Integrated energy-saving load-sensitive multi-way valve and hydraulic system

Abstract

The invention discloses an integrated energy-saving load-sensitive multi-way valve and a hydraulic system. The system comprises an oil inlet linkage valve group, a standby linkage valve group, a tipping bucket linkage valve group, a stable module linkage valve group and a movable arm linkage valve group. Valve body oil inlet P flow channels of all the valve groups, signal feedback oil way LS flow channels of all the valve groups, oil discharge L flow channels of all the valve groups, oil return T flow channels of all the valve groups and pilot oil Pst flow channels of all the valve groups are communicated with one another. According to the integrated energy-saving type load-sensitive multi-way valve, a split type structure is adopted, flexible expansion can be achieved according to different configuration requirements of a whole machine, the integrated energy-saving type load-sensitive multi-way valve comprises a dual valve, a triple valve, a quadruple valve and a stable module function valve, and meanwhile the stable module valve, a pilot oil source valve and a pilot hydraulic lock are integrated through the integrated design scheme; and the assembling performance and the maintainability are greatly improved. And meanwhile, various functional valve blocks such as overload oil supplementing valves configured for the tipping bucket unit and the standby unit, large-cavity hydraulic locks of the movable arm unit and the tipping bucket unit and a liquid filling safety valve of the stable module unit are arranged, so that various practical problems in installation application are solved.

Description

Technical Field

[0001] This invention relates to an integrated, energy-saving, load-sensitive multi-way valve and hydraulic system, belonging to the field of engineering machinery technology. Background Technology

[0002] Currently, engineering vehicles often require multiple functional valve blocks due to their diverse operating conditions. For example, a loader's multi-way valve typically comes standard with at least two functional ports: the boom port and the dump truck port. When equipped with implements, additional spare ports are usually needed, and some special implements require two spare ports to meet their usage requirements. For overseas markets, a stabilization module is often also required as standard. Currently, loader multi-way valves generally use plate valves, which are difficult to expand in terms of functionality. This results in valve groups being scattered across various operating conditions, leading to a large number of components and complex piping, causing significant inconvenience and high costs for installation and maintenance. Meanwhile, the following practical problems often occur in loader applications: ① During operation, air suction occurs on one side of the cylinder, which adversely affects the cylinder's lifespan; ② Due to inconsistent processing of multi-way valves, the cylinder settlement often fails to meet standards, while excessively reducing the valve core clearance can lead to valve core jamming; ③ For market users requiring multiple cylinders to perform compound actions, the operability is difficult to achieve good results; ④ During operation, the working device exhibits a delay in action and has poor responsiveness; ⑤ When the working device stops, the impact is significant, resulting in poor operating comfort; ⑥ In abnormal situations, the accumulator of the stabilizing module is overcharged and cannot be depressurized. Summary of the Invention

[0003] The purpose of this invention is to overcome the shortcomings of the prior art and provide an integrated energy-saving load-sensitive multi-way valve and hydraulic system, which solves the problems of numerous hydraulic valve groups, complex pipeline connections, and difficult maintenance in the prior art. To achieve the above objectives / to solve the above technical problems, the present invention is implemented using the following technical solution: First aspect: An integrated energy-saving load-sensitive multi-way valve, including an inlet valve group, a standby valve group, a tipping valve group, a stabilization module valve group, and a boom valve group. The valve body inlet P flow channel, the signal feedback oil circuit LS flow channel, the unloading L flow channel, the return oil T flow channel, and the pilot oil Pst flow channel of each valve group are interconnected.

[0004] Optionally, the inlet valve assembly includes an LS relief valve, a constant flow valve, a peak-shaving valve, a pilot pressure reducing valve, and a solenoid valve. The LS relief valve is located between the LS flow channel and the return oil T channel. The constant flow valve is located between the LS flow channel and the return oil T flow channel of the inlet valve body. The peak-shaving valve is located between the inlet P flow channel and the return oil T flow channel of the inlet valve body to eliminate the pressure peak at the P port. The pilot pressure reducing valve is located between the inlet P flow channel and the pilot oil Pst channel. A first solenoid valve is also provided between the pilot pressure reducing valve and the pilot oil Pst channel. A filter screen is provided at the inlet of the pilot pressure reducing valve.

[0005] Optionally, the constant flow valve includes a constant flow valve cartridge valve and a first damper. The pressure difference generated by the LS signal oil flowing through the first damper acts on both ends of the constant flow valve core and interacts with the spring set pressure to control the opening of the constant flow valve core.

