Loader power intelligent distribution load balancing system

Abstract

The utility model relates to the technical field of loaders, and discloses a loader power intelligent distribution load balancing system which comprises an oil tank, a main oil way variable pump, a steering variable pump, a steering gear, a flow control valve, a steering oil cylinder, a load balancing multi-way valve, a movable arm oil cylinder, a bucket oil cylinder and an accessory oil cylinder. An oil outlet of the main oil way variable pump is connected with the load balancing multi-way valve, the flow control valve, the bucket oil cylinder, the accessory oil cylinder and the movable arm oil cylinder are all connected with the load balancing multi-way valve, an oil suction port of the steering variable pump is connected with the oil tank, and an oil outlet of the steering variable pump is connected with the flow control valve and the steering gear. The steering gear is connected with the flow control valve, and the steering oil cylinder is connected with the flow control valve. Electro-hydraulic integrated control is achieved through the load-sensitive control main valve and the electric control including the controller, the purposes of reducing loss and improving efficiency are achieved, and the energy-saving effect is obvious.

Description

Technical Field

[0001] This utility model relates to the field of loader technology, specifically to a loader power intelligent distribution load balancing system. Background Technology

[0002] Currently, most loader hydraulic systems use gear pump metering systems. The working device and steering hydraulic system are each driven by two metering gear pumps, which have a dual-pump confluence function. Under the same speed, the output flow of the two metering pumps remains constant and does not change with the load. However, in actual construction operations, the load of the loader's working device changes frequently and within a large range. This causes the flow provided by the steering metering pump to generate high-pressure overflow (when the working device is digging) or low-pressure overflow (when the boom is slowly lifting) in addition to the flow to the working device. As a result, the flow is wasted and the engine power driving the hydraulic pump is not effectively utilized. Utility Model Content

[0003] The technical problem this invention aims to solve is the issue of wasted flow in existing loader hydraulic systems.

[0004] To solve the above-mentioned technical problems, the technical solution of this utility model is to provide a loader power intelligent distribution load balancing system, including an oil tank, a main oil circuit variable pump, a steering variable pump, a steering gear, a flow control valve, a steering cylinder, a load balancing multi-way valve, a boom cylinder, a bucket cylinder, and an attachment cylinder. The oil inlet of the main oil circuit variable pump is connected to the oil tank, and the oil outlet of the main oil circuit variable pump is connected to the load balancing multi-way valve. The flow control valve, the bucket cylinder, the attachment cylinder, and the boom cylinder are all connected to the load balancing multi-way valve. The oil inlet of the steering variable pump is connected to the oil tank, and the oil outlet of the steering variable pump is connected to the flow control valve and the steering gear. The steering gear is connected to the flow control valve, and the steering cylinder is connected to the flow control valve.

[0005] Optionally, the load balancing multi-way valve is provided with an X1 oil port and a T2 return oil port. An accumulator is connected to the X1 oil port, and the T2 return oil port is connected to the oil tank. A filter and a radiator are provided between the T2 return oil port of the load balancing multi-way valve and the oil tank.

[0006] Optionally, the load balancing multi-way valve is further provided with oil circuits A1, B1, A2, B2, A3, and B3. The inlet and outlet ports of the attachment cylinder are respectively connected to oil circuits A1 and B1, the inlet and outlet ports of the bucket cylinder are respectively connected to oil circuits A2 and B2, and the inlet and outlet ports of the boom cylinder are respectively connected to oil circuits A3 and B3.

[0007] Optionally, the load balancing multi-way valve is further provided with a P2 oil port and a P1 oil port, the flow control valve is provided with an EF oil port, the P2 oil port is connected to the EF oil port, and the main oil circuit variable pump is connected to the P1 oil port.

[0008] Optionally, the load balancing multi-way valve includes a neutral-position closed attachment valve stem, a neutral-position closed bucket valve stem, and a neutral-position closed boom valve stem. The load balancing multi-way valve also includes an X oil circuit, an LS oil circuit, an L oil circuit, an L1 oil circuit, and a T1 oil circuit. The L and T1 oil circuits are connected to an oil tank. Both sides of the neutral-position closed attachment valve stem, the neutral-position closed bucket valve stem, and the neutral-position closed boom valve stem are connected to the X oil circuit via proportional solenoid valves. Each of the neutral-position closed attachment valve stem, the neutral-position closed bucket valve stem, and the neutral-position closed boom valve stem is connected to the LS oil circuit via a pressure compensator. The neutral-position closed boom valve stem is connected to a shock-absorbing module and a switching solenoid valve. The shock-absorbing module is connected to the switching solenoid valve and the X oil circuit, and the switching solenoid valve is connected to the L1 oil circuit.

