CN110118243B - Tractor and power transmission device - Google Patents

Tractor and power transmission device Download PDF

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Publication number
CN110118243B
CN110118243B CN201910344853.XA CN201910344853A CN110118243B CN 110118243 B CN110118243 B CN 110118243B CN 201910344853 A CN201910344853 A CN 201910344853A CN 110118243 B CN110118243 B CN 110118243B
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CN
China
Prior art keywords
gear
shaft
input shaft
driven gear
driven
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Active
Application number
CN201910344853.XA
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Chinese (zh)
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CN110118243A (en
Inventor
肖名涛
周志
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Changsha Sanglaite Agricultural Mechanical Equipment Co Ltd
Original Assignee
Changsha Sanglaite Agricultural Mechanical Equipment Co Ltd
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Publication date
Application filed by Changsha Sanglaite Agricultural Mechanical Equipment Co Ltd filed Critical Changsha Sanglaite Agricultural Mechanical Equipment Co Ltd
Priority to CN201910344853.XA priority Critical patent/CN110118243B/en
Publication of CN110118243A publication Critical patent/CN110118243A/en
Application granted granted Critical
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
    • B60K17/08—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing of mechanical type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/10—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of fluid gearing
    • B60K17/105—Units comprising at least a part of the gearing and a torque-transmitting axle, e.g. transaxles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/20—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear
    • F16H3/22—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with gears shiftable only axially
    • F16H3/30—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with gears shiftable only axially with driving and driven shafts not coaxial
    • F16H3/32—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with gears shiftable only axially with driving and driven shafts not coaxial and an additional shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/32—Gear shift yokes, e.g. shift forks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The invention provides a tractor and a power transmission device thereof, wherein the power transmission device comprises a front axle, a clutch, a speed reducer, a speed changer, a hydraulic pump, a hydraulic motor and a plurality of universal transmission devices, and the front axle is connected with the speed changer through the universal transmission devices; the speed reducer is arranged on the clutch, and the clutch is connected with the speed changer through the universal transmission device; the speed reducer comprises an input shaft, the hydraulic pump is arranged on the input shaft, and the hydraulic pump is driven to rotate when the input shaft rotates; the speed changer comprises a speed changing assembly, the speed changing assembly comprises a direct-connection input shaft and an intermediate shaft, the intermediate shaft is arranged in parallel with the direct-connection input shaft, and an auxiliary input shaft is sleeved on the direct-connection input shaft; the hydraulic motor is fixedly arranged at one end of the intermediate shaft, and the hydraulic motor can provide power for the direct-connection input shaft and/or the auxiliary input shaft.

Description

Tractor and power transmission device
Technical Field
The invention relates to the field of tractor machinery, in particular to a tractor and a power transmission device.
Background
The articulated tractor adopts the articulated frame, and the articulated point of the front frame and the rear frame deflects in the running process of the vehicle, so the articulated tractor has small steering radius and strong maneuvering performance, and is an ideal tool in the transportation of southern hilly mountain areas and the field operation process of paddy fields. Articulated tractors are generally longer than wheeled tractors because of the increased articulation point in the middle of the frame due to the use of articulation point steering. At present, the hinge type mountain tractor which is widely applied on the market has a hinge point mainly arranged at the rear end of a speed changer, and the structure is difficult to shorten the length of a machine body. As the horsepower of agricultural machinery increases, the structure of the engine and its power unit is longer, resulting in an increase in the length of the fuselage, which reduces the maneuverability of the articulated vehicle.
The articulated mountain tractor can be used for road transportation and field operation, and the single manual speed change is difficult to meet the requirement of complex working conditions due to wide working range and complex working condition change. Therefore, how to provide a tractor and a power transmission device thereof, which are convenient in speed change and gear shift, strong in working condition adaptability, high in transmission efficiency and capable of realizing the input of various power sources, is a technical problem which needs to be solved by the person skilled in the art.
Disclosure of Invention
The invention aims to solve the technical problems that: the tractor and the power transmission device thereof have the advantages of convenient speed change and gear shift, strong working condition adaptability, high transmission efficiency and capability of realizing the input of various power sources.
