Agricultural machinery power high-low gear transmission system

Abstract

The utility model discloses an agricultural machinery power high-low gear transmission system, which belongs to the technical field, and comprises a shaft group, an oil pump OP and a clutch group, the shaft group comprises an input shaft S1, an output shaft S3 and a power take-off shaft S4 which are coaxially arranged, the power take-off shaft S4 is respectively and rotatably connected with the input shaft S1 and the output shaft S3, the oil pump OP is connected with the clutch group, the oil pump OP can be driven by the input shaft S1, and the clutch group is connected with the output shaft S3. Power of the input shaft S1 can be transmitted to the output shaft S3 or the power take-off shaft S4 through the clutch set. The problem that in the prior art, power gear shifting operation is complex is solved, the operation efficiency of agricultural machinery is greatly improved, and the operation threshold is lowered.

Description

Technical Field

[0001] The utility model belongs to the technical field of transmissions, and in particular relates to a high- and low-speed transmission system for agricultural machinery power. Background Art

[0002] At present, tractors or similar agricultural power machinery generally use a dry main clutch with a mechanical separation structure. When changing gears, changing driving direction, or switching the power take-off mechanism, it is necessary to step on the clutch pedal to cut off the power transmitted by the engine, and then use the mechanical gear lever to select the desired gear or realize the engagement and disengagement of the power take-off mechanism. When switching the driving direction, not only do you need to step on the clutch pedal, you also need to stop the car before switching forward / reverse. When switching directions, the power take-off mechanism needs to disengage the power output, which also requires stepping on the clutch pedal to achieve. The entire operation process is cumbersome and laborious. Especially when working on smaller plots of land, it is necessary to change the driving direction frequently, which places high demands on the driver's work intensity. At the same time, since the driving direction needs to be stopped before the operation can be performed, the working efficiency is greatly reduced.

[0003] In response to the above situation, in recent years, the domestic agricultural machinery industry has been vigorously promoting the development of power reversing technology. Patent No. CN201922295987.5 is a new type of three-axis tractor power high and low gear and power reversing device, which realizes power high and low gear and reversing functions through different combinations of four sets of clutches. However, in the existing technology, since the power take-off mechanism is also frequently switched during use, and the agricultural machinery chassis has extremely high requirements for the structural layout of the transmission system, a highly integrated product is needed to simultaneously meet the functional requirements of power high and low gear, reversing, and automatic switching of power take-off. At the same time, the high integration meets the layout requirements and promotes the progress of agricultural machinery modernization technology. Utility Model Content

[0004] The purpose of this utility model is to provide a high-speed transmission system for agricultural machinery with compact structure, low manufacturing cost and high working efficiency.

[0005] The technical solutions adopted by the present invention to achieve the above-mentioned purpose are:

[0006] A high- and low-speed transmission system for agricultural machinery includes a shaft assembly, an oil pump OP, and a clutch assembly. The shaft assembly includes a coaxially arranged input shaft S1, an output shaft S3, and a power take-off shaft S4. The power take-off shaft S4 is rotatably connected to the input shaft S1 and the output shaft S3, respectively. The oil pump OP is connected to the clutch assembly and can be driven by the input shaft S1. The power of the input shaft S1 can be transmitted to the output shaft S3 or the power take-off shaft S4 through the clutch assembly. The input shaft S1, output shaft S3, and power take-off shaft S4 are coaxially mounted and rotate independently. The operation of the clutches included in the clutch assembly enables power transmission from the input shaft S1 to the output shaft S3 and from the input shaft S1 to the power take-off shaft S4, thereby achieving power switching between different gears.

[0007] Preferably, the shaft group further includes an intermediate shaft S2 which is transmission-connected to the side of the input shaft S1 , the intermediate shaft S2 is rotationally connected to the gear G1 , and the gear G1 is transmission-connected to the output shaft S3 .

[0008] Preferably, the shaft group further includes an intermediate shaft S5 which is transmission-connected to the side of the input shaft S1 , the intermediate shaft S5 is rotationally connected to a gear G2 , and the gear G2 is transmission-connected to the output shaft S3 .

