High-efficiency loader hydraulic mechanical transmission system, control method and loader

Abstract

The invention provides a high-efficiency loader hydraulic mechanical transmission system, a control method and a loader. One path of power of an engine is transmitted to an energy capacity adjusting device through a first power bridging pivot; the other path of power is conveyed into the hydraulic torque converter and is output through a second power bridging pivot; the capacity adjusting device outputs power through a third power bridging pivot, and the power output by the third power bridging pivot and the power output by the second power bridging pivot converge on a tooth profile coupler B; and the combined power is output to a vehicle drive axle by an output shaft arranged in the gear transmission. Based on the power dividing characteristic of the planetary gear mechanism, the hydraulic torque converter only transmits part of output power of the engine, the remaining output power is transmitted through the tooth profile coupler with high efficiency, and therefore the overall efficiency of a hydraulic mechanical transmission system is improved, and the transmission efficiency is improved. And the capacity adjusting device can improve the matching performance of the transmission system and the engine, so that the overall efficiency of the system is further improved.

Description

Technical Field

[0001] The invention relates to a high-efficiency loader hydraulic mechanical transmission system, a control method and a loader, belonging to the technical field of engineering machinery. Background Art

[0002] Hydromechanical transmission has good buffering and vibration reduction properties and adaptability, which makes it widely used in loaders. For vehicles equipped with a torque converter, the efficiency of the powertrain is mainly determined by the efficiency of the torque converter and the matching performance of the engine-torque converter combined system. However, due to the conversion of mechanical energy-fluid kinetic energy-mechanical energy in hydromechanical transmission, its transmission efficiency has always been low. In addition, the traditional compromise matching method improves the matching performance of the combined system by taking the arithmetic average between the excavation condition and the transportation condition. This method cannot achieve the optimal fuel saving rate of the loader under both conditions. Therefore, how to improve the fuel economy of the loader while retaining the original performance advantages of the hydromechanical transmission has become an important issue.

[0003] Different from the structural characteristics of the traditional hydraulic mechanical transmission in which the torque converter and the mechanical transmission are connected in series, in the hydraulic reflow transmission system, the torque converter and the gear transmission are connected in parallel through a planetary gear mechanism. Changing the speed ratio of the energy capacity adjustment device can form a variety of matching modes between the transmission system and the engine, thereby improving the matching performance of the hydraulic transmission system and the engine.

[0004] The hydraulic reflow speed transmission system is mainly composed of an engine, a torque converter, a capacity adjustment device and a planetary gear mechanism, wherein the pump wheel of the torque converter is connected to the sun gear of the planetary gear mechanism, and the driven end is fixedly connected to the engine output shaft; the input shaft of the capacity adjustment device is fixedly connected to the engine output shaft, and the output shaft is connected to the planet carrier of the planetary gear mechanism. The power of the engine is first transmitted to the planetary gear mechanism through the capacity adjustment device, and then the planetary gear mechanism uses its power splitting characteristics to output most of the input power through the ring gear, while part of the power flows back to the engine output shaft through the torque converter, and then coupled with the engine output power and transmitted to the capacity adjustment device together.

[0005] The hydraulic reflux speed-changing transmission system has the following two technical defects: The planet carrier absorbs power from the engine and the torque converter at the same time. In the low speed ratio stage of the transmission system, the input power of the torque converter is greater than the input power of the transmission system, that is, there is parasitic power in the system. Since the torque converter itself is an inefficient transmission device, there is too much power loss in the torque converter, which reduces the efficiency of the transmission system.

[0006] The pump wheel of the torque converter is connected to the high-speed sun gear, which makes the energy capacity characteristic curve of the transmission system easy to diverge, making it difficult for the engine to operate in the high-efficiency area, resulting in poor matching performance of the combined system. Summary of the invention

[0007] Purpose of the invention: In view of the deficiencies in the prior art, the present invention provides a high-efficiency loader hydromechanical transmission system, control method and loader. Based on the power splitting characteristics of the planetary gear mechanism, the hydraulic torque converter only transmits part of the output power of the engine, and the remaining output power is transmitted through a more efficient gear profile coupler, thereby improving the overall efficiency of the hydromechanical transmission system. The energy capacity adjustment device can improve the matching performance of the transmission system and the engine, thereby further improving the overall efficiency of the system.

[0008] Technical solution: A high-efficiency loader hydraulic mechanical transmission system, including an engine, a hydraulic torque converter, an energy capacity adjustment device and a gear transmission, wherein the output end of the engine outputs power through an input shaft, and is respectively connected to the hydraulic torque converter and the energy capacity adjustment device through a planetary carrier and a planetary gear in a planetary gear; The power outputted by the engine is transmitted to the energy capacity adjustment device through the sun gear in the planetary gear and the first power bridge pivot; The power outputted by the engine on the other side is transmitted to the torque converter through the ring gear in the planetary gear and outputted from the second power bridge pivot shaft; The energy capacity adjustment device outputs power through the third power bridge pivot, the output end of the third power bridge pivot is connected to a toothed coupler A, the second power bridge pivot is provided with a toothed coupler B, the toothed coupler A is meshed with the toothed coupler B, and the power output by the third power bridge pivot passes through the toothed coupler A and merges with the power output by the second power bridge pivot on the toothed coupler B; The gear coupler B transmits the power merged in the gear coupler B to the gear transmission through the first gear coupling transmission mechanism meshing with the gear coupler C on the fifth power bridging pivot arranged in the gear transmission, and the output shaft arranged in the gear transmission outputs the power to the vehicle drive axle.

[0009] The present invention changes the transmission mode of the existing hydromechanical transmission system and, based on the power splitting characteristics of the planetary gear mechanism, enables the hydraulic torque converter to transmit only part of the output power of the engine, while the remaining output power is transmitted through a gear profile coupler with higher efficiency, thereby improving the overall efficiency of the hydromechanical transmission system; in excavation conditions, the speed ratio of the energy capacity adjustment device is preset as needed, so that the engine can operate in a high power output area, further improving the performance of the entire vehicle; in transportation conditions, the load of the working hydraulic system is zero, and at this time all the power of the engine is transmitted to the transmission system. The speed ratio of the energy capacity adjustment device is preset as needed, so that the engine can operate in a low fuel consumption rate area, further improving the fuel economy of the entire vehicle.

[0010] The first gear-profile coupling transmission mechanism includes a fourth power bridging pivot and a gear-profile coupler D and a gear-profile coupler E which are arranged on both sides of the fifth power bridging pivot and mesh with the fourth power bridging pivot and mesh with the gear-profile coupler B and the gear-profile coupler C respectively.

