Gearbox

Abstract

The utility model discloses a gearbox, belongs to the technical field of agricultural machinery, and aims to solve the problem that a special uniflow and unilateral braking steering vehicle is difficult to steer. Comprising a power input transmission assembly, a first output transmission assembly and a second output transmission assembly, harvester stepless speed change walking pumps are arranged on the two sides of a shell respectively, and the two output ends of the power input transmission assembly are correspondingly connected with the input ends of the two harvester stepless speed change walking pumps respectively. The input end of the first output transmission assembly and the input end of the second output transmission assembly are correspondingly connected with the output ends of the two harvester stepless speed change walking pumps respectively. The power input transmission assembly transmits power to the first output transmission assembly and the second output transmission assembly through the two harvester stepless speed change walking pumps, the first output transmission assembly and the second output transmission assembly do not interfere with each other, and the defects caused by braking of a crawler belt on one side during steering are overcome.

Description

Technical Field

[0001] The utility model belongs to the technical field of agricultural machinery, and particularly relates to a gearbox. Background Art

[0002] Single-flow unilateral braking steering is the main steering method adopted by special vehicles such as crawler combine harvesters. The steering principle is to separate the intermediate clutch shaft to brake one side of the crawler to complete the steering, and to complete the steering of various radii by controlling the brakes on the left and right half shafts of the clutch.

[0003] However, there are currently great problems. When one side of the crawler is braked, it produces complete sliding friction on the ground during steering, seriously damaging the paddy field soil; during steering, the braked side of the crawler will cause soil accumulation, resulting in difficult steering, incomplete fuel combustion, and at the same time, due to the market demand for large-feed combine harvesters, increasing the weight of the whole machine under the same chassis length-width ratio will make steering more difficult; during field operations, the travel route needs to be finely adjusted. The traditional unilateral braking steering system uses a point-braking steering method for fine adjustment, which causes relatively serious wear and tear on the internal friction plates and greatly reduces the service life. There is a braking power loss on the inner crawler during steering, and the outer side requires more power from the engine. Once the load increases and the resistance of the single crawler increases, the engine will stall. Summary of the Utility Model

[0004] The purpose of the utility model is to provide a gearbox to solve the problem of difficult steering of single-flow unilateral braking steering special vehicles. The technical solution adopted by the utility model is as follows:

[0005] A gearbox includes a power input transmission component, a first output transmission component, and a second output transmission component. On both sides of the housing, there are respectively provided combine harvester continuously variable travel pumps. The two output ends of the power input transmission component are respectively and correspondingly connected to the input ends of the two combine harvester continuously variable travel pumps, and the input ends of the first output transmission component and the second output transmission component are respectively and correspondingly connected to the output ends of the two combine harvester continuously variable travel pumps.

[0006] Furthermore, the power input transmission assembly includes a first rotating shaft, a second rotating shaft and a third rotating shaft respectively rotatably arranged on the housing, the first rotating shaft, the second rotating shaft and the third rotating shaft are parallel to each other and arranged in sequence, one end of the first rotating shaft protrudes out of the housing, and the end of the first rotating shaft protruding out of the housing is the input end of the power input transmission assembly, the first rotating shaft is sequentially sleeved with a first gear, a second gear and a third gear at intervals, the second rotating shaft is sequentially sleeved with a fourth gear, a fifth gear and a sixth gear, the fourth gear is a double gear, a shift seat is provided on the housing, a shift rod is inserted on the shift seat, and a left gear is provided between the shift rod and the second rotating shaft The right slide is provided with a first shift fork and a second shift fork, the inner end of the shift rod is plugged into and matched with the first shift fork, or is plugged into and matched with the second shift fork, the first shift fork shifts the fourth gear to slide along the second rotating shaft, or the second shift fork shifts the sixth gear to slide along the second rotating shaft, so that the large gear of the first gear and the fourth gear are meshed, or the small gear of the second gear and the fourth gear are meshed, or the third gear and the sixth gear are meshed, both ends of the third rotating shaft are output ends of the power input transmission assembly, both ends of the third rotating shaft protrude out of the shell, the seventh gear is sleeved on the third rotating shaft, and the fifth gear and the seventh gear are meshed.

