calculation formula for each gear position driven by internal combustion engine power alone

[0162]

[0163]

[0164] The K value of the planetary gear set refers to the ratio of the number of teeth on the planetary gear ring to the number of teeth on the sun gear. In the table above, K1=6, K2=4, and K3=3. When the transmission ratio KG1 of the gear set G11:G12 is 0.4 and the transmission ratio KG2 of the gear set G21:G22 is 4, and the input speed is 1, the transmission ratios of each gear shown in Table 2.1 can be obtained, realizing a transmission mechanism with six forward gears and one reverse gear.

[0165] Table 2.2 Control logic and transmission ratio of each gear position driven by internal combustion engine power alone (O indicates that the control element is engaged)

[0166]

[0167] The following combination Figure 6 Table 2.2 provides a detailed description of the example of the internal combustion engine power-only drive of the present invention. The transmission ratio refers to the ratio of the input shaft speed to the output shaft speed.

[0168] The first clutch C11 is engaged, and the first brake B1 and the second brake B2 are engaged at the same time, fixing the first ring gear R1 and the second sun gear S2 respectively. The first sun gear S1 is fixedly connected to the fourth connecting member L4 and is fixedly connected to the input shaft IN through the first clutch C11, rotating in the same direction and speed; in the first planetary row P1, the first sun gear S1 inputs power, and since the first ring gear R1 is fixed, the first planet carrier PC1 rotates in the same direction as the input shaft IN; the first planet carrier PC1 is fixedly connected to the second planet carrier PC2 through the planetary carrier connecting shaft L3. In the second planetary row P2, the second planet carrier PC2 inputs power, the second sun gear S2 is fixed, and the second ring gear R2 outputs power to the output shaft OUT, achieving first forward gear.

[0169] The second clutch C12 is engaged, and the third brake B3 and the planetary carrier brake BL3 are engaged at the same time, fixing the first planetary carrier PC1, the second planetary carrier PC2 and the third planetary carrier PC3 respectively; the first driving gear G11 is fixedly connected to the second clutch C12, and is fixedly connected to the input shaft IN through the second clutch C12, rotating in the same direction and speed; the first driven gear G12 is fixedly mounted on the motor MG and meshes with the first driving gear G11, rotating in the opposite direction to the input shaft IN; the second driven gear G22 is fixedly connected to the first ring gear R1, the second driving gear G21 is fixedly mounted on the motor MG and meshes with the second driven gear G22, and the second driven gear G22 is fixed to the input shaft IN The rotation direction is the same; the second driven gear G22 is fixedly connected to the first ring gear R1, and the first ring gear R1 rotates in the same direction as the input shaft IN; the first ring gear R1 and the third ring gear R3 are fixedly connected by the first connecting member L1, and in the third planetary row P3, the third ring gear R3 inputs power, the third planetary carrier PC3 is fixed, and the third sun gear S3 rotates in the opposite direction to the input shaft IN; the third sun gear S3 and the second sun gear S2 are fixedly connected by the second connecting member L2, and in the second planetary row P2, the second sun gear S2 inputs power, the second planetary carrier PC2 is fixed, the second ring gear R2 rotates in the same direction as the input shaft IN, the second ring gear R2 is fixedly connected to the output shaft OUT, and the second ring gear R2 outputs power to the output shaft OUT, realizing the second forward gear.

