A hydraulic loading control system for anchor digging machine

Abstract

The present application discloses a hydraulic loading control system for anchor excavators, including: a hydraulic plunger pump; an electro-hydraulic proportional multi-way reversing valve group, connected between the hydraulic plunger pump and the oil replenishment control valve group; at least one oil replenishment control valve group, connected between the electro-hydraulic proportional multi-way reversing valve group and the loading plunger motor, provided with a working oil circuit pressure signal extraction port; at least one loading plunger motor, connected to the oil replenishment control valve group through a pipeline, provided with a motor variable port for displacement control by a pilot control oil; a loading motor control valve group, connected to the motor variable port of the loading plunger motor, the working oil circuit signal extraction port of the oil replenishment control valve group, and the output oil pressure regulating port of the electro-hydraulic proportional multi-way reversing valve group through a pipeline. The present application can automatically switch between light-load high-speed and heavy-load low-speed working modes according to the load demand of the loading system and the working pressure of the loading device, without manual participation, and has a high degree of intelligence.

Description

Technical Field

[0001] The present application relates to the technical field of engineering machinery and equipment, and in particular, to a hydraulic loading control system for an anchor drill. Background Art

[0002] The existing construction process of anchor diggers includes three parts: excavation, anchor protection, and transportation. The excavation efficiency of the whole machine can be guaranteed only when the three parts match each other. The loading device in the transportation part of the anchor digger adopts a double star wheel moving in opposite directions to transfer the materials to the primary transportation system. The working efficiency of the loading device is also a key factor in the construction efficiency of the anchor digger.

[0003] At present, the driving modes of anchor mining machine loading devices are divided into motor-driven reducer type and low-speed high-torque motor-driven type. When the motor-driven reducer type faces the situation where there is a lot of water in the working area of ​​the coal mine tunnel, the motor is immersed in water for a long time due to the low installation height of the motor, which is easy to cause water ingress failure of the motor; at the same time, the motor is in overload operation for a long time due to the large driving force required for loading, and the motor is prone to overcurrent damage. On the one hand, the low-speed and high-torque hydraulic motor drive mode has a high cost. Under frequent impact conditions, the low-speed and high-torque motor cannot meet the service life; on the other hand, it cannot realize the switching between the two working modes of light load high speed and heavy load low speed, and can only meet the heavy load and low speed conditions. Even under light load conditions, the low-speed and high-torque motor still requires a large flow, resulting in excessively high cost of hydraulic system configuration. Summary of the invention

[0004] The embodiment of the present application provides a hydraulic loading control system for an anchor digger to solve the technical problems that the existing driving method of the anchor digger loading device is high in cost and cannot switch between the two working modes of light load high speed and heavy load low speed to meet the needs of different working conditions.

[0005] The technical solutions adopted in this application are as follows:

[0006] A hydraulic loading control system for an anchor miner, comprising:

[0007] The hydraulic piston pump, as the power source of the hydraulic system, provides hydraulic oil for the hydraulic system of the anchor miner;

[0008] The electro-hydraulic proportional multi-way reversing valve group is connected between the hydraulic piston pump and the oil replenishing control valve group to realize the oil reversing function, change the action direction of the actuator, and provide pilot control oil to the loading motor control valve group;

[0009] At least one oil replenishment control valve group is connected and arranged between the electro-hydraulic proportional multi-way reversing valve group and the loading plunger motor, and is provided with a working oil circuit pressure signal extraction port, which is used to extract the working oil circuit signal of the loading plunger motor as the control signal source of the loading motor control valve group, and at the same time, the external replenishment oil is timely replenished to the hydraulic system through this valve body;

[0010] At least one loading plunger motor is connected to the oil replenishment control valve group through a pipeline, and is provided with a motor variable port for controlling the displacement by the pilot control oil. When the pilot control oil enters the motor variable port, the motor swing angle is swung from the maximum displacement to the minimum set displacement;

[0011] The loading motor control valve group is connected to the motor variable port of the loading plunger motor, the working oil circuit signal extraction port of the oil replenishment control valve group and the output oil pressure regulating port of the electro-hydraulic proportional multi-way reversing valve group 2 through pipelines, and is used to output pilot control oil to the motor variable port of the loading plunger motor according to the real-time working pressure of the loading plunger motor, control the loading plunger motor to switch between the maximum displacement and the minimum displacement, and realize the mode switching between light load high speed and heavy load low speed.

[0012] Furthermore, the loading motor control valve group includes a first one-way sequence valve, a second one-way sequence valve, a first two-position four-way hydraulically controlled reversing valve, a second two-position four-way hydraulically controlled reversing valve, and a second shuttle valve, and is used to select the highest working pressure as the highest pressure extraction device of the signal, wherein:

[0013] The input ends of the first one-way sequence valve and the second one-way sequence valve are connected to the working oil circuit pressure signal extraction port of the oil replenishment control valve group through the maximum pressure extraction device, and the opening pressure of the first one-way sequence valve is greater than the opening pressure of the second one-way sequence valve, the output point of the second one-way sequence valve is connected to the P port of the first two-position four-way hydraulic control reversing valve, the P1 port of the second shuttle valve is connected to the output end of the first one-way sequence valve, and the P2 port of the second shuttle valve is respectively connected to the B port of the first two-position four-way hydraulic control reversing valve and the B port of the second two-position four-way hydraulic control reversing valve. The left pilot port of the four-way hydraulically controlled reversing valve is connected, the A port of the second shuttle valve is respectively connected to the left pilot port and the oil drain circuit of the first two-position four-way hydraulically controlled reversing valve, the P port of the second two-position four-way hydraulically controlled reversing valve receives the pilot control oil from the electro-hydraulic proportional multi-way directional valve group, the A port of the second two-position four-way hydraulically controlled reversing valve is connected to the motor variable port of the loading plunger motor through a pipeline, and the T port of the second two-position four-way hydraulically controlled reversing valve, the T port of the first two-position four-way hydraulically controlled reversing valve and the T port of the second two-position four-way hydraulically controlled reversing valve are all connected to the pressure relief circuit.

