A distributed hydraulic system for a loader and a loader

Abstract

The present invention provides a distributed hydraulic system for a loader and a loader. The distributed hydraulic system for the loader includes a variable working pump, a variable steering pump, a flow distribution valve group, an independent control valve group for the boom inlet and outlet, an independent control valve group for the bucket inlet and outlet, a large-displacement steering gear, and a controller. The variable working pump and the variable steering pump respectively output the hydraulic oil in the fuel tank to the flow distribution valve group. The flow distribution valve group is respectively connected to the independent control valve group for the boom inlet and outlet, the independent control valve group for the bucket inlet and outlet, and the large-displacement steering gear. The independent control valve group for the boom inlet and outlet, the independent control valve group for the bucket inlet and outlet, and the large-displacement steering gear are respectively connected to the boom cylinder, the bucket cylinder, and the steering cylinder. The controller is used to control the operation of the pump and valve group to control the flow and distribution of the hydraulic oil. The hydraulic system of the present application can improve the energy-saving effect of the loader, and when the boom cylinder, the bucket cylinder, and the steering cylinder perform combined actions, the loads do not interfere with each other, and the operation comfort is better.

Description

Technical Field

[0001] The present invention relates to the technical field of loader hydraulic systems, and more particularly, to a distributed hydraulic system for a loader and a loader. Background Art

[0002] At present, the electrification of loaders has become an inevitable trend in the industry, but it is still in its infancy. Generally, an electric motor is directly used to replace the engine to drive the original hydraulic transmission system. Although power energy conservation is achieved, the problem of low efficiency of the hydraulic transmission system has not been solved, resulting in high power consumption of the whole machine, large battery capacity, and short battery life. Directly driving each actuator with an electro-hydrostatic system is one of the ideal solutions to improve the energy efficiency of the hydraulic system. However, there is currently no high-power electro-hydrostatic direct drive system suitable for loaders at home and abroad.

[0003] In view of this, the applicant has put forward this application after studying the existing technologies. Summary of the Invention

[0004] The present invention provides a distributed hydraulic system for a loader, aiming to improve at least one of the above technical problems.

[0005] To solve the above technical problems, the present invention provides a distributed hydraulic system for a loader, including a variable working pump, a variable steering pump, a flow distribution valve group, an independent control valve group for the boom inlet and outlet, an independent control valve group for the bucket inlet and outlet, a large-displacement steering gear, and a controller, wherein:

[0006] The variable working pump and the variable steering pump respectively output the hydraulic oil in the fuel tank to the flow distribution valve group through a first oil supply pipeline and a second oil supply pipeline. The oil outlet ends of the flow distribution valve group are respectively connected with a first branch, a second branch, and a third branch. The first branch communicates with the independent control valve group for the boom inlet and outlet, the second branch communicates with the independent control valve group for the bucket inlet and outlet, and the third branch communicates with the large-displacement steering gear;

[0007] The oil outlet end of the independent control valve group for the boom inlet and outlet communicates with the boom cylinder, the oil outlet end of the independent control valve group for the bucket inlet and outlet communicates with the bucket cylinder, and the large-displacement steering gear communicates with the steering cylinder;

[0008] The independent control valve group for the boom inlet and outlet, the independent control valve group for the bucket inlet and outlet, and the large-displacement steering gear are all provided with oil return ports communicating with the fuel tank;

[0009] The controller is used to control the operation of the variable working pump, the variable steering pump, the flow distribution valve group, the independent control valve group for the boom inlet and outlet, the independent control valve group for the bucket inlet and outlet, and the large-displacement steering gear to control the flow and distribution of the hydraulic oil.

[0010] As a further optimization, a boom pump system relief valve group is connected to the first oil supply pipeline. The boom pump system relief valve group includes a first high-pressure relief valve and a first low-pressure relief valve. The oil inlets of the first high-pressure relief valve and the first low-pressure relief valve are communicated with the first oil supply pipeline, and the oil outlets are communicated with the fuel tank.

[0011] As a further optimization, a steering pump system relief valve group is connected to the second oil supply pipeline. The steering pump system relief valve group includes a second high-pressure relief valve and a second low-pressure relief valve. The oil inlets of the second high-pressure relief valve and the second low-pressure relief valve are communicated with the second oil supply pipeline, and the oil outlets are communicated with the fuel tank.

