CN101575978B - Pressure-speed mixed control shield propulsion hydraulic system - Google Patents

Abstract

The invention discloses a shield propulsion hydraulic system controlled by pressure-velocity mixing. Including three-position four-way reversing valve, three two-position three-way reversing valves, proportional pressure reducing valve, proportional speed regulating valve, two one-way valves, cartridge valves, relief valves, pressure sensors, and hydraulic cylinders. The propulsion system uses a proportional speed regulating valve to control the speed, and a proportional pressure reducing valve to control the pressure. The pressure and speed control modes can be switched in real time according to actual needs to meet the requirements of shield earth pressure balance and attitude control. Through the two-position three-way reversing valve to control the opening and closing of the cartridge valve port, the hydraulic cylinder can be fast forwarded, fast reversed and reliably locked, which increases the flexibility of the system. The shield propulsion hydraulic control system using pressure-velocity mixed control can adapt to complex geological environment excavation conditions, and is suitable for the propulsion motion control of shield tunneling equipment under various geological conditions.

Description

Shield propulsion hydraulic system with pressure-velocity mixed control

technical field

The invention relates to a fluid pressure actuator, in particular to a shield propulsion hydraulic system with pressure-velocity mixing control.

Background technique

The shield propulsion system is an important part of the shield tunneling machine, which undertakes the propulsion task of the entire shield tunneling machine. The propulsion system can not only realize the function of pushing the shield forward, but also complete related complex tasks such as the shield's curve travel, deviation correction and attitude control. The propulsion system can adapt to changes in soil quality and water and soil pressure in different construction strata, and output appropriate propulsion pressure and propulsion speed to match parameters such as soil pressure in the sealed cabin at the front of the shield, cutter head speed and slag discharge speed to jointly achieve safe, fast, Efficient digging.

The real-time and continuous adjustment of the pressure and speed parameters of the hydraulic system can be realized by using the electro-hydraulic proportional valve. In the pressure control mode, the attitude control of the shield excavation can be realized by adjusting the pressure of each group of the propulsion system. In the speed control mode, it can cooperate with the speed control of the screw conveyor to achieve the balance control of excavation and soil discharge, and maintain the stability of the excavation surface. , which can better meet the requirements of shield tunneling for propulsion control.

Contents of the invention

The purpose of the present invention is to provide a shield propulsion hydraulic system with pressure-velocity mixed control. Proportional valves can be used to realize real-time and continuous adjustment of the pressure and speed parameters of the propulsion hydraulic system, so as to meet the working needs of the propulsion system in different geological environments.

The technical scheme adopted in the present invention is:

The invention includes: three-position four-way reversing valve, the first two-position three-way reversing valve, the second two-position three-way reversing valve, proportional pressure reducing valve, proportional speed regulating valve, first one-way valve, Cartridge valve, the third two-position three-way reversing valve, the second one-way valve, relief valve, pressure sensor, hydraulic cylinder with built-in displacement sensor; the oil inlet P1 of the three-position four-way reversing valve is connected to the main inlet The oil circuit is connected, the oil return port T1 is connected with the main oil return circuit, and the oil outlets A1 and B1 are respectively connected to the first two-position three-way reversing valve oil inlet P2 and the hydraulic cylinder with built-in displacement sensor. The oil outlet B9 of the check valve is connected; the oil outlets A2 and B2 of the first two-position three-way reversing valve are respectively connected with the oil inlet P3 of the second two-position three-way reversing valve and the oil inlet A7 of the cartridge valve ;The oil outlets A3 and B3 of the second two-position three-way reversing valve are respectively connected with the oil inlet P5 of the proportional speed regulating valve and the oil inlet P4 of the proportional pressure reducing valve; the oil outlet T5 of the proportional speed regulating valve is connected with the proportional pressure reducing valve The oil outlet T4 of the valve is connected with the oil inlet A6 of the first one-way valve; the oil outlet B6 of the first one-way valve is connected with the oil outlet B7 of the cartridge valve, the oil outlet A8 of the third two-position three-way reversing valve, The oil inlet P10 of the relief valve and the pressure sensor are connected to the rodless chamber of the hydraulic cylinder with the built-in displacement sensor; the control oil port K7 of the cartridge valve is connected to the oil inlet P8 of the third two-position three-way reversing valve; the third The oil outlet B8 of the two-position three-way reversing valve is connected with the oil inlet A7 of the cartridge valve; the oil outlet T10 of the relief valve is connected with the oil inlet A9 of the second one-way valve.

