Multifunctional riding type mini-tiller

Abstract

The utility model relates to the technical field of agricultural machinery, and discloses a multifunctional riding type mini-tiller which comprises a front gearbox and a rear gearbox, the front gearbox is used for driving front wheels, the rear gearbox is used for driving rear wheels, and a front box main shaft, a front box transition shaft and a front box auxiliary shaft which are meshed with one another are sequentially arranged in the front gearbox along a power transmission path. A rear box main shaft and a rear box auxiliary shaft which are meshed with each other are sequentially arranged in the rear gearbox along a power transmission path, the front box auxiliary shaft and the rear box main shaft are in transmission connection through a cardan shaft, a brake assembly is further arranged in the rear gearbox, the rear box main shaft is sleeved with the brake assembly, and the brake assembly is located at the end, close to the cardan shaft, of the rear box main shaft. By arranging the brake assembly, after the brake pedal is stepped on, the rear box spindle and the rear gearbox shell are rapidly locked, so that the front gearbox and the rear gearbox cannot transmit rotating torsion, braking is conducted from the source of power transmission, and it is guaranteed that the mini-tiller can be braked in time.

Description

Technical Field

[0001] The utility model belongs to the technical field of agricultural machinery, and particularly relates to a multifunctional riding micro-tillage machine. Background Art

[0002] As a miniature agricultural equipment, the micro-tiller's primary function is to cultivate land. It is suitable for various terrains, including mountains, hills, and plains. In addition, the micro-tiller can also be used for various tasks such as ridging, furrowing, weeding, and harvesting. Its wide range of applications has made it an indispensable and important piece of machinery in agricultural production. With the continuous development of related technologies, the micro-tiller has evolved from its original two-wheel drive hand-held structure to a four-wheel drive ride structure, which not only improves the micro-tiller's power and control, but also effectively reduces the labor intensity of the workers.

[0003] Existing micro-tillers brake using a clutch. The clutch's input is connected to the heat engine or engine's output, while the clutch's output is connected to the transmission's input shaft. Existing micro-tillers all use wet friction clutches. The clutch fork pushes the clutch's push plate, tightening the clutch, which in turn compresses the clutch's friction plates, ultimately transmitting clutch power to the transmission's input shaft. When the micro-tiller is no longer in use, releasing the operating handle disengages the clutch fork, which no longer pushes the push plate. The clutch's friction plates are now relaxed, preventing clutch power from being transmitted to the transmission's input shaft, thus braking the micro-tiller.

[0004] However, the existing micro-tiller has the following problems during the braking process: after the clutch fork is released, it takes some time for the clutch to completely disengage from the output shaft. As a result, even after the clutch fork is released, the clutch will still drive the transmission input shaft to rotate for a period of time. During this period, the micro-tiller cannot be stopped, which will pose a threat to the surrounding environment or people. Summary of the Invention

[0005] In view of this, the purpose of the present invention is to provide a multifunctional riding micro-tillage machine to solve the technical problem in the prior art that the brakes cannot be completely applied within a short period of time after braking.

[0006] In order to achieve the above-mentioned purpose, the present invention provides the following technical solutions:

[0007] A multifunctional riding micro-tillage machine includes a front gearbox located at the front of the machine and a rear gearbox located at the rear of the machine, the front gearbox being used to drive the front wheels, and the rear gearbox being used to drive the rear wheels, wherein a front gearbox main shaft, a front gearbox transition shaft, and a front gearbox countershaft that mesh with each other are sequentially provided in the front gearbox along a power transmission path, and a rear gearbox main shaft and a rear gearbox countershaft that mesh with each other are sequentially provided in the rear gearbox along the power transmission path, wherein the front gearbox countershaft and the rear gearbox main shaft are connected to each other through a universal shaft, and a brake assembly is further provided in the rear gearbox, the brake assembly being sleeved on the rear gearbox main shaft and being located at one end of the rear gearbox main shaft that is close to the universal shaft;

[0008] Furthermore, the brake assembly includes a brake housing, which is fixedly connected to the rear box flange. The brake housing is open at one end away from the rear box flange, and a plurality of limiting holes are provided on the side wall thereof. An inner core base is provided in the brake housing, and a gap is left between the inner core base and the inner core base so that relative rotation can occur. A plurality of groups of limiting protrusions are provided on the outer side wall of the inner core base along the circumferential direction, and a guide column is provided in the inner core base along the circumferential direction.