[0012] The flow distribution valve group includes a first flow dividing valve, a second flow dividing valve, a first flow distribution valve, a second flow distribution valve and a third flow distribution valve. The first flow dividing valve and the second flow dividing valve are five-way valves. The oil inlet of the first flow dividing valve is connected to the first oil supply pipeline. Two of the oil ports of the first flow dividing valve are respectively communicated with the first branch and the first flow distribution valve. The oil inlet of the second flow dividing valve is communicated with the second oil supply pipeline. Two of the oil ports of the second flow dividing valve are respectively communicated with the second branch and the third branch. The oil outlet of the first flow distribution valve is communicated with the second branch. The second flow distribution valve is arranged on the second branch and is located before the connection point between the first flow distribution valve and the second branch. The oil inlet of the third flow distribution valve is communicated with the second branch between the second flow dividing valve and the second flow distribution valve, and its oil outlet is communicated with the first branch. The third flow distribution valve is communicated with the oil outlet of the second flow distribution valve, and a shuttle valve is arranged between them.

[0013] As a further optimization, the other two oil ports of the first flow dividing valve are respectively connected with a first left pilot oil pipe and a first right pilot oil pipe. The other end of the first left pilot oil pipe is connected to the pipeline between the first flow distribution valve and the second branch. The other end of the first right pilot oil pipe is connected to the pipeline between the first flow dividing valve and the first flow distribution valve.

[0014] As a further optimization, the other two oil ports of the second flow dividing valve are respectively connected with a second left pilot oil pipe and a second right pilot oil pipe. The other end of the second left pilot oil pipe is connected to the shuttle valve. The second right pilot oil pipe is connected to the second branch before the connection point of the third flow distribution valve.

[0015] As a further optimization, the boom inlet and outlet independent control valve group includes a first large chamber potential energy control valve, a first large chamber oil return control valve, a first large chamber oil inlet control valve, a first differential control valve, a first small chamber oil inlet control valve, a first small chamber oil return control valve, and a make-up oil check valve. The first large chamber oil return control valve, the first differential control valve, and the first large chamber oil inlet control valve are connected to the large chamber of the boom cylinder. The first small chamber oil inlet control valve, the first small chamber oil return control valve, and the first differential control valve are connected to the small chamber of the boom cylinder. The oil inlets of the first large chamber oil inlet control valve and the first small chamber oil inlet control valve are connected to the first branch. The oil outlets of the first large chamber oil return control valve and the first small chamber oil return control valve are connected to the oil return port of the boom inlet and outlet independent control valve group. The make-up oil check valve is connected to the small chamber of the boom cylinder and the oil return port of the boom inlet and outlet independent control valve group for making up oil for the small chamber of the boom cylinder. The boom inlet and outlet independent control valve group is provided with a potential energy recovery port, and the first large chamber potential energy control valve is connected to the boom cylinder and the potential energy recovery port of the boom inlet and outlet independent control valve group.

[0016] As a further optimization, the bucket inlet and outlet independent control valve group includes a second large chamber potential energy control valve, a second large chamber oil return control valve, a second large chamber oil inlet control valve, a second differential control valve, a second small chamber oil inlet control valve, a second small chamber oil return control valve, and a buffer overflow valve group. The second large chamber oil return control valve, the second differential control valve, and the second large chamber oil inlet control valve are connected to the large chamber of the bucket cylinder. The second small chamber oil inlet control valve, the second small chamber oil return control valve, and the second differential control valve are connected to the small chamber of the bucket cylinder. The oil inlets of the second large chamber oil inlet control valve and the second small chamber oil inlet control valve are connected to the second branch. The oil outlets of the second large chamber oil return control valve and the second small chamber oil return control valve are connected to the oil return port of the bucket inlet and outlet independent control valve group. The bucket inlet and outlet independent control valve group is provided with a potential energy recovery port, and the second large chamber potential energy control valve communicates with the bucket cylinder and the potential energy recovery port of the bucket inlet and outlet independent control valve group. The buffer overflow valve group is connected to the bucket cylinder and the oil return port of the bucket inlet and outlet independent control valve group.

[0017] As a further optimization, check valves are provided at the oil outlet ends of the first branch, the second branch, and the third branch.

[0018] The present application further provides a wheel loader, including any one of the above-mentioned distributed hydraulic systems for wheel loaders.

