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

Abstract

The utility model 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 piece of the first clutch is fixedly connected with a third planet carrier, and a driving piece of the first clutch is fixedly connected with a third connecting piece; 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 utility model relates to vehicle transmission technical field, especially a kind of power control mechanism of planetary array combined clutch and vehicle transmission system. BACKGROUND

[0002] The automatic transmission (AT) applied to more than six gear positions of current traffic vehicle, the transmission mechanism is basically the optimization combination of Simpson mechanism, Ravigneaux mechanism and CR-CR mechanism, selects two groups in the above three transmission mechanisms, increases brake and clutch as control mechanism, scatters the structure of two groups of transmission mechanisms, reorganizes, improves the degree of freedom of gearbox, improves the reuse rate of planetary array, usually four planetary arrays can be used to realize the change of more than six gear positions, the disadvantage is that transmission logic is complex, and further causes complex structure, often needs the special design software to assist structure design, engineering difficulty increases, manufacturing cost and maintenance cost also increase accordingly.

[0003] A kind of planetary multi-stage transmission gear mechanism (patent application number: 2024117698989), utilizes one planetary array to carry out the control mode of power transmission or interruption, can give consideration to the reuse rate of transmission mechanism under the premise of significantly reducing the complexity of transmission mechanism, provides the design idea of planetary array participating in power control.

[0004] Therefore, an urgent need exists for a gearbox that combines the above technical advantages, has multiple gear positions, a large transmission ratio range, simple gear control logic, fewer transmission mechanisms, and transmission components with high reuse rate. UTILITY MODEL CONTENT

[0005] The utility model aims at providing a kind of power control mechanism of planetary array combined clutch and vehicle transmission system to make full use of the advantages of above-mentioned technical route. To achieve this purpose, the utility model adopts the following technical solutions:

[0006] A kind of power control mechanism of planetary array combined clutch, including first clutch, third planetary array, third brake and third connecting piece;

[0007] First clutch includes first clutch driver and first clutch driven piece;

[0008] Third planetary array includes third sun gear, third planet carrier, third planet wheel and third ring gear;

[0009] First clutch driver is fixedly connected with third connecting piece;

[0010] First clutch driven piece is fixedly connected with third planet carrier;

[0011] Third sun gear of third planetary array is movably installed on third connecting piece;

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

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

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

[0015] When the third brake is engaged alone, one power is transmitted through the third connecting member, and the other power is transmitted through the third sun gear and the third ring gear, realizing double-path power transmission of non-mixed double power;

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

[0017] In some embodiments, the third sun gear and the third ring gear are interchangeable in use, and the effects are also the same.

[0018] In some embodiments, the transmission further comprises a first planetary gear set, a second planetary gear set, an input shaft and an output shaft;

[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 with the first planetary gear set, and the output shaft is connected with the second planetary gear set.

[0021] In some embodiments, the first planetary gear set comprises a fifth planetary gear set and a first planetary gear set; the input shaft is connected with the fifth planetary gear set, and the first planetary gear set is connected with the third planetary gear set.

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

[0023] The first planetary gear set comprises a first sun gear, a first planet carrier, a first planet gear and a first ring gear; the first sun gear is movably installed on the third connecting member; the first sun gear is fixedly connected with the third sun gear through the first connecting member; the first ring gear is fixedly connected with the third connecting member; and the first sun gear is connected with the first brake.

[0024] In some embodiments, the second planetary gear set comprises a second planetary gear set and a fourth planetary gear set; the second planetary gear set is connected with the third planetary gear set; and the fourth planetary gear set is connected with the output shaft.

[0025] In some embodiments, the second planetary gear set comprises a second sun gear, a second planet carrier, a second planet gear and a second ring gear; the second sun gear is movably installed on the third connecting member; the second sun gear is fixedly connected with the third ring gear through the second connecting member; the second planet carrier is fixedly connected with the fourth ring gear through the fourth connecting member; the second ring gear is fixedly connected with the third connecting member; and the second sun gear is connected with the second brake.

[0026] The fourth planetary gear set 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 with the third connecting member; the fourth ring gear is connected with the fourth brake; and the fourth planet carrier is fixedly connected with the output shaft.

[0027] The utility model discloses the beneficial effect of the following:

[0028] 1. The power control mechanism of the planetary gear set combined clutch adopts the mode of controlling the power transmission path, so that the power is transmitted in four transmission states, as the control mechanism between the two planetary gear sets, by increasing the transmission path, the number of gears is increased, the gear shifting logic is simple, the gears have strong expansibility, the number of transmission gears is: forward gear number n1x n2 + n1 + n2 + (n1-1) + (n2-1), reverse gear number 1, and the reuse rate of the planetary gear set is greatly improved; at the same time, the double-path transmission belongs to the mixed transmission of two-stage transmission and multi-stage transmission, so that the upper limit of the forward gear transmission ratio can be increased and the lower limit can be reduced, and the transmission ratio range of the forward gear is expanded.

[0029] 2. The main components of the power control mechanism of the planetary gear set combined clutch are a planetary gear set, a brake and a clutch, and the three can fully exert the power control function of the planetary gear set and the clutch, compared with the technical scheme that multiple brakes and multiple clutches are generally adopted in the prior art, the complexity and manufacturing difficulty of the speed change mechanism are significantly reduced, and the number of gears can also be easily increased, which has obvious progress. BRIEF DESCRIPTION OF DRAWINGS

[0030] Figure 1 It is a structure diagram of the power control mechanism of the planetary gear set combined clutch of the first embodiment of the utility model.

[0031] Figure 2 The structure diagram of the planetary gear set combination clutch power control mechanism of the second embodiment of the utility model.