[0011] In order to reduce the radial dimension of the gear transmission, an intermediate shaft gear coupler mechanism is arranged between the gear coupler B where the capacity adjustment device and the torque converter power converge and the gear transmission. Since the power bridging pivot in the intermediate shaft gear coupler mechanism is installed on the chassis through a base, during the power transmission process, the vibration caused by the meshing transmission between the gear couplers is dispersed to the chassis by the power bridging pivot to reduce the dynamic load of the second power bridging pivot and improve the power stability.

[0012] The energy capacity adjustment device includes a first routing coupling device which is dynamically connected to the first power bridging pivot, the first routing coupling device includes a shoveling gear C1 and a transport gear C2, the shoveling gear C1 and the transport gear C2 output power through a toothed profile coupler F and a toothed profile coupler G respectively, and the third power bridging pivot is provided with a toothed profile coupler H and a toothed profile coupler I which are respectively engaged with the toothed profile coupler F and the toothed profile coupler G.

[0013] As the main power output structure of the hydromechanical transmission system of a high-efficiency loader, the energy capacity adjustment device can improve the matching performance between the transmission system and the engine, thereby further improving the overall efficiency of the system. The power input from the engine is transmitted to the gear coupler A using the gear profile coupler structure with high transmission efficiency. The excavation and transportation gears are adjusted according to the working conditions to enable the overall transmission system to operate in the high-efficiency and high-power ranges, and the power is combined with the torque converter with low transmission efficiency to provide higher power for the gear transmission and reduce power loss.

[0014] The gear transmission includes a second route-selective coupling device connected to the fifth power bridge pivot shaft, and the second route-selective coupling device includes a reverse gear C R and forward gear CF , the reverse gear C R and forward gear C F The power is outputted through the toothed coupler J and the toothed coupler K respectively, and also includes a third routing coupling device which is connected to the second routing coupling device through the second toothed coupling transmission mechanism, and a fourth routing coupling device which is connected to the second routing coupling device through the second toothed coupling transmission mechanism.

[0015] By setting the forward, reverse and third and fourth selective coupling devices in the gear transmission, the speed ratio adjustment range of the front device can be expanded, and the speed of the loader can be more easily within the high-efficiency range of the transmission system.

[0016] The third selective coupling device includes a gear C II and gear position C III , the gear position C II and gear position C III The power is output through the toothed coupler L and the toothed coupler M respectively, and the third routing coupling device inputs power through the sixth power bridge pivot, and the sixth power bridge pivot is provided with a toothed coupler N, and the toothed coupler N is engaged with the second toothed coupling transmission mechanism for power input; The output shaft is provided with a toothed coupler O and a toothed coupler P, and the toothed coupler O and the toothed coupler P are meshed with the toothed coupler L and the toothed coupler M respectively; The fourth route-selective coupling device includes a gear position C I , the gear position C I Power is output through the gear coupler Q, and the fourth routing coupling device inputs power through the seventh power bridging pivot. The seventh power bridging pivot is provided with a gear coupler R, and the gear coupler R is engaged with the second gear coupling transmission mechanism for power input, and the gear coupler Q is engaged with the gear coupler O on the output shaft for power output.

[0017] The second gear-profile coupling transmission mechanism includes an eighth power bridging pivot and a gear-profile coupler S and a gear-profile coupler T engaged with the eighth power bridging pivot, and also includes a ninth power bridging pivot and a gear-profile coupler U and a gear-profile coupler V arranged on the ninth power bridging pivot, the gear-profile coupler S engages with the gear-profile coupler J on the second routing coupling device, the gear-profile coupler T engages with the gear-profile coupler U on the ninth power bridging pivot, the gear-profile coupler V is power-connected to the gear-profile coupler K on the second routing coupling device through an intermediate shaft gear-profile coupler structure having the same structure as the eighth power bridging pivot, the gear-profile coupler S and the gear-profile coupler T, and is engaged with the gear-profile coupler N on the sixth power bridging pivot and the gear-profile coupler R on the seventh power bridging pivot for power transmission.

[0018] A control method using a high-efficiency loader hydromechanical transmission system, Including excavation and transportation conditions; The shoveling and digging working condition is divided into a shoveling and digging forward gear and a shoveling and digging reverse gear; The transport working conditions are divided into transport forward first gear, transport forward second gear, transport forward third gear, transport reverse first gear, transport reverse second gear and transport reverse third gear.

[0019] The excavation working conditions are specifically as follows: The input shaft transmits the power output by the engine to the planetary gear through the planetary carrier, and the planetary gear divides the power to the sun gear and the ring gear. The sun gear transmits the power to the first routing coupling device in the energy capacity adjustment device through the first power bridge pivot shaft, and the ring gear transmits the power to the pump wheel in the hydraulic torque converter. The power input in the hydraulic torque converter is output to the second power bridge pivot shaft through the pump wheel, the turbine and the guide wheel. When in the first gear of excavation forward, the energy regulating device works in C1 gear and the gear transmission works in C F and C I gear, power is output by profile coupler F, the power passes through profile coupler H, the third power bridge pivot and profile coupler A, and merges with the power of the second power bridge pivot on profile coupler B, and then is transmitted to profile coupler D through profile coupler B, and the power is transmitted to profile coupler E and then to profile coupler C by the fourth power bridge pivot, and is transmitted to the second routing coupling device through the fifth power bridge pivot, and is transmitted to profile coupler V through profile coupler K and the intermediate shaft profile coupler, and is transmitted to profile coupler R on the seventh power bridge pivot by profile coupler V, driving the seventh power bridge pivot to rotate, and the power of the seventh power bridge pivot is transmitted to profile coupler O on the output shaft by the fourth routing coupling device through profile coupler Q, and profile coupler O drives the output shaft to rotate and transmits power to the drive axle; When in the first gear of excavation reverse, the energy regulating device works in C1 gear and the gear transmission works in C R and C I The power inputted through the fifth power bridge pivot is transmitted to the gear coupler S, the eighth power bridge pivot, the gear coupler T and the gear coupler U through the gear coupler J, and then transmitted to the ninth power bridge pivot. The gear coupler V on the ninth power bridge pivot transmits the power to the seventh power bridge pivot through the gear coupler R, and then passes through the gear position C. I The power is transmitted to the gear coupler O through the gear coupler Q to drive the output shaft to rotate and transmit the power to the drive axle.

