Mining multifunctional valve group and control method thereof

Abstract

The invention provides a mining multifunctional valve group and a control method thereof, the mining multifunctional valve group is connected among a hydraulic rotary motor, a pair of execution cylinders and a pair of synchronous oil cylinders, and the mining multifunctional valve group comprises a valve body, a first pressure reducing valve, three two-position three-way electromagnetic directional valves, a pair of two-position four-way proportional valves and a synchronous flow distributing and collecting valve; the two two-position four-way proportional valves are respectively provided with a pair of pressure compensation valves, a pair of pressure limiting valves and a shuttle valve; the pressure compensation valve is used for adjusting the working oil pressure, the pressure limiting valve is used for carrying out secondary pressure setting on the pressure required by each executing mechanism and simultaneously meeting the requirement for instant high-pressure discharging, and the shuttle valve is used for enabling each two-position four-way proportional valve to output pressure outwards after a fixed pressure difference is added on the corresponding highest pressure. The mining multifunctional valve group can prevent the shaking phenomenon caused by pressure fluctuation of an oil source, improve the control precision of each executive component in a bottom cleaning device, avoid impact damage to a control valve due to action change of the executive component or encountering an external load, and avoid accidental rotation of a rotation mechanism.

Description

Technical Field

[0001] This invention relates to the field of mining machinery technology, and more specifically, to a multi-functional valve group for mining and its control method. Background Technology

[0002] With the rapid development of integrated and intelligent tunneling in coal mines, the number of supporting equipment is gradually increasing. Most of this equipment requires rotation and simultaneous compound actions by multiple actuators, and these compound actions must meet requirements for precise control and rapid response. For example, the bottom-cleaning device for cleaning coal at the bottom of the transfer conveyor needs to simultaneously activate the safety brake of the milling head rotation mechanism to prevent deflection on uneven or sloping ground, reducing the risk of accidents. It also needs to switch between left and right push mechanisms to adjust the deviation from the left or right side. Simultaneously, the belt conveyor mechanisms on both sides of the bottom-cleaning device must ensure that the two hydraulic cylinders lift synchronously and remain at the same height and angle, ensuring that the terminal material drop outlets are all within the material drop area.

[0003] Existing coal mining machinery mostly uses hydraulically controlled or manually operated multi-way valves for complex operations. A multi-way directional valve controls at least two actuators. Since the actuators have different loads, and the oil pressure is configured according to the sum of these loads, fluctuations in the oil pressure distribution to each actuator can occur when the number of actuators decreases or increases. This can lead to actuator vibration due to unstable pressure supply, hindering precise control. Furthermore, if an actuator suddenly stops (e.g., reaches its end point and experiences pressure buildup or impact), the pressure at its working port may surge instantaneously, transmitting high pressure to the multi-way directional valve and causing a high-pressure shock that damages its control accuracy. Additionally, existing multi-way directional valves typically control the rotation of the slewing mechanism through a separate hydraulic branch. Rotation only requires oil supply to the slewing mechanism. When the equipment is idle or other actuators are not operating, the slewing mechanism can easily be unlocked due to triggered operations, posing a danger. Summary of the Invention

[0004] To prevent vibration caused by fluctuations in oil pressure, improve the control accuracy of each actuator in the cleaning device, avoid damage to the control valve due to changes in actuator movement or external loads, and prevent accidental unlocking and rotation of the rotary mechanism, the technical solution adopted in this invention is as follows: A mining multi-functional valve group is connected between a hydraulic rotary motor, a first actuator cylinder, a second actuator cylinder, a first synchronous cylinder, and a second synchronous cylinder. The hydraulic rotary motor is equipped with a brake pilot valve and a brake cylinder. The valve group includes a valve body and a first pressure reducing valve, a first two-position three-way solenoid directional valve, a second two-position three-way solenoid directional valve, a third two-position three-way solenoid directional valve, a first two-position four-way proportional valve, and a second two-position four-way proportional valve, which are respectively disposed inside the valve body. The inlet end of the first two-position four-way proportional valve and the inlet end of the second two-position four-way proportional valve are connected to the same working oil port of the valve body and are respectively provided with a pair of pressure compensation valves. The outlet end of the first two-position four-way proportional valve and the outlet end of the second two-position four-way proportional valve are respectively provided with a pair of pressure limiting valves. The outlet end of the first two-position four-way proportional valve is connected to the first synchronous cylinder and the second synchronous cylinder, and the outlet end of the second two-position four-way proportional valve is connected to the first actuator cylinder and the second actuator cylinder respectively through the first two-position three-way solenoid directional valve and the second two-position three-way solenoid directional valve. The pressure compensation valve is used to adjust the oil pressure provided by the working oil port, and then provide it to the first synchronous cylinder and the second synchronous cylinder through the first two-position four-way proportional valve, and to the first actuator cylinder and the second actuator cylinder through the second two-position four-way proportional valve, so as to stabilize the pressure of the first actuator cylinder, the second actuator cylinder, the first synchronous cylinder, and the second synchronous cylinder. The pressure relief valve is used to release the instantaneous high pressure generated by the first actuator, the second actuator, the first synchronizing cylinder, and the second synchronizing cylinder respectively, so as to prevent the instantaneous high pressure from being transmitted to the first two-position four-way proportional valve and the second two-position four-way proportional valve and causing damage. At the same time, it performs secondary pressure setting on the pressure required by the first actuator, the second actuator, the first synchronizing cylinder, and the second synchronizing cylinder. The pressure relief valve group is equipped with a shuttle valve group for step-by-step comparison. The output side of the shuttle valve group is connected to the first pressure reducing valve. The output side of the first pressure reducing valve is connected to the third two-position three-way solenoid directional valve. The output side of the third two-position three-way solenoid directional valve is connected to the brake pilot valve as a valve body interface, which is used to output the oil pressure of the load end in the working state for unlocking the hydraulic rotary motor.

