Slag-stagnation-preventing crushing system for super-large-diameter slurry balance shield

Abstract

The invention belongs to the technical field of slurry balance shield tunneling, and particularly relates to a slag-stagnation-preventing crushing system for an ultra-large-diameter slurry balance shield tunneling, which comprises a shell, a jaw plate, a rotary grinding head, hydraulic cylinders, hydraulic motors and a hydraulic system, the hydraulic cylinders are fixed in the shell and connected with the jaw plate, and one end face of the jaw plate is provided with a plurality of hydraulic motors; a plurality of tooth-shaped structures and a rotary grinding head are arranged on the other end surface of the jaw plate; the crusher adopts a frame structure, so that the stress is more uniform; the crushing effect is enhanced by the rotary grinding head; the hydraulic system adopts a hydraulic station for pressurization and a pressurization cylinder for pressurization, so that the rock breaking capacity of the crusher under extreme working conditions is improved.

Description

Technical Field

[0001] The present application belongs to the technical field of slurry shield, and specifically relates to an anti-slag crushing system for an ultra-large diameter slurry shield. Background Art

[0002] During the construction of rock-rich tunnels, the slurry circulation system of ultra-large diameter slurry shields is prone to blockage and slag stagnation, which restricts the efficiency and safety of tunnel construction. The traditional slurry shield chamber has problems such as poor mechanical structure bearing capacity and low rock breaking force peak, which is one of the main causes of blockage and slag stagnation. Summary of the invention

[0003] This application proposes an anti-slag crushing system for super-large diameter slurry shield. Through the overall frame design, the overall bearing capacity of the crusher is improved; the high-speed rotating grinding head is designed to improve the efficiency of rock crushing; the hydraulic system with hydraulic station boosting function and boosting cylinder boosting function is designed to enhance the peak crushing force of the crusher. The technical solution is: A super-large diameter slurry shield anti-stagnation crushing system comprises a shell, a jaw plate and a hydraulic cylinder. The hydraulic cylinder is fixed in the shell and connected to the jaw plate. One end face of the jaw plate is provided with a plurality of hydraulic motors. The other end face of the jaw plate is provided with a plurality of tooth structures and a rotating grinding head. The rotating grinding head is connected to the hydraulic motor.

[0004] Preferably, the shell is of frame design, the upper and lower edges are arc-shaped, and guide rails are arranged on the left and right sides; the rotating grinding heads are slightly higher than the toothed structures, the number is an odd number, and they are evenly spaced.

[0005] Preferably, a multi-track toothed structure is provided at the bottom of the shell.

[0006] Preferably, hydraulic cylinders are provided at both ends of the housing, the movable shaft of each hydraulic cylinder is connected to the jaw plate, and each jaw plate is provided with a plurality of hydraulic motors on one end surface and a plurality of tooth structures and a rotating grinding head on the other end surface; The rotating grinding heads on the two jaw plates are distributed at intervals.

[0007] Preferably, the motion trajectory of the hydraulic cylinder on the jaw plate is the same as the moving direction of the jaw plate.

[0008] Preferably, it includes a hydraulic cylinder control system; the hydraulic control system includes a booster cylinder, a hydraulic cylinder, a switch valve and a one-way valve, the high-pressure port of the booster cylinder is respectively connected to the rodless chamber of the hydraulic cylinder and the first one-way valve; the rod chamber of the hydraulic cylinder is connected to the second one-way valve, the first one-way valve is connected to the B port of the first switch valve, the low-pressure port of the booster cylinder is connected to the A port of the first switch valve, the P port of the first switch valve and the second one-way valve are respectively connected to the A port and B port of the second switch valve; the P port of the second switch valve is connected to the oil source system, and its T port is connected to the oil tank; a displacement sensor is provided on the hydraulic cylinder.

