Wet clutch gear shifting device for differential driving of crawler tractor

Abstract

The invention discloses a wet-type clutch gear shifting device for differential driving of a crawler tractor, and relates to the technical field of tractors, the wet-type clutch gear shifting device comprises rear transmission box bodies arranged on the two sides of the rear end of a transmission box body assembly, shells are rotationally arranged in the rear transmission box bodies, input shafts are arranged in the front ends of the shells, and the rear transmission box bodies are arranged in the input shafts. A reverse rotation mechanism is arranged between the front end of the shell and the front end of the input shaft, a forward rotation mechanism is arranged between the rear end of the shell and the rear end of the input shaft, a limiting pushing mechanism is arranged in the shell, a hydraulic driving mechanism is arranged between the middle of the shell and the middle of the input shaft, and a reverse gear mechanism is arranged on the rear side of the shell. When the steering device is used, the stable and smooth steering operation process can be achieved, operation and adjustment are convenient, the comfort of steering operation can be improved, and the multiple steering effects can be achieved; and meanwhile, the device is relatively simple and compact in structure, long in service life and free of frequent replacement, and has the effects of high working efficiency and low maintenance cost.

Description

Technical Field

[0001] This application relates to the technical field of tractors, and in particular to a wet clutch shifting device for differential drive of a tracked tractor. Background Technology

[0002] Currently, tractors are an important new generation of power equipment for modern facility agriculture machinery. They are characterized by flexibility, convenience, strong adaptability, high operation quality, and no pollution to crops and the facility environment. They are self-propelled power machines mainly used to pull and drive operating machinery to complete various mobile operations. They are widely used in rural areas of my country to replace manual labor in heavy tasks such as sowing and harvesting.

[0003] In related technologies, the tracked tractor generally includes a tractor body, a transmission housing assembly mounted on the tractor body, track assemblies mounted on both sides of the tractor body, and a steering device installed between the transmission housing assembly and the track assemblies on both sides, through which the steering device can realize the steering action of the entire tractor.

[0004] Regarding the aforementioned technologies, the inventors believe that: the steering device mostly uses a dry steering clutch and is operated by lever; however, when using such a steering device on a tractor, the steering is rough and the steering impact is large, resulting in poor operating comfort; at the same time, the structure of the steering device is relatively complex and its service life is shortened, requiring frequent replacement, which not only affects the working efficiency of the tractor, but also has high maintenance costs. Summary of the Invention

[0005] The purpose of this application is to provide a wet clutch shifting device for differential drive of tracked tractors, in order to solve the problem that in related technologies, the steering device mostly uses a dry steering clutch, which is operated by lever. However, when the tractor is used, the steering is rough and the steering impact is large, resulting in poor operating comfort. At the same time, the structure of the steering device is relatively complex and the service life is shortened, requiring frequent replacement, which not only affects the working efficiency of the tractor, but also has high maintenance costs.

[0006] The wet clutch shifting device for differential drive of tracked tractors provided in this application adopts the following technical solution: A wet clutch shifting device for differential drive of a tracked tractor includes rear transmission housings symmetrically arranged on both sides of the rear end of a transmission housing assembly. Each of the two rear transmission housings has a housing rotatably mounted inside. An input shaft is disposed inside the front end of each housing. A reversing mechanism is disposed between the inside of the housing and the shaft of the input shaft. A forward rotation mechanism is disposed between the inside of the housing and the shaft of the input shaft. A limiting and pushing mechanism is also disposed inside the housing, respectively cooperating with the reversing and forward rotation mechanisms. A hydraulic drive mechanism cooperating with the limiting and pushing mechanism is disposed between the middle of the housing and the middle of the input shaft. A reverse gear mechanism cooperating with the rear end of the input shaft is also disposed on the rear side of the housing.

[0007] Furthermore, the reversing mechanism includes a plurality of retracting friction plates slidably disposed on the inner side of the front end of the housing, a retracting clutch gear rotatably disposed on the outer side of the input shaft that simultaneously meshes with the plurality of retracting friction plates, and a plurality of retracting baffles respectively abutting against the retracting friction plates are also slidably disposed on the inner side of the front end of the housing.

[0008] Furthermore, the forward rotation mechanism includes a plurality of forward friction plates slidably disposed on the inner rear end of the housing, a forward clutch gear is disposed on the outer rear end of the input shaft that simultaneously meshes with the plurality of forward friction plates, and a plurality of forward baffles are slidably disposed on the inner rear end of the housing that respectively abut against the forward friction plates.

[0009] Furthermore, the retracting friction plates and the retracting baffles are designed to be spaced apart from each other, and the forward friction plates and the forward baffles are designed to be spaced apart from each other; the outer sides of both ends of the housing are symmetrically provided with a number of openings, and the outer sides of the retracting baffles and the outer sides of the forward baffles are provided with a number of baffle protrusion groups, the two sides of the baffle protrusion groups respectively abutting against the two sides of the openings.

