A high-flexibility tractor suitable for narrow space operation

Abstract

The application discloses a high-flexibility tractor suitable for operation in narrow space, which comprises a frame, a fixed front axle, a rear axle and a power function module movable in the front and downward direction. The power function module comprises a diesel engine and a HST variable pump, and is installed on an adjustable bearing seat. The oil pan of the diesel engine is provided with a longitudinal avoiding groove covering the moving stroke of the module, so that the fixed front axle is kept in the avoiding groove when the module moves. The HST variable pump is connected with a fixed HST hydraulic motor through a flexible pressure pipeline, and a position keeping mechanism and an end rigid positioning mechanism are arranged between the bearing seat and the frame. A control device adjusts the position of the power function module according to the load of the front axle, so as to improve the bearing state of the front axle under the heavy load working condition of the rear suspension while keeping the short axle arrangement.

Description

Technical Field

[0001] This invention relates to the field of agricultural machinery and equipment technology, and more specifically, to a highly flexible tractor suitable for operation in confined spaces. Background Technology

[0002] In greenhouses, densely planted orchards, and narrow field ridges, where space is limited, tractors often need to turn and make U-turns frequently during operation. The arrangement of the front axle, engine, and transmission along the longitudinal direction of the vehicle affects the wheelbase of the front and rear axles, the overall dimensions of the front end, and the turning radius of the vehicle.

[0003] Chinese patent document CN215204414U discloses a novel tractor in which the front drive axle assembly is mounted below the engine assembly to shorten the overall length and wheelbase. In this structure, the engine assembly and the front drive axle assembly are fixed in relative position after assembly. When heavy implements are attached to the rear, or when the tractor is going uphill, accelerating, or lifting implements, the load on the front axle changes with the stress on the entire vehicle. The fixed engine cannot adjust its position relative to the front and rear axles according to the changes in the load on the front axle.

[0004] Chinese patent document CN103858550B discloses a four-wheel self-balancing hillside tiller, in which the engine is mounted on a transverse slide rail and driven laterally by a hydraulic cylinder to adjust the lateral center of gravity position during hillside operation. This structure is mainly used in conjunction with the leveling of the left and right wheels, and the engine movement direction and transmission compensation method are both designed around lateral balance. When this structure is used in a short-wheelbase tractor with a fixed front axle, hydrostatic transmission, and rear power take-off mechanism, it is also necessary to address the spatial interference between the bottom of the engine and the fixed front axle, the displacement compensation of the hydrostatic pipeline, and the axial compensation of the power take-off transmission components.

[0005] Chinese patent document CN201884088U discloses an engine oil pan for a four-wheel drive vehicle. The oil pan has a groove at its bottom to provide installation space for the front-drive transmission mechanism below the engine, and the required oil capacity is maintained by adjusting the size of the oil pan. This groove primarily cooperates with the fixed transmission mechanism. When the engine moves longitudinally relative to the fixed component below, the clearance length provided by the local groove is limited; as the clearance area expands longitudinally, the oil storage space, connecting oil passages, and oil suction area need to be redesigned.

[0006] Existing tractors can improve front axle load under heavy rear overhang by installing counterweights at the front of the frame, but these counterweights occupy front mounting space and add mass that does not bear power, transmission, or operating functions. For vehicles operating in confined spaces, the increased front profile may also affect the vehicle's maneuverability when approaching crops, trellises, and field edges.

[0007] Furthermore, with the engine configured as a movable structure, the weight of the engine and its accessories needs to be supported by guiding and driving components; asynchrony between left and right drives may cause the load-bearing components to skew; hydrostatic transmission lines, power output drive shafts, intake and exhaust lines, fuel lines, and electrical wiring harnesses all need to accommodate relative displacement; when the moving parts are in the middle position, accidental slippage needs to be limited, and under normal traction and power output conditions, they also need to form a mechanical load-bearing connection with the fixed frame.

[0008] Therefore, it is necessary to provide a tractor that, while maintaining a fixed front axle and short wheelbase arrangement, utilizes the tractor's existing power components to adjust the longitudinal mass distribution of the entire vehicle, and takes into account guidance synchronization, transmission compensation, position holding, end locking, and engine lubrication during movement. Summary of the Invention

[0009] The purpose of this invention is to provide a highly flexible tractor suitable for operation in confined spaces, so as to improve the problem of reduced front axle load under heavy rear overhang, uphill or implement lifting conditions of short wheelbase tractors, and reduce the space occupation caused by adding independent front counterweights.

[0010] To achieve the above objectives, the present invention provides a highly flexible tractor suitable for operation in confined spaces, comprising a frame, a front axle, and a rear axle located on the frame; the frame is provided with a guide mechanism extending in a forward-downward direction, the guide mechanism being connected to an adjustable support, the adjustable support being provided with a power function module including a diesel engine and an HST variable pump, a drive mechanism being connected to the adjustable support to drive the power function module to move between a rear-upward position and a forward-downward position; the oil pan of the diesel engine is provided with a clearance groove extending longitudinally along the vehicle, the front axle being located within the clearance groove throughout the movement stroke of the power function module; the HST variable pump is connected to an HST hydraulic motor located on the frame via a flexible pressure pipeline; a position holding mechanism and an end rigid positioning mechanism are provided between the frame and the adjustable support; the front axle is provided with a load detection component, a control device being connected to the load detection component and the drive mechanism respectively, and adjusting the position of the power function module according to the load state of the front axle.

[0011] Preferably, the power function module further includes a radiator, a cooling fan, a fan shroud, an air filter, a muffler, and an exhaust aftertreatment assembly. The diesel engine and the HST variable pump are mounted on an adjustable support via flexible mounts. The radiator, cooling fan, fan shroud, air filter, muffler, and exhaust aftertreatment assembly are fixed to the adjustable support and move synchronously with it.

[0012] Preferably, the guiding mechanism includes a left-tilted guide rail and a right-tilted guide rail arranged in parallel, and the driving mechanism includes a left hydraulic cylinder and a right hydraulic cylinder respectively connected to the left and right sides of the adjustable support. The left and right hydraulic cylinders are connected to a hydraulic power source through a hydraulic diverter valve to distribute the oil supply flow of the two hydraulic cylinders.

[0013] Furthermore, a mechanical synchronization mechanism is provided between the left and right sides of the adjustable support base. The mechanical synchronization mechanism includes a transverse mechanical synchronization shaft and synchronization transmission components connecting the left and right sides of the adjustable support base respectively. Position sensors are provided on the left and right sides of the adjustable support base respectively, and the control device limits the left-right position difference of the adjustable support base based on the detection results of the two position sensors.