[0020] The specific transportation conditions are: The input shaft transmits the power output by the engine to the planetary gear through the planetary carrier, and the planetary gear divides the power to the sun gear and the ring gear. The sun gear transmits the power to the first routing coupling device in the energy capacity adjustment device through the first power bridge pivot shaft, and the ring gear transmits the power to the pump wheel in the hydraulic torque converter. The power input in the hydraulic torque converter is output to the second power bridge pivot shaft through the pump wheel, the turbine and the guide wheel. When in the transport forward first gear, the energy capacity adjustment device works in the C2 gear position, and the gearbox works in the C F and C I In the first gear, the first routing coupling device outputs power from the profile coupler G, and the power is output from the profile coupler A through the profile coupler I and the third power bridge pivot, and merges with the power of the second power bridge pivot on the profile coupler B, and then transmitted to the profile coupler D through the profile coupler B, and the power is transmitted to the profile coupler E and then to the profile coupler C by the fourth power bridge pivot, and the power is transmitted to the second routing coupling device through the fifth power bridge pivot, and the power is transmitted to the profile coupler V through the profile coupler K and the intermediate shaft profile coupler, and the power is transmitted to the profile coupler R on the seventh power bridge pivot by the profile coupler V, driving the seventh power bridge pivot to rotate, and the power of the seventh power bridge pivot is transmitted to the profile coupler O on the output shaft by the fourth routing coupling device through the profile coupler Q, and the profile coupler O drives the output shaft to rotate and transmits the power to the drive axle; When in the transport forward second gear, the energy capacity adjustment device works in the C2 gear position, and the gear transmission works in the C F and C II The gear coupler V drives the gear coupler N on the sixth power bridge pivot to rotate, and the gear coupler N drives the sixth power bridge pivot to rotate, and the gear coupler C of the third route-selective coupling device II In gear position, the gear coupler L outputs power, the gear coupler L drives the gear coupler O to rotate, and finally the output shaft outputs power to the drive axle; When in the third gear for transport, the energy regulating device works in the C2 gear position, and the gearbox works in the C F and C III The gear coupler V drives the gear coupler N on the sixth power bridge pivot to rotate, and the gear coupler N drives the sixth power bridge pivot to rotate, and the gear coupler C of the third route-selective coupling device III In gear position, the gear coupler M outputs power, the gear coupler M drives the gear coupler P to rotate, and finally the output shaft outputs power to the drive axle; When in the transport reverse gear, the energy regulating device works in the C2 gear position, and the gear transmission works in the C R and C IThe power inputted through the fifth power bridge pivot is transmitted to the gear coupler S, the eighth power bridge pivot, the gear coupler T and the gear coupler U through the gear coupler J, and then transmitted to the ninth power bridge pivot. The gear coupler V on the ninth power bridge pivot transmits the power to the seventh power bridge pivot through the gear coupler R, and then passes through the gear position C. I The power is transmitted to the gear coupler O through the gear coupler Q to drive the output shaft to rotate and transmit the power to the drive axle.

[0021] When in the transport reverse second gear, the energy capacity adjustment device works in the C2 gear position, and the gear transmission works in the C R and C II The power inputted through the fifth power bridge pivot is transmitted to the gear coupler S, the eighth power bridge pivot, the gear coupler T and the gear coupler U through the gear coupler J, and then transmitted to the ninth power bridge pivot. The gear coupler V drives the gear coupler N on the sixth power bridge pivot to rotate, and the gear coupler N drives the sixth power bridge pivot to rotate, and then the gear coupler C of the third routing coupling device is connected to the gear coupler N through the gear coupler J. II In gear position, the gear coupler L outputs power, the gear coupler L drives the gear coupler O to rotate, and finally the output shaft outputs power to the drive axle; When in the third gear of transport reverse, the energy capacity adjustment device works in the C2 gear position and the gear transmission works in the C R and C III The power inputted through the fifth power bridge pivot is transmitted to the gear coupler S, the eighth power bridge pivot, the gear coupler T and the gear coupler U through the gear coupler J, and then transmitted to the ninth power bridge pivot. The gear coupler V drives the gear coupler N on the sixth power bridge pivot to rotate, and the gear coupler N drives the sixth power bridge pivot to rotate, and then the gear coupler C of the third routing coupling device is connected to the gear coupler N through the gear coupler J. III The gear is in gear position, and the power is output by the gear coupler M, which drives the gear coupler P to rotate, and finally the output shaft outputs the power to the drive axle.

[0022] A loader uses the high-efficiency loader hydraulic mechanical transmission system and control method.

[0023] Beneficial effects: The present invention changes the transmission mode of the existing hydromechanical transmission system, based on the power splitting characteristics of the planetary gear mechanism, so that the torque converter only transmits part of the output power of the engine, and the remaining output power is transmitted through the gear profile coupler with higher efficiency, thereby improving the overall efficiency of the hydromechanical transmission system; in the excavation condition, the speed ratio of the energy capacity adjustment device is preset as needed, so that the engine can work in the high power output area, further improving the performance of the whole vehicle; in the transportation condition, the load of the working hydraulic system is zero, at this time all the power of the engine is transmitted to the transmission system, and the speed ratio of the energy capacity adjustment device is preset as needed, so that the engine can work in the low fuel consumption rate area, further improving the fuel economy of the whole vehicle. By reducing the divergence rate of the energy capacity characteristic curve of the hydromechanical transmission system, the engine can always work in the high efficiency area and high power area under different loader conditions, thereby improving the matching performance of the engine and the hydromechanical transmission system. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on the provided drawings without paying creative work.

[0025] Figure 1 The figure is a structural block diagram of the hydraulic mechanical transmission system of the high-efficiency loader of the present invention.

[0026] Figure 2 It is a simplified structural diagram of the high-efficiency hydraulic mechanical transmission system of the present invention, wherein the power flow direction is the power flow direction during the excavation working condition.

[0027] Figure 3 It is a ratio diagram of the input power of the torque converter of the present invention and the transmission system.

[0028] Figure 4 It is a transmission system efficiency-vehicle speed curve diagram of the loader of the present invention at full throttle pedal opening.

[0029] Figure 5 It is a matching diagram of the hydraulic reflow speed change transmission system and the engine under the shovel working condition of the present invention.

[0030] Figure 6 It is a matching diagram of the high-efficiency hydromechanical transmission system and the engine under the shovel working condition of the present invention.

