Power control mechanism of planet row combined clutch and vehicle transmission system

Abstract

The invention discloses a power control mechanism of a planet row combination clutch and a vehicle transmission system, the power control mechanism comprises a first clutch, a third brake and a third planet row, a driven part of the first clutch is fixedly connected with a third planet carrier, and a driving part of the first clutch is fixedly connected with a third connecting part; the third planet carrier is connected with a third brake. Four transmission states can be achieved, the transmission mechanism serves as a power control mechanism to be connected with the two planet row sets, two-stage transmission, multi-stage transmission and hybrid transmission including multi-stage transmission are achieved, and the number of gears is remarkably increased.

Description

Technical Field

[0001] The present invention relates to the technical field of vehicle transmission, and in particular to a power control mechanism of a planetary gear combination clutch and a vehicle transmission system. Background Art

[0002] Currently, the automatic transmission (AT) with more than six gears used in transportation vehicles has a transmission mechanism that is basically an optimized combination of the Simpson mechanism, the Ravenna mechanism and the CR-CR mechanism. Two groups of the above three transmission mechanisms are selected, and brakes and clutches are added as control mechanisms. The structures of the two groups of transmission mechanisms are broken up and reorganized to increase the degree of freedom of the transmission and the reuse rate of the planetary gearbox. Usually, four planetary gears can be used to achieve changes beyond six gears. The disadvantage is that the transmission logic is complex, which in turn causes a complex structure. Special design software is often required to assist in structural design, and the engineering difficulty increases accordingly, and the manufacturing cost and maintenance cost also increase accordingly.

[0003] A planetary multi-stage transmission speed change mechanism (patent application number: 2024117698989) uses a planetary gear to control power transmission or interruption. While significantly reducing the complexity of the speed change mechanism, it can take into account the reuse rate of the transmission mechanism and provide a design idea for the planetary gear to participate in power control.

[0004] Therefore, there is an urgent need for a gearbox that can combine the above technical advantages, has multiple gears, a large transmission ratio range, simple gear control logic, fewer transmission mechanisms, and a high reuse rate of transmission components. Summary of the invention

[0005] The purpose of the present invention is to provide a power control mechanism of a planetary gear combination clutch and a vehicle transmission system to fully utilize the advantages of the above technical route. To achieve this purpose, the present invention adopts the following technical solutions:

[0006] A power control mechanism of a planetary gear combination clutch comprises a first clutch, a third planetary gear, a third brake and a third connecting member;

[0007] The first clutch includes a first clutch active member and a first clutch driven member;

[0008] The third planetary gear comprises a third sun gear, a third planet carrier, a third planetary gear and a third ring gear;

[0009] The first clutch active member is fixedly connected to the third connecting member;

[0010] The first clutch driven member is fixedly connected to the third planet carrier;

[0011] The third sun gear of the third planetary gear is movably mounted on the third connecting member;

[0012] The third planet carrier is connected to the third brake.

[0013] In some embodiments, when the first clutch and the third brake are both in a disengaged state, one power path is transmitted through the third connecting member to achieve single power path power transmission;

[0014] When the first clutch is engaged alone, one power path is transmitted through the third connecting member, and the other power path is transmitted through the third sun gear. The two power paths are divided and then merged to form two new power paths, which are output from the third connecting member and the third ring gear respectively, realizing dual-path power mixed flow dual-path power transmission;

[0015] When the third brake is engaged alone, one power path is transmitted through the third connecting member, and the other power path is transmitted through the third sun gear and the third ring gear, thereby realizing dual-path power transmission without mixing.

[0016] When the first clutch and the third brake are in the engaged state at the same time, one path of power is transmitted through the third sun gear and output by the third ring gear, thus realizing single-path power transmission.

[0017] In some embodiments, the third sun gear and the third ring gear may be used interchangeably, and the effects are the same.

[0018] In some embodiments, the first planetary gear set, the second planetary gear set, the input shaft and the output shaft are also included;

[0019] The first planetary gear set is arranged on one side of the third planetary gear set, and the second planetary gear set is arranged on the other side of the third planetary gear set; that is, the first planetary gear set, the third planetary gear set and the second planetary gear set are arranged side by side;

[0020] The input shaft is connected to the first planetary gear set; the output shaft is connected to the second planetary gear set.

[0021] In some embodiments, the first planet row group includes a fifth planet row and a first planet row; the input shaft is connected to the fifth planet row, and the first planet row is connected to the third planet row.

[0022] In some embodiments, the fifth planetary gear comprises a fifth sun gear, a fifth planet carrier, a fifth planet gear and a fifth ring gear; the fifth sun gear is movably mounted on the input shaft; the fifth sun gear is fixedly connected to the first planet carrier through a fifth connecting member; the fifth ring gear is fixedly connected to the third connecting member; the fifth sun gear is connected to the fifth brake; the fifth planet carrier is fixedly connected to the input shaft;

[0023] The first planetary gear comprises a first sun gear, a first planet carrier, a first planetary gear and a first ring gear; the first sun gear is movably mounted on a third connecting member; the first sun gear is fixedly connected to the third sun gear via the first connecting member; the first ring gear is fixedly connected to the third connecting member; the first sun gear is connected to the first brake.

[0024] In some embodiments, the second planet row group includes a second planet row and a fourth planet row; the second planet row is connected to the third planet row; and the fourth planet row is connected to the output shaft.

[0025] In some embodiments, the second planetary gear comprises a second sun gear, a second planet carrier, a second planet gear and a second ring gear; the second sun gear is movably mounted on a third connecting member; the second sun gear is fixedly connected to the third ring gear via a second connecting member; the second planet carrier is fixedly connected to the fourth ring gear via a fourth connecting member; the second ring gear is fixedly connected to the third connecting member; the second sun gear is connected to the second brake;

[0026] The fourth planetary gear comprises a fourth sun gear, a fourth planet carrier, a fourth planet gear and a fourth ring gear; the fourth sun gear is fixedly connected to the third connecting member; the fourth ring gear is connected to the fourth brake; and the fourth planet carrier is fixedly connected to the output shaft.

[0027] Beneficial effects of the present invention:

[0028] 1. The power control mechanism of the planetary gear combination clutch of the present invention adopts a method of controlling the power transmission path to transmit power in four transmission states. As a control mechanism between two planetary gear groups, the number of gears is increased by increasing the transmission path. The gear shifting logic is simple and the gear has strong scalability. The number of transmission gears is: forward gear number n1×n2+n1+n2+(n1-1)+(n2-1), and the reverse gear number is 1. The reuse rate of the planetary gear is greatly improved. At the same time, the dual-path transmission belongs to a hybrid transmission of two-stage transmission and multi-stage transmission, which can realize an increase in the upper limit and a decrease in the lower limit of the forward gear transmission ratio, and expand the transmission ratio range of the forward gear.