[0170] The second clutch C12 is engaged, and the fourth brake B4 and the second brake B2 are engaged at the same time, fixing the first sun gear S1 and the second sun gear S2 respectively; the first driving gear G11 is fixedly connected to the second clutch C12, and is fixedly connected to the input shaft IN through the second clutch C12, rotating in the same direction and speed; the first driven gear G12 is fixedly mounted on the motor MG and meshes with the first driving gear G11, rotating in the opposite direction to the input shaft IN; the second driven gear G22 is fixedly connected to the first ring gear R1, the second driving gear G21 is fixedly mounted on the motor MG and meshes with the second driven gear G22, and the second driven gear G21 is fixedly mounted on the motor MG and meshes with the second driven gear G22. The driven gear G22 has the same rotation direction as the input shaft IN; the second driven gear G22 is fixedly connected to the first ring gear R1, and the first ring gear R1 rotates in the same direction as the input shaft IN; in the first planetary row P1, the first ring gear R1 inputs power, and since the first sun gear S1 is fixed, the first planetary carrier PC1 rotates in the same direction as the input shaft IN; the first planetary carrier PC1 is fixedly connected to the second planetary carrier PC2 through the planetary carrier connecting shaft L3. 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 same direction as the input shaft IN, and the second ring gear R2 outputs power to the output shaft OUT, realizing the third forward gear.

[0171] The first clutch C11 and the second clutch C12 are engaged simultaneously, the second brake B2 is engaged, and the second sun gear S2 is fixed; the first sun gear S1 is fixedly connected to the fourth connecting member L4, and is fixedly connected to the input shaft IN through the first clutch C11, and rotates in the same direction and speed; the first driving gear G11 is fixedly connected to the second clutch C12, and is fixedly connected to the input shaft IN through the second clutch C12, and rotates in the same direction and speed; the first driven gear G12 is fixedly mounted on the motor MG and meshes with the first driving gear G11, rotating in the opposite direction to the input shaft IN; the second driven gear G22 is fixedly connected to the first ring gear R1, and the second driving gear G21 is fixedly mounted on the motor MG On the first planetary gear S1, the first planetary gear S1 is fixedly connected to the second planetary gear S2, and meshes with the second driven gear G22. The second driven gear G22 has the same rotation direction as the input shaft IN; the second driven gear G22 is fixedly connected to the first ring gear R1, and the first ring gear R1 rotates in the same direction as the input shaft IN; the first sun gear S1 and the first ring gear R1 rotate in the same direction as 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 as the input shaft IN; the first planetary carrier PC1 is fixedly connected to the second planetary carrier PC2 through the planetary carrier connecting shaft L3. 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 same direction as the input shaft IN, and the second ring gear R2 outputs power to the output shaft OUT, realizing the fourth forward gear.

[0172] The second clutch C12 is engaged, and the fourth brake B4 and the third brake B3 are engaged at the same time, fixing the first sun gear S1 and the third planet carrier PC3 respectively; the first driving gear G11 is fixedly connected to the second clutch C12, and is fixedly connected to the input shaft IN through the second clutch C12, rotating in the same direction and speed; the first driven gear G12 is fixedly mounted on the motor MG and meshes with the first driving gear G11, and rotates in the opposite direction to the input shaft IN; the second driven gear G22 is fixedly connected to the first ring gear R1, and the second driving gear G21 is fixedly mounted on the motor MG and meshes with the second driven gear G22, and the second driven gear G22 has the same rotation direction as the input shaft IN; the second driven gear G22 is fixedly connected to the first ring gear R1, and the first ring gear R1 rotates in the same direction as the input shaft IN; in the first planetary row P1, the first ring gear R1 inputs power, and since the first sun gear S1 is fixed, the first The planet carrier PC1 rotates in the same direction as the input shaft IN; the first planet carrier PC1 is fixedly connected to the second planet carrier PC2 through the planet carrier connecting shaft L3, and the second planet carrier PC2 rotates in the same direction as the input shaft IN; the first ring gear R1 and the third ring gear R3 are fixedly connected through the first connecting member L1. In the third planetary row P3, the third ring gear R3 inputs power, the third planet carrier PC3 is fixed, and the third sun gear S3 rotates in the opposite direction to the input shaft IN. The third sun gear S3 and the second sun gear S2 are fixedly connected through the second connecting member L2, and the second sun gear S2 rotates in the opposite direction to the input shaft IN; in the second planetary row P2, the second planet carrier PC2 and the second sun gear S2 input power together, and the second ring gear R2 outputs power to the output shaft OUT; when the planet carrier and the sun gear input power together and the ring gear outputs power, the sun gear rotates in the opposite direction to the planet carrier, which can avoid circulating power, and the ring gear rotates in the same direction as the planet carrier, thereby achieving five forward gears.