[0010] Furthermore, the limiting and pushing mechanism includes a retracting pushing ring plate and a forward pushing ring plate symmetrically slidably disposed on the inner side of the middle of the housing. The retracting pushing ring plate abuts against the retracting end friction plate, and the forward pushing ring plate abuts against the forward end friction plate. A plurality of limiting plates that cooperate with the opening are provided on the outer side of the retracting pushing ring plate and the outer side of the forward pushing ring plate. A limiting member is provided between the two corresponding limiting plates. Fixed clamps are provided on the inner side of the front end and the inner side of the rear end of the housing. The two fixed clamps abut against the retracting end baffle and the forward end baffle, respectively.

[0011] Furthermore, the hydraulic drive mechanism includes a piston disposed inside the housing, the output end of the piston abutting against the retracting push ring plate, and a plurality of butterfly springs disposed inside the housing, the butterfly springs abutting against the forward push ring plate.

[0012] Furthermore, the reverse gear mechanism includes a reverse gear frame disposed on the rear side of the housing. The reverse gear frame has several fixed shafts (first type) inside, each of which is rotatably mounted with a double gear sleeve. The reverse gear frame also has several fixed shafts (second type) inside, each of which is rotatably mounted with a reverse gear that meshes with one of the double gear sleeves. An intermediate shaft is rotatably disposed at the rear end of the input shaft. A linkage gear assembly that meshes with the double gear sleeve and the reverse gear is disposed between the front end of the intermediate shaft and the rear end of the input shaft. A planetary reduction assembly is also disposed between the rear end of the intermediate shaft and the rear side of the rear transmission housing.

[0013] Furthermore, the linkage gear assembly includes a first linkage gear disposed on the rear end of the input shaft, the first linkage gear meshing with the double gear sleeve, and a second linkage gear disposed at the front end of the intermediate shaft, the second linkage gear meshing with the reverse gear.

[0014] Furthermore, the planetary reduction assembly includes a gear reducer disk disposed on the rear side of the rear transmission housing, a reduction ring gear disposed inside the gear reducer disk, an output shaft rotatably disposed at the rear end of the intermediate shaft, a planet carrier rotatably disposed on the output shaft, a plurality of gear shafts disposed inside the planet carrier, a planet gear respectively meshing with the reduction ring gear disposed on each of the plurality of gear shafts, and an output gear meshing with the planet gears disposed on the output shaft.

[0015] Furthermore, the front ends of the two input shafts are connected by a connecting component.

[0016] Compared with the prior art, the beneficial effects of this application are as follows: By setting up a structure in which the rear transmission housing, housing, input shaft, reversing mechanism, forward rotation mechanism, limit push mechanism, hydraulic drive mechanism, and reverse gear mechanism work together, the device can achieve a smooth and stable steering operation, with convenient operation and adjustment, thereby improving the comfort of steering operation. It can also achieve a variety of steering effects. At the same time, the structure of the device is relatively simple and compact, with a long service life and no need for frequent replacement, resulting in high work efficiency and low maintenance costs. Attached Figure Description

[0017] Figure 1This is a schematic diagram of the structure of a wet clutch shifting device for differential drive of a tracked tractor according to an embodiment of this application.

[0018] Figure 2 This is a schematic diagram of the internal structure of the transmission housing in an embodiment of this application.

[0019] Figure 3 This is a schematic diagram of the internal structure of the housing in an embodiment of this application.

[0020] Figure 4 This is a schematic diagram of the limiting push mechanism and the hydraulic drive mechanism in the embodiments of this application.

[0021] Figure 5 This is a schematic diagram of the reversing mechanism and the forward rotation mechanism in the embodiments of this application.

[0022] Figure 6 This is a schematic diagram of the hydraulic circuit device according to an embodiment of this application.

[0023] Figure 7 yes Figure 2 An enlarged schematic diagram of part A in the middle.

[0024] Figure 8 This is a schematic diagram of the internal structure of the reverse gear carrier in an embodiment of this application.

[0025] Figure 9 This is a schematic diagram of the structure of the planetary deceleration assembly according to an embodiment of this application.

[0026] Figure 10 This is a schematic diagram of differential steering, brake steering, and stationary steering according to embodiments of this application.