[0006] Optionally, the backup valve assembly includes a backup valve body, a backup valve core mounted on the backup valve body, an electro-proportional pressure reducing valve and a pressure compensator arranged at both ends of the backup valve core. The pressure oil in the inlet P flow channel is connected to the pressure compensator through the backup valve core. One of the outlet ports of the pressure compensator is connected to the signal feedback oil circuit LS flow channel, and the other is connected to port A1 and port B1 through the backup valve core. The spare valve core is connected to the pressure compensator via an inlet check valve, and oil ports A1 and B1 are respectively connected to overload replenishment valves.

[0007] Optionally, the tipping valve assembly includes a tipping valve body, a tipping valve core disposed on the tipping valve body, an electro-proportional pressure reducing valve and a pressure compensator disposed at both ends of the tipping valve core, the pressure oil in the inlet P flow channel is connected to the pressure compensator through the tipping valve core, one of the oil outlets of the pressure compensator is connected to the signal feedback oil circuit LS flow channel, and the other is connected to oil port A2 and oil port B2 through the tipping valve core; The tipping valve core is connected to the pressure compensator via an inlet check valve. Oil ports A2 and B2 are respectively connected to overload replenishing valves. The tipping valve core is connected to a hydraulic lock. The hydraulic lock is connected to oil port A2 and the return oil flow channel T. Another oil port passes through the oil circuit between the tipping valve core and the electro-proportional pressure reducing valve and is connected to oil port B2.

[0008] Optionally, the boom coupling valve assembly includes a boom coupling valve body, a boom coupling valve core disposed on the boom coupling valve body, an electro-proportional pressure reducing valve and a pressure compensator disposed at both ends of the boom coupling valve core, the pressure oil in the inlet P flow channel is connected to the pressure compensator through the boom coupling valve core, one of the oil outlets of the boom coupling pressure compensator is connected to the signal feedback oil circuit LS flow channel, and the other is connected to oil port A3 and oil port B3 through the boom coupling valve core; The boom coupling valve core is connected to the pressure compensator via an inlet check valve. A replenishing check valve is provided between the oil port B3 and the return oil T flow channel. The boom coupling valve core is connected to a hydraulic lock. The hydraulic lock is connected to the oil port A3 and the return oil T flow channel. Another oil port passes through the oil circuit between the boom coupling valve core and the electro-proportional pressure reducing valve and is connected to the oil port B3.

[0009] Optionally, the hydraulic lock includes a hydraulic lock control valve and a hydraulic lock shut-off valve. The hydraulic lock shut-off valve is connected at both ends to the working port of the large cavity of the boom coupling valve core and the large cavity of the cylinder. The three ports of the hydraulic lock control valve are respectively connected to the spring cavity of the hydraulic lock shut-off valve and its connecting port to the large cavity of the cylinder and the return oil T-channel. The right control cavity of the hydraulic lock control valve is connected to the pilot oil cavity of the small cavity of the boom coupling valve core.

[0010] Optionally, the stabilization module valve group includes a stabilization module switching valve, a second solenoid valve, a pressure balancing valve, a third solenoid valve, an accumulator safety valve, a filling control valve, a filling safety valve, and a second damper. The second solenoid valve is connected to the control port of the stabilization module switching valve. The stabilization module switching valve is connected to oil ports A3 and B3. The oil port of the pressure balancing valve is connected to the stabilization module switching valve. The third solenoid valve is used to control the working state of the pressure balancing valve and the boom connecting chamber working oil port A3. The accumulator safety valve is located between oil port X2 and the return oil T flow channel. One oil port of the filling control valve is connected to the pressure balancing valve, and the other oil port is connected to the oil line connecting the filling safety valve, the pressure balancing valve, and the stabilization module switching valve. The second damper is located between the third solenoid valve and the oil port of the filling control valve.

[0011] Optionally, an inlet check valve 2 is provided between the filling control valve and the oil inlet P channel.

[0012] Second aspect: A hydraulic system comprising the integrated energy-saving load-sensitive multi-way valve described in the first aspect, wherein the inlet P of the inlet valve group is connected to a variable pump, and the inlet X is connected to a pilot accumulator; the inlets B1 and A1 of the standby valve group are connected to a deforming tool; the inlets B2 and A2 of the tipping valve group are connected to a bucket cylinder; the inlet X2 of the stabilization module valve group is connected to a stabilization module accumulator; the inlets B3 and A3 of the dynamic valve group are connected to a boom cylinder; and the inlet A3' is connected to a manual drain valve.

