An electro-controlled multi-way directional control valve

Abstract

The present invention discloses an electronically controlled multi-way directional control valve, which comprises a valve body. A bucket tilting directional control valve and a lift directional control valve are arranged in the valve body. The bucket tilting directional control valve comprises a bucket tilting directional control valve orifice and a bucket tilting directional control valve spool. The bucket tilting directional control valve spool is slidably arranged in the bucket tilting directional control valve orifice. One end of the bucket tilting directional control valve spool is in transmission connection with a first servo motor through a first motor rotation-mechanical linear motion converter. The lift directional control valve comprises a lift directional control valve orifice and a lift directional control valve spool. The lift directional control valve spool is slidably arranged in the lift directional control valve orifice. One end of the lift directional control valve spool is in transmission connection with a second servo motor through a second motor rotation-mechanical linear motion converter. The present invention realizes the compound operation of multiple actuators, reduces the design cost, time cost and batch cost of the host machine. At the same time, the simplest and lowest-cost electronic control upgrade can be carried out on the existing host machines in the market, and has good application and popularization prospects.

Description

Technical Field

[0001] The present invention relates to the technical field of hydraulic control, and particularly to an electro-hydraulic multi-way directional control valve. Background Art

[0002] At present, many mainframe hydraulic systems hope to achieve the combined operation of multiple actuators to improve work efficiency. However, to achieve the combined operation of multiple actuators, a variable system + parallel multi-way directional control valve must be adopted, which makes the cost of the entire system very high. Therefore, for some places where it is not particularly necessary, this option is usually abandoned. Generally, a fixed-displacement system + a multi-way directional control valve with a series pressure oil circuit and a parallel return oil circuit is adopted. However, this structure can only make multiple actuators work sequentially and cannot achieve the combined operation of multiple actuators. For example, the vast majority of loaders on the market are still fixed-displacement systems, mainly because the structure of this system is simple and the cost is low. The main control multi-way directional control valve body (core component) is very mature in terms of material, valve body mold, valve body processing, assembly, testing, and pipeline layout of the mainframe, and has high reliability. The fixed-displacement system of loaders mainly uses mechanical control and hydraulic control of the spool working mode, which cannot achieve the combined operation of multiple actuators. Especially for different materials and different working environments, higher requirements are put forward for the operation skills of the operator. If a variable system and a parallel multi-way directional control valve (brand-new valve body) are adopted, not only the mold cost, processing cost, and time cost will increase significantly, but also there are many uncertain factors such as working reliability, failure rate, and after-sales maintenance.

[0003] Therefore, how to provide a multi-way directional control valve that can achieve the combined operation of multiple actuators by using the existing multi-way directional control valve body structure in a fixed-displacement hydraulic system is an urgent problem to be solved by those skilled in the art. Summary of the Invention

[0004] The purpose of the present invention is to provide an electro-hydraulic multi-way directional control valve, which can achieve the combined operation of multiple actuators by using the existing multi-way directional control valve body structure in a fixed-displacement hydraulic system, and improve the work efficiency of the mainframe.

[0005] To achieve the above purpose, the present invention provides the following technical solutions:

[0006] An electronically controlled multi-way directional control valve includes a valve body. A bucket directional control valve and a lift directional control valve are arranged inside the valve body. The bucket directional control valve includes a bucket directional control valve hole and a bucket directional control valve spool. The bucket directional control valve spool is slidably arranged inside the bucket directional control valve hole. One end of the bucket directional control valve spool is in driving connection with a first servo motor through a first motor rotation-mechanical linear motion converter. The lift directional control valve includes a lift directional control valve hole and a lift directional control valve spool. The lift directional control valve spool is slidably arranged inside the lift directional control valve hole. One end of the lift directional control valve spool is in driving connection with a second servo motor through a second motor rotation-mechanical linear motion converter. The first servo motor and the second servo motor are respectively electrically connected to an upper computer control unit. The valve body is provided with a plurality of oil ports. When the bucket directional control valve spool and the lift directional control valve spool act, different working hydraulic circuits can be formed by closing or communicating the oil ports.

[0007] Further, one end of the first motor rotation-mechanical linear motion converter is fixedly connected to the output shaft of the first servo motor, and the other end is hinged to the bucket directional control valve spool, for converting the rotational motion of the first servo motor into the linear reciprocating motion of the bucket directional control valve spool inside the bucket directional control valve hole.

[0008] Further, one end of the second motor rotation-mechanical linear motion converter is fixedly connected to the output shaft of the second servo motor, and the other end is hinged to the lift directional control valve spool, for converting the rotational motion of the second servo motor into the linear reciprocating motion of the lift directional control valve spool inside the lift directional control valve hole.

[0009] Further, the lift directional control valve is a five-position six-way directional control valve, and is provided with a lift neutral position EO, a cut-off position E1, a lift position E2, a floating position E3 and a lowering position E4.

[0010] Further, the bucket directional control valve is a three-position six-way directional control valve, and is provided with a bucket neutral position CO, an upper turn position C1 and a lower turn position C2.