[0173] The first clutch C11 and the second clutch C12 are engaged at the same time, the third brake B3 is engaged, and the third planet carrier PC3 is fixed; the first sun gear S1 is fixedly connected to the fourth connecting member L4, and is fixedly connected to the input shaft IN through the first clutch C11, and rotates in the same direction and speed; the first driving gear G11 is fixedly connected to the second clutch C12, and is fixedly connected to the input shaft IN through the second clutch C12, and rotates in the same direction and speed; the first driven gear G12 is fixedly mounted on the motor MG and meshes with the first driving gear G11, and rotates in the opposite direction to the input shaft IN; the second driven gear G22 is fixedly connected to the first ring gear R1, and the second driving gear G21 is fixedly mounted on the motor MG and meshes with the second driven gear G22, and the second driven gear G22 has the same rotation direction as the input shaft IN; the second driven gear G22 is fixedly connected to the first ring gear R1, and the first ring gear R1 rotates in the same direction as the input shaft IN; the first sun gear S1 and the first ring gear R1 rotate in the same direction as the input shaft IN; The first planet carrier PC1 rotates in the same direction as the input shaft IN; the first planet carrier PC1 is fixedly connected to the second planet carrier PC2 through the planet carrier connecting shaft L3, and the second planet carrier PC2 rotates in the same direction as the input shaft IN; the first ring gear R1 and the third ring gear R3 are fixedly connected by the first connecting member L1. In the third planetary row P3, the third ring gear R3 inputs power, the third planet carrier PC3 is fixed, and the third sun gear S3 rotates in the opposite direction to the input shaft IN. The third sun gear S3 and the second sun gear S2 are fixedly connected by the second connecting member L2, and the second sun gear S2 rotates in the opposite direction to the input shaft IN; in the second planetary row P2, the second planet carrier PC2 and the second sun gear S2 input power together, and the second ring gear R2 outputs power to the output shaft OUT; when the planet carrier and the sun gear input power together and the ring gear outputs power, the sun gear rotates in the opposite direction to the planet carrier, which can avoid circulating power. The ring gear rotates in the same direction as the planet carrier, thereby achieving the sixth forward gear.

[0174] The first clutch C11 is engaged, and the third brake B3 and the planetary carrier brake BL3 are engaged simultaneously, respectively fixing the first planetary carrier PC1, the second planetary carrier PC2, and the third planetary carrier PC3; the first sun gear S1 is fixedly connected to the fourth connecting member L4, and is fixedly connected to the input shaft IN through the first clutch C11, rotating 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 ring gear R1 rotates in the opposite direction to the input shaft IN; the first ring gear R1 and the third ring gear R3 are connected The third sun gear S3 and the second sun gear S2 are fixedly connected through the first connecting member L1. In the third planetary row P3, the third ring gear R3 inputs power, the third planet carrier PC3 is fixed, and the third sun gear S3 rotates in the same direction as the input shaft IN. The third sun gear S3 and the second sun gear S2 are fixedly connected through the second connecting member L2. In the second planetary row P2, the second sun gear S2 inputs power, the second planet carrier PC2 is fixed, the second ring gear R2 rotates in the opposite direction to the input shaft IN, and the second ring gear R2 is fixedly connected to the output shaft OUT. The second ring gear R2 outputs power to the output shaft OUT, realizing one reverse gear.