[0014] Preferably, the position holding mechanism includes a bidirectional hydraulic lock disposed at the cylinder ports of the left and right hydraulic cylinders. The cylinder ports are also equipped with a pipeline rupture shut-off valve to restrict the continued operation of the hydraulic cylinders in the event of abnormal pressure loss in the hydraulic pipeline.

[0015] Preferably, the end rigid positioning mechanism includes conical positioning seats located at the upper rear position and the lower front position, as well as a transverse locking pin. When the adjustable bearing reaches the corresponding end position, the conical positioning seats fit together, and the transverse locking pin passes through the adjustable bearing and the support fixed to the frame, thus mechanically locking the adjustable bearing to the frame.

[0016] Preferably, the left and right sides of the clearance groove are respectively provided with a left oil storage chamber and a right oil storage chamber, which are connected by a front connecting oil passage located outside the front end of the clearance groove and a rear connecting oil passage located outside the rear end of the clearance groove. The rear part of the oil pan is provided with an oil collection area lower than the bottom surface of the oil storage chamber, and the oil suction port is located in the oil collection area.

[0017] Furthermore, anti-sloshing baffles are provided in the left and right oil reservoirs. The anti-sloshing baffles are provided with oil guide ports for oil flow, and the oil guide ports are provided with one-way oil guide vanes that open toward the oil collection area.

[0018] Preferably, the flexible pressure pipeline includes two main high-pressure oil pipes and a housing drain pipe, with each pipeline forming a U-shaped compensating bend on the side of the frame. The U-shaped compensating bend is located within an arc-shaped guide groove and is equipped with a fixing clamp, an anti-torsion joint, an anti-wear sleeve, and an oil leakage detection component.

[0019] Preferably, a power output compensation mechanism is provided between the diesel engine and the power output input mechanism fixed to the vehicle frame. The power output compensation mechanism includes a telescopic spline drive shaft and couplings respectively disposed at both ends of the telescopic spline drive shaft, and the engagement state of the power output clutch is associated with the end locking state of the adjustable bearing seat.

[0020] Preferably, a telescopic flexible air guide sleeve is provided between the air intake frame fixed to the vehicle frame and the air guide shroud that moves with the power function module; a high-temperature resistant metal corrugated pipe is provided between the fixed exhaust tailpipe and the exhaust component that moves with the power function module; the fuel tank and battery are fixed at the low position of the vehicle frame, and the fuel line and electrical wiring harness compensate for the displacement of the power function module through flexible pipe sections and flexible cable chains, respectively.

[0021] Preferably, the load detection assembly includes a left strain gauge load detection assembly and a right strain gauge load detection assembly respectively disposed on the left and right load-bearing areas of the front axle. The control device determines the total load state of the front axle based on the sum of the loads on the left and right front wheels, and determines the lateral load imbalance state based on the load difference between the left and right front wheels.

[0022] Furthermore, the control device saves the factory-set safety reference load and the initial reference load for this operation, and calculates the absolute load ratio and relative unloading ratio of the front axle respectively. When the corresponding ratio reaches the adjustment condition, the control device limits the displacement of the HST variable pump and the output torque of the diesel engine, disconnects the power take-off shaft, and controls the power function module to move forward and downward along the guide mechanism.

[0023] When the front axle load is detected to be below a dangerous level and accompanied by vehicle pitching up, the control unit first returns the HST variable pump to the neutral position and applies braking, then moves the powertrain module to the lower front position. Once the risk condition is resolved, the control unit controls the powertrain module to gradually return to the upper rear position according to the return condition above the trigger threshold.

[0024] Compared to the aforementioned background technology, this invention keeps the fixed front axle within the oil pan clearance groove during the movement of the power function module. Therefore, adjusting the position of the power function module does not require changing the wheelbase of the front and rear axles or the steering geometry of the front axle. The power function module consists of a diesel engine, an HST variable pump, and its supporting functional components. The front axle load can be adjusted using the mass of existing functional components on the tractor, reducing the space occupied by a separate front counterweight.

[0025] The HST variable pump moves with the power function module, while the HST hydraulic motor remains stationary. The two are connected by a flexible pressure pipeline, eliminating the need for a high-pressure sliding seal pipe joint to accommodate the displacement of the power function module. Movement is restricted at the intermediate position by a position holding mechanism, while at the end positions, a mechanical load-bearing connection is formed by a conical positioning seat and a lateral locking pin. This allows for different load-bearing methods between the position adjustment state and the normal traction and power output states.

[0026] The oil pan forms interconnected oil storage chambers on both sides of the clearance groove, and is equipped with an oil collection area and an oil guiding structure. This allows for the maintenance of corresponding oil storage space even when the clearance groove occupies the central space of the oil pan, and improves the oil retention conditions near the oil intake when the vehicle pitches or accelerates or decelerates. Attached Figure Description

[0027] To more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0028] Figure 1 This is a schematic diagram of the overall structure of the tractor of the present invention; Figure 2 This is a schematic diagram of the connection structure between the power function module and the vehicle frame. Figure 3 A schematic diagram showing the fit between the fixed front axle and the longitudinal strip-shaped clearance groove of the oil pan; Figure 4 Schematic diagram of the guiding, driving and end positioning structure; Figure 5 A schematic diagram of the oil storage and guiding structure inside the oil pan; Figure 6 Schematic diagram of HST pipeline compensation mechanism and power output compensation mechanism; Figure 7 This is a schematic diagram of the auxiliary pipeline compensation structure; Figure 8 This is a schematic diagram of the connection relationships of the control system; Figure 9 This is a schematic diagram of the position adjustment process for the power function module.