[0005] Beneficial effects: By installing a pressure compensation valve before the valve, the oil pressure entering the first and second two-position four-way proportional valves can be kept stable, eliminating the interference of load pressure fluctuations on the flow output of the first and second two-position four-way proportional valves. This ensures that the speeds of the first and second synchronous cylinders are controlled only by the opening of the first two-position four-way proportional valve, and the speeds of the first and second actuator cylinders are controlled only by the opening of the second two-position four-way proportional valve, independent of load changes. This enables highly precise control of the displacement of the first and second synchronous cylinders, as well as the first and second actuator cylinders. By installing a pressure limiting valve after the valve, instantaneous high pressure encountered by each actuator can be promptly released, providing high-pressure impact isolation. Through the comparison function of the shuttle valve, the highest oil pressure is obtained by comparing the output oil circuits. The oil supply system adds a fixed value to the oil supply based on the highest oil pressure, avoiding the throttling losses caused by excessively high pressure settings in traditional constant pressure systems, thus achieving on-demand pressure and flow supply.

[0006] Based on the above, the first pressure reducing valve is used to reduce the pressure of the highest pressure oil in all oil circuits and divide it into two oil circuit branches. One oil circuit branch, after being depressurized by the second pressure reducing valve, serves as the replenishment oil branch for the hydraulic rotary motor. The other oil circuit branch, after passing through the third two-position three-way solenoid directional valve, splits into two pilot oil branches. One of the pilot oil branches is connected to the SH port of the brake pilot valve, and the other pilot oil branch is connected to the PG port of the brake pilot valve. The pilot oil branch connected to the SH port of the brake pilot valve is used to control the on / off state of the pilot oil branch connected to the PG port of the brake pilot valve. The brake pilot valve is connected to the brake cylinder and is used to change the state of the brake cylinder by using the pilot oil provided by the pilot oil branch connected to the SH port of the brake pilot valve, thereby releasing the braking state of the hydraulic rotary motor.

[0007] Beneficial effects: By using the shuttle valve assembly, pressure reducing valve, third two-position three-way solenoid directional valve, brake pilot valve and brake cylinder in combination, the shuttle valve assembly can only obtain oil pressure and release the braking state of the hydraulic rotary motor when each actuator is activated, thus playing a dual protection role and effectively preventing the rotary mechanism from accidentally unlocking and rotating.

[0008] Based on the above, the first synchronous cylinder and the second synchronous cylinder are connected to the first two-position four-way proportional valve through a synchronous flow divider and combiner valve. A pair of the synchronous flow divider and combiner valves are cross-connected to the first synchronous cylinder and the second synchronous cylinder. The first two-position four-way proportional valve is used to control the first synchronous cylinder and the second synchronous cylinder to perform synchronous actions respectively.

[0009] Beneficial effect: By setting up a synchronous flow divider and combiner valve and cross-setting the two synchronous flow divider and combiner valves, the control accuracy and consistency of the two synchronous cylinders can be improved.

[0010] Based on the above, the first two-position three-way solenoid directional valve and the second two-position three-way solenoid directional valve are cross-connected between the first actuator, the second actuator, and the second two-position four-way proportional valve. The first two-position three-way solenoid directional valve and the second two-position three-way solenoid directional valve are used to control the first actuator and the second actuator to perform actions alternately by switching the flow direction of the working oil.

[0011] Beneficial effects: By cross-connecting the first two-position three-way solenoid directional valve and the second two-position three-way solenoid directional valve between the first actuator cylinder, the second actuator cylinder, and the second two-position four-way proportional valve, the number of two-position three-way solenoid directional valves can be reduced, simplifying the oil circuit of the valve group.

[0012] Based on the above, the valve body is also provided with a valve group return port. The first two-position four-way proportional valve, the second two-position four-way proportional valve, the pressure limiting valve and the first pressure reducing valve are respectively connected to the valve group return port to return the working oil in the valve group to the oil tank.

[0013] Beneficial effect: By opening the valve group return port, the working oil in each valve group can be returned to the oil tank in a timely manner when not in operation, thus avoiding waste.

[0014] Based on the above, damping is provided on the oil lines connecting the pressure relief valve to the first two-position four-way proportional valve and the second two-position four-way proportional valve.

[0015] Beneficial effect: By installing damping in each oil circuit, it is possible to prevent the pressure relief oil from impacting the pressure relief valve and pressure relief pipeline.