[0013] Compared with the prior art, the beneficial effects achieved by the present invention are as follows: The integrated energy-saving load-sensitive multi-way valve disclosed in this invention adopts a segmented structure, which can be flexibly expanded and changed according to different configuration requirements of the whole machine: two-way valve, three-way valve, four-way valve and more. The stabilization module function valve is selected as a single valve group according to market demand. Furthermore, the pilot pressure reducing valve and pilot hydraulic lock are integrated into the oil inlet valve group. The integrated design can be maximized while taking into account a wide range of working conditions. The number of components is reduced, the number of pipeline connections is greatly reduced, the pipeline leakage points are reduced, and the assemblability and maintainability are greatly improved. Attached Figure Description

[0014] Figure 1 This is a hydraulic principle structure diagram of the integrated energy-saving load-sensitive multi-way valve provided by the present invention; Figure 2 This is a schematic diagram of a hydraulic system provided in an embodiment of the present invention.

[0015] In the diagram: 1-Inlet P-flow channel, 2-Return T-flow channel, 3-Pilot oil Pst-flow channel, 4-Unloading L-flow channel, 5-Signal feedback oil circuit LS-flow channel, 6-Integrated energy-saving load-sensitive multi-way valve, 7-Variable displacement pump, 8-Pilot accumulator, 9-Stabilizing module accumulator, 10-LS relief valve, 11-Constant flow valve, 11.1-Constant flow valve cartridge valve, 11.2-First damper, 12-Peak reduction valve, 13-Pilot pressure reducing valve, 14-First solenoid valve, 15-Filter screen. 16-Pressure compensator, 17-Electro-proportional pressure reducing valve, 18-Inlet check valve one, 19-Overload replenishing valve, 20-Replenishing check valve, 21-Hydraulic lock, 21.1-Hydraulic lock control valve, 21.2-Hydraulic lock shut-off valve, 22-Stabilization module switching valve, 23-Second solenoid valve, 24-Pressure balance valve, 25-Third solenoid valve, 26-Accumulator safety valve, 27-Inlet check valve two, 28-Filling control valve, 29-Filling safety valve, 30-Second damper. Detailed Implementation

[0016] To make the technical means, creative features, objectives and effects of this invention easier to understand, the invention will be further described below in conjunction with specific embodiments.

[0017] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicating orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, are used only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. Furthermore, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined with "first," "second," etc., may explicitly or implicitly include one or more of that feature. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0018] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art will understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0019] Example 1, such as Figure 1 As shown, an integrated energy-saving load-sensitive multi-way valve is arranged from left to right as follows: inlet valve group, standby valve group, tipping valve group, stabilization module valve group, boom valve group, and tail valve group. The valve bodies of each valve group have interconnected inlet (P-channel 1), return (T-channel 2), pilot oil (Pst-channel 3), unloading (L-channel 4), and signal feedback oil circuit (LS-channel 5), allowing for flexible expansion and modification. It can be flexibly expanded and modified according to different configuration requirements of the entire machine, including but not limited to the following arrangement methods: Dual valves: oil inlet valve assembly, tipping bucket valve assembly, boom valve assembly, and tail valve assembly; The three-way valve consists of an inlet valve group, a standby valve group, a tipping valve group, a boom valve group, and a tail valve.

[0020] The three-way valve integrated stabilization module includes an oil inlet valve group, a standby valve group, a tipping bucket valve group, a stabilization module valve group, a boom valve group, and a tail valve.

[0021] Four-way valve system: oil inlet valve group, standby valve group, standby valve group, tipping valve group, boom valve group, and tail valve.

[0022] The four-way valve integrated stabilization module includes an oil inlet valve group, a standby valve group, a bucket valve group, a stabilization module valve group, a boom valve group, and a tail valve group.

[0023] The inlet valve body is also equipped with an LS overflow valve 10, which is located between the LS flow channel 5 of the signal feedback oil circuit and the T flow channel 2 of the return oil circuit. It is used for overload protection of the LS signal pressure and improves system safety.

[0024] The inlet valve body is also equipped with a constant flow valve 11, which is located between the LS flow channel 5 of the inlet valve body signal feedback oil circuit and the T flow channel 2 of the return oil circuit, and is used to prevent pressure buildup caused by oil trapping in the LS signal oil circuit.

[0025] The constant flow valve 11 includes a constant flow valve cartridge valve 11.1 and a first damper 11.2. The pressure difference generated by the LS signal oil flowing through the first damper 11.2 acts on both ends of the valve core of the constant flow valve cartridge valve 11.1 and interacts with the spring-set pressure to control the opening of the valve core of the constant flow valve cartridge valve 11.1. The constant flow valve has a very small flow capacity and is used for pressure relief in the LS signal oil circuit. Furthermore, a filter screen is provided at the inlet of the constant flow valve to prevent the valve core from getting stuck.