[0009] Furthermore, a plurality of friction plates and steel plates are arranged alternately in the brake housing, the steel plates are located between adjacent friction plates, the friction plates are sleeved on the outside of the limiting protrusions, and the limiting blocks on the peripheral sides of the friction plates are snapped into the limiting holes on the outer wall of the brake housing, so that the friction plates are fixedly connected to the brake housing, and the friction plates and the inner core base can rotate relative to each other; the steel plates are also sleeved on the outside of the limiting protrusions, and the limiting protrusions are snapped into the limiting grooves on the inner side of the steel plates, thereby achieving a fixed connection between the steel plates and the inner core base;

[0010] Furthermore, an inner core gland is provided on the open side of the brake housing, and a countersunk hole is provided on the inner core gland. The free end of the guide column can pass through the countersunk hole, and a clamping bolt is provided in the countersunk hole. The clamping bolt passes through the inner core gland and is threadedly connected to the guide column. The inner core gland is limited by the clamping bolt to prevent the friction plate and the steel plate from detaching from the brake housing, but the inner core gland can still be displaced in the axial direction; a return spring is provided on the outer periphery of the guide column, and the two ends of the return spring are respectively against the inner core gland and the inner core base, and the inner core gland is elastically supported by the return spring;

[0011] Furthermore, the rear box main shaft is rotatably connected to the brake housing, the rear box main shaft is spline-connected to the inner core base, and the rear box main shaft is rotatably connected to the inner core gland; the brake assembly also includes a brake operating lever and a pressure claw arranged on the outer side of the inner core gland, the pressure claw is sleeved on the outer periphery of the brake operating lever and the two are fixedly connected;

[0012] Furthermore, one end of the front box main shaft is connected to the output shaft of the engine, and the front box main shaft is provided with a front box main shaft spur gear, a front box main shaft transition duplex gear, a front box main shaft driving duplex gear and a front box main shaft driven duplex gear in sequence in a direction away from the engine; wherein the front box main shaft spur gear is fixedly connected to the front box main shaft, the front box main shaft transition duplex gear is rotatably connected to the front box main shaft, and the front box main shaft transition duplex gear includes a front box main shaft transition duplex gear large tooth and a front box main shaft transition duplex gear small tooth arranged in sequence in a direction away from the engine; The front box main shaft driving duplex gear is fixedly connected to the front box main shaft, and the front box main shaft driving duplex gear also includes the front box main shaft driving duplex gear large gear and the front box main shaft driving duplex gear small gear, wherein the front box main shaft driving duplex gear small gear is close to the front box main shaft transition duplex gear small gear; the front box main shaft driven duplex gear is rotationally connected to the front box main shaft, and the front box main shaft driven duplex gear includes the front box main shaft driven duplex gear large gear and the front box main shaft driven duplex gear small gear, wherein the front box main shaft driven duplex gear small gear is close to the front box main shaft driving duplex gear large gear;

[0013] Furthermore, a front box transition shaft shift tooth and a front box transition shaft spur gear are sequentially provided on the front box transition shaft in a direction away from the engine, wherein the front box transition shaft shift tooth is a duplex tooth, i.e., comprises a large front box transition shaft shift tooth and a small front box transition shaft shift tooth, wherein the large front box transition shaft shift tooth is close to the engine side, the front box transition shaft shift tooth is spline-connected to the front box transition shaft and the front box transition shaft shift tooth can slide along the front box transition shaft, the front box transition shaft spur gear is fixedly connected to the front box transition shaft, and the front box transition shaft spur gear is meshed with the small driven duplex tooth of the front box main shaft;

[0014] Furthermore, a front box countershaft triplet and a front box countershaft spur gear are sequentially provided on the front box countershaft in the direction away from the engine, a front box countershaft bevel gear is provided at the end of the front box countershaft facing the engine, a spline sleeve is provided between the front box countershaft and the front box countershaft triplet, the spline sleeve is hollow inside and is rotatably connected to the countershaft, a keyway is provided on the outer wall of the spline sleeve and is spline-connected to the front box countershaft triplet, and the rotational connection between the front box countershaft triplet and the front box countershaft is realized through the spline sleeve; the front box countershaft triplet includes a front box countershaft triplet large tooth, a front box countershaft triplet small tooth and a front box countershaft triplet middle tooth arranged in sequence along the direction away from the front box countershaft bevel gear, wherein the front box countershaft triplet large tooth is meshed with the front box main shaft spur gear, and the front box countershaft triplet small tooth is meshed with the front box main shaft transition duplex large tooth.