[0019] By adopting the above technical solutions, the present invention can achieve the following technical effects:

[0020] The distributed hydraulic system of the loader provided by the present invention can enable the variable steering pump, variable working pump, and flow distribution valve group to play a variable adjustment role under all working conditions, thereby fully exerting the flow adjustment energy-saving effect of the variable steering pump, variable working pump, and flow distribution valve group, and further improving the energy-saving effect of the distributed hydraulic system.

[0021] First, it can improve the energy-saving effect of the loader; second, it can realize the composite actions of the boom cylinder, bucket cylinder, and steering cylinder, and during the composite actions, the loads do not interfere with each other, and the operation comfort is better; finally, the controller adopts electro-hydraulic proportional control, and the control accuracy is higher. Brief Description of the Drawings

[0022] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings required for the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of the present invention, and therefore should not be regarded as limiting the scope. For those of ordinary skill in the art, without creative efforts, other related drawings can also be obtained based on these drawings.

[0023] Figure 1 is the schematic diagram of the distributed hydraulic system of the loader of the present invention;

[0024] Reference numerals in the figure: 1 - variable working pump; 2 - variable steering pump; 31 - boom pump system overflow valve group; 32 - steering pump system overflow valve group; 33 - first high-pressure overflow valve; 34 - first low-pressure overflow valve; 35 - second high-pressure overflow valve; 36 - second low-pressure overflow valve; 4 - flow distribution valve group; 41 first flow dividing valve; 411 - first left pilot oil pipe; 412 - first right pilot oil pipe; 42 second flow dividing valve; 421 - second left pilot oil pipe; 422 - second right pilot oil pipe; 43 - first flow distribution valve; 44 - second flow distribution valve; 45 - third flow distribution valve; 48 - shuttle valve; 5 - large-displacement steering gear; 51 - steering cylinder; 6 - boom inlet and outlet independent control valve group; 61 - first large chamber potential energy control valve; 62 - first large chamber oil return control valve; 63 - large chamber oil inlet control valve; 64 - first differential control valve; 65 - first small chamber oil inlet control valve; 66 - first small chamber oil return control valve; 67 - oil replenishing check valve; 68 - boom cylinder; 7 - bucket inlet and outlet independent control valve group; 71 - second large chamber potential energy control valve; 72 - second large chamber oil return control valve; 73 - second large chamber oil inlet control valve; 74 - second differential control valve; 75 - second small chamber oil inlet control valve; 76 - second small chamber oil return control valve; 77 - buffer overflow valve group; 78 - bucket cylinder; 8 - controller; 9 - fuel tank; 91 - first oil supply pipeline; 92 - second oil supply pipeline; 93 - first branch; 94 - second branch; 95 - third branch; 96 - oil return pipeline; 97 - check valve. Detailed Embodiments

[0025] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are some, but not all, of the embodiments of the present invention. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts fall within the scope of protection of the present invention. Therefore, the following detailed description of the embodiments of the present invention provided in the accompanying drawings is not intended to limit the scope of the claimed invention, but merely represents selected embodiments of the present invention. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts fall within the scope of protection of the present invention.

[0026] Embodiment

[0027] As Figure 1 shown, to solve the above technical problems, the present invention provides a loader distributed hydraulic system, including a variable working pump 1, a variable steering pump 2, a flow distribution valve group 4, a boom inlet and outlet independent control valve group 6, a bucket inlet and outlet independent control valve group 7, a large-displacement steering gear 5, and a controller 8, wherein:

[0028] The variable working pump 1 and the variable steering pump 2 respectively pump the hydraulic oil in the fuel tank 9 to the flow distribution valve group 4 through a first oil supply pipeline 91 and a second oil supply pipeline 92. The oil outlet ends of the flow distribution valve group 4 are respectively connected with a first branch 93, a second branch 94, and a third branch 95. The first branch 93 communicates with the oil inlet P1 of the boom inlet and outlet independent control valve group. The second branch 94 communicates with the oil inlet P2 of the bucket inlet and outlet independent control valve group. The third branch 95 communicates with the large-displacement steering gear 5.