[0029] In the diagram: 11. Front load-bearing connecting frame; 116. Fixed support; 21. Front axle housing; 27. Left strain gauge load detection assembly; 28. Right strain gauge load detection assembly; 34. HST hydraulic motor; 36. Power input / output mechanism; 4. Power function module; 41. Adjustable load-bearing seat; 42. Diesel engine; 43. HST variable pump; 51. Left tilt guide rail; 52. Right tilt guide rail; 53. Left hydraulic cylinder; 54. Right hydraulic cylinder; 5 6. Transverse mechanical synchronous shaft; 57. Left position sensor; 58. Right position sensor; 59. End positioning and locking assembly; 591. Rear upper conical positioning seat; 592. Front lower conical positioning seat; 593. Rear upper transverse hydraulic locking pin; 594. Front lower transverse hydraulic locking pin; 596. Two-way hydraulic lock; 597. Pipeline rupture shut-off valve; 599. Conical wear-resistant bushing; 6. Oil pan assembly; 62. Longitudinal strip-shaped clearance groove; 63. Left oil reservoir; 64. Right oil reservoir; 65. Front connecting oil passage; 66. Rear connecting oil passage; 67. Rear oil collection area; 68. Oil suction port; 69. Anti-sloshing oil guide assembly; 692. One-way oil guide plate; 7. HST pipeline compensation mechanism; 71. Main high-pressure oil pipe; 73. Shell drain pipe; 74. U-shaped compensation bend; 75. Arc-shaped guide groove; 79. Oil leakage detection component; 8. Power output compensation mechanism; 81. Telescopic spline drive shaft; 82. Front universal coupling; 8 3. Rear universal joint; 84. Power output clutch; 86. Axial anti-detachment structure; 91. Telescopic flexible air guide sleeve; 93. High-temperature resistant metal bellows; 97. Automatic shut-off valve for pressure loss; 99. Flexible cable chain; 101. Controller; 102. Vehicle posture sensor; 103. Vehicle speed sensor; 104. HST circuit pressure sensor; 105. Power output status sensor; 106. Brake actuator; 109. Proportional directional valve assembly. Detailed Implementation

[0030] The present invention will be further described below with reference to the accompanying drawings and specific embodiments. The described embodiments are used to illustrate the structure and working process of the present invention and are not intended to limit the scope of protection of the present invention.

[0031] The terms "front," "back," "left," "right," "up," and "down" used in this manual are based on the direction the tractor travels normally forward. The longitudinal direction (front-back) of the tractor is defined as longitudinal, and the lateral direction (left-right) of the tractor is defined as lateral.

[0032] Example 1: Please refer to Figures 1 to 9 This embodiment provides a highly flexible tractor suitable for operation in confined spaces, including a front load-bearing connecting frame 11, a front axle, a rear axle, a power function module 4, a guide drive and locking mechanism, an oil pan assembly 6, an HST pipeline compensation mechanism 7, a power output compensation mechanism 8, an auxiliary pipeline compensation mechanism, and a control system.

[0033] The front load-bearing connecting frame 11 includes left and right longitudinal beams arranged along the longitudinal direction of the vehicle and front and rear cross beams connecting the left and right longitudinal beams. The left and right longitudinal beams and the front and rear cross beams can be made of bent steel plates or welded rectangular tubes to form a box-shaped load-bearing frame to bear the gravity, moving inertial load, and load acting under the end-locked state of the power function module.

[0034] The left and right longitudinal beams are respectively provided with guide rail mounting seats that extend obliquely from the rear-upward direction to the front-downward direction on their respective inner sides. The guide rail mounting seats are welded to the corresponding longitudinal beams. For easy maintenance of the guide rails, the oblique guide rails can also be detachably connected to the guide rail mounting seats using high-strength fasteners.

[0035] The front load-bearing connecting frame 11 is provided with fixed supports 116 at the upper rear end and lower front end of the guide rail travel. The fixed supports 116 are connected to the corresponding longitudinal beam and transverse beam. The fixed supports are provided with reinforcing plates on both sides to distribute and transfer the end positioning and locking load to the front load-bearing connecting frame 11.

[0036] A bridge-type rear axle connecting frame is connected to the rear of the front load-bearing connecting frame 11. The front end of the rear axle connecting frame is connected to the rear crossbeam of the front load-bearing connecting frame by fasteners, and the rear end is connected to the rear axle housing. The front load-bearing connecting frame, the rear axle connecting frame and the rear axle form a continuous longitudinal load-bearing path.

[0037] The front axle includes a front axle housing 21 arranged laterally along the vehicle. The front axle housing 21 is connected to the front load-bearing connecting frame 11 through a central swing support in the middle. The left and right ends are respectively rotatably connected to steering knuckles, and the left and right front wheels are mounted on the corresponding steering knuckles.

[0038] The central swing support includes a swing pin arranged along the longitudinal direction of the vehicle and bearing seats located on both sides of the swing pin. The swing pin passes through a support hole in the middle of the front axle housing 21, allowing the front axle housing to swing within a defined angle about the longitudinal axis of the vehicle; the position of the front axle housing 21 along the longitudinal direction of the vehicle is fixed relative to the front load-bearing connecting frame 11.

[0039] The front axle steering cylinder and steering tie rod are arranged according to the front axle steering space. The position adjustment of the power function module 4 does not change the steering knuckle axis, the front axle centerline, or the front and rear axle wheelbase.

[0040] The front axle housing 21 is equipped with a left strain-type load detection assembly 27 and a right strain-type load detection assembly 28 in the load-bearing areas near the left and right steering knuckles, respectively. Each load detection assembly includes a strain detection element, a protective cover, and a signal conditioning circuit. The load on the left front wheel and the load on the right front wheel are obtained through calibration under no-load and standard load conditions, respectively.

[0041] The rear axle is fixed with an HST hydraulic motor 34, a rear transmission mechanism, and a power output / input mechanism 36. The HST hydraulic motor 34 is connected to the rear transmission mechanism, and the HST hydraulic motor, the rear transmission mechanism, and the power output / input mechanism do not move with the power function module 4.

[0042] The power function module 4 includes an adjustable support 41, a diesel engine 42, an HST variable pump 43, and cooling, intake, and exhaust components that move synchronously with the diesel engine.

[0043] The adjustable support 41 consists of a base plate, left and right side beams, and front and rear connecting beams connecting the left and right side beams. The left and right side beams are arranged parallel to each other along the longitudinal direction of the vehicle. The base plate is connected to the upper part of the left and right side beams. Reinforcing ribs are provided at the junction of the side beams and the connecting beams to form a box-shaped frame that supports the diesel engine 42 and the HST variable pump 43.

[0044] The adjustable support base 41 has sliding parts on its lower left and right sides, respectively. The two sliding parts are slidably engaged with the corresponding left tilting guide rail 51 and right tilting guide rail 52. The sliding parts can be roller slides, roller sliders, or sliding seats with replaceable wear-resistant plates.

[0045] The diesel engine 42 is mounted on the adjustable support 41 via an elastic suspension component. The elastic suspension component includes a rubber-metal composite damper, an upper connecting plate, and a lower connecting plate. The upper connecting plate is connected to the diesel engine mounting feet via fasteners, and the lower connecting plate is connected to the adjustable support 41 via fasteners.

[0046] The HST variable pump 43 is installed on the power output side of the diesel engine 42. Specifically, the HST variable pump 43 can be connected to the diesel engine flywheel housing via a flange, or it can be connected to the diesel engine via a short shaft and coupling, so that the HST variable pump and the diesel engine move synchronously during position adjustment.