[0009] Preferably, the clutch group includes a clutch outer hub H1, a clutch inner hub H2, a return spring group SP1, an active friction plate group CL1, a driven friction plate group CL2 and a piston P1. The clutch outer hub H1 is connected to the input shaft S1, and the piston P1 is arranged in the inner cavity of the clutch outer hub H1. One side of the return spring group SP1 is in contact with the piston P1, and the other side of the return spring group SP1 is fixed to the clutch outer hub H1. The clutch inner hub H2 is connected to the power take-off shaft S4, the active friction plate group CL1 is connected to the clutch outer hub H1, and the driven friction plate group CL2 is connected to the clutch inner hub H2. When the oil pressure established by the oil pump OP is introduced into the cavity of the piston P1 and the clutch outer hub H1 through the control of the solenoid valve, the piston P1 will push the active friction plate group CL1 and the driven friction plate group CL2 to combine, thereby realizing the transmission of power from the input shaft S1 to the power take-off shaft S4; when the pressure oil in the piston P1 is cut off through the solenoid valve, the return spring group SP1 will push the piston P1 back, so that the active friction plate group CL1 and the driven friction plate group CL2 are separated, thereby cutting off the power to the power take-off shaft S4.

[0010] Preferably, the clutch group also includes a clutch outer hub H4, a clutch inner hub H3, a return spring group SP2, an active friction plate group CL4, a driven friction plate group CL3 and a piston P2. The clutch outer hub H4 is connected to the output shaft S3, and the piston P2 is arranged in the inner cavity of the clutch outer hub H4. One side of the return spring group SP2 is in contact with the piston P2, and the other side of the return spring group SP2 is fixed to the clutch outer hub H4. The clutch inner hub H3 is connected to the clutch outer hub H1, the active friction plate group CL4 is connected to the clutch inner hub H3, and the driven friction plate group CL3 is connected to the clutch outer hub H4. When the oil pressure established by the oil pump OP is introduced into the cavity of the piston P2 and the clutch outer hub H4 through the control of the solenoid valve, the piston P2 will push the driven friction plate group CL3 and the active friction plate group CL4 to combine, realizing the fixed synchronous operation of the output shaft S3 and the input shaft S1, and realizing the same-direction output of the forward high gear; when the pressure oil in the piston P2 is cut off by the solenoid valve, the return spring group SP2 will push the piston P2 back, so that the driven friction plate group CL3 and the active friction plate group CL4 are separated, thereby cutting off the power output of the forward high gear.

[0011] Preferably, the clutch group also includes a clutch outer hub H7, a clutch inner hub H8, a return spring group SP4, an active friction plate group CL7, a driven friction plate group CL8 and a piston P4. The clutch outer hub H7 is connected to the intermediate shaft S5, and the piston P4 is arranged in the inner cavity of the clutch outer hub H7. One side of the return spring group SP4 is in contact with the piston P4, and the other side of the return spring group SP4 is fixed on the clutch outer hub H7. The clutch inner hub H8 is connected to the gear G2, the active friction plate group CL7 is connected to the clutch outer hub H7, and the driven friction plate group CL8 is connected to the clutch inner hub H8. When the oil pressure established by the oil pump OP is introduced into the cavity of the piston P4 and the clutch outer hub H7 through the control of the solenoid valve, the piston P4 will push the active friction plate group CL7 and the driven friction plate group CL8 to combine, so that the intermediate shaft S5 and the gear G2 are fixed and run together, thereby realizing that the power of the input shaft S1 is transmitted to the gear G2 through the intermediate shaft S5, and then to the output shaft S3, realizing the same-direction output of the forward low gear; when the pressure oil in the piston P4 is cut off by the solenoid valve, the return spring group SP4 will push the piston P4 back, so that the active friction plate group CL7 and the driven friction plate group CL8 are separated, thereby cutting off the power output of the forward low gear.