[0014] Furthermore, the loading motor control valve group also includes a two-position two-way hydraulically controlled reversing valve and a relief valve, wherein:

[0015] The input of the two-position, two-way hydraulically controlled reversing valve is connected to the Ls port of the electro-hydraulic proportional multi-way directional reversing valve group, and the output end is connected to the input point of the overflow valve. The pilot control port of the two-position, two-way hydraulically controlled reversing valve is connected to the B port of the second two-position, four-way hydraulically controlled reversing valve, and the output end of the overflow valve is connected to the oil drain circuit.

[0016] Furthermore, a first damper is provided at the output end of the maximum pressure extraction device.

[0017] Furthermore, a second damper is provided on the pipeline between the output end of the first one-way sequence valve and the P1 port of the second shuttle valve.

[0018] Furthermore, a third damper is provided on the pipeline between the port A of the second shuttle valve and the pressure relief circuit.

[0019] Furthermore, the maximum pressure extraction device includes a first shuttle valve, the P1 port and the P2 port of the first shuttle valve are respectively connected to the working oil circuit pressure signal extraction port of the corresponding oil replenishment control valve group, and the A port of the first shuttle valve is connected to the input end of the first one-way sequence valve and the second one-way sequence valve.

[0020] Furthermore, the loading motor control valve group includes a maximum pressure extraction device for selecting the maximum working pressure as a signal, a two-position four-way solenoid valve, and a pressure sensor. The input end of the pressure sensor is connected to the working oil circuit pressure signal extraction port of the oil replenishment control valve group through the maximum pressure extraction device, and the electrical signal output end of the pressure sensor is connected to the solenoid valve signal of the two-position four-way solenoid valve. The P port of the two-position four-way solenoid valve receives the pilot control oil from the electro-hydraulic proportional multi-way reversing valve group. The B port of the two-position four-way solenoid valve is connected to the motor variable port of the loading plunger motor through a pipeline, and the T port of the two-position four-way solenoid valve is connected to the pressure relief circuit.

[0021] Furthermore, the maximum pressure extraction device includes a first shuttle valve, the P1 port and the P2 port of the first shuttle valve are respectively connected to the working oil circuit pressure signal extraction port of the corresponding oil replenishment control valve group, and the A port of the first shuttle valve is connected to the input end of the pressure sensor.

[0022] Furthermore, a maximum working oil circuit pressure signal extraction device is provided in the oil replenishment control valve group, and the maximum working oil circuit pressure signal extraction device includes a third shuttle valve, and the P1 port and P2 port of the third shuttle valve are respectively connected to the two hydraulic oil circuits in the oil replenishment control valve group, and the A port of the third shuttle valve is connected to the input end of the maximum pressure extraction device in the loading motor control valve group as a working oil circuit pressure signal extraction port.

[0023] Compared with the prior art, this application has the following beneficial effects:

[0024] The present application provides a hydraulic loading control system for an anchor mining machine, comprising a hydraulic plunger pump, an electro-hydraulic proportional multi-way reversing valve group, at least one oil replenishment control valve group, and at least one loading plunger motor. The electro-hydraulic proportional multi-way reversing valve group is connected between the hydraulic plunger pump and the oil replenishment control valve group to realize an oil reversing function, change the action direction of an actuator, and provide pilot control oil to the loading motor control valve group; the oil replenishment control valve group is connected and arranged between the electro-hydraulic proportional multi-way reversing valve group and the loading plunger motor, and is provided with a working oil circuit pressure signal extraction port, which is used to extract the working oil circuit signal of the loading plunger motor as a control signal source of the loading motor control valve group, and at the same time replenish the external oil through this valve body in time The hydraulic system is filled with oil. The loading piston motor is connected with the oil replenishment control valve group through a pipeline, and is provided with a motor variable port for controlling the displacement by the pilot control oil. When the pilot control oil enters the motor variable port, the motor swing angle is swung from the maximum displacement to the minimum set displacement. The loading motor control valve group is respectively connected with the motor variable port of the loading piston motor, the working oil circuit signal extraction port of the oil replenishment control valve group and the output oil pressure regulating port of the electro-hydraulic proportional multi-way reversing valve group through a pipeline, and is used to output the pilot control oil to the motor variable port of the loading piston motor according to the real-time working pressure of the loading piston motor, so as to control the loading piston motor to switch between the maximum displacement and the minimum displacement, so as to realize the mode switching between light load high speed and heavy load low speed. According to the actual demand of the anchor mining machine loading device, the present application proposes a hydraulic driving loading control system for the anchor mining machine in view of the shortcomings of the current motor-driven reducer and the low-speed and high-torque motor drive. The system uses a piston motor with adjustable displacement as the power, and can adjust the displacement of the loading piston motor according to the real-time working pressure of the loading piston motor, control the loading piston motor to switch between the maximum displacement and the minimum displacement, and realize the mode switching of light load high speed and heavy load low speed. Therefore, compared with the existing driving mode, it mainly includes the following technical advantages: First, the axial piston high-speed driving reducer loading form can effectively cope with the ground water condition and ensure the normal operation of the system; second, the control system adopts the general hydraulic components of engineering machinery, so the cost is relatively low; third, the control system adds a control valve group, which can automatically realize the light load high speed and heavy load low speed working mode switching according to the load demand of the loading system and the working pressure of the loading device, without manual participation, and has a high degree of intelligence; fourth, the control system adds an oil replenishment valve group to avoid abnormal damage to the hydraulic drive device, effectively cope with the frequent impact conditions of the loading device, greatly improve the protection of the loading motor, and prevent the motor from being damaged by air suction. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] The drawings constituting a part of the present application are used to provide a further understanding of the present application. The illustrative embodiments and descriptions of the present application are used to explain the present application and do not constitute an improper limitation on the present application. In the drawings:

[0026] Figure 1It is a schematic diagram of the principle of the hydraulic loading control system of the anchor digger according to the preferred embodiment of the present application.