[0009] Preferably, the hydraulic motor control system includes a hydraulic motor and a boosting cylinder; the hydraulic motor is connected to the high-pressure ports of the two boosting cylinders respectively, and the high-pressure port of each boosting cylinder is connected to the B port of the third switch valve and the fourth switch valve respectively through the third one-way valve and the fourth one-way valve, and its low-pressure port is connected to the A port of the third switch valve and the fourth switch valve, and the P port of the third switch valve and the fourth switch valve is connected to the A port and the B port of the fifth switch valve respectively; the P port of the fifth switch valve is connected to the oil source system, and the T port thereof is connected to the oil tank.

[0010] Preferably, the oil source system includes an electric motor, a high-pressure small-flow pump, a low-pressure large-flow pump, a safety valve and a cartridge valve; the electric motor is connected to the high-pressure small-flow pump and the low-pressure large-flow pump; the high-pressure small-flow pump is connected to the fifth one-way valve, the low-pressure large-flow pump is connected to the sixth one-way valve, the fifth one-way valve and the sixth one-way valve are connected to the safety valve, the low-pressure large-flow pump is connected to the cartridge valve, and the cartridge valve is connected to the oil tank; the sixth one-way valve is connected to the control oil circuit of the sixth switch valve, the A port of the sixth switch valve is connected to the cartridge valve through the first throttle valve, the P port of the sixth switch valve is connected to the low-pressure large-flow pump through the second throttle valve, and the T port of the sixth switch valve is connected to the oil tank through the third throttle valve.

[0011] Preferably, the hydraulic cylinder extends normally: the second switch valve works in the right position, the oil flows from the P port to the A port, the first switch valve works in the right position, the oil flows from the P port to the B port, and flows into the rodless cavity of the hydraulic cylinder through the first one-way valve, so that the piston rod of the hydraulic cylinder extends normally; when the oil circuit pressure on one side of the first one-way valve increases, the second one-way valve opens, and the oil flows back to the oil tank through the T port of the second switch valve; The hydraulic cylinder retracts normally: the second switch valve works in the left position, the oil flows from port P to port B, and flows into the rod chamber of the hydraulic cylinder through the second one-way valve, so that the hydraulic cylinder piston rod retracts normally; when the oil circuit pressure on one side of the second one-way valve increases, the first one-way valve opens, and the oil flows back to the oil tank through port T of the second switch valve.

[0012] Preferably, the rock breaking conditions are: Hydraulic cylinder high pressure extension: Initially, the motor drives the high pressure small flow pump and the low pressure large flow pump at the same time. If slag stagnation occurs, the oil circuit pressure increases, and the sixth switch valve works in the left position. At this time, the spring side of the cartridge valve is connected to the oil tank to achieve unloading, so that the cartridge valve is opened and the low pressure large flow pump is unloaded, so that the motor drives the high pressure small flow pump alone to increase the oil pressure; Strong rock breaking conditions: Ultra-high-pressure extension of the hydraulic cylinder: the displacement sensor determines the slag retention situation. When the load force needs to be further enhanced and the pressure automatically adjusted by the oil source is not enough to change the slag retention situation, the second switch valve works in the right position, and the oil flows from the P port to the A port on the basis of the motor driving the high-pressure and small-flow pump alone to enhance the oil pressure. The first switch valve works in the left position, and the oil flows from the P port to the A port. The oil flows into the low-pressure port of the booster cylinder. The pressure increase pushes the oil into the rodless cavity of the hydraulic cylinder, causing the hydraulic cylinder piston rod to be extended under ultra-high-pressure static loading. When the oil circuit pressure on one side of the first one-way valve increases, the second one-way valve opens, and the oil flows back to the oil tank through the T port of the second switch valve.

[0013] Compared with the prior art, the present invention has the following beneficial effects: 1. Overall frame design: The crusher adopts a frame structure. By setting an arc structure, the force on the crusher is more uniform, thereby improving the overall bearing capacity of the crusher.

[0014] 2. High-speed rotating grinding head: A high-speed rotating grinding head driven by a hydraulic motor is set on the jaw plate of the crusher to grind the stones, which helps to improve the crushing efficiency of the crusher for rocks.

