CN112814692A - Shield machine and posture deviation rectifying system thereof - Google Patents
Shield machine and posture deviation rectifying system thereof Download PDFInfo
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- CN112814692A CN112814692A CN202110068463.1A CN202110068463A CN112814692A CN 112814692 A CN112814692 A CN 112814692A CN 202110068463 A CN202110068463 A CN 202110068463A CN 112814692 A CN112814692 A CN 112814692A
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- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21D—SHAFTS; TUNNELS; GALLERIES; LARGE UNDERGROUND CHAMBERS
- E21D9/00—Tunnels or galleries, with or without linings; Methods or apparatus for making thereof; Layout of tunnels or galleries
- E21D9/06—Making by using a driving shield, i.e. advanced by pushing means bearing against the already placed lining
- E21D9/093—Control of the driving shield, e.g. of the hydraulic advancing cylinders
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- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21D—SHAFTS; TUNNELS; GALLERIES; LARGE UNDERGROUND CHAMBERS
- E21D9/00—Tunnels or galleries, with or without linings; Methods or apparatus for making thereof; Layout of tunnels or galleries
- E21D9/06—Making by using a driving shield, i.e. advanced by pushing means bearing against the already placed lining
- E21D9/0621—Shield advancing devices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/027—Check valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
- F15B13/0426—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with fluid-operated pilot valves, i.e. multiple stage valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
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- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Environmental & Geological Engineering (AREA)
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- General Life Sciences & Earth Sciences (AREA)
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Abstract
The invention belongs to the technical field of shield tunneling machines, and particularly relates to a shield tunneling machine and an attitude deviation rectifying system thereof. The posture correction system comprises a high-pressure oil cylinder, a boosting oil cylinder, a first logic valve, a second logic valve, a pilot valve, a reversing valve and an oil return tank, wherein the movement direction of the double-acting boosting oil cylinder is controlled through a hydraulic control reversing valve, pilot oil is provided for the hydraulic control reversing valve through the pilot valve to enable the hydraulic control reversing valve to reverse, control oil is provided for the pilot valve through the logic valve to enable the pilot valve to reverse, the double-acting boosting cylinder can be automatically reversed through pure hydraulic control, the purpose that high-pressure oil is continuously output through a small device is achieved, enough power is provided after the shield tunneling machine is planted, the shield tunneling machine is lifted, and reliable work of the shield tunneling machine is guaranteed. The device does not need electrical control and is convenient to realize on a construction site.
Description
Technical Field
The invention belongs to the technical field of shield tunneling machines, and particularly relates to a shield tunneling machine and an attitude deviation rectifying system thereof.
Background
The shield machine as equipment for large tunnel construction becomes the requirement of the development of domestic and even world tunnel engineering, and aims at the problem that the shield machine is frequently planted in the construction process of extremely-muddy strata or hard-upper and soft-lower strata. The shield machine can deviate from the original tunneling route due to the head planting, the construction safety cannot be guaranteed, construction accidents can be caused in the serious case, and after the shield machine plants the head, the thrust generated by the original thrust oil cylinder is not enough to enable the shield to raise the head.
Disclosure of Invention
The invention provides a shield machine and an attitude deviation rectifying system thereof, which are used for solving the problem that the shield machine deviates from an original tunneling route due to the fact that the shield machine is broken because of insufficient thrust generated by an oil cylinder in the prior art.