The beneficial effects that the present invention has are:

1) The proportional speed regulating valve is used to control the speed of the propulsion hydraulic cylinder, so that the propulsion speed is accurately controllable, and it is easy to cooperate with the screw conveyor to realize the earth pressure balance control;

2) The proportional pressure reducing valve is used to control the output force of the propulsion hydraulic cylinder, which is easy to realize the coordinated control of shield posture;

3) The action and reliable locking of the hydraulic cylinder are controlled by the cartridge valve group, which increases the flexibility of the system;

4) A directional valve on the main oil circuit is used to cooperate with the cartridge valve group of each hydraulic cylinder to realize the forward and backward of each propulsion hydraulic cylinder, which greatly reduces the number of electromagnetic directional valves in the propulsion multi-cylinder system and improves the electrical reliability of the system sex.

Description of drawings

The accompanying drawing is a schematic diagram of the single-cylinder control of the shield propulsion hydraulic system under pressure-velocity mixed control in the present invention.

In the figure: 1. Three-position four-way reversing valve, 2, 3, 8. Two-position three-way reversing valve, 4. Proportional pressure reducing valve, 5. Proportional speed regulating valve, 6, 9. One-way valve, 7 . Cartridge valve, 10. Relief valve, 11. Pressure sensor, 12. Hydraulic cylinder with built-in displacement sensor.

Detailed ways

The present invention will be further described below in conjunction with drawings and embodiments.

As shown in the drawings, the present invention includes: a three-position four-way reversing valve 1, a first two-position three-way reversing valve 2, a second two-position three-way reversing valve 3, a proportional pressure reducing valve 4, a proportional Speed control valve 5, first one-way valve 6, cartridge valve 7, third two-position three-way reversing valve 8, second one-way valve 9, overflow valve 10, pressure sensor 11, hydraulic pressure sensor with built-in displacement sensor Cylinder 12; the oil inlet P1 of the three-position four-way reversing valve 1 is connected to the main oil inlet circuit, the oil return port T1 is connected to the main oil return circuit, and the oil outlets A1 and B1 are respectively connected to the first two-position three-way switch The oil inlet P2 of the directional valve 2 is connected with the rod cavity of the hydraulic cylinder 12 with a built-in displacement sensor and the oil outlet B9 of the second one-way valve 9; the oil outlets A2 and B2 of the first two-position three-way reversing valve 2 are respectively connected with The oil inlet P3 of the second two-position three-way reversing valve 3 is connected with the oil inlet A7 of the cartridge valve 7; the oil outlets A3 and B3 of the second two-position three-way reversing valve 3 are connected with the proportional speed regulating valve 5 The oil inlet P5 is connected to the oil inlet P4 of the proportional pressure reducing valve 4; the oil outlet T5 of the proportional speed regulating valve 5 and the oil outlet T4 of the proportional pressure reducing valve 4 are connected to the oil inlet A6 of the first one-way valve 6; Oil outlet B6 of one-way valve 6 and oil outlet B7 of cartridge valve 7, oil outlet A8 of third two-position three-way reversing valve 8, oil inlet P10 of relief valve 10 and pressure sensor 11 are all aligned with the built-in displacement The hydraulic cylinder 12 of the sensor is connected to the rodless chamber; the control oil port K7 of the cartridge valve 7 is connected to the third two-position three-way reversing valve 8 oil inlet P8; the third two-position three-way reversing valve 8 oil outlet B8 is connected with the oil inlet A7 of the cartridge valve 7; the oil outlet T10 of the overflow valve 10 is connected with the oil inlet A9 of the second one-way valve 9.

The working principle of the present invention is as follows:

As shown in the attached figure, when the shield is moving forward, the electromagnet on the left side of the three-position four-way reversing valve 1 is energized, and the pressure oil in the main oil circuit enters through the P1 port of the three-position four-way reversing valve 1, and flows out to the second port A1. The oil inlet P2 of the three-way reversing valve 2 and other groups of hydraulic cylinder control valves of the propulsion system.

When the electromagnet of the two-position three-way reversing valve 2 is energized, it works in the left position, and the pressure oil flows through the P2 port and the A2 port to the P3 port.