[0016] Based on the above, the valve body is also provided with valve group A1 oil port, valve group A2 oil port, valve group B1 oil port, valve group B2 oil port, valve group A21 oil port, valve group A22 oil port, valve group B21 oil port, and valve group B22 oil port. The first two-position three-way solenoid directional valve is connected to the first actuator cylinder through the oil port A1 of the valve group, and the first two-position three-way solenoid directional valve is connected to the second actuator cylinder through the oil port A2 of the valve group; the second two-position three-way solenoid directional valve is connected to the first actuator cylinder through the oil port B1 of the valve group, and the second two-position three-way solenoid directional valve is connected to the second actuator cylinder through the oil port B2 of the valve group, so as to reduce the number of two-position three-way solenoid directional valves; One of the synchronous flow divider and combiner valves is connected to the second synchronous cylinder through the oil port A21 of the valve group and to the first synchronous cylinder through the oil port A22 of the valve group. The other synchronous flow divider and combiner valve is connected to the second synchronous cylinder through the oil port B21 of the valve group and to the first synchronous cylinder through the oil port B22 of the valve group, so as to realize synchronous control of the first synchronous cylinder and the second synchronous cylinder.

[0017] Beneficial effects: By setting the above-mentioned oil port on the valve body, it is easy to cross-connect the first actuator cylinder, the second actuator cylinder and the synchronous flow divider valve, and cross-connect the first synchronous oil cylinder and the second synchronous oil cylinder, thereby improving control efficiency.

[0018] Based on the above, the second pressure reducing valve is connected to the return port of the valve group to return the working oil in the second pressure reducing valve to the oil tank.

[0019] The beneficial effect is that by connecting the second pressure reducing valve to the return port of the valve group, the residual hydraulic oil in the second pressure reducing valve can be returned to the oil tank when not in operation, thus improving the utilization rate.

[0020] This invention also provides a control method for a multi-functional valve group used in mining, comprising the following steps: The working pressure oil in the main valve is compensated by the corresponding pressure compensation valve and then supplied to the first two-position four-way proportional valve and the second two-position four-way proportional valve respectively. The first two-position four-way proportional valve is used to supply the compensated working pressure oil to the first synchronous cylinder and the second synchronous cylinder at a specific flow rate, so as to control the first synchronous cylinder and the second synchronous cylinder to perform synchronous actions. The compensated working pressure oil is supplied to the first two-position three-way solenoid directional valve and the second two-position three-way solenoid directional valve at a specific flow rate using the second two-position three-way solenoid directional valve. The first two-position three-way solenoid directional valve and the second two-position three-way solenoid directional valve are used to control the first actuator and the second actuator to perform actions alternately. Several shuttle valve groups are used to select the highest pressure oil in all oil circuits by comparing the pressure magnitude and deliver it to the first pressure reducing valve as the pilot oil for the brake pilot valve to open the brake cylinder. The opening and closing state of the brake cylinder is controlled by the third two-position three-way solenoid directional valve and the brake pilot valve. When an impact causes instantaneous high pressure, the pressure relief valve is used to unload the instantaneous high pressure generated by the first actuator cylinder, the second actuator cylinder, the first synchronous cylinder, and the second synchronous cylinder, respectively, to prevent the instantaneous high pressure from being transmitted to the first two-position four-way proportional valve and the second two-position four-way proportional valve and causing damage. At the same time, the pressure required by the first actuator cylinder, the second actuator cylinder, the first synchronous cylinder, and the second synchronous cylinder is set in a secondary pressure setting. By utilizing the highest pressure on each load branch fed back by the shuttle valve, the first two-position four-way proportional valve and the second two-position four-way proportional valve each increase a fixed pressure difference on their respective highest pressures before outputting pressure to ensure sufficient pressure and flow.

[0021] This invention has significant substantive features and remarkable progress compared to existing technologies. Specifically, the invention provides a multi-functional valve group for mining and its control method. Firstly, a first synchronous cylinder and a second synchronous cylinder requiring synchronized operation are connected to the same first two-position four-way proportional valve via a first synchronous flow divider and a second ... The system is equipped with a third pressure compensation valve and a fourth pressure compensation valve, which ensures that the oil pressure entering the first two-position four-way proportional valve and the second two-position four-way proportional valve remains stable, respectively. This eliminates the interference of load pressure fluctuations on the flow output of the first two-position four-way proportional valve and the second two-position four-way proportional valve. As a result, the speeds of the first and second synchronous cylinders are controlled only by the opening of the first two-position four-way proportional valve, and the speeds of the first and second actuator cylinders are controlled only by the opening of the second two-position four-way proportional valve, independent of load changes. This enables highly precise control of the displacement of the first and second synchronous cylinders, the first actuator cylinder, and the second actuator cylinder.