In order to solve the technical problems, the technical scheme and the corresponding beneficial effects of the technical scheme are as follows:
the invention provides a shield machine posture correcting system which comprises a high-pressure oil cylinder, a booster oil cylinder, a first logic valve, a second logic valve, a pilot valve, a reversing valve and an oil return tank, wherein the booster oil cylinder is arranged on the high-pressure oil cylinder;
the boosting oil cylinder comprises a cylinder body, and a first piston, a second piston and a third piston which are assembled in the cylinder body in a sliding manner, wherein a first high-pressure cavity, a first boosting cavity, a second boosting cavity and a second high-pressure cavity are respectively formed between the cylinder body and the first piston, between the first piston and the second piston, between the second piston and the third piston and between the third piston and the cylinder body; the first piston is connected with the second piston through a first connecting rod, and the second piston is connected with the third piston through a second connecting rod; the first piston is provided with a first force application surface and is used for applying pressure to hydraulic oil in the first high-pressure cavity; the second piston is provided with a first stress surface and a second stress surface which are respectively used for being pressurized by hydraulic oil in the first pressurizing cavity and the second pressurizing cavity; the third piston is provided with a second force application surface and is used for applying pressure to the hydraulic oil in the second high-pressure cavity; the area of the first force bearing surface is larger than that of the second force application surface, and the area of the second force bearing surface is larger than that of the first force application surface; the first high-pressure cavity and the second high-pressure cavity are both connected with an oil inlet of the high-pressure oil cylinder;
the reversing valve has a left working state and a right working state; the left working state of the reversing valve is used for communicating the hydraulic pump station with the first pressurizing cavity and communicating the second pressurizing cavity with the oil return tank; the right working state is used for communicating the hydraulic pump station with the second pressurizing cavity and communicating the first pressurizing cavity with the oil return tank;
the pilot valve has a left working state and a right working state; the left working state of the pilot valve is used for communicating the hydraulic pump station with a left control oil port of the reversing valve and communicating a right control oil port of the reversing valve with an oil return tank; the right working state of the pilot valve is used for communicating a left control oil port of the reversing valve with the oil return tank and communicating an oil port of the hydraulic pump station with a right control oil port of the reversing valve;
the first logic valve comprises a first oil inlet, a first oil outlet and a third control oil port; the first oil outlet is connected to a left control oil port of the pilot valve, and the first control oil port is connected to the first pressurizing cavity; when the second piston moves to the left limit position of the second piston, the first oil inlet is connected to the second pressurizing cavity, and the first oil inlet is connected to the first pressurizing cavity in the rest state;
the second logic valve comprises a second oil inlet, a second oil outlet and a second control oil port; the second oil outlet is connected to a right control oil port of the pilot valve, and the second control oil port is connected to the second pressurizing cavity; when the second piston moves to the right limit position of the second piston, the second oil inlet is connected to the first pressurizing cavity, and the second oil inlet is connected to the second pressurizing cavity in the other states; wherein the first piston is located to the left of the second piston.
The beneficial effects of the above technical scheme are: the movement direction of the double-acting pressurization oil cylinder is controlled by the hydraulic control reversing valve, pilot oil is provided for the hydraulic control reversing valve by the pilot valve to reverse the hydraulic control reversing valve, control oil is provided for the pilot valve by the logic valve to reverse the pilot valve, the double-acting pressurization oil cylinder can be automatically reversed by pure hydraulic control, high-pressure oil can be continuously output by a small device, sufficient power is provided after the shield machine is planted, the shield machine is lifted, and reliable work of the shield machine is guaranteed. The device does not need electrical control and is convenient to realize on a construction site.
Furthermore, in order to output continuously adjustable high-pressure oil, the deviation correcting system further comprises a pressure reducing valve which is arranged on an oil way connected with an oil port of the hydraulic pump station.
Furthermore, in order to adjust the oil inlet flow to control the propelling speed of the high-pressure oil cylinder, the deviation correcting system further comprises a speed regulating valve which is arranged on an oil path connected with an oil port of the hydraulic pump station.
Furthermore, in order to prevent oil in the high-pressure oil cylinder from flowing back, the deviation correcting system further comprises a first one-way valve which is arranged on an oil path between the first high-pressure cavity and the high-pressure oil cylinder, so that high-pressure oil can only enter the high-pressure oil cylinder from the first high-pressure cavity.
Furthermore, in order to prevent oil in the high-pressure oil cylinder from flowing back, the deviation correcting system further comprises a fourth one-way valve which is arranged on an oil path between the second high-pressure cavity and the high-pressure oil cylinder, so that high-pressure oil can only enter the high-pressure oil cylinder from the fourth high-pressure cavity.
Furthermore, in order to prevent the first high-pressure cavity from being sucked empty, the deviation correcting system further comprises a second one-way valve which is arranged on an oil path between the first high-pressure cavity and the first pressurizing cavity, so that hydraulic oil can only enter the first high-pressure cavity from the first pressurizing cavity.
Furthermore, in order to prevent the second high-pressure cavity from being sucked empty, the deviation correcting system further comprises a third one-way valve which is arranged on an oil path between the second high-pressure cavity and the second pressurizing cavity, so that hydraulic oil can only enter the second high-pressure cavity from the second pressurizing cavity.
Further, the reversing valve is a two-position four-way valve.
Further, the pilot valve is a two-position four-way valve.
The invention also provides a shield machine, which comprises a shield machine body and the shield machine posture correction system, wherein the shield machine body comprises a hydraulic pump station and can achieve the same technical effect as the shield machine posture correction system.
Drawings
FIG. 1 is a structural diagram of a shield tunneling machine attitude deviation rectifying system of the present invention;
the hydraulic control system comprises a hydraulic pump station 1, a pressure reducing valve 2, a speed regulating valve 3, a hydraulic control reversing valve 4, a pilot valve 5, a first logic valve 6.1, a second logic valve 6.2, a double-acting pressurization oil cylinder 7, a first check valve 8.1, a second check valve 8.2, a first check valve 8.3, a fourth check valve 8.4, a high-pressure oil cylinder 9, a first piston 18.1, a second piston 18.2 and a third piston 18.3.