[0027] Explanation of reference numerals in the attached figures: 1. Rear transmission housing; 2. Housing; 21. Reverse end friction plate; 22. Reverse end baffle; 23. Reverse end cavity; 24. Forward end friction plate; 25. Forward end baffle; 26. Forward end cavity; 27. Opening; 28. Baffle protrusion assembly; 29. ​​Reverse pushing ring plate; 210. Forward pushing ring plate; 211. Limiting plate; 212. Limiting component; 213. Fixing clamp; 214. Clamp groove; 215. Piston; 216. Disc spring; 217. Fixing flange; 218. Hydraulic oil inlet; 219. Hydraulic oil outlet; 3. 31. Input shaft; 32. Reverse clutch gear; 33. Forward clutch gear; 34. Linkage gear one; 35. Input shaft oil inlet; 4. Ball expansion plug; 5. Transmission housing assembly; 6. Spline sleeve; 7. Reverse gear carrier; 8. Fixed shaft one; 9. Double gear set; 10. Fixed shaft two; 11. Reverse gear; 12. Intermediate shaft; 13. Linkage gear two; 14. Gear reducer; 15. Reduction ring gear; 16. Output shaft; 17. Planetary carrier; 18. Gear shaft; 19. Planetary gear; 10. Output gear; 11. Drive wheel. Detailed Implementation

[0028] The following is in conjunction with the appendix Figure 1-10 This application will be described in further detail.

[0029] This application discloses a wet clutch shifting device for differential drive of a tracked tractor, referring to... Figure 1 and Figure 2 In this embodiment, the steering device includes a rear transmission housing 1, a housing 2, an input shaft 3, a reversing mechanism, a forward rotation mechanism, a limiting push mechanism, a hydraulic drive mechanism, and a reverse gear mechanism. There are two rear transmission housings 1, symmetrically mounted on both sides of the rear end of the transmission housing assembly 4. There are also two housings 2, symmetrically rotatably mounted inside the two rear transmission housings 1. There are two input shafts 3, with their rear ends extending into the interiors of the two rear transmission housings 1 and rotatably connected to the two housings 2. The front ends of the two input shafts 3 extend into the interior of the transmission housing assembly 4 and are connected to each other via a connecting assembly.

[0030] Specifically, the connecting assembly includes a spline sleeve 5 and clamping strips. The spline sleeve 5 is generally cylindrical, and several clamping strips are evenly installed on the inner wall of the spline sleeve 5. Several clamping grooves are formed on the outer front ends of both input shafts 3, and these grooves engage with the clamping strips, thereby fixing the front ends of the two input shafts 3 together via the spline sleeve 5. Simultaneously, one of the input shafts 3 cooperates with the output end of the transmission housing assembly 4, allowing the output end of the transmission housing assembly 4 to drive the input shaft 3 to rotate. Under the action of the structure formed by the spline sleeve 5, clamping strips, and clamping grooves, both input shafts 3 rotate simultaneously.

[0031] Additionally, refer to Figures 3-6 In this embodiment, two reversing mechanisms are provided, one inside the front end of each of the two housings 2 and the other between the shafts of the two input shafts 3. By providing the reversing mechanisms, the input shafts 3 and housings 2 can achieve the effect of reversing the power output. Specifically, the reversing mechanism includes a retracting friction plate 21, a retracting clutch gear 31, and a retracting baffle 22. The housing 2 has a retraction cavity 23 at its front inner side. Several retraction friction plates 21 are provided, slidably mounted inside the retraction cavity 23. A retraction clutch gear 31 is rotatably mounted on the outer side of the input shaft 3 via a deep groove ball bearing, and simultaneously meshes with the retraction friction plates 21. Several retraction baffles 22 are provided, slidably mounted inside the retraction cavity 23, and abut against the retraction friction plates 21. Specifically, the retraction friction plates 21 and the retraction baffles 22 are spaced apart from each other, and are arranged around the outer side of the input shaft 3.

[0032] At the same time, refer to Figures 3-7In this embodiment, two forward rotation mechanisms are provided, which are respectively located between the inner rear ends of the two housings 2 and the shafts of the two input shafts 3. By setting the forward rotation mechanisms, the forward rotation power output effect of the input shafts 3 and housings 2 can be achieved. Specifically, the forward rotation mechanism includes a forward friction plate 24, a forward clutch gear 32, and a forward baffle 25. The housing 2 has a forward cavity 26 located on the inner rear end. Several forward friction plates 24 are provided, slidably mounted inside the forward cavity 26. A forward clutch gear 32 is mounted on the outer rear end of the input shaft 3 and meshes with the forward friction plates 24. Several forward baffles 25 are provided, slidably mounted inside the forward cavity 26 and abutting against the forward friction plates 24. Specifically, the forward friction plates 24 and the forward baffles 25 are spaced apart and arranged around the outer side of the input shaft 3.

[0033] Better, refer to Figure 3 , Figure 5 as well as Figure 7 In this embodiment, three openings 27 are symmetrically provided on the outer sides of both ends of the housing 2. These openings 27 are respectively connected to the forward cavity 26 and the backward cavity 23. Three baffle protrusion groups 28 are provided on the outer sides of the backward baffles 22 and the forward baffles 25. These baffle protrusion groups 28 extend into the openings 27. Specifically, each baffle protrusion group 28 is provided with two baffle protrusions, and the two baffle protrusions abut against the two sides of the opening 27 respectively, so as to effectively limit the backward baffles 22 and the forward baffles 25.