[0029] 2. The main components of the power control mechanism of the planetary gear combination clutch of the present invention are a planetary gear, a brake and a clutch. The cooperation of the three can give full play to the power control function of the planetary gear and the clutch. Compared with the technical solution of multi-brake and multi-clutch control commonly used in the prior art, the complexity and manufacturing difficulty of the speed change mechanism are significantly reduced, and the number of gears can be easily increased, which is a significant improvement. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] Figure 1 The present invention is a structural diagram of a power control mechanism of a planetary gear combination clutch according to the first embodiment of the present invention.

[0031] Figure 2 It is a schematic structural diagram of a planetary gear set according to the first embodiment of the present invention.

[0032] Figure 3 The figure is a structural diagram of a power control mechanism of a planetary gear combination clutch according to the second embodiment of the present invention. DETAILED DESCRIPTION

[0033] The present invention will be further described in detail below in conjunction with the accompanying drawings.

[0034] First embodiment:

[0035] refer to Figure 1 , a power control mechanism of a planetary gear combination clutch, comprising a first clutch C1, a third planetary gear P3, a third brake B3 and a third connecting member L3;

[0036] The first clutch C1 includes a first clutch active member C11 and a first clutch driven member C12;

[0037] 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 is meshed with the third planetary gear CA3, and the third planetary gear CA3 is meshed with the third sun gear S3;

[0038] The first clutch active member C11 is fixedly connected to the third connecting member L3;

[0039] The first clutch driven member C12 is fixedly connected to the third planet carrier PC3;

[0040] The third sun gear S3 of the third planetary row P3 is movably mounted on the third connecting member L3;

[0041] 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.

[0042] Among them, the movable installation can be understood as a rotating connection; the fixed connection can be understood as a linkage connection.

[0043] Working principle:

[0044] The third sun gear S3 and the third connecting member L3 can both serve as power input ends. For example, power can be input to the third sun gear S3, or power can be input to the third connecting member L3, or corresponding power can be input to both the third sun gear S3 and the third connecting member L3. Accordingly, under different combinations of the first clutch C1 and the third brake B3, the third ring gear R3 and the third connecting member L3 will form different output powers.

[0045] Based on the above power control mechanism, four transmission states can be formed under different combinations of the first clutch C1 and the third brake B3, as follows:

[0046] The first transmission state: the first clutch C1 and the third brake B3 are both in the disengaged state.

[0047] The first power input: The third connecting member L3 inputs the first power, and the first power is transmitted through the third connecting member L3. Since the first clutch C1 is in an unengaged state, the power is not transmitted to the third planetary carrier PC3. The first power is directly output on the third connecting member L3, and the rotation direction of the output power is the same as that of the input power.

[0048] Second power input: The third sun gear S3 inputs the second power. Since the first clutch C1 and the third brake B3 are both in the disengaged state, the power is not output to the outside.

[0049] The first power and the second power are input at the same time: since the second power is not output externally, only the first power is output externally, realizing the single-path transmission of the first power.

[0050] The second transmission state: the first clutch C1 is engaged alone.

[0051] Input of power route 1: The third connecting member L3 inputs power route 1, and power route 1 is transmitted through the third connecting member L3; on the third connecting member L3, the power is split into two transmission routes, and power route 1.1 is output through the third connecting member L3; power route 1.2 is output to the third planetary carrier PC3 through the first clutch active member C11 and the first clutch driven member C12, and finally output to the outside through the third ring gear R3;

[0052] Second power input: The third sun gear S3 inputs the second power, and the power is split into two transmissions. The 2.1 power is output to the third connecting member L3 through the third planet carrier PC3, the first clutch driven member C12 and the first clutch active member C11; the 2.2 power is output to the outside through the third ring gear R3;

[0053] The 1st power and the 2nd power are input simultaneously: the 1.1th power and the 2.1th power are output after merging on the third connecting member L3, and the 1.2th power and the 2.2th power are output after merging on the third ring gear R3, realizing dual-power mixed-flow dual-path power transmission.

[0054] The third transmission state: the third brake B3 is engaged alone to fix the third planet carrier PC3.

[0055] First power input: The third connecting member L3 inputs the first power, and the first power is transmitted through the third connecting member L3, and the output power has the same rotation direction as the input power;

[0056] Second power input: The third sun gear S3 inputs the second power, and the second power is transmitted through the third sun gear S3. In the third planetary row P3, the third sun gear S3 inputs power, and outputs the power to the third ring gear R3 through the third planetary gear CA3. The rotation direction of the output power is opposite to that of the input power.

[0057] The first power and the second power are input simultaneously: because the first clutch C1 is not engaged, the transmission paths of the first power and the second power do not interfere with each other, thus realizing dual-path power transmission without mixing of the first power and the second power.

[0058] The fourth transmission state: the first clutch C1 and the third brake B3 are engaged simultaneously, fixing the third connecting member L3 and the third planet carrier PC3 respectively.

[0059] Power input for route 1: The third connecting member L3 inputs power for route 1. Since the third connecting member L3 is fixed, power for route 1 is not output externally.

[0060] Second power input: The third sun gear S3 inputs the second power, and the second power is transmitted through the third sun gear S3. In the third planetary row P3, the third sun gear S3 inputs power, and outputs the power to the third ring gear R3 through the third planetary gear CA3. The rotation direction of the output power is opposite to that of the input power.

[0061] The first power and the second power are input at the same time: since the first power is not output to the outside, only the second power is output to the outside, thus realizing the single-path transmission of the second power.

[0062] As mentioned above, the third sun gear S3 and the third ring gear R3 are interchanged in use, and the effect is the same.

[0063] In the above embodiments, reference Figure 2 , Figure 3 , n1 planetary rows can be arranged in parallel to form a first planetary row group PZ1, and the third connecting member L3 and the third sun gear S3 are respectively fixedly connected to two basic components on a planetary row on the first planetary row group PZ1; n2 planetary rows can be arranged in parallel to form a second planetary row group PZ2, and the third connecting member L3 and the third ring gear R3 are respectively fixedly connected to two basic components on a planetary row on the second planetary row group PZ2; wherein the planetary row includes three basic components, namely a sun gear, a planet carrier and a ring gear; each planetary row in the two planetary row groups is provided with a corresponding brake.

[0064] The first transmission state: the first clutch C1 and the third brake B3 are both in the disengaged state, the third planetary gear P3 does not transmit power, and the power is transmitted in a single path by the third connecting member L3; 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, and there are a total of n1×n2 combinations. The brakes set on a pair of planetary gears in each of the n1×n2 combinations are braked at the same time, which can 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 single-power single-path transmissions can be realized.

[0065] The second transmission state: the first clutch C1 is engaged alone, and the two-way power is mixed on the third connecting member L3 and the third planetary gear P3; after the brakes set on the n1 planetary gears on the first planetary gear group PZ1 and the n2 planetary gears on the second planetary gear group PZ2 are braked in sequence, the system has only one degree of freedom, with a certain input and output, and can realize n1+n2 two-way power mixed-flow dual-path power transmission.