[0007] Further, the first output transmission assembly includes a fourth shaft, a ninth gear, a tenth gear, an eleventh gear, a twelfth gear, a thirteenth gear and a ninth shaft, the fourth shaft and the ninth shaft are respectively rotatably matched with a side wall of the shell, one end of the fourth shaft protrudes out of the shell, and the end of the fourth shaft protruding out of the shell is the input end of the first output transmission assembly, one end of the ninth shaft protrudes out of the shell, and the end of the ninth shaft protruding out of the shell is the output end of the first output transmission assembly, and a fifth shaft, a sixth shaft, a seventh shaft and an eighth shaft are arranged between the fourth shaft and the ninth shaft, and the fourth shaft, the ninth shaft, the fifth shaft, the sixth shaft, the seventh shaft and the eighth shaft are arranged between the fourth shaft and the ninth shaft The 12th gear is parallel to each other, an eighth gear is provided at one end of the fourth rotating shaft in the housing, the 13th gear is sleeved on one end of the ninth rotating shaft in the housing, the ninth gear is rotatably arranged on the fifth shaft, the tenth gear is rotatably arranged on the sixth shaft, the 11th gear is rotatably arranged on the seventh shaft, the 12th gear is rotatably arranged on the eighth shaft, the ninth gear, the 11th gear and the 12th gear are all double gears, the eighth gear is meshed with the large gear of the ninth gear, the small gear of the ninth gear is meshed with the large gears of the tenth gear and the 11th gear in sequence, the small gear of the 11th gear is meshed with the large gear of the 12th gear, and the small gear of the 12th gear is meshed with the 13th gear.

[0008] Furthermore, the second output transmission assembly has the same structure as the first output transmission assembly and is bilaterally symmetrical.

[0009] Furthermore, the input end of the harvester's continuously variable speed travel pump is connected to the third rotating shaft via a spline sleeve, and the output end of the harvester's continuously variable speed travel pump is connected to the corresponding fourth rotating shaft via a spline sleeve.

[0010] Further, the eighth gear and the fourth rotating shaft are of an integral structure.

[0011] Further, a maintenance opening is provided on the front side of the housing, and the end cover is detachably connected to the housing, and the end cover opens and closes the maintenance opening.

[0012] Further, the infinitely variable speed traveling pump of the harvester is fixed to the housing through a bracket.

[0013] Further, lifting lugs are provided on the housing.

[0014] Compared with the prior art, the beneficial effects of the present utility model are as follows:

[0015] For the power input transmission assembly of the present utility model, the two output ends respectively transmit power to the first output transmission assembly and the second output transmission assembly through two infinitely variable speed traveling pumps of the harvester. Driven by the hydraulic steering system, stepless speed change can be achieved between the two spline shafts of the infinitely variable speed traveling pump of the harvester. The first output transmission assembly and the second output transmission assembly are two sets of independent transmission assemblies and do not interfere with each other. Therefore, when the present utility model is linked with the hydraulic steering system, bilateral drive of the crawlers on both sides of the special vehicle can be realized, so that when a special vehicle such as a crawler combine harvester steers, the crawler on the inner bending side can move forward or backward slowly, solving the drawbacks brought by the braking of one crawler during steering. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 is an axonometric view of the present utility model;

[0017] Figure 2 is a schematic diagram of the cooperation between the power input transmission assembly, the first output transmission assembly and the second output transmission assembly;

[0018] Figure 3 is a transmission principle diagram between the power input transmission assembly, the first output transmission assembly and the second output transmission assembly.

[0019] In the figure, 1. housing, 2. end cover, 3. first output transmission assembly, 4. infinitely variable speed traveling pump of the harvester, 5. power input transmission assembly, 6. shift lever, 7. lifting lug, 8. bracket, 9. second output transmission assembly, 10. third gear, 11. second gear, 12. first gear, 13. fourth gear, 14. fifth gear, 15. sixth gear, 16. second rotating shaft, 17. third rotating shaft, 18. seventh gear, 19. fourth rotating shaft, 20. fifth shaft, 21. ninth gear, 22. sixth shaft, 23. tenth gear, 24. seventh shaft, 25. eleventh gear, 26. eighth shaft, 27. twelfth gear, 28. ninth rotating shaft, 29. thirteenth gear, 30. first rotating shaft, 31. eighth gear. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0020] To make the objectives, technical solutions and advantages of the present utility model clearer and more understandable, the present utility model will be described below through specific embodiments shown in the accompanying drawings. However, it should be understood that these descriptions are merely exemplary and are not intended to limit the scope of the present utility model. In addition, in the following description, descriptions of well-known structures and technologies are omitted to avoid unnecessarily confusing the concept of the present utility model.