[0175] Table 3.1 Calculation formula for motor MG power drive alone

[0176]

[0177] The K value of the planetary gear set refers to the ratio of the number of teeth on the planetary gear ring to the number of teeth on the sun gear. In the table above, K1=6, K2=4, and K3=3. When the transmission ratio KG2=4 of the gear set G21:G22 and the input speed of the motor MG is 1, the transmission ratios of each gear shown in Table 3.1 can be obtained, realizing a three-gear transmission mechanism.

[0178] Table 3.2 Control logic and transmission ratio of each gear position driven by the motor MG power alone (O indicates that the control element is engaged)

[0179]

[0180] The following combination Figure 6 Table 3.2 provides a detailed description of the motor power alone drive example of the present invention. The transmission ratio refers to the ratio of the input shaft speed to the output shaft speed.

[0181] The third brake B3 and the planetary carrier brake BL3 are simultaneously engaged, respectively fixing the first planetary carrier PC1, the second planetary carrier PC2, and the third planetary carrier PC3. The second driving gear G21 is fixedly mounted on the motor MG and meshes with the second driven gear G22. The second driven gear G22 rotates in the opposite direction of the motor MG. The second driven gear G22 is fixedly connected to the first ring gear R1, which rotates in the opposite direction to the motor MG. The first ring gear R1 and the third ring gear R3 are fixedly connected by the first connecting member L1. In the third planetary row P3, the third ring gear R3 inputs power, the third planetary carrier PC3 is fixed, and the third sun gear S3 rotates in the same direction as the motor MG. The third sun gear S3 is fixedly connected to the second sun gear S2 by the second connecting member L2. In the second planetary row P2, the second sun gear S2 inputs power, the second planetary carrier PC2 is fixed, and the second ring gear R2 rotates in the opposite direction to the motor MG. The second ring gear R2 is fixedly connected to the output shaft OUT and outputs power to the output shaft OUT, achieving first gear.

[0182] The fourth brake B4 and the second brake B2 are engaged simultaneously, fixing the first sun gear S1 and the second sun gear S2 respectively; the second driving gear G21 is fixedly mounted on the motor MG and meshes with the second driven gear G22, and the rotation direction of the second driven gear G22 is opposite to that of the motor MG; the second driven gear G22 is fixedly connected to the first ring gear R1, and the first ring gear R1 rotates in the opposite direction to the motor MG; in the first planetary row P1, the first ring gear R1 inputs power, and since the first sun gear S1 is fixed, the first planet carrier PC1 rotates in the opposite direction to the motor MG; the first planet carrier PC1 is fixedly connected to the second planet carrier PC2 through the planetary carrier connecting shaft L3. In the second planetary row P2, the second planet carrier PC2 inputs power, the second sun gear S2 is fixed, the second ring gear R2 rotates in the opposite direction to the motor MG, and the second ring gear R2 outputs power to the output shaft OUT, realizing the second gear.

[0183] The fourth brake B4 and the third brake B3 are engaged at the same time, fixing the first sun gear S1 and the third planet carrier PC3 respectively; the second driving gear G21 is fixedly mounted on the motor MG and meshes with the second driven gear G22, and the second driven gear G22 rotates in the opposite direction to the motor MG; the second driven gear G22 is fixedly connected to the first ring gear R1, and the first ring gear R1 rotates in the opposite direction to the motor MG; in the first planetary row P1, the first ring gear R1 inputs power, and since the first sun gear S1 is fixed, the first planet carrier PC1 rotates in the opposite direction to the motor MG; the first planet carrier PC1 is fixedly connected to the second planet carrier PC2 through the planet carrier connecting shaft L3, and the second planet carrier PC2 rotates in the opposite direction to the motor MG; the first ring gear R1 and the third gear are fixedly connected. The ring R3 is fixedly connected by the first connecting member L1. In the third planetary row P3, the third ring gear R3 inputs power, the third planetary carrier PC3 is fixed, the third sun gear S3 rotates in the same direction as the motor MG, the third sun gear S3 and the second sun gear S2 are fixedly connected by the second connecting member L2, and the second sun gear S2 rotates in the same direction as the motor MG; in the second planetary row P2, the second planetary carrier PC2 and the second sun gear S2 jointly input power, the second ring gear R2 rotates in the opposite direction to the motor MG, and the second ring gear R2 outputs power to the output shaft OUT; when the planetary carrier and the sun gear jointly input power and the ring gear outputs power, the sun gear rotates in the opposite direction to the planetary carrier, which can avoid circulating power, and the ring gear rotates in the same direction as the planetary carrier, thereby realizing the third gear.