[0066] The third transmission state: the third brake B3 is engaged alone to fix the third planetary carrier PC3; the two-way power of the third connecting member L3 and the third planetary row P3 is not mixed; after the brakes set on the n1 planetary rows on the first planetary row group PZ1 and the n2 planetary rows on the second planetary row group PZ2 are braked in sequence, the system has only one degree of freedom, with definite input and output, and can realize n1+n2 transmission combinations; after the brake set on the planetary row that has a connection relationship with the third planetary row P3 is braked, when the third brake B3 is engaged and the third planetary carrier PC3 is fixed, the third planetary row P3 does not transmit power, and only the single-way power single-path transmission of the third connecting member L3 is realized, which coincides with the first transmission state. After elimination, (n1-1)+(n2-1) dual-way power non-mixed dual-path power transmissions can be realized.

[0067] The fourth transmission state: the first clutch C1 and the third brake B3 are engaged at the same time, fixing the third connecting member L3 and the third planetary carrier PC3 respectively; the third connecting member L3 is fixed and no power is transmitted; the power is transmitted through the third sun gear S3, and in the third planetary row P3, the third sun gear S3 inputs power, and outputs power to the third ring gear R3 through the third planetary gear CA3, and the output power rotation direction is opposite to the input power rotation direction, realizing a single-power single-path transmission.

[0068] The power control mechanism of the planetary gear combination clutch is applied to two planetary gear groups, and can realize a forward gear number of n1×n2+n1+n2+(n1-1)+(n2-1) in the same direction as the power input direction, and a reverse gear number of 1 in the opposite direction of the power input direction.

[0069] In addition, in the above embodiments, two power flows are allowed, as follows:

[0070] In the first type, power flows in from the third sun gear S3 and the third connecting member L3 at one end in the same direction as the third sun gear S3, and flows out from the third ring gear R3 and the third connecting member L3 at one end in the same direction as the third ring gear R3.

[0071] Second, power flows in from the third ring gear R3 and the third connecting member L3 at one end in the same direction as the third ring gear R3, and flows out from the third sun gear S3 and the third connecting member L3 at one end in the same direction as the third sun gear S3.

[0072] Optionally, the third brake B3 and the first clutch C1 are both friction-type operating structures.

[0073] Second embodiment:

[0074] refer to Figure 3 , a power control mechanism of a planetary gear combination clutch, applying the first embodiment, adding a fifth planetary gear P5, a first planetary gear P1, a second planetary gear P2 and a fourth planetary gear P4 on the basis of the first embodiment; arrangement: the fifth planetary gear P5, the first planetary gear P1, the third planetary gear P3, the first clutch C1, the second planetary gear P2 and the fourth planetary gear P4 are sequentially and parallelly distributed;

[0075] The fifth planetary gear P5 includes a fifth sun gear S5, a fifth planet carrier PC5, a fifth planetary gear CA5 and a fifth ring gear R5. The fifth planetary gear CA5 is movably mounted on the fifth planet carrier PC5. The fifth ring gear R5 is meshed with the fifth planetary gear CA5. The fifth planetary gear CA5 is meshed with the fifth sun gear S5. The fifth sun gear S5 is connected to the fifth brake B5, that is, the fifth sun gear S5 can be braked by the fifth brake B5.

[0076] The first planetary row 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 is meshed with the first planetary gear CA1. The first planetary gear CA1 is meshed with the first sun gear S1. The first sun gear S1 is connected to the first brake B1, that is, the first sun gear S1 can be braked by the first brake B1.

[0077] 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 meshed with the third planetary gear CA3. The third planetary gear CA3 is meshed with the third sun gear S3. The third planet carrier PC3 is connected to the third brake B3, that is, the third planet carrier PC3 can be braked by the third brake B3.

[0078] The first clutch C1 includes a first clutch driving member C11 and a first clutch driven member C12. When the first clutch C1 is engaged, the first clutch driving member C11 and the first clutch driven member C12 move synchronously.

[0079] 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 meshed with the second planetary gear CA2. The second planetary gear CA2 is meshed with the second sun gear S2. The second sun gear S2 is connected to the second brake B2, that is, the second sun gear S2 can be braked by the second brake B2.

[0080] 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 meshed with the fourth planetary gear CA4. The fourth planetary gear CA4 is meshed with the fourth sun gear S4. The fourth ring gear R4 is connected to the fourth brake B4, that is, the fourth ring gear R4 is braked by the fourth brake B4.

[0081] The fifth planet carrier PC5 is fixedly connected to the input shaft IN; the fifth sun gear S5 is movably mounted on the input shaft IN, and the first sun gear S1 is movably mounted on the third connecting member L3; the fifth sun gear S5 is fixedly connected to the first planet carrier PC1 through the fifth connecting member L5, the fifth ring gear R5 is fixedly connected to the third connecting member L3, the first sun gear S1 is fixedly connected to the third sun gear S3 through the first connecting member L1, and the first ring gear R1 is fixedly connected to the third connecting member L3.

[0082] The third sun gear S3 is movably mounted on the third connecting member L3, the first clutch active member C11 is fixedly connected to the third connecting member L3, the first clutch driven member C12 is fixedly connected to the third planet carrier PC3, and when the first clutch C1 is engaged, the third connecting member L3 and the third planet carrier PC3 move synchronously.

[0083] The fourth planet carrier PC4 is fixedly connected to the output shaft OUT; the second sun gear S2 is movably mounted on the third connecting member L3, and the fourth sun gear S4 is fixedly connected to the third connecting member L3; the second sun gear S2 is fixedly connected to the third ring gear R3 through the second connecting member L2, the second planet carrier PC2 is fixedly connected to the fourth ring gear R4 through the fourth connecting member L4, and the second ring gear R2 is fixedly connected to the third connecting member L3.

[0084] Optionally, the input shaft IN, the fifth sun gear S5, the first sun gear S1, the third sun gear S3, the first clutch C1, the second sun gear S2, the fourth sun gear S4 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.

[0085] The fifth planetary row P5 and the first planetary row P1 constitute the first planetary row group PZ1, the number of planetary rows n1=2, the second planetary row P2 and the fourth planetary row P4 constitute the second planetary row group PZ2, the number of planetary rows n2=2; the number of forward gears is n1×n2+n1+n2+(n1-1)+(n2-1)=2×2+2+2+(2-1)+(2-1)=10, and the number of reverse gears is 1;

[0086] The first clutch C1 and the fourth brake B4 are engaged simultaneously to achieve the first forward gear;

[0087] The third brake B3 and the fourth brake B4 are engaged simultaneously to realize the second forward gear;

[0088] The first brake B1 and the fourth brake B4 are engaged simultaneously to achieve the third forward gear;

[0089] The fifth brake B5 and the fourth brake B4 are engaged simultaneously to realize the fourth forward gear;

[0090] The first clutch C1 and the second brake B2 are engaged simultaneously to achieve the fifth forward gear;

[0091] The first brake B1 and the second brake B2 are engaged simultaneously to achieve the sixth forward gear;

[0092] The first brake B1 and the first clutch C1 are engaged simultaneously to achieve the seventh forward gear;

[0093] The fifth brake B5 and the second brake B2 are engaged simultaneously to achieve the eighth forward gear;

[0094] The fifth brake B5 and the third brake B3 are engaged simultaneously to achieve the ninth forward gear;

[0095] The fifth brake B5 and the first clutch C1 are engaged simultaneously to achieve the tenth forward gear;

[0096] The third brake B3 and the first clutch C1 are engaged simultaneously to achieve the first reverse gear.