[0012] Preferably, the clutch group also includes a clutch outer hub H6, a clutch inner hub H5, a return spring group SP3, an active friction plate group CL5, a driven friction plate group CL6 and a piston P3. The clutch outer hub H6 is connected to the intermediate shaft S2, and the piston P3 is arranged in the inner cavity of the clutch outer hub H6. One side of the return spring group SP3 is in contact with the piston P3, and the other side of the return spring group SP3 is fixed to the clutch outer hub H6. The clutch inner hub H5 is connected to the gear G1, the active friction plate group CL5 is connected to the clutch outer hub H6, and the driven friction plate group CL6 is connected to the clutch inner hub H5. When the solenoid valve controls the oil pressure generated by the oil pump OP and introduced into the cavity of the piston P3 and the clutch outer hub H6, the piston P3 pushes the active friction plate group CL5 and the driven friction plate group CL6 to engage, achieving a fixed and coordinated rotation of the intermediate shaft S2 and the gear G1, thereby achieving reverse power output between the output shaft S3 and the input shaft S1, and realizing reverse gear output. When the pressure oil in the piston P3 is cut off by the solenoid valve, the return spring group SP3 pushes the piston P3 back to its original position, causing the active friction plate group CL5 and the driven friction plate group CL6 to separate, thereby cutting off the power output of the reverse gear.

[0013] The above implementation plan can meet the needs of agricultural machinery in different horsepower ranges for automatic high and low gear shifting, power reversing and electronically controlled automatic power take-off, improve the operating efficiency of agricultural machinery, and reduce energy consumption during operation. The entire plan realizes power output control by controlling oil pressure, is easy to operate, reduces labor intensity, and provides a technical basis for unmanned operation, reducing the cost of personnel deployment.

[0014] Preferably, a sprocket W1 is fixed to the driving end of the oil pump OP, a sprocket W2 is fixed to the intermediate shaft S2, and a chain CH1 is connected to the sprocket W1 and the sprocket W2. The chain CH1 is meshed with the sprockets W1 and W2 respectively, so that the oil pump OP is driven by the intermediate shaft S2. When the input shaft S1 rotates continuously, the power can always be transmitted to the oil pump OP through the intermediate shaft S2, the sprocket W2, the chain CH1 and the sprocket W1. That is, the oil pressure of the clutch group can be controlled by adjusting the power of the input shaft S1, which is convenient for

[0015] Preferably, the power take-off shaft S4 is arranged to extend through the output shaft S3. The input shaft S1 includes an assembly end D11. The power take-off shaft S4 has a plug-in end D41 proximate to the assembly end D11. The plug-in end D41 and the assembly end D11 are rotatably connected via a bearing B2. The clutch inner hub H2 and the clutch outer hub H1 are positioned adjacent to and peripherally located around the bearing B2. The power take-off shaft S4 coaxially extends through the output shaft S3, reducing the overall axial length of the shaft assembly. This reduces the size of the housing SH and manufacturing costs. Furthermore, it allows the clutch inner hub H2 and the clutch outer hub H1 to be relatively concentrated around one end of the output shaft S1, thereby shortening the speed at which the clutch inner hub H2 and the clutch outer hub H1 engage, thereby increasing the speed at which power is transmitted from the input shaft S1 to the power take-off shaft S4 and improving the power switching efficiency of the agricultural machinery.

[0016] The power take-off shaft S4 is coaxially threaded within the output shaft S3. The two shafts correct each other's rotational coaxiality during rotation, minimizing the possibility of lateral interference and slipping of the output shaft S3 when power is transmitted from gears G1 and G2 to the output shaft S3. This helps reduce power loss from the output shaft S# and improves power transmission efficiency. The coaxiality correction of the output shaft S3 within the power take-off shaft S4 maintains parallelism between the active friction plate group CL4 and the driven friction plate group CL3 during engagement, thereby improving the tightness of the engagement and ensuring high-speed power output efficiency. It also maintains parallelism between the active friction plate group CL4 and the driven friction plate group CL3 during disengagement, improving the smoothness of the power cutoff process and enhancing shifting safety. It also reduces the possibility of excessive friction due to uneven contact between the active friction plate group CL4 and the driven friction plate group CL3, reducing unnecessary wear of the friction plate groups and lowering maintenance costs.