[0032] Figure 3 The structure diagram of the planetary gear set combination clutch power control mechanism of the second embodiment of the utility model. DETAILED DESCRIPTION

[0033] The utility model will be further explained in detail in connection with the drawings.

[0034] First embodiment:

[0035] Reference Figure 1 A planetary gear set combination clutch power control mechanism, comprising a first clutch C1, a third planetary gear set P3, a third brake B3 and a third connecting piece L3.

[0036] The first clutch C1 comprises a first clutch driving piece C11 and a first clutch driven piece C12.

[0037] The third planetary gear set P3 comprises a third sun gear S3, a third planet carrier PC3, a third planet gear CA3 and a third ring gear R3; the third planet gear CA3 is movably installed on the third planet carrier PC3, the third ring gear R3 is engaged with the third planet gear CA3, and the third planet gear CA3 is engaged with the third sun gear S3.

[0038] The first clutch driving piece C11 is fixedly connected with the third connecting piece L3.

[0039] The first clutch driven piece C12 is fixedly connected with the third planet carrier PC3.

[0040] The third sun gear S3 of the third planetary gear set P3 is movably installed on the third connecting piece L3.

[0041] The third planet carrier PC3 is connected with 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 the rotary connection; the fixed connection can be understood as the linkage connection.

[0043] Working principle:

[0044] The third sun gear S3 and the third connecting piece L3 can both be used as the input end of the power, for example, the power is input on the third sun gear S3, or the power is input on the third connecting piece L3, or the corresponding power is input on the third sun gear S3 and the third connecting piece L3 at the same time, and correspondingly, under the different combinations of the first clutch C1 and the third brake B3, the third ring gear R3 and the third connecting piece 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] First transmission state: the first clutch C1 and the third brake B3 are both in the disengaged state.

[0047] First power input: the third connecting piece L3 inputs the first power, and the first power is transmitted through the third connecting piece L3. Since the first clutch C1 is in the disengaged state, power is not transmitted to the third planet carrier PC3, and the first power is directly output on the third connecting piece L3, with the same rotation direction as 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 externally.

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

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

[0051] First power input: the third connecting piece L3 inputs the first power, and the first power is transmitted through the third connecting piece L3. On the third connecting piece L3, the power is split into two paths, the first 1.1 power is output through the third connecting piece L3, and the first 1.2 power is output to the third planet carrier PC3 through the first clutch driver C11 and the first clutch follower C12, and finally output externally 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 paths, the second 2.1 power is output to the third connecting piece L3 through the third planet carrier PC3, the first clutch follower C12, and the first clutch driver C11, and the second 2.2 power is output externally through the third ring gear R3.

[0053] Simultaneous input of the first power and the second power: the first 1.1 power and the second 2.1 power are output after merging on the third connecting piece L3, and the first 1.2 power and the second 2.2 power are output after merging on the third ring gear R3, realizing double-path power transmission of mixed double power.

[0054] Third transmission state: the third brake B3 is engaged alone, fixing the third planet carrier PC3.

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

[0056] The second power input: the third sun gear S3 inputs the second power, and the second power is transmitted through the third sun gear S3, and in the third planetary gear set P3, the third sun gear S3 inputs power, and the power is output 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;

[0057] The first power and the second power are simultaneously input: 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, and the double-path power transmission of the first power and the second power is realized without mixing.

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

[0059] The first power input: the third connecting piece L3 inputs the first power, and because the third connecting piece L3 is fixed, the first power is not output externally;

[0060] The second power input: the third sun gear S3 inputs the second power, and the second power is transmitted through the third sun gear S3, and in the third planetary gear set P3, the third sun gear S3 inputs power, and the power is output 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;

[0061] The first power and the second power are simultaneously input: because the first power is not output externally, only the second power is output externally, and the single-path transmission of the second power is realized.

[0062] The 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 embodiment, with reference to Figure 2 , Figure 3 , n1 planetary gear sets can be arranged side by side to form a first planetary gear set group PZ1, and the third connecting piece L3 and the third sun gear S3 are fixedly connected with two basic components on one planetary gear set in the first planetary gear set group PZ1; n2 planetary gear sets are arranged side by side to form a second planetary gear set group PZ2, and the third connecting piece L3 and the third ring gear R3 are fixedly connected with two basic components on one planetary gear set in the second planetary gear set group PZ2; wherein the planetary gear set includes three basic components, which are sun gear, planetary carrier and ring gear; each planetary gear set in the two planetary gear set 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 set P3 does not transmit power, realizing single-path transmission of power by the third connecting piece L3; n1 planetary gear sets in the first planetary gear set group PZ1 and n2 planetary gear sets in the second planetary gear set group PZ2 are combined in pairs, and there are n1*n2 combinations, the brakes arranged on a pair of planetary gear sets in each of the n1*n2 combinations are simultaneously braked, a two-stage transmission can be realized, the rotation direction of the power output is the same as that 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 two-way power is mixed on the third connecting piece L3 and the third planetary gear set P3; after the brakes arranged on the n1 planetary gear sets in the first planetary gear set group PZ1 and the n2 planetary gear sets in the second planetary gear set group PZ2 are sequentially braked, the system has only one degree of freedom, has a determined input and output, and n1+n2 two-way power mixed double-path power transmission can be realized.

[0066] The third transmission state: the third brake B3 is engaged alone, fixing the third planet carrier PC3; the two-way power of the third connecting piece L3 and the third planetary gear set P3 is not mixed; after the brakes arranged on the n1 planetary gear sets in the first planetary gear set group PZ1 and the n2 planetary gear sets in the second planetary gear set group PZ2 are sequentially braked, the system has only one degree of freedom, has a determined input and output, and n1+n2 transmission combinations can be realized; after the brakes arranged on the planetary gear sets having a connection relationship with the third planetary gear set P3 are braked, in the state that the third brake B3 is engaged and the third planet carrier PC3 is fixed, the third planetary gear set P3 does not transmit power, only single-path transmission of single-way power of the third connecting piece L3 is realized, which coincides with the first transmission state, and after being removed, (n1-1)+(n2-1) two-way power non-mixed double-path power transmission can be realized.