When the electromagnet of the two-position three-way reversing valve 3 is powered off, the pressure oil at the P3 port enters the hydraulic cylinder with built-in displacement sensor through the B3 port of the two-position three-way reversing valve 3, the proportional pressure reducing valve 4 and the one-way valve 6 12 Rodless chambers, push the piston rod of the hydraulic cylinder to extend, and the shield machine is pushed forward under the pressure control mode. At this time, the electromagnet of the two-position three-way reversing valve 8 is powered off, and the cartridge valve 7 is in a closed state because the control oil port K7 is connected to the high-pressure oil in the rodless chamber of the hydraulic cylinder through the left position of the two-position three-way reversing valve 8 .

When the electromagnet of the two-position three-way reversing valve 3 is energized, the pressure oil at the P3 port enters the hydraulic cylinder 12 with a built-in displacement sensor through the A3 port of the two-position three-way reversing valve, the proportional speed control valve 5, and the one-way valve 6. Cavity, push the piston rod of the hydraulic cylinder to extend, and the shield machine moves forward under the speed control mode. At this time, the electromagnet of the two-position three-way reversing valve 8 is powered off, and the cartridge valve 7 is in a closed state because the control oil port K7 is connected to the high-pressure oil in the rodless chamber of the hydraulic cylinder through the left position of the two-position three-way reversing valve 8 .

In the propulsion pressure or speed control mode, the shield propulsion pressure and speed can be monitored in real time through the pressure sensor 11 and the displacement sensor built in the hydraulic cylinder 12, and the electric signal is fed back to the control system to output an appropriate signal to control the proportional valve.

The rod chamber of the hydraulic cylinder 12 is connected to the oil port B1 of the three-position four-way reversing valve 1 through a pipeline. When the shield is pushed forward, the hydraulic oil in the rod chamber of the hydraulic cylinder 12 passes through the three-position four-way reversing valve The oil ports B1 and T1 of 1 are connected to the main oil return circuit back to the oil tank.

During the propulsion process of the shield machine, when the load suddenly increases, causing the pressure in the rodless chamber of the hydraulic cylinder 12 to suddenly increase, the overflow valve 10 is opened. At the same time, the high-pressure oil in the rodless cavity of the hydraulic cylinder 12 flows to the oil outlet B6 of the one-way valve 6 and is blocked. Finally, the high-pressure oil in the rodless cavity of the hydraulic cylinder 12 flows into the oil tank through the overflow valve 10, the one-way valve 9, and the three-position four-way reversing valve 1 to the main return oil circuit, realizing the protection of the components under sudden load conditions Function.

When the electromagnet 2 of the two-position three-way reversing valve is powered off, it works in the right position, and the pressure oil flows to the port A7 through ports P2 and B2. If the electromagnet 8 of the two-position three-way reversing valve is powered off, the cartridge valve 7 The control oil port K7 is connected to the rodless chamber of the hydraulic cylinder through the two-position three-way reversing valve 8, the hydraulic oil at the A7 port pushes the valve core open, and the hydraulic oil from the main oil circuit enters the hydraulic cylinder through the cartridge valve 7 12 Rodless cavity, the hydraulic cylinder 12 realizes the no-load fast-forward action; if the electromagnet of the two-position three-way reversing valve 8 is energized, the control oil port K7 of the cartridge valve 7 passes through the right position of the two-position three-way reversing valve 8 and the cartridge The oil inlet port A7 of valve 7 is connected, and the hydraulic oil at port A7 will flow to the top of the cartridge spool. Due to the difference in the upper and lower areas of the spool, the spool is in a closed state. All the pressure oil to the A1 port of valve 1 flows to the control valves of other hydraulic cylinders in the propulsion system, thereby realizing the single-group fast-forward control of the propulsion hydraulic cylinders and meeting the needs of actual working conditions such as single-cylinder debugging.

When the shield segment is assembled, push the hydraulic cylinder back. At this time, the electromagnet on the right side of the three-position four-way reversing valve 1 is energized, and the pressure oil of the main oil circuit enters through the P1 port of the three-position four-way reversing valve 1, and B1 The port flows out to the rod cavity of hydraulic cylinder 12 and other groups of hydraulic cylinders of the propulsion system.