[0027] Figure 2 It is a schematic diagram of the principle of the excavator loading motor control valve group of the preferred embodiment of the present application.

[0028] Figure 3 It is a schematic diagram of the principle of a hydraulic loading control system for an anchor digger according to another preferred embodiment of the present application.

[0029] Figure 4 It is a schematic diagram of the principle of a control valve group for a loader motor according to another preferred embodiment of the present application.

[0030] In the figure:

[0031] 1. Hydraulic piston pump; 2. Electro-hydraulic proportional multi-way reversing valve group; 3. Loading motor control valve group; 3.1. First shuttle valve; 3.2. First damper; 3.3. Second damper; 3.3.1. First one-way sequence valve; 3.3.2. Second one-way sequence valve; 3.4. Second shuttle valve; 3.5.1. First two-position four-way hydraulically controlled reversing valve; 3.5.2. Second two-position four-way hydraulically controlled reversing valve; 3.6. Third damper; 3.7. Two-position two-way hydraulically controlled reversing valve; 3.8. Overflow valve; 3.9. Two-position four-way solenoid valve; 3.10. Pressure sensor; 3.11. Third shuttle valve; 4.1. First oil replenishment control valve group; 4.2. Second oil replenishment control valve group; 5.1. First loading piston motor; 5.2. Second loading piston motor. DETAILED DESCRIPTION

[0032] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present application can be combined with each other. The present application will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0033] Reference Figure 1 and Figure 2 The preferred embodiment of the present application provides a hydraulic loading control system for an anchor miner, comprising a hydraulic piston pump 1, an electro-hydraulic proportional multi-way reversing valve group 2, a first oil replenishment control valve group 4.1, a second oil replenishment control valve group 4.2, a first loading piston motor 5.1, a second loading piston motor 5.2, and a loading motor control valve group 3, wherein:

[0034] The hydraulic piston pump 1 serves as a power source for the hydraulic system and provides hydraulic oil for the hydraulic system of the anchor miner. The hydraulic piston pump 1 can control the output flow rate according to the operator's instructions to achieve energy saving.

[0035] The electro-hydraulic proportional multi-way reversing valve group 2 includes two electro-hydraulic proportional multi-way reversing valve groups, which are respectively connected between the hydraulic piston pump 1 and the first oil replenishment control valve group 4.1 and the second oil replenishment control valve group 4.2, and are used to realize the oil reversing function, change the action direction of the actuator, and provide pilot control oil to the loading motor control valve group 3;

[0036] The first oil replenishment control valve group 4.1 and the second oil replenishment control valve group 4.2 are connected and arranged between the electro-hydraulic proportional multi-way reversing valve group 2 and the first loading plunger motor 5.1 and the second loading plunger motor 5.2, and are provided with a working oil circuit pressure signal extraction port for extracting the working oil circuit signals of the first loading plunger motor 5.1 and the second loading plunger motor 5.2 as the control signal source of the loading motor control valve group 3, and at the same time, the external replenishment oil is timely supplemented to the hydraulic system through this valve body to prevent the motor from being damaged by cavitation;

[0037] The first loading plunger motor 5.1 and the second loading plunger motor 5.2 are connected to the first oil replenishment control valve group 4.1 and the second oil replenishment control valve group 4.2 through pipelines, respectively, and their function is to drive the corresponding loading reducer to realize the operation of the loading mechanism. The first loading plunger motor 5.1 and the second loading plunger motor 5.2 are both provided with a motor variable port (X port) for displacement control by pilot control oil. The initial displacement of the motor is the maximum displacement. When the pilot control oil enters the motor variable port, the swing angle of the first loading plunger motor 5.1 and the second loading plunger motor 5.2 is swung from the maximum displacement to the minimum set displacement.

[0038] The loading motor control valve group 3 is connected to the motor variable ports (X ports) of the first loading plunger motor 5.1 and the second loading plunger motor 5.2, the working oil circuit signal extraction ports of the first oil replenishment control valve group 4.1 and the second oil replenishment control valve group 4.2, and the output oil pressure regulating port (Z port) of the electro-hydraulic proportional multi-way reversing valve group 2 through pipelines, and is used to output pilot control oil to the motor variable ports (X ports) of the first loading plunger motor 5.1 and the second loading plunger motor 5.2 according to the real-time working pressure of the first loading plunger motor 5.1 and the second loading plunger motor 5.2, so as to control the first loading plunger motor 5.1 and the second loading plunger motor 5.2 to switch between the maximum displacement and the minimum displacement, thereby realizing the mode switching between light load high speed and heavy load low speed.