[0067] The fourth transmission state: the first clutch C1 and the third brake B3 are simultaneously engaged, respectively fixing the third connecting piece L3 and the third planet carrier PC3; the third connecting piece L3 is fixed and does not transmit power; power is transmitted through the third sun gear S3, in the third planetary gear set P3, the third sun gear S3 inputs power, and the power is output to the third ring gear R3 through the third planet gear CA3, the rotation direction of the output power is opposite to that of the input power, and 1 single-power single-path transmission can be realized.

[0068] The power control mechanism of the planetary gear set combination clutch can be applied to two planetary gear sets, and the number of forward gears with the same direction as the power input is n1*n2+n1+n2+(n1-1)+(n2-1), and the number of reverse gears with the opposite direction as the power input is 1.

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

[0070] First, power flows from the third sun gear S3 and the third connecting piece L3 to the same end of the third sun gear S3, and flows out from the third ring gear R3 and the third connecting piece L3 to the same end of the third ring gear R3.

[0071] Second, power flows from the third ring gear R3 and the third connecting piece L3 to the same end of the third ring gear R3, and flows out from the third sun gear S3 and the third connecting piece L3 to the same end of 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] Reference Figure 3 A power control mechanism of a planetary gear set combined clutch, which is applied to the first embodiment and additionally provided with a fifth planetary gear set P5, a first planetary gear set P1, a second planetary gear set P2 and a fourth planetary gear set P4; the arrangement is that the fifth planetary gear set P5, the first planetary gear set P1, the third planetary gear set P3, the first clutch C1, the second planetary gear set P2 and the fourth planetary gear set P4 are sequentially and parallelly distributed.

[0075] The fifth planetary gear set 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 gear CA5 is movably installed on the fifth planet carrier PC5, the fifth ring gear R5 is engaged with the fifth planet gear CA5, the fifth planet gear CA5 is engaged with the fifth sun gear S5, and the fifth sun gear S5 is connected with the fifth brake B5, that is, the fifth sun gear S5 can be braked through the fifth brake B5.

[0076] The first planetary gear set P1 includes a first sun gear S1, a first planet carrier PC1, a first planet gear CA1 and a first ring gear R1, the first planet gear CA1 is movably installed on the first planet carrier PC1, the first ring gear R1 is engaged with the first planet gear CA1, the first planet gear CA1 is engaged with the first sun gear S1, and the first sun gear S1 is connected with the first brake B1, that is, the first sun gear S1 can be braked through the first brake B1.

[0077] The third planetary gear set P3 includes a third sun gear S3, a third planet carrier PC3, a third planet gear CA3 and a third ring gear R3, the third planet gear CA3 is movably installed on the third planet carrier PC3, the third ring gear R3 is engaged with the third planet gear CA3, the third planet gear CA3 is engaged with the third sun gear S3, and the third planet carrier PC3 is connected with the third brake B3, that is, the third planet carrier PC3 can be braked through the third brake B3.

[0078] The first clutch C1 comprises a first clutch driving part C11 and a first clutch driven part C12, and the first clutch driving part C11 and the first clutch driven part C12 move synchronously when the first clutch C1 is engaged.

[0079] The second planetary gear set 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 planet gear CA2 is movably installed on the second planet carrier PC2, the second ring gear R2 is in mesh with the second planet gear CA2, the second planet gear CA2 is in mesh with the second sun gear S2, and the second sun gear S2 is connected with the second brake B2, that is, the second sun gear S2 can be braked through the second brake B2.

[0080] The fourth planetary gear set P4 comprises a fourth sun gear S4, a fourth planet carrier PC4, a fourth planet gear CA4 and a fourth ring gear R4, the fourth planet gear CA4 is movably installed on the fourth planet carrier PC4, the fourth ring gear R4 is in mesh with the fourth planet gear CA4, the fourth planet gear CA4 is in mesh with the fourth sun gear S4, and the fourth ring gear R4 is connected with the fourth brake B4, that is, the fourth ring gear R4 is braked through the fourth brake B4.

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

[0082] The third sun gear S3 is movably installed on the third connecting piece L3, the first clutch driving part C11 is fixedly connected with the third connecting piece L3, the first clutch driven part C12 is fixedly connected with the third planet carrier PC3, and the third connecting piece L3 and the third planet carrier PC3 move synchronously when the first clutch C1 is engaged.

[0083] The fourth planet carrier PC4 is fixedly connected with the output shaft OUT, the second sun gear S2 is movably installed on the third connecting piece L3, and the fourth sun gear S4 is fixedly connected with the third connecting piece L3; the second sun gear S2 is fixedly connected with the third ring gear R3 through the second connecting piece L2, the second planet carrier PC2 is fixedly connected with the fourth ring gear R4 through the fourth connecting piece L4, and the second ring gear R2 is fixedly connected with the third connecting piece 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; the power flow direction is: power flows in from the input shaft IN and flows out from the output shaft OUT.