[0015] The beneficial effects of the present invention are:

[0016] (1) Compared with the existing technology, the cooperation of the front and rear gearboxes can not only meet the walking requirements, but also switch to the appropriate gear according to different working conditions (soil softness, arable land slope and soil moisture, etc.), thereby improving the operation capacity and applicability of the micro-tillage machine; in addition, the rear gearbox main shaft is extended to the outside of the rear gearbox, and the rear gearbox main shaft is used as the power input shaft to drive other machines (such as potato harvesters, rear rotary tillers, etc.), thereby expanding the functions of the micro-tillage machine and increasing the scope of use of the micro-tillage machine;

[0017] (2) By setting the above-mentioned brake assembly, after the brake pedal is stepped on, the rear box main shaft and the rear gearbox housing are quickly locked, so that the front gearbox and the rear gearbox cannot transmit rotational torque, braking is performed from the source of power transmission, ensuring that the micro-tiller can brake in time and stop moving. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] In order to make the purpose, technical solution and beneficial effects of the present invention clearer, the present invention is described with the following drawings:

[0019] Figure 1 This is a schematic diagram of the internal structure of the multifunctional riding micro-tillage machine in the first embodiment of the present utility model;

[0020] Figure 2 This is a schematic diagram of the internal structure of the front gearbox in Example 1 of the present utility model;

[0021] Figure 3 This is a schematic diagram of the structure inside the rear gearbox in the first embodiment of the present invention.

[0022] Figure 4 This is an exploded view of the brake assembly in Example 1 of the present utility model;

[0023] Figure 5 This is a cross-sectional view of the brake assembly in Example 1 of the present invention.

[0024] The following are marked in the accompanying drawings:

[0025] Front gearbox 1, front box main shaft 11, front box main shaft spur gear 111, front box main shaft transition duplex gear 112, front box main shaft transition duplex gear large gear 1121, front box main shaft transition duplex gear small gear 1122, front box main shaft active duplex gear 113, front box main shaft active duplex gear large gear 1131, front box main shaft active duplex gear small gear 1132, front box main shaft driven duplex gear 114, front box main shaft driven duplex gear large gear 1141 , front box main shaft driven double tooth small tooth 1142, front box transition shaft 12, front box transition shaft shift tooth 121, front box transition shaft shift tooth large tooth 1211, front box transition shaft shift tooth small tooth 1212, front box transition shaft spur gear 122, front box countershaft 13, spline sleeve 131, front box countershaft triple tooth 132, front box countershaft triple tooth large tooth 1321, front box countershaft triple tooth small tooth 1322, front box countershaft triple tooth middle tooth 13 23. Front box countershaft spur gear 133, front box countershaft bevel gear 134, rear gearbox 2, rear box mainshaft 21, rear box mainshaft duplex gear 211, rear box mainshaft duplex large gear 2111, rear box mainshaft duplex small gear 2112, rear box mainshaft shift gear 212, rear box countershaft 22, rear box countershaft spur gear 221, rear box countershaft duplex gear 222, rear box countershaft duplex large gear 2221, rear box countershaft duplex small gear 2222 , rear box countershaft bevel gear 223, brake assembly 5, brake housing 501, limiting hole 5011, rear box flange 502, inner core base 503, brake operating lever 504, pressure claw 505, limiting protrusion 506, guide column 507, friction plate 508, limiting block 5081, steel plate 509, limiting groove 5091, inner core pressure cover 510, return spring 511, tightening bolt 512, universal joint 3, engine 4. DETAILED DESCRIPTION

[0026] Example 1, specifically as Figure 1-Figure 5 shown.

[0027] A multifunctional riding micro-tillage machine includes a front gearbox 1 located at the front of the machine and a rear gearbox 2 located at the rear of the machine. The front gearbox 1 is used to drive the front wheels, and the rear gearbox 2 is used to drive the rear wheels. The front gearbox 1 is provided with a front box main shaft 11, a front box transition shaft 12 and a front box secondary shaft 13 that are mutually meshed along the power transmission path. The rear gearbox 2 is provided with a rear box main shaft 21 and a rear box secondary shaft 22 that are mutually meshed along the power transmission path. The front box secondary shaft 13 and the rear box main shaft 21 are connected to each other through a universal joint 3.