[0039] This embodiment provides a hydraulic driven loading control system for an anchor miner, comprising a hydraulic piston pump 1, an electro-hydraulic proportional multi-way reversing valve group 2, a first oil replenishment control valve group 4.1, a second oil replenishment control valve group 4.2, a first loading piston motor 5.1, a second loading piston motor 5.2, and a loading motor control valve group 3. According to the actual demand of the anchor mining machine loading device, this embodiment proposes a hydraulic driving loading control system for the anchor mining machine in view of the shortcomings of the current motor-driven reducer and low-speed and high-torque motor drive. The system uses a piston motor with adjustable displacement as the power, and can adjust the displacement of the loading piston motor according to the real-time working pressure of the loading piston motor, control the loading piston motor to switch between the maximum displacement and the minimum displacement, and realize the mode switching of light load high speed and heavy load low speed. Therefore, compared with the existing driving mode, it mainly includes the following technical advantages: the control system adopts the axial piston high-speed driving reducer loading form, which can effectively cope with the ground water surface condition and ensure the normal operation of the system; the control system has a low cost because it adopts the general hydraulic components of engineering machinery; the control system adds a control valve group, which can automatically realize the light load high speed and heavy load low speed working mode switching according to the load demand of the loading system and the working pressure of the loading device, without manual participation, and has a high degree of intelligence; the control system adds an oil replenishment valve group to avoid abnormal damage to the hydraulic drive device, effectively cope with the frequent impact conditions of the loading device, greatly improve the protection of the loading motor, and prevent the motor from being damaged by air suction.

[0040] Preferably, the loading motor control valve group 3 comprises a first one-way sequence valve 3.3.1, a second one-way sequence valve 3.3.2, a first two-position four-way hydraulically controlled directional control valve 3.5.1, a second two-position four-way hydraulically controlled directional control valve 3.5.2, and a second shuttle valve 3.4, which is used to select the highest working pressure as the highest pressure extraction device of the signal, wherein:

[0041] The input ends of the first one-way sequence valve 3.3.1 and the second one-way sequence valve 3.3.2 are connected to the working oil circuit pressure signal extraction port of the oil replenishment control valve group through the maximum pressure extraction device, and the opening pressure of the first one-way sequence valve 3.3.1 is greater than the opening pressure of the second one-way sequence valve 3.3.2. The output point of the second one-way sequence valve 3.3.2 is connected to the P port of the first two-position four-way hydraulically controlled reversing valve 3.5.1, the P1 port of the second shuttle valve 3.4 is connected to the output end of the first one-way sequence valve 3.3.1, the P2 port of the second shuttle valve 3.4 is respectively connected to the B port of the first two-position four-way hydraulically controlled reversing valve 3.5.1 and the left pilot port of the second two-position four-way hydraulically controlled reversing valve 3.5.2, and the A port of the second shuttle valve 3.4 is respectively connected to the left pilot port of the first two-position four-way hydraulically controlled reversing valve 3.5.1 and the oil drain circuit The P port of the second two-position four-way hydraulically controlled reversing valve 3.5.2 receives the pilot control oil from the electro-hydraulic proportional multi-way reversing valve group 2, the A port of the second two-position four-way hydraulically controlled reversing valve 3.5.2 is connected to the motor variable port of the loading plunger motor through a pipeline, the T port of the second two-position four-way hydraulically controlled reversing valve 3.5.2, the T port of the first two-position four-way hydraulically controlled reversing valve 3.5.1 and the T port of the second two-position four-way hydraulically controlled reversing valve 3.5.2 are all connected to the pressure relief circuit. The second shuttle valve 3.4 of this embodiment can realize the reversing control of the first two-position four-way hydraulically controlled reversing valve 3.5.1. The first two-position four-way hydraulically controlled reversing valve 3.5.1 and the second two-position four-way hydraulically controlled reversing valve 3.5.2 have the function of switching the working position according to the system working pressure, thereby realizing the control of the working oil circuit signal of the first loading plunger motor 5.1 and the second loading plunger motor 5.2.

[0042] Specifically, the loading motor control valve group further includes a two-position two-way hydraulically controlled reversing valve 3.7 and a relief valve 3.8, wherein:

[0043] The input of the two-position two-way hydraulic control reversing valve 3.7 is connected to the Ls port of the electro-hydraulic proportional multi-way reversing valve group 2, and the output end is connected to the input point of the relief valve 3.8. The pilot control port of the two-position two-way hydraulic control reversing valve 3.7 is connected to the B port of the second two-position four-way hydraulic control reversing valve 3.5.2, and the output end of the relief valve 3.8 is connected to the oil drain circuit. The two-position two-way hydraulic control reversing valve 3.7 of this embodiment is used to realize the opening and closing of the pressure limiting function of the control signal Ls, and the relief valve 3.8 is used to realize the pressure limiting function of the control signal Ls.

[0044] Preferably, the output end of the maximum pressure extraction device is provided with a first damper 3.2 for limiting the control flow and ensuring that the control pressure is stable and without shock.

[0045] Preferably, a second damper 3.3 is provided on the pipeline between the output end of the first one-way sequence valve 3.3.1 and the P1 port of the second shuttle valve 3.4 to achieve pressure filtering and ensure that the control pressure is stable and has no impact.

[0046] Preferably, a third damper 3.6 is provided on the pipeline between the A port of the second shuttle valve 3.4 and the pressure relief circuit, which is used for bypassing the oil leakage and can also ensure that the oil output from the A port of the second shuttle valve 3.4 to the left pilot port of the first two-position four-way hydraulically controlled reversing valve 3.5.1 has a certain pressure to push the first two-position four-way hydraulically controlled reversing valve 3.5.1 to the left position.

[0047] Preferably, the maximum pressure extraction device comprises a first shuttle valve 3.1, the P1 port and the P2 port of the first shuttle valve 3.1 are respectively connected to the working oil circuit pressure signal extraction ports of the first oil replenishment control valve group 4.1 and the second oil replenishment control valve group 4.2, and the A port of the first shuttle valve 3.1 is connected to the input ends of the first one-way sequence valve 3.3.1 and the second one-way sequence valve 3.3.2. This embodiment adopts the first shuttle valve 3.1 to realize the maximum pressure extraction, which has a simple structure, low cost, durability and reliability.