[0011] Further, an oil inlet P, an oil outlet T, a first working oil port A1 of the tilting cylinder, a second working oil port B1 of the tilting cylinder, a first working oil port A2 of the lifting cylinder, and a second working oil port B2 of the lifting cylinder are provided on the surface of the valve body. A tilting reversing valve hole and a lifting reversing valve hole are provided inside the valve body. Tilting reversing valve ports that are respectively communicated with the tilting reversing valve hole are provided inside the valve body. The tilting reversing valve ports include a first oil port P0 of the tilting reversing valve, a second oil port P1 of the tilting reversing valve, a third oil port P2 of the tilting reversing valve, a fourth oil port D0 of the tilting reversing valve, a fifth oil port D1 of the tilting reversing valve, and a sixth oil port D2 of the tilting reversing valve. When the tilting reversing valve spool is in different positions, it can block or communicate with the corresponding tilting reversing valve ports. Lifting reversing valve ports that are respectively communicated with the lifting reversing valve hole are provided inside the valve body. The lifting reversing valve ports include a first oil port Q0 of the lifting reversing valve, a second oil port Q1 of the lifting reversing valve, a third oil port Q2 of the lifting reversing valve, a fourth oil port F0 of the lifting reversing valve, a fifth oil port F1 of the lifting reversing valve, and a sixth oil port F2 of the lifting reversing valve. When the lifting reversing valve spool is in different positions, it can block or communicate with the corresponding lifting reversing valve ports. The first oil port P0 of the tilting reversing valve and the third oil port P2 of the tilting reversing valve are communicated with the oil inlet P through internal channels. The second oil port P1 of the tilting reversing valve, the second oil port Q1 of the lifting reversing valve, and the fourth oil port F0 of the lifting reversing valve are respectively communicated with the oil outlet T through internal channels. The fifth oil port D1 of the tilting reversing valve is communicated with the second working oil port B1 of the tilting cylinder through an internal channel. The sixth oil port D2 of the tilting reversing valve is communicated with the first working oil port A1 of the tilting cylinder through an internal channel. The first oil port Q0 of the lifting reversing valve and the third oil port Q2 of the lifting reversing valve are communicated with the fourth oil port D0 of the tilting reversing valve through internal channels. The fifth oil port F1 of the lifting reversing valve is communicated with the second working oil port B2 of the lifting cylinder through an internal channel. The sixth oil port F2 of the lifting reversing valve is communicated with the first working oil port A2 of the lifting cylinder through an internal channel.

[0012] Further, a safety valve is provided inside the valve body. Both ends of the safety valve are respectively communicated with the oil inlet P and the oil outlet T through internal channels.

[0013] Further, a one-way oil replenishing valve is provided inside the valve body. The inlet of the one-way oil replenishing valve is communicated with the oil outlet T through an internal channel. The outlet of the one-way oil replenishing valve is communicated with the second working oil port B2 of the lifting cylinder through an internal channel.

[0014] Further, a first overload oil replenishing valve and a second overload oil replenishing valve are provided inside the valve body. Both ends of the first overload oil replenishing valve are respectively communicated with the second working oil port B1 of the tilting cylinder and the oil outlet T through internal channels. Both ends of the second overload oil replenishing valve are respectively communicated with the first working oil port A1 of the tilting cylinder and the oil outlet T through internal channels.

[0015] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0016] 1. The present invention is provided with a servo motor and a motor rotation-mechanical linear motion converter. The upper computer control unit is electrically connected to the servo motor. Both ends of the motor rotation-mechanical linear motion converter are respectively connected to the servo motor and the spool of the directional control valve. The upper computer control unit can control the forward and reverse rotation of the servo motor and convert the rotational motion of the servo motor into a linear reciprocating motion of the spool of the directional control valve in the valve hole of the directional control valve through the motor rotation-mechanical linear motion converter, and realize the position control of the spool of the directional control valve, so as to meet the working requirements to be achieved by the electric control multi-way directional control valve.

[0017] 2. The lift directional control valve is a five-position six-way directional control valve, provided with a lift neutral position EO, a cut-off position E1, a lift position E2, a floating position E3 and a lowering position E4. The bucket tilt directional control valve is a three-position six-way directional control valve, provided with a bucket tilt neutral position CO, an upper tilt position C1 and a lower tilt position C2. By controlling the positions of the spools of the bucket tilt directional control valve and the lift directional control valve, a variety of working modes can be combined, and the host can realize functions such as the bucket tilt up, the bucket tilt down, the boom lift, the boom lower, the bucket float and the bucket tilt-boom compound action, etc., to adapt to different working conditions, improve the working performance of the host. At the same time, the bucket tilt-boom compound action can greatly improve the operation efficiency, reduce the energy consumption, and also reduce the requirements for the operation skills of the operator.

[0018] 3. The present invention makes little change to the existing multi-way directional control valve body structure, ensuring the compatibility with the existing multi-way directional control valve, and realizing the compound work of multiple actuators, reducing the design cost, time cost and batch cost of the host. At the same time, the simplest and lowest-cost electric control upgrade can be carried out on the existing hosts in the market, having good application and popularization prospects. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 It is the schematic diagram of the neutral position of the electric control multi-way directional control valve of the present invention;

[0020] Figure 2 It is the schematic diagram of the working principle of the bucket tilt micro-motion-slow upward rotation of the electric control multi-way directional control valve of the present invention;

[0021] Figure 3 It is the schematic diagram of the working principle of the bucket tilt full-speed upward rotation of the electric control multi-way directional control valve of the present invention;

[0022] Figure 4 It is the schematic diagram of the working principle of the bucket tilt micro-motion-slow downward rotation of the electric control multi-way directional control valve of the present invention;

[0023] Figure 5 It is the schematic diagram of the working principle of the bucket tilt full-speed downward rotation of the electric control multi-way directional control valve of the present invention;

[0024] Figure 6 It is the schematic diagram of the working principle of the boom lift of the electric control multi-way directional control valve of the present invention;

[0025] Figure 7 This is the working schematic diagram of the boom self-weight (unpressurized) lowering of the electro-hydraulic multi-way directional control valve of the present invention;

[0026] Figure 8 This is the working schematic diagram of the boom pressurized lowering of the electro-hydraulic multi-way directional control valve of the present invention;

[0027] Figure 9 This is the working schematic diagram of the bucket upward rotation - boom lifting compound of the electro-hydraulic multi-way directional control valve of the present invention;

[0028] Figure 10 This is the working schematic diagram of the bucket upward rotation - boom lowering compound of the electro-hydraulic multi-way directional control valve of the present invention;

[0029] Figure 11 This is the working schematic diagram of the bucket downward rotation - boom lifting compound of the electro-hydraulic multi-way directional control valve of the present invention;

[0030] Figure 12 This is the working schematic diagram of the bucket downward rotation - boom lowering compound of the electro-hydraulic multi-way directional control valve of the present invention;

[0031] In the figure: 1 - valve body, 101 - bucket directional control valve orifice, 102 - lifting directional control valve orifice, 2 - first servo motor, 3 - first motor rotation - mechanical linear motion converter, 4 - bucket directional control valve spool, 5 - second servo motor, 6 - second motor rotation - mechanical linear motion converter, 7 - lifting directional control valve spool, 8 - one-way oil replenishing valve, 9 - safety valve, 10 - first overload oil replenishing valve, 11 - second overload oil replenishing valve, 12 - bucket cylinder, 13 - lifting cylinder, 14 - upper computer control unit. Specific embodiments

[0032] The present invention will be described in detail below with reference to the accompanying drawings and specific embodiments.