[0015] 3. Hydraulic station booster system: The oil source is equipped with a high-pressure small-flow pump and a low-pressure large-flow pump. According to the slag situation, the operation of the pump is automatically adjusted through the pressure change of the oil source oil circuit to enhance the crushing force of the crusher.

[0016] 4. Booster cylinder booster system: An ultra-high pressure static loading system is set up in the hydraulic cylinder and hydraulic motor hydraulic control system of the crusher. When large rocks enter the crusher, the booster cylinder is started by controlling the two-position four-way switch valve to provide higher pressure for the hydraulic cylinder and hydraulic motor, further enhancing the crushing force of the crusher. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 This is the front view of the crusher scheme 1; Figure 2 This is a cross-sectional view of the crusher scheme 1; Figure 3 This is the isometric drawing of the crusher scheme. Figure 4 This is the front view of crusher scheme 2; Figure 5This is the isometric drawing of the first direction of the crusher scheme 2; Figure 6 This is the isometric drawing of the second direction of the crusher scheme 2; Figure 7 This is the hydraulic principle diagram of crusher scheme 1; Figure 8 This is the hydraulic principle diagram of the oil source system.

[0018] 1-housing, 2-jaw plate, 3-guide rail, 141-first hydraulic cylinder, 142-second hydraulic cylinder, 151-first hydraulic motor, 152-second hydraulic motor, 153-third hydraulic motor, 161-first high-speed rotating grinding head, 162-second high-speed rotating grinding head, 163-third high-speed rotating grinding head, 143-third hydraulic cylinder, 144-fourth hydraulic cylinder, 154-fourth hydraulic motor, 164-fourth high-speed rotating grinding head; 101 - first switch valve, 102 - second switch valve, 103 - third switch valve, 104 - fourth switch valve, 105 - fifth switch valve; 111 - sixth switch valve, 112 - seventh switch valve, 113 - eighth switch valve, 114 - ninth switch valve, 115 - tenth switch valve, 116 - eleventh switch valve, 117 - twelfth switch valve, 118 - thirteenth switch valve; 121-first hydraulically controlled one-way valve, 122-second hydraulically controlled one-way valve, 123-third hydraulically controlled one-way valve, 124-fourth hydraulically controlled one-way valve, 125-fifth hydraulically controlled one-way valve, 126-sixth hydraulically controlled one-way valve, 127-seventh hydraulically controlled one-way valve, 128-eighth hydraulically controlled one-way valve, 129-ninth hydraulically controlled one-way valve, 130-tenth hydraulically controlled one-way valve; 131 - first boost cylinder, 132 - second boost cylinder, 133 - third boost cylinder, 134 - fourth boost cylinder, 135 - fifth boost cylinder, 136 - sixth boost cylinder, 137 - seventh boost cylinder, 138 - eighth boost cylinder; 31-displacement sensor; 41-electric motor, 42-high-pressure small-flow pump, 43-low-pressure large-flow pump, 44-first one-way valve, 45-second one-way valve, 46-safety valve, 47-oil tank, 48-cartridge valve, 49-first throttle valve, 50-second throttle valve, 51-third throttle valve, 52-fourteenth switch valve. DETAILED DESCRIPTION

[0019] In order to facilitate understanding of the present application, the present application will be described more fully below with reference to the relevant drawings. Embodiments of the present application are provided in the drawings. However, the present application can be implemented in many different forms and is not limited to the embodiments described herein. On the contrary, the purpose of providing these embodiments is to make the disclosure of the present application more thorough and comprehensive.