The solution of the invention is realized as follows: the invention provides a power transmission device which is characterized by comprising a front axle, a clutch, a speed reducer, a speed changer, a hydraulic pump, a hydraulic motor and a plurality of universal transmission devices, wherein the front axle is connected with the speed changer through the universal transmission devices; the speed reducer is arranged on the clutch, and the clutch is connected with the speed changer through the universal transmission device; the speed reducer comprises an input shaft, the hydraulic pump is arranged on the input shaft, and the hydraulic pump is driven to rotate when the input shaft rotates; the speed changer comprises a speed changing assembly, the speed changing assembly comprises a speed changing box body, a direct-connection input shaft and an intermediate shaft, the direct-connection input shaft and the intermediate shaft are arranged in the speed changing box body, the intermediate shaft is arranged in parallel with the direct-connection input shaft, and a secondary input shaft is sleeved on the direct-connection input shaft; the hydraulic motor is fixedly arranged at one end of the intermediate shaft, and the hydraulic motor can provide power for the direct-connection input shaft and/or the auxiliary input shaft. According to the power transmission device with the structure, the hydraulic pump is arranged on the speed reducer, the hydraulic motor is arranged on the speed changer, and the direct-connection transmission of the hydraulic motor and the machinery is realized, so that the transmission efficiency of the tractor is higher, the speed change and the gear shift are more convenient, the working condition adaptability is stronger, and the operation field is wider.
The speed reducer further comprises a speed reduction box body and a speed reduction box cover arranged on the speed reduction box body, an output shaft is arranged in the speed reduction box body, the output shaft is arranged in parallel with the input shaft, an input shaft driving gear is arranged on the input shaft, and an output shaft driven gear is further arranged on the output shaft.
The other technical scheme of the invention is that on the basis of the above, a first gear driving gear, a second gear driving gear, a third gear driving gear and a fourth gear driving gear are sequentially arranged on the auxiliary input shaft, and the first gear driving gear, the second gear driving gear, the third gear driving gear and the fourth gear driving gear are respectively sleeved on the auxiliary input shaft through splines; or the first gear driving gear and the second gear driving gear can also be in an integrated structure with the auxiliary input shaft.
The other technical scheme of the invention is that on the basis of the above, a plurality of bearings are arranged between the auxiliary input shaft and the direct-connection input shaft, and the direct-connection input shaft is arranged on the gearbox body through the plurality of bearings; and a retainer ring is arranged between the third-gear driving gear and the fourth-gear driving gear, and the third-gear driving gear and the fourth-gear driving gear are positioned through the retainer ring and an axle step on the auxiliary input shaft.
The other technical scheme of the invention is that on the basis of the above, a first-gear driven gear, a second-gear driven gear, a third-gear driven gear and a fourth-gear driven gear are sequentially arranged on the intermediate shaft, and the first-gear driven gear, the second-gear driven gear, the third-gear driven gear and the fourth-gear driven gear are respectively sleeved on the intermediate shaft through bearings; bearings are arranged between the first-gear driven gear and the gearbox body and between the fourth-gear driven gear and the gearbox body; the first-gear driven gear and the bearing are respectively provided with a thrust bearing, and the first-gear driven gear, the second-gear driven gear, the third-gear driven gear and the fourth-gear driven gear can rotate relatively at different speeds.
The other technical scheme of the invention is that on the basis of the above, a second gear spline hub and a third and fourth gear spline hub are further arranged on the intermediate shaft, the first gear spline hub is arranged between the first gear driven gear and the second gear driven gear, and the third and fourth gear spline hub is arranged between the third gear driven gear and the fourth gear driven gear; a second gear engagement sleeve is arranged on the periphery of the second gear spline hub, and the second gear engagement sleeve can move left and right along the second gear spline hub; the periphery of the third and fourth gear spline hub is provided with a third and fourth gear engagement sleeve, and the third and fourth gear engagement sleeve can move left and right along the third and fourth gear spline hub.
The other technical scheme of the invention is that on the basis of the above, the auxiliary input shaft is also provided with a power switching gear, and the power switching gear is arranged on the auxiliary input shaft through a spline; one side of the power switching gear is also provided with a power switching shifting fork, and the power switching gear can move left and right along the auxiliary input shaft under the action of the power switching shifting fork.
The other technical scheme of the invention is that on the basis of the above, one side of the first and second gear engagement sleeve is also provided with a first and second gear shifting fork, and under the action of the first and second gear shifting fork, the first and second gear engagement sleeve can move left and right along the first and second gear spline hub; and a third-fourth gear shifting fork is further arranged on one side of the third-fourth gear engagement sleeve, and the third-fourth gear engagement sleeve can move left and right along the third-fourth gear spline hub under the action of the third-fourth gear shifting fork.