[0033] Embodiment 1:

[0034] Taking the installation of the present invention on a loader as an example, please refer to Figure 1, an electronically controlled multi-way directional control valve, comprising a valve body 1. A bucket directional control valve and a lift directional control valve are arranged inside the valve body 1. The bucket directional control valve includes a bucket directional control valve hole 101 and a bucket directional control valve spool 4. The bucket directional control valve spool 4 is slidably arranged inside the bucket directional control valve hole 101. One end of the bucket directional control valve spool 4 is in driving connection with a first servo motor 2 through a first motor rotation-mechanical linear motion converter 3. The lift directional control valve includes a lift directional control valve hole 102 and a lift directional control valve spool 7. The lift directional control valve spool 7 is slidably arranged inside the lift directional control valve hole 102. One end of the lift directional control valve spool 7 is in driving connection with a second servo motor 5 through a second motor rotation-mechanical linear motion converter 6. The first servo motor 2 and the second servo motor 5 are respectively electrically connected to a host computer control unit 14. The valve body 1 is provided with a plurality of oil ports. When the bucket directional control valve spool 4 and the lift directional control valve spool 7 act, different working hydraulic circuits can be formed by closing or connecting the oil ports.

[0035] Wherein, one end of the first motor rotation-mechanical linear motion converter 3 is fixedly connected to the output shaft of the first servo motor 2 through a flat key, and the other end is hinged to the bucket directional control valve spool 4, and is used for converting the rotational motion of the first servo motor 2 into the linear reciprocating motion of the bucket directional control valve spool 4 inside the bucket directional control valve hole 101.

[0036] Wherein, one end of the second motor rotation-mechanical linear motion converter 6 is fixedly connected to the output shaft of the second servo motor 5 through a flat key, and the other end is hinged to the lift directional control valve spool 7, and is used for converting the rotational motion of the second servo motor 5 into the linear reciprocating motion of the lift directional control valve spool 7 inside the lift directional control valve hole 102.

[0037] Wherein, the lift directional control valve is a five-position six-way directional control valve, and is provided with a lift neutral position EO, a cut-off position E1, a lift position E2, a floating position E3 and a lowering position E4.

[0038] Wherein, the bucket directional control valve is a three-position six-way directional control valve, and is provided with a bucket neutral position CO, an upper rotation position C1 and a lower rotation position C2.

[0039] Among them, the surface of the valve body 1 is provided with an oil inlet P, an oil outlet T, a first working oil port A1 of the tipping cylinder, a second working oil port B1 of the tipping cylinder, a first working oil port A2 of the lifting cylinder, and a second working oil port B2 of the lifting cylinder. Inside the valve body 1, a tipping reversing valve hole 101 and a lifting reversing valve hole 102 are provided. Inside the valve body 1, tipping reversing valve ports respectively communicating with the tipping reversing valve hole 101 are provided. The tipping reversing valve ports include a first oil port P0 of the tipping reversing valve, a second oil port P1 of the tipping reversing valve, a third oil port P2 of the tipping reversing valve, a fourth oil port D0 of the tipping reversing valve, a fifth oil port D1 of the tipping reversing valve, and a sixth oil port D2 of the tipping reversing valve. When the tipping reversing valve spool 4 is in different positions, it can block or communicate with the corresponding tipping reversing valve ports. Inside the valve body 1, lifting reversing valve ports respectively communicating with the lifting reversing valve hole 102 are provided. The lifting reversing valve ports include a first oil port Q0 of the lifting reversing valve, a second oil port Q1 of the lifting reversing valve, a third oil port Q2 of the lifting reversing valve, a fourth oil port F0 of the lifting reversing valve, a fifth oil port F1 of the lifting reversing valve, and a sixth oil port F2 of the lifting reversing valve. When the lifting reversing valve spool 7 is in different positions, it can block or communicate with the corresponding lifting reversing valve ports. The first oil port P0 of the tipping reversing valve and the third oil port P2 of the tipping reversing valve are communicated with the oil inlet P through internal channels. The second oil port P1 of the tipping reversing valve, the second oil port Q1 of the lifting reversing valve, and the fourth oil port F0 of the lifting reversing valve are respectively communicated with the oil outlet T through internal channels. The fifth oil port D1 of the tipping reversing valve is communicated with the second working oil port B1 of the tipping cylinder through an internal channel. The sixth oil port D2 of the tipping reversing valve is communicated with the first working oil port A1 of the tipping cylinder through an internal channel. The first oil port Q0 of the lifting reversing valve and the third oil port Q2 of the lifting reversing valve are communicated with the fourth oil port D0 of the tipping reversing valve through internal channels. The fifth oil port F1 of the lifting reversing valve is communicated with the second working oil port B2 of the lifting cylinder through an internal channel. The sixth oil port F2 of the lifting reversing valve is communicated with the first working oil port A2 of the lifting cylinder through an internal channel. The oil inlet P is communicated with the oil suction port of the fuel tank through a hydraulic pipeline. The oil outlet T is communicated with the oil return port of the fuel tank through a hydraulic pipeline. The first working oil port A1 of the tipping cylinder is communicated with the large chamber of the tipping cylinder 12 through a hydraulic hose. The second working oil port B1 of the tipping cylinder is communicated with the small chamber of the tipping cylinder 12 through a hydraulic hose. The first working oil port A2 of the lifting cylinder is communicated with the large chamber of the lifting cylinder 13 through a hydraulic hose. The second working oil port B2 of the lifting cylinder is communicated with the small chamber of the lifting cylinder 13 through a hydraulic hose.

[0040] Among them, a safety valve 9 is installed inside the valve body 1. Both ends of the safety valve 9 are communicated with the oil inlet P and the oil outlet T respectively through internal channels. The safety valve 9 is used to set the working pressure of the hydraulic system and prevent the hydraulic system from overloading.