The hydraulic oil in the rodless chamber of the hydraulic cylinder 12 flows to the B7 port of the cartridge valve 7 and the oil outlet B6 of the one-way valve 6, and the one-way valve 6 is reversed to stop. If the electromagnet of the two-position three-way reversing valve 8 is energized, and the electromagnet of the two-position three-way electromagnetic reversing valve 2 is de-energized, the control oil port K7 of the cartridge valve 7 is connected to the right position of the two-position three-way reversing valve 8 and the cartridge The valve 7 is connected to the oil inlet A7, and then connected to the main return oil circuit through the two-position three-way reversing valve 2 and the three-position four-way reversing valve 1 to return to the oil tank, the valve core is opened, and the hydraulic oil in the rodless chamber of the hydraulic cylinder 12 Through the cartridge valve 7, the two-position three-way reversing valve 2, the three-position four-way reversing valve 1 and the main return oil circuit are connected back to the oil tank, at this time the hydraulic cylinder 12 retreats; if the two-position three-way reversing valve 8 When the electromagnet is powered off, the control oil port K7 of the cartridge valve 7 communicates with the rodless chamber of the hydraulic cylinder through the left position of the two-position three-way reversing valve 8, and the hydraulic oil in the rodless chamber will flow to the top of the cartridge valve core. The area is poor, and the spool is in the closed state. At this time, the hydraulic cylinder 12 does not operate, and the pressure oil from the B1 port of the three-position four-way reversing valve 1 all flows to the control valves of other hydraulic cylinders in the propulsion system, thereby realizing The group retreat control of the propulsion hydraulic cylinder meets the needs of actual working conditions such as segment assembly.

When the shield propulsion is suspended, in order to maintain the stability of the excavation surface, the propulsion system is required to maintain pressure. At this time, all the electromagnets of the three-position four-way reversing valve 1 are powered off and work in the neutral position. The pressure oil of the main oil circuit flows in through the P1 port and flows out of the T1 port back to the oil tank, so that the system is unloaded. Two-position three-way reversing valve 8 electromagnet is powered off, cartridge valve 7 controls oil port K7 through the left position of two-position three-way reversing valve 8 to communicate with the rodless chamber of hydraulic cylinder 12, and the hydraulic oil in the rodless chamber has a certain pressure , will act on the top of the cartridge spool, and the spool is closed due to the difference in the upper and lower areas of the spool. Under the joint action of the one-way valve 6 and the cartridge valve 7, the hydraulic oil in the rodless cavity of the hydraulic cylinder 12 realizes reliable pressure maintenance.

Claims (1)

1. a pressure-speed mixes the shield propulsion hydraulic system of controlling, and it is characterized in that comprising: the hydraulic cylinder (12) of three position four-way directional control valve (1), first two position three way directional control valve (2), second two position three way directional control valve (3), proportional pressure-reducing valve (4), proportional velocity regulating valve (5), first one way valve (6), cartridge valve (7), the 3rd two position three way directional control valve (8), second one way valve (9), overflow valve (10), pressure sensor (11), inbuilt displacement sensor; The oil inlet P 1 of three position four-way directional control valve (1) links to each other with main in-line, oil return inlet T 1 links to each other with main oil return line, oil-out A1 links to each other with first two position three way directional control valve (2) oil inlet P 2, and oil-out B1 links to each other with hydraulic cylinder (12) rod chamber and second one way valve (9) the oil-out B9 of inbuilt displacement sensor; First two position three way directional control valve (2) oil-out A2 links to each other with cartridge valve (7) oil-in A7 with second two position three way directional control valve (3) oil inlet P 3 respectively with B2; Second two position three way directional control valve (3) oil-out A3 links to each other with proportional pressure-reducing valve (4) oil inlet P 4 with proportional velocity regulating valve (5) oil inlet P 5 respectively with B3; Proportional velocity regulating valve (5) oil-out T5 links to each other with first one way valve (6) oil-in A6 with proportional pressure-reducing valve (4) oil-out T4; First one way valve (6) oil-out B6 all links to each other with hydraulic cylinder (12) rodless cavity of inbuilt displacement sensor with cartridge valve (7) oil-out B7, the 3rd two position three way directional control valve (8) oil-out A8, overflow valve (10) oil inlet P 10 and pressure sensor (11); Cartridge valve (7) control port K7 links to each other with the 3rd two position three way directional control valve (8) oil inlet P 8; The 3rd two position three way directional control valve (8) oil-out B8 links to each other with cartridge valve (7) oil-in A7; Overflow valve (10) oil-out T10 links to each other with second one way valve (9) oil-in A9.

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