[0048] Preferably, a maximum working oil circuit pressure signal extraction device is provided in the oil replenishment control valve group, and the maximum working oil circuit pressure signal extraction device comprises a third shuttle valve 3.11, and the P1 port and the P2 port of the third shuttle valve 3.11 are respectively connected to the two hydraulic oil circuits in the oil replenishment control valve group, and the A port of the third shuttle valve 3.11 is connected to the input end of the maximum pressure extraction device in the loading motor control valve group as a working oil circuit pressure signal extraction port.

[0049] The control system of the above embodiment can realize efficient driving of the anchor miner loading and realize automatic switching control of light load high speed and heavy load low speed mode. The detailed working principle is as follows:

[0050] When the operator starts the loading device, the first and second links of the electro-hydraulic proportional multi-way reversing valve group 2 are both in upper working position after receiving the control signal, the Ls port of the electro-hydraulic proportional multi-way reversing valve group 2 outputs the pilot feedback signal to the X port of the hydraulic piston pump 1, and the A port of the hydraulic piston pump 1 outputs the required oil to the P port of the electro-hydraulic proportional multi-way reversing valve group 2, and the oil enters the valve bodies of the first oil replenishment control valve group 4.1 and the second oil replenishment control valve group 4.2 through the B port of the first link and the A port of the second link of the electro-hydraulic proportional multi-way reversing valve group 2, and extracts their respective working pressure signals, which are transported to the K1 port and the K2 port of the loading motor control valve group 3 through pipelines. After the oil flows through the first oil replenishment control valve group 4.1 and the second oil replenishment control valve group 4.2, it enters the A port of the first loading piston motor 5.1 and the B port of the second loading piston motor 5.2, drives the respective reducers to rotate, and then drives the loading device to work. After the oil in the oil replenishment system enters the first oil replenishment control valve group 4.1 and the second oil replenishment control valve group 4.2, it waits for the pipeline to show a tendency of cavitation, and then enters the corresponding side for oil replenishment to prevent the system from oil driving the motor. Then, the oil enters the multi-way valve from the B port of the first loading plunger motor 5.1 and the A port of the second loading plunger motor 5.2 through the first A port and the second B port of the electro-hydraulic proportional multi-way reversing valve group 2, and finally returns to the oil tank through the T port of the electro-hydraulic proportional multi-way reversing valve group 2.

[0051] When the working pressure of the first loading piston motor 5.1 and the second loading piston motor 5.2 does not reach the set pressure value of the first one-way sequence valve 3.3.1 of the loading motor control valve group 3, the second two-position four-way hydraulic control reversing valve 3.5.2 is in the right position, and the pilot pressure oil output from the Z port of the electro-hydraulic proportional multi-way reversing valve group 2 passes through the P port of the second two-position four-way hydraulic control reversing valve 3.5.2 to the A port, and then the oil enters the X port of the first loading piston motor 5.1 and the second loading piston motor 5.2 through the A port of the loading motor control valve group 3. At the X port of the plunger motor 5.2, both loading plunger motors are working in small displacement, and the whole machine is in light-load high-speed working mode. At this time, the pilot control port of the two-position two-way hydraulic control reversing valve 3.7 of the loading motor control valve group 3 is connected to the drain tank through the B port of the second two-position four-way hydraulic control reversing valve 3.5.2 to the T port. The two-position two-way hydraulic control reversing valve 3.7 is working in the lower position, and the oil circuit is normally disconnected. The Ls oil signal of the electro-hydraulic proportional multi-way reversing valve group 2 flows to the inlet of the two-position two-way hydraulic control reversing valve 3.7 and stops;

[0052] When the working pressure of the loading device gradually increases to the set pressure value of the second one-way sequence valve 3.3.2 of the loading motor control valve group 3, the working pressure signal of the working oil circuit of the B port of the first loading plunger motor 5.1 and the A port of the second loading plunger motor 5.2 is extracted to the K1 port and K2 port of the loading motor control valve group 3. After the first shuttle valve 3.1 of the loading motor control valve group 3 is selected, the highest pressure is output and flows all the way to the inlet of the first one-way sequence valve 3.3.1. Since the set pressure is not reached, force value, the hydraulic oil is locked here, and the other oil flow to the inlet of the second one-way sequence valve 3.3.2, open the second one-way sequence valve 3.3.2 and enter the P port of the first two-position four-way hydraulic control reversing valve 3.5.1. However, since the first two-position four-way hydraulic control reversing valve 3.5.1 is in the right position at this time, the oil flows to the A port of the first two-position four-way hydraulic control reversing valve 3.5.1 and is locked. At this time, the two loading plunger motors are still working in small displacement, and the whole machine is in light load and high speed working mode.