[0041] Among them, a one-way oil replenishing valve 8 is installed in the valve body 1. The inlet of the one-way oil replenishing valve 8 is communicated with the oil outlet T through an internal passage, and the outlet of the one-way oil replenishing valve 8 is communicated with the second working oil port B2 of the lifting cylinder through an internal passage. When the lifting cylinder 13 works and descends, due to the weight of the materials loaded in the bucket plus the self-weight of the bucket, the main boom of the host accelerates downward. The oil supply in the small chamber of the lifting cylinder 13 is insufficient and prone to form a vacuum. The oil in the fuel tank overcomes the spring force under the action of atmospheric pressure to open the one-way oil replenishing valve 8 and replenish oil to the small chamber of the lifting cylinder 13 to prevent the generation of cavitation phenomenon and ensure the normal operation of the hydraulic system.

[0042] Among them, a first overload oil replenishing valve 10 and a second overload oil replenishing valve 11 are installed in the valve body 1. Both ends of the first overload oil replenishing valve 10 are respectively communicated with the second working oil port B1 and the oil outlet T of the tilting cylinder through internal passages. Both ends of the second overload oil replenishing valve 11 are respectively communicated with the first working oil port A1 and the oil outlet T of the tilting cylinder through internal passages. The first overload oil replenishing valve 10 is used to prevent overload in the small chamber of the tilting cylinder 12 and replenish oil to the small chamber of the tilting cylinder 12 when the oil supply in the small chamber of the tilting cylinder 12 is insufficient. The second overload oil replenishing valve 11 is used to prevent overload in the large chamber of the tilting cylinder 12 and replenish oil to the large chamber of the tilting cylinder 12 when the oil supply in the large chamber of the tilting cylinder 12 is insufficient.

[0043] When the loader is walking without loading operation, the spool 4 of the tilting direction valve is in the tilting middle position CO, and the spool 7 of the lifting direction valve is in the lifting middle position EO. At this time, the first oil port P0 of the tilting direction valve is communicated with the fourth oil port D0 of the tilting direction valve, and the second oil port P1, the third oil port P2, the fifth oil port D1, and the sixth oil port D2 of the tilting direction valve are closed. The first oil port Q0 of the lifting direction valve is communicated with the fourth oil port F0 of the lifting direction valve, and the second oil port Q1, the third oil port Q2, the fifth oil port F1, and the sixth oil port F2 of the lifting direction valve are closed. The pressure oil flow path is as Figure 1 shown by the thick solid line. The pressure oil returns to the fuel tank from the fuel tank through the oil inlet P, the first oil port P0 of the tilting direction valve, the fourth oil port D0 of the tilting direction valve, the first oil port Q0 of the lifting direction valve, the fourth oil port F0 of the lifting direction valve, and the oil outlet T, realizing the middle position unloading function.

[0044] Embodiment 2:

[0045] When the loader needs to perform the bucket fine movement - slow upward rotation operation, the driver sends a control signal through the upper computer control unit 14 to control the operation of the first servo motor 2 and the second servo motor 5, causing the spool 4 of the bucket change-over valve to move to the upward rotation position C1 and the spool 7 of the lift change-over valve to move to the lift middle position EO. At this time, the first oil port P0 of the bucket change-over valve is connected to the fourth oil port D0 of the bucket change-over valve, the second oil port P1 of the bucket change-over valve is connected to the fifth oil port D1 of the bucket change-over valve, the third oil port P2 of the bucket change-over valve is connected to the sixth oil port D2 of the bucket change-over valve, the first oil port Q0 of the lift change-over valve is connected to the fourth oil port F0 of the lift change-over valve, and the second oil port Q1, the third oil port Q2, the fifth oil port F1, and the sixth oil port F2 of the lift change-over valve are closed. The pressure oil flow path is as Figure 2 shown by the thick solid line. The pressure oil is distributed into two pressure oil circuits after passing through the oil inlet P. One of them passes through the third oil port P2 of the bucket change-over valve, the sixth oil port D2 of the bucket change-over valve, and the first working oil port A1 of the bucket cylinder to enter the large chamber of the bucket cylinder 12, pushing the piston rod of the bucket cylinder 12 to extend to make the bucket rotate upward. The oil in the small chamber of the bucket cylinder 12 returns to the fuel tank through the second working oil port B1 of the bucket cylinder, the fifth oil port D1 of the bucket change-over valve, the second oil port P1 of the bucket change-over valve, and the oil outlet T. The other redundant oil returns to the fuel tank through the first oil port P0 of the bucket change-over valve, the fourth oil port D0 of the bucket change-over valve, the first oil port Q0 of the lift change-over valve, the fourth oil port F0 of the lift change-over valve, and the oil outlet T. The position of the spool 4 of the bucket change-over valve can be controlled by the first servo motor 2 to control the opening size of the third oil port P2 of the bucket change-over valve, and further control the flow rate of the oil flowing through the third oil port P2 of the bucket change-over valve. The flow rate of the oil flowing through the third oil port P2 of the bucket change-over valve determines the upward rotation speed of the bucket, so that the bucket fine movement - slow upward rotation operation can be realized.

[0046] Embodiment Three:

[0047] When the loader needs to perform the bucket full-speed upward rotation operation, the driver sends a control signal through the upper computer control unit 14 to control the operation of the first servo motor 2 and the second servo motor 5, causing the spool 4 of the bucket change-over valve to move to the upward rotation position C1 and the spool 7 of the lift change-over valve to move to the cut-off position E1. At this time, the first oil port P0 of the bucket change-over valve is connected to the fourth oil port D0 of the bucket change-over valve, the second oil port P1 of the bucket change-over valve is connected to the fifth oil port D1 of the bucket change-over valve, the third oil port P2 of the bucket change-over valve is connected to the sixth oil port D2 of the bucket change-over valve, and the first oil port Q0, the second oil port Q1, the third oil port Q2, the fourth oil port F0, the fifth oil port F1, and the sixth oil port F2 of the lift change-over valve are closed. The pressure oil flow path is as Figure 3As shown by the thick solid line, the full flow of the pressure oil enters the large chamber of the bucket cylinder 12 through the oil inlet P, the third oil port P2 of the bucket control valve, the sixth oil port D2 of the bucket control valve, and the first working oil port A1 of the bucket cylinder, pushing the piston rod of the bucket cylinder 12 to extend and causing the bucket to rotate upward at full speed. The oil in the small chamber of the bucket cylinder 12 returns to the fuel tank through the second working oil port B1 of the bucket cylinder, the fifth oil port D1 of the bucket control valve, the second oil port P1 of the bucket control valve, and the oil outlet T, realizing the full-speed upward rotation of the bucket.