[0029] The oil outlet end of the boom inlet and outlet independent control valve group 6 communicates with a boom cylinder 68. The oil outlet end of the bucket inlet and outlet independent control valve group 7 communicates with a bucket cylinder 78. The large-displacement steering gear 5 communicates with a steering cylinder 51;

[0030] The boom inlet and outlet independent control valve group 6, the bucket inlet and outlet independent control valve group 7, and the large-displacement steering gear 5 are all provided with oil return ports. Among them, the boom inlet and outlet independent control valve group 6 is provided with an oil return port T1, the bucket inlet and outlet independent control valve group 7 is provided with an oil return port T2, and the three oil return ports are all connected to the fuel tank 9 through an oil return pipeline 96 for oil return;

[0031] The controller 8 is used to control the operation of the variable working pump 1, the variable steering pump 2, the flow distribution valve group 4, the boom inlet and outlet independent control valve group 6, the bucket inlet and outlet independent control valve group 7, and the large-displacement steering gear 5, so as to control the flow and distribution of hydraulic oil, so that the boom cylinder, the bucket cylinder and the steering cylinder work, and realize the traveling, steering and lifting of the bucket of the loader, etc.

[0032] In this embodiment, the controller 8 adopts electro-hydraulic proportional control. When the loader is only in the steering condition, the controller 8 controls the displacement and speed of the variable steering pump 2 to increase the required flow rate, and distributes it through the flow distribution valve group 4 to the large-displacement steering gear 5 to the steering cylinder 51 to drive the steering cylinder 51 to work. When the loader is in the steering condition and when the boom cylinder 68 or the bucket cylinder 78 is working, the variable steering pump 2 needs to provide flow. The controller 8 will control the flow distribution valve group 4 to give priority to providing the required flow rate to the steering cylinder 51, and then provide the required flow rate to the boom cylinder 68 or the bucket cylinder 78.

[0033] Further, a boom pump system relief valve group 31 is connected to the first oil supply pipeline 91 in a branch manner. The boom pump system relief valve group 31 includes a first high-pressure relief valve 33 and a first low-pressure relief valve 34. The inlet ends of the first high-pressure relief valve 33 and the first low-pressure relief valve 34 are communicated with the first oil supply pipeline 91, and the outlet ends are communicated with the fuel tank 9. A steering pump system relief valve group 32 is connected to the second oil supply pipeline 92 in a branch manner. The steering pump system relief valve group 32 includes a second high-pressure relief valve 35 and a second low-pressure relief valve 36. The inlet ends of the second high-pressure relief valve 35 and the second low-pressure relief valve 36 are communicated with the second oil supply pipeline 92, and the outlet ends are communicated with the fuel tank 9. By setting the relief valve group, when the pressure in the oil supply pipeline exceeds the set value, the excess hydraulic oil can flow back to the fuel tank 9, so as to avoid the risk of equipment damage caused by too high system pressure, or after the hydraulic system is closed, the oil in the hydraulic system can flow back to the fuel tank 9.

[0034] Further, the flow distribution valve group 4 includes a first shunt valve 41, a second shunt valve 42, a first flow distribution valve 43, a second flow distribution valve 44, and a third flow distribution valve 45. Among them, both the first shunt valve 41 and the second shunt valve 42 are five-way valves. The oil inlet of the first shunt valve 41 is connected to the first oil supply pipeline 91, and two of its oil outlets are respectively connected to the first branch 93 and the first flow distribution valve 43. The oil inlet of the second shunt valve 42 is connected to the second oil supply pipeline 92, and two of its oil outlets are respectively connected to the second branch 94 and the third branch 95. The oil outlet end of the first flow distribution valve 43 is connected to the second branch 94. The second flow distribution valve 44 is arranged on the second branch 94 and is located before the connection point of the first flow distribution valve 43 and the second branch 94. The oil inlet end of the third flow distribution valve 45 is connected to the second branch 94 between the second shunt valve 42 and the second flow distribution valve 44, and its oil outlet end is connected to the first branch 93. The oil outlet end of the third flow distribution valve 45 is connected to the oil outlet end of the second flow distribution valve 44, and a shuttle valve 48 is provided therebetween.

[0035] Further, the other two oil ports of the first shunt valve 41 are respectively connected with a first left pilot oil pipe 411 and a first right pilot oil pipe 412. The other end of the first left pilot oil pipe 411 is connected to the pipeline between the first flow distribution valve 43 and the second branch 94, and the other end of the first right pilot oil pipe 412 is connected to the pipeline between the first shunt valve 41 and the first flow distribution valve 43. The other two oil ports of the second shunt valve are respectively connected with a second left pilot oil pipe 421 and a second right pilot oil pipe 422. The second left pilot oil pipe 421 is connected to the oil outlet of the shuttle valve 48, and the second right pilot oil pipe 422 is connected to the second branch 94 before the connection point of the third flow distribution valve 45.