[0097] The relevant calculation formula is shown in Table 1, and the control logic and transmission ratio of each gear are shown in Table 2.

[0098] Table 1 Calculation formula for each gear:

[0099]

[0100]

[0101] The K value of the planetary gear row refers to the ratio of the number of teeth of the planetary gear ring to the number of teeth of the sun gear. The tooth number ratio of the first ring gear R1 of the first planetary gear row P1 to the first sun gear S1 is K1. Similarly, the tooth number ratios of the first planetary gear row P1 to the fifth planetary gear row P5 are K1 to K5 respectively. When K1=3, K2=5, K3=4, K4=K5=3 in Table 1 and the input speed is 1, the transmission ratios of each gear shown in Table 1 can be obtained, realizing a speed change mechanism with ten forward gears and one reverse gear.

[0102] The calculation formula in Table 1 also reveals how the power control mechanism of the planetary gear combination clutch works when expanding the transmission ratio range. Compared with the speed formula of the F3 gear control part B1-B4 combination, the F2 gear control part B3-B4 combination has an additional coefficient (K2×K3) / (K1+1) 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 F2 gear control part B3-B4 combination, the F1 gear control part C1-B4 combination has an additional coefficient (K3+1) / (K1+1) composed of K1 and K3 in the denominator, further reducing the speed and increasing the transmission ratio;

[0103] Compared with the speed formula of the F8 gear operating component B5-B2 combination, the F9 gear operating component B5-B3 combination has an additional coefficient K4×(K1 / K3) / (K2+1) composed of K1, K2, K3 and K4, which increases the speed and reduces the transmission ratio; compared with the F9 gear operating component B5-B3 combination formula, the F10 gear operating component B5-C1 combination has an additional coefficient K4×(1+1 / K3) / (K2+1) composed of K2, K3 and K4, which further increases the speed and reduces the transmission ratio.

[0104] Table 2 Control logic and transmission ratio of each gear position (O means the control part is engaged)

[0105]

[0106] Combine the following Figure 2 Detailed description of the embodiments of the present invention is given in Table 2. The transmission ratio refers to the ratio of the input shaft speed to the output shaft speed.

[0107] F1: The first clutch C1 and the fourth brake B4 are engaged at the same time, the third connecting member L3 and the third planet carrier PC3 move synchronously, the fourth ring gear R4 is fixed, the fifth planet carrier PC5 is fixedly connected to the input shaft IN, and the input shaft IN inputs power; in the fifth planet row P5, the fifth planet carrier PC5 inputs power, and the power is split into two paths, one path is split to the fifth sun gear S5, and output to the first planet carrier PC1 through the fifth connecting member L5, and the other path is split to the fifth ring gear R5 and output to the third connecting member L3; in the first row In the planetary gear P1, the first planetary carrier PC1 inputs power, and the power is split into two paths. One path is split to the first sun gear S1, and is output to the third sun gear S3 through the first connecting member L1, and the other path is split to the first ring gear R1, and is output to the third connecting member L3. In the third planetary gear P3, the third sun gear S3 inputs power, and the split part of the power is output to the third ring gear R3 through the third planetary gear CA3. The third planetary carrier PC3 obtains part of the power split by the third connecting member L3 through the first clutch C1, and is output to the third ring gear R3 through the third planetary gear CA3. CA3 is output to the third ring gear R3. After the two powers merge in the third ring gear R3, they are output to the second sun gear S2 through the second connecting member L2. In the second planetary row P2, the second planetary carrier PC2 is fixedly connected to the fourth ring gear R4 through the fourth connecting member L4 and is in a fixed state. The second sun gear S2 inputs power and is output to the second ring gear R2 and the third connecting member L3 in sequence through the second planetary gear CA2. In the fourth planetary row P4, the fourth ring gear R4 is fixed, the fourth sun gear S4 inputs power, and the fourth sun gear S4 inputs power. CA4 is output to the fourth planetary carrier PC4, and outputs power to the output shaft OUT; on the third connecting member L3, after the two powers of the fifth ring gear R5 and the first ring gear R1 merge, one path is diverted and output to the third planetary carrier PC3, the second connecting member L2, the second sun gear S2, and the second ring gear R2 in sequence, and after merging with the other diverted power again on the third connecting member L3, it is output to the fourth sun gear S4, and finally output to the output shaft OUT by the fourth planetary carrier PC4, and the rotation direction is the same as the input shaft IN, realizing the first forward gear.

[0108] F2: The third brake B3 and the fourth brake B4 are engaged at the same time, the third planet carrier PC3 and the fourth ring gear R4 are fixed, the fifth planet carrier PC5 is fixedly connected to the input shaft IN, and the input shaft IN inputs power; in the fifth planet row P5, the fifth planet carrier PC5 inputs power, and the power is split into two paths, one path is split to the fifth sun gear S5, and is output to the first planet carrier PC1 through the fifth connecting member L5, and the other path is split to the fifth ring gear R5, and is output to the third connecting member L3; in the first planet row P1, the first planet carrier PC1 inputs power, and the power is split into two paths, one path is split to the first sun gear S1, and is output to the third sun gear S3 through the first connecting member L1, and the other path is split to the first ring gear R1, and is output to the third connecting member L3; in the third planet row P3, the third sun gear S3 inputs power, and is output to the third sun gear S3 through the third planet gear CA3. The three-ring gear R3 is output to the second sun gear S2 through the second connecting member L2; in the second planetary row P2, the second planetary carrier PC2 is fixedly connected to the fourth ring gear R4 through the fourth connecting member L4 and is in a fixed state, the second sun gear S2 inputs power, and outputs it to the second ring gear R2 and the third connecting member L3 in sequence through the second planetary gear CA2; in the fourth planetary row P4, the fourth ring gear R4 is fixed, the fourth sun gear S4 inputs power, and outputs it to the fourth planetary carrier PC4 through the fourth planetary gear CA4, and outputs power to the output shaft OUT; on the third connecting member L3, the three-way power on the fifth ring gear R5, the first ring gear R1 and the second ring gear R2 merges into the third connecting member L3, passes through the fourth sun gear S4 and the fourth planetary carrier PC4 in sequence, and finally outputs power to the output shaft OUT, and the rotation direction is the same as that of the input shaft IN, realizing the second forward gear.