The other technical scheme of the invention is that on the basis of the above, the transmission further comprises a precursor assembly, a main speed reduction assembly and a power output assembly which are arranged in the transmission box body; the precursor assembly comprises a precursor shaft and a precursor shaft joint sleeve arranged on the precursor shaft, and one end of the precursor shaft joint sleeve is also provided with a precursor shifting fork; the main speed reduction assembly comprises a rear drive shaft arranged at one end of the front drive shaft, a rear drive shaft driven gear and a rear drive driving bevel gear which are arranged on the rear drive shaft, and a main speed reducer is arranged at one end of the rear drive driving bevel gear, which is away from the rear drive shaft driven gear; the power take-off assembly comprises a PTO input shaft, a second intermediate shaft and a PTO shaft, wherein the second intermediate shaft and the PTO shaft are arranged in parallel with the PTO input shaft; the PTO input shaft is sequentially provided with a fast gear driving gear, a fast and slow gear spline hub, a slow gear driving gear, a fast and slow gear engaging sleeve and a fast and slow gear shifting fork; the second intermediate shaft is provided with a gear driven gear, a PTO driving gear and a slow gear driven gear; and the PTO shaft is provided with a PTO shaft driven gear.
In another aspect, the present invention also provides a tractor comprising a power transmission device, the power transmission device being as described above.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention.
FIG. 1 is a schematic view of a tractor according to the present invention;
FIG. 2 is a schematic diagram of the transmission system of FIG. 1;
The structural schematic diagram of the decelerator of fig. 1 of fig. 3;
FIG. 4 is a schematic illustration of the transmission of FIG. 1;
FIG. 5 is a transmission shift schematic;
FIG. 6 is a reverse gear schematic of the transmission;
fig. 7 is a schematic diagram of a power take-off assembly.
The reference sign correspondence is:
1 engine 2 chassis 3 frame
4 Cab 5 suspension device
31 Front frame 32 hinge point 33 rear frame
41 Instrument desk 42 operating mechanism 43 seat
51 Front counterweight 52 suspension lifter
A front axle B clutch C speed reducer
Universal X piece for D speed variator E universal driving device
A C1 reduction box body C2 reduction box cover C3 input shaft,
C4 output shaft C5 output shaft driven gear C6 hydraulic pump
D1 speed change component D2 precursor component D3 main speed reduction component
D4 power take-off assembly D5 hydraulic motor
X1 end cover X2 bearing X3 bolt
X4 sealing ring X5 check ring X6 flange
X7 thrust sleeve X8 shaft sleeve X9 end cover
X10 clasp
S0 direct-connection input shaft S1 auxiliary input shaft G10 hydraulic input gear
G11 power switching gear G12 four-gear driving gear G13 three-gear driving gear
G14 second gear driving gear G15 third first gear driving gear
S2 intermediate shaft G21 four-gear driven gear G22 three-four-gear spline hub
G23 three-gear driven gear G24 two-gear driven gear G25 two-gear spline hub
G26 first gear driven gear J1 first gear engagement sleeve J2 third and fourth gear engagement sleeve
B1 first gear shifting fork B2 third gear shifting fork B3 precursor shifting fork
S3 precursor shaft J3 precursor joint sleeve
S4 rear drive shaft G41 rear drive shaft driven gear G42 rear drive bevel gear
D31 main speed reducer
S5PTO input shaft G51 fast gear driving gear G52 fast and slow gear spline hub
G53 slow-gear driving gear J4 fast-slow-gear engagement sleeve B4 fast-slow-gear shifting fork
G61 fast-shift driven gear G62PTO driving gear G63 slow-shift driven gear
S6 second intermediate shaft S7PTO shaft G71PTO shaft driven gear
Detailed Description
The following detailed description of the invention, taken in conjunction with the accompanying drawings, is given by way of illustration and explanation only, and should not be taken as limiting the scope of the invention in any way. Furthermore, the features in the embodiments and in the different embodiments in this document can be combined accordingly by a person skilled in the art from the description of this document.
In one embodiment, referring to fig. 1 to 7, the tractor and the power transmission device thereof are shown, and in particular, as shown in fig. 1, the tractor includes an engine 1, a chassis 2, a frame 3, a cab 4, and a suspension device 5. The chassis includes a drive train and a travel system. The frame 3 comprises a front frame 31, a hinge point 32 and a rear frame 33. The cab 4 includes an instrument desk 41, an operating mechanism 42, and a seat 43. The suspension device comprises a front counterweight 51 and a suspension lifter 52.
As shown in fig. 1 and 2, wherein the driveline includes a front axle a, a clutch B, a retarder C, a transmission D, and a universal drive E. The travelling system comprises a suspension and wheels W, although a suspension may be omitted for tractors which are mainly engaged in field operations. The front end of the clutch B is mounted on the engine A, the rear end of the clutch B is mounted with the reducer C, the reducer C is mounted with the hinge point 32, the front frame 31 is mounted on the engine 1, the front axle A and the counterweight 51 are mounted on the front frame 31, and the front frame 31, the front axle A, the engine 1, the clutch B and the reducer C form a front frame. The front fuselage may deflect about the hinge point 32, the rear frame 33 is mounted on the hinge point 32, the transmission D is mounted on the rear frame 33, the cab 4 is mounted on the transmission D, and the suspension lifter 52 is mounted on the transmission D.