[0028] like Figure 1As shown, one end of the front box main shaft 11 is connected to the output shaft of the engine 4, and a clutch assembly is provided between the two for connecting and disconnecting the power input of the engine 4. A front box main shaft spur gear 111, a front box main shaft transition duplex gear 112, a front box main shaft driving duplex gear 113, and a front box main shaft driven duplex gear 114 are provided on the front box main shaft 11 in the direction away from the engine 4. Among them, the front box main shaft spur gear 111 is integrally formed and fixedly connected to the front box main shaft 11, and the front box main shaft transition duplex gear 112 is rotatably connected to the front box main shaft 11, that is, the front box main shaft transition duplex gear 112 can rotate freely on the front box main shaft 11 to form idling, and the front box main shaft transition duplex gear 112 includes a front box main shaft transition duplex gear large tooth 1121 and a front box main shaft transition duplex gear small tooth 1122 arranged in sequence in the direction away from the engine 4; the front box main shaft active duplex gear 113 is fixedly connected to the front box main shaft 11 by a spline, and the front box main shaft active duplex gear 113 is fixedly connected to the front box main shaft 11 by a spline. The coupling gear 113 also includes a large tooth 1131 of the front box main shaft active double-coupled gear and a small tooth 1132 of the front box main shaft active double-coupled gear, wherein the small tooth 1132 of the front box main shaft active double-coupled gear is close to the small tooth 1122 of the front box main shaft transition double-coupled gear; the front box main shaft driven double-coupled gear 114 is rotationally connected to the front box main shaft 11, and the front box main shaft driven double-coupled gear 114 includes a large tooth 1141 of the front box main shaft driven double-coupled gear and a small tooth 1142 of the front box main shaft driven double-coupled gear, and the small tooth 1142 of the front box main shaft driven double-coupled gear is close to the large tooth 1131 of the front box main shaft active double-coupled gear.

[0029] A front box transition shaft shift tooth 121 and a front box transition shaft spur gear 122 are sequentially provided on the front box transition shaft 12 in the direction away from the engine 4. The front box transition shaft shift tooth 121 is a duplex tooth, i.e., it includes a large front box transition shaft shift tooth 1211 and a small front box transition shaft shift tooth 1212. The large front box transition shaft shift tooth 1211 is close to the engine 4 side. The front box transition shaft shift tooth 121 is spline-connected to the front box transition shaft 12 and can slide along the front box transition shaft 12. The front box transition shaft spur gear 122 is integrally formed and fixedly connected to the front box transition shaft 12. It should be noted that the front box transition shaft spur gear 122 is meshed with the small duplex tooth 1142 of the front box main shaft driven tooth.

[0030] A front box countershaft triplet 132 and a front box countershaft spur gear 133 are sequentially provided on the front box countershaft 13 in the direction away from the engine 4. A front box countershaft bevel gear 134 is provided at the end of the front box countershaft 13 facing the engine. A spline sleeve 131 is provided between the front box countershaft 13 and the front box countershaft triplet 132. The spline sleeve 131 is hollow inside and is rotatably connected to the countershaft 13. A keyway is provided on the outer wall of the spline sleeve 131 and is spline-connected to the front box countershaft triplet 132. The rotational connection between the front box countershaft triplet 132 and the front box countershaft 13 is achieved through the spline sleeve 131. The front box countershaft triplet teeth 132 include a front box countershaft triplet teeth large tooth 1321, a front box countershaft triplet teeth small tooth 1322 and a front box countershaft triplet teeth medium tooth 1323 arranged in sequence along the direction away from the front box countershaft bevel gear 134, wherein the front box countershaft triplet teeth large tooth 1321 is engaged with the front box main shaft spur gear 111, and the front box countershaft triplet teeth small tooth 1322 is engaged with the front box main shaft transition duplex teeth large tooth 1121.

[0031] The front gearbox 1 has three forward gears and one reverse gear, wherein the forward gears are divided into 3rd gear, 2nd gear and 1st gear in descending order of speed. The power input process corresponding to different gears is as follows.

[0032] When switching to 3rd gear, the small gear 1212 of the front box transition shaft shift gear is engaged with the large gear 1131 of the front box main shaft active double gear. First, the power is transmitted to the small gear 1212 of the front box transition shaft shift gear through the large gear 1131 of the front box main shaft active double gear. Then, the front box transition shaft spur gear 122 transmits the power to the small gear 1142 of the front box main shaft driven double gear. The large gear 1141 of the front box main shaft driven double gear transmits the power to the spur gear 133 of the front box countershaft. Finally, the power is output to the front wheels through the bevel gear 134 of the front box countershaft.