[0021] The connections mentioned in the present utility model are divided into fixed connections and detachable connections. The fixed connections, that is, non-detachable connections, include but are not limited to conventional fixed connection methods such as hemming connection, rivet connection, bonding connection, and welding connection. The detachable connections include but are not limited to conventional disassembly methods such as bolt connection, snap connection, pin connection, and hinge connection. When the specific connection method is not clearly defined, it is defaulted that at least one connection method can be found among the existing connection methods to achieve this function, and those skilled in the art can select according to their needs. For example: welding connection is selected for the fixed connection, and bolt connection is selected for the detachable connection.

[0022] The present utility model will be further described in detail below with reference to the accompanying drawings. The following embodiments are explanations of the present utility model, and the present utility model is not limited to the following embodiments.

[0023] Embodiment: As Figures 1 to 3 shown, a transmission includes a power input transmission assembly 5, a first output transmission assembly 3, and a second output transmission assembly 9. On the left and right sides of the housing 1, there are respectively provided harvester continuously variable speed traveling pumps 4. The two output ends of the power input transmission assembly 5 are respectively connected corresponding to the input ends of the two harvester continuously variable speed traveling pumps 4. The input ends of the first output transmission assembly 3 and the second output transmission assembly 9 are respectively connected corresponding to the output ends of the two harvester continuously variable speed traveling pumps 4. The output ends of the first output transmission assembly 3 and the second output transmission assembly 9 are respectively connected corresponding to the input ends of the traveling tracks on both sides.

[0024] The output end of the power input transmission assembly 5 is provided with a driven pulley, and the driven pulley is connected to the driving pulley at the output end of the engine through a number of V-belts. The power of the engine is input through a number of V-belts in the utility model. The two output ends of the power input transmission assembly 5 respectively transmit the power to the first output transmission assembly 3 and the second output transmission assembly 9 through two infinitely variable speed walking pumps 4 for harvesters. The infinitely variable speed walking pump 4 for harvesters has two spline shafts, namely the input end and the output end. The hydraulic oil inlet and outlet of the infinitely variable speed walking pump 4 for harvesters are connected to the hydraulic steering system of the special vehicle and realize linkage. The infinitely variable speed walking pump 4 for harvesters is prior art, and its structure will not be described herein again. Driven by the hydraulic steering system, stepless speed change can be realized between the two spline shafts of the infinitely variable speed walking pump 4 for harvesters, that is, the input end and the output end of the infinitely variable speed walking pump 4 for harvesters can cooperate for forward transmission, can also cooperate for reverse transmission, or disconnect the cooperation to realize zero torque output. The first output transmission assembly 3 and the second output transmission assembly 9 are two sets of independent transmission assemblies and do not interfere with each other. Therefore, when the utility model is linked with the hydraulic steering system, the infinitely variable speed walking pump 4 on the outer side of the turn obtains sufficient positive hydraulic oil supply, and the output end of the infinitely variable speed walking pump 4 on the outer side of the turn well transmits the torque of the input end of the infinitely variable speed walking pump 4, while the infinitely variable speed walking pump 4 on the inner side of the turn cannot obtain sufficient hydraulic oil supply, and the output end of the infinitely variable speed walking pump 4 on the inner side of the turn reduces the torque output of the input end, or outputs in the reverse direction. The power input transmission assembly 5 is connected to the first output transmission assembly 3 and the second output transmission assembly 9 respectively through two infinitely variable speed walking pumps 4 for harvesters, so that bilateral drive of the crawlers on both sides of the special vehicle can be realized, and when a special vehicle such as a tracked combine harvester turns, the crawler on the inner bend side can move forward or backward slowly, solving the drawback brought by the braking of one crawler during turning.

[0025] The two infinitely variable speed walking pumps 4 for harvesters, the first output transmission assembly 3 and the second output transmission assembly 9 of the utility model are independent of each other, which can reduce the manufacturing difficulty, reduce the maintenance difficulty and reduce the accessory cost.