[0053] When the working pressure continues to rise to the setting value of opening the first one-way sequence valve 3.3.1, the oil flows through the first one-way sequence valve 3.3.1 and the second damper 3.3, and then flows to the P1 port of the second shuttle valve 3.4. After passing through the A port of the second shuttle valve 3.4, one way acts on the left pilot port of the first two-position four-way hydraulic control reversing valve 3.5.1, thereby switching the two-position four-way hydraulic control reversing valve 3.5.1 to the left position for operation, and the other way flows back to the oil drain circuit through the third damper 3.6. The first two After the two-position four-way hydraulically controlled reversing valve 3.5.1 is in the left position, the oil at the outlet of the second one-way sequence valve 3.3.2 flows to the B port through the P port of the first two-position four-way hydraulically controlled reversing valve 3.5.1, and the oil continues to flow, one way flows to the P2 port of the second shuttle valve 3.4, but because the P1 port of the second shuttle valve 3.4 has been acted on by hydraulic pressure, this way of hydraulic oil is locked here, and the other way acts on the left pilot port of the second two-position four-way hydraulically controlled reversing valve 3.5.2, pushing the second two-position four-way hydraulically controlled reversing valve 3.5.2 to push ...4 to push the second two-position four-way hydraulically controlled reversing valve 3.4 to push the second two-position four-way hydraulically controlled reversing valve 3.5.2 to push the second two-position four-way hydraulically controlled reversing valve 3.4 to push the second two-position four-way hydraulically controlled reversing valve 3.4 to push the second two-position four-way hydraulically controlled reversing valve 3.4 to push the second two-position four-way hydraulically controlled reversing valve 3.4 to push the second two-position four-way When the control reversing valve 3.5.2 is in the left position, the pilot control oil for displacement control flows through the P port of the second two-position four-way hydraulic control reversing valve 3.5.2 and the B port to the upper pilot port of the two-position two-way hydraulic control reversing valve 3.7, so that the upper position of the two-position two-way hydraulic control reversing valve 3.7 works, and the system pressure feedback signal Ls is led to the inlet of the relief valve 3.8 and enters the oil drain circuit through the relief valve 3.8, so that the output pressure of the hydraulic plunger pump 1 is reduced to 20MPa to avoid The loading reducer causes internal damage, and after the second two-position four-way hydraulically controlled reversing valve 3.5.2 is in the left position, the pilot pressure oil at the X port of the first loading piston motor 5.1 and the X port of the second loading piston motor 5.2 flows through the A port to the T port of the second two-position four-way hydraulically controlled reversing valve 3.5.2 to the oil drain circuit. At this time, the displacement of the first loading piston motor 5.1 and the second loading piston motor 5.2 changes from the minimum displacement to the maximum displacement, and the loading device is in heavy-load and low-speed working mode.

[0054] When the working pressure of the loading system drops to less than the set pressure value of the first one-way sequence valve 3.3.1, the first one-way sequence valve 3.3.1 is closed, and the pressure between the outlet of the first one-way sequence valve 3.3.1 and the second shuttle valve 3.4 gradually decreases due to leakage. When the pressure continues to drop to less than the pressure of the P2 port of the second shuttle valve 3.4, the pressure of the P2 port of the second shuttle valve 3.4 pushes the shuttle valve, and the oil enters the P2 port of the second shuttle valve 3.4 into the A port, and then enters the left pilot port of the first two-position four-way hydraulic control reversing valve 3.5.1, ensuring the first two-position four-way hydraulic control reversing valve 3.5.1. 5.1 is still working in the left position, and the working states of other components remain unchanged. At this time, the pressure of the P port of the electro-hydraulic proportional multi-way reversing valve group is reduced through the restriction of the relief valve 3.8, and the control pressure of the variable port (X port) of the first loading piston motor 5.1 and the second loading piston motor 5.2 is released at the same time, so that the first loading piston motor 5.1 and the second loading piston motor 5.2 return to large displacement. At this time, the loading device is still in the heavy load and low speed mode. The purpose of this process is mainly to prevent the displacement change frequency of the loading piston motor 5.1 and the loading piston motor 5.2 from being too fast, causing system oscillation.

[0055] When the working pressure of the loading system drops to less than the set pressure value of the second one-way sequence valve 3.3.2, the oil is locked at the inlet of the second one-way sequence valve 3.3.2, and the pilot pressure on the left side of the first two-position four-way hydraulically controlled reversing valve 3.5.1 is reduced to zero due to the action of the third damper 3.6. The first two-position four-way hydraulically controlled reversing valve 3.5.1 returns to the right position under the action of the return spring force. The pressure between the pilot port of the second shuttle valve 3.4 and the pilot port of the second two-position four-way hydraulically controlled reversing valve 3.5.2 and the B port of the first two-position four-way hydraulically controlled reversing valve 3.5.1 drops to zero due to the oil leakage from the B port to the T port of the first two-position four-way hydraulically controlled reversing valve 3.5.1. The second two-position four-way hydraulically controlled reversing valve 3.5.2 returns to the right position under the action of the return spring force. The right position is restored under the action of the pilot control oil, which re-enters the variable port (X port) of the first loading plunger motor 5.1 and the second loading plunger motor 5.2 through the P port to the A port of the second two-position four-way hydraulically controlled reversing valve 3.5.2, and the displacement changes from the maximum displacement to the minimum displacement. At the same time, the pilot port pressure oil of 3.7 of the two-position two-way hydraulically controlled reversing valve flows to the oil drain circuit through the B port to the T port of the second two-position four-way hydraulically controlled reversing valve 3.5.2. Under the action of the reset spring force, 3.7 of the two-position two-way hydraulically controlled reversing valve resumes the lower position, and the Ls signal oil port of the loading motor control valve group 3 is locked at the inlet of 3.7 of the two-position two-way hydraulically controlled reversing valve. In this way, the loading device automatically changes to the light-load high-speed mode as the working pressure decreases.

[0056] like Figure 3 and Figure 4As shown, in another preferred embodiment of the present application, the loading motor control valve group 3 includes a maximum pressure extraction device for selecting the maximum working pressure as a signal, a two-position four-way solenoid valve 3.9, and a pressure sensor 3.10. The input end of the pressure sensor 3.10 is connected to the working oil circuit pressure signal extraction port of the oil replenishment control valve group through the maximum pressure extraction device, the electrical signal output end of the pressure sensor 3.10 is connected to the solenoid valve signal of the two-position four-way solenoid valve 3.9, the P port of the two-position four-way solenoid valve 3.9 receives the pilot control oil from the electro-hydraulic proportional multi-way reversing valve group 2, the B port of the two-position four-way solenoid valve 3.9 is connected to the motor variable port of the loading plunger motor through a pipeline, and the T port of the two-position four-way solenoid valve 3.9 is connected to the pressure relief circuit.