[0022] On the other hand, by setting a first pressure limiting valve and a second pressure limiting valve at the outlet end of the first two-position four-way proportional valve, and setting a third pressure limiting valve and a fourth pressure limiting valve at the outlet end of the second two-position four-way proportional valve, the present invention can promptly release some of the high-pressure oil when the first synchronous cylinder, the second synchronous cylinder, the first actuator cylinder, or the second actuator cylinder experiences instantaneous high pressure due to sudden stop or impact. This provides a high-pressure impact isolation function, effectively protecting the first two-position four-way proportional valve and the second two-position four-way proportional valve from the impact and damage of instantaneous high pressure. This ensures that the first two-position four-way proportional valve and the second two-position four-way proportional valve have high control accuracy and can achieve secondary pressure setting for the pressure required by the first actuator cylinder, the second actuator cylinder, the first synchronous cylinder, and the second synchronous cylinder.

[0023] Meanwhile, this invention also incorporates a shuttle valve assembly, which allows the highest pressure among the load pressures to be obtained through comparison. After obtaining this highest oil pressure, the main oil supply line outputs a pressure exceeding this pressure by a fixed pressure differential. This avoids the throttling losses caused by excessively high pressure settings in traditional constant pressure systems, thereby achieving on-demand pressure and flow supply, significantly improving system efficiency and preventing energy waste. Furthermore, the shuttle valve also prevents interference between different load circuits. The isolation function of the shuttle valve ensures that each circuit only receives the required pressure, without interfering with each other.

[0024] Thirdly, the rotation function of the hydraulic rotary motor is controlled by setting up a shuttle valve assembly, a pressure reducing valve, a third two-position three-way solenoid directional valve, a brake pilot valve, and a brake cylinder. Since the hydraulic oil in the shuttle valve assembly comes from the actions of each load end, the brake of the hydraulic rotary motor can only be released when there is an action at the load end, thus effectively avoiding the situation where the hydraulic rotary motor is accidentally unlocked and rotates. At the same time, the oil pressure with the highest pressure value is used as the power source to release the brake of the hydraulic rotary motor, ensuring a stable supply of oil for unlocking and avoiding unlocking failure due to a branch not working or insufficient oil pressure.

[0025] Furthermore, by simultaneously controlling the unlocking oil circuit of the brake cylinder using the third two-position three-way solenoid directional valve and the brake pilot valve, the slewing mechanism cannot be activated even when the original unlocking action is triggered. The slewing mechanism can only be slewing after the third two-position three-way solenoid directional valve is connected before slewing. This ensures that the slewing braking function has dual protection.

[0026] Furthermore, by setting damping on the first pressure relief valve, the second pressure relief valve, the third pressure relief valve and the fourth pressure relief valve, the high pressure oil output to each pressure relief valve can be damped and its speed regulated.

[0027] Therefore, the mining multi-functional valve group provided by the present invention adopts the method of pre-valve compensation and post-valve pressure reduction, and uses the oil circuit of the shuttle valve group as the source of pilot oil and replenishment oil to release the hydraulic rotary motor brake, thereby achieving the purpose of preventing the shaking phenomenon caused by oil source pressure fluctuation, improving the control accuracy of each actuator in the bottom cleaning device, avoiding impact damage to the control valve due to changes in actuator movement or encountering external load, and preventing the rotary mechanism from rotating unexpectedly. Attached Figure Description

[0028] Figure 1 This is a schematic diagram of a mining multi-functional valve group and its control method provided in Embodiment 1 of the present invention.

[0029] Figure 2 This is a schematic diagram of a mining multi-functional valve group and its control method provided in Embodiment 2 of the present invention.

[0030] Figure 3 This is a connection diagram of the application state of the mining multi-functional valve group in Embodiment 1 of the present invention.

[0031] Figure 4 This is a connection diagram of the application state of the mining multi-functional valve group in Embodiment 2 of the present invention.

[0032] In the diagram: 1. First synchronous flow divider / combiner valve; 2. Second synchronous flow divider / combiner valve; 3. First two-position three-way solenoid directional valve; 4. Second two-position three-way solenoid directional valve; 5. Third two-position three-way solenoid directional valve; 6. First pressure reducing valve; 7. Second pressure reducing valve; 8. First two-position four-way proportional valve; 9. First damper; 10. First pressure limiting valve; 11. First shuttle valve; 12. Second pressure limiting valve; 13. Second shuttle valve; 14. First pressure compensating valve; 15. Second pressure compensating valve; 16. Third shuttle valve; 17. Second two-way proportional valve; 18. Four-way proportional valve; 19. Second damper; 20. Third damper; 21. Third pressure limiting valve; 22. Fourth pressure limiting valve; 23. Fourth shuttle valve; 24. Third pressure compensation valve; 25. Fifth shuttle valve; 26. Sixth shuttle valve; 27. Hydraulic rotary motor; 28. First actuator cylinder; 29. ​​Second actuator cylinder; 30. First synchronizing cylinder; 31. Second synchronizing cylinder; 32. Seventh shuttle valve; 33. Brake pilot valve; 34. Brake cylinder; 35. Valve body; 37. Fourth damper. Detailed Implementation

[0033] The technical solution of the present invention will be further described in detail below through specific embodiments.