[0047] The cooling components include a radiator, a cooling fan, and an air guide shroud. The radiator is fixed to the front of the adjustable support 41, the cooling fan is located between the radiator and the diesel engine 42, and the air guide shroud is connected to the periphery of the radiator and surrounds the outside of the cooling fan. The air filter is fixed to the side of the adjustable support and is connected to the diesel engine through the intake pipe.

[0048] The exhaust components include a muffler and an exhaust aftertreatment assembly. The muffler and exhaust aftertreatment assembly are fixed to an adjustable support 41 via a heat-insulating bracket and connected to a diesel engine 42 via an exhaust connection pipe. Thus, the diesel engine, HST variable pump, and corresponding cooling, intake, and exhaust components constitute a movable power functional module 4.

[0049] In this embodiment, the total mass of the power function module 4 can be set from 300kg to 400kg depending on the diesel engine power and accessory configuration. The components included in the power function module all undertake power, transmission, cooling, intake or exhaust functions, and there is no separate independent counterweight at the front of the frame for adjusting the front axle load.

[0050] In this embodiment, the wheelbase between the front axle and the rear axle can be set to 1400mm to 1460mm, preferably 1437mm.

[0051] The guiding drive and locking mechanism includes a left tilting guide rail 51 and a right tilting guide rail 52 that are parallel to each other, a left hydraulic cylinder 53 and a right hydraulic cylinder 54 that are respectively connected to the left and right sides of the adjustable bearing seat 41, a transverse mechanical synchronous shaft 56, a left position sensor 57, a right position sensor 58, and an end positioning and locking assembly 59.

[0052] The left-tilting guide rail 51 and the right-tilting guide rail 52 extend from the rear upper direction to the front lower direction. Their angles with the horizontal plane can be set from 10° to 18°. The longitudinal forward movement of the power function module 4 can be set from 60mm to 110mm, and the vertical descent can be set from 15mm to 30mm. Let the longitudinal forward movement be Δx, the vertical descent be Δh, the angle between the guide rail and the horizontal plane be α, and the effective travel of the guide rail be L. When the guide rail adopts a straight trajectory, the parameters satisfy the following formula: ; ; In this embodiment, when Δx=90mm and Δh=22mm, α is approximately 13.7°, which is within the aforementioned guide rail angle range.

[0053] The cylinder end of the left hydraulic cylinder 53 is hinged to the front bearing connecting frame 11, and the piston rod end is hinged to the left side of the adjustable bearing seat 41; the right hydraulic cylinder 54 is connected to the right side of the adjustable bearing seat in the same way. The axes of the two hydraulic cylinders are basically parallel to the corresponding inclined guide rails, so that the output force of the hydraulic cylinders mainly acts on the adjustable bearing seat along the direction of the guide rails.

[0054] The left hydraulic cylinder 53 and the right hydraulic cylinder 54 are connected to the tractor's hydraulic power source through a hydraulic diverter valve. The hydraulic diverter valve initially distributes the flow into the two hydraulic cylinders to reduce the difference in movement speed between the two sides.

[0055] The transverse mechanical synchronous shaft 56 is rotatably connected to the front bearing connecting frame 11 via a bearing seat, and synchronous gears are connected to its left and right ends respectively; the sliding parts on the left and right sides of the adjustable bearing seat 41 are respectively provided with racks that mesh with the synchronous gears.

[0056] When the left hydraulic cylinder 53 and the right hydraulic cylinder 54 drive the adjustable support 41 to move, the racks on both sides drive the same transverse mechanical synchronous shaft 56 to rotate, thereby limiting the relative displacement between the sliding parts on both sides. The transverse mechanical synchronous shaft mainly bears the correction torque generated by the difference in left and right positions, while the main moving load of the power function module 4 is still borne by the two hydraulic cylinders.

[0057] Left position sensor 57 and right position sensor 58 are respectively set along the corresponding inclined guide rails. Specifically, they can be magnetostrictive displacement sensors, wire displacement sensors, or linear displacement sensors. Controller 101 determines the position difference between the left and right sides of the power function module 4 based on the detection values ​​of the two position sensors.

[0058] The end positioning and locking assembly 59 includes a rear upper conical surface positioning seat 591 and a rear upper transverse hydraulic locking pin 593 disposed at the rear upper position, and a front lower conical surface positioning seat 592 and a front lower transverse hydraulic locking pin 594 disposed at the front lower position.

[0059] Both the upper rear conical positioning seat 591 and the lower front conical positioning seat 592 include mating parts respectively disposed on the fixed support 116 and the adjustable bearing seat 41. When the power function module 4 approaches the corresponding end position, the mating conical surfaces first make contact, and the adjustable bearing seat is laterally and vertically guided while the hydraulic cylinder continues to operate at low speed.

[0060] After the conical surface positioning is completed, the upper rear transverse hydraulic locking pin 593 or the lower front transverse hydraulic locking pin 594 passes through the corresponding locking holes on the fixed support 116 and the adjustable bearing seat 41. The control system confirms whether the corresponding locking pin has reached the locking position through the locking pin position detection switch.

[0061] Both the left hydraulic cylinder 53 and the right hydraulic cylinder 54 are equipped with a two-way hydraulic lock 596 and a pipeline rupture shut-off valve 597 at their cylinder ports. The two-way hydraulic lock 596 is used to maintain the position of the hydraulic cylinder, and the pipeline rupture shut-off valve 597 is used to close the cylinder port oil circuit when the pipeline flow rate increases abnormally or the pressure drops suddenly.

[0062] The oil pan assembly 6 includes a longitudinally elongated clearance groove 62, a left oil storage chamber 63 and a right oil storage chamber 64 located on the left and right sides of the clearance groove, a front connecting oil passage 65, a rear connecting oil passage 66, a rear oil collection area 67, an oil suction port 68, and an anti-sloshing oil guiding assembly 69.

[0063] The oil pan body is connected to the lower part of the diesel engine 42 via circumferential fasteners and gaskets. A longitudinally elongated clearance groove 62 is formed by an upward indentation from the bottom wall of the oil pan body and extends longitudinally along the vehicle.

[0064] The length of the longitudinal elongated clearance groove 62 covers the entire travel distance of the power function module 4 from the rear upper position to the front lower position. When the power function module is in the rear upper position, any intermediate position, or the front lower position, the fixed front axle housing 21 is located within the space of the longitudinal elongated clearance groove 62.

[0065] The width of the longitudinal strip-shaped clearance groove 62 is greater than the lateral outline dimension of the corresponding part of the front axle housing 21, and its depth satisfies the upper swing space when the front axle housing swings around the central swing support; the left and right sides and the top of the clearance groove also have gaps to compensate for manufacturing errors, assembly errors and structural deformation.