The front end of the clutch B is arranged on the engine A, the rear end of the clutch B is provided with the speed reducer C, the front driving component D2 of the speed changer transmits power to the front axle A through the universal transmission device E, and in order to improve the power transmission efficiency, if a suspension is not arranged on the front axle A, the input end of the front axle A is coaxial with the output end of the front driving component D2. If the front axle is provided with a suspension, the input of the front axle a is coaxial with the output of the front drive assembly D2, allowing only a small amount of up-and-down oscillation. The front drive component D2 is in a normally-off state, rear wheel drive is adopted when the tractor normally runs, and the front drive is cut in only when the rear drive slips, so that four-wheel drive of the tractor is realized. The hydraulic pump C6 is spline-mounted on the input shaft C3, the hydraulic motor D5 is mounted on the transmission D, and the hydraulic input gear G10 is spline-mounted on the hydraulic motor D5.
The hinge point 32 is mounted on the speed reducer C, the rear frame 33 is mounted on the hinge point 32, the transmission D is mounted on the rear frame 33, and the auxiliary input shaft S1 of the transmission D is connected with the output shaft C4 of the speed reducer C through the universal transmission E. The universal drive E between the transmission D and the reduction C is a duplex constant velocity joint with its joint on the axis extension of the frame hinge point 32.
As shown in fig. 3, the reduction gear C includes a reduction gear box C1, a reduction gear box cover C2, an input shaft C3, an output shaft C4, an output shaft driven gear C5, and a hydraulic pump C6.
As shown in fig. 4, the transmission D includes a transmission assembly D1, a front drive assembly D2, a main reduction assembly D3, a power take-off assembly D4, and a hydraulic motor D5. The speed reducer C and the speed changer D are also provided with a plurality of universal parts X.
More specifically, an input shaft driving gear is machined on an input shaft C3 of the speed reducer C, the input shaft C3 is supported on a speed reduction box C1 through a bearing X2, and both ends of the input shaft C3 are positioned through end covers X1 and fixed on the box through bolts X3. The output shaft driven gear C5 is sleeved on the output shaft C4 through a spline, the output shaft driven gear C5 is positioned on the output shaft C5 through a check ring X5, the output shaft C5 is supported on the reduction gearbox C1 through a bearing X2, and two ends of the output shaft driven gear C5 are positioned through end covers X1 and fixed on the gearbox through bolts X3. The power input end of the input shaft C3 and the power output end cover X1 of the output shaft C4 are provided with sealing rings X4. The driving gear of the input shaft is meshed with the driven gear C5 of the output shaft, the rotation speed of the output shaft is reduced through secondary gear transmission, and the shake of a transmission system in the large-angle power transmission process is reduced.
As shown in fig. 5, the transmission assembly D1 includes a direct input shaft S0, a sub-input shaft S1, a hydraulic input gear G10, a power switching gear G11, a fourth-gear drive gear G12, a third-gear drive gear G13, a second-gear drive gear G14, and a first-gear drive gear G15. Intermediate shaft S2, fourth gear driven gear G21, third and fourth gear spline hub G22, third gear driven gear G23, second gear driven gear G24, first and second gear spline hub G25, first gear driven gear G26, first and second gear engagement sleeve J1, third and fourth gear engagement sleeve J2, power shift fork B0, first and second gear shift fork B1, third and fourth gear shift fork B2, and common member X. The auxiliary input shaft S1 is sleeved on the direct-connection input shaft S0, and a plurality of bearings are arranged between the direct-connection input shaft S0 and the auxiliary input shaft S1. For the general part X, mainly include end cover X1, bearing X2, bolt X3, sealing washer X4, retaining ring X5, flange X6, thrust collar X7, axle sleeve X8, end cover X9 and snap ring X10.
The power switching gear G11 is spline-mounted on the auxiliary input shaft S1, and is axially slidable along the auxiliary input shaft S1 under the control of the power switching fork B0. The first gear driving gear G15, the second gear driving gear G14, the third gear driving gear G13 and the fourth gear driving gear G12 are sleeved on the auxiliary input shaft S1 through splines, or the first gear driving gear G15 and the second gear driving gear G14 are directly processed on the auxiliary input shaft S1. The auxiliary input shaft S1 is supported on the direct-connection input shaft S0 through a bearing X2, the direct-connection input shaft S0 is supported on the box body through a bearing, and external splines which are output by power are machined on the direct-connection input shaft S0. A retainer ring F6 is arranged between the fourth-gear driving gear G12 and the third-gear driving gear G13, and the fourth-gear driving gear G12 and the third-gear driving gear G13 are positioned through the auxiliary input shaft S1 and the retainer ring X10.
