Four-wheel-drive mini-tiller and gearbox structure thereof

Abstract

A four-wheel-drive mini-tiller and a gearbox structure thereof relate to the technical field of agricultural machinery and can distribute power supplied to two rear wheels by a walking box and reduce the steering difficulty of the four-wheel-drive mini-tiller, and a power distribution shaft and two output half shafts are arranged in the walking box; power output teeth are arranged in the middle of the power distribution shaft, transmission shaft sleeves symmetrically sleeve the two sides of the power distribution shaft, and a containing cavity is formed in the inner surface of the power distribution shaft; a mounting through hole is formed in the axial direction of the power distribution shaft, limiting holes are formed in the two sides of the power distribution shaft in the radial direction, and the limiting holes communicate with the mounting through hole; a reset spring is arranged in the middle of the mounting through hole, clutch pins are arranged at the two ends of the mounting through hole, a pressing plate and a pressing rod are further arranged on the outer surface of the walking box, the sides, away from each other, of the two clutch pins are conical containing parts, one end of the pressing rod abuts against the pressing plate, and the other end of the pressing rod penetrates through the outer wall to be connected with the clutch pins; a clutch bead is arranged in the limiting hole; distribution teeth are arranged on the outer surface of the transmission shaft sleeve and meshed with the gear teeth on the corresponding output half shaft.

Description

Technical Field

[0001] The present invention relates to the technical field of agricultural machinery, and particularly relates to a four-wheel drive micro-tiller and its gearbox structure. Background Art

[0002] The micro-tiller is powered by a small diesel engine or gasoline engine, and has the characteristics of light weight, small size, simple structure, etc. It is widely applicable to dry land, paddy fields, orchards, etc. in plains, mountains, and hills. The micro-tiller generally has functions such as ditch digging, sowing, fertilizing, and plant protection. With corresponding agricultural tools, it can carry out operations such as pumping water, generating electricity, spraying pesticides, and sprinkling, and can also tow a trailer for short-distance transportation. The micro-tiller can travel freely in the field, which is convenient for users to use and store, and eliminates the trouble that large agricultural machinery cannot enter mountain fields. It is the best choice for farmers to replace ox plowing.

[0003] Generally, it includes a direct drive type and a belt drive type. In the direct drive type, the engine and the gearbox are directly connected through a flange. For example, in the four-wheel drive micro-tiller with the application number 202111442151.9, the power is directly transmitted into the gearbox through a wet friction clutch or a conical friction clutch. There are three shafts in the gearbox, namely the main shaft, the countershaft, and the reverse gear shaft. By shifting the position of the double-connected spur gears on the main shaft and the reverse gear shaft, the fast gear, slow gear, and reverse gear can be realized. Then, after the power is reversed and decelerated through two sets of straight bevel gears, the power is output. Importantly, it also improves the operation by improving the transmission structure and the micro-tiller blades, and the specific movement is driven by the walking shaft to directly drive the walking wheels.

[0004] However, during the actual operation of the micro-tiller, steering operation is also involved. Usually, the operator rotates the micro-tiller by lifting the handrail. When the existing micro-tiller actually steers in this way, both walking wheels will rotate at the same time, and it is easy to slip during steering. Moreover, since the driving force of the four-wheel drive micro-tiller engine directly comes from the engine, the control difficulty is relatively large, and the force requirement for the steering operation is also greater. Therefore, the convenience of the steering operation of the four-wheel drive micro-tiller is reduced. Summary of the Invention

[0005] I. Technical Problems to be Solved

[0006] In view of the deficiencies of the prior art, the present invention provides a four-wheel drive micro-tiller and its gearbox structure, which can distribute the power supplied to the two rear wheels by the walking box. Specifically, through the linkage control of the clutch pin and the clutch ball, the power transmission of the unilateral walking wheel can be interrupted during steering, making the steering more labor-saving, and it can also automatically resume transmission after steering to avoid power interruption.