[0026] The power input transmission assembly 5 includes a first rotating shaft 30, a second rotating shaft 16 and a third rotating shaft 17 which are respectively rotatably arranged on the housing 1. The first rotating shaft 30, the second rotating shaft 16 and the third rotating shaft 17 are parallel to each other and arranged in sequence. One end of the first rotating shaft 30 protrudes out of the housing 1. The end of the first rotating shaft 30 protruding out of the housing 1 is the input end of the power input transmission assembly 5. The first rotating shaft 30 is sleeved with a first gear 12, a second gear 11 and a third gear 10 in sequence. The second rotating shaft 16 is sleeved with a fourth gear 13, a fifth gear 14 and a sixth gear 15 in sequence. The fourth gear 13 is a double gear. A shift seat is provided on the housing 1. The shift lever 6 is inserted into the shift seat. A gear is provided between the shift lever 6 and the second rotating shaft 16 for sliding left and right movement. The first shift fork and the second shift fork, the inner end of the shift rod 6 is plugged and matched with the first shift fork, or is plugged and matched with the second shift fork, the first shift fork shifts the fourth gear 13 to slide along the second rotating shaft 16, or the second shift fork shifts the sixth gear 15 to slide along the second rotating shaft 16, so that the large gear of the first gear 12 and the fourth gear 13 are meshed, or the second gear 11 and the small gear of the fourth gear 13 are meshed, or the third gear 10 and the sixth gear 15 are meshed, both ends of the third rotating shaft 17 are output ends of the power input transmission assembly 5, both ends of the third rotating shaft 17 protrude out of the shell 1, the output end of the third rotating shaft 17 is a spline shaft section, the seventh gear 18 is sleeved on the third rotating shaft 17, and the fifth gear 14 and the seventh gear 18 are meshed.

[0027] The gear lever 6 is used for shifting gears. There is a three-speed shifting mode between the first rotating shaft 30 and the second rotating shaft 16. The gear lever 6 shifts the first shift fork or the second shift fork, and then adjusts the position of the sixth gear 15 or the fourth gear 13 relative to the second rotating shaft 16, so that the large gear of the first gear 12 and the fourth gear 13 can be meshed, or the small gear of the second gear 11 and the fourth gear 13 can be meshed, or the third gear 10 and the sixth gear 15 can be meshed. Three groups of meshing gears are formed between the first gear 12 and the fourth gear 13, between the second gear 11 and the small gear of the fourth gear 13, and between the third gear 10 and the sixth gear 15. Only one group of the three groups of meshing gears is meshed at the same time. Since the transmission ratios of the three groups of meshing gears are different, different meshing gears can be adjusted to adjust different output reduction ratios.

[0028] The first output transmission assembly 3 includes a fourth rotating shaft 19, a ninth gear 21, a tenth gear 23, an eleventh gear 25, a twelfth gear 27, a thirteenth gear 29, and a ninth rotating shaft 28. The fourth rotating shaft 19 and the ninth rotating shaft 28 are respectively rotationally engaged with a side wall of the housing 1. One end of the fourth rotating shaft 19 extends out of the housing 1, and the end of the fourth rotating shaft 19 extending out of the housing 1 is the input end of the first output transmission assembly 3 with a spline shaft structure. One end of the ninth rotating shaft 28 extends out of the housing 1, and the end of the ninth rotating shaft 28 extending out of the housing 1 is the output end of the first output transmission assembly 3. A fifth shaft 20, a sixth shaft 22, a seventh shaft 24, and an eighth shaft 26 are provided between the fourth rotating shaft 19 and the ninth rotating shaft 28. The fourth rotating shaft 19, the ninth rotating shaft 28, the fifth shaft 20, the sixth shaft 22, the seventh shaft 24, and the eighth shaft 26 are parallel to each other. One end of the fourth rotating shaft 19 inside the housing 1 is provided with an eighth gear 31. The thirteenth gear 29 is sleeved on one end of the ninth rotating shaft 28 inside the housing 1. The ninth gear 21 is rotatably arranged on the fifth shaft 20. The tenth gear 23 is rotatably arranged on the sixth shaft 22. The eleventh gear 25 is rotatably arranged on the seventh shaft 24. The twelfth gear 27 is rotatably arranged on the eighth shaft 26. The ninth gear 21, the eleventh gear 25, and the twelfth gear 27 are all double gears. The eighth gear 31 meshes with the large gear of the ninth gear 21. The small gear of the ninth gear 21 meshes with the large gears of the tenth gear 23 and the eleventh gear 25 in sequence. The small gear of the eleventh gear 25 meshes with the large gear of the twelfth gear 27. The small gear of the twelfth gear 27 meshes with the thirteenth gear 29.