The first gear driven gear G26, the second gear driven gear G24, the third gear driven gear G23 and the fourth gear driven gear G21 are sleeved on the intermediate shaft S2 in an empty mode through a shaft sleeve X8. The bearing X2 of the driven gear G21 of the fourth gear is positioned through the thrust sleeve X7 between the driven gear G26 of the first gear and the bearing X2, between the driven gear G23 of the third gear and the driven gear G24 of the second gear, so that the components of the groups can rotate relatively at different rotating speeds. The third and fourth gear spline hub G22 and the first and second gear spline hub G25 are sleeved on the intermediate shaft S2 through splines. The third and fourth gear engagement sleeve J2 is fitted over the third and fourth gear spline hub G22 by a spline sleeve and is slidable back and forth along the third and fourth gear spline hub G22. The second gear joint sleeve J1 is sleeved on the second gear spline hub G25 through a spline and can slide back and forth along the second gear spline hub G25. The second-gear driven gear G24, the first-gear joint sleeve J1, the first-gear spline hub G25 and the first-gear driven gear G26 form a second-gear switching module. The fourth-gear driven gear G21, the third-fourth-gear joint sleeve J2, the third-fourth-gear spline hub G22 and the third-gear driven gear G23 form a third-fourth-gear switching module.
As shown in fig. 6, the precursor assembly D2 includes a precursor shaft S3, and a precursor joint sleeve J3 and a precursor fork B3 disposed on the precursor shaft S3, where the precursor joint sleeve J3 can move left and right on the precursor shaft S3 under the action of the precursor fork B3. The main speed reduction assembly D3 comprises a rear drive shaft S4, wherein the rear drive shaft S4 is arranged at the right end of the front drive shaft S3, and a rear drive shaft driven gear G41 and a rear drive bevel gear G42 are sequentially arranged on the rear drive shaft. The final drive D31 is provided at the right end of the rear drive shaft S4.
The rear drive shaft driven gear G41 is sleeved on the rear drive shaft S4 through a spline, the rear drive shaft driven gear G41 is in constant mesh with external teeth on the first gear and second gear joint sleeve J1, the rear drive shaft driven gear G41 is a wide gear, and the first gear and second gear joint sleeve J1 slides to be in constant mesh transmission with the rear drive shaft driven gear G41 in neutral, first gear and second gear. The rear drive shaft S4 is provided with a rear drive bevel gear G42, and the rear drive bevel gear G42 transmits power to a driven bevel gear of the final drive D31. The rear drive shaft S4 is fixed to the case via a bearing X2. The precursor shaft S3 is respectively supported on the box body and the rear drive shaft S4 through a bearing X2 and a shaft sleeve X8, and a precursor joint sleeve J3 and a precursor shifting fork B3 are arranged on the precursor shaft.
As shown in fig. 7, the power take-off assembly D4 includes a PTO input shaft S5, and a fast-gear drive gear G51, a fast-gear spline hub G52, a slow-gear drive gear G53, a fast-gear engagement sleeve J4, and a fast-gear shift fork B4 provided on the PTO input shaft S5. The power take-off assembly D4 further includes a second intermediate shaft S6 disposed parallel to the PTO input shaft S5, and a fast driven gear G61, a PTO driving gear G62 and a slow driven gear G63 are disposed on the second intermediate shaft S6. The power take-off assembly D4 further includes a PTO shaft S7, the PTO shaft S7 being disposed parallel to the PTO input shaft S5, and a PTO shaft driven gear G71.
The principle of mechanical direct gear shifting is as follows:
the power switching gear G11 is driven by the power switching gear B0 to slide forwards, the external teeth of the power switching gear G11 are separated from the hydraulic input gear D10, the internal spline of the power switching gear G11 is combined with the external spline of the direct-connection input shaft S0 and the external spline of the auxiliary input shaft at the same time, at the moment, power is input to the auxiliary input shaft S1 through the direct-connection input shaft S0, and the auxiliary input shaft S1 runs at a mechanical input rotating speed.
The hydrostatic continuously variable shift principle is as follows:
The power switching gear G11 is driven by the power switching gear B0 to slide backwards, the external teeth of the power switching gear G11 are meshed with the hydraulic input gear D10, the internal spline of the power switching gear G11 is connected with the external spline port of the direct-connection input shaft S0, the internal spline of the power switching gear G11 is combined with the external spline of the auxiliary input shaft, at the moment, power is transmitted to the power switching gear G11 by the hydraulic motor D5 through the hydraulic input gear G10 to be input to the auxiliary input shaft S1, and the auxiliary input shaft S1 runs at a hydraulic stepless rotating speed.
The reverse gear is realized by hydrostatic stepless speed change, and reverse gear cannot be obtained in mechanical direct gear change.