[0184] The motor MG can be controlled to rotate in the forward and reverse directions, thereby achieving three gears each for forward and reverse.

[0185] The transmission ratios for each of the aforementioned gears are determined by the transmission ratios of the two pairs of gear sets and the K values ​​of the three planetary gear sets. In this example, the gear set ratios are: KG1 = 0.4 for gear set G11:G12, and KG2 = 4 for gear set G21:G22. The planetary gear K value, which refers to the ratio of the number of teeth on the ring gear to the number of teeth on the sun gear, is K1 = 6, K2 = 4, and K3 = 3. This yields the transmission ratios for each gear shown in Tables 2.2 and 3.2, enabling a transmission mechanism with six forward gears and one reverse gear independently driven by the internal combustion engine, and a transmission mechanism with three forward gears and three reverse gears independently driven by the electric motor.

[0186] Optionally, during gear shifting, only the first clutch C11 is engaged, and the motor MG is connected in parallel with the internal combustion engine, using the motor MG as a generator to generate electricity. This, on the one hand, balances the load on the engine, allowing the engine to provide sufficient driving force during the gear shifting phase; 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 to generate electricity to charge the power battery, greatly improving the smoothness of gear shifting. During normal driving, the first clutch C11 and the second clutch C12 are engaged simultaneously, and the motor MG is driven in parallel with the internal combustion engine. The motor MG assists the internal combustion engine in its operation, and the output transmission ratio remains unchanged, thereby increasing the total output power and output torque.

[0187] Optionally, only the first clutch C11 is engaged, and the motor MG is driven in parallel with the internal combustion engine. The motor MG is used for speed and torque adjustment, which can achieve stepless speed change and realize the function of ECVT transmission. It can reduce the sliding friction work and heat loss of the clutch friction plate, improve power utilization efficiency, and improve the reliability of the friction plate.

[0188] Optionally, the internal combustion engine is placed in front and a rear-wheel drive motor is provided. Only the first set of clutches C11 is engaged, and the motor MG is connected in parallel with the internal combustion engine. The motor MG is used as a generator to generate electricity, and the generated electricity is used to drive the rear-wheel motor, thereby redistributing the power of the internal combustion engine to the front and rear wheels to achieve four-wheel drive.

[0189] Optionally, the ratio of the number of teeth of the first driven gear G12 to the first driving gear G11 is 0.4. The ratio of the number of teeth of the second driven gear G22 to 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 ring gear R3 to the number of teeth of the third sun gear S3 is 3.

[0190] Optionally, if the internal combustion engine is independently powered, the transmission ratios for forward first gear are 5.60, forward second gear is 2.13, forward third gear is 1.49, forward fourth gear is 1.18, forward fifth gear is 0.88, and forward sixth gear is 0.76; the transmission ratio for reverse first gear is 8.00. Furthermore, if the internal combustion engine is independently powered, the step ratios for forward first gear and forward second gear are 2.63, the step ratios for forward second gear and forward third gear are 1.43, the step ratios for forward third gear and forward fourth gear are 1.27, the step ratios for forward fourth gear and forward fifth gear are 1.34, and the step ratios for forward fifth gear and forward sixth gear are 1.16; the transmission ratio range between the highest and lowest gears is 7.38.