[0007] II. Specific Technical Solutions

[0008] A four-wheel drive micro-tiller gearbox structure includes a main shaft box. The front end of the main shaft box is the installation end for the engine assembly. Below the front end of the main shaft box, there is a tool box. At the rear end of the main shaft box, there is a walking box. Inside the main shaft box, there is a main output shaft. At the front and rear ends of the main output shaft, there are respectively a first helical gear and a second helical gear. The first helical gear is used to drive the power input of the tool box; the second helical gear is used to drive the power input of the walking box. Inside the walking box, there are a power distribution shaft and two output half shafts; in the middle of the power distribution shaft, there is a power output gear. On both sides of the power distribution shaft, there are symmetrically sleeved drive shaft sleeves. The inner surface of the drive shaft sleeve is provided with a receiving cavity; along the axial direction, there is an installation through hole at the central position of the power distribution shaft. Along the radial direction on both sides of the power distribution shaft, there are limiting holes, and the limiting holes communicate with the installation through hole; in the middle of the installation through hole, there is a return spring. At both ends in the length direction of the installation through hole, there are clutch pins. On one side away from each other of the two clutch pins, there are conical receiving parts. On the outer surfaces on both sides of the walking box, there are also a pressing plate and a pressing rod. One end of the pressing rod abuts against the pressing plate, and the other end of the pressing rod passes through the outer wall and is connected to the clutch pin; in the limiting holes, there are clutch beads; on the outer surfaces of the drive shaft sleeves, there are respectively distribution teeth, and the distribution teeth mesh with the teeth on the corresponding output half shafts.

[0009] Implementation principle, working principle:

[0010] In this solution, the power provided by the main output shaft is output through the first helical gear and the second helical gear, which can effectively improve the integration degree of the gearbox structure and is beneficial to its miniaturization. Among them, the diameter of the second helical gear is smaller than the walking input helical gear inside the walking box. Specifically, on the gearbox, there is a clutch cable that drives the pressing plate to rotate. The clutch cable drives the pressing plate to rotate, and then drives the pressing rod to push the clutch pin forward towards the middle of the installation through hole. When the clutch bead enters the conical receiving part, the engagement between the drive shaft sleeve and the power distribution shaft fails, and the engagement on the other side is still effective. In this case, operating the steering will be more labor-saving; when the cable is released, due to the restoring force of the return spring, it will drive the clutch pin to reset, and then the engagement between the drive shaft sleeve and the power distribution shaft will be restored to maintain the transmission efficiency and normal operation.

[0011] Preferably, the installation through hole includes a spring installation section and a clutch pin installation section, and the aperture of the spring installation section is smaller than that of the clutch pin installation section; on each side of the power distribution shaft, there are 3 - 5 limiting holes, which are evenly arranged along the circumferential direction of the power distribution shaft; on the outer surface of the walking box, there is also an installation seat. The pressing plate is an L-shaped pressing plate, and one end of the pressing plate is rotatably connected to the installation seat.

[0012] Preferably, a first sleeve is provided at the front end of the main output shaft. The main output shaft is connected to the first sleeve through a bearing. The first helical gear is fixedly arranged on the first sleeve. A tool double gear is also fixedly arranged on the outer surface of the first sleeve. A limit plug is further arranged on the end face of the first helical gear near the tool box. The limit plug passes through the first helical gear and is threadedly connected to the front end of the main output shaft.

[0013] Preferably, the tool box is inclined and arranged at the front end of the main shaft box. A tool drive shaft and a power output shaft are arranged in the tool box. A tool power input helical gear is arranged at the upper end of the tool drive shaft. The power output bevel gear at the bottom end of the tool drive shaft meshes with the tool power output helical gear on the power output shaft.

[0014] Preferably, a second sleeve is sleeved at the rear end of the main output shaft. The second helical gear is arranged at one end of the second sleeve close to the walking box. The walking box is obliquely connected to the rear end of the main output shaft. A walking input shaft and a transition shaft are sequentially arranged in the walking box from top to bottom. A walking input helical gear matching with the second helical gear is arranged on the walking input shaft. A walking output straight gear is also arranged on the walking input shaft. A transition double gear is arranged on the transition shaft. The large gear of the transition double gear meshes with the walking output straight gear. The small gear of the transition double gear meshes with the power output gear.

[0015] Preferably, a main clutch is further included. An input shaft and a shift shaft are also arranged in the main shaft box. The output end of the engine assembly is connected to one end of the input shaft through the main clutch. A main output gear is fixedly arranged at the other end of the input shaft. A main input gear meshing with the main output gear is arranged at one end of the shift shaft. A shift four - gear is also connected to the shift shaft through a spline. The shift four - gear is the first gear, the second gear, the third gear, and the fourth gear from front to back in sequence. The first gear cooperates with the large tool gear of the tool double gear. The small tool gear of the tool double gear cooperates with the second gear.