[0033] When switching to 2nd gear, the front box transition shaft shift tooth small tooth 1212 is engaged with the front box main shaft active double tooth small tooth 1132. First, the power is transmitted to the front box transition shaft shift tooth small tooth 1212 through the front box main shaft active double tooth small tooth 1132. Then, the front box transition shaft spur gear 122 transmits the power to the front box main shaft driven double tooth small tooth 1142. The front box main shaft driven double tooth large tooth 1141 then transmits the power to the front box countershaft spur gear 133. Finally, the power is output to the front wheel through the front box countershaft bevel gear 134.

[0034] When switching to 1st gear, the front box transition shaft shift tooth big tooth 1211 is engaged with the front box main shaft transition double tooth small tooth 1122. First, the power is transmitted to the front box countershaft triple tooth big tooth 1321 through the front box main shaft spur gear 111, and is transmitted to the front box main shaft transition double tooth big tooth 1121 by the front box countershaft triple tooth small tooth 1322. Then, the front box main shaft transition double tooth small tooth 1122 transmits the power to the front box transition shaft shift tooth big tooth 1211, the front box transition shaft spur gear 122 transmits the power to the front box main shaft driven double tooth small tooth 1142, the front box main shaft driven double tooth big tooth 1141 then transmits the power to the front box countershaft spur gear 133, and finally is output to the front wheel through the front box countershaft bevel gear 134.

[0035] When switching to reverse gear, the front box transition shaft shift tooth big tooth 1211 and the front box countershaft triplet tooth middle tooth 1323, first, the power is transmitted to the front box countershaft triplet tooth big tooth 1321 through the front box main shaft spur gear 111, and is transmitted to the front box countershaft triplet tooth middle tooth 1323 by the front box transition shaft shift tooth big tooth 1211, then, the front box transition shaft spur gear 122 transmits the power to the front box main shaft driven duplex tooth small tooth 1142, the front box main shaft driven duplex tooth big tooth 1141 then transmits the power to the front box countershaft spur gear 133, and finally output to the front wheel through the front box countershaft bevel gear 134.

[0036] A rear box main shaft 21 is provided with a rear box main shaft duplex gear 211 and a rear box main shaft shift gear 212 in sequence along a direction away from the cardan shaft 3. The rear box main shaft duplex gear 211 is rotationally connected to the rear box main shaft 21. The rear box main shaft duplex gear 211 includes a rear box main shaft duplex gear small tooth 2112 and a rear box main shaft duplex gear large tooth 2111 arranged in sequence along a direction away from the cardan shaft 3. The rear box main shaft shift gear 212 is spline-connected to the rear box main shaft 21 and can slide along the rear box main shaft 21. It is worth emphasizing that the rear box main shaft duplex gear large tooth 2111 is provided with an internal tooth for engaging the rear box main shaft shift gear 212 on the side facing the rear box main shaft shift gear 212.

[0037] A rear box countershaft 22 is provided with a rear box countershaft spur gear 221 and a rear box countershaft duplex gear 222 in sequence along the direction away from the universal joint 3. A rear box countershaft bevel gear 223 is provided at the end of the rear box countershaft 22 facing the universal joint 3. The rear box countershaft spur gear 221 is connected to the rear box countershaft 22 with a flat key, and the rear box countershaft spur gear 221 is engaged with the small tooth 2112 of the rear box main shaft duplex gear; the rear box countershaft duplex gear 222 is rotationally connected to the rear box countershaft 22, and the rear box countershaft duplex gear 222 includes a rear box countershaft duplex gear small tooth 2222 and a rear box countershaft duplex gear large tooth 2221 arranged in sequence along the direction away from the rear box countershaft bevel gear 223, and the rear box countershaft duplex gear small tooth 2222 is engaged with the large tooth 2111 of the rear box main shaft duplex gear.

[0038] The rear gearbox 2 has two forward gears and a neutral gear. The forward gears are divided into fast gear and full gear according to the speed from high to low. The power input process corresponding to different gears is as follows.