[0057] The maximum pressure extraction device comprises a first shuttle valve 3.1, wherein the P1 port and the P2 port of the first shuttle valve 3.1 are respectively connected to the working oil circuit pressure signal extraction ports of the corresponding oil replenishment control valve group, and the A port of the first shuttle valve 3.1 is connected to the input end of the pressure sensor 3.10.

[0058] The loading motor control valve group 3 of the above embodiment includes a first shuttle valve 3.1, a two-position four-way solenoid valve 3.2, and a pressure sensor 3.3. The first shuttle valve 3.1 is used to detect the working pressure of the loading system in real time, realize the maximum pressure extraction, and provide the pressure sensor 3.10 for pressure detection;

[0059] The function of the two-position four-way solenoid valve 3.2 shown is to realize on-off control of the pilot control oil of the variable port (X port) of the first loading plunger motor 5.1 and the second loading plunger motor 5.2 by reversing the solenoid valve according to the pressure signal output by the pressure sensor 3.10, thereby realizing the displacement control of the first loading plunger motor 5.1 and the second loading plunger motor 5.2.

[0060] The oil enters the valve bodies of the first oil replenishment control valve group 4.1 and the second oil replenishment control valve group 4.2 through the first joint B port and the second joint A port of the electro-hydraulic proportional multi-way reversing valve group 2, and extracts their respective working pressure signals, which are transported to the K1 port and the K2 port of the loading motor control valve group 3 through pipelines. After flowing through the first oil replenishment control valve group 4.1 and the second oil replenishment control valve group 4.2, the oil enters the A port of the first loading plunger motor 5.1 and the B port of the second loading plunger motor 5.2, driving their respective reducers to rotate, and then driving the loading device to work. After the oil in the oil replenishment system enters the first oil replenishment control valve group 4.1 and the second oil replenishment control valve group 4.2, it waits for the pipeline to show a tendency to be sucked empty, and then enters the corresponding side for oil replenishment to prevent the system from lack of oil and wear. After the oil drives the motor, it enters the multi-way valve from the B port of the first loading plunger motor 5.1 and the A port of the second loading plunger motor 5.2 through the first A port and the second B port of the electro-hydraulic proportional multi-way reversing valve group 2, and finally returns to the oil tank through the T port of the electro-hydraulic proportional multi-way reversing valve group 2. Otherwise, the B port of the first loading plunger motor 5.1 and the second loading plunger motor 5.2 are reversed respectively.

[0061] After the system working pressure is transmitted to the K1 and K2 ports of the loading motor control valve group 3 through the pipeline, it is delivered to the pressure sensor 3.10 after passing through the first shuttle valve 3.1. When the system working pressure is lower than the shift setting pressure value, the two-position four-way solenoid valve 3.9 is not energized and works in the right position. The control oil enters the valve body through the P port of the loading motor control valve group 3 and is locked at the P port of the two-position four-way solenoid valve 3.9. The oil circuit of the variable port (X port) of the first loading plunger motor 5.1 and the second loading plunger motor 5.2 enters the valve body through the A port of the loading motor control valve group 3, and reaches the T port through the B port of the two-position four-way solenoid valve 3.9, and finally returns the oil through the L port of the loading motor control valve group 3. At this time, the B port of the first loading plunger motor 5.1 and the second loading plunger motor 5.2 are in a large displacement state, and the loading device is in a low-speed and high-torque state.

[0062] When the system working pressure is higher than the shift setting pressure value, the two-position four-way solenoid valve 3.9 is energized and works in the left position. The control oil enters the valve body through the P port of the loading motor control valve group 3, reaches the B port through the P port of the two-position four-way solenoid valve 3.9, and enters the variable port (X port) of the first loading plunger motor 5.1 and the second loading plunger motor 5.2 through the A port of the loading motor control valve group 3, realizing the motor variable and finally realizing the high-speed and light-load state of the loading device.

[0063] The above description is only a preferred embodiment of the present application and is not intended to limit the present application. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present application should be included in the protection scope of the present application.

Claims

1. A hydraulic loading control system for bolter digger, characterized in that: include: A hydraulic piston pump (1), serving as a power source for the hydraulic system, provides hydraulic oil to the hydraulic system of the anchor miner; The electro-hydraulic proportional multi-way reversing valve group (2) is connected between the hydraulic piston pump (1) and the oil replenishment control valve group to realize the oil reversing function, change the action direction of the actuator, and provide pilot control oil to the loading motor control valve group; At least one oil replenishment control valve group is connected and arranged between the electro-hydraulic proportional multi-way reversing valve group (2) and the loading plunger motor, and is provided with a working oil circuit pressure signal extraction port, which is used to extract the working oil circuit signal of the loading plunger motor as a control signal source of the loading motor control valve group, and at the same time, external replenishment oil is timely replenished to the hydraulic system through this valve body; At least one loading plunger motor is connected to the oil replenishment control valve group through a pipeline, and is provided with a motor variable port for controlling the displacement by the pilot control oil. When the pilot control oil enters the motor variable port, the motor swing angle is swung from the maximum displacement to the minimum set displacement; The loading motor control valve group is connected to the motor variable port of the loading piston motor, the working oil circuit signal extraction port of the oil replenishment control valve group and the output oil pressure adjustment port of the electro-hydraulic proportional multi-way reversing valve group (2) through pipelines, and is used to output pilot control oil to the motor variable port of the loading piston motor according to the real-time working pressure of the loading piston motor, control the loading piston motor to switch between the maximum displacement and the minimum displacement, and realize the mode switching between light load high speed and heavy load low speed.