[0066] The left side of the longitudinally elongated clearance groove 62 forms a left oil storage chamber 63, and the right side forms a right oil storage chamber 64. The front connecting oil passage 65 is located outside the front end of the clearance groove, and the rear connecting oil passage 66 is located outside the rear end of the clearance groove. The left oil storage chamber 63 and the right oil storage chamber 64 are connected through the front connecting oil passage 65 and the rear connecting oil passage 66.

[0067] The rear oil collection area 67 is located at the rear of the oil pan, and its bottom surface is lower than the main bottom surfaces of the left oil reservoir 63 and the right oil reservoir 64. The oil suction port 68 is located in the rear oil collection area 67 and is connected to the oil suction pipe of the diesel engine lubricating oil pump.

[0068] The anti-sloshing oil guiding assembly 69 includes an anti-sloshing baffle, a one-way oil guiding plate 692, and an oil guiding slope disposed in the left oil storage chamber 63 and the right oil storage chamber 64. The lower part of the anti-sloshing baffle is provided with an oil guiding port, the upper part of the one-way oil guiding plate 692 is connected to the edge of the oil guiding port, and its lower part can open towards the rear oil collection area 67.

[0069] When the tractor goes uphill or accelerates, the oil in the oil reservoir can flow to the rear oil collection area 67 through the oil guide port; when the oil has a tendency to flow forward, the one-way oil guide plate 692 restricts the oil in the oil collection area from moving forward quickly, while the oil guide slope guides the oil to flow towards the oil suction port 68.

[0070] The HST pipeline compensation mechanism 7 includes two main high-pressure oil pipes 71, a shell drain pipe 73, a U-shaped compensation bend 74, an arc-shaped guide groove 75, and an oil leakage detection component 79.

[0071] Two main high-pressure oil pipes 71 connect the HST variable pump 43, which moves with the power function module 4, to the HST hydraulic motor 34, which is fixed to the frame. The housing drain pipe 73 connects the housing drain port of the HST variable pump to the fixed oil tank.

[0072] Both main high-pressure oil pipes 71 and the housing drain pipe 73 are made of high-pressure flexible hoses, and a U-shaped compensating bend 74 is formed on the side of the front bearing connecting frame 11. The arc-shaped guide groove 75 is fixed to the side of the frame. When the power function module 4 moves, the U-shaped compensating bend 74 expands or contracts along the arc-shaped guide groove 75.

[0073] Both ends of each flexible hose are connected to the adjustable support 41 and the fixed frame by fixing clamps. The joint adopts an anti-torsion structure, and the repeated bending area is provided with an anti-wear sleeve to limit the bending deformation of the hose within the predetermined compensation area.

[0074] The radius of curvature of the arc-shaped guide groove 75 is not less than the minimum allowable bending radius of the high-pressure flexible hose used. An oil leakage detection component 79 is disposed below the arc-shaped guide groove 75 and includes an oil collection section and an oil detection element for detecting leakage in the hose or joint.

[0075] The power output compensation mechanism 8 includes a telescopic spline drive shaft 81, a front universal joint 82, a rear universal joint 83, a power output clutch 84, and an axial anti-disengagement structure 86.

[0076] The telescopic spline drive shaft 81 includes a spline inner shaft and a spline sleeve that slide against each other, and the two can move relative to each other axially and transmit torque. The front universal joint 82 is connected to the power output end on the diesel engine side, and the rear universal joint 83 is connected to the fixed power output / input mechanism 36.

[0077] A dustproof telescopic cover is provided on the outside of the spline telescopic area. The axial anti-disengagement structure 86 includes a limiting step and a limiting component set on the inner shaft and spline sleeve to limit the abnormal disengagement of the two. The power output clutch 84 is set on the diesel engine side or inside the power output input mechanism 36.

[0078] The auxiliary pipeline compensation mechanism includes a telescopic flexible air guide sleeve 91, a high-temperature resistant metal bellows 93, an automatic pressure-reducing shut-off valve 97 installed on the fuel supply pipeline, and a flexible drag chain 99 for accommodating electrical wiring harnesses.

[0079] One end of the telescopic flexible air guide sleeve 91 is sealed and fixed to the air intake frame of the vehicle frame, and the other end is sealed and connected to the air guide shroud that moves with the power function module 4. A folded corrugated section is formed in the middle of the flexible air guide sleeve, and a limiting support is provided on the outside of the folded corrugated section to limit its excessive contraction and avoid interference with the cooling fan.

[0080] The fixed hood air intake area is connected to an air filter that moves with the power function module 4 via a flexible air intake pipe. A high-temperature resistant metal bellows 93 connects the muffler or exhaust aftertreatment assembly that moves with the power function module to the fixed exhaust tailpipe, and its outer side is equipped with a heat insulation layer and an anti-torsion bracket.

[0081] The fuel tank is fixed to the low position of the vehicle frame. The fuel supply hose and the fuel return hose are connected to the fuel tank and the diesel engine 42, respectively, and an arc-shaped compensation section is reserved along the movement direction of the power function module 4. An automatic pressure loss shut-off valve 97 is installed on the fuel supply hose near the fuel tank.

[0082] The battery is fixed to the low position of the vehicle frame, and the starting cable, generator cable, and sensor harness are centrally located within the flexible cable chain 99. One end of the flexible cable chain 99 is connected to the vehicle frame, and the other end is connected to the adjustable support 41. High-current lines are equipped with fuse protection devices near the battery.

[0083] The control system includes a controller 101, a vehicle posture sensor 102, a vehicle speed sensor 103, an HST circuit pressure sensor 104, a power output status sensor 105, a brake actuator 106, a proportional directional valve group 109, and alarm and human-machine interaction components.

[0084] The controller 101 is connected to the left strain gauge load detection component 27, the right strain gauge load detection component 28, the left position sensor 57, the right position sensor 58, the locking pin position detection switch, the vehicle body attitude sensor 102, the vehicle speed sensor 103, the HST circuit pressure sensor 104, and the power output status sensor 105, and controls the proportional directional valve group 109, the HST variable pump 43, the power output clutch 84, and the brake actuator 106.

[0085] The working process of this embodiment is as follows.

[0086] When the tractor is calibrated at the factory, the power function module 4 is in the rear-up position, and the controller 101 records the corresponding factory safety reference total front axle load F. s After attaching the implements, the tractor is parked on a relatively flat surface, and the controller collects the load F on the left front wheel. L and right front wheel load F R The sum of these two values ​​is recorded as the initial reference total front axle load F0 for this operation. L F R F s Both F0 and F0 use the same force unit, which is Newton in this embodiment.

