Power reversing and power gear integration module, gearbox and agricultural machinery

Abstract

This invention provides a power reversing and high / low gear integration module, a gearbox, and agricultural machinery. One of the two power shafts is a power input shaft, and the other is a power output shaft. One power shaft has a forward clutch and a reverse clutch sequentially arranged along its axial direction, while the other power shaft has a low-gear clutch and a high-gear clutch sequentially arranged along its axial direction. An intermediate shaft is connected to a first gear set and a second gear set with different speed ratios. The intermediate shaft transmits power from the power input shaft to the power output shaft. The axis of the intermediate shaft is not coplanar with the axes of the two power shafts. At least one of the two power shafts is located on the top of the gearbox housing. This invention integrates power reversing and high / low gear functions through the cooperation of one intermediate shaft and two power shafts, meeting various usage scenarios while fully utilizing the circumferential and axial space of the power reversing and high / low gear integration module.

Description

Technical Field

[0001] This utility model belongs to the field of agricultural machinery technology, and in particular relates to a power reversal and power high and low gear integrated module, a gearbox, and agricultural machinery. Background Technology

[0002] With the development of agricultural technology, agricultural machinery such as tractors is being used more and more widely. Agricultural machinery generally uses a transmission system for power transmission. Existing transmission systems typically use a sequential axial arrangement for power reversal and high / low gears, which places high demands on the axial dimensions of the gearbox, resulting in a non-compact structure and low space utilization.

[0003] To save axial space, existing technologies generally sacrifice high-power reverse gear functionality in exchange for a shorter axial dimension, which to some extent fails to meet the needs of more user scenarios. This results in existing transmission systems being unable to ensure they meet the requirements of a wider range of applications while simultaneously improving space utilization. Utility Model Content

[0004] The main purpose of this utility model is to propose a power reversing and power high and low gear integrated module, a gearbox and agricultural machinery, which aims to solve the technical problems that the transmission device in the prior art cannot adapt to the current use scenarios and occupies a large space.

[0005] To achieve the above objectives, this utility model provides a power reversing and high / low gear integration module for a gearbox. The power reversing and high / low gear integration module includes: two power shafts, one of which is a power input shaft and the other a power output shaft. One power shaft has a forward clutch and a reverse clutch sequentially arranged along its axial direction, while the other power shaft has a low-gear clutch and a high-gear clutch sequentially arranged along its axial direction; an intermediate shaft, which is driven by a first gear set and a second gear set with different speed ratios. The intermediate shaft is used to transmit power from the power input shaft to the power output shaft. The axis of the intermediate shaft is not coplanar with the axes of the two power shafts, and at least one of the two power shafts is located on the top of the gearbox housing.

[0006] In this embodiment of the utility model, the power reversing and high / low gear integration module includes a first gear, a second gear, a third gear, a sixth gear, a seventh gear, an idler shaft with a fourth gear, and a fifth gear meshing with the fourth gear. The first gear set includes the first gear, the second gear, and the third gear; the second gear set includes the fifth gear, the sixth gear, and the seventh gear. The forward clutch engages the first gear, and the reverse clutch engages the fifth gear. The second and sixth gears are located at opposite ends of the intermediate shaft. The first and third gears are both connected to the second gear, and the fourth and seventh gears are both connected to the sixth gear. The speed ratio between the second and third gears is greater than the speed ratio between the sixth and seventh gears. The axes of the intermediate shaft, the idler shaft, and the two power shafts are not coplanar.

[0007] In this embodiment of the invention, the power input shaft and the power output shaft are arranged sequentially in the transverse direction, and the intermediate shaft is located in the transverse direction between the power input shaft and the power output shaft.

[0008] In this embodiment of the invention, the idler shaft is located vertically below the two power shafts, the axis of the power input shaft and the axis of the power output shaft are located in a first plane, and the axis of the idler shaft and the axis of the intermediate shaft are located in a second plane.

[0009] In this embodiment of the invention, the axis of the idler shaft, the axis of the power input shaft, the axis of the intermediate shaft, and the axis of the power output shaft are arranged vertically in sequence, and the axis of the intermediate shaft is located horizontally between the axis of the power input shaft and the axis of the idler shaft.

[0010] This utility model also proposes a gearbox, which includes a main transmission module capable of multi-speed shifting and a power reversal and power high / low gear integration module as described above. The power reversal and power high / low gear integration module transmits power to the main transmission module through the power output axis.

[0011] In this embodiment of the invention, the main transmission module is a four-speed transmission module. The gearbox is used in agricultural machinery and includes a two-speed crawling module that can reduce speed and increase torque, and a three-speed auxiliary transmission module that can shift to three speeds. The main transmission module transmits power to the walking system of the agricultural machinery through the two-speed crawling module and the three-speed auxiliary transmission module.

[0012] In this embodiment of the present invention, the main transmission module includes a main transmission output shaft with a first main shifter, a second main shifter, and a first gear set, a second gear set, a third gear set, and a fourth gear set with different speed ratios. The second main shifter is disposed on the power output shaft. The first main shifter is used to engage the first gear set or the second gear set. The second main shifter is used to engage the third gear set and the fourth gear set. The power input shaft transmits power to the main transmission output shaft through gear sets with different speed ratios.