[0048] Example 4:

[0049] When the loader needs to perform the bucket fine movement - slow downward rotation operation, the driver sends a control signal through the upper computer control unit 14 to control the operation of the first servo motor 2 and the second servo motor 5, causing the spool 4 of the bucket control valve to move to the downward rotation position C2 and the spool 7 of the lift control valve to move to the lift middle position EO. At this time, the first oil port P0 of the bucket control valve is connected to the fourth oil port D0 of the bucket control valve, the second oil port P1 of the bucket control valve is connected to the sixth oil port D2 of the bucket control valve, the third oil port P2 of the bucket control valve is connected to the fifth oil port D1 of the bucket control valve, the first oil port Q0 of the lift control valve is connected to the fourth oil port F0 of the lift control valve, and the second oil port Q1, the third oil port Q2, the fifth oil port F1, and the sixth oil port F2 of the lift control valve are closed. The pressure oil flow path is as Figure 4 shown by the thick solid line. The pressure oil is divided into two pressure oil circuits after passing through the oil inlet P. One of them enters the small chamber of the bucket cylinder 12 through the third oil port P2 of the bucket control valve, the fifth oil port D1 of the bucket control valve, and the second working oil port B1 of the bucket cylinder, pushing the piston rod of the bucket cylinder 12 to retract and causing the bucket to rotate downward. The oil in the large chamber of the bucket cylinder 12 returns to the fuel tank through the first working oil port A1 of the bucket cylinder, the sixth oil port D2 of the bucket control valve, the second oil port P1 of the bucket control valve, and the oil outlet T. The other excess oil returns to the fuel tank through the first oil port P0 of the bucket control valve, the fourth oil port D0 of the bucket control valve, the first oil port Q0 of the lift control valve, the fourth oil port F0 of the lift control valve, and the oil outlet T. The position of the spool 4 of the bucket control valve can be controlled by the first servo motor 2 to control the opening size of the third oil port P2 of the bucket control valve, and further control the flow rate of the oil flowing through the third oil port P2 of the bucket control valve. The flow rate of the oil flowing through the third oil port P2 of the bucket control valve determines the downward rotation speed of the bucket, thus enabling the bucket fine movement - slow downward rotation operation.

[0050] Example 5:

[0051] When the loader needs to perform the full-speed downward rotation of the bucket, the driver sends a control signal through the upper computer control unit 14 to control the operation of the first servo motor 2 and the second servo motor 5, causing the spool 4 of the bucket reversing valve to move to the downward rotation position C2 and the spool 7 of the lift reversing valve to move to the cut-off position E1. At this time, the first oil port P0 of the bucket reversing valve is connected to the fourth oil port D0 of the bucket reversing valve, the second oil port P1 of the bucket reversing valve is connected to the sixth oil port D2 of the bucket reversing valve, the third oil port P2 of the bucket reversing valve is connected to the fifth oil port D1 of the bucket reversing valve, and the first oil port Q0, the second oil port Q1, the third oil port Q2, the fourth oil port F0, the fifth oil port F1, and the sixth oil port F2 of the lift reversing valve are closed. The pressure oil flow path is as Figure 5 shown by the thick solid line. The full flow of the pressure oil passes through the oil inlet P, the third oil port P2 of the bucket reversing valve, the fifth oil port D1 of the bucket reversing valve, and the second working oil port B1 of the bucket cylinder to enter the small chamber of the bucket cylinder 12, pushing the piston rod of the bucket cylinder 12 to retract to make the bucket rotate downward at full speed. The oil in the large chamber of the bucket cylinder 12 passes through the first working oil port A1 of the bucket cylinder, the sixth oil port D2 of the bucket reversing valve, the second oil port P1 of the bucket reversing valve, and the oil outlet T back to the fuel tank, realizing the full-speed downward rotation of the bucket.

[0052] Example Six:

[0053] When the loader needs to perform the boom lifting operation, the driver sends a control signal through the upper computer control unit 14 to control the operation of the first servo motor 2 and the second servo motor 5, causing the spool 4 of the bucket reversing valve to move to the middle position CO of the bucket and the spool 7 of the lift reversing valve to move to the lifting position E2. At this time, the first oil port P0 of the bucket reversing valve is connected to the fourth oil port D0 of the bucket reversing valve, and the second oil port P1, the third oil port P2, the fifth oil port D1, and the sixth oil port D2 of the bucket reversing valve are closed. The second oil port Q1 of the lift reversing valve is connected to the fifth oil port F1 of the lift reversing valve, the third oil port Q2 of the lift reversing valve is connected to the sixth oil port F2 of the lift reversing valve, and the first oil port Q0 and the fourth oil port F0 of the lift reversing valve are closed. The pressure oil flow path is as Figure 6 shown by the thick solid line. The full flow of the pressure oil passes through the oil inlet P, the first oil port P0 of the bucket reversing valve, the fourth oil port D0 of the bucket reversing valve, the third oil port Q2 of the lift reversing valve, the sixth oil port F2 of the lift reversing valve, and the first working oil port A2 of the lift cylinder to enter the large chamber of the lift cylinder 13, pushing the piston rod of the lift cylinder 13 to extend to lift the boom. The oil in the small chamber of the lift cylinder 13 passes through the second working oil port B2 of the lift cylinder, the fifth oil port F1 of the lift reversing valve, the second oil port Q1 of the lift reversing valve, and the oil outlet T back to the fuel tank, realizing the boom lifting operation.