The principle of a second gear shift is as follows:
A second gear engagement sleeve J1 is in an intermediate position to achieve neutral between a second gear. The second shift fork B1 is operated to enable the second shift joint sleeve J1 to move backwards, so that the internal spline of the second shift joint sleeve J1 is combined with the external spline of the first shift driven gear G26, power is transmitted to the first shift driven gear G26 through the first drive gear G15, is transmitted to the second shift joint sleeve J1 through the external spline of the first shift driven gear G26 and is transmitted to the second shift spline hub G25, and is transmitted to the intermediate shaft S2, and the intermediate shaft S2 rotates in the first shift. The second shift fork B1 is operated to move the first shift joint sleeve J1 forwards, so that the internal spline of the first shift joint sleeve J1 is combined with the external spline of the second shift driven gear G24, power is transmitted to the second shift driven gear G24 from the second drive gear G14, is transmitted to the first shift joint sleeve J1 through the external spline of the second shift driven gear G24 and is transmitted to the first shift spline hub G25, and is transmitted to the intermediate shaft S2, and the intermediate shaft S2 rotates in the second shift.
The three-four gear shift principle is as follows:
The third and fourth gear engagement sleeve J2 is positioned at the middle position, so that the neutral position between the third and fourth gears is realized. The third-fourth shift fork B2 is operated to enable the third-fourth shift joint sleeve J2 to move backwards, so that the internal spline of the third-fourth shift joint sleeve J2 is combined with the external spline of the third-shift driven gear B39, power is transmitted to the third-shift driven gear G23 through the third-shift driving gear G13, is transmitted to the third-fourth shift joint sleeve J2 through the external spline of the third-shift driven gear G23, is transmitted to the third-fourth shift spline hub G22, and is transmitted to the intermediate shaft S2, and the intermediate shaft S2 rotates in the third shift. The third and fourth shift fork B2 is operated to move the third and fourth shift joint sleeve J2 forwards, so that the internal spline of the third and fourth shift joint sleeve J2 is combined with the external spline of the fourth shift driven gear G21, power is transmitted to the fourth shift driven gear G21 from the fourth shift driving gear G12, is transmitted to the third and fourth shift joint sleeve J2 through the external spline of the fourth shift driven gear G21 and is transmitted to the third and fourth shift spline hub G22, and is transmitted to the intermediate shaft S2, and the intermediate shaft S2 rotates in the fourth shift.
The four-wheel drive conversion principle is as follows:
The front drive shifting fork B3 drives the front drive joint sleeve J3 to slide backwards, and the internal spline of the front drive joint sleeve J3 is simultaneously combined with the external spline of the front drive shaft S3 and the external spline of the rear drive shaft S4, so that the tractor is driven by four wheels. The front drive shifting fork B3 drives the front drive joint sleeve J3 to slide forwards, the internal spline of the front drive joint sleeve J3 is only combined with the external spline of the front drive shaft S3, but not combined with the external spline of the rear drive shaft S4, and the tractor is only driven by the rear wheels.
The principle of PTO shifting is as follows:
PTO fast gear: the fast and slow gear engagement sleeve J4 moves forward, and the fast and slow gear engagement sleeve J4 is simultaneously combined with external splines of the fast and slow gear spline hub G52 and the fast gear driving gear G51, so that the PTO transmission shifts to fast gear. The power transmission route is as follows. PTO input shaft S5, to the speed spline hub G52, the speed engagement sleeve J4, the speed drive gear G51, the speed driven gear G61, the second intermediate shaft S6, the PTO drive gear G62, the PTO driven gear E10, the PTO shaft S7.
PTO slow gear: the fast and slow gear engagement sleeve J4 moves backwards, the fast and slow gear engagement sleeve J4 is combined with external splines of the fast and slow gear spline hub G52 and the slow gear driving gear G53 at the same time, and the PTO transmission shifts to slow gear. The power transmission route is as follows. PTO input shaft S5, to the speed spline hub G52, the speed engagement sleeve J4, the slow drive gear G53, the slow driven gear G63, the second intermediate shaft S6, the PTO drive gear G62, the PTO driven gear E10, the PTO shaft S7.
The tractor with the structure and the power transmission device thereof have the following advantages:
Firstly, the length of the transmission can not influence the length layout of the whole tractor because the transmission is arranged at the rear position and the hinge point, so that the whole tractor length can be effectively reduced, and the maneuverability and the passing performance of the tractor can be improved.
Secondly, through setting up the hydraulic pump on the reduction gear, set up hydraulic motor on the derailleur, make the tractor can adopt two kinds of power source inputs of machinery and hydraulic pressure, have two kinds of functions of mechanical direct connection and hydraulic pressure infinitely variable speed, be fit for using in the occasion that the operating mode changes complicacy.