[0013] In this embodiment of the utility model, the two-speed crawling module includes a crawling transition shaft, a crawling output shaft with a crawling shifter, a transmission gear set, and a climbing gear set for deceleration. The crawling shifter is used to engage the transmission gear set or the climbing gear set. The crawling transition shaft is connected to the main transmission module or the three-speed auxiliary transmission module through the transmission gear set.

[0014] In this embodiment of the present invention, the three-speed auxiliary transmission module is connected to the main transmission module through the two-speed creeping module. The three-speed auxiliary transmission module includes an auxiliary transmission output shaft with a first auxiliary shifter, a second auxiliary shifter, and low-speed gear sets, medium-speed gear sets, and high-speed gear sets with different speed ratios. The second auxiliary shifter is disposed on the creeping output shaft. The first auxiliary shifter is used to engage the low-speed gear set or the medium-speed gear set. The second auxiliary shifter is used to engage or disengage the high-speed gear set. The creeping output shaft is used to transmit power to the auxiliary transmission output shaft through gear sets with different speed ratios.

[0015] In this embodiment of the invention, the second-speed crawling module is connected to the main transmission module via the third-speed auxiliary transmission module. The third-speed auxiliary transmission module includes an auxiliary transmission input shaft with a first auxiliary shifter, a second auxiliary shifter, and low-speed gear sets, medium-speed gear sets, and high-speed gear sets with different speed ratios. The second auxiliary shifter is disposed on the crawling transition shaft. The first auxiliary shifter is used to engage the low-speed gear set or the medium-speed gear set, and the second auxiliary shifter is used to engage the high-speed gear set. The auxiliary transmission input shaft is used to transmit power to the crawling transition shaft through gear sets with different speed ratios.

[0016] In this embodiment of the present invention, the gearbox includes a four-wheel drive mechanism, which includes a front-wheel drive module and a rear-wheel drive module. The main transmission module is used to transmit power to the four-wheel drive mechanism. The front-wheel drive module includes a four-wheel drive clutch, which is used to engage or disengage the front axle of the walking system. The rear-wheel drive module is used to drive the rear axle of the walking system. And / or, the gearbox further includes a PTO module, which includes a PTO input shaft with a PTO clutch, a PTO gear set, and a PTO output shaft. The PTO clutch is used to engage or disengage the power input shaft. The PTO input shaft transmits power to the PTO output shaft through the PTO gear set. The PTO output shaft is used to drive the implements of the agricultural machinery.

[0017] This utility model also proposes an agricultural machine, which includes a gearbox as described above.

[0018] Through the above technical solution, the gearbox provided by this utility model embodiment has the following beneficial effects: The power reversing and high / low gear integration module integrates reversing and high / low gear functions simultaneously through an intermediate shaft and two power shafts. Its simple structure allows it to meet a wider range of application scenarios. Furthermore, by placing the four clutches in pairs on the two power shafts, eliminating the need for any clutches on the intermediate shaft, the circumferential distance between the two power shafts and the intermediate shaft is reduced, improving the circumferential space utilization of the module. Additionally, placing at least one of the two power shafts on the top of the transmission housing reduces the oil churning losses of the clutches on the two power shafts, thereby reducing the heat output of the module and improving its overall efficiency. Moreover, in this embodiment, the axes of the two power shafts and the intermediate shaft are not coplanar, avoiding a three-axis planar configuration. This spatial layout fully utilizes the circumferential space (including lateral and vertical space) and axial space of the module. The power reversing and high / low gear integration module of this utility model integrates power reversing and high / low gear functions through the cooperation of an intermediate shaft and two power shafts. While meeting various usage scenarios, it can also make full use of the circumferential and axial space of the power reversing and high / low gear integration module through a spatially staggered layout, thereby reducing the space occupation of the power reversing and high / low gear integration module.

[0019] Other features and advantages of this invention will be described in detail in the following detailed description section. Attached Figure Description

[0020] The accompanying drawings are provided to illustrate the present invention and form part of the specification. They are used together with the following detailed description to explain the present invention, but do not constitute a limitation thereof. In the drawings: Figure 1 This is a structural schematic diagram of a gearbox according to an embodiment of the present invention; Figure 2 This is a structural schematic diagram of the gearbox according to another embodiment of the present invention; Figure 3 This is a structural schematic diagram of the gearbox according to another embodiment of the present utility model; Figure 4 This is a partial structural schematic diagram of the gearbox according to one embodiment of the present utility model; Figure 5 This is a partial structural schematic diagram of the gearbox according to another embodiment of the present invention; Figure 6 This is a partial structural schematic diagram of the gearbox according to another embodiment of the present utility model; Figure 7 This is a partial structural schematic diagram of the gearbox according to one embodiment of the present utility model; Figure 8 This is a schematic diagram of the PTO module structure of the gearbox according to one embodiment of the present invention; Figure 9 This is a schematic diagram of the power reversal and high / low gear integration module structure of the gearbox according to one embodiment of the present invention.