[0016] Preferably, a walking input straight gear and a walking input double gear are sequentially arranged on the second sleeve from front to back. The walking input straight gear cooperates with the fourth gear. The small walking gear of the walking input double gear is consistent with the walking input straight gear. The large walking gear cooperates with the third gear. The input shaft is a smooth shaft. A reverse double gear is sleeved on the input shaft. The large reverse gear of the reverse double gear cooperates with the second gear. The small reverse gear of the reverse double gear cooperates with the large walking gear.

[0017] A four - wheel drive micro - tiller adopts the transmission structure described in any one of the above.

[0018] The beneficial effects of the present invention are as follows:

[0019] 1. The power of both the tool box and the traveling box is provided by the main output shaft, which reduces the number of shafts and simplifies the structure. A first sleeve and a second sleeve are respectively arranged on the main output shaft. Through the arrangement of the four-speed shift gear on the shift shaft, the power input of the tool box and the traveling box does not affect each other, which can not only simplify the structure but also better adjust the power distribution to improve safety.

[0020] 2. Among them, the reverse double gear can idle on the input shaft, which can reverse the power provided by the four-speed shift gear for the straight gear of the traveling input, realizing reverse rotation in reverse gear; it can also reduce the number of shafts and simplify the structure.

[0021] 3. Among them, a clutch cable for driving the pressure plate to rotate is arranged on the gearbox. The clutch cable drives the pressure plate to rotate, and then drives the pressure rod to push the clutch pin forward towards the middle of the installation through hole. When the clutch ball enters the conical accommodating part, the engagement between the transmission shaft sleeve and the power distribution shaft fails, and the engagement on the other side is still effective. In this case, operating the steering will be more labor-saving; when the cable is released, due to the restoring force of the return spring, the clutch pin will be reset, and then the engagement between the transmission shaft sleeve and the power distribution shaft will be restored to maintain the transmission efficiency and normal traveling. Description of the Drawings

[0022] Figure 1 It is a schematic cross-sectional view of the gearbox structure of the four-wheel drive micro-tiller of the present invention.

[0023] Figure 2 It is a schematic front view of the gearbox structure of the four-wheel drive micro-tiller of the present invention.

[0024] Figure 3 It is Figure 1 A side cross-sectional view.

[0025] Figure 4 It is a schematic view of the traveling power distribution structure of the gearbox structure of the four-wheel drive micro-tiller of the present invention.

[0026] Figure 5 It is a schematic view of the power distribution shaft structure of the gearbox structure of the four-wheel drive micro-tiller of the present invention.

[0027] Figure 6 It is Figure 2 An enlarged schematic view of part B in

[0028] Figure 7 It is a schematic top view of the gearbox structure of the four-wheel drive micro-tiller of the present invention.

[0029] Description of the Reference Numerals:

[0030] Spindle box 1, main output shaft 101, first helical gear 102, second helical gear 103, first sleeve 104, tool double gear 105, limit plug 106, second sleeve 107, input shaft 108, shift shaft 109, main output gear 110, main input gear 111, shift four - gear 112, first gear 113, second gear 114, third gear 115, fourth gear 116, tool large gear 117, tool small gear 118, walking input spur gear 119, walking input double gear 120, walking small gear 121, walking large gear 122, reverse double gear 123, reverse large gear 124, reverse small gear 125;

[0031] Engine assembly installation end 2, tool box 3, tool drive shaft 301, power output shaft 302, input helical gear 303, power output bevel gear 304, output helical gear 305,

[0032] Walking box 4, power distribution shaft 401, output half - shaft 402, power output gear 403, transmission shaft sleeve 404, accommodation cavity 405, installation through - hole 406, limit hole 407, return spring 408, clutch pin 409, conical accommodation part 410, pressure plate 411, pressure rod 412, clutch ball 413, distribution gear 414, spring installation section 415, clutch pin installation section 416, mounting seat 417, walking input shaft 418, transition shaft 419, walking input helical gear 420, transition double gear 422, main clutch 5. Specific embodiments

[0033] The following elaborates on the preferred embodiments of the present invention in conjunction with the attached drawings, so that the advantages and features of the present invention can be more easily understood by those skilled in the art, thereby making the protection scope of the present invention more clearly defined. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts fall within the protection scope of the present invention.