[0026] Specifically, when the working device suddenly stops operating, the valve cores of each valve quickly return to the neutral position, cutting off the pressure pathway between the LS oil circuit and the inlet P flow channel. The LS signal pressure cannot be released quickly and will remain residual in the LS flow channel. At this time, the constant flow valve 11 connects the LS flow channel and the return oil T with a very small flow rate, allowing the LS signal pressure to be released rapidly. Because the constant flow valve 11 has a very small flow rate, a filter screen is installed at the inlet of the constant flow valve 11 to prevent valve core jamming, thus improving the reliability of the constant flow valve.

[0027] The inlet valve body is also equipped with a peak-suppression valve 12, which is located between the inlet P flow channel and the return T flow channel of the inlet valve body and is used to eliminate the pressure peak at the P port.

[0028] Specifically, when the working device suddenly stops operating, the valve cores of each valve quickly return to the neutral position. Because the return response of the variable pump 7 is slower than the valve core closing speed, a sudden surge of high pressure occurs at port P. At this time, the pressure at both ends of the peak-suppression valve 12 is acted upon by the inlet pressure at port P and the LS signal pressure, respectively. The high pressure at port P exceeds the sum of the LS signal pressure and the spring force, pushing the valve core to move, connecting the inlet port P with the return port T, quickly relieving pressure and avoiding pressure shocks caused by the high pressure at port P. The LS signal oil passage is connected to the spring chamber of the peak-suppression valve. The pressure in the inlet P flow channel acts on the peak-suppression valve core and is compared with the LS signal pressure and the spring force to control the opening of the peak-suppression valve core. When a pressure shock occurs at port P during a rapid stop of the working device, the peak-suppression valve can react quickly and eliminate the pressure peak.

[0029] The inlet valve body is also equipped with a pilot pressure reducing valve 13, which is located between the inlet P flow channel and the pilot oil Pst channel. A first solenoid valve 14 is also installed between the pilot pressure reducing valve 13 and the pilot oil Pst channel as a pilot hydraulic lock to prevent misoperation. Integrating the pilot oil source function valve into the inlet valve body shortens the oil path from the pilot oil to each pilot proportional pressure reducing valve 17. Compared with a separate pilot oil source valve, the pilot oil Pst pressure is transmitted to both ends of each reversing valve core more quickly, reducing the impact of the pilot path on the valve core reversing speed and improving the responsiveness of the multi-way valve. A filter screen 15 is installed at the inlet of the pilot pressure reducing valve 13 to ensure the cleanliness of the pilot oil source and prevent the pilot proportional pressure reducing valve from jamming.

[0030] Pressure compensator 16: The boom valve group, bucket valve group, and standby valve group of the integrated energy-saving load-sensitive multi-way valve are all equipped with a valve post-pressure compensator. Through pressure compensation, it can prevent more oil from flowing to the side with lower load pressure when multiple cylinders operate simultaneously, and realize the reasonable distribution of oil among multiple cylinders according to the valve core opening, so as to achieve a better compound action effect.

[0031] Inlet check valve 18 is installed in the oil circuits connected to working ports A1, B1, A2, B2, A3, B3, and B2 respectively, in the spare valve group / tipping valve group / boom valve group pressure compensator 16. This prevents the hydraulic pump from reversing due to back dragging caused by the cylinder load when the pump is not powered during system failure or in a non-starting state, thus avoiding damage to system components.

[0032] Overload replenishing valve 19 is installed at the working ports A1 and B1 of the standby valve group and A2 and B2 of the tipping valve group. This valve is used for overload protection and to replenish oil when the hydraulic cylinder cavities. In current practical applications, the standby valve group typically does not have an overload replenishing valve, resulting in the hydraulic cylinder caving and the inability to replenish oil. Furthermore, the pressure shock generated by the load on the hydraulic cylinder cannot be quickly eliminated, significantly impacting the cylinder's lifespan. Installing overload replenishing valve 19 at the working ports A1 and B1 of the standby valve group prevents the hydraulic cylinder from caving and provides overload protection.

[0033] The oil replenishment check valve 20 is installed at the working oil port B3 of the small chamber of the boom valve assembly. It is used to replenish the oil in the small chamber of the boom cylinder to solve the problem of replenishing the oil in the small chamber when the boom cylinder descends rapidly.