[0109] F3: The first brake B1 and the fourth brake B4 are engaged at the same time, the first sun gear S1 and the fourth ring gear R4 are fixed, the fifth planet carrier PC5 is fixedly connected to the input shaft IN, and the input shaft IN inputs power; in the fifth planet row P5, the fifth planet carrier PC5 inputs power, and the power is split into two paths, one is split to the fifth sun gear S5, and is output to the first planet carrier PC1 through the fifth connecting member L5, and the other is split to the fifth ring gear R5, and is output to the third connecting member L3; in the first planet row P1, the first sun gear S1 is fixed, and the first planet carrier PC1 inputs power. The power is inputted and outputted to the first ring gear R1 and the third connecting member L3 in sequence; in the fourth planetary row P4, the fourth ring gear R4 is fixed, the fourth sun gear S4 inputs power, and outputs it to the fourth planet carrier PC4 through the fourth planetary gear CA4, and outputs power to the output shaft OUT; on the third connecting member L3, the fifth ring gear R5 and the two-way power on the first ring gear R1 merge into the third connecting member L3, pass through the fourth sun gear S4 and the fourth planet carrier PC4 in sequence, and finally output power to the output shaft OUT, with the same rotation direction as the input shaft IN, to realize the third forward gear.

[0110] F4: The fifth brake B5 and the fourth brake B4 are engaged at the same time, the fifth sun gear S5 and the fourth ring gear R4 are fixed, the fifth planet carrier PC5 is fixedly connected to the input shaft IN, and the input shaft IN inputs power; in the fifth planetary row P5, the fifth sun gear S5 is fixed, the fifth planet carrier PC5 inputs power, and outputs power to the fifth ring gear R5 and the third connecting member L3 in sequence; in the fourth planetary row P4, the fourth ring gear R4 is fixed, the fourth sun gear S4 inputs power, and outputs it to the fourth planet carrier PC4 through the fourth planetary gear CA4, and outputs power to the output shaft OUT; on the third connecting member L3, the fifth ring gear R5 outputs power to the third connecting member L3, passes through the fourth sun gear S4 and the fourth planet carrier PC4 in sequence, and finally outputs power to the output shaft OUT, and the rotation direction is the same as that of the input shaft IN, realizing the fourth forward gear.

[0111] F5: The first clutch C1 and the second brake B2 are engaged at the same time, the third connecting member L3 and the third planet carrier PC3 move synchronously, the second sun gear S2 is fixed, the fifth planet carrier PC5 is fixedly connected to the input shaft IN, and the input shaft IN inputs power; in the fifth planet row P5, the fifth planet carrier PC5 inputs power, and the power is divided into two paths, one path is divided to the fifth sun gear S5, and output to the first planet carrier PC1 through the fifth connecting member L5, and the other path is divided to the fifth ring gear R5, and output to the third connecting member L3; in the first planet row P1, the first planet carrier PC1 inputs power, and the power is divided into two paths, one path is divided to the first sun gear S1, and output to the third sun gear S3 through the first connecting member L1, and the other path is divided to the first ring gear R1, and output to the third connecting member L3; in the third planet row P3, the third ring gear R3 is fixedly connected to the second sun gear S2 through the second connecting member L2 and is in a fixed state, the third sun gear S3 inputs power, and outputs to the third planet carrier PC3 through the third planet gear CA3, and the power is transferred to the third planet carrier PC3 through the first clutch C1 The output is to the third connecting member L3; in the second planetary row P2, the second sun gear S2 is fixed, the third connecting member L3 diverts one-way power to the second ring gear R2, outputs it to the second planet carrier PC2 through the second planetary gear CA2, and outputs it to the fourth ring gear R4 through the fourth connecting member L4; in the fourth planetary row P4, the fourth ring gear R4 inputs one-way power, outputs it to the fourth planet carrier PC4 through the fourth planetary gear CA4, the fourth sun gear S4 obtains one-way power diverted by the third connecting member L3, and outputs it to the fourth ring gear R4 through the fourth planetary gear CA4. The power is output to the fourth planetary carrier PC4, and the two powers are output to the output shaft OUT after merging; on the third connecting member L3, the three powers on the fifth ring gear R5, the first ring gear R1 and the third planetary carrier PC3 are merged, and one power is diverted and output to the second ring gear R2, the second planetary carrier PC2, the fourth connecting member L4, and the fourth ring gear R4 in sequence, and the other diverted power is output to the fourth sun gear S4, and finally, after merging with the fourth planetary carrier PC4, the power is output to the output shaft OUT, and the rotation direction is the same as the input shaft IN, realizing the fifth forward gear.

[0112] F6: The first brake B1 and the second brake B2 are engaged at the same time, the first sun gear S1 and the second sun gear S2 are fixed, the fifth planet carrier PC5 is fixedly connected to the input shaft IN, and the input shaft IN inputs power; in the fifth planet row P5, the fifth planet carrier PC5 inputs power, and the power is split into two paths, one path is split to the fifth sun gear S5, and is output to the first planet carrier PC1 through the fifth connecting member L5, and the other path is split to the fifth ring gear R5, and is output to the third connecting member L3; in the first planet row P1, the first sun gear S1 is fixed, the first planet carrier PC1 inputs power, and the power is output to the first ring gear R1 and the third connecting member L3 in sequence; in the second planet row P2, the second sun gear S2 is fixed, and the third connecting member L3 splits one path of power to the second ring gear R2, and is output to the second row through the second planet gear CA2. The fourth planetary gear P4 inputs one power path to the fourth ring gear R4, and outputs it to the fourth planetary gear carrier PC4 through the fourth planetary gear CA4. The fourth sun gear S4 obtains one power path diverted by the third connecting member L3, and outputs it to the fourth planetary gear carrier PC4 through the fourth planetary gear CA4. The two powers merge and are output to the output shaft OUT. On the third connecting member L3, the fifth ring gear R5 merges with the two powers on the first ring gear R1, and one power path is diverted and output to the second ring gear R2, the second planetary gear carrier PC2, the fourth connecting member L4, and the fourth ring gear R4 in sequence. The other power path is output to the fourth sun gear S4, and finally, after merging with the fourth planetary gear carrier PC4, the power is output to the output shaft OUT. The rotation direction is the same as that of the input shaft IN, realizing the sixth forward gear.