[0017] Preferably, the output shaft S3 has a mating end D31, which is positioned proximate to the assembly end D11. The clutch inner hub H4 is disposed on the periphery of the output shaft S3 proximate to the mating end D31, and the clutch inner hub H3 is connected to the inner side of the clutch inner hub H4. The driving friction plate group CL4 is splined to the clutch inner hub H3, and the driven friction plate group CL3 is splined to the clutch outer hub H4. Because the output shaft S3 is positioned proximate to the assembly end D11 of the input shaft S1, the axial spacing between the clutch inner hub H3 and the clutch inner hub H4 along the output shaft S3 is shortened, thereby increasing the speed at which the driven friction plate group CL3 and the driving friction plate group CL4 engage. This improves the efficiency of the agricultural machine's shift from other gears to the higher forward gear, reduces shifting time, shortens the machine's stagnation during shifting, and improves its operational efficiency.

[0018] The utility model realizes automatic shifting control of forward high and low gears by separately controlling the piston pressure of the clutch, and realizes automatic forward and reverse control by separately controlling the piston oil pressure of the forward gear clutch and the reverse gear clutch; it solves the complex problems of the prior art in operating the clutch pedal when switching between high and low gears, switching the driving direction, and operating the power take-off mechanism, not only realizes automatic control to improve working efficiency and reduce labor intensity, but also makes the structural scheme of the entire transmission system compact and reduces system cost through optimized structural design. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 This is a schematic diagram of the overall structure of a high- and low-speed transmission system for agricultural machinery power;

[0020] Figure 2 for Figure 1 A magnified schematic diagram of area A in the middle;

[0021] Figure 3 for Figure 1 The middle B area is intended to be enlarged;

[0022] Figure 4 for Figure 1 Enlarged schematic diagram of area C in the middle;

[0023] Figure 5 for Figure 1 Enlarged schematic diagram of area D in the middle. DETAILED DESCRIPTION

[0024] The technical solution of the present invention is further described in detail below with reference to the specific embodiments and accompanying drawings:

[0025] Obviously, the embodiments described are only some of the embodiments of the present invention, not all of them. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0026] See attached Figure 1 -Attached Figure 5 A high- and low-speed transmission system for agricultural machinery power includes: a housing SH, a shaft group, an oil pump OP and a clutch group. The shaft group includes a coaxially arranged input shaft S1, an output shaft S3 and a power take-off shaft S4. The power take-off shaft S4 is rotationally connected to the input shaft S1 and the output shaft S3 respectively. The oil pump OP is connected to the clutch group. The oil pump OP can be driven by the input shaft S1. The power of the input shaft S1 can be transmitted to the output shaft S3 or the power take-off shaft S4 through the clutch group.

[0027] The input shaft S1 is rotatably connected to the housing SH through the bearing B1;

[0028] The output shaft S3 is rotatably connected to the housing SH via the bearing B4;

[0029] The power take-off shaft S4 is rotatably connected to the output shaft S3 via the bearing B3;

[0030] The power take-off shaft S4 is connected to the housing SH through the bearing B2;

[0031] The input shaft S1, output shaft S3 and power take-off shaft S4 can rotate independently of each other;

[0032] The outer shell of the oil pump OP is fixed to the housing SH.

[0033] The clutch pack is equipped with a solenoid valve in the oil circuit connected to the oil pump OP. By controlling the solenoid valve, the flow path of the oil in the clutch pack can be controlled.

[0034] The input shaft S1, output shaft S3, and power take-off shaft S4 are coaxially mounted and rotate independently. Through the action of each clutch included in the clutch group, power is transferred from the input shaft S1 to the output shaft S3 and from the input shaft S1 to the power take-off shaft S4, thereby realizing power switching between different gears.

[0035] The shaft group also includes an intermediate shaft S2 that is transmission-connected to the side of the input shaft S1. The intermediate shaft S2 is rotationally connected to the gear G1, and the gear G1 is transmission-connected to the output shaft S3.