[0034] More specifically, when the forward end baffles 25 and the forward end friction plates 24 are fully clamped together, the forward end baffles 25 and the forward end friction plates 24 do not rotate relative to each other. Since the forward end friction plates 24 are engaged with the forward end clutch gear 32, when the input shaft 3 rotates, it drives the forward end clutch gear 32 to rotate. The forward end clutch gear 32 then drives the forward end baffles 25 and the forward end friction plates 24 to rotate simultaneously. At this time, since the baffle protrusion group 28 and the inner side of the opening 27 on the housing 2 mutually limit and abut against each other, the forward end baffles 25 drive the entire housing 2 to rotate.

[0035] In addition, refer to Figure 3 , Figure 5 as well as Figure 6In this embodiment, two limiting and pushing mechanisms are provided, each located inside one of the two housings 2, and each limiting and pushing mechanism cooperates with a reversing mechanism and a forward rotating mechanism, respectively. Specifically, the limiting and pushing mechanism includes a retracting pushing ring plate 29, a forward pushing ring plate 210, a limiting plate 211, a limiting member 212, and a fixing clamp 213. The retracting pushing ring plate 29 is slidably installed inside the retracting end cavity 23 of the housing 2, with one side of the retracting pushing ring plate 29 abutting against the retracting end friction plate 21 located at the rearmost end, and the other side abutting against the inner side of the housing 2; the forward pushing ring plate 210 is slidably installed inside the forward end cavity 26 of the housing 2, with one side of the forward pushing ring plate 210 abutting against the forward end friction plate 24 located at the foremost end, and the other side abutting against the inner side of the housing 2.

[0036] Meanwhile, six limiting plates 211 are provided, three of which are installed on the outer side of the retracting push ring plate 29, and the other three are installed on the outer side of the forward push ring plate 210. These limiting plates 211 cooperate with the openings 27 to extend out of the housing 2 along the openings 27. Three limiting members 212 are provided, installed between the limiting plates 211. These limiting members 212 are all bolt and nut mating structures, which securely install corresponding limiting plates 211, thereby connecting the retracting push ring plate 29 and the forward push ring plate 210.

[0037] Clamping grooves 214 are provided on the inner walls of the forward cavity 26 and the rear cavity 23 of the housing 2. Two clamping clamps 213 are provided, and the two clamping clamps 213 are respectively installed in the two clamping grooves 214. The clamping clamp 213 at the front end abuts against the rearmost rear end baffle 22, and the clamping clamp 213 at the rear end abuts against the forward end baffle 25 at the rear end. In this way, by using the rearward pushing ring plate 29 and one clamping clamp 213, the rear end friction plates 21 and the rear end baffle 22, which are designed to be spaced apart, can be limited and clamped. By using the forward pushing ring plate 210 and another clamping clamp 213, the forward end friction plates 24 and the forward end baffle 25, which are designed to be spaced apart, can be limited and clamped.

[0038] Secondly, refer to Figures 3-5In this embodiment, two hydraulic drive mechanisms are provided, each installed between the middle of the two housings 2 and the middle of the two input shafts 3, and each hydraulic drive mechanism cooperates with two limiting push mechanisms. Specifically, the hydraulic drive mechanism includes a piston 215 and a butterfly spring 216. The piston 215 is installed on the inner wall of the rearward end cavity 23 of the housing 2, and is connected to the hydraulic oil supply device in the tractor body. The output end of the piston 215 abuts against the side of the rearward push ring plate 29 facing the forward push ring plate 210. Several butterfly springs 216 are provided, and these butterfly springs 216 are slidably installed in the forward end cavity 26 of the housing 2. The rightmost butterfly spring 216 abuts against the side of the forward push ring plate 210 facing the rearward push ring plate 29. Thus, these butterfly springs 216 are designed to be stacked on the left and right to provide sufficient elastic extension.

[0039] Specifically, refer to Figure 6 In this embodiment, a hydraulic circuit device is also included. This device includes a fixed flange 217 mounted on the end of the housing 2. A hydraulic oil inlet 218 is provided within the fixed flange 217. The hydraulic oil inlet 218 is connected to the output end of a hydraulic oil supply system installed inside the tractor, thereby injecting hydraulic oil into the hydraulic oil inlet 218. An input shaft inlet 34 is provided within the input shaft 3, communicating with the hydraulic oil inlet 218. A hydraulic oil outlet 219 is also provided within the housing 2. The two ends of 219 are respectively connected to the input shaft oil inlet 34 and the retracting end cavity 23. The front end of the input shaft oil inlet 34 is closed and the rear end is equipped with a ball expansion plug 35 to seal the rear end of the input shaft oil inlet 34. Hydraulic oil enters from the hydraulic oil inlet 218 and then enters the hydraulic oil outlet 219 along the input shaft oil inlet 34. At the same time, the hydraulic oil enters the retracting end cavity 23 from the hydraulic oil outlet 219 and pushes the piston 215 outward, thereby starting the piston 215.