[0113] F7: The first brake B1 and the first clutch C1 are engaged at the same time, the first sun gear S1 is fixed, the third connecting member L3 and the third planet carrier PC3 move synchronously, the fifth planet carrier PC5 is fixedly connected to the input shaft IN, and the input shaft IN inputs power; in the fifth planet row P5, the fifth planet carrier PC5 inputs power, and the power is split into two paths, one is split to the fifth sun gear S5, and output to the first planet carrier PC1 through the fifth connecting member L5, and the other is split to the fifth ring gear R5, and output to the third connecting member L3; in the first planet row P1, the first sun gear S1 is fixed, the first planet carrier PC1 ... The power is output to the first ring gear R1 and the third connecting member L3 in sequence; in the third planetary row P3, the third sun gear S3 is fixedly connected to the first sun gear S1 through the first connecting member L1 and is in a fixed state, and the third planetary carrier PC3 obtains a path of power diverted by the third connecting member L3 through the first clutch C1, outputs it to the third ring gear R3 through the third planetary gear CA3, and outputs it to the second sun gear S2 through the second connecting member L2; in the second planetary row P2, the second sun gear S2 inputs a path of power, outputs it to the second planetary carrier PC2 through the second planetary gear CA2, and the third connecting member L3 diverts the power. One power path is output to the second ring gear R2, and is output to the second planet carrier PC2 through the second planetary gear CA2. The second planet carrier PC2 is fixedly connected to the fourth ring gear R4 through the fourth connecting member L4. The two powers are combined and output to the fourth ring gear R4. In the fourth planetary row P4, the fourth ring gear R4 inputs one power path, and is output to the fourth planet carrier PC4 through the fourth planetary gear CA4. The fourth sun gear S4 obtains one power path diverted by the third connecting member L3, and is output to the fourth planet carrier PC4 through the fourth planetary gear CA4. The two powers are combined and output to the output shaft OUT. On the third connecting member L3, the fourth sun gear S4 receives one power path diverted by the third connecting member L3, and is output to the fourth planet carrier PC4 through the fourth planetary gear CA4. The two powers are combined and output to the output shaft OUT. After the two-way power on the fifth ring gear R5 merges with the first ring gear R1, one way is diverted to the third planet carrier PC3, and is output to the third ring gear R3, the second connecting member L2, the second sun gear S2, the second planet carrier PC2, the fourth connecting member L4, and the fourth ring gear R4 in sequence. The second way is diverted to the second ring gear R2, and is output to the second planet carrier PC2, the fourth connecting member L4, and the fourth ring gear R4 in sequence. The diverted third way of power is output to the fourth sun gear S4. Finally, the three ways of power are output to the output shaft OUT after merging on the fourth planet carrier PC4. The rotation direction is the same as that of the input shaft IN, realizing the seventh forward gear.

[0114] F8: The fifth brake B5 is engaged with the second brake B2 at the same time, the fifth sun gear S5 and the second sun gear S2 are fixed, the fifth planet carrier PC5 is fixedly connected to the input shaft IN, and the input shaft IN inputs power; in the fifth planet row P5, the fifth sun gear S5 is fixed, the fifth planet carrier PC5 inputs power, and outputs power to the fifth ring gear R5 and the third connecting member L3 in sequence; in the second planet row P2, the second sun gear S2 is fixed, the third connecting member L3 diverts one path of power to the second ring gear R2, outputs to the second planet carrier PC2 through the second planet gear CA2, and outputs to the fourth ring gear R4 through the fourth connecting member L4; in the fourth planet row P4, the fourth ring gear R4 One power path is input and output to the fourth planet carrier PC4 through the fourth planetary gear CA4. The fourth sun gear S4 obtains one power path diverted by the third connecting member L3, and output to the fourth planet carrier PC4 through the fourth planetary gear CA4. The two power paths are combined and output to the output shaft OUT. On the third connecting member L3, the fifth ring gear R5 outputs power to the third connecting member L3, and one power path is diverted to the second ring gear R2, which is output to the second planet carrier PC2, the fourth connecting member L4, and the fourth ring gear R4 in sequence. The other diverted power path is output to the fourth sun gear S4, and finally, after merging with the fourth planet carrier PC4, the power is output to the output shaft OUT. The rotation direction is the same as that of the input shaft IN, realizing the eighth forward gear.

[0115] F9: The fifth brake B5 and the third brake B3 are engaged at the same time, the fifth sun gear S5 and the third planet carrier PC3 are fixed, the fifth planet carrier PC5 is fixedly connected to the input shaft IN, and the input shaft IN inputs power; in the fifth planet row P5, the fifth sun gear S5 is fixed, the fifth planet carrier PC5 inputs power, and outputs power to the fifth ring gear R5 and the third connecting member L3 in sequence; in the first planet row P1, the first planet carrier PC1 is connected to the fifth sun gear S5 through the fifth connecting member L5, and is synchronously in a fixed state, the first ring gear R1 is fixedly connected to the fifth ring gear R5 through the third connecting member L3, and the fifth ring gear R5 is fixedly connected to the fifth ring gear R5 through the third connecting member L3. The first ring gear R1 inputs power, and the power is output to the first sun gear S1 through the first planetary gear CA1, and is output to the third sun gear S3 through the first connecting member L1; in the third planetary row P3, the third planetary carrier PC3 is fixed, the third sun gear S3 inputs power, and is output to the third ring gear R3 through the third planetary gear CA3, and is output 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, and is output to the second planetary carrier PC2 through the second planetary gear CA2, and the third connecting member L3 diverts power to the second ring gear R2, and outputs power to the second sun gear S2 through the second planetary gear CA2. The star gear CA2 outputs to the second planet carrier PC2, and the second planet carrier PC2 is fixedly connected to the fourth ring gear R4 through the fourth connecting member L4, and the two powers are output to the fourth ring gear R4 after merging; in the fourth planet row P4, the fourth ring gear R4 inputs one power, and outputs to the fourth planet carrier PC4 through the fourth planet gear CA4, the fourth sun gear S4 obtains one power diverted by the third connecting member L3, and outputs to the fourth planet carrier PC4 through the fourth planet gear CA4, and the two powers are output to the output shaft OUT after merging; on the third connecting member L3, the fifth ring gear R5 outputs power to the third connecting member L3, and the power is diverted to the fourth sun gear S4. One path of power flows to the first ring gear R1, and is output to the first sun gear S1, the first connecting member L1, the third sun gear S3, the third ring gear R3, the second connecting member L2, the second sun gear S2, the second planetary carrier PC2, the fourth connecting member L4, and the fourth ring gear R4 in sequence. The second path of power is diverted to the second ring gear R2, and is output to the second planetary carrier PC2, the fourth connecting member L4, and the fourth ring gear R4 in sequence. The diverted third path of power is output to the fourth sun gear S4, and finally the three diverted powers are merged at the fourth planetary carrier PC4 and output to the output shaft OUT. The direction of rotation is the same as that of the input shaft IN, realizing the ninth forward gear.