[0034] As Figure 1-7 shown:

[0035] A four - wheel drive micro - tiller gearbox structure, as Figure 1As shown in the figure, it includes a headstock 1. The left end of the headstock 1 is an installation end 2 for the engine assembly, and the installation end for the engine assembly is used for installing diesel engines, gasoline engines and their fuel tanks. The lower left part of the headstock 1 is connected with a tool box 3 through a flange or bolts. The lower right end of the headstock 1 is connected with a traveling box 4 through bolts or flange ends. A main output shaft 101 is connected in the headstock 1 through bearings. A first helical gear 102 and a second helical gear 103 are respectively arranged at the front end and the rear end of the main output shaft 101. The first helical gear 102 is used to drive the power input of the tool box 3; the second helical gear 103 is used to drive the power input of the traveling box 4. In this embodiment, the first helical gear 102 and the second helical gear 103 are used as power inputs. The advantage of this is that it can improve the integration of the transmission, reduce the floor area and volume of the transmission.

[0036] Specifically, as Figure 2 shown, a first sleeve 104 is sleeved on the front end of the main output shaft 101. The main output shaft 101 and the first sleeve 104 are connected through bearings. The first helical gear 103 is integrally formed or directly machined at the right end of the first sleeve 104. A tool double gear 105 is also connected or integrally formed on the left side of the outer surface of the first sleeve 104 through a key. Specifically, in order to prevent the first sleeve 104 from axially sliding during operation and affecting the transmission, a limit plug 106 is also arranged at the end face of the right end of the first helical gear 103. The limit plug 106 passes through the first helical gear 103 and is threadedly connected with the front end of the main output shaft 101. Among them, when hard ground rough tillage is required, only the large tool gear 117 of the tool double gear 105 needs to be connected to the corresponding power input to achieve greater power with low speed and high torque. When soft ground fine tillage is required, only the small tool gear 118 needs to be connected to the corresponding power input to achieve high speed, with reduced power and increased speed for faster tillage.

[0037] During implementation, as Figure 2 shown, the tool box 3 is fastened to the front end of the headstock 1 through a flange or bolts. A tool drive shaft 301 and a power output shaft 302 are respectively arranged in the tool box 3 through bearings. The tool drive shaft 301 is inclined and arranged in the tool box 3, and the power output shaft 302 is horizontally rotatably connected to the bottom of the tool box 3. A tool power input helical gear 303 is arranged at the upper end of the tool drive shaft 301. The tool power input helical gear 303 is key-connected to the tool drive shaft 301 and limited by a plug, which can well maintain the stability of the tool power input helical gear 303 during power transmission. A power output bevel gear 304 is arranged at the bottom end of the tool drive shaft 301, and an output helical gear 305 is arranged on the power output shaft 302. The power output bevel gear 304 meshes with the tool power output helical gear 305.