[0040] Finally, refer to Figure 3 , Figure 4 as well as Figure 8In this embodiment, two reverse gear mechanisms are provided, each mounted on the rear side of one of the two housings 2, and each of the two reverse gear mechanisms cooperates with the rear ends of the two input shafts 3. Specifically, the reverse gear mechanism includes a reverse gear carrier 6, a first fixed shaft 61, a double gear sleeve 62, a second fixed shaft 63, a reverse gear 64, an intermediate shaft 7, a linkage gear assembly, and a planetary reduction assembly. The reverse gear carrier 6 is mounted on the rear side of the housing 2; several first fixed shafts 61 are provided, each mounted inside the reverse gear carrier 6; several double gear sleeves 62 are provided, each including a sleeve rotatably mounted on the first fixed shaft 61 and two gears mounted on the outer side of the sleeve.

[0041] Several fixed shafts 63 are provided, and these fixed shafts 63 are respectively installed inside the reverse gear carrier 6; several reverse gears 64 are provided, and these reverse gears 64 are rotatably mounted on the fixed shafts 63, and these reverse gears 64 respectively mesh with the gears at the rear end of the double gear sleeves 62. Specifically, the reverse gears 64 and the double gear sleeves 62 are designed to be spaced apart from each other.

[0042] Meanwhile, the intermediate shaft 7 is rotatably mounted at the rear end of the input shaft 3; the linkage gear assembly is located between the front end of the intermediate shaft 7 and the rear end of the forward clutch gear 32, and the linkage gear assembly respectively cooperates with the double gear sleeve 62 and the reverse gear 64. Specifically, in this embodiment, the linkage gear assembly includes a first linkage gear 33 and a second linkage gear 71. A connecting sleeve is installed at the rear end of the forward clutch gear 32, and the connecting sleeve is sleeved on the outside of the input shaft 3. The first linkage gear 33 is mounted on the outer side of the rear end of the connecting sleeve, so that the forward clutch gear 32, the connecting sleeve, and the first linkage gear 33 form a double gear structure, and the first linkage gear 33 simultaneously meshes with the gears at the front end of the double gear sleeve 62; the second linkage gear 71 is mounted on the front end of the intermediate shaft 7, and the second linkage gear 71 simultaneously meshes with the reverse gear 64.

[0043] When the input shaft 3 drives the forward clutch gear 32 to rotate clockwise, the forward clutch gear 32 simultaneously drives the first linkage gear 33 to rotate clockwise. At this time, the first linkage gear 33 simultaneously drives the double gear sets 62 to rotate counterclockwise. The double gear sets 62 then drive the reverse gears 64 to rotate clockwise. Then, the reverse gears 64 simultaneously drive the second linkage gear 71 to rotate counterclockwise. Finally, the second linkage gear 71 drives the intermediate shaft 7 to rotate counterclockwise, thereby realizing the reverse deceleration output process of the intermediate shaft 7.

[0044] More specifically, when the retracting friction plate 21 and the retracting baffle 22 are disengaged from each other, a 1.3mm gap is provided between the foremost retracting baffle 22 and the fixing clamp 213 located in the retracting cavity 23. This gap is the movement distance when the retracting friction plate 21 and the retracting baffle 22 are fully engaged with each other. When hydraulic oil enters, it pushes the piston 215 outward, causing the piston 215 to drive the retracting push ring plate 29 to move. This causes the retracting push ring plate 29 to drive the forward push ring plate 210 to press the disc spring 216 forward and overcome the elastic force of the disc spring 216. This causes the forward end friction plate 24 and the forward end baffle 25 to disengage from each other. When the forward end friction plate 24 is completely disengaged from friction, the retracting end friction plate 21 and the retracting end baffle 22 engage with each other to press the gap to the bottom. As oil continues to enter, the retracting push ring plate 29 continues to move to press the retracting end friction plate 21. This process can successively realize the reverse half-clutch and the fully reverse state.

[0045] Additionally, refer to Figure 3 , Figure 4 as well as Figure 9 In this embodiment, the planetary reduction assembly is installed between the rear end of the intermediate shaft 7 and the rear side of the rear transmission housing 1, and the output end of the planetary reduction assembly cooperates with the track assembly, thereby achieving an effective deceleration effect on the forward and reverse power output of the track assembly.