[0036] Further, the boom inlet and outlet independent control valve group 6 further includes a first large chamber potential energy control valve 61, a first large chamber oil return control valve 62, a first large chamber oil inlet control valve 63, a first differential control valve 64, a first small chamber oil inlet control valve 65, a first small chamber oil return control valve 66, and a make-up oil check valve 67. The oil inlet ends of the first large chamber oil inlet control valve 63 and the first small chamber oil inlet control valve 65 are connected to the oil inlet P1. The oil outlet end of the first large chamber oil inlet control valve 63 is connected to the large chamber of the boom cylinder 68. The oil outlet end of the first small chamber oil inlet control valve 65 is connected to the small chamber of the boom cylinder 68. The first differential control valve 64 is connected to the large chamber and the small chamber of the boom cylinder 68. The first large chamber oil return control valve 62 connects the large chamber of the boom cylinder 68 to the oil return port T1, so that the oil in the large chamber of the boom cylinder 68 can flow back to the fuel tank 9. The first small chamber oil return control valve 66 connects the small chamber of the boom cylinder 68 to the oil return port T1, so that the oil in the small chamber of the boom cylinder 68 can flow back to the fuel tank 9. The make-up oil check valve 67 connects the small chamber of the boom cylinder 68 to the oil return port T1, thereby making it possible to make up oil for the small chamber of the boom cylinder 68. The boom inlet and outlet independent control valve group 6 is also provided with a potential energy recovery port R1. The first large chamber potential energy control valve 61 is connected to the large chamber of the boom cylinder 68 and the potential energy recovery port R1 to recover the potential energy of the boom cylinder 68.

[0037] The bucket inlet and outlet independent control valve group 7 further includes a first large chamber potential energy control valve 71, a second large chamber oil return control valve 72, a second large chamber oil inlet control valve 73, a second differential control valve 74, a second small chamber oil inlet control valve 75, a second small chamber oil return control valve 76, and a buffer overflow valve group 77. The oil inlet ends of the second large chamber oil inlet control valve 73 and the second small chamber oil inlet control valve 75 are connected to the oil inlet P2. The oil outlet end of the second large chamber oil inlet control valve 73 is connected to the large chamber of the bucket cylinder 78. The oil outlet end of the second small chamber oil inlet control valve 75 is connected to the small chamber of the bucket cylinder 78. The second differential control valve 74 is connected to the large chamber and the small chamber of the bucket cylinder. The second large chamber oil return control valve 72 connects the large chamber of the bucket cylinder 78 to the oil return port T2, so that the oil in the large chamber of the bucket cylinder 78 can flow back to the fuel tank 9. The small chamber oil return control valve (76) connects the small chamber of the bucket cylinder 78 to the oil return port T2, so that the oil in the small chamber of the bucket cylinder 78 can flow back to the fuel tank 9. The bucket inlet and outlet independent control valve group 7 is also provided with a potential energy recovery port R2. The second large chamber potential energy control valve 71 is connected to the large chamber of the bucket cylinder 78 and the potential energy recovery port R2 to recover the potential energy of the bucket cylinder. The buffer overflow valve group 77 is connected to the large chamber, the small chamber, and the oil return port T2 of the bucket cylinder 78 to ensure that the bucket cylinder 78 will not be overloaded during operation.

[0038] Further, check valves 97 are provided at the oil outlets of the first branch 93, the second branch 94, and the third branch 95. Additionally, directional valves can be provided at the oil outlets of the high-pressure relief valve and the low-pressure relief valve to prevent reverse flow of the hydraulic oil.

[0039] In the present application, the variable working pump 1 and the variable steering pump 2 can provide the flow rate required by the system according to the control instructions of the controller 8, and supply hydraulic oil sources to the boom cylinder 68, the bucket cylinder 78, and the steering cylinder 51 respectively through the shunt and confluence in the flow distribution valve group 4. This enables the boom cylinder 68, the bucket cylinder 78, and the steering cylinder 51 to work independently simultaneously without being affected by insufficient oil supply in the hydraulic system, thereby solving the problem of inability to perform combined actions caused by insufficient oil supply in the hydraulic system.