Thirdly, the hydraulic stepless speed change device is arranged in series before the gear shifting mechanism to form hydraulic stepless multi-gear speed, so that the power and torque range is wider, and the adaptability is stronger.
The foregoing is merely a preferred embodiment of the present invention and it should be noted that modifications and adaptations to those skilled in the art may be made without departing from the principles of the present invention, which are intended to be comprehended within the scope of the present invention.

Claims (7)

1. The power transmission device is characterized by comprising a front axle, a clutch, a speed reducer, a speed changer, a hydraulic pump, a hydraulic motor and a plurality of universal transmission devices, wherein the front axle is connected with the speed changer through the universal transmission devices;
The speed reducer is arranged on the clutch, and the clutch is connected with the speed changer through the universal transmission device;
The speed reducer comprises an input shaft, the hydraulic pump is arranged on the input shaft, and the hydraulic pump is driven to rotate when the input shaft rotates;
The speed changer comprises a speed changing assembly, the speed changing assembly comprises a speed changing box body, a direct-connection input shaft and an intermediate shaft, the direct-connection input shaft and the intermediate shaft are arranged in the speed changing box body, the intermediate shaft is arranged in parallel with the direct-connection input shaft, and a secondary input shaft is sleeved on the direct-connection input shaft;
The hydraulic motor is fixedly arranged at one end of the intermediate shaft and can provide power for the direct-connection input shaft and/or the auxiliary input shaft;
the auxiliary input shaft is also provided with a first gear driving gear, a second gear driving gear, a third gear driving gear and a fourth gear driving gear in sequence, and the first gear driving gear, the second gear driving gear, the third gear driving gear and the fourth gear driving gear are respectively sleeved on the auxiliary input shaft through splines;
the auxiliary input shaft is also provided with a power switching gear, and the power switching gear is arranged on the auxiliary input shaft through a spline;
One side of the power switching gear is also provided with a power switching shifting fork, and the power switching gear can move left and right along the auxiliary input shaft under the action of the power switching shifting fork;
the transmission further comprises a precursor component, a main speed reduction component and a power output component which are arranged in the transmission box body;
The precursor assembly comprises a precursor shaft and a precursor shaft joint sleeve arranged on the precursor shaft, and one end of the precursor shaft joint sleeve is also provided with a precursor shifting fork;
The main speed reduction assembly comprises a rear drive shaft arranged at one end of the front drive shaft, a rear drive shaft driven gear and a rear drive driving bevel gear which are arranged on the rear drive shaft, and a main speed reducer is arranged at one end of the rear drive driving bevel gear, which is away from the rear drive shaft driven gear;
The power take-off assembly comprises a PTO input shaft, a second intermediate shaft and a PTO shaft, wherein the second intermediate shaft and the PTO shaft are arranged in parallel with the PTO input shaft;
The PTO input shaft is sequentially provided with a fast gear driving gear, a fast and slow gear spline hub, a slow gear driving gear, a fast and slow gear engaging sleeve and a fast and slow gear shifting fork; the second intermediate shaft is provided with a gear driven gear, a PTO driving gear and a slow gear driven gear; the PTO shaft is provided with a PTO shaft driven gear;
The cab is mounted on the transmission and the suspension lifter is mounted on the transmission.
2. The power transmission device according to claim 1, wherein the speed reducer further comprises a speed reduction box body and a speed reduction box cover arranged on the speed reduction box body, an output shaft is arranged in the speed reduction box body, the output shaft is arranged in parallel with the input shaft, an input shaft driving gear is arranged on the input shaft, and an output shaft driven gear is further arranged on the output shaft.
3. The power transmission device according to claim 2, wherein a plurality of bearings are provided between the auxiliary input shaft and the direct-connection input shaft, the direct-connection input shaft being provided on the transmission case through a plurality of bearings;
and a retainer ring is arranged between the third-gear driving gear and the fourth-gear driving gear, and the third-gear driving gear and the fourth-gear driving gear are positioned through the retainer ring and an axle step on the auxiliary input shaft.
4. The power transmission device according to claim 3, wherein the intermediate shaft is provided with a first-gear driven gear, a second-gear driven gear, a third-gear driven gear and a fourth-gear driven gear in sequence, and the first-gear driven gear, the second-gear driven gear, the third-gear driven gear and the fourth-gear driven gear are respectively sleeved on the intermediate shaft through bearings;
Bearings are arranged between the first-gear driven gear and the gearbox body and between the fourth-gear driven gear and the gearbox body;
The first-gear driven gear and the bearing are respectively provided with a thrust bearing, and the first-gear driven gear, the second-gear driven gear, the third-gear driven gear and the fourth-gear driven gear can rotate relatively at different speeds.