[0039] When switching to fast gear, the rear box main shaft shift tooth 212 enters the rear box main shaft double-tooth large tooth 2111 and engages with the internal tooth. First, the power is transmitted to the rear box main shaft double-tooth large tooth 2111 through the rear box main shaft shift tooth 212, and then the rear box main shaft double-tooth small tooth 2112 transmits the power to the rear box countershaft spur gear 221, and finally outputs it to the rear wheel through the rear box countershaft bevel gear 223.

[0040] When switched to full gear, the rear box main shaft shift gear 212 is engaged with the rear box countershaft double-tooth large gear 2221. First, the power is transmitted to the rear box countershaft double-tooth large gear 2221 through the rear box main shaft shift gear 212, and the power is transmitted to the rear box main shaft double-tooth large gear 2111 through the rear box countershaft double-tooth small gear 2222. Then, the rear box main shaft double-tooth small gear 2112 transmits the power to the rear box countershaft spur gear 221, and finally output to the rear wheel through the rear box countershaft bevel gear 223.

[0041] When the rear box main shaft shift tooth 212 is not engaged with any other gear, it is in neutral.

[0042] Through the coordination between the front and rear gearboxes, the walking mode and the tilling mode can be formed, as follows:

[0043] In walking mode, when the road conditions are bad or the tiller needs to be loaded, the front gearbox selects one of the three front forward gears according to the road conditions and usage scenario, and the rear gearbox switches to fast gear; when the road conditions are good or there is no load, the front gearbox selects any of the three front forward gears according to the actual situation, and the rear gearbox switches to neutral gear;

[0044] In tillage mode, the front gearbox switches to one of the three front forward gears according to the softness of the soil, and the rear gearbox switches to slow gear. The front gearbox meets the effect of rotary tillage at a higher speed, while the rear gearbox drives the entire machine forward at a lower speed.

[0045] The coordination of the front and rear gearboxes not only meets the requirements of travel but also enables the shifting of appropriate gears according to different working conditions (such as soil softness, farmland slope, and soil moisture), thereby improving the micro-tiller's operational capacity and applicability. Furthermore, by extending the rear gearbox spindle 21 outside the rear gearbox, it serves as the power input shaft to drive other implements (such as a potato harvester and rear-mounted rotary tiller), thereby expanding the micro-tiller's functionality and extending its scope of use.

[0046] like Figure 4As shown, the rear transmission case 2 also includes a brake assembly 5. The brake assembly 5 is mounted on the rear transmission spindle 21 and is located at the end of the rear transmission spindle 21 near the universal joint 3. The brake assembly 5 comprises a cylindrical brake housing 501. The bottom of the brake housing 501 is threadedly connected to the rear transmission flange 502, securing the brake housing 501 to the rear transmission case 2. The end of the brake housing 501 facing away from the rear transmission flange 502 is open, and its sidewalls are provided with a plurality of retaining holes 5011 spaced evenly along the circumference. An inner core base 503 is located within the brake housing 501, with a gap between the inner core base 503 and the inner core base 503 allowing for relative rotation. Multiple sets of retaining protrusions 506 are circumferentially arranged on the outer wall of the inner core base 503. Four guide posts 507 are circumferentially arranged within the inner core base 503. The guide posts 507 extend in the same direction as the length of the rear transmission spindle 21, and their bottom ends are welded to the bottom plate of the inner core base 503.

[0047] Multiple friction plates 508 and steel plates 509 are arranged alternately within the brake housing 501. In this embodiment, there are five friction plates 508 and four steel plates 509, with the steel plates 509 positioned between adjacent friction plates 508. The friction plates 508 are fitted around the outer limiting protrusions 506, and the limiting blocks 5081 on the sides of the friction plates 508 engage with the limiting holes 5011 on the outer wall of the brake housing 501, thereby securing the friction plates 508 to the brake housing 501 and allowing relative rotation between the friction plates 508 and the inner core base 503. Similarly, the steel plates 509 are fitted around the outer limiting protrusions 506, and the limiting protrusions 506 engage with the limiting grooves 5091 on the inner side of the steel plates 509, thereby securing the steel plates 509 to the inner core base 503.