[0085] The fifth planetary gear set P5 and the first planetary gear set P1 constitute a first planetary gear set group PZ1, the number of planetary gear sets n1=2, the second planetary gear set P2 and the fourth planetary gear set P4 constitute a second planetary gear set group PZ2, the number of planetary gear sets 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, the number of reverse gears is 1;

[0086] The first clutch C1 and the fourth brake B4 are engaged at the same time to realize the first forward gear;

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

[0088] The first brake B1 and the fourth brake B4 are engaged at the same time to realize the third forward gear;

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

[0090] The first clutch C1 and the second brake B2 are engaged at the same time to realize the fifth forward gear;

[0091] The first brake B1 and the second brake B2 are engaged at the same time to realize the sixth forward gear;

[0092] The first brake B1 and the first clutch C1 are engaged at the same time to realize the seventh forward gear;

[0093] The fifth brake B5 and the second brake B2 are engaged at the same time to realize the eighth forward gear;

[0094] The fifth brake B5 and the third brake B3 are engaged at the same time to realize the ninth forward gear;

[0095] The fifth brake B5 and the first clutch C1 are engaged at the same time to realize the tenth forward gear;

[0096] The third brake B3 and the first clutch C1 are engaged at the same time to realize the first reverse gear.

[0097] The related 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: Gear calculation formula:

[0099]

[0100]

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

[0102] The calculation formula in Table 1 also discloses how the power control mechanism of the planetary gear set combination clutch functions when the range of gear ratios is expanded. Compared with the speed formula of the F3 gear control member B1-B4 combination, the denominator of the speed formula of the F2 gear control member B3-B4 combination has an additional coefficient (K2xK3) / (K1+1) composed of K1, K2 and K3, thereby reducing the speed and increasing the gear ratio. Compared with the speed formula of the F2 gear control member B3-B4 combination, the denominator of the speed formula of the F1 gear control member C1-B4 combination has an additional coefficient (K3+1) / (K1+1) composed of K1 and K3, thereby further reducing the speed and increasing the gear ratio.

[0103] Compared with the speed formula of the F8 gear control member B5-B2 combination, the speed formula of the F9 gear control member B5-B3 combination has an additional coefficient K4x(K1 / K3) / (K2+1) composed of K1, K2, K3 and K4, thereby increasing the speed and reducing the gear ratio. Compared with the speed formula of the F9 gear control member B5-B3 combination, the speed formula of the F10 gear control member B5-C1 combination has an additional coefficient K4x(1+1 / K3) / (K2+1) composed of K2, K3 and K4, thereby further increasing the speed and reducing the gear ratio.

[0104] Table 2 Control logic and gear ratios of each gear position (O represents the engagement of the control member)

[0105]

[0106] The present example is described in detail below in combination with Table 2. The gear ratio refers to the ratio of the input shaft speed to the output shaft speed. Figure 2

[0107] ​F1: the first clutch C1 is engaged and the fourth brake B4 is engaged at the same time, the third connecting piece L3 and the third planet carrier PC3 move synchronously, the fourth ring gear R4 is fixed, the fifth planet carrier PC5 is fixedly connected with the input shaft IN, and the input shaft IN inputs power; in the fifth planetary gear set P5, the fifth planet carrier PC5 inputs power, the power is branched into two paths, one path is branched to the fifth sun gear S5 and is output to the first planet carrier PC1 through the fifth connecting piece L5, and the other path is branched to the fifth ring gear R5 and is output to the third connecting piece L3; in the first planetary gear set P1, the first planet carrier PC1 inputs power, the power is branched into two paths, one path is branched to the first sun gear S1 and is output to the third sun gear S3 through the first connecting piece L1, and the other path is branched to the first ring gear R1 and is output to the third connecting piece L3; in the third planetary gear set P3, the third sun gear S3 inputs power, part of the power is branched and is output to the third ring gear R3 through the third planet gear CA3, the third planet carrier PC3 obtains part of the power branched from the third connecting piece L3 through the first clutch C1 and outputs the power to the third ring gear R3 through the third planet gear CA3, and the two paths of power are combined after the third ring gear R3 and are output to the second sun gear S2 through the second connecting piece L2; in the second planetary gear set P2, the second planet carrier PC2 is fixedly connected with the fourth ring gear R4 through the fourth connecting piece L4 and is in a fixed state, the second sun gear S2 inputs power and outputs the power to the second ring gear R2 and the third connecting piece L3 in turn through the second planet gear CA2; in the fourth planetary gear set P4, the fourth ring gear R4 is fixed, the fourth sun gear S4 inputs power and outputs the power to the fourth planet carrier PC4 through the fourth planet gear CA4, and the output power is output to the output shaft OUT; on the third connecting piece L3, the two paths of power combined after the fifth ring gear R5 and the first ring gear R1 are branched and output to the third planet carrier PC3, the second connecting piece L2, the second sun gear S2 and the second ring gear R2 in turn, and the two paths of power are combined again on the third connecting piece L3 and are output to the fourth sun gear S4, and finally the power is output to the output shaft OUT by the fourth planet carrier PC4, the rotating direction is the same as that of the input shaft IN, and gear one is realized.

[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 with the input shaft IN, and the input shaft IN inputs power; in the fifth planetary gear set P5, the fifth planet carrier PC5 inputs power, and the power is branched into two paths, one of which is branched to the fifth sun gear S5 and is output to the first planet carrier PC1 through the fifth connecting piece L5, and the other of which is branched to the fifth ring gear R5 and is output to the third connecting piece L3; in the first planetary gear set P1, the first planet carrier PC1 inputs power, and the power is branched into two paths, one of which is branched to the first sun gear S1 and is output to the third sun gear S3 through the first connecting piece L1, and the other of which is branched to the first ring gear R1 and is output to the third connecting piece L3; in the third planetary gear set P3, the third sun gear S3 inputs power, and the power is output to the third ring gear R3 through the third planet gear CA3 and is output to the second sun gear S2 through the second connecting piece L2; in the second planetary gear set P2, the second planet carrier PC2 is fixedly connected with the fourth ring gear R4 through the fourth connecting piece L4 and is in a fixed state, the second sun gear S2 inputs power, and the power is sequentially output to the second ring gear R2 and the third connecting piece L3 through the second planet gear CA2; in the fourth planetary gear set P4, the fourth ring gear R4 is fixed, the fourth sun gear S4 inputs power, and the power is output to the fourth planet carrier PC4 through the fourth planet gear CA4 and is output to the output shaft OUT; on the third connecting piece L3, the three paths of power on the fifth ring gear R5, the first ring gear R1 and the second ring gear R2 are converged to the third connecting piece L3, sequentially pass through the fourth sun gear S4 and the fourth planet carrier PC4, and finally output power to the output shaft OUT, the rotating direction of which is the same as that of the input shaft IN, and the second gear position is realized.