[0009] Optionally, a pressure reducing valve II, a pressure reducing valve III, and a one-way throttle valve are connected in parallel between the LS oil circuit and the L oil circuit of the load balancing multi-way valve. The pressure reducing valve II is also connected to the P2 oil port. The A1 oil circuit, B1 oil circuit, A2 oil circuit, B2 oil circuit, and A3 oil circuit of the load balancing multi-way valve are all connected to the T2 oil circuit through an overload protection valve. A one-way valve, a filter II, and a throttle valve are connected in series between the P1 oil circuit and the L1 oil circuit of the load balancing multi-way valve. A proportional solenoid valve 12-1, a two-position three-way valve, and a two-position two-way valve are connected in series between the T1 oil circuit and the X oil circuit of the load balancing multi-way valve.

[0010] Optionally, the outlet of the variable steering pump includes a PP2 port and an LSa port, the flow control valve is further provided with a PP3 port and an L2 port, the steering gear is provided with a PP4 inlet port, the PP2 port of the variable steering pump is connected to the PP3 port of the flow control valve and the PP4 inlet port of the steering gear, and the L2 port of the flow control valve is connected to the LSa port of the variable steering pump.

[0011] Optionally, a pressure reducing valve is provided between the PP2 port of the steering variable pump and the steering gear.

[0012] Optionally, a shuttle valve is provided between the LSa port of the steering variable pump and the flow control valve. The shuttle valve has a P7 port, and the flow control valve has a P4 port. The P7 port of the shuttle valve is connected to the P4 port and the L2 port of the flow control valve, respectively. The shuttle valve is also connected to the LS oil circuit of the load balancing multi-way valve.

[0013] Optionally, the steering gear is further provided with LE port and R1 port, and the flow control valve is further provided with Pa port, P3 port, A port and B port. The LE port and R1 port of the steering gear are respectively connected to the Pa port and P3 port of the flow control valve, and the A port and B port of the flow control valve are connected to the steering cylinder.

[0014] In summary, this utility model provides an intelligent power distribution and load balancing system for loaders. It achieves electro-hydraulic integrated control through a load-sensitive control main valve and an electronic control unit (including a controller). A variable displacement piston pump is used as the power element in the loader's hydraulic system. Based on the operation signal from the pilot handle control valve, it achieves intelligent power distribution and flow and pressure control under varying load conditions. During loading operations, it supplies oil to the working device, achieving high pressure and low flow to reduce energy loss. During turning operations, it supplies oil to the working device according to actual needs, without generating excess flow. During single-travel operations, the variable displacement pump operates at its minimum displacement, avoiding high-pressure overflow losses. This allows the loader to operate stably and coordinately under different conditions, achieving the goals of reducing losses and improving efficiency, resulting in significant energy savings. Attached Figure Description

[0015] Figure 1 This is a schematic diagram of the hydraulic principle of the intelligent power distribution and load balancing system for a loader according to this utility model.

[0016] Figure 2 This is a hydraulic schematic diagram of the load balancing multi-way valve of this utility model;

[0017] In the diagram: 1. Oil tank; 2. Main oil circuit variable pump; 3. Radiator; 4. Filter 1; 5. Steering variable pump; 6. Shuttle valve; 7. Pressure reducing valve 1; 8. Steering gear; 9. Flow control valve; 10. Steering cylinder; 11. Accumulator; 12. Load balancing multi-way valve; 12-1. Proportional solenoid valve; 12-2. Pressure compensator; 12-3. Pressure reducing valve 2; 12-4. Pressure reducing valve 3; 12-5. One-way throttle valve; 12-6. Middle... 12-7. Attachment valve stem in neutral position; 12-8. Overload protection valve; 12-9. Bucket valve stem in neutral position; 12-10. Boom valve stem in neutral position; 12-11. Shock absorption module; 12-12. Solenoid valve; 12-13. Filter II; 12-14. Throttle valve; 12-15. Two-position three-way valve; 12-16. Two-position two-way valve; 12-17. Check valve; 18. Boom cylinder; 19. Bucket cylinder; 10. Attachment cylinder. Detailed Implementation

[0018] The following combination Figure 1-2 The present invention will be described in further detail below.

