Loader distributed hydraulic system and loader

Abstract

The invention provides a loader distributed hydraulic system and a load.The loader distributed hydraulic system comprises a variable working pump, a variable steering pump, a flow distribution valve set, a movable arm inlet and outlet independent control valve set, a bucket inlet and outlet independent control valve set, a large-displacement steering gear and a controller; the variable working pump and the variable steering pump output oil in the oil tank to the flow distribution valve set, and the flow distribution valve set is communicated with the movable arm inlet and outlet independent control valve set, the bucket inlet and outlet independent control valve set and the large-displacement steering gear. The movable arm inlet and outlet independent control valve group, the bucket inlet and outlet independent control valve group and the large-displacement steering gear are respectively communicated with the movable arm oil cylinder, the bucket oil cylinder and the steering oil cylinder; the controller is used for controlling the flow and distribution of hydraulic oil when the pump machine valve group works. According to the hydraulic system, the energy-saving effect of the loader can be improved, loads do not interfere with one another when the movable arm oil cylinder, the bucket oil cylinder and the steering oil cylinder act in a composite mode, and the operation comfort is better.

Description

Technical Field

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

[0002] At present, the electrification of loaders has become an inevitable trend in the development of the industry, but it is still in its infancy. Generally, motors are directly used instead of engines to drive the original hydraulic transmission system. Although power energy saving 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. Direct drive of each actuator with an electrostatic hydraulic system is one of the ideal solutions to improve the energy efficiency of the hydraulic system. However, there is currently no high-power electrostatic hydraulic direct drive system suitable for loaders at home and abroad.

[0003] In view of this, the applicant filed this application after studying the existing technology. 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-mentioned technical problems.

[0005] In order 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 boom inlet and outlet, an independent control valve group for bucket inlet and outlet, a large-displacement steering gear and a controller, wherein: 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 hydraulic oil.

[0006] As a further optimization, a boom pump system overflow valve group is connected to the first oil supply pipeline, 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.

[0007] As a further optimization, a steering pump system overflow valve group is connected to the second oil supply pipeline, 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.

[0008] 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.

[0009] As a further optimization, 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.

[0010] As a further optimization, 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.

[0011] As a further optimization, 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 oil inlet of the first 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 one-way 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.

[0012] As a further optimization, 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. 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, and 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. 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.

[0013] As a further optimization, one-way valves are provided at the oil outlet ends of the first branch, the second branch and the third branch.

[0014] The present application further provides a loader, comprising any of the above-mentioned distributed hydraulic systems for the loader.

[0015] By adopting the above technical solution, the present invention can achieve the following technical effects: The distributed hydraulic system for loaders provided by the present invention can realize the variable steering pump, the variable working pump and the distribution valve group to play a role of variable regulation under all working conditions, thereby giving full play to the flow regulation energy-saving effect of the variable steering pump, the variable working pump and the distribution valve group, thereby improving the energy-saving effect of the distributed hydraulic system.

[0016] Firstly, it can improve the energy-saving effect of the loader; secondly, it can realize the compound action of the boom cylinder, bucket cylinder and steering cylinder, and during the compound action, the loads do not interfere with each other, and the operation comfort is better; finally, the controller adopts electric proportional control, which has higher control accuracy. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings required for use in the embodiments will be briefly introduced below. It should be understood that the following drawings only show certain embodiments of the present invention and therefore should not be regarded as limiting the scope. For ordinary technicians in this field, other related drawings can be obtained based on these drawings without paying creative work.

[0018] Figure 1 It is a schematic diagram of the distributed hydraulic system of the loader of the present invention; Markings 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 diverter valve; 411-first left pilot oil pipe; 412-first right pilot oil pipe; 42-second diverter valve; 421-second left pilot oil pipe; 422-second right pilot oil pipe; 43-first distribution valve; 44-second distribution valve; 45-third 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 cavity potential energy control valve; 62-first large cavity 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 replenishment one-way 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-oil 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-one-way valve. DETAILED DESCRIPTION

[0019] In order to make the purpose, 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 drawings in the embodiments of the present invention. Obviously, the described embodiments are 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 making creative work are within the scope of protection of the present invention. Therefore, the following detailed description of the embodiments of the present invention provided in the drawings is not intended to limit the scope of the invention claimed for protection, but merely represents the selected embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of the present invention.

[0020] Example like Figure 1 As shown, in order to solve the above technical problems, the present invention provides a distributed hydraulic system for a loader, including a variable working pump 1, a variable steering pump 2, a flow distribution valve group 4, an independent control valve group for boom inlet and outlet 6, an independent control valve group for bucket inlet and outlet 7, a large-displacement steering gear 5 and a controller 8, wherein: The variable working pump 1 and the variable steering pump 2 pump the oil in the oil tank 9 to the flow distribution valve group 4 through the first oil supply pipeline 91 and the second oil supply pipeline 92 respectively. The oil outlet end of the flow distribution valve group 4 is connected to the first branch 93, the second branch 94 and the third branch 95 respectively. The first branch 93 is connected to the oil inlet P1 of the boom inlet and outlet independent control valve group, the second branch 94 is connected to the oil inlet P2 of the bucket inlet and outlet independent control valve group, and the third branch 95 is connected to the large-displacement steering gear 5.