[0034] Hydraulic lock 21 is installed at the working port A3 of the large chamber of the boom linkage valve group and the working port A2 of the large chamber of the bucket linkage valve group to effectively reduce internal leakage. The hydraulic lock includes a hydraulic lock control valve 21.1 and a hydraulic lock shut-off valve 21.2. Taking the boom linkage as an example, the two ends of the hydraulic lock shut-off valve 21.2 are connected to the working port of the large chamber of the boom linkage valve group and the large chamber of the boom cylinder. The hydraulic lock control valve is designed as a two-position three-way directional valve. The three ports are respectively connected to the spring chamber of the hydraulic lock shut-off valve 21.2 and its connection to the port of the large chamber of the boom cylinder and the return oil T-channel. The right control chamber of the hydraulic lock control valve 21.1 is connected to the pilot oil chamber of the small chamber of the boom linkage valve core.

[0035] The stabilization module switching valve 22 has its spring chamber connected to the unloading oil flow channel 4 (L). The control oil on the other side is connected to the outlet oil of the second solenoid valve 23. The oil pressure at the outlet of the second solenoid valve is compared with the spring force to control the opening of the stabilization module switching valve core. The outlet X2 port of the stabilization module switching valve is located in the valve body and connected to the stabilization module accumulator 9.

[0036] The second solenoid valve 23 has its outlet connected to the control oil on the other side of the spring chamber of the stabilization module switching valve 22, and its two inlets connected to the unloading oil L channel and the pilot oil Pst channel. The oil inlet path is selected by electromagnet control.

[0037] The pressure balancing valve 24 is designed as a three-position three-way directional valve with a middle position O-type function. The spring forces of the left and right spring chambers are equal, and the control pressures of the left and right spring chambers are respectively connected to the working oil port A3 of the large chamber of the boom linkage valve group and the oil outlet of the third solenoid valve.

[0038] The third solenoid valve 25 is designed as a two-position, three-way solenoid directional valve. Its three ports are connected to the right spring chamber of the pressure balance valve, the return oil T-channel, and the oil outlet of the pressure balance valve, respectively. When the solenoid is energized, it connects the right spring chamber of the pressure balance valve to the return oil T-channel; when the solenoid is de-energized, it connects the right spring chamber of the pressure balance valve to the oil outlet of the pressure balance valve.

[0039] Accumulator safety valve 26 is located between the X2 oil port connecting the accumulator and the return oil T flow channel, and is used for the safety protection of the accumulator.

[0040] The filling control valve 28 is located between the inlet check valve and the pressure balancing valve. It is a two-position two-way directional valve, with its two control chambers connected to the oil outlet of the filling control valve and the oil outlet of the pressure balancing valve, respectively. A second damping 30 is provided between the oil outlet of the pressure balancing valve and the right control chamber of the filling control valve.

[0041] The filling safety valve 29 is located between the oil outlet of the pressure balance valve and the return oil T channel 2.

[0042] Hydraulic locks are installed at the working port A3 of the boom valve assembly and the working port A2 of the tipping valve assembly. This eliminates the need for valve core control to prevent internal leakage, thus avoiding differences in settlement due to inconsistent product processing. It also allows for a proper increase in the valve core clearance, preventing the risk of jamming due to valve core processing accuracy issues.

[0043] The stabilization module valve group is equipped with a filling safety valve to prevent excessive pressure surges in the cylinder when the stabilization module is not activated, which would cause the accumulator pressure to remain at a high level after filling, thus improving the accumulator's lifespan.

[0044] The pressure balancing valve in the stabilization module's valve assembly is used to balance the pressure difference between the accumulator and the main chamber before the stabilization module is opened, preventing boom wobbling during opening due to high accumulator pressure. Simultaneously, the pressure balancing valve depressurizes the accumulator when the third solenoid valve loses power.