[0020] An anti-slag crushing system for an ultra-large diameter slurry shield includes a shell 1, a jaw plate 2 and a hydraulic cylinder. The shell is a frame design with arc-shaped upper and lower edges and guide rails 3 on both sides. The rotating grinding heads are slightly higher than the tooth structures, with an odd number and evenly spaced distribution. The hydraulic cylinder is fixed in the shell and connected to the jaw plate. One end face of the jaw plate is provided with multiple hydraulic motors, and the other end face of the jaw plate is provided with multiple tooth structures and a rotating grinding head. The rotating grinding head is connected to the hydraulic motor. In Example 1, the bottom of the shell is provided with multiple tooth structures ( Figure 1-Figure 3 As shown). In Example 2, both ends of the housing are provided with hydraulic cylinders, and the movable shaft of each hydraulic cylinder is connected to the jaw plate. One end face of one of the jaw plates is provided with two hydraulic motors, and the other end face is provided with a multi-track tooth structure and a rotating grinding head; the other jaw plate is provided with a hydraulic motor; the rotating grinding heads on the two jaw plates are spaced apart ( Figure 4-Figure 6 as shown).

[0021] In Example 1, there are two hydraulic cylinders, namely the first hydraulic cylinder 141 and the second hydraulic cylinder 142, and three hydraulic motors, namely the first hydraulic motor 151, the second hydraulic motor 152, and the third hydraulic motor 153; there are three rotating grinding heads, namely the first high-speed rotating grinding head 161, the second high-speed rotating grinding head 162, and the third high-speed rotating grinding head 163.

[0022] The upper end of the jaw plate 2 is connected to the first hydraulic cylinder 141 and the second hydraulic cylinder 142, and a plurality of tooth structures are arranged at the lower end to crush rocks.

[0023] The jaw plate 2 is respectively provided with a first high-speed rotating grinding head 161 driven by the first hydraulic motor 151 , a second high-speed rotating grinding head 162 driven by the second hydraulic motor 152 , and a third high-speed rotating grinding head 163 driven by the third hydraulic motor 153 .

[0024] In the second embodiment, one end surface of one of the jaw plates is provided with two hydraulic motors (respectively, a second hydraulic motor 152 and a third hydraulic motor 153); the other jaw plate is provided with a hydraulic motor (respectively, a fourth hydraulic motor 154, which drives a fourth high-speed rotating grinding head 164.

[0025] The one-way valves in the hydraulic cylinder control system and the hydraulic motor hydraulic control system use hydraulically controlled one-way valves.

[0026] Hydraulic cylinder hydraulic control system: The hydraulic control system of the first hydraulic cylinder 141, the oil source is connected to the P port of the first switch valve 101, the A port of the first switch valve 101 is connected to the P port of the sixth switch valve 111, the B port of the first switch valve 101 is connected to the second hydraulic control check valve 122; the B port of the sixth switch valve 111 is connected to the first hydraulic control check valve 121, the A port of the sixth switch valve 111 is connected to the low pressure port of the first booster cylinder 131, and the high pressure port of the first booster cylinder 131 is connected to the rodless chamber of the hydraulic cylinder and the first hydraulic control check valve 121. The rod chamber of the hydraulic cylinder is connected to the second hydraulic control check valve 122. The displacement sensor 31 is located on the first hydraulic cylinder 141.

[0027] The hydraulic control system of the second hydraulic cylinder 142 has an oil source connected to the P port of the second switch valve 102, the A port of the second switch valve 102 is connected to the P port of the seventh switch valve 112, and the B port of the second switch valve 102 is connected to the fourth hydraulically controlled one-way valve 124; the B port of the seventh switch valve 112 is connected to the third hydraulically controlled one-way valve 123, the A port of the seventh switch valve 112 is connected to the low-pressure port of the second booster cylinder 132, and the high-pressure port of the second booster cylinder 132 is connected to the rodless chamber of the hydraulic cylinder and the third hydraulically controlled one-way valve 123. The rod chamber of the hydraulic cylinder is connected to the fourth hydraulically controlled one-way valve 124.

[0028] Hydraulic motor hydraulic control system: The hydraulic control system of the first hydraulic motor 151 and the oil source system are connected to the P port of the third switch valve 103, the A port of the third switch valve 103 is connected to the P port of the eighth switch valve 113, and the B port of the third switch valve 103 is connected to the P port of the ninth switch valve 114; the A port of the eighth switch valve 113 and the ninth switch valve 114 are connected to the low-pressure port of the third boosting cylinder 133 and the fourth boosting cylinder 134, and the high-pressure port of the third boosting cylinder 133 and the fourth boosting cylinder 134 are connected to both ends of the first hydraulic motor and the fifth hydraulically controlled one-way valve 125 and the sixth hydraulically controlled one-way valve 126.