[0021] The oil outlet of the boom inlet and outlet independent control valve group 6 is connected to the boom cylinder 68, the oil outlet of the bucket inlet and outlet independent control valve group 7 is connected to the bucket cylinder 78, and the large-displacement steering gear 5 is connected to the steering cylinder 51; 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, wherein the boom inlet and outlet independent control valve group 6 is provided with an oil return port T1, and 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 oil tank 9 through an oil return pipeline 96 for oil return; 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 the hydraulic oil, so as to make the boom cylinder, bucket cylinder and steering cylinder work, realize the movement, steering and lifting of the bucket of the loader.

[0022] In this embodiment, the controller 8 adopts electric proportional control. When the loader is only in the steering condition, the displacement and speed of the variable steering pump 2 are controlled by the controller 8 to increase the required flow, and the flow distribution valve group 4 distributes it 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 provide the required flow to the steering cylinder 51 first, and then provide the required flow to the boom cylinder 68 or the bucket cylinder 78.

[0023] Further, the first oil supply pipeline 91 is connected to a boom pump system overflow valve group 31 in a branch manner, and the boom pump system overflow valve group 31 includes a first high-pressure overflow valve 33 and a first low-pressure overflow valve 34. The oil inlet ends of the first high-pressure overflow valve 33 and the first low-pressure overflow valve 34 are in communication with the first oil supply pipeline 91, and the oil outlet ends are in communication with the oil tank 9. The second oil supply pipeline 92 is connected to a steering pump system overflow valve group 32 in a branch manner, and the steering pump system overflow valve group 32 includes a second high-pressure overflow valve 35 and a second low-pressure overflow valve 36. The oil inlet ends of the second high-pressure overflow valve 35 and the second low-pressure overflow valve 36 are in communication with the second oil supply pipeline 92, and the oil outlet ends are in communication with the oil tank 9. By setting up a relief valve group, when the pressure in the oil supply pipeline exceeds the set value, the excess hydraulic oil can flow back to the oil tank 9, thereby avoiding the risk of equipment damage caused by excessive system pressure, or after the hydraulic system is shut down, the oil in the hydraulic system can flow back to the oil tank 9.

[0024] Further, the flow distribution valve group 4 includes a first diverter valve 41, a second diverter valve 42, a first distribution valve 43, a second distribution valve 44 and a third distribution valve 45, wherein the first diverter valve 41 and the second diverter valve 42 are both five-way valves, the oil inlet of the first diverter valve 41 is connected to the first oil supply pipeline 91, wherein the two oil outlets are respectively connected to the first branch 93 and the first distribution valve 43, the oil inlet of the second diverter valve 42 is connected to the second oil supply pipeline 92, wherein the two oil outlets are respectively connected to the second branch 94 and the third distribution valve 45. Three branches 95, the oil outlet end of the first distribution valve 43 is connected to the second branch 94, the second distribution valve 44 is arranged on the second branch 94, and is located before the connection point of the first distribution valve 43 and the second branch 94, the oil inlet end of the third distribution valve 45 is connected to the second branch 94 between the second diverter valve 42 and the second distribution valve 44, and its oil outlet end is connected to the first branch 93, the oil outlet end of the third distribution valve 45 is connected to the oil outlet end of the second distribution valve 44, and a shuttle valve 48 is arranged between them.

[0025] Further, the other two oil ports of the first flow divider valve 41 are respectively connected to the first left pilot oil pipe 411 and the 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 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 flow divider valve 41 and the first distribution valve 43. The other two oil ports of the second flow divider valve are respectively connected to the second left pilot oil pipe 421 and the 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 distribution valve 45.