[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 with the input shaft IN, and the input shaft IN inputs power; in the fifth planetary gear set P5, the fifth planet carrier PC5 inputs power, and the power is branched into two paths, one of which is branched to the fifth sun gear S5 and is output to the first planet carrier PC1 through the fifth connecting piece L5, and the other of which is branched to the fifth ring gear R5 and is output to the third connecting piece L3; in the first planetary gear set P1, the first sun gear S1 is fixed, the first planet carrier PC1 inputs power, and the power is sequentially output to the first ring gear R1 and the third connecting piece L3; in the fourth planetary gear set P4, the fourth ring gear R4 is fixed, the fourth sun gear S4 inputs power, and the power is output to the fourth planet carrier PC4 through the fourth planet gear CA4 and is output to the output shaft OUT; on the third connecting piece L3, the two paths of power on the fifth ring gear R5 and the first ring gear R1 are converged to the third connecting piece L3, sequentially pass through the fourth sun gear S4 and the fourth planet carrier PC4, and finally output power to the output shaft OUT, the rotating direction of which is the same as that of the input shaft IN, and the third gear position is realized.

[0110] F4: the fifth brake B5 is engaged at the same time with the fourth brake B4, the fifth sun gear S5 and the fourth ring gear R4 are fixed, the fifth carrier PC5 is fixedly connected with the input shaft IN, and the input shaft IN inputs power; in the fifth planetary gear set P5, the fifth sun gear S5 is fixed, the fifth carrier PC5 inputs power, and power is sequentially output to the fifth ring gear R5 and the third connecting piece L3; in the fourth planetary gear set P4, the fourth ring gear R4 is fixed, the fourth sun gear S4 inputs power, and power is output to the fourth carrier PC4 through the fourth planetary gear CA4 and then output to the output shaft OUT; on the third connecting piece L3, the fifth ring gear R5 outputs power to the third connecting piece L3, and power is sequentially output to the fourth sun gear S4, the fourth carrier PC4 and finally to the output shaft OUT in the same direction as the input shaft IN, so that the fourth forward gear is achieved.

[0111] F5: the first clutch C1 is engaged and the second brake B2 is engaged at the same time, the third connecting piece L3 and the third planet carrier PC3 move synchronously, the second sun gear S2 is fixed, the fifth planet carrier PC5 is fixed with the input shaft IN, the input shaft IN inputs power; in the fifth planetary gear P5, the fifth planet carrier PC5 inputs power, the power is branched into two paths, one path is branched to the fifth sun gear S5 and is output to the first planet carrier PC1 through the fifth connecting piece L5, the other path is branched to the fifth ring gear R5 and is output to the third connecting piece L3; in the first planetary gear P1, the first planet carrier PC1 inputs power, the power is branched into two paths, one path is branched to the first sun gear S1 and is output to the third sun gear S3 through the first connecting piece L1, the other path is branched to the first ring gear R1 and is output to the third connecting piece L3; in the third planetary gear P3, the third ring gear R3 is fixed with the second sun gear S2 through the second connecting piece L2 and is in a fixed state, the third sun gear S3 inputs power, the power is output to the third planet carrier PC3 through the third planet gear CA3 and is output to the third connecting piece L3 through the first clutch C1; in the second planetary gear P2, the second sun gear S2 is fixed, the third connecting piece L3 branches one path of power and outputs the power to the second ring gear R2 through the second planet gear CA2 and outputs the power to the fourth ring gear R4 through the fourth connecting piece L4; in the fourth planetary gear P4, the fourth ring gear R4 inputs one path of power, the power is output to the fourth planet carrier PC4 through the fourth planet gear CA4, the fourth sun gear S4 obtains one path of power branched by the third connecting piece L3, the power is output to the fourth planet carrier PC4 through the fourth planet gear CA4, and the two paths of power are merged and output to the output shaft OUT; on the third connecting piece L3, the fifth ring gear R5, the first ring gear R1 and the three paths of power on the third planet carrier PC3 are merged, one path of the branched power is output to the second ring gear R2, the second planet carrier PC2, the fourth connecting piece L4 and the fourth ring gear R4 in sequence, the other path of the branched power is output to the fourth sun gear S4, and finally the power is merged on the fourth planet carrier PC4 and is output to the output shaft OUT, the rotating direction is the same as that of the input shaft IN, and the fifth forward gear is implemented.