[0029] The hydraulic control system of the second hydraulic motor 151 and the oil source system are connected to the P port of the fourth switch valve 104, the A port of the fourth switch valve 104 is connected to the P port of the tenth switch valve 115, and the B port of the fourth switch valve 104 is connected to the P port of the eleventh switch valve 116; the A port of the tenth switch valve 115 and the eleventh switch valve 116 are connected to the low-pressure port of the fifth booster cylinder 135 and the sixth booster cylinder 136, and the high-pressure port of the fifth booster cylinder 135 and the sixth booster cylinder 136 are connected to both ends of the second hydraulic motor and the seventh hydraulic-controlled one-way valve 127 and the eighth hydraulic-controlled one-way valve 128.

[0030] The hydraulic control system of the third hydraulic motor 153, the oil source system is connected to the P port of the fifth switch valve 105, the A port of the fifth switch valve 105 is connected to the P port of the twelfth switch valve 117, and the B port of the fifth switch valve 105 is connected to the P port of the thirteenth switch valve 118; the A ports of the twelfth switch valve 117 and the thirteenth switch valve 118 are connected to the low-pressure ports of the seventh booster cylinder 137 and the eighth booster cylinder 138, and the high-pressure ports of the seventh booster cylinder 137 and the eighth booster cylinder 138 are connected to both ends of the third hydraulic motor and the ninth hydraulically controlled one-way valve 129 and the tenth hydraulically controlled one-way valve 130.

[0031] Oil source system: The motor 41 is connected to the high-pressure small-flow pump 42 and the low-pressure large-flow pump 43, the high-pressure small-flow pump 42 is connected to the first one-way valve 44, the low-pressure large-flow pump 43 is connected to the second one-way valve 45, the first one-way valve 44 and the second one-way valve 45 are connected to the safety valve 46, the low-pressure large-flow pump 43 is connected to the cartridge valve 48, and the cartridge valve 48 is connected to the oil tank 47. The second one-way valve 45 is connected to the control oil circuit of the fourteenth switch valve 52, the A port of the fourteenth switch valve 52 is connected to the cartridge valve 48 through the first throttle valve 49, the P port of the fourteenth switch valve 52 is connected to the low-pressure large-flow pump 43 through the third throttle valve 51, and the T port of the fourteenth switch valve 52 is connected to the oil tank 47 through the second throttle valve 50.

[0032] Normal situation: The first hydraulic cylinder A141 extends normally: the first switch valve 101 works in the right position, the oil flows from the P port to the A port, the sixth switch valve 111 works in the right position, the oil flows from the P port to the B port, and flows into the rodless cavity of the hydraulic cylinder through the first hydraulic control check valve 121, so that the hydraulic cylinder piston rod extends normally. When the oil pressure on one side of the first hydraulic control check valve 121 increases, the second hydraulic control check valve 122 opens, and the oil flows back to the oil tank through the T port of the first switch valve 101.

[0033] The first hydraulic cylinder A141 retracts normally: the first switch valve 101 works in the left position, the oil flows from the P port to the B port, and flows into the rod chamber of the hydraulic cylinder through the second hydraulic control check valve 122, so that the hydraulic cylinder piston rod retracts normally. When the oil circuit pressure on one side of the second hydraulic control check valve 122 increases, the first hydraulic control check valve 121 opens, and the oil flows back to the oil tank through the T port of the first switch valve 101.