[0087] Controller 101 calculates the absolute front axle load ratio R according to the following formula. a : ; The relative unloading ratio D is calculated according to the following formula. r : ; Absolute front axle load ratio R a and relative unloading ratio D r All are dimensionless parameters. When F L +F R When D is not less than F0, r Take 0; when F L +F R When it is less than F0, calculate D according to the above formula. rThis is to avoid representing an increase in front axle load as a negative unloading.

[0088] When the front axle load meets normal operating conditions, the power function module 4 is in the upper rear position, the upper rear conical positioning seats 591 are in contact with each other, and the upper rear lateral hydraulic locking pin 593 passes through the corresponding locking hole. After the controller 101 confirms that the locking pin has reached the locked position, it allows the HST variable pump 43 to adjust the displacement normally and allows the power output clutch 84 to engage.

[0089] When the absolute front axle load ratio R a Below the first adjustment threshold, or the relative unloading ratio D r When the set value is reached and the confirmation time is maintained, the controller 101 enters the position adjustment state. The left-right load imbalance ratio η is only used for lateral risk interlocking and is not used as a direct trigger for the longitudinal forward movement of the drive power function module.

[0090] Before adjusting the position, the controller 101 first determines whether the vehicle speed is within the allowable adjustment range. Specifically, the allowable adjustment speed can be set to no more than 3 km / h; when the vehicle speed is higher than the allowable value, the controller limits the displacement of the HST variable pump 43, thereby reducing the vehicle speed.

[0091] Subsequently, the controller 101 disconnects the power output clutch 84, limiting the displacement of the HST variable pump 43 and the output torque of the diesel engine 42, and reducing the HST closed-loop pressure. After confirmation that the upper lateral hydraulic locking pin 593 has retracted, the controller drives the left hydraulic cylinder 53 and the right hydraulic cylinder 54 to actuate via the proportional directional valve group 109.

[0092] Controller 101 based on the absolute front axle load ratio R a Relative unloading ratio D r The target displacement of the power function module 4 is determined by the vehicle body pitch angle; when the front axle load decreases or the vehicle body pitch angle increases, the target position moves forward and downward accordingly.

[0093] During the movement of the power function module 4, the hydraulic flow divider valve distributes the flow, the transverse mechanical synchronous shaft 56 restricts the relative offset of the left and right sliding parts, and the left position sensor 57 and right position sensor 58 detect the position difference between the two sides. When the position difference between the two sides exceeds the set range, the controller 101 stops the hydraulic cylinder from moving, and the bidirectional hydraulic lock 596 keeps the power function module in its current position.

[0094] When the power function module 4 is in the middle position, the tractor maintains low speed, limited displacement and limited torque operation, and the power output clutch 84 remains disengaged; the middle position is maintained by the two-way hydraulic lock 596 and is not used as the normal high-load traction and power output operation position.

[0095] Current bridge absolute load ratio R aWhen the vehicle's head-up angle is below the danger threshold and reaches the set value and continues to reach the confirmation time, the controller 101 first returns the HST variable pump 43 to the neutral position and applies braking through the brake actuator 106, and then moves the power function module 4 to the forward lower position.

[0096] When the power function module 4 approaches the lower front position, the controller 101 reduces the moving speed of the hydraulic cylinders on both sides, causing the lower front conical positioning seat 592 to gradually engage. When the left-right position difference and the end position meet the locking conditions, the lower front lateral hydraulic locking pin 594 passes through the corresponding locking hole.

[0097] After the front lower transverse hydraulic locking pin 594 is locked, the weight of the power function module 4 and the driving impact are mainly transmitted to the front bearing connecting frame 11 through the front lower conical surface positioning seat 592 and the fixed support 116. The transverse hydraulic locking pin restricts the adjustable bearing seat 41 from moving along the guide rail direction in a double shearing manner.

[0098] After the mechanical locking is completed in the lower front position and the front axle load is restored to the allowable range, the controller 101 can release the corresponding HST displacement and diesel engine torque limits; the power output clutch 84 is only allowed to engage after the end lock state is confirmed.

[0099] When the absolute front axle load ratio R a Once the vehicle body pitches down and remains at a set position for a period of time after returning to a position above the return threshold, the controller 101 allows the power function module 4 to move back to the rear-up position. The return threshold is higher than the trigger threshold for forward-down movement to reduce repeated movement of the power function module when the load fluctuates within a critical range.

[0100] Controller 101 in F L +F R When the load exceeds the preset lower limit, the unbalanced load ratio η between the left and right sides is calculated according to the following formula: ; When the left and right load imbalance ratio η reaches the set threshold, the controller 101 suspends the movement of the power function module 4 and limits the HST output to identify lateral risks such as cross slope, single-sided wheel sinking, or partial suspension; η is not used as a direct trigger for the power function module to move forward and downward.

[0101] When the power supply is interrupted, the hydraulic line loses pressure or the line ruptures, the two-way hydraulic lock 596 and the line rupture shut-off valve 597 close the hydraulic cylinder oil circuit, keeping the power function module 4 in its current position; the controller 101 simultaneously returns the HST variable pump 43 to the neutral position and applies the brake, prohibiting the power function module from continuing to move and the power output clutch 84 from engaging until the fault is cleared.

[0102] The longitudinal torque increment ΔM generated by the forward movement of power module 4 can be estimated using the formula ΔM = mgΔx, where m is the mass of the power module (kg), g is the acceleration due to gravity (m / s²), Δx is the longitudinal forward movement of the power module's center of gravity (m), and ΔM is in N·m. In this embodiment, m is taken as 340 kg, g as 9.81 m / s², and Δx as 0.09 m. Substituting these values, the result is: ΔM=mgΔx ΔM=340×9.81×0.09≈300 N·m The dimensions of the above calculation are kg×m / s²×m=N·m, which is used to illustrate the impact of moving the power function module forward on the longitudinal force of the whole vehicle; the specific parameters can be adjusted according to the vehicle wheelbase, rear suspension load and diesel engine configuration.

[0103] When the power function module 4 moves along the inclined guide rail, the gravity component along the guide rail direction is mainly borne by the left hydraulic cylinder 53, the right hydraulic cylinder 54 and the bidirectional hydraulic lock 596, while the gravity component perpendicular to the guide rail direction is mainly borne by the left inclined guide rail 51, the right inclined guide rail 52 and the corresponding sliding part.

[0104] After the power function module 4 completes the end locking, the conical positioning seat mainly bears the vertical load, the lateral load and part of the longitudinal impact. The lateral hydraulic locking pin restricts the adjustable bearing seat 41 from moving along the guide rail direction, so that the main load under normal traction and power output conditions does not need to be borne by the hydraulic cylinder for a long time.