[0038] During implementation, as Figure 2, a second sleeve 107 is sleeved on the left end of the main output shaft 101, where, as Figure 1 , the second helical gear 102 is integrally formed or welded to the left end of the second sleeve 107; the traveling box 4 is inclinedly connected to the rear end of the traveling box 4 through a flange or bolts, specifically as Figure 3 , in the traveling box 4, a traveling input shaft 418, an intermediate shaft 419, a power distribution shaft 401, and an output half shaft 402 are sequentially arranged from top to bottom through bearings. A traveling input helical gear 420 that mates with the second helical gear 103 is key-connected or welded to the traveling input shaft 418. The power of the main output shaft 101 is input through the second helical gear 102 and the traveling input helical gear 420. A traveling output spur gear 421 is also key-connected or integrally formed on the traveling input shaft 418; an intermediate double gear 422 is key-connected or integrally formed on the intermediate shaft 419. The large gear of the intermediate double gear 422 meshes with the traveling output spur gear 418. Since the diameters of the two meshing gears are different, a first-stage speed reduction can be achieved. The small gear of the intermediate double gear 422 meshes with the power output gear 403. Among them, the diameter of the power output gear 403 is larger than the small gear of the intermediate double gear 422, achieving a second-stage speed reduction; during implementation, a power distribution shaft 401 and two output half shafts 402 are further arranged at the bottom of the intermediate shaft 419; specifically as Figure 3 and 4As shown, the spline of the power output gear 403 is connected to the middle of the power distribution shaft 401. Transmission shaft sleeves 404 are symmetrically sleeved on both sides of the power distribution shaft 401, and relative rotation can occur between the transmission shaft sleeve 404 and the power distribution shaft 401; the inner surface at the end of the transmission shaft sleeve 404 extends outward to form an accommodation cavity 405; an installation through hole 406 is axially opened at the central position of the power distribution shaft 401, and limiting holes 407 are radially arranged on both sides of the power distribution shaft 401. Specifically, there are 3 - 5 limiting holes on each side, and they are evenly distributed at intervals along the circumferential direction of the power distribution shaft. Among them, the limiting holes 407 communicate with the installation through hole 406, and the limiting holes 407 are opened at the corresponding positions of the accommodation cavity 405; a return spring 408 is arranged in the middle of the installation through hole 406, and clutch pins 409 are arranged at both ends in the length direction of the installation through hole 406. On the side where the two clutch pins 409 are away from each other, there are conical accommodation parts 410. Pressure plates 411 and pressure rods 412 are also rotatably arranged on the outer surfaces on both sides of the traveling box 4. One end of the pressure rod 412 abuts against the pressure plate 411, and the other end of the pressure rod 412 passes through the outer wall and is connected to the clutch pin 409; clutch beads 413 are arranged in the limiting holes 407. When traveling, the clutch beads 413 abut against the clutch pin 409 and the transmission shaft sleeve 404 on the upper and lower sides; distribution teeth 414 are arranged on the outer surfaces of the transmission shaft sleeves 404, and teeth meshing with the distribution teeth 414 are also arranged on the two transmission half shafts 402; Specifically, during implementation, a clutch cable for driving the pressure plate 411 to rotate is arranged on the gearbox. Among them, the clutch cable drives the pressure plate 411 to rotate, and then drives the pressure rod 412 to push the clutch pin forward towards the middle of the installation through hole 406. When the clutch bead 413 enters the conical accommodation part 410, the engagement between the transmission shaft sleeve 404 and the power distribution shaft 401 fails, and the engagement on the other side is still effective. In this case, operating the steering will be more labor-saving; when the cable is released, due to the restoring force of the return spring, the clutch pin will be driven to reset, and then the engagement between the transmission shaft sleeve and the power distribution shaft will be restored to maintain the transmission efficiency and normal operation.

[0039] During implementation, such as Figure 5 、 6As shown in Figures 6 and 7, it also includes a main clutch 5. An input shaft 108 and a shift shaft 109 are also arranged in the main gearbox 1. The output end of the engine assembly 2 is connected to the left end of the input shaft 108 through the main clutch 5. A main output gear 110 is integrally formed at the right end of the input shaft 108. A main input gear 111 meshing with the main output gear 110 is arranged at the right end of the shift shaft 109. The power of the input shaft 108 is transmitted to the shift shaft 109 through the main output gear 110 and the main input gear 111. A shift four-tooth gear 112 is also connected to the shift shaft 109 through a spline. The shift four-tooth gear 112 is successively the first tooth 113, the second tooth 114, the third tooth 115 and the fourth tooth 116 from front to back. The first tooth 113 cooperates with the large tool tooth 117 of the tool double-tooth gear 105, and the small tool tooth 118 of the tool double-tooth gear 105 cooperates with the second tooth 114. A walking input straight tooth 119 and a walking input double-tooth gear 120 are successively arranged in the second sleeve 107 from front to back. The walking input straight tooth 119 cooperates with the fourth tooth 116. The small walking tooth 121 of the walking input double-tooth gear 120 is aligned with the walking input straight tooth 119, and the large walking tooth 122 thereof cooperates with the third tooth 115. The input shaft 108 is a smooth shaft. A reverse double-tooth gear 123 is sleeved on the input shaft 108. The large reverse tooth 124 of the reverse double-tooth gear 123 cooperates with the second tooth 114, and the small reverse tooth 125 of the reverse double-tooth gear 123 cooperates with the large walking tooth 122.

[0040] A four-wheel drive micro-tiller adopts the gearbox structure described in any one of the above.