[0036] The first gear is coaxially mounted on the intermediate shaft S2, and the input gear is coaxially mounted on the input shaft S1. The intermediate gear and the input gear are constantly meshed.

[0037] Intermediate shaft S2 is rotatably connected to housing SH via bearings B5 and B6 at both ends. Gear G1 is coaxially sleeved on intermediate shaft S2 via bearing B7. Output shaft S3 is coaxially mounted with the output gear. The shaft assembly also includes an idler gear S6, which is rotatably connected to housing SH via an idler gear bearing. Idler gear S6 is in constant mesh with the output gear and gear G1, respectively.

[0038] The shaft group also includes an intermediate shaft S5 that is transmission-connected to the side of the input shaft S1. The intermediate shaft S5 is rotationally connected to the gear G2, and the gear G2 is transmission-connected to the output shaft S3.

[0039] The intermediate shaft S5 is coaxially mounted with a second gear which is constantly meshed with the input gear;

[0040] The intermediate shaft S5 is rotationally connected to the housing SH through bearings B8 and B9. The gear G2 is coaxially sleeved on the intermediate shaft S5 through bearing B10. The gear G2 is constantly meshed with the output gear on the output shaft S3.

[0041] The intermediate shaft S2 and the intermediate shaft S5 are respectively located on both sides of the input shaft S1 , and the axes of the intermediate shaft S2 , the intermediate shaft S5 and the input shaft S1 are located in the same plane.

[0042] The clutch group includes a clutch outer hub H1, a clutch inner hub H2, a return spring group SP1, an active friction plate group CL1, a driven friction plate group CL2 and a piston P1. The clutch outer hub H1 is connected to the input shaft S1, and the piston P1 is arranged in the inner cavity of the clutch outer hub H1. One side of the return spring group SP1 is in contact with the piston P1, and the other side of the return spring group SP1 is fixed to the clutch outer hub H1. The clutch inner hub H2 is connected to the power take-off shaft S4, the active friction plate group CL1 is connected to the clutch outer hub H1, and the driven friction plate group CL2 is connected to the clutch inner hub H2.

[0043] When the oil pressure generated by the oil pump OP is introduced into the cavity of the piston P1 and the clutch outer hub H1 through the control of the solenoid valve, the piston P1 will push the active friction plate group CL1 and the driven friction plate group CL2 to engage, realizing the power transmission from the input shaft S1 to the power take-off shaft S4;

[0044] When the pressure oil in the piston P1 is cut off by the solenoid valve, the return spring group SP1 will push the piston P1 back, so that the active friction plate group CL1 and the driven friction plate group CL2 are separated, thereby cutting off the power of the power take-off shaft S4.

[0045] The clutch group also includes a clutch outer hub H4, a clutch inner hub H3, a return spring group SP2, an active friction plate group CL4, a driven friction plate group CL3 and a piston P2. The clutch outer hub H4 is connected to the output shaft S3, and the piston P2 is arranged in the inner cavity of the clutch outer hub H4. One side of the return spring group SP2 is in contact with the piston P2, and the other side of the return spring group SP2 is fixed to the clutch outer hub H4. The clutch inner hub H3 is connected to the clutch outer hub H1, the active friction plate group CL4 is connected to the clutch inner hub H3, and the driven friction plate group CL3 is connected to the clutch outer hub H4.

[0046] When the oil pressure generated by the oil pump OP is introduced into the cavity of the piston P2 and the clutch outer hub H4 through the control of the solenoid valve, the piston P2 will push the driven friction plate group CL3 and the active friction plate group CL4 to engage, realizing the fixed synchronous operation of the output shaft S3 and the input shaft S1, and achieving the same-direction output of the forward high gear;

[0047] When the pressure oil in the piston P2 is cut off by the solenoid valve, the return spring group SP2 will push the piston P2 back, so that the driven friction plate group CL3 and the active friction plate group CL4 are separated, thereby cutting off the power output of the forward high gear.