[0040] When the boom cylinder 68 is lowering the cylinder, the controller 8 controls the first large-chamber oil return control valve 62 and the first differential control valve 64 in the boom inlet and outlet independent control valve group 6 to work, and the other valves in the boom inlet and outlet independent control valve group 6 do not work, enabling the flow regeneration function.

[0041] When the boom cylinder 68 is lowering the cylinder, the controller 8 controls the first large-chamber oil return control valve 62, the first small-chamber oil inlet control valve 65, and the first differential control valve 64 in the boom inlet and outlet independent control valve group 6 to work, and the other valves in the boom inlet and outlet independent control valve group 6 do not work, enabling the boom floating condition function.

[0042] When the bucket cylinder 78 is lowering the cylinder, the controller 8 controls the second large-chamber oil return control valve 72 and the second differential control valve 74 in the bucket inlet and outlet independent control valve group 7 to work, and the other valves in the bucket inlet and outlet independent control valve group 7 do not work, enabling the flow regeneration function.

[0043] The present application further provides a wheel loader, including the wheel loader distributed hydraulic system described in any one of the above. By adopting the above wheel loader distributed hydraulic system, first, the energy-saving effect of the wheel loader can be improved; second, combined actions of the boom cylinder, the bucket cylinder, and the steering cylinder can be achieved, and during the combined actions, the loads do not interfere with each other, and the operating comfort is better; finally, the controller 8 adopts electro-hydraulic proportional control, and the control accuracy is higher.

[0044] Obviously, the above embodiments of the present invention are merely examples for clearly explaining the present invention, rather than limitations on the implementation manners of the present invention. For those of ordinary skill in the art, other different forms of changes or modifications can be made based on the above description. It is not necessary and impossible to enumerate all implementation manners here. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the claims of the present invention.

[0045] The above is only the preferred implementation manner of the present invention and is not used to limit the present invention. For those skilled in the art, the present invention can have various changes and modifications. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A distributed hydraulic system for a loader, characterized in that: It includes a variable working pump, a variable steering pump, a flow distribution valve group, an independent control valve group for the inlet and outlet of the boom, an independent control valve group for the inlet and outlet of the bucket, a large-displacement steering gear and a controller, among which: The variable working pump and the variable steering pump output the oil in the oil tank to the flow distribution valve group through the first oil supply pipeline and the second oil supply pipeline respectively. The oil outlet end of the flow distribution valve group is connected to the first branch, the second branch and the third branch respectively. The first branch is connected to the boom inlet and outlet independent control valve group, the second branch is connected to the bucket inlet and outlet independent control valve group, and the third branch is connected to the large-displacement steering gear; The oil outlet end of the boom inlet and outlet independent control valve group is connected to the boom cylinder, the oil outlet end of the bucket inlet and outlet independent control valve group is connected to the bucket cylinder, and the large-displacement steering gear is connected to the steering cylinder; The boom inlet and outlet independent control valve group, the bucket inlet and outlet independent control valve group and the large-displacement steering gear are all provided with an oil return port connected to the oil tank; The controller is used to control the operation of the variable working pump, the variable steering pump, the flow distribution valve group, the boom inlet and outlet independent control valve group, the bucket inlet and outlet independent control valve group and the large-displacement steering gear to control the flow and distribution of the hydraulic oil; The flow distribution valve group includes a first diverter valve, a second diverter valve, a first distribution valve, a second distribution valve and a third distribution valve. The first diverter valve and the second diverter valve are five-way valves. The oil inlet of the first diverter valve is connected to the first oil supply pipeline, and two of the oil ports of the first diverter valve are respectively connected to the first branch and the first distribution valve; the oil inlet of the second diverter valve is connected to the second oil supply pipeline, and two of the oil ports of the second diverter valve are respectively connected to the second branch and the third branch. The oil outlet of the first distribution valve is connected to the second branch. The second distribution valve is arranged on the second branch and is located before the connection point between the first distribution valve and the second branch. The oil inlet of the third distribution valve is connected to the second branch between the second diverter valve and the second distribution valve, and its oil outlet is connected to the first branch. The third distribution valve is connected to the oil outlet of the second distribution valve, and a shuttle valve is arranged between them.