[0116] F10: The fifth brake B5 is engaged with the first clutch C1 at the same time, the fifth sun gear S5 is fixed, the third connecting member L3 and the third planet carrier PC3 move synchronously, the fifth planet carrier PC5 is fixedly connected to the input shaft IN, and the input shaft IN inputs power; in the fifth planet row P5, the fifth sun gear S5 is fixed, the fifth planet carrier PC5 inputs power, and outputs power to the fifth ring gear R5 and the third connecting member L3 in sequence; in the first planet row P1, the first planet carrier PC1 is connected to the fifth sun gear S5 through the fifth connecting member L5, and is synchronously in a fixed state, the first ring gear R1 is fixedly connected to the fifth ring gear R5 through the third connecting member L3, the first ring gear R1 inputs power, and the power is output to through the first planet gear CA1 The first sun gear S1 is output to the third sun gear S3 through the first connecting member L1; in the third planetary row P3, the third sun gear S3 inputs one-way power, and the diverted part of the power is output to the third ring gear R3 through the third planetary gear CA3, and the third planetary carrier PC3 obtains part of the power diverted by the third connecting member L3 through the first clutch C1, and outputs it to the third ring gear R3 through the third planetary gear CA3. After the two-way power merges in the third ring gear R3, it is output to the second sun gear S2 through the second connecting member L2; in the second planetary row P2, the second sun gear S2 inputs one-way power, and outputs it to the second planetary carrier PC2 through the second planetary gear CA2, and the third connecting member L3 diverts one-way power to the second ring gear R2, and outputs it to the second planetary carrier PC2 through the second planetary gear CA2. The second planetary gear CA2 outputs to the second planetary carrier PC2, and the second planetary carrier PC2 is fixedly connected to the fourth ring gear R4 through the fourth connecting member L4, and the two powers are combined and output to the fourth ring gear R4; in the fourth planetary row P4, the fourth ring gear R4 inputs one power path, which is output to the fourth planetary carrier PC4 through the fourth planetary gear CA4, and the fourth sun gear S4 obtains one power path diverted by the third connecting member L3, which is output to the fourth planetary carrier PC4 through the fourth planetary gear CA4, and the two powers are combined and output to the output shaft OUT; on the third connecting member L3, the fifth ring gear R5 outputs power to the third connecting member L3, which is diverted to the first ring gear R1, and is output to the first sun gear S1, the first connecting member L1, and the third sun gear S1 in sequence. S3, third planet carrier PC3, third ring gear R3, second connecting member L2, second sun gear S2, second planet carrier PC2, fourth connecting member L4, fourth ring gear R4, the second path is shunted to the third planet carrier PC3, and output to the third ring gear R3, second connecting member L2, second sun gear S2, second planet carrier PC2, fourth connecting member L4, fourth ring gear R4 in sequence, the third path is shunted to the second ring gear R2, and output to the second planet carrier PC2, fourth connecting member L4, fourth ring gear R4 in sequence, the shunted fourth path power is output to the fourth sun gear S4, and finally the four shunted powers are output to the output shaft OUT after merging at the fourth planet carrier PC4, and the rotation direction is the same as the input shaft IN, realizing the tenth forward gear.

[0117] R: The third brake B3 and the first clutch C1 are engaged at the same time, and the fifth ring gear R5, the first ring gear R1, the third planet carrier PC3, the second ring gear R2, and the fourth sun gear S4 are fixed respectively. The fifth planet carrier PC5 is fixedly connected to the input shaft IN, and the input shaft IN inputs power; in the fifth planet row P5, the fifth ring gear R5 is fixed, the fifth sun gear S5 is fixedly connected to the first planet carrier PC1 through the fifth connecting member L5, and the fifth planet carrier PC5 inputs power, and outputs power to the fifth sun gear S5, the fifth connecting member L5, the first planet carrier P C1; in the first planetary row P1, the first ring gear R1 is fixed, the first sun gear S1 is fixedly connected to the third sun gear S3 through the first connecting member L1, the first planetary carrier PC1 inputs power, and through the first planetary gear CA1, the power is sequentially output to the first sun gear S1, the first connecting member L1, and the third sun gear S3; in the third planetary row P3, the third planetary carrier PC3 is fixed, the third ring gear R3 is fixedly connected to the second sun gear S2 through the second connecting member L2, the third sun gear S3 inputs power, and through the third planetary gear CA3, the power is sequentially output to The third ring gear R3, the second connecting member L2, and the second sun gear S2; in the second planetary row P2, the second ring gear R2 is fixed, the second planet carrier PC2 is fixedly connected to the fourth ring gear R4 through the fourth connecting member L4, the second sun gear S2 inputs power, and through the second planetary gear CA2, the power is sequentially output to the second planetary carrier PC2, the fourth connecting member L4, and the fourth ring gear R4; in the fourth planetary row P4, the fourth sun gear S4 is fixed, the fourth ring gear R4 inputs power, and is output to the fourth planet carrier PC4 through the fourth planetary gear CA4, and finally output to the output Shaft OUT; the power is transmitted in the fifth planetary gear P5, the first planetary gear P1, the third planetary gear P3, the second planetary gear P2 and the fourth planetary gear P4 in a single-path power mode. In the fifth planetary gear P5, the first planetary gear P1, the second planetary gear P2 and the fourth planetary gear P4, the power output direction is the same as the input direction. In the third planetary gear P3, because the sun gear inputs power and the ring gear outputs power, the output power direction is opposite to the input power direction. Finally, the power rotates on the output shaft OUT in the opposite direction to the input shaft IN, achieving one reverse gear.

[0118] The transmission ratio of each gear is determined by the K value of the five planetary gears. The K value of the planetary gear refers to the ratio of the number of teeth of the planetary gear ring to the number of teeth of the sun gear. For example, when K1=3, K2=5, K3=4, K4=K5=3, the transmission ratio of each gear shown in Table 1 can be obtained, and a speed change mechanism with ten forward gears and one reverse gear can be realized; the transmission ratio range of this embodiment is relatively large, and is divided into three working ranges. In the high transmission ratio range, the first gear is used for climbing and the second gear is used for starting; in the medium transmission ratio range, the third and fourth gears provide large torque acceleration, which can ensure good acceleration performance at a higher vehicle speed; in the low transmission ratio range, the fifth to tenth gears gradually transition from low speed gear to overspeed gear, and the step ratio is more fine, which can make the engine run more in the economic working area, thereby improving the economy of the whole machine.

[0119] It can be seen from the shifting logic of each gear in Table 2 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.

[0120] 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 3. 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 5. 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 4. 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.

[0121] Optionally, the transmission ratio of the first forward gear is 10.00, the transmission ratio of the second forward gear is 8.75, the transmission ratio of the third forward gear is 3.75, the transmission ratio of the fourth forward gear is 3.00, the transmission ratio of the fifth forward gear is 1.43, the transmission ratio of the sixth forward gear is 1.07, the transmission ratio of the seventh forward gear is 0.91, the transmission ratio of the eighth forward gear is 0.86, the transmission ratio of the ninth forward gear is 0.77, and the transmission ratio of the tenth forward gear is 0.67; the transmission ratio of the first reverse gear is 2.00.

[0122] Optionally, the step ratio of the first forward gear to the second forward gear is 1.14, the step ratio of the second forward gear to the third forward gear is 2.33, the step ratio of the third forward gear to the fourth forward gear is 1.25, the step ratio of the fourth forward gear to the fifth forward gear is 2.10, the step ratio of the fifth forward gear to the sixth forward gear is 1.33, the step ratio of the sixth forward gear to the seventh forward gear is 1.18, the step ratio of the seventh forward gear to the eighth forward gear is 1.06, the step ratio of the eighth forward gear to the ninth forward gear is 1.11, and the step ratio of the ninth forward gear to the tenth forward gear is 1.16; the transmission ratio range of the highest gear and the lowest gear is about 15.00.