[0041] The basic principle and advantages of this solution are as follows:

[0042] Advantages: The power of the tool box 3 and the walking box 4 is provided by the main output shaft 101, which reduces the number of shafts and simplifies the structure. The first sleeve 104 and the second sleeve 107 are respectively arranged on the main output shaft 101. Through the arrangement of the shift four-tooth gear 112 of the shift shaft 109, the power inputs of the tool box 3 and the walking box 4 do not affect each other, which can not only simplify the structure but also better adjust the power distribution to improve safety. Among them, through the reverse double-tooth gear 123, it can idle on the input shaft 108, which can reverse the power provided by the shift four-tooth gear 112 for the walking input straight tooth 119 to realize reverse rotation. Among them, a clutch cable for driving the rotation of the driving pressure plate 411 is arranged on the gearbox. The clutch cable drives the pressure plate 411 to rotate, and then drives the pressure rod 412 to push the clutch pin towards the middle of the installation through-hole 406. When the clutch bead 413 enters the conical accommodating part 410, the engagement between the transmission shaft sleeve 404 and the power distribution shaft 401 fails, and the engagement on the other side is still effective. In this case, operating the steering will be more labor-saving.

[0043] Implementation principle:

[0044] Such asFigure 7 :

[0045] 1. When the straight spur gear 119 in the walking input meshes with the fourth gear 116, the other teeth of the four-speed shift gear 112 are idling. At this time, the power of the engine only provides power for the walking box 4, that is, it is used for walking;

[0046] 2. When the four-speed shift gear 112 moves to the right, the third gear 115 meshes with the large walking gear 122, and the first gear 113 meshes with the large cutter gear 117. At this time, since the diameter of the small walking gear 121 is larger than that of the straight spur gear 119 in the walking input, and the diameter of the fourth gear 116 is larger than that of the third gear 115, the speed is lower than the walking speed in 1 above, and it is used for low-speed walking; the large cutter gear 117 receives power and performs low-speed rotary tillage work, which is suitable for rough tillage of hard land;

[0047] 3. When the four-speed shift gear 112 continues to move to the right, the third gear 115 meshes with the small cutter gear 118 for high-speed rotary tillage, which is suitable for fine tillage, and the fourth gear 116 meshes with the small walking gear 121. At this time, the walking speed is the same as that in 1;

[0048] 4. When reverse gear is needed, such as Figure 6 and 7 , the reverse two-speed gear 123 and the four-speed shift gear 112 are toggled so that the second gear 114 meshes with 124. At this time, the reverse small gear 125 will mesh with the large walking gear 122. Through the setting of the reverse two-speed gear 123, the walking driving force is reversed to achieve reverse gear.

[0049] Although the embodiments of the present invention have been shown and described, for those of ordinary skill in the art, it can be understood that various changes, modifications, substitutions and variations can be made to these embodiments without departing from the principle and spirit of the present invention. The scope of the present invention is defined by the appended claims.

Claims

1. A gearbox structure for a four-wheel drive micro-tillage machine, comprising a spindle box (1), the front end of the spindle box (1) being an engine assembly mounting end (2), a tool box (3) being arranged below the front end of the spindle box (1), a travel box (4) being arranged at the rear end of the spindle box (1), a main output shaft (101) being arranged in the spindle box (1), the front end and the rear end of the main output shaft (101) being respectively provided with a first helical tooth (103) and a second helical tooth (102), the first helical tooth (103) being used for driving the power input of the tool box (3); the second helical tooth (102) being used for driving the power input of the travel box (4), characterized in that: The travel box (4) is provided with a power distribution shaft (401) and two output half shafts (402); a power output tooth (403) is provided in the middle of the power distribution shaft (401); transmission sleeves (404) are sleeved on both sides of the power distribution shaft (401); and a receiving cavity (405) is provided on the inner surface of the transmission sleeve (404); a mounting through hole (406) is axially provided at the center of the power distribution shaft (401); limiting holes (407) are radially provided on both sides of the power distribution shaft (401); the limiting holes (407) are communicated with the mounting through hole (406); a return spring (403) is provided in the middle of the mounting through hole (406). 408), clutch pins (409) are arranged at both ends of the mounting through hole (406) in the length direction, and a conical accommodating portion (410) is arranged on the side where the two clutch pins (409) are far away from each other. The outer surfaces of both sides of the traveling box (4) are also provided with a pressure plate (411) and a pressure rod (412), one end of the pressure rod (412) is in contact with the pressure plate (411), and the other end of the pressure rod (412) passes through the outer wall and is connected to the clutch pin (409); a clutch bead (413) is arranged in the limiting hole (407); and the outer surface of the transmission shaft sleeve (404) is provided with a distribution tooth (414), and the distribution tooth (414) is meshed with the gear teeth on the corresponding output half shaft (402).