[0029] This embodiment gives the specific structure of the first output transmission assembly 3. The first output transmission assembly 3 realizes speed reduction through the sequential meshing between the eighth gear 31, the ninth gear 21, the tenth gear 23, the eleventh gear 25, the twelfth gear 27, and the thirteenth gear 29.

[0030] The second output transmission assembly 9 has the same structure as the first output transmission assembly 3 and is symmetric left and right. The second output transmission assembly 9 also includes a fourth rotating shaft 19, a ninth gear 21, a tenth gear 23, an eleventh gear 25, a twelfth gear 27, a thirteenth gear 29, and a ninth rotating shaft 28. The two fourth rotating shafts 19, the two ninth gears 21, the two tenth gears 23, the two eleventh gears 25, the two twelfth gears 27, the two thirteenth gears 29, and the two ninth rotating shafts 28 between the second output transmission assembly 9 and the first output transmission assembly 3 rotate independently respectively. One end of the fourth rotating shaft 19 of the second output transmission assembly 9 extending out of the housing 1 is the input end of the second output transmission assembly 9. One end of the ninth rotating shaft 28 of the second output transmission assembly 9 extending out of the housing 1 is the output end of the second output transmission assembly 9.

[0031] The input end of the stepless speed change walking pump 4 of the harvester is connected to the third rotating shaft 17 through a spline sleeve, and the output end of the stepless speed change walking pump 4 of the harvester is connected to the corresponding fourth rotating shaft 19 through a spline sleeve.

[0032] The eighth gear 31 and the fourth rotating shaft 19 are of an integral structure. Setting the eighth gear 31 and the fourth rotating shaft 19 as an integral structure can minimize the number of teeth of the eighth gear 31 to facilitate setting the overall transmission ratio.

[0033] An inspection opening is provided on the front side of the housing 1, and the end cover 2 is detachably connected to the housing 1, and the end cover 2 opens and closes the inspection opening.

[0034] The stepless speed change walking pump 4 of the harvester is fixed to the housing 1 through a bracket 8.

[0035] Lifting lugs 7 are provided on the housing 1 to facilitate the lifting and transportation of the present utility model.

[0036] The above embodiments are only exemplary descriptions of the present utility model and do not limit its protection scope. Those skilled in the art can also make partial changes to it, as long as they do not exceed the spiritual essence of the present utility model, they are within the protection scope of the present utility model.

Claims

1. A transmission gearbox, characterized in that: The utility model comprises a power input transmission assembly (5), a first output transmission assembly (3) and a second output transmission assembly (9); a continuously variable speed travel pump (4) for a harvester is respectively arranged on both sides of a housing (1); two output ends of the power input transmission assembly (5) are respectively connected to the input ends of two continuously variable speed travel pumps (4) for a harvester; and the input ends of the first output transmission assembly (3) and the second output transmission assembly (9) are respectively connected to the output ends of two continuously variable speed travel pumps (4) for a harvester.