[0048] The clutch group also includes a clutch outer hub H7, a clutch inner hub H8, a return spring group SP4, an active friction plate group CL7, a driven friction plate group CL8 and a piston P4. The clutch outer hub H7 is connected to the intermediate shaft S5, and the piston P4 is arranged in the inner cavity of the clutch outer hub H7. One side of the return spring group SP4 is in contact with the piston P4, and the other side of the return spring group SP4 is fixed to the clutch outer hub H7. The clutch inner hub H8 is connected to the gear G2, the active friction plate group CL7 is connected to the clutch outer hub H7, and the driven friction plate group CL8 is connected to the clutch inner hub H8.

[0049] When the oil pressure generated by the oil pump OP is introduced into the cavity of the piston P4 and the clutch outer hub H7 through the control of the solenoid valve, the piston P4 will push the active friction plate group CL7 and the driven friction plate group CL8 to engage, so that the intermediate shaft S5 and the gear G2 are fixed and run together, thereby realizing that the power of the input shaft S1 is transmitted to the gear G2 through the intermediate shaft S5 and then to the output shaft S3, realizing the same-direction output in the forward low gear;

[0050] When the pressure oil in the piston P4 is cut off by the solenoid valve, the return spring group SP4 will push the piston P4 back, so that the active friction plate group CL7 and the driven friction plate group CL8 are separated, thereby cutting off the power output of the forward low gear.

[0051] The clutch group also includes a clutch outer hub H6, a clutch inner hub H5, a return spring group SP3, an active friction plate group CL5, a driven friction plate group CL6 and a piston P3. The clutch outer hub H6 is connected to the intermediate shaft S2, and the piston P3 is arranged in the inner cavity of the clutch outer hub H6. One side of the return spring group SP3 is in contact with the piston P3, and the other side of the return spring group SP3 is fixed to the clutch outer hub H6. The clutch inner hub H5 is connected to the gear G1, the active friction plate group CL5 is connected to the clutch outer hub H6, and the driven friction plate group CL6 is connected to the clutch inner hub H5. When the solenoid valve controls the oil pressure generated by the oil pump OP and introduced into the cavity of the piston P3 and the clutch outer hub H6, the piston P3 pushes the active friction plate group CL5 and the driven friction plate group CL6 to engage, achieving a fixed and coordinated rotation of the intermediate shaft S2 and the gear G1, thereby achieving reverse power output between the output shaft S3 and the input shaft S1, and realizing reverse gear output. When the pressure oil in the piston P3 is cut off by the solenoid valve, the return spring group SP3 pushes the piston P3 back to its original position, causing the active friction plate group CL5 and the driven friction plate group CL6 to separate, thereby cutting off the power output of the reverse gear.

[0052] The above implementation plan can meet the needs of agricultural machinery in different horsepower ranges for automatic high and low gear shifting, power reversing and electronically controlled automatic power take-off, improve the operating efficiency of agricultural machinery, and reduce energy consumption during operation. The entire plan realizes power output control by controlling oil pressure, is easy to operate, reduces labor intensity, and provides a technical basis for unmanned operation, reducing the cost of personnel deployment.

[0053] The drive end of the oil pump OP is fixed with a sprocket W1, and the intermediate shaft S2 is fixed with a sprocket W2. The sprocket W1 and the sprocket W2 are connected by a chain CH1. The chain CH1 is meshed with the sprockets W1 and W2 respectively, and the oil pump OP is driven by the intermediate shaft S2. When the input shaft S1 rotates continuously, the power can always be transmitted to the oil pump OP through the intermediate shaft S2, the sprocket W2, the chain CH1 and the sprocket W1. That is, by adjusting the power of the input shaft S1, the oil pressure of the clutch group can be controlled, which is convenient for

[0054] The power take-off shaft S4 runs through the output shaft S3. The input shaft S1 includes an assembly end D11. The power take-off shaft S4 has a plug-in end D41 adjacent to the assembly end D11. The plug-in end D41 and the assembly end D11 are rotatably connected via a bearing B2. The clutch inner hub H2 and the clutch outer hub H1 are positioned adjacent to and peripherally around bearing B2. The power take-off shaft S4 coaxially passes through the output shaft S3, reducing the overall axial length of the shaft assembly. This reduces the size of the housing SH and manufacturing costs. It also allows the clutch inner hub H2 and the clutch outer hub H1 to be relatively concentrated around one end of the output shaft S1, shortening the speed at which the clutch inner hub H2 and the clutch outer hub H1 engage. This increases the speed at which power is transmitted from the input shaft S1 to the power take-off shaft S4, improving the power switching efficiency of the agricultural machinery.