[0046] Specifically, in this embodiment, the planetary reduction assembly includes a gear reducer 8, a reduction ring gear 81, an output shaft 9, a planetary carrier 91, a gear shaft 92, a planetary gear 93, and an output gear 94. The gear reducer 8 is mounted on the rear side of the rear transmission housing 1; the reduction ring gear 81 is mounted in the middle of the gear reducer 8; the front end of the output shaft 9 is mounted on the rear end of the intermediate shaft 7, and the track assembly includes a drive wheel 95 mounted on the rear end of the output shaft 9; the planetary carrier 91 is rotatably mounted on the shaft of the output shaft 9, and the planetary carrier 91 is located inside the reduction ring gear 81.

[0047] The gear shaft 92 is provided with three shafts, each mounted inside the planetary carrier 91. Three planetary gears 93 are rotatably mounted on the three gear shafts 92, and each planetary gear 93 meshes with the reduction ring gear 81. The output gear 94 is mounted on the front end of the output shaft 9, and simultaneously meshes with the planetary gears 93. This structure, with its gear reducer 8, reduction ring gear 81, output shaft 9, planetary carrier 91, gear shaft 92, planetary gears 93, and output gear 94 working together, effectively reduces the speed of both forward and reverse rotation power output of the track assembly.

[0048] In summary, the solution proposed in this application, through the coordinated structure of the rear transmission housing 1, housing 2, input shaft 3, reversing mechanism, forward rotation mechanism, limit pushing mechanism, hydraulic drive mechanism, and reverse gear mechanism, not only achieves a smooth and stable steering operation during use, but also facilitates operation and adjustment, thereby improving the comfort of steering operation, and can also achieve multiple steering effects. At the same time, the structure of this device is relatively simple and compact, with a long service life and no need for frequent replacement, resulting in high work efficiency and low maintenance costs.

[0049] When forward rotation is required, the oil pressure is zero, the piston 215 stops, and the disc springs 216 compress the forward push ring plate 210 according to their own elastic force. This causes the forward push ring plate 210 to compress the spaced-apart forward end friction plates 24 and forward end baffles 25, making them fully engaged. This ensures that the forward end friction plates 24 and forward end baffles 25 are clamped together with no relative rotation. Simultaneously, the forward end friction plates 24 mesh with the forward end clutch gear 32, and the power from the input shaft 3 drives the forward end clutch gear 32 to rotate. This causes the forward end clutch gear 32 to drive the forward end friction plates 24 and forward end baffles 25 to rotate, thus causing the baffles on the forward end baffles 25 to... The cam assembly 28 drives the entire housing 2 to rotate. Since the reverse gear carrier 6 is installed on the rear side of the housing 2, the housing 2 drives the reverse gear carrier 6 to rotate at the same speed. Since the first linkage gear 33 meshes with the gear at the front end of the double gear set 62, and the gear at the rear end of the double gear set 62 meshes with the reverse gear 64, and the reverse gear 64 meshes with the second linkage gear 71, when the reverse gear carrier 6 rotates at the same speed, the first linkage gear 33, the double gear set 62, the reverse gear 64, and the second linkage gear 71 are in a relatively stationary state. This enables the forward rotation power output of the input shaft 3 to be transmitted to the intermediate shaft 7 at the same speed, so that the intermediate shaft 7 can also achieve a forward rotation power output state. Finally, the intermediate shaft 7 achieves forward rotation deceleration through the planetary reduction assembly.

[0050] When forward half-clutch power output is required, the oil pressure is increased, and piston 215 starts. The output end of piston 215 drives the retracting push ring plate 29 to move. At this time, the retracting push ring plate 29 drives the forward push ring plate 210 to press the disc spring 216 forward, overcoming part of the pressure of the disc spring 216. This causes the forward friction plates 24 and the forward baffles 25 to not be completely engaged, so that the forward friction plates 24 and the forward baffles 25 rotate relative to each other. At this time, the entire housing 2 can still be driven. When the input shaft 3 rotates, the housing 2 drives the reverse gear carrier 6 to rotate. However, due to the relative rotation of the forward friction plate 24 and the forward baffle 25, the reverse gear carrier 6 and the housing 2 rotate at different speeds with the input shaft 3. In this way, when the input shaft 3 outputs power, the forward rotation power output of the input shaft 3 can be transmitted to the intermediate shaft 7, so that the intermediate shaft 7 can also achieve a forward rotation power output state. However, at this time, the input shaft 3 and the intermediate shaft 7 rotate at different speeds. Finally, the intermediate shaft 7 achieves forward rotation half-clutch through the planetary reduction assembly.

[0051] When neutral / braking is required, the oil pressure continues to increase. The output end of the piston 215 continues to drive the reversing push ring plate 29 to move. At this time, the reversing push ring plate 29 continues to drive the forward push ring plate 210 to squeeze the disc spring 216 forward to overcome the full pressure of the disc spring 216. This causes the forward friction plates 24 and the forward baffle 25 to disengage from each other. The forward clutch gear 32 only drives the forward friction plates 24 to rotate, and does not simultaneously drive the forward baffle 25, the housing 2, and the reverse gear frame 6 to rotate. At the same time, the input shaft 3 and the intermediate shaft 7 are rotatably connected, so that the input shaft 3 is in an idling state and cannot transmit power to the intermediate shaft 7. This cuts off the power to the drive wheel 95, thus achieving neutral / braking.