2. The bolter digging machine hydraulic drive loading control system according to claim 1, characterized in that: The loading motor control valve group comprises a first one-way sequence valve (3.3.1), a second one-way sequence valve (3.3.2), a first two-position four-way hydraulically controlled reversing valve (3.5.1), a second two-position four-way hydraulically controlled reversing valve (3.5.2), and a second shuttle valve (3.4), and is used to select the highest working pressure as a highest pressure extraction device for the signal, wherein: The input ends of the first one-way sequence valve (3.3.1) and the second one-way sequence valve (3.3.2) are connected to the working oil circuit pressure signal extraction port of the oil replenishment control valve group through the maximum pressure extraction device, and the opening pressure of the first one-way sequence valve (3.3.1) is greater than the opening pressure of the second one-way sequence valve (3.3.2), the output point of the second one-way sequence valve (3.3.2) is connected to the P port of the first two-position four-way hydraulic control reversing valve (3.5.1), the P1 port of the second shuttle valve (3.4) is connected to the output end of the first one-way sequence valve (3.3.1), and the P2 port of the second shuttle valve (3.4) is respectively connected to the B port of the first two-position four-way hydraulic control reversing valve (3.5.1) and the P3 port of the second shuttle valve (3.4). The second shuttle valve (3.4) is connected to the left pilot port of the second two-position four-way hydraulically controlled reversing valve (3.5.2); the A port of the second shuttle valve (3.4) is respectively connected to the left pilot port and the oil drain circuit of the first two-position four-way hydraulically controlled reversing valve (3.5.1); the P port of the second two-position four-way hydraulically controlled reversing valve (3.5.2) receives the pilot control oil from the electro-hydraulic proportional multi-way reversing valve group (2); the A port of the second two-position four-way hydraulically controlled reversing valve (3.5.2) is connected to the motor variable port of the loading plunger motor through a pipeline; the T port of the second two-position four-way hydraulically controlled reversing valve (3.5.2), the T port of the first two-position four-way hydraulically controlled reversing valve (3.5.1) and the T port of the second two-position four-way hydraulically controlled reversing valve (3.5.2) are all connected to the pressure relief circuit.

3. The bolter digging machine hydraulic drive loading control system according to claim 2, characterized in that: The loading motor control valve group also includes a two-position two-way hydraulically controlled reversing valve (3.7) and a relief valve (3.8), wherein: The input of the two-position two-way hydraulically controlled directional valve (3.7) is connected to the Ls port of the electro-hydraulic proportional multi-way directional valve group (2), and the output end is connected to the input point of the relief valve (3.8). The pilot control port of the two-position two-way hydraulically controlled directional valve (3.7) is connected to the B port of the second two-position four-way hydraulically controlled directional valve (3.5.2), and the output end of the relief valve (3.8) is connected to the oil drain circuit.

4. The bolter digging machine hydraulic drive loading control system according to claim 2, characterized in that: The output end of the maximum pressure extraction device is provided with a first damping (3.2).

5. The bolter digging machine hydraulic drive loading control system according to claim 2, characterized in that: A second damper (3.3) is provided on the pipeline between the output end of the first one-way sequence valve (3.3.1) and the A port of the second shuttle valve (3.4).

6. The bolter digging machine hydraulic drive loading control system according to claim 2, characterized in that: A third damper (3.6) is provided on the pipeline between the A port of the second shuttle valve (3.4) and the pressure relief circuit.

7. The bolter digging machine hydraulic drive loading control system according to claim 2, characterized in that: The maximum pressure extraction device comprises a first shuttle valve (3.1), wherein ports P1 and P2 of the first shuttle valve (3.1) are respectively connected to corresponding working oil circuit pressure signal extraction ports of the oil replenishment control valve group, and port A of the first shuttle valve (3.1) is connected to input ends of the first one-way sequence valve (3.3.1) and the second one-way sequence valve (3.3.2).

8. The bolter digging machine hydraulic drive loading control system according to claim 1, characterized in that: The loading motor control valve group (3) comprises a maximum pressure extraction device for selecting the maximum working pressure as a signal, a two-position four-way solenoid valve (3.9), and a pressure sensor (3.10); the input end of the pressure sensor (3.10) is connected to the working oil circuit pressure signal extraction port of the oil replenishment control valve group through the maximum pressure extraction device; the electrical signal output end of the pressure sensor (3.10) is connected to the solenoid valve signal of the two-position four-way solenoid valve (3.9); the P port of the two-position four-way solenoid valve (3.9) receives the pilot control oil from the electro-hydraulic proportional multi-way reversing valve group (2); the B port of the two-position four-way solenoid valve (3.9) is connected to the motor variable port of the loading plunger motor through a pipeline; and the T port of the two-position four-way solenoid valve (3.9) is connected to the pressure relief circuit.

9. The bolter digging machine hydraulic drive loading control system according to claim 8, characterized in that: The maximum pressure extraction device comprises a first shuttle valve (3.1), wherein ports P1 and P2 of the first shuttle valve (3.1) are respectively connected to corresponding working oil circuit pressure signal extraction ports of the oil replenishment control valve group, and port A of the first shuttle valve (3.1) is connected to an input end of the pressure sensor (3.10).

10. The bolter digging machine hydraulic drive loading control system according to claim 1, characterized in that: A maximum working oil circuit pressure signal extraction device is arranged in the oil replenishment control valve group, and the maximum working oil circuit pressure signal extraction device comprises a third shuttle valve (3.11), and the P1 port and the P2 port of the third shuttle valve (3.11) are respectively connected to the two hydraulic oil circuits in the oil replenishment control valve group, and the A port of the third shuttle valve (3.11) is connected to the input end of the maximum pressure extraction device in the loading motor control valve group as a working oil circuit pressure signal extraction port.

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