[0019] This utility model discloses a loader power intelligent distribution and load balancing system, referring to... Figure 1The system includes an oil tank 1, a main hydraulic variable pump 2, a steering variable pump 5, a steering gear 8, a flow control valve 9, a steering cylinder 10, a load balance multi-way valve 12, a boom cylinder 13, a bucket cylinder 14, and an attachment cylinder 15. The suction port of the main hydraulic variable pump 2 is connected to the oil tank 1, and the discharge port of the main hydraulic variable pump 2 is connected to the load balance multi-way valve 12. The flow control valve 9, the bucket cylinder 14, the attachment cylinder 15, and the boom cylinder 13 are all connected to the load balance multi-way valve 12. The suction port of the steering variable pump 5 is connected to the oil tank 1, and the discharge port of the steering variable pump 5 is connected to the flow control valve 9 and the steering gear 8. The steering gear 8 is connected to the flow control valve 9, and the steering cylinder 10 is connected to the flow control valve 9. A filter 4 and a radiator 3 are provided between the load balance multi-way valve 12 and the oil tank 1.

[0020] Specifically, refer to Figure 1 The load balancing multi-way valve 12 is equipped with an X1 oil port, a T2 return oil port, an A1 oil circuit, a B1 oil circuit, an A2 oil circuit, a B2 oil circuit, an A3 oil circuit, a B3 oil circuit, a P1 oil port, and a P2 oil port. An accumulator 11 is connected to the X1 oil port. The T2 return oil port is connected to the oil tank 1. The T2 return oil port is connected to the P6 oil port of the filter 4-. The filter 4- is connected to the P5 oil port of the radiator 3. The radiator 3 is connected to the oil tank 1. The inlet and outlet oil ports of the attachment cylinder 15 are connected to the A1 oil circuit and the B1 oil circuit, respectively. The inlet and outlet oil ports of the bucket cylinder 14 are connected to the A2 oil circuit and the B2 oil circuit, respectively. The inlet and outlet oil ports of the boom cylinder 13 are connected to the A3 oil circuit and the B3 oil circuit, respectively. The PP1 oil port of the main oil circuit variable pump 2 is connected to the P1 oil port of the load balancing multi-way valve 12.

[0021] The flow control valve 9 is equipped with EF port, PP3 port, L2 port, Pa port, P3 port, A port and B port. The P2 port of the load balancing multi-way valve 12 is connected to the EF port.

[0022] The outlet of the variable steering pump 5 includes a PP2 port and an LSa port. The steering gear 8 is equipped with a PP4 inlet port, an LE port and an R1 port. The PP2 port of the variable steering pump 5 is connected to the PP3 port of the flow control valve 9 and the PP4 inlet port of the steering gear. The L2 port of the flow control valve 9 is connected to the LSa port of the variable steering pump 5. The LE port and R1 port of the steering gear 8 are respectively connected to the Pa port and P3 port of the flow control valve 9 to operate the valve core to achieve steering. The A port and B port of the flow control valve 9 are connected to the steering cylinder 10.

[0023] The steering gear 8 is equipped with a T4 oil port that connects to the oil tank 1, and the flow control valve 9 is equipped with a T3 oil port that connects to the filter 4.

[0024] In a further implementation, refer to Figure 2The load balancing multi-way valve 12 is equipped with a neutral-position closed attachment valve stem 12-6, a neutral-position closed bucket valve stem 12-8, and a neutral-position closed boom valve stem 12-9. The load balancing multi-way valve 12 also has X, LS, L, L1, and T1 oil passages. The L and T1 oil passages are connected to the oil tank 1. Both sides of the neutral-position closed attachment valve stem 12-6, the neutral-position closed bucket valve stem 12-8, and the neutral-position closed boom valve stem 12-9 are connected by proportional solenoid valves 1. 2-1 is connected to the X oil circuit. The neutral position closed attachment valve stem 12-6, the neutral position closed bucket valve stem 12-8 and the neutral position closed boom valve stem 12-9 are all connected to the LS oil circuit through the pressure compensator 12-2. The neutral position closed boom valve stem 12-9 is connected to the shock absorption module 12-10 and the switching solenoid valve 12-11. The shock absorption module 12-10 is connected to the switching solenoid valve 12-11 and the X oil circuit. The switching solenoid valve 12-11 is connected to the L1 oil circuit.