[0052] When reverse half-clutch power output is required, the oil pressure is increased further, causing the output end of piston 215 to drive the retracting ring plate 29 to continue moving. This causes the retracting friction plates 21 and retracting baffles 22 to engage, resulting in relative rotation between them. Simultaneously, the retracting friction plates 21 mesh with the retracting clutch gear 31, and due to the retracting clutch gear 31's rotational connection with the input shaft 3, the housing 2 and reverse gear carrier 6 rotate slowly clockwise relative to the input shaft 3. This causes the power output from the input shaft 3 to drive the forward clutch gear 32 clockwise. When the clock hand rotates clockwise, the forward clutch gear 32 simultaneously drives the first linkage gear 33 to rotate clockwise. At this time, the first linkage gear 33 simultaneously drives the double gear sets 62 to rotate counterclockwise. The double gear sets 62 then drive the reverse gears 64 to rotate clockwise. Then, the reverse gears 64 simultaneously drive the second linkage gear 71 to rotate counterclockwise. Finally, the second linkage gear 71 drives the intermediate shaft 7 to rotate counterclockwise, thereby realizing the reverse deceleration output process of the intermediate shaft 7. Finally, the intermediate shaft 7 is decelerated again in reverse through the planetary reduction assembly, thus realizing the reverse half-clutch power output process.

[0053] When reverse power output is required, the oil pressure is increased, and the output end of the piston 215 continues to drive the retracting push ring plate 29 to move, so that the retracting friction plates 21 and the retracting baffle 22 are fully engaged, so that the retracting friction plates 21 and the retracting baffle 22 do not rotate relative to each other. Under the action of the retracting friction plates 21 meshing with the retracting clutch gear 31, and because the retracting clutch gear 31 is rotatably connected to the input shaft 3, the housing 2 and the reverse gear carrier 6 are in a stationary state. Then, under the action of the meshing of the linkage gear one, the double gear set, the reverse gear, and the linkage gear two, the intermediate shaft 7 rotates counterclockwise, thereby realizing the complete reverse deceleration output process of the intermediate shaft 7. Finally, the intermediate shaft 7 is reversed again by the planetary reduction assembly, thus realizing the complete reverse power output process.

[0054] Specifically, refer to Figure 10 In this embodiment, when differential steering is performed, the hydraulic pressure of the drive half shaft on the inner side of the steering increases to the point that the friction plate 24 and the baffle 25 on the front end are partially engaged, the speed of the drive wheel 95 decreases, while the speed on the outer side of the steering remains unchanged. Differential steering is achieved by the speed difference between the outer and inner sides of the steering.

[0055] When braking and steering are performed, the hydraulic pressure of the inner steering drive half shaft increases until the friction plate 24 and the baffle 25 at the front end disengage, and the speed of the drive wheel 95 drops to zero, thus braking the inner steering drive wheel 95. Meanwhile, the speed of the outer steering wheel remains unchanged, and braking and steering are achieved only through the movement of the outer steering wheel.

[0056] When turning in place, the hydraulic pressure of the inner drive half shaft increases to engage the friction plate 21 and the baffle 22 at the rear end, causing the drive wheel 95 to reverse, while the steering of the outer drive wheel 95 remains unchanged. The rotation speed of the inner and outer drive wheels 95 is controlled by the electro-hydraulic system in the tractor body to achieve turning in place.

[0057] The above description is merely an embodiment of the present invention and does not limit the patent scope of the present invention. Any equivalent structural or procedural transformations made based on the content of the present invention's specification and drawings, or direct or indirect applications in other related technical fields, are similarly included within the patent protection scope of the present invention.

Claims

1. A wet clutch shifting device for differential drive of a tracked tractor, characterized in that: The system includes rear transmission housings (1) symmetrically arranged on both sides of the rear end of the transmission housing assembly (4). Each of the two rear transmission housings (1) has a housing (2) rotatably installed inside. Each of the two housings (2) has an input shaft (3) installed inside its front end. A reversing mechanism is installed between the inside of the housing (2) and the shaft of the input shaft (3). A forward rotation mechanism is installed between the inside of the housing (2) and the shaft of the input shaft (3). A limiting and pushing mechanism that cooperates with the reversing mechanism and the forward rotation mechanism is also installed inside the housing (2). A hydraulic drive mechanism that cooperates with the limiting and pushing mechanism is installed between the middle of the housing (2) and the middle of the input shaft (3). A reverse gear mechanism that cooperates with the rear end of the input shaft (3) is also installed on the rear side of the housing (2).