[0055] The power take-off shaft S4 is coaxially threaded within the output shaft S3. The two shafts correct each other's rotational coaxiality during rotation, minimizing the possibility of lateral interference and slipping of the output shaft S3 when power is transmitted from gears G1 and G2 to the output shaft S3. This helps reduce power loss from the output shaft S# and improves power transmission efficiency. The coaxiality correction of the output shaft S3 within the power take-off shaft S4 maintains parallelism between the active friction plate group CL4 and the driven friction plate group CL3 during engagement, thereby improving the tightness of the engagement and ensuring high-speed power output efficiency. It also maintains parallelism between the active friction plate group CL4 and the driven friction plate group CL3 during disengagement, improving the smoothness of the power cutoff process and enhancing shifting safety. It also reduces the possibility of excessive friction due to uneven contact between the active friction plate group CL4 and the driven friction plate group CL3, reducing unnecessary wear of the friction plate groups and lowering maintenance costs.

[0056] The output shaft S3 has a mating end D31, which is positioned adjacent to the assembly end D11. The clutch inner hub H4 is positioned around the output shaft S3 near the mating end D31, and the clutch inner hub H3 is connected to the inner side of the clutch inner hub H4. The driving friction plate group CL4 is splined to the clutch inner hub H3, while the driven friction plate group CL3 is splined to the clutch outer hub H4. Because the output shaft S3 is positioned adjacent to the assembly end D11 of the input shaft S1, the axial spacing between the clutch inner hub H3 and the clutch inner hub H4 along the output shaft S3 is shortened, increasing the speed at which the driven friction plate group CL3 and the driving friction plate group CL4 engage. This improves the efficiency of the agricultural machine's shift from other gears to the higher forward gear, reduces shifting time, shortens the machine's downtime during shifting, and enhances its operational efficiency.

[0057] It will be apparent to those skilled in the art that the present invention is not limited to the details of the exemplary embodiments described above and that the present invention can be implemented in other specific forms without departing from the spirit or essential characteristics of the present invention. Therefore, the embodiments should be considered in all respects as illustrative and non-restrictive, and the scope of the present invention is defined by the appended claims, not the foregoing description, and all variations within the meaning and range of equivalents of the claims are intended to be encompassed within the present invention. Any reference sign in a claim should not be construed as limiting the claim to which it relates.

Claims

1. A high- and low-speed transmission system for agricultural machinery power, comprising: The shaft group, oil pump OP and clutch group are characterized in that: the shaft group includes a coaxially arranged input shaft S1, an output shaft S3 and a power take-off shaft S4, the power take-off shaft S4 is rotationally connected to the input shaft S1 and the output shaft S3 respectively, the oil pump OP is connected to the clutch group, the oil pump OP can be driven by the input shaft S1, and the power of the input shaft S1 can be transmitted to the output shaft S3 or the power take-off shaft S4 through the clutch group.

2. The agricultural machinery power high and low gear transmission system according to claim 1, characterized in that: The shaft assembly further includes an intermediate shaft S2 that is transmission-connected to the side of the input shaft S1 . The intermediate shaft S2 is rotationally connected to a gear G1 , and the gear G1 is transmission-connected to the output shaft S3 .

3. The agricultural machinery power high and low gear transmission system according to claim 2, characterized in that: The shaft assembly further includes an intermediate shaft S5 that is transmission-connected to the side of the input shaft S1 . The intermediate shaft S5 is rotationally connected to a gear G2 , and the gear G2 is transmission-connected to the output shaft S3 .