[0045] The working principle is as follows: When the boom is lifted, the pilot of the small chamber of the boom coupling valve core is pressureless. The hydraulic lock control valve 21.1 operates in the left position under the action of the spring force. The pressure of the spring chamber of the shut-off valve 21.2 is equal to that of the oil port of the large chamber of the boom cylinder. The boom coupling valve core moves, and the oil pressure at port P overcomes the spring force of the hydraulic lock shut-off valve 21.2 through the boom coupling valve core. The oil enters the large chamber of the boom cylinder through the hydraulic lock shut-off valve 21.2, and the oil in the small chamber of the boom cylinder returns to the oil tank through the boom coupling valve core. When the boom descends, the pilot oil pressure in the small chamber of the boom coupling valve core acts on the right control chamber of the hydraulic lock control valve 21.1 to overcome the spring force, and the hydraulic lock control valve 21.1 operates in the right position. The spring chamber of the hydraulic lock shut-off valve 21.2 connects with the return oil T-channel to discharge oil. The boom coupling valve core moves, and the oil from port P enters the small chamber of the boom cylinder through the working port of the boom coupling valve core and the large chamber of the boom coupling valve assembly. The oil in the large chamber of the boom cylinder flows to the hydraulic lock shut-off valve 21.2, which overcomes the spring force and opens in the reverse direction. The oil in the large chamber of the boom cylinder returns to the oil tank through the hydraulic lock shut-off valve 21.2 and the boom coupling valve core. When the boom is not in motion, there is no pressure in the pilot chamber of the boom coupling valve core. The hydraulic lock control valve 21.1 operates in the left position under spring force. The pressure in the spring chamber of the hydraulic lock shut-off valve 21.2 is equal to the pressure at the port of the boom cylinder's large chamber. At this time, the boom coupling valve core is in the neutral shut-off position, and the spring force of the hydraulic lock shut-off valve 21.2 ensures that the valve core is in the shut-off position. At this time, shutting off the oil in the boom cylinder's large chamber via the hydraulic lock shut-off valve 21.2 is more reliable than controlling the settlement amount by simply controlling the lubrication within the neutral position of the boom coupling valve core. It also avoids the risk of valve core jamming by ensuring the valve core clearance is not too small.

[0046] The stabilization module valve group includes a stabilization module valve body, an inlet P flow channel 1, a signal feedback oil circuit LS flow channel 5, an unloading L flow channel 4, a return oil T flow channel 2, and a pilot oil Pst flow channel 3 disposed on the stabilization module valve body, and also includes a stabilization module switching valve 22, a second solenoid valve 23, a pressure balancing valve 24, a third solenoid valve 25, an accumulator safety valve 26, an inlet check valve 27, a filling control valve 28, and a filling safety valve 29.

[0047] Example 2 Figure 2 As shown, a hydraulic system is disclosed, including the integrated energy-saving load-sensitive multi-way valve 6 described in Embodiment 1. The inlet P of the inlet valve group is connected to a variable pump, and the inlet X is connected to a pilot accumulator. The inlets B1 and A1 of the standby valve group are connected to a deforming tool. The inlets B2 and A2 of the tipping valve group are connected to a bucket cylinder. The inlet X2 of the stabilization module valve group is connected to a stabilization module accumulator. The inlets B3 and A3 of the dynamic valve group are connected to a boom cylinder, and the inlet A3' is connected to a manual drain valve.

[0048] The integrated energy-saving load-sensitive multi-way valve; A variable displacement pump, acting as a power element, provides pressurized oil; The pilot accumulator serves as a pilot oil source, providing pilot pressure oil. The stabilization module accumulator, as an elastic damping element, works in conjunction with the stabilization module valve group to achieve elastic connection of the working device.

[0049] The working principle is as follows: When the machine starts up, the stabilizing module accumulator 9 begins filling. At this time, the third solenoid valve 25 is energized, while the second solenoid valve 23 is de-energized. When the second solenoid valve 23 is de-energized, both the left and right control chambers of the stabilizing module switching valve 22 are connected to the pressure in the L flow channel. Under the action of the spring force at the right end, it operates in the right position, and the oil inlet of the stabilizing module switching valve 22 is connected to the stabilizing module accumulator 9. When the third solenoid valve 25 is energized, the right control chamber of the pressure balancing valve 24 is connected to the pressure in the T flow channel, and the left control chamber is connected to the working oil port A3 of the boom linkage chamber. When there is pressure in the working oil port A3 of the boom linkage chamber, it pushes the valve core of the pressure balancing valve 24 to the right, connecting in the left position. The pressure in the stabilizing module accumulator 9 is connected to the filling control valve 28 through the stabilizing module switching valve 22 and the pressure balancing valve 24. The initial position of the filling control valve 28 connects to the inlet and outlet oil ports, thus connecting the P oil passage pressure to the stabilizing module accumulator 9 via the inlet check valve 27, the filling control valve 28, the pressure balance valve 24, and the stabilizing module switching valve 22, thereby achieving filling. The filling safety valve 29 is located between the outlet of the pressure balance valve 24 and the return oil T flow channel, with a second damper 30 installed between them to prevent the filling pressure of the stabilizing module accumulator 9 from reaching a high value. When the filling pressure does not cause the filling safety valve 29 to open, no oil flows through the second damper 30. The oil pressure from the pressure balance valve 24 acts on the right control chamber of the filling control valve 28 via the second damper 30, and the oil pressure from the pressure balance valve 24 acts on the left control chamber of the filling control valve 28. Under the action of the spring force, the filling control valve 28 remains in the right position, continuously filling. When the filling pressure reaches the set pressure of the filling safety valve 29, the filling safety valve opens to overflow, and the oil flows through the second damper 30, generating a pressure drop. This pressure drop acts on the control chambers at both ends of the filling control valve 28, overcoming the spring force, and the valve core moves to the left to stop filling.