[0048] An inner core pressure cover 510 is provided on the open side of the brake housing 501, and a countersunk hole is provided on the inner core pressure cover 510. The free end of the guide column 507 can pass through the countersunk hole, and a clamping bolt 512 is provided in the countersunk hole. A threaded hole is provided on the end face of the free end of the guide column 507. The clamping bolt 512 passes through the inner core pressure cover 510 and is threadedly connected to the guide column 507. The inner core pressure cover 510 is limited by the clamping bolt 512 to prevent the friction plate 508 and the steel plate 509 from detaching from the brake housing 501, but the inner core pressure cover 510 can still be displaced axially. In addition, a return spring 511 is provided on the outer periphery of the guide column 507, and the two ends of the return spring 511 are respectively against the inner core pressure cover 510 and the inner core base 503. The return spring 511 elastically supports the inner core pressure cover 510 to ensure that in the non-braking state, the inner core pressure cover 510 will not squeeze the internal friction plate 508 and the steel plate 509, and ensure that there is a designed gap between the friction plate 508, the steel plate 509 and the inner core base 503.

[0049] The rear housing spindle 21 axially extends through the brake assembly 5. The rear housing spindle 21 is rotationally connected to the brake housing 501 via a bearing. The rear housing spindle 21 is splined with the inner core base 503 for synchronous rotation. The rear housing spindle 21 is also rotationally connected to the inner core gland 510. The brake assembly 5 also includes a brake operating lever 504 and a pressure claw 505 disposed on the outside of the inner core gland 510. The pressure claw 505 is sleeved around the brake operating lever 504 and fixedly connected by a latch.

[0050] When braking, the brake lever 504 and the pressure claw 505 are rotated by pulling the brake line. The pressure claw 505 acts on the outer side of the inner core pressure cover 510 and pushes the inner core pressure cover 510 to move along the rear box main shaft 21 toward the inner core base 503. During this process, the return spring 511 is compressed and the inner core pressure cover 510 presses the friction plate 508 and the steel plate 509. Since the friction plate 508 is fixed, the steel plate 509 is restricted in rotation under the resistance of the friction plates 508 on both sides, and the resistance exerted by the friction plate 508 is transmitted to the rear box main shaft 21 through the steel plate 509 and the inner core base 503. The rear box main shaft 21 and the front box main shaft 11 connected to the rear box main shaft 21 are also restricted in rotation, thereby realizing the braking function.

[0051] By setting the above-mentioned brake assembly, after the brake pedal is stepped on, the rear box main shaft 21 and the rear gearbox housing are quickly locked, so that the front gearbox 1 and the rear gearbox 2 cannot transmit rotational torque, braking is performed from the source of power transmission, ensuring that the micro-tiller can brake in time and stop moving.

[0052] Finally, it should be noted that the above preferred embodiments are only used to illustrate the technical solutions of the present invention and are not limiting. Although the present invention has been described in detail through the above preferred embodiments, those skilled in the art should understand that various changes can be made in form and details without departing from the scope defined by the claims of the present invention.

Claims

1. A multifunctional riding micro-tillage machine, characterized in that: It includes a front gearbox located at the front of the vehicle and a rear gearbox located at the rear of the vehicle. The front gearbox is used to drive the front wheels, and the rear gearbox is used to drive the rear wheels. The front gearbox is provided with a front box main shaft, a front box transition shaft and a front box secondary shaft that are meshed with each other along the power transmission path. The rear gearbox is provided with a rear box main shaft and a rear box secondary shaft that are meshed with each other along the power transmission path. The front box secondary shaft and the rear box main shaft are connected by a universal shaft. The rear gearbox is also provided with a brake assembly, which is mounted on the rear box main shaft and is located at the end of the rear box main shaft close to the universal shaft.

2. The multifunctional riding micro-tillage machine according to claim 1, characterized in that: The brake assembly includes a brake housing, which is fixedly connected to the rear box flange. The brake housing is open at one end away from the rear box flange, and a plurality of limiting holes are provided on its side wall. An inner core base is provided in the brake housing, and a gap is left between the two so that relative rotation can occur. Multiple groups of limiting protrusions are provided on the outer side wall of the inner core base along the circumferential direction, and a guide column is provided in the inner core base along the circumferential direction.

3. The multifunctional riding micro-tillage machine according to claim 2, characterized in that: There are multiple friction plates and steel plates arranged alternately in the brake housing. The steel plates are located between adjacent friction plates. The friction plates are sleeved on the outside of the limiting protrusions and the limiting blocks on the peripheral sides of the friction plates are inserted into the limiting holes on the outer wall of the brake housing, so that the friction plates are fixedly connected to the brake housing and the friction plates and the inner core base can rotate relative to each other; the steel plates are also sleeved on the outside of the limiting protrusions and the limiting protrusions are inserted into the limiting grooves on the inside of the steel plates, thereby realizing a fixed connection between the steel plates and the inner core base.