[0191] Optionally, the motor can be independently driven, with a transmission ratio of 5.33 for first gear, 3.73 for second gear, and 2.2 for third gear. The motor can control forward and reverse rotation, enabling three gears each for forward and reverse. Furthermore, with the motor independently driven, the step ratios for forward first and second gears are 1.43, and for forward second and third gears are 1.7. The transmission ratio range between the highest and lowest gears is 2.43.

[0192] This embodiment discloses a planetary multi-stage transmission speed change mechanism for a vehicle transmission system. Figure 6 As shown, it includes a dual clutch C1, a motor MG, an input shaft IN, an output shaft OUT, three planetary gears (P1-P3), five brakes (BL3, B1-B4), and four connecting parts (L1-L4).

[0193] Each planetary gear row includes: sun gears (S1~S3), planet carriers (PC1~PC3), planetary gears (CA1~CA3) and ring gears (R1~R3); the ring gear is coaxial with the sun gear, and the planetary gears are mounted on the planet carrier through planet shafts and bearings, and each planetary gear is internally meshed with the ring gear on the same planetary gear row and externally meshed with the sun gear on the same planetary gear row.

[0194] The dual clutch C1 and three planetary gears are arranged in parallel from left to right, and the dual clutch C1, three sun gears, input shaft IN and output shaft OUT are arranged coaxially. The motor MG is arranged parallel to the input shaft IN.

[0195] Power Flow: Power flows in from the input shaft IN and out from the output shaft OUT. When the motors MG are driven in parallel, the power of the motors MG flows in from the first ring gear R1 and out from the output shaft OUT.

[0196] The vehicle transmission system in this application utilizes a planetary multi-stage transmission mechanism, including three planetary gears and five brakes. Each of the gears is a simple, single-planet planetary gear, capable of achieving up to six forward gears and one reverse gear. The first forward gear has a transmission ratio greater than 5, enabling hybrid oil-electric drive, allowing the engine to operate more efficiently within its operating range and improving overall vehicle efficiency. The five brakes are all friction-operated, and the gear position is controlled by two elements, reducing frictional work and heat loss on the friction plates and improving their reliability.

[0197] Seventh embodiment:

[0198] A vehicle transmission system includes a planetary multi-stage transmission speed change mechanism according to any one of the first to sixth embodiments.

[0199] In summary, the vehicle transmission system of the present invention has a simple structure, a large transmission ratio range, a strong torque transmission capability, and strong gear scalability. Compared with the existing transmission system, it can better adapt to the transmission needs of the vehicle.

[0200] The above disclosure is only some embodiments of the present invention. For those skilled in the art, several modifications and improvements can be made without departing from the inventive concept of the present invention, and these all fall within the scope of protection of the present invention.

Claims

1. A planetary multi-stage transmission speed change mechanism, characterized in that: Includes input shaft (IN), output shaft (OUT), first planetary gear (P1), second planetary gear (P2) and third planetary gear (P3); The input shaft (IN) is connected to the first planetary gear (P1); the output shaft (OUT) is connected to the second planetary gear (P2); The first ring gear (R1) or the first sun gear (S1) of the first planetary gear (P1) is connected to the first brake (B1); The second ring gear (R2) or the second sun gear (S2) of the second planetary gear (P2) is connected to the second brake (B2); The first planetary gear (P1) includes a first planetary gear carrier (PC1); the second planetary gear (P2) includes a second planetary gear carrier (PC2); the third planetary gear (P3) includes a third planetary gear carrier (PC3); The first planet carrier (PC1) and the second planet carrier (PC2) are fixedly connected via a planet carrier connecting shaft (L3); The third sun gear (S3) of the third planetary gear (P3) is movably mounted on the planet carrier connecting shaft (L3); The third planet carrier (PC3) is connected to the third brake (B3); the second planet carrier (PC2) is connected to the planet carrier brake (BL3).