[0021] Explanation of reference numerals in the attached figures Detailed Implementation

[0022] The specific embodiments of this utility model will be described in detail below with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are for illustration and explanation only and are not intended to limit the scope of this utility model.

[0023] The gearbox 100 according to the present invention is described below with reference to the accompanying drawings.

[0024] like Figures 1 to 4As shown in the embodiment of this utility model, a power reversing and high / low gear integration module is used in a gearbox 100. The power reversing and high / low gear integration module includes an intermediate shaft S2 and two power shafts. One of the two power shafts is a power input shaft S1, and the other is a power output shaft S3. One power shaft is provided with a forward clutch C1 and a reverse clutch C2 in sequence along its own axial direction, and the other power shaft is provided with a low-gear clutch and a high-gear clutch C4 in sequence along its own axial direction. The intermediate shaft S2 is connected to a first gear set and a second gear set with different speed ratios. The intermediate shaft S2 is used to transmit power from the power input shaft S1 to the power output shaft S3. The axis of the intermediate shaft S2 is not coplanar with the axes of the two power shafts. At least one of the two power shafts is located on the top of the gearbox housing of the gearbox 100.

[0025] like Figure 1 As shown, in one embodiment, the forward clutch C1 and reverse clutch C2 in the power reversing and high / low gear integration module are mounted on the power input shaft S1, while the low-gear clutch C3 and high-gear clutch C4 are mounted on the power output shaft S3. Through a first gear set and a second gear set with different speed ratios, the power reversing and high / low gear integration module integrates both reversing and high / low gear functions, thus meeting the needs of different application scenarios. Figure 9 As shown, in another embodiment, the forward clutch C1 and the reverse clutch C2 are mounted on the power output shaft S3, and the low-gear clutch C3 and the high-gear clutch C4 are mounted on the power input shaft S1. Figure 7 As shown, both the forward clutch C1 and the reverse clutch C2 are housed in the first outer hub, with each pair of clutches housed in the same outer hub, which improves the axial structural compactness of the power reversing and power high and low gear integration module. Both the low gear clutch C3 and the high gear clutch C4 are housed in the second outer hub, with each pair of clutches housed in the same outer hub, which further improves the axial space utilization of the power reversing and power high and low gear integration module.

[0026] In this embodiment, the circumferential space of the power reversing and high / low gear integration module may include the lateral and longitudinal spaces of the power reversing and high / low gear integration module, such as... Figure 6 As shown, the horizontal direction is left-right, and the vertical direction is up-down. Both the horizontal and vertical directions are perpendicular to the axis of the power reversing and power high / low gear integration module.

[0027] In this embodiment, the power reversing and high / low gear integration module integrates reversing and high / low gear functions simultaneously through the intermediate shaft S2 and two power shafts. Its simple structure allows it to meet a wider range of application scenarios. Furthermore, by placing the four clutches in pairs on the two power shafts, eliminating the need for any clutches on the intermediate shaft S2, the circumferential distance between the two power shafts and the intermediate shaft S2 is reduced, improving the circumferential space utilization of the power reversing and high / low gear integration module. Additionally, placing at least one of the two power shafts on the top of the gearbox 100 housing reduces the oil churning loss of the clutches on the two power shafts, thereby reducing the heat output of the power reversing and high / low gear integration module and improving its overall efficiency. Moreover, in this embodiment, the axes of the two power shafts and the axis of the intermediate shaft S2 are not coplanar, avoiding a three-axis planar configuration. This spatial layout fully utilizes the circumferential space (including lateral and vertical space) and axial space of the power reversing and high / low gear integration module. In this embodiment, the power reversing and power high / low gear integration module works with one intermediate shaft S2 and two power shafts to integrate power reversing and power high / low gear functions. This satisfies various usage scenarios and, through a spatially staggered layout, fully utilizes the circumferential and axial space of the power reversing and power high / low gear integration module, thereby reducing its space occupation.

[0028] It should be noted that in one embodiment, the forward clutch C1, reverse clutch C2, low-gear clutch C3, and high-gear clutch C4 are all electronically controlled automatic clutches. Under the control of the electro-hydraulic system, the four clutches can slowly disengage and slowly engage. Specifically, during high-gear shifting, the low-gear clutch C3 can slowly disengage, causing the high-gear clutch C4 to slowly engage. This disengagement and engagement ensures continuous and uninterrupted power input during gear shifting.

[0029] Specifically, the power reversing and high / low gear integration module includes a first gear 1, a second gear 2, a third gear 3, a sixth gear 6, a seventh gear 7, an idler shaft S4 with a fourth gear 4, and a fifth gear 5 meshing with the fourth gear 4. The first gear set includes the first gear 1, the second gear 2, and the third gear 3; the second gear set includes the fifth gear 5, the sixth gear 6, and the seventh gear 7. The forward clutch C1 engages the first gear 1, and the reverse clutch C2 engages the fifth gear 5. The second gear 2 and the sixth gear 6 are located at opposite ends of the intermediate shaft S2. The first gear 1 and the third gear 3 are both connected to the second gear 2, and the fifth gear 5 and the fourth gear 4 are both connected to the sixth gear 6. The speed ratio between the second gear 2 and the third gear 3 is greater than the speed ratio between the sixth gear 6 and the seventh gear 7. The axes of the intermediate shaft S2, the idler shaft S4, and the two power shafts are not coplanar.