[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 carrier PC5 is fixedly connected with the input shaft IN, and the input shaft IN inputs power; in the fifth planetary gear P5, the fifth carrier PC5 inputs power, the power is branched into two paths, one path is branched to the fifth sun gear S5 and is output to the first carrier PC1 through the fifth connecting piece L5, and the other path is branched to the fifth ring gear R5 and is output to the third connecting piece L3; in the first planetary gear P1, the first sun gear S1 is fixed, the first carrier PC1 inputs power, and the power is sequentially output to the first ring gear R1 and the third connecting piece L3; in the second planetary gear P2, the second sun gear S2 is fixed, the third connecting piece L3 branches one path of power and outputs the power to the second ring gear R2, and outputs the power to the second carrier PC2 through the second planetary gear CA2 and outputs the power to the fourth ring gear R4 through the fourth connecting piece L4; in the fourth planetary gear P4, the fourth ring gear R4 inputs one path of power, outputs the power to the fourth carrier PC4 through the fourth planetary gear CA4, the fourth sun gear S4 obtains one path of power branched by the third connecting piece L3, outputs the power to the fourth carrier PC4 through the fourth planetary gear CA4, and the two paths of power are merged and output to the output shaft OUT; on the third connecting piece L3, the fifth ring gear R5 and the two paths of power on the first ring gear R1 are merged, one path of the branched power is sequentially output to the second ring gear R2, the second carrier PC2, the fourth connecting piece L4 and the fourth ring gear R4, and the other path of the branched power is output to the fourth sun gear S4, finally the power is merged after the fourth carrier PC4 and is output to the output shaft OUT, the rotating direction is the same as that of the input shaft IN, and the forward sixth gear is realized.

[0113] F7: the first brake B1 is engaged and the first clutch C1 is engaged at the same time, the first sun gear S1 is fixed, the third connecting piece L3 and the third planet carrier PC3 move synchronously, the fifth planet carrier PC5 is fixedly connected with the input shaft I N, and the input shaft I N inputs power; in the fifth planetary gear P5, the fifth planet carrier PC5 inputs power, the power is branched into two paths, one path is branched to the fifth sun gear S5 and is output to the first planet carrier PC1 through the fifth connecting piece L5, and the other path is branched to the fifth ring gear R5 and is output to the third connecting piece L3; in the first planetary gear P1, the first sun gear S1 is fixed, the first planet carrier PC1 inputs power, and the power is sequentially output to the first ring gear R1 and the third connecting piece L3; in the third planetary gear P3, the third sun gear S3 is fixedly connected with the first sun gear S1 through the first connecting piece L1 and is in a fixed state, the third planet carrier PC3 obtains the power branched from the third connecting piece L3 through the first clutch C1, and the power is output to the third ring gear R3 through the third planet gear CA3 and is output to the second sun gear S2 through the second connecting piece L2; in the second planetary gear P2, the second sun gear S2 inputs power, the power is output to the second planet carrier PC2 through the second planet gear CA2, the third connecting piece L3 branches the power and outputs the power to the second ring gear R2, the power is output to the second planet carrier PC2 through the second planet gear CA2, the second planet carrier PC2 is fixedly connected with the fourth ring gear R4 through the fourth connecting piece L4, the two paths of power are merged and output to the fourth ring gear R4; in the fourth planetary gear P4, the fourth ring gear R4 inputs power, the power is output to the fourth planet carrier PC4 through the fourth planet gear CA4, the fourth sun gear S4 obtains the power branched from the third connecting piece L3, the power is output to the fourth planet carrier PC4 through the fourth planet gear CA4, the two paths of power are merged and output to the output shaft OUT; on the third connecting piece L3, the fifth ring gear R5 and the two paths of power on the first ring gear R1 are merged, one path of power is branched to the third planet carrier PC3 and is sequentially output to the third ring gear R3, the second connecting piece L2, the second sun gear S2, the second planet carrier PC2, the fourth connecting piece L4 and the fourth ring gear R4, the second path of power is branched to the second ring gear R2 and is sequentially output to the second planet carrier PC2, the fourth connecting piece L4 and the fourth ring gear R4, the third path of branched power is output to the fourth sun gear S4, finally the three paths of branched power are merged after the fourth planet carrier PC4 and output power to the output shaft OUT, the rotating direction is the same as that of the input shaft I N, and gear seven is achieved.

[0114] F8: the fifth brake B5 is engaged at the same time with the second brake B2, the fifth sun gear S5 and the second sun gear S2 are fixed, the fifth carrier PC5 is fixedly connected with the input shaft I N, and the input shaft I N inputs power; in the fifth planetary gear set P5, the fifth sun gear S5 is fixed, the fifth carrier PC5 inputs power, and power is sequentially output to the fifth ring gear R5 and the third connecting piece L3; in the second planetary gear set P2, the second sun gear S2 is fixed, the third connecting piece L3 splits a road of power and outputs the road of power to the second ring gear R2, outputs the road of power to the second carrier PC2 through the second planetary gear CA2, and outputs the road of power to the fourth ring gear R4 through the fourth connecting piece L4; in the fourth planetary gear set P4, the fourth ring gear R4 inputs a road of power, outputs the road of power to the fourth carrier PC4 through the fourth planetary gear CA4, the fourth sun gear S4 obtains a road of power split by the third connecting piece L3, outputs the road of power to the fourth carrier PC4 through the fourth planetary gear CA4, and the two roads of power are merged and output to the output shaft OUT; on the third connecting piece L3, the fifth ring gear R5 outputs power to the third connecting piece L3, splits a road of power to the second ring gear R2, and sequentially outputs the road of power to the second carrier PC2, the fourth connecting piece L4 and the fourth ring gear R4; another road of split power is output to the fourth sun gear S4, finally the two roads of power are merged after the fourth carrier PC4 and output power to the output shaft OUT, the rotation direction is the same as that of the input shaft I N, and the eighth forward gear is realized.