2. A planetary multi-stage transmission speed change mechanism according to claim 1, characterized in that: One fixed-axis rotating member of the first planetary gear (P1) is fixedly connected to the input shaft (IN), and another fixed-axis rotating member of the first planetary gear (P1) is fixedly connected to one fixed-axis rotating member of the third planetary gear (P3) via a first connecting member (L1); Another fixed-axis rotating member of the third planetary gear (P3) is fixedly connected to a fixed-axis rotating member of the second planetary gear (P2) via a second connecting member (L2); Another fixed-axis rotating component of the second planetary gear (P2) is fixedly connected to the output shaft (OUT).

3. A planetary multi-stage transmission speed change mechanism according to claim 2, characterized in that: The first planetary gear (P1) includes a first sun gear (S1), a first planetary gear (CA1) and a first ring gear (R1); The second planetary gear (P2) includes a second sun gear (S2), a second planetary gear (CA2) and a second ring gear (R2); The third planetary gear (P3) includes a third sun gear (S3), a third planetary gear (CA3) and a third ring gear (R3); The third sun gear (S3) is movably mounted on the planet carrier connecting shaft (L3); The input shaft (IN) is fixedly connected to the first sun gear (S1), the first ring gear (R1) is fixedly connected to the third sun gear (S3) via a first connecting member (L1), the third ring gear (R3) is fixedly connected to the second ring gear (R2) via a second connecting member (L2), and the output shaft (OUT) is fixedly connected to the second sun gear (S2); The first ring gear (R1) is connected to the first brake (B1); the second ring gear (R2) is connected to the second brake (B2); the second planet carrier (PC2) is connected to the planet carrier brake (BL3); and the third planet carrier (PC3) is connected to the third brake (B3).

4. A planetary multi-stage transmission speed change mechanism according to claim 2, characterized in that: The first planetary gear (P1) includes a first sun gear (S1), a first planetary gear (CA1) and a first ring gear (R1); The second planetary gear (P2) includes a second sun gear (S2), a second planetary gear (CA2) and a second ring gear (R2); The third planetary gear (P3) includes a third sun gear (S3), a third planetary gear (CA3) and a third ring gear (R3); The second sun gear (S2) and the third sun gear (S3) are both movably mounted on the planet carrier connecting shaft (L3); The input shaft (IN) is fixedly connected to the first sun gear (S1), the first ring gear (R1) is fixedly connected to the third ring gear (R3) via a first connecting member (L1), the third sun gear (S3) is fixedly connected to the second sun gear (S2) via a second connecting member (L2), and the output shaft (OUT) is fixedly connected to the second ring gear (R2); The first ring gear (R1) is connected to the first brake (B1); the second sun gear (S2) is connected to the second brake (B2); the second planet carrier (PC2) is connected to the planet carrier brake (BL3); and the third planet carrier (PC3) is connected to the third brake (B3).

5. A planetary multi-stage transmission speed change mechanism according to claim 2, characterized in that: The first planetary gear (P1) includes a first sun gear (S1), a first planetary gear (CA1) and a first ring gear (R1); The second planetary gear (P2) includes a second sun gear (S2), a second planetary gear (CA2) and a second ring gear (R2); The third planetary gear (P3) includes a third sun gear (S3), a third planetary gear (CA3) and a third ring gear (R3); The second sun gear (S2) and the third sun gear (S3) are both movably mounted on the planet carrier connecting shaft (L3); the input shaft (IN) is fixedly connected to the first sun gear (S1); the first ring gear (R1) is fixedly connected to the third sun gear (S3) via a first connecting member (L1); the third ring gear (R3) is fixedly connected to the second sun gear (S2) via a second connecting member (L2); and the output shaft (OUT) is fixedly connected to the second ring gear (R2); The first ring gear (R1) is connected to the first brake (B1); the second sun gear (S2) is connected to the second brake (B2); the second planet carrier (PC2) is connected to the planet carrier brake (BL3); and the third planet carrier (PC3) is connected to the third brake (B3).