Detailed Description
The overall concept of the invention is as follows: the double-acting booster oil cylinder is matched with some hydraulic control valves to realize that the low-pressure oil source outputs high-pressure oil, and the output high-pressure oil is connected to the high-pressure oil cylinder arranged at the bottom of the shield machine so as to improve the thrust at the bottom of the shield machine and change the tunneling posture of the shield machine. Based on the above, the invention provides a shield machine and a shield machine posture rectification system, which are described in detail below with reference to the accompanying drawings and embodiments.
The embodiment of the shield machine comprises:
the embodiment of the invention discloses a shield machine, which comprises a shield machine body and a shield machine deviation rectifying system, wherein the shield machine body comprises a hydraulic pump station 1, and the structure of the shield machine deviation rectifying system is shown in figure 1 and comprises a pressure reducing valve 2, a speed regulating valve 3, a hydraulic control reversing valve 4, a pilot valve 5, a first logic valve 6.1, a second logic valve 6.2, a double-acting pressurizing oil cylinder 7, a first check valve 8.1, a second check valve 8.2, a third check valve 8.3, a fourth check valve 8.4 and a high-pressure oil cylinder 9.
The double-acting pressurization oil cylinder 7 comprises a cylinder body, a first piston 18.1, a second piston 18.2 and a third piston 18.3 which are assembled in the cylinder body in a sliding mode, a first high-pressure cavity J, a first pressurization cavity K, a second pressurization cavity L and a second high-pressure cavity M are formed between the cylinder body and the first piston 18.1, between the first piston 18.1 and the second piston 18.2, between the second piston 18.2 and the third piston 18.3 and between the third piston 18.3 and the cylinder body respectively, the first piston and the second piston are connected through a first connecting rod, and the second piston and the third piston are connected through a second connecting rod. The first piston is provided with a first force application surface and is used for applying pressure to hydraulic oil in the first high-pressure cavity J cavity; the second piston is provided with a first stress surface and a second stress surface which are respectively used for being pressurized by hydraulic oil in the first pressurizing cavity K cavity and the second pressurizing cavity L cavity; the third piston is provided with a second force application surface and is used for applying pressure to hydraulic oil in the second high-pressure cavity M; the area of the first force bearing surface is larger than that of the second force application surface, and the area of the second force bearing surface is larger than that of the first force application surface. Moreover, the first high-pressure cavity J cavity is connected to the HP port of the high-pressure oil cylinder 9 through a first check valve 8.1, and the second high-pressure cavity M cavity is connected to the HP port of the high-pressure oil cylinder 9 through a fourth check valve 8.4; the first pressurizing cavity K is connected to the first high-pressure cavity J through a port D1 of the double-acting pressurizing oil cylinder, a second one-way valve 8.2 and a port C1 of the double-acting pressurizing oil cylinder, so that hydraulic oil can only enter the first high-pressure cavity J from the first pressurizing cavity K; the second pressurization cavity L cavity is connected to the second high-pressure cavity M cavity through a D2 well third one-way valve 8.3 of the double-acting pressurization oil cylinder and a C2 port of the double-acting pressurization oil cylinder, so that hydraulic oil can only enter the second high-pressure cavity M cavity from the second pressurization cavity L cavity. The first high-pressure cavity J cavity is also connected to the high-pressure oil cylinder 9 through an HP1 port of the double-acting pressurization oil cylinder 7 through a first check valve 8.1, and the second high-pressure cavity M cavity is also connected to the high-pressure oil cylinder 9 through an HP2 port of the double-acting pressurization oil cylinder 7 through a fourth check valve 8.4.
The hydraulic control reversing valve 4 comprises four oil ports, namely a P1 port, an A1 port, a B1 port and a T1 port. The hydraulic control reversing valve 4 has two working states, the first working state is a left working state in which a P1 port is communicated with an A1 port, and a B1 port is communicated with a T1 port, so that the oil port P of a hydraulic pump station is communicated with a first pressurizing cavity K after sequentially passing through a reducing valve 2 and a speed regulating valve 3, and a second pressurizing cavity L is communicated with an oil return tank R; the second is a right working state that the port P1 is communicated with the port B1, and the port A1 is communicated with the port T1, so that the port P of the hydraulic pump station is communicated with the L cavity of the second pressure increasing cavity and the K cavity of the first pressure increasing cavity is communicated with the R box of the oil return tank after sequentially passing through the pressure reducing valve 2 and the speed regulating valve 3.