[0026] Furthermore, the boom inlet and outlet independent control valve group 6 also includes a first large cavity potential energy control valve 61, a first large cavity return oil control valve 62, a first large cavity oil inlet control valve 63, a first differential control valve 64, a first small cavity oil inlet control valve 65, a first small cavity return oil control valve 66 and an oil replenishment check valve 67, the oil inlet ends of the first large cavity oil inlet control valve 63 and the first small cavity oil inlet control valve 65 are connected to the oil inlet port P1, the oil outlet end of the first large cavity oil inlet control valve 63 is connected to the large cavity of the boom oil cylinder 68, and the oil outlet end of the first small cavity oil inlet control valve 65 is connected to the boom oil cylinder 68. The first differential control valve 64 is connected to the large and small chambers of the boom oil cylinder 68, the first large chamber oil return control valve 62 is connected to the large chamber of the boom oil cylinder 68 and the oil return port T1, so that the oil in the large chamber of the boom oil cylinder 68 can flow back to the oil tank 9; the first small chamber oil return control valve 66 is connected to the small chamber of the boom oil cylinder 68 and the oil return port T1, so that the oil in the small chamber of the boom oil cylinder 68 can flow back to the oil tank 9; the oil replenishment check valve 67 is connected to the small chamber of the boom oil cylinder 68 and the oil return port T1, so that the small chamber of the boom oil cylinder 68 can be replenished. The boom inlet and outlet independent control valve group 6 is also provided with a potential energy recovery port R1, and the first large chamber potential energy control valve 61 is connected to the large chamber of the boom oil cylinder 68 and the potential energy recovery port R1 to recover the potential energy of the boom oil cylinder 68.

[0027] The bucket inlet and outlet independent control valve group 7 also includes a first large cavity potential energy control valve 71, a second large cavity return oil control valve 72, a second large cavity oil inlet control valve 73, a second differential control valve 74, a second small cavity oil inlet control valve 75, a second small cavity return oil control valve 76 and a buffer overflow valve group 77. The oil inlet ends of the second large cavity oil inlet control valve 73 and the second small cavity oil inlet control valve 75 are connected to the oil inlet port P2, the oil outlet end of the second large cavity oil inlet control valve 73 is connected to the large cavity of the bucket cylinder 78, and the oil outlet end of the second small cavity oil inlet control valve 75 is connected to the small cavity of the bucket cylinder 78; the second differential control valve 74 connects the large chamber and small chamber of the bucket oil cylinder; the second large chamber oil return control valve 72 connects the large chamber of the bucket oil cylinder 78 with the oil return port T2, so that the oil in the large chamber of the bucket oil cylinder 78 can flow back to the oil tank 9; the small chamber oil return control valve (76) connects the small chamber of the bucket oil cylinder 78 with the oil return port T2, so that the oil in the small chamber of the bucket oil cylinder 78 can flow back to the oil tank 9; the bucket inlet and outlet independent control valve group 7 is also provided with a potential energy recovery port R2, and the second large chamber potential energy control valve 71 connects the large chamber of the bucket oil cylinder 78 with the potential energy recovery port R2 to recover the potential energy of the bucket oil cylinder. The buffer overflow valve group 77 is connected to the large chamber, small chamber and oil return port T2 of the bucket oil cylinder 78 to ensure that the bucket oil cylinder 78 will not be overloaded during operation.

[0028] Furthermore, one-way valves 97 are provided at the oil outlets of the first branch 93, the second branch 94 and the third branch 95. In addition, directional valves can be provided at the oil outlets of the high-pressure relief valve and the low-pressure relief valve to prevent oil backflow.

[0029] The variable working pump 1 and the variable steering pump 2 described in the present application can provide the flow required by the system according to the control instruction of the controller 8, and respectively provide the hydraulic oil source to the boom cylinder 68, the bucket cylinder 78 and the steering cylinder 51 through the flow distribution valve group 4. The boom cylinder 68, the bucket cylinder 78 and the steering cylinder 51 can work independently at the same time and are not affected by the insufficient oil supply of the hydraulic system, thereby solving the problem of being unable to perform compound actions due to the influence of insufficient oil supply of the hydraulic system.

[0030] When the boom cylinder 68 is lowered, 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 other valves in the boom inlet and outlet independent control valve group 6 do not work, thereby realizing the flow regeneration function.

[0031] When the boom cylinder 68 is lowered, 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 other valves in the boom inlet and outlet independent control valve group 6 do not work, so that the boom floating working condition function can be realized.

[0032] When the bucket cylinder 78 is lowered, 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 other valves in the bucket inlet and outlet independent control valve group 7 do not work, thereby realizing the flow regeneration function.

[0033] The present application further provides a loader, comprising any one of the above-mentioned loader distributed hydraulic systems. By adopting the above-mentioned loader distributed hydraulic system, firstly, the energy-saving effect of the loader can be improved; secondly, the compound action of the boom cylinder, bucket cylinder and steering cylinder can be realized, and during the compound action, the loads do not interfere with each other, and the operation comfort is better; finally, the controller 8 adopts electric proportional control, and the control accuracy is higher.

[0034] Obviously, the above embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the embodiments of the present invention. For those skilled 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 list all the embodiments here. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present invention should be included in the protection scope of the claims of the present invention.

[0035] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, 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 hydraulic oil.

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 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.

5. A loader distributed hydraulic system according to claim 4, 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.

6. A loader distributed hydraulic system according to claim 4, 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.

7. 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.

8. 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.

9. 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.

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

Images