[0025] The LS and L oil circuits of the load balancing multi-way valve 12 are connected in parallel with pressure reducing valve 2 12-3, pressure reducing valve 3 12-4, and one-way throttle valve 12-5. Pressure reducing valve 2 12-3 is also connected to port P2. The A1, B1, A2, B2, and A3 oil circuits of the load balancing multi-way valve 12 are all connected to the T2 oil circuit through overload protection valve 12-7. The P1 and L1 oil circuits of the load balancing multi-way valve 12 are connected in series with one-way valve 12-16, filter 2 12-12, and throttle valve 12-3. The T1 and X oil circuits of the load balancing multi-way valve 12 are connected in series with proportional solenoid valve 12-1, two-position three-way valve 12-14, and two-position two-way valve 12-15. The X and L1 oil circuits are internal oil circuits of the load balancing multi-way valve 12 and are used for internal communication of the load balancing multi-way valve 12.

[0026] In a further embodiment, a pressure reducing valve 7 is provided between the PP2 port of the variable steering pump 5 and the steering gear 8. The P8 port of the pressure reducing valve 7 is connected to the PP2 port of the variable steering pump 5, and the other end of the pressure reducing valve 7 is connected to the PP4 port of the steering gear 8. A shuttle valve 6 is provided between the LSa port of the PP2 port of the variable steering pump 5 and the flow control valve 9. The shuttle valve 6 is provided with a P7 port, and the flow control valve 9 is provided with a P4 port. The P7 port of the shuttle valve 6 is connected to the P4 port and the L2 port of the flow control valve 9, respectively. The shuttle valve 6 is also connected to the LS oil circuit of the load balance multi-way valve 12. The LS oil circuit is a load-sensitive feedback oil circuit. The load balance multi-way valve 12 is provided with a boom connection ACC oil port, on which a boom shock absorption auxiliary device is connected.

[0027] In this embodiment, the load balancing multi-way valve 12, the main oil circuit variable pump 2, and the steering variable pump 5 are controlled by an electronic control controller and a pilot handle control valve for electro-hydraulic integration. This fully automatic adaptive control enables intelligent cross-control of the loader's travel system and working system power. The hydraulic operating conditions include loading operation, steering operation, travel drive + boom lifting operation, single travel operation, boom + bucket combined operation, and other combined operation conditions.

[0028] During loading operations, the main oil circuit variable pump 2 supplies oil to the bucket cylinder 14. Through the load-sensitive feedback oil circuit of the load balance multi-way valve 12, the working device can achieve high pressure and low flow, reducing energy loss. The walking system can effectively absorb the remaining power, making the power stronger.

[0029] During steering operations, the priority valve of flow control valve 9 is in the right position, which allows the steering variable pump 5 to supply oil to the steering cylinder as needed, without generating excess flow, so as to achieve steering that is not sinking at low speed and not drifting at high speed, making steering operation comfortable and energy-saving.

[0030] In the walking drive + boom lifting operation, the boom damping auxiliary device is installed on the damping module 12-10 of the load balance multi-way valve 12 and the ACC oil port. This can effectively smooth the pressure fluctuation and water hammer phenomenon in the main oil circuit, making the compound action highly coordinated and stable.

[0031] In single-run operation, the main oil circuit variable pump 2 reduces the pressure through LS pressure feedback, automatically reducing the output flow and pressure, avoiding high-pressure overflow loss, and achieving significant energy-saving effect;

[0032] In the boom + bucket combined operation mode, the load balance multi-way valve 12 regulates the main oil circuit variable pump 2 to supply oil to the boom cylinder 13 and the bucket cylinder 14. The steering variable pump 5 realizes the dual pump combined flow oil supply through the EF oil port. Each working device independently adjusts the pressure difference of each valve port through the pressure compensator 12-2 built into the load balance multi-way valve 12. The flow of each branch is independently distributed as needed, and the micro-control performance is more outstanding, which can achieve precise control.

[0033] In addition, a priority valve is installed on the flow control valve 9, which controls the flow supplied by the steering variable pump 5 on demand during individual steering. In combined working conditions, the excess flow enters the working hydraulic system through the EF port to realize the dual pump confluence function. The flow control valve 9 is also equipped with a safety valve and a buffer valve to ensure the stability of the steering system pressure.