2. The gearbox structure of the four-wheel drive micro-tillage machine according to claim 1 is characterized in that: The mounting through hole (406) includes a spring mounting section (415) and a clutch pin mounting section (416), and the aperture of the spring mounting section (415) is smaller than that of the clutch pin mounting section (416); there are multiple limit holes (401) on each side of the power distribution shaft (401), which are evenly spaced and arranged along the circumference of the power distribution shaft (401); the outer surface of the travel box (4) is also provided with a mounting seat (417), and the pressure plate (411) is an L-shaped pressure plate, and one end of the pressure plate (411) is rotatably connected to the mounting seat (417).

3. The gearbox structure of the four-wheel drive micro-tillage machine according to claim 1 is characterized in that: A first sleeve (104) is arranged at the front end of the main output shaft (101); the main output shaft (101) and the first sleeve (104) are connected via a bearing; the first bevel tooth (103) is fixedly arranged on the first sleeve (104); a tool double-linked tooth (105) is also fixedly arranged on the outer surface of the first sleeve (104); a limit screw plug (106) is also arranged on the end surface of the first bevel tooth (103) close to one end of the tool box (3); the limit screw plug (106) passes through the first bevel tooth (103) and is threadedly connected to the front end of the main output shaft (101).

4. The gearbox structure of the four-wheel drive micro-tillage machine according to claim 3 is characterized in that: The tool box (3) is arranged obliquely at the front end of the spindle box (1); a tool drive shaft (301) and a power output shaft (302) are arranged in the tool box (3); a tool power input helical tooth (303) is arranged at the upper end of the tool drive shaft (301); and a power output bevel tooth (304) at the bottom end of the tool drive shaft (301) meshes with a tool power output helical tooth (305) on the power output shaft (302).

5. The gearbox structure of the four-wheel drive micro-tillage machine according to claim 4 is characterized in that: The rear end of the main output shaft (101) is sleeved with a second sleeve (107), and the second helical tooth (102) is arranged at an end of the second sleeve (107) close to the travel box (4); the travel box (4) is obliquely connected to the rear end of the travel box (4), and a travel input shaft (418) and a transition shaft (419) are arranged in sequence from top to bottom in the travel box (4); the travel input shaft (418) is provided with a travel input helical tooth (420) matched with the second helical tooth (102), and the travel input shaft (418) is also provided with a travel output spur tooth (421); the transition shaft (419) is provided with a transition double tooth (422), the large tooth of the transition double tooth (422) is meshed with the travel output spur tooth (418), and the small tooth of the transition double tooth (422) is meshed with the power output tooth (403).

6. The gearbox structure of the four-wheel drive micro-tillage machine according to claim 5 is characterized in that: It also includes a main clutch (5), an input shaft (108) and a shift shaft (109) are arranged in the main shaft box (1), the output end of the engine assembly (2) is connected to one end of the input shaft (108) through the main clutch (5), and the other end of the input shaft (108) is fixedly provided with a main output gear (110); one end of the shift shaft (109) is provided with a main input gear (111) meshing with the main output gear (110); The shift shaft (109) is also connected with a shift quadruple tooth (112) via a spline, wherein the shift quadruple tooth (112) comprises, from front to back, a first tooth (113), a second tooth (114), a third tooth (115) and a fourth tooth (116); the first tooth (113) cooperates with a large tool tooth (117) of the tool double tooth (105), and the small tool tooth (118) of the tool double tooth (105) cooperates with the second tooth (114).

7. The gearbox structure of the four-wheel drive micro-tillage machine according to claim 6 is characterized in that: A travel input spur tooth (119) and a travel input duplex tooth (120) are sequentially arranged on the second sleeve (107) from front to back; the travel input spur tooth (119) cooperates with the fourth tooth (116); the travel small tooth (121) of the travel input duplex tooth (120) is consistent with the travel input spur tooth (119), and the travel large tooth (122) cooperates with the third tooth (115).

8. The gearbox structure of the four-wheel drive micro-tillage machine according to claim 7 is characterized in that: The input shaft (108) is a light shaft, and a reverse gear double-linked tooth (123) is sleeved on the input shaft (108). The reverse gear large tooth (124) of the reverse gear double-linked tooth (123) cooperates with the second tooth (114), and the reverse gear small tooth (125) of the reverse gear double-linked tooth (123) cooperates with the travel large tooth (122).

9. A four-wheel drive micro-tillage machine, characterized in that: A gearbox structure comprising any one of claims 1 to 8.

Images