[0105] Example 2: The overall structure and working process of this example are basically the same as those of Example 1. The difference is that the mechanical synchronization mechanism adopts a sprocket roller chain structure instead of a gear and rack structure.

[0106] In this embodiment, the left and right ends of the transverse mechanical synchronous shaft 56 are respectively fixed with synchronous sprockets, the left inclined guide rail 51 is provided with a left roller chain, and the right inclined guide rail 52 is provided with a right roller chain.

[0107] The left and right roller chains are respectively wound around the corresponding synchronous sprocket and driven sprocket, and the two sliding parts are respectively connected to the carrying chain segments of the corresponding roller chains.

[0108] When the left hydraulic cylinder 53 and the right hydraulic cylinder 54 drive the power function module 4 to move, the left and right roller chains respectively drive the synchronous sprockets fixed on the same transverse mechanical synchronous shaft 56 to rotate, thereby limiting the relative position difference of the sliding parts on both sides.

[0109] The return sections of the left and right roller chains are each equipped with tensioning pulleys, which are connected to the front bearing connecting frame 11 via adjustable tensioning seats. The outer side of the sprocket roller chain structure is equipped with a removable protective cover to reduce the entry of soil and plant debris into the transmission area.

[0110] Both the sprocket roller chain structure and the gear rack structure are used to limit the relative displacement of the left and right sides of the adjustable bearing seat 41, without changing the structural relationship of the power function module 4 moving in the forward and downward direction, fixing the front axle in the longitudinal long strip clearance groove 62, and the end mechanical locking.

[0111] Example 3: Based on Example 1, this example further modifies the end positioning and locking assembly 59 and the guide rail bearing part.

[0112] The upper rear conical positioning seat 591 and the lower front conical positioning seat 592 respectively include a fixed conical seat, a movable conical seat, and a replaceable conical wear-resistant bushing 599. The fixed conical seat is connected to the fixed support 116, the movable conical seat is connected to the adjustable bearing seat 41 through fasteners, and the conical wear-resistant bushing 599 is connected to the fixed conical seat or the movable conical seat through countersunk fasteners or pressure plates.

[0113] The included angle between the mating conical surfaces can be set from 18° to 22°, specifically 20°. When the included angle is too small, the axial force required to release the positioning seat increases accordingly; when the included angle is too large, the guiding stroke of the conical surface for lateral and vertical errors decreases accordingly. The above angle range can take into account both end-point guidance and locking release.

[0114] The fixed and movable cone seats can be made of 40Cr steel, with a hardness of 32HRC to 38HRC after quenching and tempering. The wear-resistant bushing 599 on the cone surface can be made of 20CrMnTi steel, with a surface hardness of 58HRC to 62HRC after surface hardening treatment, and a hardened layer depth of 0.8mm to 1.2mm.

[0115] The upper rear transverse hydraulic locking pin 593 and the lower front transverse hydraulic locking pin 594 can be made of 42CrMo steel, with a diameter ranging from 28mm to 34mm depending on the mass of the power function module and the impact load. After the locking pins are inserted into the fixed support 116 and the adjustable bearing seat 41, they form a double shear force.

[0116] The connection between the fixed support 116 and the front load-bearing connecting frame 11 is provided with a transition fillet and a reinforcing rib. The radius of the transition fillet can be set to 8mm to 12mm, and the ends of the reinforcing ribs are rounded to reduce the abrupt change in cross-section at the junction of the plates.

[0117] The bearing surfaces of the left tilting guide rail 51 and the right tilting guide rail 52 are provided with a hardened layer, and the sliding part of the adjustable bearing seat 41 is provided with a replaceable wear-resistant plate at the contact position with the guide rail. When the wear reaches the maintenance limit, the wear-resistant plate or the conical wear-resistant bushing 599 can be replaced without replacing the entire adjustable bearing seat 41 or the fixed support 116.

[0118] Compared with Embodiment 1, this embodiment makes the end positioning load distributed relatively uniformly on the contact surface by limiting the taper angle, material hardness, transition fillet and replaceable wear-resistant part, and provides replaceable components for gap maintenance after repeated switching.

[0119] Embodiment 4: This embodiment further generalizes the common structures of the foregoing embodiments.

[0120] The tractor of this embodiment includes a fixed load-bearing structure, a fixed front walking axle, a rear walking axle, a movable power functional assembly, a displacement guiding mechanism, a linear driving mechanism, a position holding mechanism, an end rigid positioning mechanism, a transmission compensation mechanism, a state detection assembly and a control device.

[0121] The movable power functional assembly at least includes a power source for generating the driving force of the whole vehicle and a power transmission component matched with the power source. The power source may specifically adopt a diesel engine or other internal combustion power devices, and the power transmission component may specifically adopt a hydrostatic pump or a mechanical transmission input component.

[0122] The movable power functional assembly is connected to a load-bearing member, and the load-bearing member is connected to the fixed load-bearing structure through the displacement guiding mechanism. The movement path defined by the displacement guiding mechanism at least has a component toward the front of the vehicle, and may also have a component toward the lower side of the vehicle.

[0123] The displacement guiding mechanism may adopt a sliding guide rail, a rolling guide rail, a roller guide rail or a linear bearing. The linear driving mechanism may adopt a hydraulic cylinder, an electric push rod, a screw driving mechanism or a rack and pinion driving mechanism.

[0124] When the linear driving mechanisms are respectively arranged on both sides, a mechanical synchronization assembly, a hydraulic synchronization assembly, an electric control synchronization assembly or a combination of at least two of them may be used to limit the left-right position difference. The mechanical synchronization assembly may specifically adopt a synchronization shaft, a gear and rack, a sprocket and roller chain or a link assembly.

[0125] The position holding mechanism is used to restrict the movable power functional assembly from uncommanded movement at the intermediate position, and it may adopt a hydraulic lock, a brake, a self-locking transmission component or a stop member.

[0126] The end rigid positioning mechanism is used to form a mechanical load-bearing connection between the load-bearing member and the fixed load-bearing structure when the movable power functional assembly reaches a preset end position. The end rigid positioning mechanism may adopt taper surface positioning, inclined surface positioning, pin-hole positioning or concave-convex fit positioning, and may be locked by a lock pin, a lock hook, a wedge block or a clamping member.

[0127] An oil collecting member or a shell member with an avoidance space is arranged at the lower part of the power source, and the avoidance space extends along the moving direction of the movable power functional assembly, so that the fixed front walking axle is located in the avoidance space at at least two positions of the movable power functional assembly.