[0034] The working principle of this utility model is as follows: When the system starts working, the main oil circuit variable pump 2 and the steering variable pump 5 start working. Their oil suction ports are connected to the oil tank 1 to supply oil to the hydraulic system. The steering system supplies oil through the flow control valve P port of the flow control valve 9 connected to the steering variable pump 5. The branch circuit connects to the pressure reducing valve - 7 to the steering gear oil inlet P port of the steering gear 8. The steering gear L port and R port of the steering gear 8 control the Pa port and P1 port of the flow control valve 9 to realize the valve core reversal, so that the hydraulic oil of the steering variable pump 5 enters the steering cylinder to realize steering.

[0035] When steering alone, the main valve core of the flow control valve 9 is in the right position, and the steering variable pump 5 adjusts the flow rate into the steering cylinder 10 according to the pressure feedback from the L port of the flow control valve, so as not to generate excess flow.

[0036] During compound operation, the flow control valve 9 controls the steering variable pump 5 to prioritize supplying the steering cylinder 10. Excess oil enters the working hydraulic system through the EF port to achieve dual pump confluence. The working hydraulic system is connected to the main oil circuit variable pump 2, and its outlet is connected to the attachment cylinder 15, bucket cylinder 14, boom cylinder 13 through the load balance multi-way valve 12. The T return port of the load balance multi-way valve 12 is connected in series with the filter 4 and radiator 3 to return to the oil tank 1.

[0037] When moving independently, the main oil circuit variable pump 2 receives feedback pressure from the system and adjusts to the minimum displacement to avoid high pressure overflow loss;

[0038] During loading operations, the main oil circuit variable pump 2 and steering variable pump 5 supply oil to the boom cylinder 13 and bucket cylinder. On the one hand, the load balancing multi-way valve 12 adjusts the pressure difference of each valve port through the pressure compensator 12-2. On the other hand, the electromagnetic proportional valve controls the valve core opening to ensure that each oil circuit is supplied as needed, so as to achieve high pressure and low flow of the working device and reduce energy loss.

[0039] This utility model uses a load-balanced multi-way valve 12 as a control port. Based on a load-sensitive system and pressure compensation technology, it can reasonably distribute the flow and pressure from the main oil circuit variable pump 2 by adjusting the valve opening through a proportional solenoid valve 12-1, thereby achieving coordinated operation of multiple working devices. The load-balanced multi-way valve 12 is equipped with a pressure compensator 12-2 to maintain a stable valve port pressure difference. It is also equipped with a load-sensitive feedback oil circuit (LS oil circuit) to feed back the highest pressure of the hydraulic system to the variable pump and the pressure compensator 12-2, so that the main oil circuit variable pump 2 supplies oil as needed.

[0040] It should be noted that the above embodiments are only used to illustrate the technical solution of this utility model and are not intended to limit it. Although this utility model has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications or equivalent substitutions can be made to the technical solution of this utility model without departing from the spirit and scope of the technical solution of this utility model, and all such modifications or substitutions should be covered within the scope of the claims of this utility model.

Claims

1. A loader power intelligent distribution load balancing system, characterized by, The hydraulic system comprises an oil tank (1), a main oil path variable pump (2), a steering variable pump (5), a steering gear (8), a flow control valve (9), a steering cylinder (10), a load balance multi-way valve (12), a boom cylinder (13), a bucket cylinder (14) and an attachment cylinder (15), the oil suction port of the main oil path variable pump (2) is connected with the oil tank (1), the oil outlet of the main oil path variable pump (2) is connected with the load balance multi-way valve (12), the flow control valve (9), the bucket cylinder (14), the attachment cylinder (15) and the boom cylinder (13) are all connected with the load balance multi-way valve (12), the oil suction port of the steering variable pump (5) is connected with the oil tank (1), the oil outlet of the steering variable pump (5) is connected with the flow control valve (9) and the steering gear (8), the steering gear (8) is connected with the flow control valve (9), and the steering cylinder (10) is connected with the flow control valve (9).

2. The loader power intelligent distribution load balance system of claim 1, wherein, The load balance multi-way valve (12) is provided with an X1 oil port and a T2 oil return port, the X1 oil port is connected with an accumulator (11), the T2 oil return port is connected with the oil tank (1), and a filter one (4) and a radiator (3) are arranged between the T2 oil return port of the load balance multi-way valve (12) and the oil tank (1).