[0123] This embodiment discloses a power control mechanism for a planetary gear combination clutch for a vehicle transmission system, such as Figure 3As shown, it includes an input shaft IN, an output shaft OUT, five planetary gears (P1 to P5), five brakes (B1 to B5), a clutch (C1), and five connecting parts (L1 to L5).

[0124] Each planetary row includes: a sun gear (S1 to S5), a planet carrier (PC1 to PC5), a planetary gear (CA1 to CA5) and a ring gear (R1 to R5); the ring gear is coaxially distributed with the sun gear, and the planetary gears are respectively mounted on the planet carrier through planetary shafts and bearings, and each planetary gear is internally meshed with the ring gear on the same planetary row and externally meshed with the sun gear on the same planetary row.

[0125] Five planetary gears and one clutch are arranged in parallel from left to right, and five sun gears, one clutch, an input shaft IN and an output shaft OUT are arranged coaxially.

[0126] The power control mechanism of the planetary gear combined clutch for the vehicle transmission system in the present application includes five planetary gears, five brakes, and one clutch. The planetary gears are all single-planet simple planetary gears, which can achieve up to ten forward gears and one reverse gear, with multiple gears and a large transmission ratio range. The transmission ratio has three working ranges of high, medium, and low, which can make the engine adapt to different working conditions and operate more in the economic working area, thereby improving the economy of the whole machine. The five brakes and one clutch are all friction control structures, and the gear position is controlled by two elements, which can reduce the sliding friction work and heat loss of the friction plate and improve the reliability of the friction plate.

[0127] Third embodiment:

[0128] A vehicle transmission system includes a power control mechanism of a planetary gear combination clutch according to any one of the first embodiment and the second embodiment.

[0129] 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 requirements of the vehicle.

[0130] 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 creative concept of the present invention, which all belong to the protection scope of the present invention.

Claims

1. A power control mechanism of a planetary gear combination clutch, characterized in that: It includes a first clutch (C1), a third planetary gear (P3), a third brake (B3) and a third connecting member (L3); The first clutch (C1) comprises a first clutch active member (C11) and a first clutch driven member (C12); 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 first clutch active member (C11) is fixedly connected to the third connecting member (L3); The first clutch driven member (C12) is fixedly connected to the third planet carrier (PC3); The third sun gear (S3) of the third planetary gear (P3) is movably mounted on the third connecting member (L3); The third planet carrier (PC3) is connected to the third brake (B3).

2. A power control mechanism of a planetary gear combination clutch according to claim 1, characterized in that: When the first clutch (C1) and the third brake (B3) are both in a disengaged state, one-way power is transmitted through the third connecting member (L3), thereby realizing single-way power single-path power transmission; When the first clutch (C1) is engaged alone, one power path is transmitted through the third connecting member (L3), and the other power path is transmitted through the third sun gear (S3). The two power paths are divided and then merged to form two new power paths, which are output from the third connecting member (L3) and the third ring gear (R3) respectively, thus realizing dual-path power mixed flow dual-path power transmission; When the third brake (B3) is engaged alone, one power path is transmitted through the third connecting member (L3), and the other power path is transmitted through the third sun gear (S3) and the third ring gear (R3), thereby realizing dual-path power transmission with non-mixed flow and dual paths; When the first clutch (C1) and the third brake (B3) are in the engaged state at the same time, one power path is transmitted through the third sun gear (S3) and output through the third ring gear (R3), thus realizing single power path power transmission.

3. A power control mechanism of a planetary gear combination clutch according to claim 2, characterized in that: The third sun gear (S3) and the third ring gear (R3) are interchangeable in purpose.

4. A power control mechanism for a planetary gear combination clutch according to claim 1, characterized in that: Also includes a first planetary gear set (PZ1), a second planetary gear set (PZ2), an input shaft (IN) and an output shaft (OUT); The first planetary gear set (PZ1) is arranged on one side of the third planetary gear set (P3), and the second planetary gear set (PZ2) is arranged on the other side of the third planetary gear set (P3); The input shaft (IN) is connected to the first planetary gear set (PZ1); The output shaft (OUT) is connected to the second planetary gear set (PZ2).

5. A power control mechanism for a planetary gear combination clutch according to claim 4, characterized in that: The first planetary gear set (PZ1) comprises a fifth planetary gear (P5) and a first planetary gear (P1); The input shaft (IN) is connected to the fifth planetary gear (P5), and the first planetary gear (P1) is connected to the third planetary gear (P3).

6. A power control mechanism for a planetary gear combination clutch according to claim 5, characterized in that: The fifth planetary gear (P5) comprises a fifth sun gear (S5), a fifth planet carrier (PC5), a fifth planet gear (CA5) and a fifth ring gear (R5); the fifth sun gear (S5) is movably mounted on the input shaft (IN); the fifth sun gear (S5) is fixedly connected to the first planet carrier (PC1) via a fifth connecting member (L5); the fifth ring gear (R5) is fixedly connected to the third connecting member (L3); the fifth sun gear (S5) is connected to the fifth brake (B5); the fifth planet carrier (PC5) is fixedly connected to the input shaft (IN); The first planetary gear (P1) comprises a first sun gear (S1), a first planet carrier (PC1), a first planetary gear (CA1) and a first ring gear (R1); the first sun gear (S1) is movably mounted on a third connecting member (L3); the first sun gear (S1) is fixedly connected to the third sun gear (S3) via the first connecting member (L1); the first ring gear (R1) is fixedly connected to the third connecting member (L3); the first sun gear (S1) is connected to a first brake (B1).

7. A power control mechanism for a planetary gear combination clutch according to claim 4, characterized in that: The second planetary gear set (PZ2) comprises a second planetary gear (P2) and a fourth planetary gear (P4); The second planetary gear (P2) is connected to the third planetary gear (P3); and the fourth planetary gear (P4) is connected to the output shaft (OUT).

8. A power control mechanism for a planetary gear combination clutch according to claim 7, characterized in that: The second planetary gear (P2) comprises a second sun gear (S2), a second planet carrier (PC2), a second planet gear (CA2) and a second ring gear (R2); the second sun gear (S2) is movably mounted on a third connecting member (L3); the second sun gear (S2) is fixedly connected to the third ring gear (R3) via the second connecting member (L2); the second planet carrier (PC2) is fixedly connected to the fourth ring gear (R4) via a fourth connecting member (L4); the second ring gear (R2) is fixedly connected to the third connecting member (L3); the second sun gear (S2) is connected to a second brake (B2); 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 sun gear (S4) is fixedly connected to a third connecting member (L3); the fourth ring gear (R4) is connected to a fourth brake (B4); and the fourth planet carrier (PC4) is fixedly connected to an output shaft (OUT).

9. A power control mechanism for a planetary gear combination clutch according to claim 4, characterized in that: Calculate the number of forward gears using the formula n1×n2+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).

10. A vehicle transmission system, characterized in that: A power control mechanism comprising a planetary gear combination clutch as described in any one of claims 1-9.

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