[0031] Figure 7 It is a matching diagram of the hydraulic reflow speed change transmission system and the engine under the transportation working condition of the present invention.

[0032] Figure 8It is a matching diagram of the high-efficiency hydromechanical transmission system and the engine under the transportation working condition of the present invention. DETAILED DESCRIPTION

[0033] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0034] In the description of the present invention, it is necessary to understand that the terms "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating the orientation or position relationship are based on the orientation or position relationship shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0035] In the present invention, unless otherwise clearly specified and limited, a first feature being "above" or "below" a second feature may include that the first and second features are in direct contact, or may include that the first and second features are not in direct contact but are in contact through another feature between them. Moreover, a first feature being "above", "above" and "above" a second feature includes that the first feature is directly above and obliquely above the second feature, or simply indicates that the first feature is higher in level than the second feature. A first feature being "below", "below" and "below" a second feature includes that the first feature is directly below and obliquely below the second feature, or simply indicates that the first feature is lower in level than the second feature.

[0036] like Figure 1 and 2 As shown, a high-efficiency loader hydraulic mechanical transmission system includes an engine, a hydraulic torque converter, an energy capacity adjustment device and a gear transmission, wherein the output end of the engine outputs power through an input shaft 1, and is connected to the hydraulic torque converter and the energy capacity adjustment device through a planet carrier 2 and a planetary gear 3 in a planetary gear 3; The power outputted by the engine is transmitted to the energy capacity adjustment device through the sun gear 4 in the planetary gear 3 and the first power bridge pivot 5; The power outputted by the engine on the other side is transmitted to the pump wheel 7 in the torque converter through the ring gear 6 in the planetary gear 3, and then transmitted to the pump wheel 7 through the turbine 8 and the guide wheel 9 through the second power bridge pivot 10; The energy capacity adjustment device outputs power through the third power bridge pivot 11, the output end of the third power bridge pivot 11 is connected to a toothed coupler A12, the second power bridge pivot 10 is provided with a toothed coupler B13, the toothed coupler A12 is meshed with the toothed coupler B13, and the power output by the third power bridge pivot 11 passes through the toothed coupler A12 and merges with the power output by the second power bridge pivot 10 on the toothed coupler B13; The gear coupler B13 transmits the power merged at the gear coupler B13 to the gear transmission through the first gear coupling transmission mechanism meshing with the gear coupler C15 on the fifth power bridging pivot 14 provided in the gear transmission, and the power is output to the vehicle drive axle by the output shaft 16 provided in the gear transmission. The gear coupler in this embodiment is configured as a gear.

[0037] The present invention changes the transmission mode of the existing hydromechanical transmission system and, based on the power splitting characteristics of the planetary gear mechanism, enables the hydraulic torque converter to transmit only part of the output power of the engine, while the remaining output power is transmitted through a gear profile coupler with higher efficiency, thereby improving the overall efficiency of the hydromechanical transmission system; in excavation conditions, the speed ratio of the energy capacity adjustment device is preset as needed, so that the engine can operate in a high power output area, further improving the performance of the entire vehicle; in transportation conditions, the load of the working hydraulic system is zero, and at this time all the power of the engine is transmitted to the transmission system. The speed ratio of the energy capacity adjustment device is preset as needed, so that the engine can operate in a low fuel consumption rate area, further improving the fuel economy of the entire vehicle.

[0038] The first gear coupling transmission mechanism includes a fourth power bridging pivot 17 and a gear coupler D18 and a gear coupler E19 which are engaged with the fourth power bridging pivot 17 and are arranged on both sides of the fifth power bridging pivot 14 and are respectively engaged with the gear coupler B13 and the gear coupler C15.

[0039] In order to reduce the radial size of the gear transmission, an intermediate shaft gear coupler mechanism is arranged between the gear coupler B13 where the capacity adjustment device and the torque converter power converge and the gear transmission. Since the power bridging pivot in the intermediate shaft gear coupler mechanism is installed on the chassis through a base, during the power transmission process, the vibration caused by the meshing transmission between the gear couplers is dispersed to the chassis by the power bridging pivot, so as to reduce the dynamic load of the second power bridging pivot 10 and improve the power stability.

[0040] The energy capacity adjustment device includes a first routing coupling device 20 which is dynamically connected to the first power bridging pivot 5. The first routing coupling device 20 includes a shoveling gear C1 and a transport gear C2. The shoveling gear C1 and the transport gear C2 output power through a toothed profile coupler F21 and a toothed profile coupler G22, respectively. The third power bridging pivot 11 is provided with a toothed profile coupler H23 and a toothed profile coupler I24 which are respectively engaged with the toothed profile coupler F21 and the toothed profile coupler G22.

[0041] As the main power output structure of the high-efficiency loader's hydromechanical transmission system, the energy capacity adjustment device uses a high-efficiency gear coupler structure to transmit the power input from the engine to the gear coupler A12, and adjusts the digging and transportation gears according to working conditions to enable the overall transmission system to operate in the high-efficiency and high-power range. It merges with the torque converter with lower transmission efficiency to provide higher power for the gear transmission and reduce power loss.

[0042] The gear transmission includes a second route-selective coupling device 25 connected to the fifth power bridge pivot 14, and the second route-selective coupling device 25 includes a reverse gear C R and forward gear C F , the reverse gear C R and forward gear C F The power is outputted through the gear profile coupler J26 and the gear profile coupler K27 respectively, and also includes a third routing coupling device 28 which is connected to the second routing coupling device 25 through the second gear profile coupling transmission mechanism, and a fourth routing coupling device 29 which is connected to the second routing coupling device 25 through the second gear profile coupling transmission mechanism.

[0043] By setting the forward, reverse and third and fourth selective coupling devices 29 in the gear transmission, the speed ratio adjustment range of the front device can be expanded, and the speed of the loader can be more within the high-efficiency range of the transmission system.

[0044] The third selective coupling device 28 includes a gear position C II and gear position C III , the gear position C II and gear position C III The power is output through the toothed coupler L30 and the toothed coupler M31 respectively, and the third routing coupling device 28 inputs power through the sixth power bridge pivot 32, and the sixth power bridge pivot 32 is provided with a toothed coupler N33, and the toothed coupler N33 is engaged with the second toothed coupling transmission mechanism for power input; The output shaft 16 is provided with a toothed coupler O34 and a toothed coupler P35, and the toothed coupler O34 and the toothed coupler P35 are respectively meshed with the toothed coupler L30 and the toothed coupler M31; The fourth route-selective coupling device 29 includes a gear position C I , the gear position C I The power is output through the gear coupler Q36, and the fourth routing coupling device 29 inputs power through the seventh power bridging pivot 37. The seventh power bridging pivot 37 is provided with a gear coupler R38. The gear coupler R38 engages with the second gear coupling transmission mechanism for power input, and the gear coupler Q36 engages with the gear coupler O34 on the output shaft 16 for power output.