3. The loader power intelligent distribution load balance system of claim 2, wherein, The load balance multi-way valve (12) is further provided with an A1 oil path, a B1 oil path, an A2 oil path, a B2 oil path, an A3 oil path and a B3 oil path, the inlet and outlet ports of the attachment cylinder (15) are connected to the A1 oil path and the B1 oil path respectively, the inlet and outlet ports of the bucket cylinder (14) are connected to the A2 oil path and the B2 oil path respectively, and the inlet and outlet ports of the boom cylinder (13) are connected to the A3 oil path and the B3 oil path respectively.

4. The loader power intelligent distribution load balance system of claim 3, wherein, The load balance multi-way valve (12) is further provided with a P2 oil port and a P1 oil port, the flow control valve (9) is provided with an EF oil port, the P2 oil port is connected with the EF oil port, and the main oil path variable pump (2) is connected with the P1 oil port.

5. The loader power intelligent distribution load balance system of claim 4, wherein, The load balance multi-way valve (12) is provided with a middle closed attachment valve rod (12-6), a middle closed bucket valve rod (12-8) and a middle closed boom valve rod (12-9), the load balance multi-way valve (12) is provided with an X oil path, an LS oil path, an L oil path, an L1 oil path and a T1 oil path, the L oil path and the T1 oil path are connected with the oil tank (1), the middle closed attachment valve rod (12-6), the middle closed bucket valve rod (12-8) and the middle closed boom valve rod (12-9) are connected to the X oil path through proportional solenoid valves (12-1) on both sides, the middle closed attachment valve rod (12-6), the middle closed bucket valve rod (12-8) and the middle closed boom valve rod (12-9) are connected to the LS oil path through pressure compensators (12-2), the middle closed boom valve rod (12-9) is connected with a damping module (12-10) and an on-off solenoid valve (12-11), the damping module (12-10) is connected with the on-off solenoid valve (12-11) and the X oil path, and the on-off solenoid valve (12-11) is connected with the L1 oil path.

6. The loader power intelligent distribution load balance system of claim 5, wherein, The load balancing multi-way valve (12) is connected in parallel between the LS oil way and the L oil way, and is connected with a second pressure reducing valve (12-3), a third pressure reducing valve (12-4) and a one-way throttle valve (12-5), the second pressure reducing valve (12-3) is also connected with a P2 oil port, the A1 oil way, the B1 oil way, the A2 oil way, the B2 oil way and the A3 oil way of the load balancing multi-way valve (12) are connected with the T2 oil way through an overload protection valve (12-7), the P1 oil way of the load balancing multi-way valve (12) is connected in series between the L1 oil way, a one-way valve (12-16), a second filter (12-12) and a throttle valve (12-13), and the T1 oil way of the load balancing multi-way valve (12) is connected in series between the X oil way, a proportional solenoid valve (12-1), a two-position three-way valve (12-14) and a two-position two-way valve (12-15).

7. The loader power intelligent distribution load balance system of claim 1, wherein, The oil outlet of the steering variable pump (5) comprises a PP2 port and an LSa port, the flow control valve (9) is further provided with a PP3 port and an L2 port, the steering gear (8) is provided with a PP4 inlet port, the PP2 port of the steering variable pump (5) is connected with the PP3 port of the flow control valve (9) and the steering gear PP4 inlet port, and the L2 port of the flow control valve (9) is connected with the LSa port of the steering variable pump (5).

8. The loader power intelligent distribution load balance system of claim 7, wherein, The PP2 port of the steering variable pump (5) is connected with the steering gear (8) through a first pressure reducing valve (7).

9. The loader power intelligent distribution load balance system of claim 7, wherein, The LSa port of the steering variable pump (5) is connected with the flow control valve (9) through a shuttle valve (6), the shuttle valve (6) is provided with a P7 port, the flow control valve (9) is provided with a P4 port, the P7 port of the shuttle valve (6) is connected with the P4 port and the L2 port of the flow control valve (9), and the shuttle valve (6) is also connected with the LS oil way of the load balancing multi-way valve (12).

10. The loader power intelligent distribution load balance system of claim 7, wherein, The steering gear (8) is further provided with an LE port and an R1 port, the flow control valve (9) is further provided with a Pa port, a P3 port, an A port and a B port, the LE port and the R1 port of the steering gear (8) are connected with the Pa port and the P3 port of the flow control valve (9), and the A port and the B port of the flow control valve (9) are connected with the steering cylinder (10).

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