2. A loader distributed hydraulic system according to claim 1, characterized in that The first oil supply pipeline is connected to a boom pump system overflow valve group, and the boom pump system overflow valve group includes a first high-pressure overflow valve and a first low-pressure overflow valve. The oil inlet ends of the first high-pressure overflow valve and the first low-pressure overflow valve are connected to the first oil supply pipeline, and the oil outlet ends are connected to the oil tank.

3. A loader distributed hydraulic system according to claim 1, characterized in that The second oil supply pipeline is connected to a steering pump system overflow valve group, and the steering pump system overflow valve group includes a second high-pressure overflow valve and a second low-pressure overflow valve. The oil inlet ends of the second high-pressure overflow valve and the second low-pressure overflow valve are connected to the second oil supply pipeline, and the oil outlet ends are connected to the oil tank.

4. A loader distributed hydraulic system according to claim 1, characterized in that The other two oil ports of the first diverter valve are respectively connected to the first left pilot oil pipe and the first right pilot oil pipe. The other end of the first left pilot oil pipe is connected to the pipeline between the first distribution valve and the second branch, and the other end of the first right pilot oil pipe is connected to the pipeline between the first diverter valve and the first distribution valve.

5. A loader distributed hydraulic system according to claim 1, characterized in that The other two oil ports of the second diverter valve are respectively connected to the second left pilot oil pipe and the second right pilot oil pipe. The other end of the second left pilot oil pipe is connected to the shuttle valve, and the second right pilot oil pipe is connected to the second branch before the connection point of the third distribution valve.

6. A loader distributed hydraulic system according to claim 1, characterized in that The boom inlet and outlet independent control valve group includes a first large cavity potential energy control valve, a first large cavity oil return control valve, a first large cavity oil inlet control valve, a first differential control valve, a first small cavity oil inlet control valve, a first small cavity oil return control valve and an oil replenishment check valve. The first large cavity oil return control valve, the first differential control valve and the first large cavity oil inlet control valve are connected to the large cavity of the boom cylinder, the first small cavity oil inlet control valve, the first small cavity oil return control valve and the first differential control valve are connected to the small cavity of the boom cylinder, and the first large cavity oil inlet control valve and the first The oil inlet of the small-chamber oil inlet control valve is connected to the first branch, the oil outlets of the first large-chamber oil return control valve and the first small-chamber oil return control valve are connected to the oil return port of the boom inlet and outlet independent control valve group, the oil replenishment check valve is connected to the small chamber of the boom cylinder and the oil return port of the boom inlet and outlet independent control valve group, and is used to replenish oil to the small chamber of the boom cylinder. The boom inlet and outlet independent control valve group is provided with a potential energy recovery port, and the first large-chamber potential energy control valve is connected to the boom cylinder and the potential energy recovery port of the boom inlet and outlet independent control valve group.

7. A loader distributed hydraulic system according to claim 1, characterized in that The bucket inlet and outlet independent control valve group includes a second large cavity potential energy control valve, a second large cavity oil return control valve, a second large cavity oil inlet control valve, a second differential control valve, a second small cavity oil inlet control valve, a second small cavity oil return control valve and a buffer overflow valve group. The second large cavity oil return control valve, the second differential control valve and the second large cavity oil inlet control valve are connected to the large cavity of the bucket cylinder, the second small cavity oil inlet control valve, the second small cavity oil return control valve and the second differential control valve are connected to the small cavity of the bucket cylinder, and the second large cavity The oil inlet control valve and the oil inlet of the second small chamber oil inlet control valve are connected to the second branch, the oil outlets of the second large chamber oil return control valve and the second small chamber oil return control valve are connected to the oil return port of the bucket inlet and outlet independent control valve group, the bucket inlet and outlet independent control valve group is provided with a potential energy recovery port, the second large chamber potential energy control valve is connected to the bucket cylinder and the potential energy recovery port of the bucket inlet and outlet independent control valve group, and the buffer overflow valve group is connected to the bucket cylinder and the oil return port of the bucket inlet and outlet independent control valve group.

8. A loader distributed hydraulic system according to claim 1, characterized in that The oil outlet ends of the first branch, the second branch and the third branch are all provided with a one-way valve.

9. A loader, characterized in that , including a loader distributed hydraulic system as described in any one of claims 1-8.

Images