[0030] like Figures 1 to 3 As shown, the power reversing and power high / low gear integration module in this embodiment includes seven gears, of which the fourth gear 4 is a reversing idler wheel. Reversing is achieved through the reversing idler wheel on the idler wheel shaft S4. The structure is simple and easy to manufacture.

[0031] In this embodiment, the power transmission route of the power reversing and power high and low gear integration module in high gear forward is as follows: forward clutch C1 engages with gear 1, high gear clutch C4 engages with gear 7, the power of power input shaft S1 is transmitted to intermediate shaft S2 via gear 1-gear 2 meshing, and the power of intermediate shaft S2 is transmitted to power output shaft S3 via gear 6-gear 7 meshing. The power transmission route of the power reversal and power high and low gear integration module in low gear forward is as follows: forward clutch C1 engages with gear 1, low gear clutch C3 engages with gear 3, the power of power input shaft S1 is transmitted to intermediate shaft S2 through gear 1-gear 2 meshing, and the power of intermediate shaft S2 is transmitted to power output shaft S3 through gear 2-gear 3 meshing. The power transmission route of the power reversing and power high and low gear integrated module in high gear reverse is as follows: reverse clutch C2 engages with five gear 5, high gear clutch C4 engages with seven gear 7, the power of power input shaft S1 is transmitted to idler shaft S4 through five gear 5-four gear 4 meshing, then to intermediate shaft S2 through four gear 4-six gear 6 meshing, and finally to power output shaft S3 through six gear 6-seven gear 7 meshing; The power transmission route of the power reversing and power high and low gear integrated module in low gear reverse is as follows: the reverse clutch C2 engages with the fifth gear 5, the low gear clutch C3 engages with the third gear 3, the power of the power input shaft S1 is transmitted to the idler shaft S4 through the meshing of the fifth gear 5 and the fourth gear 4, and then through the fourth gear 4 and the sixth gear 6 to the intermediate shaft S2. The power of the intermediate shaft S2 is transmitted to the power output shaft S3 through the meshing of the second gear 2 and the third gear 3.

[0032] In this embodiment, the power reversing and high / low gear integration module can achieve the integration of four gears through the cooperation of seven gears, four clutches and three shafts. The structure is simple and easy to shift gears. Moreover, the axis of the intermediate shaft S2, the axis of the idler wheel shaft S4 and the axes of the two power shafts are not coplanar. The four shafts adopt a spatial layout, which can make full use of the axial and circumferential space in the power reversing and high / low gear integration module compared with the planar layout.

[0033] In one embodiment, such as Figure 4 As shown, the power input shaft S1 and the power output shaft S3 are arranged sequentially in the horizontal direction, and the intermediate shaft S2 is located horizontally between the power input shaft S1 and the power output shaft S3. Specifically, the intermediate shaft S2 can be located vertically below the two power shafts. In this embodiment, the power input shaft S1 and the power output shaft S3 can be arranged side by side with an interval above the intermediate shaft S2. By staggering the intermediate shaft S2 between the power input shaft S1 and the power output shaft S3, the horizontal and vertical space of the power reversing and power high / low gear integration module is fully utilized. In other embodiments, the intermediate shaft S2 can be located vertically in the middle or above the two power shafts.

[0034] Specifically, such as Figure 5 As shown, the idler shaft S4 is vertically located below the two power shafts. The axes of the power input shaft S1 and the power output shaft S3 are located in a first plane, and the axes of the idler shaft S4 and the intermediate shaft S2 are located in a second plane. In one embodiment, the first plane is parallel to the second plane; in another embodiment, the first plane and the second plane intersect. Further, the axes of the power input shaft S1 and the power output shaft S3 are arranged side-by-side laterally in the first plane, and the idler shaft S4 and the intermediate shaft S2 are arranged side-by-side laterally in the second plane. The first and second planes are arranged vertically in sequence, allowing the four shafts to fully utilize the lateral and longitudinal space of the power reversing and power high / low gear integration module, while avoiding excessive axial space occupation.

[0035] It should be noted that, in another embodiment, the axes of the idler shaft S4, the power input shaft S1, the intermediate shaft S2, and the power output shaft S3 are arranged vertically in sequence, and the axis of the intermediate shaft S2 is located laterally between the axes of the power input shaft S1 and the idler shaft S4. In this embodiment, the four shafts are arranged vertically in a staggered manner, and are also staggered horizontally, which maximizes the use of the lateral and longitudinal space of the power reversing and power high / low gear integration module.

[0036] This utility model also proposes a gearbox 100, which includes a main transmission module capable of multi-gear shifting and a power reversing and high / low gear integration module as described above. The power reversing and high / low gear integration module transmits power to the main transmission module via the power output shaft S3. In one embodiment, the main transmission module and the power reversing and high / low gear integration module share the power output shaft S3; in another embodiment, the power output shaft S3 and the main transmission module can be connected via a spline.