[0034] Rock breaking situation: The first hydraulic cylinder 141 extends at high pressure (the oil source is automatically adjusted): initially, the motor 41 drives the high-pressure small-flow pump 42 and the low-pressure large-flow pump 43 at the same time. If slag stagnation occurs, the oil circuit pressure increases, and the fourteenth switch valve 52 automatically works in the left position. At this time, the spring side of the cartridge valve 48 is connected to the oil tank to achieve unloading, so that the cartridge valve 48 opens and the low-pressure large-flow pump 43 is unloaded, so that the motor 41 drives the high-pressure small-flow pump 42 alone to enhance the oil pressure.

[0035] Strong rock breaking: The first hydraulic cylinder 141 extends at ultra-high pressure: The displacement sensor 31 determines the slag stagnation situation. When the load force needs to be further enhanced and the pressure of the oil source automatically adjusted is still insufficient to change the slag stagnation situation, the first switch valve 101 works in the right position, and the oil flows from the P port to the A port. The sixth switch valve 111 works in the left position, and the oil flows from the P port to the A port. The oil flows into the low-pressure port of the first booster cylinder 131. The pressure increase pushes the oil into the rodless cavity of the first hydraulic cylinder 141, so that the hydraulic cylinder piston rod extends at ultra-high pressure static loading. When the oil circuit pressure on one side of the first hydraulic control one-way valve 121 increases, the second hydraulic control one-way valve 122 opens, and the oil flows back to the oil tank through the T port of the first switch valve 101.

[0036] The control principles of the hydraulic cylinder hydraulic control, hydraulic motor hydraulic control and oil source system in Example 2 are the same as those in Example 1 and are not counted here.

[0037] The above description of the disclosed embodiments enables one skilled in the art to implement or use the present invention. Various modifications to these embodiments will be apparent to one skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the present invention. Therefore, the present invention will not be limited to the embodiments shown herein, but rather to the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. An anti-slag crushing system for an ultra-large diameter slurry shield, characterized in that: It includes a shell, a jaw plate and a hydraulic cylinder. The hydraulic cylinder is fixed in the shell and connected to the jaw plate. One end face of the jaw plate is provided with multiple hydraulic motors. The other end face of the jaw plate is provided with multiple tooth structures and a rotating grinding head. The rotating grinding head is connected to the hydraulic motor.

2. The anti-slag crushing system for the super-large diameter slurry shield according to claim 1 is characterized in that: The shell is of frame design, with arc-shaped upper and lower edges and guide rails on the left and right sides; the rotating grinding heads are slightly higher than the toothed structures, with an odd number and evenly spaced distribution.

3. The anti-slag crushing system for the super-large diameter slurry shield according to claim 1 is characterized in that: The bottom of the shell is provided with a plurality of tooth-shaped structures.

4. The anti-slag crushing system for the super-large diameter slurry shield according to claim 1 is characterized in that: Both ends of the housing are provided with hydraulic cylinders, the movable shaft of each hydraulic cylinder is connected to the jaw plate, one end surface of each jaw plate is provided with multiple hydraulic motors, and the other end surface is provided with multiple tooth structures and a rotating grinding head; The rotating grinding heads on the two jaw plates are distributed at intervals.

5. The anti-slag crushing system for a super-large diameter slurry shield according to any one of claims 1 to 4, characterized in that: The motion track of the hydraulic cylinder on the jaw plate is the same as the moving direction of the jaw plate.

6. The anti-slag crushing system for a super-large diameter slurry shield according to any one of claims 1 to 3, characterized in that: It includes a hydraulic cylinder control system; the hydraulic control system includes a booster cylinder, a hydraulic cylinder, a switch valve and a one-way valve, the high-pressure port of the booster cylinder is respectively connected to the rodless chamber of the hydraulic cylinder and the first one-way valve; the rod chamber of the hydraulic cylinder is connected to the second one-way valve, the first one-way valve is connected to the B port of the first switch valve, the low-pressure port of the booster cylinder is connected to the A port of the first switch valve, the P port of the first switch valve and the second one-way valve are respectively connected to the A port and the B port of the second switch valve; the P port of the second switch valve is connected to the oil source system, and its T port is connected to the oil tank; a displacement sensor is provided on the hydraulic cylinder.