[0054] Example Seven:

[0055] When the loader needs to perform the boom self-weight (unpressurized) lowering operation or floating operation, the driver sends a control signal through the upper computer control unit 14 to control the operation of the first servo motor 2 and the second servo motor 5, so that the spool 4 of the bucket turning valve moves to the neutral position CO of the bucket turning, and the spool 7 of the lift valve moves to the floating position E3. At this time, the first oil port P0 of the bucket turning valve is connected to the fourth oil port D0 of the bucket turning valve, and the second oil port P1, the third oil port P2, the fifth oil port D1, and the sixth oil port D2 of the bucket turning valve are closed. The first oil port Q0 of the lift valve is connected to the fourth oil port F0 of the lift valve, the second oil port Q1 of the lift valve is connected to the sixth oil port F2 of the lift valve, and the third oil port Q2 of the lift valve is connected to the fifth oil port F1 of the lift valve. The pressure oil flow path is as Figure 7 shown by the thick solid line. The pressure oil passes through the oil inlet P, the first oil port P0 of the bucket turning valve, the fourth oil port D0 of the bucket turning valve, the first oil port Q0 of the lift valve, the fourth oil port F0 of the lift valve, and the oil outlet T and returns to the fuel tank for unloading. At the same time, since the fifth oil port F1 and the sixth oil port F2 of the lift valve are respectively connected to the fuel tank through the third oil port Q2 and the second oil port Q1 of the lift valve, the large chamber and the small chamber of the lift cylinder 13 are also connected to the fuel tank. The pressures in the large chamber and the small chamber of the lift cylinder 13 are balanced and in a low-pressure state, and the boom descends under the action of its own weight, causing the bucket to float freely on the ground, realizing the bucket floating operation.

[0056] Example Eight:

[0057] When the loader needs to perform the boom pressurized lowering operation, the driver sends a control signal through the upper computer control unit 14 to control the operation of the first servo motor 2 and the second servo motor 5, so that the spool 4 of the bucket turning valve moves to the neutral position CO of the bucket turning, and the spool 7 of the lift valve moves to the lowering position E4. At this time, the first oil port P0 of the bucket turning valve is connected to the fourth oil port D0 of the bucket turning valve, and the second oil port P1, the third oil port P2, the fifth oil port D1, and the sixth oil port D2 of the bucket turning valve are closed. The second oil port Q1 of the lift valve is connected to the sixth oil port F2 of the lift valve, and the third oil port Q2 of the lift valve is connected to the fifth oil port F1 of the lift valve. The first oil port Q0 and the fourth oil port F0 of the lift valve are closed. The pressure oil flow path is as Figure 8 shown by the thick solid line. The pressure oil passes through the oil inlet P, the first oil port P0 of the bucket turning valve, the fourth oil port D0 of the bucket turning valve, the third oil port Q2 of the lift valve, the fifth oil port F1 of the lift valve, and the second working oil port B2 of the lift cylinder and enters the small chamber of the lift cylinder 13, pushing the piston rod of the lift cylinder 13 to retract, causing the boom to lower. The oil in the large chamber of the lift cylinder 13 passes through the first working oil port A2 of the lift cylinder, the sixth oil port F2 of the lift valve, the second oil port Q1 of the lift valve, and the oil outlet T and returns to the fuel tank, realizing the boom pressurized lowering operation.

[0058] Example 9:

[0059] When the loader needs to perform the combined operation of bucket rotation upward - boom lifting, the driver sends a control signal through the upper computer control unit 14 to control the operation of the first servo motor 2 and the second servo motor 5, so that the spool 4 of the bucket rotation reversing valve moves to the upward rotation position C1, and the spool 7 of the lifting reversing valve moves to the lifting position E2. At this time, the first oil port P0 of the bucket rotation reversing valve is connected to the fourth oil port D0 of the bucket rotation reversing valve, the second oil port P1 of the bucket rotation reversing valve is connected to the fifth oil port D1 of the bucket rotation reversing valve, the third oil port P2 of the bucket rotation reversing valve is connected to the sixth oil port D2 of the bucket rotation reversing valve, the second oil port Q1 of the lifting reversing valve is connected to the fifth oil port F1 of the lifting reversing valve, the third oil port Q2 of the lifting reversing valve is connected to the sixth oil port F2 of the lifting reversing valve, and the first oil port Q0 and the fourth oil port F0 of the lifting reversing valve are closed. The pressure oil flow path is as Figure 9 shown by the thick solid line. The pressure oil is distributed into two pressure oil circuits after passing through the oil inlet P. One of the circuits passes through the first oil port P0 of the bucket rotation reversing valve, the fourth oil port D0 of the bucket rotation reversing valve, the third oil port Q2 of the lifting reversing valve, the sixth oil port F2 of the lifting reversing valve, and the first working oil port A2 of the lifting cylinder to enter the large chamber of the lifting cylinder 13 to push the piston rod of the lifting cylinder 13 to extend and lift the boom. The oil in the small chamber of the lifting cylinder 13 returns to the fuel tank through the second working oil port B2 of the lifting cylinder, the fifth oil port F1 of the lifting reversing valve, the second oil port Q1 of the lifting reversing valve, and the oil outlet T. The other circuit passes through the third oil port P2 of the bucket rotation reversing valve, the sixth oil port D2 of the bucket rotation reversing valve, and the first working oil port A1 of the bucket rotation cylinder to enter the large chamber of the bucket rotation cylinder 12, push the piston rod of the bucket rotation cylinder 12 to extend and rotate the bucket upward. The oil in the small chamber of the bucket rotation cylinder 12 returns to the fuel tank through the second working oil port B1 of the bucket rotation cylinder, the fifth oil port D1 of the bucket rotation reversing valve, the second oil port P1 of the bucket rotation reversing valve, and the oil outlet T, realizing the combined operation of bucket rotation upward - boom lifting.