[0037] In this embodiment, the main transmission module can be a multi-speed transmission module capable of four-speed or six-speed transmission. By integrating a power reversing and high / low gear integration module into the gearbox 100, and working in conjunction with the multi-speed main transmission module, the gearbox 100 can be further adapted to more application scenarios. Furthermore, in this embodiment, the main transmission module and the power reversing and high / low gear integration module share the power output shaft S3, using the power output shaft S3 as the input shaft of the main transmission module. This saves on additional axial components in the gearbox 100, reducing component costs, simplifying the transmission path, reducing the weight of the gearbox 100, and minimizing its space requirements.

[0038] It should be noted that the main transmission module is a four-speed transmission module. The gearbox 100 is used in agricultural machinery and includes a two-speed crawler module that can reduce speed and increase torque, and a three-speed auxiliary transmission module that can shift to three speeds. The main transmission module transmits power to the walking system of the agricultural machinery through the two-speed crawler module and the three-speed auxiliary transmission module. In this embodiment, the power reversing and power high / low gear integration module integrates power reversing and power high / low gears. Together with the four-speed main transmission module, the two-speed crawler module that can reduce speed and increase torque, and the three-speed auxiliary transmission module, it can achieve 48 forward gears + 48 reverse gears, for a total of 96 gears. The speed range is wider, the operation and driving are more flexible, and the experience is better.

[0039] Understandably, the relative positions between the second-gear crawling module and the third-gear auxiliary transmission module can be set according to actual usage requirements. In one embodiment, power is transmitted sequentially to the walking system of the agricultural machinery through the power reversing and power high / low gear integration module, the main transmission module, the second-gear crawling module, and the third-gear auxiliary transmission module. In another embodiment, power is transmitted sequentially to the walking system of the agricultural machinery through the power reversing and power high / low gear integration module, the main transmission module, the third-gear auxiliary transmission module, and the second-gear crawling module.

[0040] Specifically, the main transmission module includes a main transmission output shaft S5 with a first main shifter T1, a second main shifter T2, and a first gear set, a second gear set, a third gear set, and a fourth gear set with different speed ratios. The second main shifter T2 is disposed on the power output shaft S3. The first main shifter T1 is used to engage the first gear set or the second gear set. The second main shifter T2 is used to engage the third gear set and the fourth gear set. The power input shaft S1 transmits power to the main transmission output shaft S5 through gear sets with different speed ratios.

[0041] In this embodiment, the first main shifter T1 and the second main shifter T2 can be synchronizers or meshing gear sleeves. By setting two shifters on the power output shaft S3 and the main transmission output shaft S5, the large axial space occupied by the two shafts can be avoided. To further utilize the circumferential space of the transmission 100, the first main shifter T1 and the second main shifter T2 are arranged sequentially along the axial direction of the transmission 100. Specifically, the first main shifter T1 is located close to the power reversing and high / low gear integration module, and the first main shifter T1 is located axially between the power reversing and high / low gear integration module and the second main shifter T2. The first gear set may include meshing eight gears 8 and nine gears 9; the second gear set may include meshing ten gears 10 and eleven gears 11; the third gear set may include meshing twelve gears 12 and thirteen gears 13; and the fourth gear set may include meshing fourteen gears 14 and fifteen gears 15. The first and second gear sets are located on opposite sides of the axial direction of the first main shifter T1, while the third and fourth gear sets are located on opposite sides of the axial direction of the second main shifter T2. The first main shifter T1 engages with either the eighth gear (8) or the ninth gear (9), and the second main shifter T2 engages with either the thirteenth gear (13) or the fifteenth gear (15). The eighth gear (8), tenth gear (10), twelfth gear (12), and fourteenth gear (14) are sequentially arranged along the axial direction of the main transmission output shaft S5, while the ninth gear (9), eleventh gear (11), thirteenth gear (13), and fifteenth gear (15) are sequentially arranged along the axial direction of the power output shaft S3. In this embodiment, the four-speed transmission of the main transmission module can be achieved through the structure of four gear sets and two shifters, which is simple in structure and easy to control.

[0042] Furthermore, the second-gear crawling module includes a crawling transition shaft S6, a crawling output shaft S7 with a crawling shifter T3, a transmission gear set, and a climbing gear set for deceleration. The crawling shifter T3 is used to engage the transmission gear set or the climbing gear set. The crawling transition shaft S6 is connected to the main transmission module or the third-gear auxiliary transmission module through the transmission gear set.