5. The power transmission device according to claim 4, wherein a second gear spline hub and a third and fourth gear spline hub are further provided on the intermediate shaft, the first gear spline hub is provided between the first gear driven gear and the second gear driven gear, and the third and fourth gear spline hub is provided between the third gear driven gear and the fourth gear driven gear;
a second gear engagement sleeve is arranged on the periphery of the second gear spline hub, and the second gear engagement sleeve can move left and right along the second gear spline hub;
the periphery of the third and fourth gear spline hub is provided with a third and fourth gear engagement sleeve, and the third and fourth gear engagement sleeve can move left and right along the third and fourth gear spline hub.
6. The power transmission device according to claim 5, wherein a first gear shift fork is further provided on one side of the first gear engagement sleeve, and the first gear engagement sleeve is movable left and right along the first gear spline hub under the action of the first gear shift fork;
And a third-fourth gear shifting fork is further arranged on one side of the third-fourth gear engagement sleeve, and the third-fourth gear engagement sleeve can move left and right along the third-fourth gear spline hub under the action of the third-fourth gear shifting fork.
7. A tractor comprising a power transmission device, characterized in that the power transmission device is the power transmission device according to any one of claims 1 to 6.
CN201910344853.XA 2019-04-26 2019-04-26 Tractor and power transmission device Active CN110118243B (en)

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CN110118243B true CN110118243B (en) 2024-05-28

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Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004125110A (en) * 2002-10-04 2004-04-22 Honda Motor Co Ltd Transmission with auxiliary shift mechanism
CN201246458Y (en) * 2008-04-22 2009-05-27 赵宏坚 Mechanical and hydraulic combined transmission device
CN201461919U (en) * 2009-08-27 2010-05-12 天津建筑机械厂 Mechanical and hydraulic drive gear box
CN204385794U (en) * 2014-12-15 2015-06-10 湖南三一路面机械有限公司 A kind of land leveller and power drive system thereof
CN204512351U (en) * 2015-03-31 2015-07-29 南京农业大学 Double clutch hydraulic mechanical stepless gearbox
CN105114587A (en) * 2015-09-16 2015-12-02 湖南省农友机械集团有限公司 Mechanical direct-connection and hydrostatic stepless parallel-connection tri-speed type dual-power input device
CN205089929U (en) * 2015-10-22 2016-03-16 吉首市宗南重工制造有限公司 Machine liquid hybrid -driven formula gearbox
CN108146238A (en) * 2018-01-10 2018-06-12 西安卓士博液压工程有限责任公司 A kind of vehicle composite drive chassis system
CN208602320U (en) * 2018-05-18 2019-03-15 长沙桑铼特农业机械设备有限公司 A kind of tractor transmission system and 4 wheel driven type tractor
CN210344179U (en) * 2019-04-26 2020-04-17 长沙桑铼特农业机械设备有限公司 Tractor and power transmission device

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004125110A (en) * 2002-10-04 2004-04-22 Honda Motor Co Ltd Transmission with auxiliary shift mechanism
CN201246458Y (en) * 2008-04-22 2009-05-27 赵宏坚 Mechanical and hydraulic combined transmission device
CN201461919U (en) * 2009-08-27 2010-05-12 天津建筑机械厂 Mechanical and hydraulic drive gear box
CN204385794U (en) * 2014-12-15 2015-06-10 湖南三一路面机械有限公司 A kind of land leveller and power drive system thereof
CN204512351U (en) * 2015-03-31 2015-07-29 南京农业大学 Double clutch hydraulic mechanical stepless gearbox
CN105114587A (en) * 2015-09-16 2015-12-02 湖南省农友机械集团有限公司 Mechanical direct-connection and hydrostatic stepless parallel-connection tri-speed type dual-power input device
CN205089929U (en) * 2015-10-22 2016-03-16 吉首市宗南重工制造有限公司 Machine liquid hybrid -driven formula gearbox
CN108146238A (en) * 2018-01-10 2018-06-12 西安卓士博液压工程有限责任公司 A kind of vehicle composite drive chassis system
CN208602320U (en) * 2018-05-18 2019-03-15 长沙桑铼特农业机械设备有限公司 A kind of tractor transmission system and 4 wheel driven type tractor
CN210344179U (en) * 2019-04-26 2020-04-17 长沙桑铼特农业机械设备有限公司 Tractor and power transmission device

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Denomination of invention: A tractor and power transmission device

Granted publication date: 20240528

Pledgee: Industrial and Commercial Bank of China Limited Ningxiang Branch

Pledgor: CHANGSHA SUNLIGHT AGRICULTUREMACHINERY FACILITIES Co.,Ltd.

Registration number: Y2024980033727