[0034] Example 1 This embodiment provides a multi-functional valve assembly for mining applications, such as... Figure 1 , Figure 3 As shown, it is connected between the hydraulic rotary motor 27, the first actuator cylinder 28, the second actuator cylinder 29, the first synchronizing cylinder 30, and the second synchronizing cylinder 31. The hydraulic rotary motor 27 is equipped with a brake pilot valve 33 and a brake cylinder 34. It includes a valve body 35 and a first pressure reducing valve 6, a first two-position three-way solenoid directional valve 3, a second two-position three-way solenoid directional valve 4, a third two-position three-way solenoid directional valve 5, a first two-position four-way proportional valve 8, and a second two-position four-way proportional valve 17, which are respectively disposed inside the valve body 35.

[0035] The inlet ends of the first two-position four-way proportional valve 8 and the second two-position four-way proportional valve 17 are connected to the same working port of the valve body 35 and are each equipped with a pair of pressure compensation valves. The outlet ends of the first two-position four-way proportional valve and the second two-position four-way proportional valve are each equipped with a pair of pressure limiting valves. Specifically, based on their distribution positions, they can be divided into a first pressure compensation valve 14, a second pressure compensation valve 15, a third pressure compensation valve 23, a fourth pressure compensation valve 24, a first pressure limiting valve 10, a second pressure limiting valve 12, a third pressure limiting valve 20, and a fourth pressure limiting valve 21.

[0036] The outlet end of the first two-position four-way proportional valve 3 is connected to the first synchronous cylinder 30 and the second synchronous cylinder 31. The outlet end of the second two-position four-way proportional valve 17 is connected to the first actuator 28 and the second actuator 29 respectively through the first two-position three-way solenoid valve 3 and the second two-position three-way solenoid valve 4.

[0037] The pressure compensation valve is used to adjust the oil pressure provided by the working oil port, and then provide it to the first synchronous cylinder 30 and the second synchronous cylinder 31 through the first two-position four-way proportional valve 8, and to the first actuator cylinder 28 and the second actuator cylinder 29 through the second two-position four-way proportional valve 17, so as to stabilize the pressure of the first actuator cylinder 28, the second actuator cylinder 29, the first synchronous cylinder 30, and the second synchronous cylinder 31.

[0038] The pressure relief valve is used to release the instantaneous high pressure generated by the first actuator 28, the second actuator 29, the first synchronizing cylinder 30, and the second synchronizing cylinder 31, respectively, so as to prevent the instantaneous high pressure from being transmitted to the first two-position four-way proportional valve 8 and the second two-position four-way proportional valve 17 and causing damage. At the same time, it performs secondary pressure setting on the pressure required by the first actuator, the second actuator, the first synchronizing cylinder, and the second synchronizing cylinder.

[0039] A shuttle valve is provided between each pair of pressure limiting valves. The shuttle valve is used to obtain the highest pressure of the first synchronous cylinder 30 and the second synchronous cylinder 31 by comparing the pressure magnitudes, as well as the highest pressure of the first actuator cylinder 28 and the second actuator cylinder 29. This pressure is fed back to the load-sensitive pump of the main oil circuit through the load-sensitive circuit, so that the first two-position four-way proportional valve 8 and the second two-position four-way proportional valve 17 output pressure after adding a fixed pressure difference to the corresponding highest pressure, so as to achieve sufficient pressure and flow supply.

[0040] At the same time, the oil pressure of the shuttle valve assembly is also supplied to the unlocking circuit of the hydraulic rotary motor. Specifically, the output side of the shuttle valve assembly is connected to the first pressure reducing valve, the output side of the first pressure reducing valve is connected to the third two-position three-way solenoid directional valve, and the output side of the third two-position three-way solenoid directional valve is connected to the brake pilot valve as a valve body interface, which is used to output the load end oil pressure in the working state for unlocking the hydraulic rotary motor.

[0041] Its core purpose is to achieve the safety function of unlocking the hydraulic rotary motor. The hydraulic rotary motor can only be unlocked when at least one of the first synchronous cylinder 30, the second synchronous cylinder 31, the first actuator cylinder 28, and the second actuator cylinder 29 is working. To achieve this purpose, a shuttle valve group is set up to compare the oil circuit pressure at the actuator end. By comparison, the oil circuit pressure that is in the working state can be obtained, which is also the highest pressure, and is supplied to the unlocking end to unlock the hydraulic rotary motor.

[0042] Specifically, based on their distribution locations, the shuttle valves and shuttle valve groups are respectively designated as the first shuttle valve 11, the sixth shuttle valve 26, and the seventh shuttle valve 32.

[0043] In this embodiment, specifically, the first pressure reducing valve is used to reduce the pressure of the highest pressure oil in all oil circuits and then divide it into two oil circuit branches.

[0044] One oil circuit branch, after being depressurized by the second pressure-reducing valve 7, serves as the replenishment oil branch for the hydraulic rotary motor 27. The other oil circuit branch, after passing through the third two-position three-way solenoid directional valve 5, further divides into two pilot oil branches. One of these pilot oil branches is connected to the SH port of the brake pilot valve, and the other pilot oil branch is connected to the PG port of the brake pilot valve. The pilot oil branch connected to the SH port of the brake pilot valve is used to control the on / off state of the pilot oil branch connected to the PG port of the brake pilot valve.

[0045] The brake pilot valve 33 is connected to the brake cylinder 34 and is used to change the state of the brake cylinder 34 by using the pilot oil provided by the pilot oil branch connected to the SH port of the brake pilot valve, thereby releasing the braking state of the hydraulic rotary motor 27.