[0115] F9: the fifth brake B5 is engaged at the same time with the third brake B3, the fifth sun gear S5 and the third planet carrier PC3 are fixed, the fifth planet carrier PC5 is fixedly connected with the input shaft I N, the input shaft I N inputs power; in the fifth planetary gear P5, the fifth sun gear S5 is fixed, the fifth planet carrier PC5 inputs power, and the power is sequentially output to the fifth ring gear R5 and the third connecting piece L3; in the first planetary gear P1, the first planet carrier PC1 is connected with the fifth sun gear S5 through the fifth connecting piece L5 and is in a fixed state synchronously, the first ring gear R1 is fixedly connected with the fifth ring gear R5 through the third connecting piece L3, the first ring gear R1 inputs power, 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 piece L1; in the third planetary gear P3, the third planet carrier PC3 is fixed, the third sun gear S3 inputs power, the power 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 piece L2; in the second planetary gear P2, the second sun gear S2 inputs power, the power is output to the second planet carrier PC2 through the second planetary gear CA2, the third connecting piece L3 branches a road of power and outputs the road of power to the second ring gear R2 through the second planetary gear CA2 and to the second planet carrier PC2, the second planet carrier PC2 is fixedly connected with the fourth ring gear R4 through the fourth connecting piece L4, two roads of power are merged and output to the fourth ring gear R4; in the fourth planetary gear P4, the fourth ring gear R4 inputs a road of power, the power is output to the fourth planet carrier PC4 through the fourth planetary gear CA4, the fourth sun gear S4 obtains a road of power branched by the third connecting piece L3, the power is output to the fourth planet carrier PC4 through the fourth planetary gear CA4, two roads of power are merged and output to the output shaft OUT; on the third connecting piece L3, the fifth ring gear R5 outputs power to the third connecting piece L3, branches a road of power to the first ring gear R1, and sequentially outputs to the first sun gear S1, the first connecting piece L1, the third sun gear S3, the third ring gear R3, the second connecting piece L2, the second sun gear S2, the second planet carrier PC2, the fourth connecting piece L4 and the fourth ring gear R4, branches a second road of power to the second ring gear R2 and sequentially outputs to the second planet carrier PC2, the fourth connecting piece L4 and the fourth ring gear R4, a third road of branched power is output to the fourth sun gear S4, finally the three roads of branched power are merged after the fourth planet carrier PC4 and output power to the output shaft OUT, the rotating direction is same as that of the input shaft I N, and ninth forward gear is achieved.

[0116] F10: the fifth brake B5 is engaged and the first clutch Cl is engaged at the same time, the fifth sun gear S5 is fixed, the third connecting component L3 and the third planet carrier PC3 move synchronously, the fifth planet carrier PC5 is fixedly connected with the input shaft IN, the input shaft IN inputs power; in the fifth planetary gear set P5, the fifth sun gear S5 is fixed, the fifth planet carrier PC5 inputs power, and power is sequentially output to the fifth ring gear R5 and the third connecting component L3; in the first planetary gear set Pl, the first planet carrier PC1 is connected with the fifth sun gear S5 through the fifth connecting component L5 and is in a fixed state synchronously, the first ring gear R1 is fixedly connected with the fifth ring gear R5 through the third connecting component L3, the first ring gear R1 inputs power, 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 component L1; in the third planetary gear set P3, the third sun gear S3 inputs power, part of the power is output to the third ring gear R3 through the third planetary gear CA3, the third planet carrier PC3 obtains part of the power branched by the third connecting component L3 through the first clutch Cl, and outputs the power to the third ring gear R3 through the third planetary gear CA3, the two routes of power are output to the second sun gear S2 through the second connecting component L2 after converging at the third ring gear R3; in the second planetary gear set P2, the second sun gear S2 inputs power, outputs the power to the second planet carrier PC2 through the second planetary gear CA2, the third connecting component L3 branches a route of power and outputs the power to the second ring gear R2 through the second planetary gear CA2, the second planet carrier PC2 is fixedly connected with the fourth ring gear R4 through the fourth connecting component L4, and the two routes of power are output to the fourth ring gear R4 after converging; in the fourth planetary gear set P4, the fourth ring gear R4 inputs power, outputs the power to the fourth planet carrier PC4 through the fourth planetary gear CA4, the fourth sun gear S4 obtains a route of power branched by the third connecting component L3, outputs the power to the fourth planet carrier PC4 through the fourth planetary gear CA4, and the two routes of power are output to the output shaft OUT after converging; on the third connecting component L3, the fifth ring gear R5 outputs power to the third connecting component L3, branches a route of power to the first ring gear R1, and sequentially outputs the power to the first sun gear S1, the first connecting component L1, the third sun gear S3, the third planet carrier PC3, the third ring gear R3, the second connecting component L2, the second sun gear S2, the second planet carrier PC2, the fourth connecting component L4 and the fourth ring gear R4, branches a second route of power to the third planet carrier PC3 and sequentially outputs the power to the third ring gear R3, the second connecting component L2, the second sun gear S2, the second planet carrier PC2, the fourth connecting component L4 and the fourth ring gear R4, branches a third route of power to the second ring gear R2 and sequentially outputs the power to the second planet carrier PC2, the fourth connecting component L4 and the fourth ring gear R4, a fourth route of branched power is output to the fourth sun gear S4, finally, the four routes of branched power are output to the output shaft OUT after converging at the fourth planet carrier PC4, the rotating direction is the same as that of the input shaft IN, and gear ten is achieved.

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

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

[0119] As shown by the gear shifting logic of each gear in Table 2, each gear is controlled by operating two elements, which can reduce the friction work and heat loss of the friction plate, and improve the reliability of the friction plate.

[0120] Optionally, the ratio of the first gear ring R1 tooth number to the first sun gear S1 tooth number is 3. The ratio of the second gear ring R2 tooth number to the second sun gear S2 tooth number is 5. The ratio of the third gear ring R3 tooth number to the third sun gear S3 tooth number is 4. The ratio of the fourth gear ring R4 tooth number to the fourth sun gear S4 tooth number is 3. The ratio of the fifth gear ring R5 tooth number to the fifth sun gear S5 tooth number is 3.