[0043] like Figure 1 and Figure 2 As shown, in this embodiment, the crawler shifter T3 can be a synchronizer or a meshing gear sleeve. The transmission gear set can include meshing sixteen-gear 16 and seventeen-gear 17, and the climbing gear set can include meshing eighteen-gear 18 and nineteen-gear 19. The crawler shifter T3 can be used to engage either sixteen-gear 16 or eighteen-gear 18. The transmission gear set and the climbing gear set are located on both sides of the axial direction of the crawler shifter T3. Sixteen-gear 16 and eighteen-gear 18 are arranged sequentially along the axial direction of the crawling output shaft S7, and seventeen-gear 17 and nineteen-gear 19 are arranged sequentially along the axial direction of the crawling transition shaft S6. Under normal conditions where no large torque is required, the crawler shifter T3 is coupled with sixteen-gear 16, and the power is directly transmitted from the main transmission output shaft S5 to the crawling output shaft S7 without deceleration. When the crawler shifter T3 is coupled with eighteen-gear 18, the power transmission becomes main transmission output shaft S5 - crawling transition shaft S6 - crawling output shaft S7, and gears 16-19 participate in deceleration and torque amplification. The second-gear crawling module in this embodiment can obtain greater torque when high torque is required, enabling the gearbox 100 to adapt to more usage scenarios. Furthermore, switching between normal and climbing scenarios can be achieved through just two gear sets, resulting in a simple structure.

[0044] In one embodiment, the three-speed auxiliary transmission module is connected to the main transmission module via the two-speed creeper module. The three-speed auxiliary transmission module includes an auxiliary transmission output shaft S9 with a first auxiliary shifter T4, a second auxiliary shifter T5, and low-gear, medium-gear, and high-gear gear sets with different speed ratios. The second auxiliary shifter T5 is disposed on the creeper output shaft S7. The first auxiliary shifter T4 is used to engage the low-gear or medium-gear gear set, and the second auxiliary shifter T5 is used to engage or disengage the high-gear gear set. The creeper output shaft S7 is used to transmit power to the auxiliary transmission output shaft S9 through gear sets with different speed ratios. Figure 1As shown, the three-speed auxiliary transmission module and the two-speed crawling module share the crawling output shaft S7, which simplifies the structure of the transmission 100, reduces the cost of shaft components, simplifies the power transmission path, reduces the weight of the transmission 100, and reduces the axial space occupied by the transmission 100. The first auxiliary shifter T4 and the second auxiliary shifter T5 can both use synchronizers or meshing gear sleeves. In this embodiment, the low-speed gear set may include meshing gears 20 and 21, the medium-speed gear set may include meshing gears 22 and 23, and the high-speed gear set may include meshing gears 24 and 25. The low-speed gear set, medium-speed gear set, and high-speed gear set can be arranged sequentially along the axial direction of the transmission 100. The first auxiliary shifter T4 engages with either the 21st gear 21 or the 23rd gear 23, and the second auxiliary shifter T5 engages with the 24th gear 24. The 20th, 22nd, and 24th gears are sequentially arranged along the axial direction of the crawling output shaft S7, while the 21st and 23rd gears are sequentially arranged along the axial direction of the secondary transmission output shaft S9. In this embodiment, three-speed transmission can be achieved using three sets of gears and two shifters, resulting in a simple structure. Furthermore, the sequential arrangement of the first auxiliary shifter T4 and the second auxiliary shifter T5 along the axial direction of the transmission 100 reduces the space occupied by the shifters in the axial direction of the transmission 100. In this embodiment, the first auxiliary shifter T4 can be located axially between the crawling shifter T3 and the second auxiliary shifter T5, further improving the utilization rate of the axial space of the transmission 100 and making the structure more compact.

[0045] like Figure 2As shown, in another embodiment, the second-speed crawling module is connected to the main transmission module via the third-speed auxiliary transmission module. The third-speed auxiliary transmission module includes an auxiliary transmission input shaft S8 with a first auxiliary shifter T4, a second auxiliary shifter T5, and low-gear, medium-gear, and high-gear gear sets with different speed ratios. The second auxiliary shifter T5 is disposed on the crawling transition shaft S6. The first auxiliary shifter T4 is used to engage the low-gear gear set or the medium-gear gear set, and the second auxiliary shifter T5 is used to engage the high-gear gear set. The auxiliary transmission input shaft S8 is used to transmit power to the crawling transition shaft S6 through gear sets with different speed ratios. In this embodiment, the third-speed auxiliary transmission module and the second-speed crawling module share the crawling transition shaft S6, which can save on the shaft component cost of the transmission 100. In this embodiment, the second auxiliary shifter T5 can be located axially between the first auxiliary shifter T4 and the crawling shifter T3, making full use of the axial space of the transmission 100. The three-speed auxiliary transmission module in this embodiment may include gears 20, 21, 22, 23, 24, 25, 26, and 27. The main transmission module transmits power to the auxiliary transmission input shaft S8 through the meshing gears 26 and 27. The first auxiliary shifter T4 is disposed on the auxiliary transmission input shaft S8, and the second auxiliary shifter T5 is disposed on the creeping transition shaft S6. The first auxiliary shifter T4 is axially located between the main transmission module and the second auxiliary shifter T5.