[0045] The second gear-profile coupling transmission mechanism includes an eighth power bridge pivot 39 and a gear-profile coupler S40 and a gear-profile coupler T41 meshed with the eighth power bridge pivot 39, and also includes a ninth power bridge pivot 42 and a gear-profile coupler U43 and a gear-profile coupler V44 arranged on the ninth power bridge pivot 42, the gear-profile coupler S40 meshing with the gear-profile coupler J26 on the second route-selective coupling device 25, the gear-profile coupler T41 meshing with the ninth power bridge pivot The gear coupler U43 on 42 is engaged, and the gear coupler V44 is connected to the gear coupler K27 on the second routing coupling device 25 through an intermediate shaft gear coupler structure that is the same as the eighth power bridging pivot 39, the gear coupler S40 and the gear coupler T41, and is engaged with the gear coupler N33 on the sixth power bridging pivot 32 and the gear coupler R38 on the seventh power bridging pivot 37 for power transmission.

[0046] Since the torque converter is an inefficient transmission device, the more power input to the torque converter, the lower the efficiency of the transmission system. Figure 3 It can be seen that the power split ratio of the high-efficiency hydromechanical transmission system is always less than 1, so the efficiency of this transmission system is greater than that of the transmission hydromechanical transmission system. In the low speed ratio stage, the power split ratio of the hydraulic reflow transmission system is greater than 1; the power split ratio curves of the two transmission systems intersect at a speed ratio of 0.81. This shows that in most speed ratio ranges (0~0.81), the efficiency of the high-efficiency hydromechanical transmission system is greater than that of the hydraulic reflow transmission system.

[0047] Figure 4The transmission-vehicle speed curve is shown when the accelerator pedal is 100% open and the loader shifts from 1st gear to 3rd gear. When the vehicle speed is less than 10.2km / h, the average efficiency of the high-efficiency hydromechanical transmission system is 24% higher than that of the hydraulic return transmission system. Considering that the typical operation mode of the loader is to shovel and move materials, the vehicle speed is generally less than 10km / h. The high-efficiency hydromechanical transmission system can completely replace the hydraulic return transmission system and the traditional transmission system of the hydraulic torque converter and gear coupler gearbox in series.

[0048] Figure 5 and Figure 6 The matching performance of the hydraulic reflow transmission system and the high-efficiency hydraulic mechanical transmission system with the engine when the loader is shoveling materials is compared. It can be seen that the input torque curve distribution range of the high-efficiency hydraulic mechanical transmission system is narrower, and its average output power is also higher, which is conducive to improving the loader's shoveling efficiency. Moreover, the matching point of the high-efficiency hydraulic mechanical transmission system and the engine is closer to the minimum fuel consumption rate curve, so the average fuel consumption rate of the engine is also lower, which is conducive to improving the fuel economy of the loader.

[0049] Figure 7 and Figure 8 The matching performance of the hydraulic reflow transmission system and the high-efficiency hydraulic mechanical transmission system with the engine when the loader is transporting materials is compared. It can be seen that the input characteristic curve distribution range of the high-efficiency hydraulic mechanical transmission system is narrower and its average output power is higher, which is conducive to improving the working efficiency of the loader.

[0050] A control method for applying the high-efficiency loader hydromechanical transmission system, including a shoveling and transporting working condition; The shoveling and digging working condition is divided into a shoveling and digging forward gear and a shoveling and digging reverse gear; The transport working conditions are divided into transport forward first gear, transport forward second gear, transport forward third gear, transport reverse first gear, transport reverse second gear and transport reverse third gear.

[0051] The excavation working conditions are specifically as follows: The power outputted by the engine is transmitted from the input shaft 1 to the planetary gear 3 through the planetary carrier 2, and the planetary gear 3 distributes the power to the sun gear 4 and the ring gear 6. The sun gear 4 transmits the power to the first routing coupling device 20 in the energy capacity adjustment device through the first power bridge pivot 5, and the ring gear 6 transmits the power to the pump wheel 7 in the hydraulic torque converter. The power inputted into the hydraulic torque converter is outputted to the second power bridge pivot 10 through the pump wheel 7, the turbine 8 and the guide wheel 9; When in the first gear of excavation forward, the energy capacity adjustment device works in C1 gear and the gear transmission works in C F and C IThe gear coupler F21 outputs power, passes through the gear coupler H23, the third power bridge pivot 11 and the gear coupler A12, and merges with the power of the second power bridge pivot 10 on the gear coupler B13, and then is transmitted to the gear coupler D18 through the gear coupler B13, and then is transmitted to the gear coupler E19 and then to the gear coupler C15 by the fourth power bridge pivot 17, and then is transmitted to the second routing coupling device 25 through the fifth power bridge pivot 14, and then is transmitted to the gear coupler C15 by the fifth power bridge pivot 14. The power is transmitted to the profile coupler V44 through the profile coupler K27 and the intermediate shaft profile coupler, and the profile coupler V44 transmits the power to the profile coupler R38 on the seventh power bridge pivot 37, driving the seventh power bridge pivot 37 to rotate, and the fourth routing coupling device 29 transmits the power of the seventh power bridge pivot 37 to the profile coupler O34 on the output shaft 16 through the profile coupler Q36, and the profile coupler O34 drives the output shaft 16 to rotate and transmit the power to the drive axle; When in the first gear of excavation reverse, the energy regulating device works in C1 gear and the gear transmission works in C R and C I The power inputted through the fifth power bridge pivot 14 is transmitted to the gear coupler S40, the eighth power bridge pivot 39, the gear coupler T41 and the gear coupler U43 through the gear coupler J26, and then transmitted to the ninth power bridge pivot 42. The gear coupler V44 on the ninth power bridge pivot 42 transmits the power to the seventh power bridge pivot 37 through the gear coupler R38, and then the gear coupler V44 on the ninth power bridge pivot 42 transmits the power to the seventh power bridge pivot 37 through the gear coupler R38. I The power is transmitted to the gear coupler O34 through the gear coupler Q36 to drive the output shaft 16 to rotate and transmit the power to the drive axle.