[0050] Upon receiving the stabilization module activation command, the third solenoid valve 25 is de-energized. The pressure from the stabilization module accumulator 9 acts on the right control chamber of the pressure balancing valve 24 via the stabilization module switching valve 22 and the third solenoid valve 25. The pressure from the boom cylinder's large chamber A3 port acts on the left control chamber of the pressure balancing valve 24. Comparing the two pressures, the stabilization module accumulator 9 pressure is higher, causing the valve core to move to the left, thus depressurizing the stabilization module accumulator 9. When the stabilization module accumulator 9 pressure is lower, the valve core moves to the right, continuing the filling process until the pressures are balanced. After a short interval, once the pressure balancing operation is complete, the second solenoid valve 23 is energized, introducing the pilot oil Pst flow channel pressure into the left control chamber of the stabilization module switching valve 22. Overcoming the spring force, the valve core moves to the right. At this point, the boom cylinder's large chamber port A3 is connected to the stabilization module accumulator 9, and the boom cylinder's small chamber port B3 is connected to the return oil T, achieving a flexible connection.

[0051] There are two ways to depressurize the stabilizing module accumulator: Method 1: With power on, the boom is lowered to the floating lowering position by operating the handle, and the stabilizing module accumulator oil is opened and connected to the oil tank through the boom floating position to depressurize. Method 2: When the system fails and the whole machine cannot be powered on, thus the boom cannot be lowered by operating the handle, the boom can be lowered through the two-way ball valve connected to the oil port A3' of the boom cylinder. At this time, the second solenoid valve 23 is not energized, so the stabilizing module switching valve 22 is in the right position for filling. At this time, the third solenoid valve 25 is not energized and is connected in the left position. The pressure of the boom's large chamber and the pressure of the stabilizing module accumulator 9 act on the two control chambers of the pressure balance valve 24 respectively. At this time, the boom is in the low position and the pressure of the boom's large chamber is low. After pressure comparison, the valve core moves to the left and the pressure balance valve 24 is in the right position. The stabilizing module accumulator pressure is connected to the return oil T flow channel to depressurize. This method can achieve depressurization of the stabilizing module accumulator without opening the stabilizing module. In existing applications, the pressure relief is generally achieved by activating the stabilization module. In this invention, the stabilization module valve group can relieve the pressure on the stabilization module accumulator when the system fails and the whole machine cannot be powered on, thus preventing the safety impact caused by the inability to relieve the pressure of the accumulator.

[0052] The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. An integrated energy-saving load-sensing multi-way valve, characterized in that, The valve body oil inlet P flow channel of each valve group, the signal feedback oil circuit LS flow channel of each valve group, the oil discharge L flow channel of each valve group, the oil return T flow channel of each valve group and the pilot oil Pst flow channel of each valve group are in communication with each other.

2. The integrated energy-saving load sensing multiple spool valve of claim 1, wherein, The oil inlet valve group comprises an LS overflow valve, a constant flow valve, a peak elimination valve, a pilot pressure reducing valve and an electromagnetic valve, the LS overflow valve is arranged between the LS flow channel and the oil return T, the constant flow valve is arranged between the oil inlet valve body LS flow channel and the oil return T flow channel, the peak elimination valve is arranged between the oil inlet valve body oil inlet P flow channel and the oil return T flow channel, and is used for eliminating the pressure peak of the P port, the pilot pressure reducing valve is arranged between the oil inlet P flow channel and the pilot oil Pst oil channel, a first electromagnetic valve is further arranged between the pilot oil Pst oil channel of the pilot pressure reducing valve, and a filter screen is arranged at the inlet of the pilot pressure reducing valve.

3. The integrated energy-saving load sensing multiple spool valve of claim 2, wherein, The constant flow valve comprises a constant flow valve cartridge and a first damper, and the pressure difference generated by the oil flow of the LS signal in the first damper acts on both ends of the constant flow valve cartridge and interacts with the spring set pressure to control the opening of the constant flow valve cartridge.

4. The integrated energy-saving load sensing multiple spool valve of claim 1, wherein, The standby valve group comprises a standby valve body, a standby valve core arranged on the standby valve body, an electric proportional pressure reducing valve and a pressure compensator arranged at both ends of the standby valve core, the pressure oil of the oil inlet P flow channel is connected with the pressure compensator through the standby valve core, one of the oil outlet ports of the pressure compensator is connected with the signal feedback oil circuit LS flow channel, and the other is connected with the oil port A1 and the oil port B1 through the standby valve core; The standby valve core is connected with the pressure compensator through an inlet check valve, and the oil port A1 and the oil port B1 are respectively connected with overload oil supplement valves.