4. The agricultural machinery power high and low gear transmission system according to claim 1, characterized in that: The clutch group includes a clutch outer hub H1, a clutch inner hub H2, a return spring group SP1, an active friction plate group CL1, a driven friction plate group CL2 and a piston P1. The clutch outer hub H1 is connected to the input shaft S1. The piston P1 is arranged in the inner cavity of the clutch outer hub H1. One side of the return spring group SP1 is in contact with the piston P1, and the other side of the return spring group SP1 is fixed to the clutch outer hub H1. The clutch inner hub H2 is connected to the power take-off shaft S4. The active friction plate group CL1 is connected to the clutch outer hub H1, and the driven friction plate group CL2 is connected to the clutch inner hub H2.

5. The agricultural machinery power high and low gear transmission system according to claim 4, characterized in that: The clutch group also includes a clutch outer hub H4, a clutch inner hub H3, a return spring group SP2, an active friction plate group CL4, a driven friction plate group CL3 and a piston P2. The clutch outer hub H4 is connected to the output shaft S3, and the piston P2 is arranged in the inner cavity of the clutch outer hub H4. One side of the return spring group SP2 is in contact with the piston P2, and the other side of the return spring group SP2 is fixed to the clutch outer hub H4. The clutch inner hub H3 is connected to the clutch outer hub H1, the active friction plate group CL4 is connected to the clutch inner hub H3, and the driven friction plate group CL3 is connected to the clutch outer hub H4.

6. The agricultural machinery power high and low gear transmission system according to claim 3, characterized in that: The clutch group also includes a clutch outer hub H7, a clutch inner hub H8, a return spring group SP4, an active friction plate group CL7, a driven friction plate group CL8 and a piston P4. The clutch outer hub H7 is connected to the intermediate shaft S5, and the piston P4 is arranged in the inner cavity of the clutch outer hub H7. One side of the return spring group SP4 is in contact with the piston P4, and the other side of the return spring group SP4 is fixed to the clutch outer hub H7. The clutch inner hub H8 is connected to the gear G2, the active friction plate group CL7 is connected to the clutch outer hub H7, and the driven friction plate group CL8 is connected to the clutch inner hub H8.

7. The agricultural machinery power high and low gear transmission system according to claim 2, characterized in that: The clutch group also includes a clutch outer hub H6, a clutch inner hub H5, a return spring group SP3, an active friction plate group CL5, a driven friction plate group CL6 and a piston P3. The clutch outer hub H6 is connected to the intermediate shaft S2, and the piston P3 is arranged in the inner cavity of the clutch outer hub H6. One side of the return spring group SP3 is in contact with the piston P3, and the other side of the return spring group SP3 is fixed to the clutch outer hub H6. The clutch inner hub H5 is connected to the gear G1, the active friction plate group CL5 is connected to the clutch outer hub H6, and the driven friction plate group CL6 is connected to the clutch inner hub H5.

8. The agricultural machinery power high and low gear transmission system according to claim 2, characterized in that: A sprocket W1 is fixed to the driving end of the oil pump OP, a sprocket W2 is fixed to the intermediate shaft S2 , and a chain CH1 is drivingly connected between the sprocket W1 and the sprocket W2 .

9. The agricultural machinery power high and low gear transmission system according to claim 4, characterized in that: The power take-off shaft S4 is arranged through the output shaft S3, the input shaft S1 includes an assembly end D11, the power take-off shaft S4 has a plug-in end D41 close to the assembly end D11, the plug-in end D41 and the assembly end D11 are rotatably connected to a bearing B2, and the clutch inner hub H2 is arranged close to the clutch outer hub H1 and is located outside the bearing B2.

10. The agricultural machinery power high and low gear transmission system according to claim 9, characterized in that: The output shaft S3 has a mating end D31, which is arranged close to the assembly end D11. The clutch inner hub H4 is arranged on the periphery of the output shaft S3 close to the mating end D31, and the clutch inner hub H3 is connected to the inner side of the clutch inner hub H4.

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