[0046] like Figure 1 As shown, the gearbox 100 includes a four-wheel drive mechanism, which includes a front-wheel drive module and a rear-wheel drive module. The main transmission module is used to transmit power to the four-wheel drive mechanism. The front-wheel drive module includes a four-wheel drive clutch C6, which is used to engage or disengage the front axle of the drive system. The rear-wheel drive module is used to drive the rear axle of the drive system. In this embodiment, the front-wheel drive module may include meshing 28-speed gears 28 and 29-speed gears 29. The auxiliary transmission output shaft S9 can output power to the front-wheel drive shaft S12 through the 28-speed gears 28 and 29-speed gears 29. The four-wheel drive clutch C6 is located on the front-wheel drive shaft S12 and can control whether power is input to the front axle. When the four-wheel drive clutch C6 is engaged, the front axle will receive power; otherwise, it will not. In this embodiment, the cooperation between the front-wheel drive module and the rear-wheel drive module enables the switching between four-wheel drive and rear-wheel drive, further meeting the needs of different usage scenarios. The rear drive module may include a rear drive shaft S12 and a differential lock clutch C5. The power input of the rear drive module is the auxiliary transmission output shaft S8, and the power is finally output by the rear drive shaft S12. The auxiliary transmission output shaft S8 and the rear drive shaft S12 contain a bevel gear differential mechanism and a planetary reduction mechanism. The differential lock clutch C5 can control the differential lock state.

[0047] Furthermore, the gearbox 100 also includes a PTO module, which includes a PTO input shaft S10 with a PTO clutch C7, a PTO gear set, and a PTO output shaft S11. The PTO clutch C7 is used to engage or disengage the power input shaft S10. The PTO input shaft S10 transmits power to the PTO output shaft S11 through the PTO gear set. The PTO output shaft S11 is used to drive the implements of the agricultural machinery. Figure 8 As shown, in one embodiment, the PTO module can be a two-stage module, such as... Figure 1 As shown, in another embodiment, the PTO module can be a three-speed module. A first PTO shifter T6 is provided on the PTO input shaft S10, and a second PTO shifter T7 is provided on the PTO output shaft S11. The first PTO shifter T6 and the second PTO shifter T7 can employ synchronizers and meshing sleeves. The PTO module may include meshing gears 30 and 31, 32 and 33, and 34 and 35. The second PTO shifter T7 is used to engage gear 34, and the first PTO shifter T6 is used to engage gear 31 or gear 33. The first PTO shifter T6 is axially located between the PTO clutch C7 and the second PTO shifter T7, which can fully utilize the axial space of the transmission 100. Gears 30, 32, and 34 are arranged sequentially along the axial direction of the PTO input shaft S10, while gears 31, 33, and 35 are arranged sequentially along the axial direction of the PTO output shaft S11. Gears 30 and 31 are first gears, gears 32 and 33 are second gears, and gears 34 and 35 are third gears. The PTO module transmits power to the working implement via the PTO. The PTO clutch C7 controls the opening and closing of the PTO; when the PTO clutch C7 is engaged, the PTO is in the open working state, and vice versa. In this embodiment, the PTO module enables the gearbox 100 to drive the working implement, thus broadening the application scenarios of the gearbox 100.

[0048] This utility model also proposes an agricultural machine, which includes a walking system and a gearbox 100 as described above. The specific structure of the gearbox 100 is as described in the above embodiments. Since the agricultural machine adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here. In one embodiment, the agricultural machine can be applied to a tractor, and the working implement can be the working implement of the tractor, such as a header.

[0049] In the description of this utility model, it should be understood that the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this utility model, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0050] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between them; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0051] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0052] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention.

Claims

1. A power reversing and high / low gear integrated module for a gearbox (100), characterized in that, The power reversing and power high / low gear integration module includes: Two power shafts, one of which is a power input shaft (S1) and the other is a power output shaft (S3). One of the power shafts is provided with a forward clutch (C1) and a reverse clutch (C2) in sequence along its own axis, and the other power shaft is provided with a low gear clutch (C3) and a high gear clutch (C4) in sequence along its own axis. An intermediate shaft (S2) is connected to a first gear set and a second gear set with different speed ratios. The intermediate shaft (S2) is used to transmit power from the power input shaft (S1) to the power output shaft (S3). The axis of the intermediate shaft (S2) is not coplanar with the axes of the two power shafts. At least one of the two power shafts is located on the top of the housing of the gearbox (100).

2. The power commutation and power range integration module of claim 1, wherein, The power reversing and power high / low gear integration module includes a first gear (1), a second gear (2), a third gear (3), a sixth gear (6), a seventh gear (7), an idler shaft (S4) with a fourth gear (4), and a fifth gear (5) meshing with the fourth gear (4). The first gear set includes the first gear (1), the second gear (2), and the third gear (3), and the second gear set includes the fifth gear (5), the sixth gear (6), and the seventh gear (7). The forward clutch (C1) engages the first gear (1), and the reverse clutch (… C2) is used to connect the five gears (5). The two gears (2) and the six gears (6) are respectively located at both ends of the intermediate shaft (S2). The first gear (1) and the third gear (3) are connected to the second gear (2) in a transmission. The fourth gear (4) and the seventh gear (7) are connected to the sixth gear (6) in a transmission. The speed ratio of the second gear (2) and the third gear (3) is greater than the speed ratio of the sixth gear (6) and the seventh gear (7). The axis of the intermediate shaft (S2), the axis of the idler shaft (S4), and the axes of the two power shafts are not coplanar.