[0128] The oil collecting component may have liquid storage areas located on both sides of the clearance space, as well as fluid channels connecting different liquid storage areas. Flow isolation components, flow guides, unidirectional flow components, and confluence areas may be installed within the liquid storage areas.

[0129] The transmission compensation mechanism is used to compensate for the relative displacement between the movable power functional component and the fixed transmission component. The hydraulic transmission can use flexible pressure pipes and guided bending compensation sections, while the mechanical power output can use telescopic shafts, splined shafts, universal joints, or flexible couplings.

[0130] The displacement of the movable power function components can be compensated by flexible connectors, telescopic connectors, cable chains, guides or margin sections.

[0131] The condition detection component is used to detect at least one of the following: front axle load, vehicle posture, power function component position, vehicle speed, power output status, and end-lock status. The control device controls the linear drive mechanism based on the signals from the condition detection component, and restricts driving power, power output, or position adjustment actions when preset operating conditions are not met.

[0132] The connections, fixations, or installations described in this manual may be made using welding, fastener connections, riveting, interference fits, snap-fits, or other detachable connection methods, depending on the load-bearing requirements of the corresponding components.

Claims

1. A highly flexible tractor suitable for operation in confined spaces, comprising a frame, a front axle and a rear axle located on the frame, characterized in that: The vehicle frame is equipped with a guide mechanism extending in a forward-downward direction. The guide mechanism is connected to an adjustable support. The adjustable support is equipped with a power function module including a diesel engine and an HST variable displacement pump. A drive mechanism is connected to the adjustable support to drive the power function module to move between a rear-upward position and a front-downward position. The oil pan of the diesel engine is equipped with a clearance groove extending longitudinally along the vehicle. The front axle is located within the clearance groove throughout the movement stroke of the power function module. The HST variable displacement pump is connected to an HST hydraulic motor located on the vehicle frame via a flexible pressure pipeline. A position holding mechanism and an end rigid positioning mechanism are provided between the vehicle frame and the adjustable support. The front axle is equipped with a load detection component. A control device is connected to the load detection component and the drive mechanism respectively, and adjusts the position of the power function module according to the front axle load status.

2. The high-flexibility tractor according to claim 1, characterized in that, The power function module also includes a radiator, a cooling fan, a shroud, an air filter, a muffler, and an exhaust aftertreatment assembly; the diesel engine and the HST variable pump are mounted on the adjustable support via elastic suspension components, and the radiator, cooling fan, shroud, air filter, muffler, and exhaust aftertreatment assembly are fixed to the adjustable support.

3. The high-flexibility tractor according to claim 1, characterized in that, The guiding mechanism includes a left tilting guide rail and a right tilting guide rail that are parallel to each other. The driving mechanism includes a left hydraulic cylinder and a right hydraulic cylinder that are respectively connected to the left and right sides of the adjustable bearing seat. The left and right hydraulic cylinders are connected to a hydraulic source through a hydraulic diverter valve. The left and right sides of the adjustable bearing seat are connected by a transverse mechanical synchronous shaft and a synchronous transmission component, and are respectively equipped with position sensors.

4. The high-flexibility tractor according to claim 3, characterized in that, The position holding mechanism includes a bidirectional hydraulic lock and a pipeline rupture shut-off valve respectively disposed on the cylinder ports of the hydraulic cylinders on both sides of the drive mechanism; the end rigid positioning mechanism includes a conical positioning seat and a transverse hydraulic locking pin respectively disposed on the upper rear position and the lower front position, the transverse hydraulic locking pin being used to pass through the adjustable bearing seat and the fixed support located on the frame.

5. The high-flexibility tractor according to claim 1, characterized in that, The left and right sides of the clearance groove form a left oil storage chamber and a right oil storage chamber, respectively. The left and right oil storage chambers are connected by a front connecting oil passage located outside the front end of the clearance groove and a rear connecting oil passage located outside the rear end of the clearance groove. The rear part of the oil pan is provided with an oil collection area, and the oil suction port is located in the oil collection area. The oil storage chamber is provided with an anti-sloshing baffle, the anti-sloshing baffle is provided with an oil guide port, and the oil guide port is provided with a one-way oil guide plate. The lower part of the one-way oil guide plate can open towards the oil collection area.

6. The high-flexibility tractor according to claim 1, characterized in that, The flexible pressure pipeline includes two main high-pressure oil pipes connecting the HST variable pump and the HST hydraulic motor, as well as a housing drain pipe. Each pipeline forms a U-shaped compensation bend on the side of the frame. The U-shaped compensation bend is set in an arc-shaped guide groove and is equipped with a rigid fixing clamp, an anti-torsion joint, an anti-wear sleeve, and an oil leakage detection component.

7. The high-flexibility tractor according to claim 1, characterized in that, A telescopic spline drive shaft is provided between the diesel engine and the power output input mechanism located on the vehicle frame, and couplings are provided at both ends of the telescopic spline drive shaft; a power output clutch is also provided between the diesel engine and the power output input mechanism, and the control device is configured to prevent the power output clutch from engaging when the power function module leaves the end rigid positioning state.

8. The high-flexibility tractor according to claim 1, characterized in that, A telescopic flexible air guide sleeve is provided between the air intake frame of the vehicle frame and the air guide shroud that moves with the power function module. A high-temperature resistant metal corrugated pipe is provided between the fixed exhaust tailpipe and the exhaust component that moves with the power function module. The fuel tank and battery are located on the vehicle frame. The fuel line is connected to the diesel engine through a flexible pipe section. The electrical wiring harness is connected to the power function module through a flexible cable chain.

9. The high-flexibility tractor according to claim 1, characterized in that, The load detection components include a left strain-type load detection component and a right strain-type load detection component respectively disposed on the left and right load-bearing areas of the front axle; the control device is also connected to a vehicle body attitude sensor and stores the factory safety reference total front axle load F. s The initial reference total front axle load for this operation is F0; let the load on the left front wheel be F. L The load on the right front wheel is F R The absolute front axle load ratio When F L +F R When the relative unloading ratio D is not less than F0, r Take 0; when F L +F R When it is less than F0, The control device is based on R a D r The target position of the power function module is determined by the vehicle body pitch angle.

10. The high-flexibility tractor according to claim 1, characterized in that, The wheelbase between the front and rear axles is 1400mm to 1460mm, the angle between the guide mechanism and the horizontal plane is 10° to 18°, the longitudinal forward movement of the power function module from the rear upper position to the front lower position is 60mm to 110mm and the vertical descent is 15mm to 30mm, and the front of the frame is not equipped with an independent counterweight.

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