2. A wet clutch shifting device for differential drive of a tracked tractor according to claim 1, characterized in that: The reversing mechanism includes several retracting friction plates (21) that are slidably disposed on the inner side of the front end of the housing (2). A retracting clutch gear (31) that meshes with several retracting friction plates (21) is rotatably disposed on the outer side of the input shaft (3). Several retracting baffles (22) that abut against the retracting friction plates (21) are also slidably disposed on the inner side of the front end of the housing (2).

3. A wet clutch shifting device for differential drive of a tracked tractor according to claim 2, characterized in that: The forward rotation mechanism includes several forward friction plates (24) that are slidably disposed on the inner rear end of the housing (2). The outer rear end of the input shaft (3) is provided with a forward clutch gear (32) that meshes with several forward friction plates (24) simultaneously. The inner rear end of the housing (2) is also provided with several forward baffles (25) that abut against the forward friction plates (24) respectively.

4. A wet clutch shifting device for differential drive of a tracked tractor according to claim 3, characterized in that: The retracting friction plates (21) and the retracting baffles (22) are designed to be spaced apart from each other, and the forward friction plates (24) and the forward baffles (25) are designed to be spaced apart from each other. The outer sides of both ends of the housing (2) are symmetrically provided with a number of openings (27). The outer sides of the retracting baffles (22) and the outer sides of the forward baffles (25) are provided with a number of baffle protrusion groups (28). The two sides of the baffle protrusion groups (28) abut against the two sides of the openings (27).

5. A wet clutch shifting device for differential drive of a tracked tractor according to claim 4, characterized in that: The limiting and pushing mechanism includes a retracting pushing ring plate (29) and a forward pushing ring plate (210) symmetrically slidably disposed on the inner side of the middle of the housing (2). The retracting pushing ring plate (29) abuts against the retracting end friction plate (21), and the forward pushing ring plate (210) abuts against the forward end friction plate (24). A plurality of limiting plates (211) that cooperate with the opening (27) are provided on the outer side of the retracting pushing ring plate (29) and the outer side of the forward pushing ring plate (210). A limiting member (212) is provided between the two limiting plates (211). A fixing clamp (213) is provided on the inner side of the front end and the inner side of the rear end of the housing (2). The two fixing clamps (213) abut against the retracting end baffle (22) and the forward end baffle (25) respectively.

6. A wet clutch shifting device for differential drive of a tracked tractor according to claim 5, characterized in that: The hydraulic drive mechanism includes a piston (215) disposed inside the housing (2), the output end of the piston (215) abutting against the retracting push ring plate (29), and a plurality of butterfly springs (216) disposed inside the housing (2), the butterfly springs (216) abutting against the forward push ring plate (210).

7. A wet clutch shifting device for differential drive of a tracked tractor according to claim 1, characterized in that: The reverse gear mechanism includes a reverse gear frame (6) disposed on the rear side of the housing (2). The reverse gear frame (6) has several fixed shafts (61) inside. Each of the fixed shafts (61) is rotatably mounted with a double gear sleeve (62). The reverse gear frame (6) also has several fixed shafts (63) inside. Each of the fixed shafts (63) is rotatably mounted with a reverse gear (64) that meshes with the double gear sleeve (62). An intermediate shaft (7) is rotatably disposed at the rear end of the input shaft (3). A linkage gear assembly that meshes with the double gear sleeve (62) and the reverse gear (64) is disposed between the front end of the intermediate shaft (7) and the rear end of the input shaft (3). A planetary reduction assembly is disposed between the rear end of the intermediate shaft (7) and the rear side of the rear transmission housing (1).

8. A wet clutch shifting device for differential drive of a tracked tractor according to claim 7, characterized in that: The linkage gear assembly includes a first linkage gear (33) disposed on the rear end of the input shaft (3), the first linkage gear (33) meshing with the double gear sleeve (62), and a second linkage gear (71) disposed at the front end of the intermediate shaft (7), the second linkage gear (71) meshing with the reverse gear (64).

9. A wet clutch shifting device for differential drive of a tracked tractor according to claim 7, characterized in that: The planetary reduction assembly includes a gear reducer disc (8) disposed on the rear side of the rear transmission housing (1). A reduction ring gear (81) is disposed inside the gear reducer disc (8). An output shaft (9) is rotatably disposed at the rear end of the intermediate shaft (7). A planet carrier (91) is also rotatably disposed on the output shaft (9). A plurality of gear shafts (92) are disposed inside the planet carrier (91). A planet gear (93) is rotatably disposed on each of the plurality of gear shafts (92) and meshes with the reduction ring gear (81). An output gear (94) meshes with the planet gear (93) is disposed on the output shaft (9).

10. A wet clutch shifting device for differential drive of a tracked tractor according to claim 1, characterized in that: The front ends of the two input shafts (3) are connected by a connecting component.

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