[0060] Example 10:

[0061] When the loader needs to perform the combined operation of bucket rotation upward - boom lowering, the driver sends a control signal through the upper computer control unit 14 to control the operation of the first servo motor 2 and the second servo motor 5, so that the spool 4 of the bucket rotation reversing valve moves to the upward rotation position C1, and the spool 7 of the lifting reversing valve moves to the floating position E3. At this time, the first oil port P0 of the bucket rotation reversing valve is connected to the fourth oil port D0 of the bucket rotation reversing valve, the second oil port P1 of the bucket rotation reversing valve is connected to the fifth oil port D1 of the bucket rotation reversing valve, the third oil port P2 of the bucket rotation reversing valve is connected to the sixth oil port D2 of the bucket rotation reversing valve, the first oil port Q0 of the lifting reversing valve is connected to the fourth oil port F0 of the lifting reversing valve, the second oil port Q1 of the lifting reversing valve is connected to the sixth oil port F2 of the lifting reversing valve, the third oil port Q2 of the lifting reversing valve is connected to the fifth oil port F1 of the lifting reversing valve. The pressure oil flow path is as Figure 10As shown by the thick solid line, the pressure oil is divided into two pressure oil circuits after passing through the oil inlet P. One circuit enters the large chamber of the bucket cylinder 12 through the third oil port P2 of the bucket control valve, the sixth oil port D2 of the bucket control valve, and the first working oil port A1 of the bucket cylinder, pushing the piston rod of the bucket cylinder 12 to extend and causing the bucket to rotate upward. The oil in the small chamber of the bucket cylinder 12 returns to the fuel tank through the second working oil port B1 of the bucket cylinder, the fifth oil port D1 of the bucket control valve, the second oil port P1 of the bucket control valve, and the oil outlet T. The other circuit returns to the fuel tank through the first oil port P0 of the bucket control valve, the fourth oil port D0 of the bucket control valve, the first oil port Q0 of the lift control valve, the fourth oil port F0 of the lift control valve, and the oil outlet T. At the same time, since the fifth oil port F1 and the sixth oil port F2 of the lift control valve are respectively connected to the fuel tank through the third oil port Q2 and the second oil port Q1 of the lift control valve, the large chamber and the small chamber of the lift cylinder 13 are also connected to the fuel tank. The pressures in the large chamber and the small chamber of the lift cylinder 13 are balanced and in a low-pressure state, and the boom descends under its own weight, realizing the combined operation of the bucket rotating upward and the boom descending.

[0062] Embodiment XI:

[0063] When the loader needs to perform the combined operation of the bucket rotating downward and the boom lifting, the driver sends a control signal through the upper computer control unit 14 to control the operation of the first servo motor 2 and the second servo motor 5, causing the spool 4 of the bucket control valve to move to the downward rotation position C2 and the spool 7 of the lift control valve to move to the lifting position E2. At this time, the first oil port P0 of the bucket control valve is connected to the fourth oil port D0 of the bucket control valve, the second oil port P1 of the bucket control valve is connected to the sixth oil port D2 of the bucket control valve, the third oil port P2 of the bucket control valve is connected to the fifth oil port D1 of the bucket control valve, the second oil port Q1 of the lift control valve is connected to the fifth oil port F1 of the lift control valve, the third oil port Q2 of the lift control valve is connected to the sixth oil port F2 of the lift control valve, and the first oil port Q0 and the fourth oil port F0 of the lift control valve are closed. The pressure oil flow path is as Figure 11As shown by the thick solid line, the pressure oil is divided into two pressure oil circuits after passing through the oil inlet P. One circuit enters the small chamber of the tipping cylinder 12 through the third oil port P2 of the tipping control valve, the fifth oil port D1 of the tipping control valve, and the second working oil port B1 of the tipping cylinder, pushing the piston rod of the tipping cylinder 12 to retract and causing the tipping bucket to rotate downward. The oil in the large chamber of the tipping cylinder 12 returns to the fuel tank through the first working oil port A1 of the tipping cylinder, the sixth oil port D2 of the tipping control valve, the second oil port P1 of the tipping control valve, and the oil outlet T. The other circuit enters the large chamber of the lifting cylinder 13 through the first oil port P0 of the tipping control valve, the fourth oil port D0 of the tipping control valve, the third oil port Q2 of the lifting control valve, the sixth oil port F2 of the lifting control valve, and the first working oil port A2 of the lifting cylinder, pushing the piston rod of the lifting cylinder 13 to extend and causing the boom to lift. The oil in the small chamber of the lifting cylinder 13 returns to the fuel tank through the second working oil port B2 of the lifting cylinder, the fifth oil port F1 of the lifting control valve, the second oil port Q1 of the lifting control valve, and the oil outlet T, realizing the combined operation of tipping bucket downward rotation - boom lifting.

[0064] Embodiment Twelve:

[0065] When the loader needs to perform the combined operation of tipping bucket downward rotation - boom lowering, the driver sends a control signal through the upper computer control unit 14 to control the operation of the first servo motor 2 and the second servo motor 5, moving the spool 4 of the tipping control valve to the downward rotation position C2 and moving the spool 7 of the lifting control valve to the floating position E3. At this time, the first oil port P0 of the tipping control valve is connected to the fourth oil port D0 of the tipping control valve, the second oil port P1 of the tipping control valve is connected to the sixth oil port D2 of the tipping control valve, the third oil port P2 of the tipping control valve is connected to the fifth oil port D1 of the tipping control valve, the first oil port Q0 of the lifting control valve is connected to the fourth oil port F0 of the lifting control valve, the second oil port Q1 of the lifting control valve is connected to the sixth oil port F2 of the lifting control valve, and the third oil port Q2 of the lifting control valve is connected to the fifth oil port F1 of the lifting control valve. The pressure oil flow path is as Figure 12As shown by the thick solid line, the pressure oil is divided into two pressure oil circuits after passing through the oil inlet P. One circuit enters the small chamber of the bucket cylinder 12 through the third oil port P2 of the bucket control valve, the fifth oil port D1 of the bucket control valve, and the second working oil port B1 of the bucket cylinder, pushing the piston rod of the bucket cylinder 12 to retract and causing the bucket to rotate downward. The oil in the large chamber of the bucket cylinder 12 returns to the fuel tank through the first working oil port A1 of the bucket cylinder, the sixth oil port D2 of the bucket control valve, the second oil port P1 of the bucket control valve, and the oil outlet T. The other circuit returns to the fuel tank through the first oil port P0 of the bucket control valve, the fourth oil port D0 of the bucket control valve, the first oil port Q0 of the lift control valve, the fourth oil port F0 of the lift control valve, and the oil outlet T. At the same time, since the fifth oil port F1 and the sixth oil port F2 of the lift control valve are respectively connected to the fuel tank through the third oil port Q2 and the second oil port Q1 of the lift control valve, the large chamber and the small chamber of the lift cylinder 13 are also connected to the fuel tank. The pressures in the large chamber and the small chamber of the lift cylinder 13 are balanced and in a low-pressure state, and the boom descends under its own weight, realizing the combined operation of the bucket rotating downward and the boom descending.