[0052] The specific transportation conditions are: The power outputted by the engine is transmitted from the input shaft 1 to the planetary gear 3 through the planetary carrier 2, and the planetary gear 3 distributes the power to the sun gear 4 and the ring gear 6. The sun gear 4 transmits the power to the first routing coupling device 20 in the energy capacity adjustment device through the first power bridge pivot 5, and the ring gear 6 transmits the power to the pump wheel 7 in the hydraulic torque converter. The power inputted into the hydraulic torque converter is outputted to the second power bridge pivot 10 through the pump wheel 7, the turbine 8 and the guide wheel 9; When in the transport forward gear, the energy capacity adjustment device works in the C2 gear position, and the gear transmission works in the C F and C IThe first routing coupling device 20 outputs power from the gear coupler G22, and through the gear coupler I24 and the third power bridge pivot 11, the power is output from the gear coupler A12, and merges with the power of the second power bridge pivot 10 on the gear coupler B13, and then transmitted to the gear coupler D18 through the gear coupler B13, and the power is transmitted to the gear coupler E19 and then to the gear coupler C15 by the fourth power bridge pivot 17, and then transmitted to the second routing coupling through the fifth power bridge pivot 14. The coupling device 25 transmits power to the profile coupler V44 through the profile coupler K27 and the intermediate shaft profile coupler, and the profile coupler V44 transmits power to the profile coupler R38 on the seventh power bridge pivot 37, driving the seventh power bridge pivot 37 to rotate, and the fourth routing coupling device 29 transmits power of the seventh power bridge pivot 37 to the profile coupler O34 on the output shaft 16 through the profile coupler Q36, and the profile coupler O34 drives the output shaft 16 to rotate and transmit power to the drive axle; When in the transport forward second gear, the energy capacity adjustment device works in the C2 gear position, and the gear transmission works in the C F and C II The gear coupler V44 drives the gear coupler N33 on the sixth power bridge pivot 32 to rotate, and the gear coupler N33 drives the sixth power bridge pivot 32 to rotate, and the gear coupler C44 drives the sixth power bridge pivot 32 to rotate. II In gear position, the gear coupler L30 outputs power, the gear coupler L30 drives the gear coupler O34 to rotate, and finally the output shaft 16 outputs power to the drive axle; When in the third gear for transport, the energy regulating device works in the C2 gear position, and the gearbox works in the C F and C III The gear coupler V44 drives the gear coupler N33 on the sixth power bridge pivot 32 to rotate, and the gear coupler N33 drives the sixth power bridge pivot 32 to rotate, and the gear coupler C44 drives the sixth power bridge pivot 32 to rotate. III In gear position, the gear coupler M31 outputs power, the gear coupler M31 drives the gear coupler P35 to rotate, and finally the output shaft 16 outputs power to the drive axle; When in the transport reverse gear, the energy capacity adjustment device works in the C2 gear position, and the gear transmission works in the C R and C I The power inputted through the fifth power bridge pivot 14 is transmitted to the gear coupler S40, the eighth power bridge pivot 39, the gear coupler T41 and the gear coupler U43 through the gear coupler J26, and then transmitted to the ninth power bridge pivot 42. The gear coupler V44 on the ninth power bridge pivot 42 transmits the power to the seventh power bridge pivot 37 through the gear coupler R38, and then the gear coupler V44 on the ninth power bridge pivot 42 transmits the power to the seventh power bridge pivot 37 through the gear coupler R38.I The power is transmitted to the gear coupler O34 through the gear coupler Q36 to drive the output shaft 16 to rotate and transmit the power to the drive axle.

[0053] When in the transport reverse second gear, the energy capacity adjustment device works in the C2 gear position, and the gear transmission works in the C R and C II The power inputted through the fifth power bridge pivot 14 is transmitted to the gear coupler S40, the eighth power bridge pivot 39, the gear coupler T41 and the gear coupler U43 through the gear coupler J26, and then transmitted to the ninth power bridge pivot 42. The gear coupler V44 drives the gear coupler N33 on the sixth power bridge pivot 32 to rotate, and the gear coupler N33 drives the sixth power bridge pivot 32 to rotate, and then passes through the C of the third routing coupling device 28. II In gear position, the gear coupler L30 outputs power, the gear coupler L30 drives the gear coupler O34 to rotate, and finally the output shaft 16 outputs power to the drive axle; When in the third gear of transport reverse, the energy capacity adjustment device works in the C2 gear position and the gear transmission works in the C R and C III The power inputted through the fifth power bridge pivot 14 is transmitted to the gear coupler S40, the eighth power bridge pivot 39, the gear coupler T41 and the gear coupler U43 through the gear coupler J26, and then transmitted to the ninth power bridge pivot 42. The gear coupler V44 drives the gear coupler N33 on the sixth power bridge pivot 32 to rotate, and the gear coupler N33 drives the sixth power bridge pivot 32 to rotate, and then passes through the C of the third routing coupling device 28. III In the gear position, the power is output by the gear coupler M31, which drives the gear coupler P35 to rotate, and finally the power is output to the drive axle by the output shaft 16.

[0054] A loader uses a high-efficiency loader hydraulic mechanical transmission system and a control method.

[0055] In this specification, each embodiment is described in a progressive manner, and each embodiment focuses on the differences from other embodiments. The same or similar parts between the embodiments can be referred to each other. For the device disclosed in the embodiment, since it corresponds to the method disclosed in the embodiment, the description is relatively simple, and the relevant parts can be referred to the method part.

[0056] The above description of the disclosed embodiments enables one skilled in the art to implement or use the present invention. Various modifications to these embodiments will be apparent to one skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the present invention. Therefore, the present invention will not be limited to the embodiments shown herein, but rather to the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A high-efficiency loader hydraulic mechanical transmission system, comprising an engine, a hydraulic torque converter, an energy capacity adjustment device and a gear transmission, characterized in that: The output end of the engine outputs power through an input shaft (1), and is respectively connected to a hydraulic torque converter and a capacity regulating device through a planet carrier (2) and a planet gear (3) in a planet gear (3); The power outputted by the engine passes through the sun gear (4) in the planetary gear (3) and is transmitted to the energy capacity adjustment device through the first power bridge pivot (5); The power outputted by the engine on the other hand is transmitted to the hydraulic torque converter through the ring gear (6) in the planetary gear (3) and then outputted from the second power bridge pivot (10); The energy capacity adjustment device outputs power through a third power bridge pivot (11); an output end of the third power bridge pivot (11) is connected to a toothed coupler A (12); a toothed coupler B (13) is provided on the second power bridge pivot (10); the toothed coupler A (12) is meshed with the toothed coupler B (13); the power output from the third power bridge pivot (11) passes through the toothed coupler A (12) and merges with the power output from the second power bridge pivot (10) on the toothed coupler B (13); The gear coupler B (13) transmits the power merged in the gear coupler B (13) to the gear transmission through a first gear coupling transmission mechanism meshing with a gear coupler C (15) on a fifth power bridge pivot (14) provided in the gear transmission, and the power is output to a vehicle drive axle by an output shaft (16) provided in the gear transmission.