[0046] The first synchronizing cylinder 30 and the second synchronizing cylinder 32 are respectively connected to the first two-position four-way proportional valve 8 via the first synchronizing flow divider valve 1 and the second synchronizing flow divider valve 2. A pair of synchronizing flow divider valves are cross-connected to the first synchronizing cylinder 30 and the second synchronizing cylinder 32. The first two-position four-way proportional valve 8 is used to control the first synchronizing cylinder 30 and the second synchronizing cylinder 32 to perform synchronized actions.

[0047] The first two-position three-way solenoid directional valve 3 and the second two-position three-way solenoid directional valve 4 are cross-connected between the first actuator 28, the second actuator 29, and the second two-position four-way proportional valve 17. The first two-position three-way solenoid directional valve 3 and the second two-position three-way solenoid directional valve 4 are used to control the first actuator 28 and the second actuator 29 to alternately perform actions by switching the flow direction of the working oil.

[0048] Example 2 like Figure 2 and Figure 4 As shown, the shuttle valve group includes a first shuttle valve 11, a second shuttle valve 13, a third shuttle valve 16, a fourth shuttle valve 22, a fifth shuttle valve 25, a sixth shuttle valve 26, and a seventh shuttle valve 32.

[0049] In this embodiment, a pressure comparison for the pressure compensation valve is introduced. The pressure compensation valve is set before the two two-position four-way proportional valves. The pressure compensation valve essentially controls the pressure before the valve by consuming hydraulic oil. Therefore, its pressure before the valve is relatively higher and more sufficient. Thus, by introducing these shuttle valves, the highest oil pressure of the entire oil circuit can be obtained, and the control of the oil pressure in the oil circuit is more sufficient. However, under this condition, the output side of the shuttle valve group is connected to the unlocking circuit of the hydraulic rotary motor. It can be used when the actuator and the hydraulic rotary motor do not need to work together.

[0050] Of course, when it is still necessary for the actuator and the hydraulic rotary motor to work together, the shuttle valve group can be divided into groups to achieve the linkage effect as shown in Example 1.

[0051] Example 3 This embodiment provides a multi-functional valve group for mining. The main difference from Embodiment 1 is that in this embodiment, the valve body is further provided with valve group A1 oil port, valve group A2 oil port, valve group B1 oil port, valve group B2 oil port, valve group A21 oil port, valve group A22 oil port, valve group B21 oil port, and valve group B22 oil port.

[0052] The first two-position three-way solenoid directional valve 3 is connected to the first actuator 28 via the oil port of valve group A1. The first two-position three-way solenoid directional valve 3 is connected to the second actuator 29 via the oil port of valve group A2.

[0053] The second two-position three-way solenoid directional valve 4 is connected to the first actuator 28 via the oil port B1 of the valve group. The second two-position three-way solenoid directional valve 4 is connected to the second actuator 29 via the oil port B2 of the valve group, thereby reducing the number of two-position three-way solenoid directional valves.

[0054] The first synchronous flow divider valve 1 is connected to the second synchronous cylinder 31 through the oil port of valve group A21, and is connected to the first synchronous cylinder 30 through the oil port of valve group A22.

[0055] The second synchronous flow divider / combiner valve 2 is connected to the second synchronous cylinder 31 through the oil port of valve group B21 and to the first synchronous cylinder 30 through the oil port of valve group B22, so as to realize synchronous control of the first synchronous cylinder 30 and the second synchronous cylinder 31.

[0056] Example 4 This embodiment provides a multi-functional valve group for mining. The main difference from Embodiment 1 is that, in this embodiment, the valve body 35 is further provided with a valve group return port, shown as a T-port in the figure. The first two-position four-way proportional valve 8, the second two-position four-way proportional valve 17, the pressure limiting valve, and the first pressure reducing valve 6 are respectively connected to the valve group T-port for returning the working oil in the valve group to the oil tank. The second pressure reducing valve 7 is connected to the valve group T-port for returning the working oil in the second pressure reducing valve 7 to the oil tank.

[0057] Example 5 This embodiment provides a multi-functional valve group for mining. The main difference from Embodiment 1 is that, in this embodiment, dampers are respectively provided on the oil lines connecting each pressure relief valve to the first two-position four-way proportional valve 8 and the second two-position four-way proportional valve 17. The dampers are used to dampen and regulate the speed of the high-pressure oil discharged from each pressure relief valve, so as to reduce the impact on the first two-position four-way proportional valve 8 and the second two-position four-way proportional valve 17. According to the distribution position, the dampers can be divided into a first damper 9, a second damper 18, a third damper 19, and a fourth damper 37.

[0058] Example 6 This embodiment also provides a control method for a mining multi-functional valve group, the specific steps of which include: after the working pressure oil in the main valve is compensated by the corresponding pressure compensation valve, it is supplied to the first two-position four-way proportional valve 8 and the second two-position four-way proportional valve 17 respectively.