[0066] Although the embodiments of the present invention have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, substitutions, and variations can be made to these embodiments without departing from the principles and spirit of the present invention. The scope of the present invention is defined by the appended claims and their equivalents.

Claims

1. An electronically controlled multi-way directional control valve, comprising a valve body (1), characterized in that: A swing valve and a lift valve are arranged in the valve body (1). The swing valve includes a swing valve orifice (101) and a swing valve spool (4). The swing valve spool (4) is slidably arranged in the swing valve orifice (101). One end of the swing valve spool (4) is in transmission connection with a first servo motor (2) through a first motor rotation-mechanical linear motion converter (3). The lift valve includes a lift valve orifice (102) and a lift valve spool (7). The lift valve spool (7) is slidably arranged in the lift valve orifice (102). One end of the lift valve spool (7) is in transmission connection with a second servo motor (5) through a second motor rotation-mechanical linear motion converter (6). The first servo motor (2) and the second servo motor (5) are respectively electrically connected with a host computer control unit (14). The valve body (1) is provided with a plurality of oil ports. When the swing valve spool (4) and the lift valve spool (7) act, different working hydraulic circuits can be formed by closing or communicating the oil ports; The surface of the valve body (1) is provided with an oil inlet P, an oil outlet T, a first working oil port A1 of the tipping cylinder, a second working oil port B1 of the tipping cylinder, a first working oil port A2 of the lifting cylinder, and a second working oil port B2 of the lifting cylinder. Inside the valve body (1), there are a tipping reversing valve hole (101) and a lifting reversing valve hole (102). Inside the valve body (1), there are tipping reversing valve ports respectively communicating with the tipping reversing valve hole (101). The tipping reversing valve ports include a first oil port P0 of the tipping reversing valve, a second oil port P1 of the tipping reversing valve, a third oil port P2 of the tipping reversing valve, a fourth oil port D0 of the tipping reversing valve, a fifth oil port D1 of the tipping reversing valve, and a sixth oil port D2 of the tipping reversing valve. When the tipping reversing valve spool (4) is in different positions, it can block or connect the corresponding tipping reversing valve ports. Inside the valve body (1), there are lifting reversing valve ports respectively communicating with the lifting reversing valve hole (102). The lifting reversing valve ports include a first oil port Q0 of the lifting reversing valve, a second oil port Q1 of the lifting reversing valve, a third oil port Q2 of the lifting reversing valve, a fourth oil port F0 of the lifting reversing valve, a fifth oil port F1 of the lifting reversing valve, and a sixth oil port F2 of the lifting reversing valve. When the lifting reversing valve spool (7) is in different positions, it can block or connect the corresponding lifting reversing valve ports. The first oil port P0 of the tipping reversing valve and the third oil port P2 of the tipping reversing valve are connected to the oil inlet P through internal channels. The second oil port P1 of the tipping reversing valve, the second oil port Q1 of the lifting reversing valve, and the fourth oil port F0 of the lifting reversing valve are respectively connected to the oil outlet T through internal channels. The fifth oil port D1 of the tipping reversing valve is connected to the second working oil port B1 of the tipping cylinder through an internal channel. The sixth oil port D2 of the tipping reversing valve is connected to the first working oil port A1 of the tipping cylinder through an internal channel. The first oil port Q0 of the lifting reversing valve and the third oil port Q2 of the lifting reversing valve are connected to the fourth oil port D0 of the tipping reversing valve through internal channels. The fifth oil port F1 of the lifting reversing valve is connected to the second working oil port B2 of the lifting cylinder through an internal channel. The sixth oil port F2 of the lifting reversing valve is connected to the first working oil port A2 of the lifting cylinder through an internal channel.

2. The electro-control multi-way change-over valve according to claim 1, characterized in that: One end of the first motor rotation-mechanical linear motion converter (3) is fixedly connected to the output shaft of the first servo motor (2), and the other end is hinged to the tipping reversing valve spool (4), which is used to convert the rotational motion of the first servo motor (2) into a linear reciprocating motion of the tipping reversing valve spool (4) in the tipping reversing valve hole (101).

3. An electro-controlled multi-way directional control valve according to claim 1, characterized in that: One end of the second motor rotation-mechanical linear motion converter (6) is fixedly connected to the output shaft of the second servo motor (5), and the other end is hinged to the lifting reversing valve spool (7), which is used to convert the rotational motion of the second servo motor (5) into a linear reciprocating motion of the lifting reversing valve spool (7) in the lifting reversing valve hole (102).

4. An electro-control multi-way directional valve according to claim 1, characterized in that: The lifting reversing valve is a five-position six-way reversing valve, and is provided with a lifting neutral position EO, a cut-off position E1, a lifting position E2, a floating position E3, and a lowering position E4.

5. An electro-control multi-way directional valve according to claim 1, characterized in that: The tipping reversing valve is a three-position six-way reversing valve, which is provided with a tipping neutral position CO, an upper tipping position C1 and a lower tipping position C2.

6. The electro-control multi-way change-over valve according to claim 1, characterized in that: A safety valve (9) is arranged in the valve body (1), and both ends of the safety valve (9) are communicated with the oil inlet P and the oil outlet T respectively through internal channels.

7. An electro-controlled multi-way directional control valve according to claim 1, characterized in that: A one-way oil replenishing valve (8) is arranged in the valve body (1), the inlet of the one-way oil replenishing valve (8) is communicated with the oil outlet T through an internal channel, and the outlet of the one-way oil replenishing valve (8) is communicated with the second working oil port B2 of the lifting cylinder through an internal channel.

8. An electro-controlled multi-way directional control valve according to claim 1, characterized in that: A first overload oil replenishing valve (10) and a second overload oil replenishing valve (11) are arranged in the valve body (1), both ends of the first overload oil replenishing valve (10) are communicated with the second working oil port B1 of the tipping cylinder and the oil outlet T respectively through internal channels, and both ends of the second overload oil replenishing valve (11) are communicated with the first working oil port A1 of the tipping cylinder and the oil outlet T respectively through internal channels.

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