4. The multifunctional riding micro-tillage machine according to claim 3, characterized in that: An inner core pressure cover is provided on the open side of the brake housing, and a countersunk hole is provided on the inner core pressure cover. The free end of the guide column can pass through the countersunk hole. A clamping bolt is provided in the countersunk hole. The clamping bolt passes through the inner core pressure cover and is threadedly connected to the guide column. The inner core pressure cover is limited by the clamping bolt to prevent the friction plate and the steel plate from detaching from the brake housing, but the inner core pressure cover can still be displaced axially; a return spring is provided on the outer periphery of the guide column, and the two ends of the return spring are respectively against the inner core pressure cover and the inner core base, and the inner core pressure cover is elastically supported by the return spring.

5. The multifunctional riding micro-tillage machine according to claim 4, characterized in that: The rear box main shaft is rotatably connected to the brake housing, the rear box main shaft is spline-connected to the inner core base, and the rear box main shaft is rotatably connected to the inner core pressure cover; the brake assembly also includes a brake operating lever and a pressure claw arranged on the outside of the inner core pressure cover, the pressure claw is sleeved on the outer periphery of the brake operating lever and the two are fixedly connected.

6. The multifunctional riding micro-tillage machine according to any one of claims 1 to 5, characterized in that: One end of the front box main shaft is connected to the output shaft of the engine, and the front box main shaft is provided with a front box main shaft spur gear, a front box main shaft transition duplex gear, a front box main shaft active duplex gear and a front box main shaft driven duplex gear in sequence along the direction away from the engine; wherein, the front box main shaft spur gear is fixedly connected to the front box main shaft, the front box main shaft transition duplex gear is rotatably connected to the front box main shaft, and the front box main shaft transition duplex gear includes a front box main shaft transition duplex gear large tooth and a front box main shaft transition duplex gear small tooth arranged in sequence along the direction away from the engine; the front box main shaft The main shaft driving duplex gear is fixedly connected to the front box main shaft, and the front box main shaft driving duplex gear also includes the front box main shaft driving duplex gear large teeth and the front box main shaft driving duplex gear small teeth, wherein the front box main shaft driving duplex gear small teeth are close to the front box main shaft transition duplex gear small teeth; the front box main shaft driven duplex gear is rotationally connected to the front box main shaft, and the front box main shaft driven duplex gear includes the front box main shaft driven duplex gear large teeth and the front box main shaft driven duplex gear small teeth, and the front box main shaft driven duplex gear small teeth are close to the front box main shaft driving duplex gear large teeth.

7. The multifunctional riding micro-tillage machine according to claim 6, characterized in that: The front box transition shaft is provided with front box transition shaft shift teeth and front box transition shaft spur gears in sequence along the direction away from the engine, wherein the front box transition shaft shift teeth are double teeth, i.e., they include front box transition shaft shift teeth large teeth and front box transition shaft shift teeth small teeth, wherein the front box transition shaft shift teeth large teeth are close to the engine side, the front box transition shaft shift teeth are splined to the front box transition shaft and the front box transition shaft shift teeth can slide along the front box transition shaft, the front box transition shaft spur gear is fixedly connected to the front box transition shaft, and the front box transition shaft spur gear is engaged with the driven double teeth small teeth of the front box main shaft.

8. The multifunctional riding micro-tillage machine according to claim 7, characterized in that: The front box countershaft triplet and the front box countershaft spur gear are provided in sequence on the direction away from the engine, and the front box countershaft bevel gear is provided at the end of the front box countershaft facing the engine. A spline sleeve is provided between the front box countershaft and the front box countershaft triplet. The spline sleeve is hollow inside and is rotatably connected to the countershaft. A keyway is provided on the outer wall of the spline sleeve and is spline-connected to the front box countershaft triplet. The rotational connection between the front box countershaft triplet and the front box countershaft is achieved through the spline sleeve; the front box countershaft triplet includes the front box countershaft triplet large teeth, the front box countershaft triplet small teeth and the front box countershaft triplet middle teeth which are arranged in sequence along the direction away from the front box countershaft bevel gear, wherein the front box countershaft triplet large teeth are meshed with the front box main shaft spur gear, and the front box countershaft triplet small teeth are meshed with the front box main shaft transition duplex large teeth.

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