[0059] The first two-position four-way proportional valve 8 is used to supply the compensated working pressure oil to the first synchronous cylinder 30 and the second synchronous cylinder 31 at a specific pressure and flow rate, so as to control the first synchronous cylinder 30 and the second synchronous cylinder 31 to perform synchronous actions.

[0060] The compensated working pressure oil is supplied to the first two-position three-way solenoid directional valve 3 and the second two-position three-way solenoid directional valve 4 at a specific pressure and flow rate using the second two-position three-way solenoid directional valve 17. The first two-position three-way solenoid directional valve 3 and the second two-position three-way solenoid directional valve 4 are used to control the first actuator 28 and the second actuator 29 to perform actions alternately.

[0061] Several shuttle valve groups are used to select the highest pressure oil in all oil circuits by comparing the pressure magnitude and deliver it to the first pressure reducing valve 6. This serves as the pilot oil for the brake pilot valve 33 to open the brake cylinder 34. The opening and closing state of the brake cylinder 34 is controlled by the third two-position three-way solenoid directional valve 5 and the brake pilot valve 33.

[0062] When an impact causes instantaneous high pressure, the pressure relief valves are used to release the instantaneous high pressure generated by the first actuator 28, the second actuator 29, the first synchronizing cylinder 30, and the second synchronizing cylinder 31, respectively, preventing the instantaneous high pressure from being transmitted to the first two-position four-way proportional valve 8 and the second two-position four-way proportional valve 17 and causing damage. At the same time, the pressure required by the first actuator, the second actuator, the first synchronizing cylinder, and the second synchronizing cylinder is set for secondary pressure.

[0063] The highest pressure on each load branch is fed back by the shuttle valve, so that the first two-position four-way proportional valve 8 and the second two-position four-way proportional valve 17 are respectively increased by a fixed pressure difference on the corresponding highest pressure and then output pressure to the outside to ensure sufficient pressure and flow.

[0064] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and not to limit them; although the present invention has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications can still be made to the specific implementation of the present invention or equivalent substitutions can be made to some technical features without departing from the spirit of the technical solutions of the present invention, and all such modifications and substitutions should be covered within the scope of the technical solutions claimed in the present invention.

Claims

1. A multi-functional valve group for mining, connected between a hydraulic rotary motor, a first actuator cylinder, a second actuator cylinder, a first synchronizing cylinder, and a second synchronizing cylinder, wherein the hydraulic rotary motor is equipped with a brake pilot valve and a brake cylinder, characterized in that: It includes a valve body and a first pressure reducing valve, a first two-position three-way solenoid directional valve, a second two-position three-way solenoid directional valve, a third two-position three-way solenoid directional valve, a first two-position four-way proportional valve, and a second two-position four-way proportional valve, which are respectively disposed inside the valve body. The inlet end of the first two-position four-way proportional valve and the inlet end of the second two-position four-way proportional valve are connected to the same working oil port of the valve body and are respectively provided with a pair of pressure compensation valves. The outlet end of the first two-position four-way proportional valve and the outlet end of the second two-position four-way proportional valve are respectively provided with a pair of pressure limiting valves. The outlet end of the first two-position four-way proportional valve is connected to the first synchronous cylinder and the second synchronous cylinder, and the outlet end of the second two-position four-way proportional valve is connected to the first actuator cylinder and the second actuator cylinder respectively through the first two-position three-way solenoid directional valve and the second two-position three-way solenoid directional valve. The pressure compensation valve is used to adjust the oil pressure provided by the working oil port, and then provide it to the first synchronous cylinder and the second synchronous cylinder through the first two-position four-way proportional valve, and to the first actuator cylinder and the second actuator cylinder through the second two-position four-way proportional valve, so as to stabilize the pressure of the first actuator cylinder, the second actuator cylinder, the first synchronous cylinder, and the second synchronous cylinder. The pressure relief valve is used to release the instantaneous high pressure generated by the first actuator, the second actuator, the first synchronizing cylinder, and the second synchronizing cylinder respectively, so as to prevent the instantaneous high pressure from being transmitted to the first two-position four-way proportional valve and the second two-position four-way proportional valve and causing damage. At the same time, it performs secondary pressure setting on the pressure required by the first actuator, the second actuator, the first synchronizing cylinder, and the second synchronizing cylinder. The pressure relief valve group is equipped with a shuttle valve group for step-by-step comparison. The output side of the shuttle valve group is connected to the first pressure reducing valve. The output side of the first pressure reducing valve is connected to the third two-position three-way solenoid directional valve. The output side of the third two-position three-way solenoid directional valve is connected to the brake pilot valve as a valve body interface, which is used to output the oil pressure of the load end in the working state for unlocking the hydraulic rotary motor.

2. The multi-functional valve assembly for mining as described in claim 1, characterized in that: The first pressure reducing valve is used to reduce the pressure of the highest pressure oil in all oil circuits and then divide it into two oil circuit branches; One oil circuit branch, after being depressurized by the second pressure reducing valve, serves as the replenishment oil branch for the hydraulic rotary motor. The other oil circuit branch, after passing through the third two-position three-way solenoid directional valve, splits into two pilot oil branches. One of the pilot oil branches is connected to the SH port of the brake pilot valve, and the other pilot oil branch is connected to the PG port of the brake pilot valve. The pilot oil branch connected to the SH port of the brake pilot valve is used to control the on / off state of the pilot oil branch connected to the PG port of the brake pilot valve. The brake pilot valve is connected to the brake cylinder and is used to change the state of the brake cylinder by using the pilot oil provided by the pilot oil branch connected to the SH port of the brake pilot valve, thereby releasing the braking state of the hydraulic rotary motor.