5. The integrated energy-saving load sensing multiple spool valve of claim 1, wherein, The bucket valve group comprises a bucket valve body, a bucket valve core arranged on the bucket valve body, an electric proportional pressure reducing valve and a pressure compensator arranged at both ends of the bucket valve core, the pressure oil of the oil inlet P flow channel is connected with the pressure compensator through the bucket valve core, one of the oil outlet ports of the pressure compensator is connected with the signal feedback oil circuit LS flow channel, and the other is connected with the oil port A2 and the oil port B2 through the bucket valve core; The bucket valve core is connected with the pressure compensator through an inlet check valve, the oil port A2 and the oil port B2 are respectively connected with overload oil supplement valves, the bucket valve core is connected with a hydraulic lock, the hydraulic lock is connected with the oil port A2 and the oil return T flow channel, and the other oil port is connected with the b2 oil port through the oil circuit between the bucket valve core and the electric proportional pressure reducing valve.

6. The integrated energy-saving load sensing multiple spool valve of claim 1, wherein, The boom valve group comprises a boom valve body, a boom valve core arranged on the boom valve body, an electric proportional pressure reducing valve and a pressure compensator arranged at both ends of the boom valve core, the pressure oil of the oil inlet P flow channel is connected with the pressure compensator through the boom valve core, one of the oil outlet ports of the boom pressure compensator is connected with the signal feedback oil circuit LS flow channel, and the other is connected with the oil port A3 and the oil port B3 through the boom valve core; The boom joint valve core is connected with the pressure compensator through an inlet check valve, a supplement oil check valve is arranged between the oil port B3 and the oil return T flow channel, the boom joint valve core is connected with a hydraulic lock, the hydraulic lock is connected with the oil port A3 and the oil return T flow channel, and another oil port is connected with the B3 oil port through an oil path between the boom joint valve core and the electric proportional pressure reducing valve.

7. The integrated energy-saving load sensing multiple spool valve of claim 1, wherein, The hydraulic lock comprises a hydraulic lock control valve and a hydraulic lock stop valve, the hydraulic lock stop valve is connected with the boom joint valve core large cavity working oil port and the oil cylinder large cavity at both ends, the hydraulic lock control valve three oil ports are respectively connected with the spring cavity of the hydraulic lock stop valve and the oil cylinder large cavity oil port and the oil return T flow channel, and the hydraulic lock control valve right control cavity is communicated with the boom joint valve core small cavity pilot oil cavity.

8. The integrated energy-saving load sensing multiple spool valve of claim 1, wherein, The stabilizing module joint valve group comprises a stabilizing module switching valve, a second electromagnetic valve, a pressure balance valve, a third electromagnetic valve, an accumulator safety valve, a liquid filling control valve, a liquid filling safety valve and a second damping, the second electromagnetic valve is connected with the stabilizing module switching valve control port, the stabilizing module switching valve is connected with the oil port A3 and the oil port B3, the pressure balance valve oil port is connected with the stabilizing module switching valve, the third electromagnetic valve is used for controlling the working state of the pressure balance valve and the boom joint large cavity working oil port A3, the accumulator safety valve is arranged between the oil port X2 and the oil return T flow channel, one oil port of the liquid filling control valve is connected with the pressure balance valve, another oil port is connected on the oil path of the liquid filling safety valve and the pressure balance valve and the stabilizing module switching valve, and the second damping is arranged between the third electromagnetic valve and the liquid filling control valve oil port.

9. The integrated energy-saving load sensing multiple spool valve of claim 8, wherein, An inlet check valve two is arranged between the liquid filling control valve and the oil inlet P flow channel.

10. A hydraulic system characterized by, The integrated energy-saving load-sensitive multi-way valve comprises the integrated energy-saving load-sensitive multi-way valve, a variable pump is connected with the oil inlet port P of the oil inlet joint valve group, a pilot accumulator is connected with the oil port X, a deformed machine tool is connected with the oil port B1 and the oil port A1 of the standby joint valve group, a bucket oil cylinder is connected with the B2 oil port and the A2 oil port of the bucket joint valve group, a stabilizing module accumulator is connected with the X2 oil port of the stabilizing module joint valve group, a boom oil cylinder is connected with the B3 oil port and the A3 oil port of the moving joint valve group, and a manual oil drain valve is connected with the A3' oil port.

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