7. The anti-slag crushing system for the super-large diameter slurry shield according to claim 6 is characterized in that: The hydraulic motor control system includes a hydraulic motor and a booster cylinder; the hydraulic motor is connected to the high-pressure ports of the two booster cylinders respectively, and the high-pressure port of each booster cylinder is connected to the B port of the third switch valve and the fourth switch valve respectively through the third one-way valve and the fourth one-way valve, and its low-pressure port is connected to the A port of the third switch valve and the fourth switch valve, and the P port of the third switch valve and the fourth switch valve is connected to the A port and the B port of the fifth switch valve respectively; the P port of the fifth switch valve is connected to the oil source system, and the T port is connected to the oil tank.

8. The anti-slag crushing system for the super-large diameter slurry shield according to claim 7 is characterized in that: The oil source system includes an electric motor, a high-pressure small-flow pump, a low-pressure large-flow pump, a safety valve and a cartridge valve; the electric motor is connected to the high-pressure small-flow pump and the low-pressure large-flow pump; the high-pressure small-flow pump is connected to the fifth one-way valve, the low-pressure large-flow pump is connected to the sixth one-way valve, the fifth one-way valve and the sixth one-way valve are connected to the safety valve, the low-pressure large-flow pump is connected to the cartridge valve, and the cartridge valve is connected to the oil tank; the sixth one-way valve is connected to the control oil circuit of the sixth switch valve, the A port of the sixth switch valve is connected to the cartridge valve through the first throttle valve, the P port of the sixth switch valve is connected to the low-pressure large-flow pump through the second throttle valve, and the T port of the sixth switch valve is connected to the oil tank through the third throttle valve.

9. The anti-slag crushing system for the super-large diameter slurry shield according to claim 8 is characterized in that: The hydraulic cylinder extends normally: the second switch valve works in the right position, the oil flows from the P port to the A port, the first switch valve works in the right position, the oil flows from the P port to the B port, and flows into the rodless chamber of the hydraulic cylinder through the first check valve, so that the hydraulic cylinder piston rod extends normally; when the oil circuit pressure on one side of the first check valve increases, the second check valve opens, and the oil flows back to the oil tank through the T port of the second switch valve; The hydraulic cylinder retracts normally: the second switch valve works in the left position, the oil flows from port P to port B, and flows into the rod chamber of the hydraulic cylinder through the second one-way valve, so that the hydraulic cylinder piston rod retracts normally; when the oil circuit pressure on one side of the second one-way valve increases, the first one-way valve opens, and the oil flows back to the oil tank through port T of the second switch valve.

10. The anti-slag crushing system for the super-large diameter slurry shield according to claim 8, characterized in that: Rock breaking conditions include: Hydraulic cylinder high pressure extension: Initially, the motor drives the high pressure small flow pump and the low pressure large flow pump at the same time. If slag stagnation occurs, the oil circuit pressure increases, and the sixth switch valve works in the left position. At this time, the spring side of the cartridge valve is connected to the oil tank to achieve unloading, so that the cartridge valve is opened and the low pressure large flow pump is unloaded, so that the motor drives the high pressure small flow pump alone to increase the oil pressure; Strong rock breaking conditions: Ultra-high-pressure extension of the hydraulic cylinder: the displacement sensor determines the slag retention situation. When the load force needs to be further enhanced and the pressure automatically adjusted by the oil source is not enough to change the slag retention situation, the second switch valve works in the right position, and the oil flows from the P port to the A port on the basis of the motor driving the high-pressure and small-flow pump alone to enhance the oil pressure. The first switch valve works in the left position, and the oil flows from the P port to the A port. The oil flows into the low-pressure port of the booster cylinder. The pressure increase pushes the oil into the rodless cavity of the hydraulic cylinder, causing the hydraulic cylinder piston rod to be extended under ultra-high-pressure static loading. When the oil circuit pressure on one side of the first one-way valve increases, the second one-way valve opens, and the oil flows back to the oil tank through the T port of the second switch valve.

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