2. The high-efficiency loader hydraulic mechanical transmission system according to claim 1, characterized in that: The first toothed profile coupling transmission mechanism comprises a fourth power bridging pivot (17), and a toothed profile coupler D (18) and a toothed profile coupler E (19) which are arranged on both sides of a fifth power bridging pivot (14) and mesh with the fourth power bridging pivot (17) and mesh with the toothed profile coupler B (13) and the toothed profile coupler C (15), respectively.

3. The high-efficiency loader hydraulic mechanical transmission system according to claim 2, characterized in that: The energy capacity adjustment device comprises a first routing coupling device (20) which is connected to the first power bridge pivot shaft (5) by power, the first routing coupling device (20) comprising a shoveling gear position C1 and a transport gear position C2, the shoveling gear position C1 and the transport gear position C2 being respectively connected to the first power bridge pivot shaft (5) by power, F (21) and the toothed coupler G (22) output power, and the third power bridge pivot (11) is provided with two gears respectively connected to the toothed coupler F (21) and toothed coupler G (22) meshing with toothed coupler H (23) and toothed coupler I (twenty four).

4. The high-efficiency loader hydraulic mechanical transmission system according to claim 3, characterized in that: The gear transmission comprises a second route-selective coupling device (25) which is power-connected to the fifth power bridge pivot (14), wherein the second route-selective coupling device (25) comprises a reverse gear C R and forward gear C F , the reverse gear C R and forward gear C F Power is outputted through the toothed coupler J (26) and the toothed coupler K (27) respectively, and also includes a third path-selective coupling device (28) which is connected to the second path-selective coupling device (25) through a second toothed coupling transmission mechanism, and a fourth path-selective coupling device (29) which is connected to the second path-selective coupling device (25) through a second toothed coupling transmission mechanism.

5. The high-efficiency loader hydraulic mechanical transmission system according to claim 4, characterized in that: The third routing coupling device (28) includes a gear position C II and gear position C III , the gear position C II and gear position C III Power is outputted through the toothed coupler L (30) and the toothed coupler M (31) respectively, and the third routing coupling device (28) inputs power through a sixth power bridge pivot (32), and a toothed coupler N (33) is provided on the sixth power bridge pivot (32), and the toothed coupler N (33) is meshed with the second toothed coupling transmission mechanism to input power; The output shaft (16) is provided with a toothed coupler O (34) and a toothed coupler P (35), wherein the toothed coupler O (34) and the toothed coupler P (35) are respectively meshed with the toothed coupler L (30) and the toothed coupler M (31); The fourth route-selective coupling device (29) comprises a gear position C I , the gear position C I Power is output through the toothed coupler Q (36), and the fourth routing coupling device (29) inputs power through the seventh power bridging pivot (37). The seventh power bridging pivot (37) is provided with a toothed coupler R (38), and the toothed coupler R (38) is meshed with the second toothed coupling transmission mechanism for power input, and the toothed coupler Q (36) is meshed with the toothed coupler O (34) on the output shaft (16) for power output.

6. The high-efficiency loader hydraulic mechanical transmission system according to claim 5, characterized in that: The second gear-profile coupling transmission mechanism comprises an eighth power bridging pivot (39) and a gear-profile coupler S (40) and a gear-profile coupler T (41) meshed with the eighth power bridging pivot (39), and also comprises a ninth power bridging pivot (42) and a gear-profile coupler U (43) and a gear-profile coupler V (44) arranged on the ninth power bridging pivot (42), the gear-profile coupler S (40) meshing with a gear-profile coupler J (26) on the second routing coupling device (25), and the gear-profile coupler T (41) meshing with the ninth power bridging pivot ( The gear coupler V (44) is engaged with the gear coupler U (43) on the second routing coupling device (25), and the gear coupler V (44) is connected to the gear coupler K (27) on the second routing coupling device (25) through an intermediate shaft gear coupler structure having the same structure as the eighth power bridge pivot (39), the gear coupler S (40) and the gear coupler T (41), and is engaged with the gear coupler N (33) on the sixth power bridge pivot (32) and the gear coupler R (38) on the seventh power bridge pivot (37) for power transmission.

7. A control method for the high-efficiency loader hydromechanical transmission system according to any one of claims 1 to 6, characterized in that: Including excavation and transportation conditions; The shoveling and digging working condition is divided into a shoveling and digging forward gear and a shoveling and digging reverse gear; The transport working conditions are divided into transport forward first gear, transport forward second gear, transport forward third gear, transport reverse first gear, transport reverse second gear and transport reverse third gear.

8. The control method of the high-efficiency loader hydraulic mechanical transmission system according to claim 7, characterized in that: The excavation working conditions are specifically as follows: The input shaft (1) transmits the power output by the engine to the planetary gear (3) through the planetary carrier (2), and the planetary gear (3) distributes the power to the sun gear (4) and the ring gear (6). The sun gear (4) transmits the power to the first routing coupling device (20) in the energy capacity adjustment device through the first power bridge pivot (5), and the ring gear (6) transmits the power to the pump wheel (7) in the hydraulic torque converter. The power input into the hydraulic torque converter is output to the second power bridge pivot (10) through the pump wheel (7), the turbine (8) and the guide wheel (9); When in the first gear of excavation forward, the energy capacity adjustment device works in C1 gear, and the gear transmission works in C F and C I The gear coupler F (21) outputs power, passes through the gear coupler H (23), the third power bridge pivot (11) and the gear coupler A (12), and merges with the power of the second power bridge pivot (10) at the gear coupler B (13), and then is transmitted to the gear coupler D (18) through the gear coupler B (13), and then is transmitted to the gear coupler E (19) and then to the gear coupler C (15) through the fourth power bridge pivot (17), and then is transmitted to the second routing coupling device (25) through the fifth power bridge pivot (14), and then to the gear coupler C (15). The power is transmitted to the gear coupler V (44) through the gear coupler K (27) and the intermediate shaft gear coupler, and the gear coupler V (44) transmits the power to the gear coupler R (38) on the seventh power bridge pivot (37), driving the seventh power bridge pivot (37) to rotate, and the fourth routing coupling device (29) transmits the power of the seventh power bridge pivot (37) to the gear coupler O (34) on the output shaft (16) through the gear coupler Q (36), and the gear coupler O (34) drives the output shaft (16) to rotate and transmit the power to the drive axle; When in the first gear of excavation reverse, the energy regulating device works in C1 gear and the gear transmission works in C R and C I The power inputted from the fifth power bridge pivot (14) is transmitted to the gear coupler S (40), the eighth power bridge pivot (39), the gear coupler T (41) and the gear coupler U (43) through the gear coupler J (26), and then to the ninth power bridge pivot (42). The gear coupler V (44) on the ninth power bridge pivot (42) transmits the power to the seventh power bridge pivot (37) through the gear coupler R (38), and then to the gear coupler R (38) through the gear coupler C. I The power is transmitted to the gear coupler O (34) through the gear coupler Q (36), driving the output shaft (16) to rotate, thereby transmitting the power to the drive axle.