6. A planetary multi-stage transmission speed change mechanism according to claim 2, characterized in that: The first planetary gear (P1) includes a first sun gear (S1), a first planetary gear (CA1) and a first ring gear (R1); The second planetary gear (P2) includes a second sun gear (S2), a second planetary gear (CA2) and a second ring gear (R2); The third planetary gear (P3) includes a third sun gear (S3), a third planetary gear (CA3) and a third ring gear (R3); 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 input shaft (IN) is fixedly connected to the first ring gear (R1); the first sun gear (S1) is fixedly connected to the third sun gear (S3) via a first connecting member (L1); the third ring gear (R3) is fixedly connected to the second sun gear (S2) via a second connecting member (L2); and the output shaft (OUT) is fixedly connected to the second ring gear (R2); The first sun gear (S1) is connected to a first brake (B1); the second sun gear (S2) is connected to a second brake (B2); the second planet carrier (PC2) is connected to a planet carrier brake (BL3); and the third planet carrier (PC3) is connected to a third brake (B3).

7. A planetary multi-stage transmission speed change mechanism according to claim 3, characterized in that: Also included is the fifth planetary row (P5); The fifth planetary gear (P5) includes a fifth sun gear (S5), a fifth planet carrier (PC5), a fifth planet gear (CA5) and a fifth ring gear (R5); the fifth planet carrier (PC5) is fixedly connected to the first planet carrier (PC1); the fifth ring gear (R5) is connected to the fifth brake (B5); the planetary carrier brake (BL3) is connected to the fifth planet carrier (PC5); the fifth sun gear (S5) is fixedly connected to the input shaft (IN); Also included are the fourth planetary gear (P4) and the sixth planetary gear (P6); The fourth planetary gear (P4) includes a fourth sun gear (S4), a fourth planetary carrier (PC4), a fourth planetary gear (CA4) and a fourth ring gear (R4); the fourth planetary carrier (PC4) is fixedly connected to the second ring gear (R2); the fourth ring gear (R4) is connected to the fourth brake (B4); the fourth sun gear (S4) is fixedly connected to the output shaft (OUT); The sixth planetary gear (P6) includes a sixth sun gear (S6), a sixth planetary carrier (PC6), a sixth planetary gear (CA6) and a sixth ring gear (R6); the sixth planetary carrier (PC6) is fixedly connected to the fourth planetary carrier (PC4); the sixth ring gear (R6) is connected to the sixth brake (B6); and the sixth sun gear (S6) is fixedly connected to the output shaft (OUT).

8. A planetary multi-stage transmission speed change mechanism according to claim 4, characterized in that: It also includes a dual clutch (C1) and a motor (MG); The input shaft (IN) is connected to the dual clutch (C1), the first clutch group (C11) of the dual clutch (C1) is fixedly connected to the fourth connecting member (L4), the fourth connecting member (L4) is connected to the fourth brake (B4); the fourth connecting member (L4) is fixedly connected to the first sun gear (S1); One end of the motor (MG) is connected to the second clutch group C12 of the dual clutch (C1), and the other end of the motor (MG) is connected to the first ring gear (R1).

9. A planetary multi-stage transmission speed change mechanism according to any one of claims 1 to 8, characterized in that: Calculate the number of forward gears using the formula n1×n2+(n1-1)+(n2-1); Wherein, n1 is the number of planetary gears in the first planetary gear set (PZ1), and n2 is the number of planetary gears in the second planetary gear set (PZ2); Set the gear ratio between the number of teeth of the planetary gear ring and the number of teeth of the sun gear to be K; When the first planetary gear set (PZ1) includes the first planetary gear (P1) and the fifth planetary gear (P5), K1 is set to be greater than K5; Wherein: K1 is the gear ratio of the first planetary gear (P1), and K5 is the gear ratio of the fifth planetary gear (P5).

10. A vehicle transmission system, characterized in that: It comprises a planetary multi-stage transmission speed change mechanism as described in any one of claims 1-8.

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