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

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

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

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

[0125] The five planetary gear sets and the clutch are arranged side by side from left to right, and the five sun gears, the clutch, the input shaft IN, and the output shaft OUT are coaxially arranged.

[0126] The power control mechanism of the planetary gear set combined clutch for a vehicle transmission system in the present application includes five planetary gear sets, five brakes, and a clutch. Each planetary gear set is a single-planet simple planetary gear set, and the highest gear ratio can achieve ten forward gears and one reverse gear. The gear ratio range is large, and the gear ratio is divided into three working intervals, i.e., high, medium, and low. This can make the engine adapt to different working conditions, more operating in the economic working area, and improve the economy of the whole machine. The five brakes and the clutch are all friction control structures, and the gear ratio is controlled by two elements. This can reduce the 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 the power control mechanism of the planetary gear set combined clutch of any one of the first embodiment and the second embodiment.

[0129] In summary, the vehicle transmission system of the present disclosure has the advantages of simple structure, large gear ratio range, strong torque transmission capacity, and strong gear extension capability. Compared with existing transmission systems, it can better adapt to the transmission needs of vehicles.

[0130] The above disclosure is only some embodiments of the present application. Those skilled in the art can make several modifications and improvements without departing from the inventive concept, and these all belong to the protection scope of the present application.

Claims

1. A power control mechanism for a planetary array combination clutch, characterized by, The first clutch (C1), the third planetary gear set (P3), the third brake (B3) and the third connecting member (L3) are included. The first clutch (C1) includes a first clutch driving member (C11) and a first clutch driven member (C12). The third planetary gear set (P3) includes a third sun gear (S3), a third planet carrier (PC3), a third planet gear (CA3) and a third ring gear (R3). The first clutch driving member (C11) is fixedly connected with the third connecting member (L3). The first clutch driven member (C12) is fixedly connected with the third planet carrier (PC3). The third sun gear (S3) of the third planetary gear set (P3) is movably mounted on the third connecting member (L3). The third planet carrier (PC3) is connected with the third brake (B3).

2. The power control mechanism of the planetary gear set combined clutch according to claim 1, wherein, when the first clutch (C1) and the third brake (B3) are both in the disengaged state, one-way power is transmitted through the third connecting member (L3) to realize single-way power single-path power transmission; when the first clutch (C1) is engaged alone, one-way power is transmitted through the third connecting member (L3) and the other way power is transmitted through the third sun gear (S3), the two-way power is divided and then combined to form new two-way power, which is output from the third connecting member (L3) and the third ring gear (R3) respectively, realizing double-way power mixed-flow double-path power transmission; when the third brake (B3) is engaged alone, one-way power is transmitted through the third connecting member (L3) and the other way power is transmitted through the third sun gear (S3) and the third ring gear (R3), realizing double-way power non-mixed-flow double-path power transmission; when the first clutch (C1) and the third brake (B3) are both in the engaged state, one-way power is transmitted through the third sun gear (S3) and the third ring gear (R3) is output, realizing single-way power single-path power transmission.

3. A power control mechanism for a planetary array combined clutch according to claim 2, characterized by The third sun gear (S3) and the third ring gear (R3) can be used interchangeably.

4. A power control mechanism for a planetary array combined clutch as defined in claim 1, wherein The first planetary gear set (PZ1), the second planetary gear set (PZ2), the input shaft (IN) and the output shaft (OUT) are further included. 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 with the first planetary gear set (PZ1). The output shaft (OUT) is connected with the second planetary gear set (PZ2).

5. A power control mechanism for a planetary array combined clutch as defined in claim 4, wherein The first planetary gear set (PZ1) includes a fifth planetary gear set (P5) and a first planetary gear set (P1). The input shaft (IN) is connected with the fifth planetary gear set (P5), and the first planetary gear set (P1) is connected with the third planetary gear set (P3).

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

7. A power control mechanism for a planetary array combined clutch as defined in claim 4, wherein The second planetary gear set group (PZ2) comprises a second planetary gear set (P2) and a fourth planetary gear set (P4); The second planetary gear set (P2) is connected with the third planetary gear set (P3); the fourth planetary gear set (P4) is connected with the output shaft (OUT).

8. A power control mechanism for a planetary array combined clutch as defined in claim 7, wherein The second planetary gear set (P2) comprises a second sun gear (S2), a second carrier (PC2), second planet gears (CA2) and a second ring gear (R2); the second sun gear (S2) is movably mounted on the third connecting member (L3); the second sun gear (S2) is fixedly connected with the third ring gear (R3) through a second connecting member (L2); the second carrier (PC2) is fixedly connected with the fourth ring gear (R4) through a fourth connecting member (L4); the second ring gear (R2) is fixedly connected with the third connecting member (L3); the second sun gear (S2) is connected with a second brake (B2); The fourth planetary gear set (P4) comprises a fourth sun gear (S4), a fourth carrier (PC4), fourth planet gears (CA4) and a fourth ring gear (R4); the fourth sun gear (S4) is fixedly connected with the third connecting member (L3); the fourth ring gear (R4) is connected with a fourth brake (B4); the fourth carrier (PC4) is fixedly connected with the output shaft (OUT).

9. A power control mechanism for a planetary array combined clutch as defined in claim 4 wherein, The number of forward gears is calculated according to the formula n1×n2+n1+n2+(n1-1)+(n2-1); Wherein, n1 is the number of planetary gear sets of the first planetary gear set group (PZ1), and n2 is the number of planetary gear sets of the second planetary gear set group (PZ2).

10. A vehicle driveline system characterised in that, A power control mechanism comprising the planetary gear set combination clutch of any one of claims 1-9.

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