9. The control method of the high-efficiency loader hydraulic mechanical transmission system according to claim 7, characterized in that: The specific transportation conditions are: The input shaft (1) transmits the power output by the engine to the planetary gear (3) through the planetary carrier (2), and the planetary gear (3) distributes the power to the sun gear (4) and the ring gear (6). The sun gear (4) transmits the power to the first routing coupling device (20) in the energy capacity adjustment device through the first power bridge pivot (5), and the ring gear (6) transmits the power to the pump wheel (7) in the hydraulic torque converter. The power input into the hydraulic torque converter is output to the second power bridge pivot (10) through the pump wheel (7), the turbine (8) and the guide wheel (9); When in the transport forward gear, the energy capacity adjustment device works in the C2 gear position, and the gear transmission works in the C F and C I The first selective-routing coupling device (20) outputs power from the toothed coupler G (22), passes through the toothed coupler I (24) and the third power bridge pivot (11), and outputs power from the toothed coupler A (12), merges with the power of the second power bridge pivot (10) on the toothed coupler B (13), and then passes through the toothed coupler B (13) to the toothed coupler D (18), and then passes through the fourth power bridge pivot (17) to the toothed coupler E (19), and then to the toothed coupler C (15), and then passes through the fifth power bridge pivot (14) to the second selective-routing coupling device (20). The device (25) transmits power to the gear coupler V (44) through the gear coupler K (27) and the intermediate shaft gear coupler, and the gear coupler V (44) transmits power to the gear coupler R (38) on the seventh power bridge pivot (37), driving the seventh power bridge pivot (37) to rotate, and the fourth routing coupling device (29) transmits power of the seventh power bridge pivot (37) to the gear coupler O (34) on the output shaft (16) through the gear coupler Q (36), and the gear coupler O (34) drives the output shaft (16) to rotate and transmit power to the drive axle; When in the transport forward second gear, the energy capacity adjustment device works in the C2 gear position, and the gear transmission works in the C F and C II The gear coupler V (44) drives the gear coupler N (33) on the sixth power bridge pivot (32) to rotate, and the gear coupler N (33) drives the sixth power bridge pivot (32) to rotate, and passes through the C of the third routing coupling device (28). II In the gear position, the gear coupler L (30) outputs power, the gear coupler L (30) drives the gear coupler O (34) to rotate, and finally the output shaft (16) outputs power to the drive axle; When in the third gear for transport, the energy regulating device works in the C2 gear position, and the gearbox works in the C F and C III The gear coupler V (44) drives the gear coupler N (33) on the sixth power bridge pivot (32) to rotate, and the gear coupler N (33) drives the sixth power bridge pivot (32) to rotate, and passes through the C of the third routing coupling device (28). III In the gear position, the gear coupler M (31) outputs power, the gear coupler M (31) drives the gear coupler P (35) to rotate, and finally the output shaft (16) outputs power to the drive axle; When in the transport reverse gear, the energy capacity adjustment device works in the C2 gear position, and the gear transmission works in the C R and C I The power inputted from the fifth power bridge pivot (14) is transmitted to the gear coupler S (40), the eighth power bridge pivot (39), the gear coupler T (41) and the gear coupler U (43) through the gear coupler J (26), and then to the ninth power bridge pivot (42). The gear coupler V (44) on the ninth power bridge pivot (42) transmits the power to the seventh power bridge pivot (37) through the gear coupler R (38), and then to the gear coupler R (38) through the gear coupler C. I The power is transmitted to the gear coupler O (34) through the gear coupler Q (36) to drive the output shaft (16) to rotate and transmit the power to the drive axle; When in the transport reverse second gear, the energy capacity adjustment device works in the C2 gear position, and the gear transmission works in the C R and C II The power inputted from the fifth power bridge pivot (14) is transmitted to the gear coupler S (40), the eighth power bridge pivot (39), the gear coupler T (41) and the gear coupler U (43) through the gear coupler J (26), and then to the ninth power bridge pivot (42). The gear coupler V (44) drives the gear coupler N (33) on the sixth power bridge pivot (32) to rotate. The gear coupler N (33) drives the sixth power bridge pivot (32) to rotate, and then passes through the C of the third routing coupling device (28). II In the gear position, the gear coupler L (30) outputs power, the gear coupler L (30) drives the gear coupler O (34) to rotate, and finally the output shaft (16) outputs power to the drive axle; When in the third gear of transport reverse, the energy capacity adjustment device works in the C2 gear position and the gear transmission works in the C R and C III The power inputted from the fifth power bridge pivot (14) is transmitted to the gear coupler S (40), the eighth power bridge pivot (39), the gear coupler T (41) and the gear coupler U (43) through the gear coupler J (26), and then to the ninth power bridge pivot (42). The gear coupler V (44) drives the gear coupler N (33) on the sixth power bridge pivot (32) to rotate. The gear coupler N (33) drives the sixth power bridge pivot (32) to rotate, and then passes through the C of the third routing coupling device (28). III In the gear position, the gear coupler M (31) outputs power, the gear coupler M (31) drives the gear coupler P (35) to rotate, and finally the output shaft (16) outputs power to the drive axle.

10. A loader, characterized in that: The high-efficiency loader hydromechanical transmission system and control method as described in claims 1 to 9 are used.

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