3. The multi-functional valve assembly for mining as described in claim 1, characterized in that: The first synchronous cylinder and the second synchronous cylinder are respectively connected to the first two-position four-way proportional valve through a synchronous flow divider and combiner valve. A pair of the synchronous flow divider and combiner valves are cross-connected to the first synchronous cylinder and the second synchronous cylinder. The first two-position four-way proportional valve is used to control the first synchronous cylinder and the second synchronous cylinder to perform synchronous actions.

4. The mining multi-functional valve assembly according to claim 1, 2, or 3, characterized in that: The first two-position three-way solenoid directional valve and the second two-position three-way solenoid directional valve are cross-connected between the first actuator cylinder, the second actuator cylinder and the second two-position four-way proportional valve. The first two-position three-way solenoid directional valve and the second two-position three-way solenoid directional valve are used to control the first actuator cylinder and the second actuator cylinder to perform actions alternately by switching the flow direction of the working oil.

5. The mining multi-functional valve assembly according to claim 2 or 3, characterized in that: The valve body is also provided with a valve group return port. The first two-position four-way proportional valve, the second two-position four-way proportional valve, the pressure limiting valve and the first pressure reducing valve are respectively connected to the valve group return port to return the working oil in the valve group to the oil tank.

6. The multi-functional valve assembly for mining as described in claim 1, characterized in that: Damping is provided on the oil lines connecting the pressure relief valve to the first two-position four-way proportional valve and the second two-position four-way proportional valve. The damping is used to dampen and regulate the speed of the high-pressure oil output to each pressure relief valve.

7. The multi-functional valve assembly for mining according to claim 3, characterized in that: The valve body is also provided with valve group A1 oil port, valve group A2 oil port, valve group B1 oil port, valve group B2 oil port, valve group A21 oil port, valve group A22 oil port, valve group B21 oil port, and valve group B22 oil port. The first two-position three-way solenoid directional valve is connected to the first actuator cylinder through the oil port A1 of the valve group, and the first two-position three-way solenoid directional valve is connected to the second actuator cylinder through the oil port A2 of the valve group; the second two-position three-way solenoid directional valve is connected to the first actuator cylinder through the oil port B1 of the valve group, and the second two-position three-way solenoid directional valve is connected to the second actuator cylinder through the oil port B2 of the valve group. One of the synchronous flow divider and combiner valves is connected to the second synchronous cylinder through the oil port A21 of the valve group and to the first synchronous cylinder through the oil port A22 of the valve group. The other synchronous flow divider and combiner valve is connected to the second synchronous cylinder through the oil port B21 of the valve group and to the first synchronous cylinder through the oil port B22 of the valve group, so as to realize synchronous control of the first synchronous cylinder and the second synchronous cylinder.

8. The multi-functional valve assembly for mining according to claim 5, characterized in that: The second pressure reducing valve is connected to the return port of the valve group T, and is used to return the working oil in the second pressure reducing valve to the oil tank.

9. A control method for a mining multi-functional valve group according to any one of claims 1 to 8, comprising the steps of: The working pressure oil in the main valve is compensated by the corresponding pressure compensation valve and then supplied to the first two-position four-way proportional valve and the second two-position four-way proportional valve respectively. The first two-position four-way proportional valve is used to supply the compensated working pressure oil to the first synchronous cylinder and the second synchronous cylinder at a specific pressure and flow rate, so as to control the first synchronous cylinder and the second synchronous cylinder to perform synchronous actions. The compensated working pressure oil is supplied to the first two-position three-way solenoid directional valve and the second two-position three-way solenoid directional valve according to a specific pressure and flow rate using the second two-position three-way solenoid directional valve and the second two-position three-way solenoid directional valve. The first two-position three-way solenoid directional valve and the second two-position three-way solenoid directional valve are used to control the first actuator and the second actuator to perform actions alternately. The shuttle valve assembly is used to select the highest pressure oil in all oil circuits by comparing the pressure magnitude and deliver it to the first pressure reducing valve as the pilot oil for the brake pilot valve to open the brake cylinder. The opening and closing state of the brake cylinder is controlled by the third two-position three-way solenoid directional valve and the brake pilot valve. When an impact occurs and instantaneous high pressure is generated, the pressure relief valves are used to release the instantaneous high pressure generated by the first actuator cylinder, the second actuator cylinder, the first synchronizing cylinder, and the second synchronizing cylinder, respectively, to prevent the instantaneous high pressure from being transmitted to the first two-position four-way proportional valve and the second two-position four-way proportional valve and causing damage. By utilizing the highest pressure on each load branch fed back by the shuttle valve assembly, the first two-position four-way proportional valve and the second two-position four-way proportional valve each increase a fixed pressure difference on their respective highest pressures before outputting pressure to ensure sufficient pressure and flow.

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