2. The transmission according to claim 1, wherein: The power input transmission assembly (5) comprises a first rotating shaft (30), a second rotating shaft (16) and a third rotating shaft (17) which are rotatably arranged on the housing (1) respectively. The first rotating shaft (30), the second rotating shaft (16) and the third rotating shaft (17) are parallel to each other and arranged in sequence. One end of the first rotating shaft (30) protrudes out of the housing (1). The end of the first rotating shaft (30) protruding out of the housing (1) is the input end of the power input transmission assembly (5). The first rotating shaft (30) is sleeved with a first gear (12), a second gear (11) and a third gear (10) in sequence at intervals. The second rotating shaft (16) is sleeved with a fourth gear (13), a fifth gear (14) and a sixth gear (15) in sequence. The fourth gear (13) is a double gear. A shift seat is provided on the housing (1). A shift rod (6) is inserted into the shift seat. The shift rod (6) and the second gear (15) are sleeved with a first gear (12), a second gear (11) and a third gear (10) in sequence at intervals. A first shift fork and a second shift fork are provided between the rotating shaft (16) for sliding left and right movement. The inner end of the shift rod (6) is plugged and matched with the first shift fork, or plugged and matched with the second shift fork. The first shift fork shifts the fourth gear (13) to slide along the second rotating shaft (16), or the second shift fork shifts the sixth gear (15) to slide along the second rotating shaft (16), so that the first gear (12) and the large gear of the fourth gear (13) are meshed, or the second gear (11) and the small gear of the fourth gear (13) are meshed, or the third gear (10) and the sixth gear (15) are meshed. Both ends of the third rotating shaft (17) are output ends of the power input transmission assembly (5). Both ends of the third rotating shaft (17) protrude outside the housing (1). The third rotating shaft (17) is sleeved with a seventh gear (18), and the fifth gear (14) and the seventh gear (18) are meshed.

3. The transmission according to claim 2, characterized in that: The first output transmission assembly (3) includes a fourth rotating shaft (19), a ninth gear (21), a tenth gear (23), an eleventh gear (25), a twelfth gear (27), a thirteenth gear (29), and a ninth rotating shaft (28). The fourth rotating shaft (19) and the ninth rotating shaft (28) are respectively rotationally engaged with a side wall of the housing (1). One end of the fourth rotating shaft (19) extends out of the housing (1), and the end of the fourth rotating shaft (19) extending out of the housing (1) is the input end of the first output transmission assembly (3). One end of the ninth rotating shaft (28) extends out of the housing (1), and the end of the ninth rotating shaft (28) extending out of the housing (1) is the output end of the first output transmission assembly (3). A fifth shaft (20), a sixth shaft (22), a seventh shaft (24), and an eighth shaft (26) are provided between the fourth rotating shaft (19) and the ninth rotating shaft (28). The fourth rotating shaft (19), the ninth rotating shaft (28), the fifth shaft (20), the sixth shaft (22), the seventh shaft (24), and the eighth shaft (26) are parallel to each other. One end of the fourth rotating shaft (19) inside the housing (1) is provided with an eighth gear (31). The thirteenth gear (29) is sleeved on one end of the ninth rotating shaft (28) inside the housing (1). The ninth gear (21) is rotatably arranged on the fifth shaft (20). The tenth gear (23) is rotatably arranged on the sixth shaft (22). The eleventh gear (25) is rotatably arranged on the seventh shaft (24). The twelfth gear (27) is rotatably arranged on the eighth shaft (26). The ninth gear (21), the eleventh gear (25), and the twelfth gear (27) are all double gears. The eighth gear (31) meshes with the large gear of the ninth gear (21). The small gear of the ninth gear (21) meshes with the large gears of the tenth gear (23) and the eleventh gear (25) in sequence. The small gear of the eleventh gear (25) meshes with the large gear of the twelfth gear (27). The small gear of the twelfth gear (27) meshes with the thirteenth gear (29).

4. The transmission according to claim 3, wherein: The second output transmission assembly (9) has the same structure as the first output transmission assembly (3) and is symmetric left and right.

5. A gearbox according to claim 4, characterized in that: The input end of the harvester continuously variable transmission walking pump (4) is connected to the third rotating shaft (17) through a spline sleeve, and the output end of the harvester continuously variable transmission walking pump (4) is connected to the corresponding fourth rotating shaft (19) through a spline sleeve.

6. A gearbox according to claim 4, characterized in that: The eighth gear (31) and the fourth rotating shaft (19) are of an integral structure.

7. A gearbox according to claim 1, characterized in that: An inspection opening is provided on the front side of the housing (1). The end cover (2) is detachably connected to the housing (1), and the end cover (2) opens and closes the inspection opening.

8. A gearbox according to claim 1, characterized in that: The harvester continuously variable transmission walking pump (4) is fixed to the housing (1) through a bracket (8).

9. A gearbox according to any one of claims 1-8, characterized in that: The housing (1) is provided with a lifting lug (7).

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