3. The power commutation and power range integration module of claim 2, wherein, The power input shaft (S1) and the power output shaft (S3) are arranged sequentially in the transverse direction, and the intermediate shaft (S2) is located in the transverse direction between the power input shaft (S1) and the power output shaft (S3).

4. The power commutation and power range integration module of claim 3, wherein, The idler shaft (S4) is located vertically below the two power shafts. The axis of the power input shaft (S1) and the axis of the power output shaft (S3) are located in a first plane, and the axis of the idler shaft (S4) and the axis of the intermediate shaft (S2) are located in a second plane.

5. The power commutation and power range integration module of claim 2, wherein, The axes of the idler shaft (S4), the power input shaft (S1), the intermediate shaft (S2), and the power output shaft (S3) are arranged vertically in sequence, and the axis of the intermediate shaft (S2) is located horizontally between the axis of the power input shaft (S1) and the axis of the idler shaft (S4).

6. A gearbox, characterized in that, The gearbox (100) includes a main transmission module capable of multi-speed shifting and a power reversing and high / low power gear integration module as described in any one of claims 1 to 5. The power reversing and high / low power gear integration module transmits power to the main transmission module through the power output shaft (S3).

7. The gearbox according to claim 6, characterized in that, The main transmission module is a four-speed transmission module. The gearbox (100) is used in agricultural machinery and includes a two-speed crawling module that can reduce speed and increase torque and a three-speed auxiliary transmission module that can shift to three speeds. The main transmission module transmits power to the walking system of the agricultural machinery through the two-speed crawling module and the three-speed auxiliary transmission module.

8. The gearbox according to claim 7, characterized in that, The main transmission module includes a main transmission output shaft (S5) with a first main shifter (T1), a second main shifter (T2), and first, second, third, and fourth gear sets with different speed ratios. The second main shifter (T2) is disposed on the power output shaft (S3). The first main shifter (T1) is used to engage the first gear set or the second gear set, and the second main shifter (T2) is used to engage the third gear set and the fourth gear set. The power input shaft (S1) transmits power to the main transmission output shaft (S5) through gear sets with different speed ratios.

9. The gearbox according to claim 7, characterized in that, The second-speed crawling module includes a crawling transition shaft (S6), a crawling output shaft (S7) with a crawling shifter (T3), a transmission gear set, and a climbing gear set for deceleration. The crawling shifter (T3) is used to engage the transmission gear set or the climbing gear set. The crawling transition shaft (S6) is connected to the main transmission module or the third-speed auxiliary transmission module through the transmission gear set.

10. The gearbox according to claim 9, characterized in that, The three-speed auxiliary transmission module is connected to the main transmission module through the two-speed creeping module. The three-speed auxiliary transmission module includes an auxiliary transmission output shaft (S9) with a first auxiliary shifter (T4), a second auxiliary shifter (T5), and low-speed, medium-speed, and high-speed gear sets with different speed ratios. The second auxiliary shifter (T5) is disposed on the creeping output shaft (S7). The first auxiliary shifter (T4) is used to engage the low-speed gear set or the medium-speed gear set. The second auxiliary shifter (T5) is used to engage or disengage the high-speed gear set. The creeping output shaft (S7) is used to transmit power to the auxiliary transmission output shaft (S9) through gear sets with different speed ratios.

11. The gearbox according to claim 9, characterized in that, The second-speed crawling module is connected to the main transmission module through the third-speed auxiliary transmission module. The third-speed auxiliary transmission module includes an auxiliary transmission input shaft (S8) with a first auxiliary shifter (T4), a second auxiliary shifter (T5), and low-speed, medium-speed, and high-speed gear sets with different speed ratios. The second auxiliary shifter (T5) is disposed on the crawling transition shaft (S6). The first auxiliary shifter (T4) is used to engage the low-speed gear set or the medium-speed gear set, and the second auxiliary shifter (T5) is used to engage the high-speed gear set. The auxiliary transmission input shaft (S8) is used to transmit power to the crawling transition shaft (S6) through gear sets with different speed ratios.

12. The gearbox according to any one of claims 7 to 11, characterized in that, The gearbox (100) includes a four-wheel drive mechanism, which includes a front-wheel drive module and a rear-wheel drive module. The main transmission module is used to transmit power to the four-wheel drive mechanism. The front-wheel drive module includes a four-wheel drive clutch (C6), which is used to engage or disengage the front axle of the travel system. The rear-wheel drive module is used to drive the rear axle of the travel system. And / or, The gearbox (100) also includes a PTO module, which includes a PTO input shaft (S10) with a PTO clutch (C7), a PTO gear set and a PTO output shaft (S11). The PTO clutch (C7) is used to engage or disengage the power input shaft (S1). The PTO input shaft (S10) transmits power to the PTO output shaft (S11) through the PTO gear set. The PTO output shaft (S11) is used to drive the working implements of the agricultural machinery.

13. An agricultural machine, characterized in that, The agricultural machinery includes the gearbox (100) as described in any one of claims 6 to 12.

Images