The pilot valve 5 comprises four oil ports, namely a port P2, a port A2, a port B2 and a port T2. The pilot valve 5 has two working states, the first one is a left working state with a P1 port communicated with an A2 port and a B2 port communicated with a T2 port, so that an oil port P of a hydraulic pump station is communicated with a left control oil port of the hydraulic control reversing valve 4 after sequentially passing through the reducing valve 2 and the speed regulating valve 3, and a right control oil port of the hydraulic control reversing valve 4 is communicated with an oil return tank R; the second is a right working state that the port A2 is communicated with the port T2, and the port P2 is communicated with the port B2, so that a left control oil port of the hydraulic control reversing valve 4 is communicated with an oil return tank R tank, and an oil port P of a hydraulic pump station is communicated with a right control oil port of the hydraulic control reversing valve 4 after sequentially passing through the pressure reducing valve 2 and the speed regulating valve 3.
The first logic valve 6.1 comprises three oil ports which are respectively a first oil inlet, a first oil outlet and a third control oil port, the first oil outlet is connected to a left control oil port of the pilot valve 5, and the first control oil port is connected to a first pressurizing cavity K cavity through a Y1 port of the double-acting pressurizing oil cylinder; when the second piston moves to the left limit position of the second piston, the first oil inlet is connected to the second pressurizing cavity L cavity through an X1 port of the pressurizing oil cylinder, and is connected to the first pressurizing cavity K cavity through an X1 port of the pressurizing oil cylinder in the rest states. The X1 port and the Y1 port are located at different positions of the double-acting boost cylinder, and the state of the second piston in fig. 1 is the "rest state" described herein.
The second logic valve 6.2 comprises three oil ports which are respectively a second oil inlet, a second oil outlet and a second control oil port, the second oil outlet is connected to a right control oil port of the pilot valve 5, and the second control oil port is connected to a second pressurizing cavity L cavity through a Y2 port of the double-acting pressurizing oil cylinder; when the second piston moves to the right limit, the second oil inlet is connected to the first pressurizing intensity K cavity through an X2 port of the pressurizing oil cylinder, and is connected to the second pressurizing cavity L cavity through an X1 port of the pressurizing oil cylinder in other states. The state of the second piston in fig. 1 is the "rest state" described herein. And moreover, the pressure reducing valve 2 arranged on an oil path connected with an oil port P of the hydraulic pump station can realize continuous adjustment of output high pressure, and the speed regulating valve 3 can regulate the oil inlet flow by regulating the size of the oil port of the speed regulating valve 3, so that the propelling speed of the high-pressure oil cylinder is controlled. The high-pressure oil cylinder is arranged at the bottom of the shield machine body to improve the thrust at the bottom of the shield machine, so that the tunneling posture of the shield machine is changed.
The working process of the correction system of the shield tunneling machine introduced above is as follows:
the low-pressure oil of the hydraulic pump station 1 is introduced from a port P, the hydraulic control reversing valve 4 and the pilot valve 5 work in a left position, the low-pressure oil is decompressed by the decompression valve 2, speed is regulated by the speed regulating valve 3, and then enters a port Y1 of the double-acting pressurizing oil cylinder 7 through the hydraulic control reversing valve 4, so that three pistons of the double-acting pressurizing oil cylinder 7 are pushed to move rightwards; when the second piston of the double-acting pressurizing oil cylinder 7 moves to the rightmost side, the port X2 is connected with the first pressurizing intensity K cavity, high-pressure oil is introduced into the high-pressure oil inlet of the port X2 to be guided to the left side of the second logic valve 6.2 (an oil inlet of the second logic valve 6.2), the port Y2 is connected to the L cavity of the second pressurizing cavity, low-pressure oil is introduced into the low-pressure oil inlet of the port Y2 to be guided to the right side of the second logic valve 6.2 (a control oil inlet of the second logic valve 6.2), the left side force of the second logic valve 6.2 is larger than the right side force, and the left side of the second logic valve 6.2 works; the hydraulic oil with the X2 port is led to the right side of the pilot valve 5 (a right control port of the pilot valve 5) through the second logic valve 6.2, and the pilot valve 5 is changed to work towards the right; the pilot oil is led to the right side of the hydraulic control reversing valve 4 through the pilot valve 5, the hydraulic control reversing valve 4 is shifted to the right to work, the hydraulic oil of the port P is led to the port Y2 of the double-acting pressurizing oil cylinder 7 through the right of the hydraulic control reversing valve 4, and three pistons of the double-acting pressurizing oil cylinder 7 are pushed to move left; when the second piston of the double-acting pressurizing oil cylinder 7 moves to the leftmost side, the port X1 is connected to the L cavity of the second pressurizing cavity, high-pressure oil is introduced, high-pressure oil of the port X1 is introduced to the right side of the first logic valve 6.1 (an oil inlet of the first logic valve 6.1), the port Y1 is connected to the K cavity of the first pressurizing cavity, low-pressure oil is introduced, low-pressure oil of the port Y1 is introduced to the left side of the first logic valve 6.1 (a control oil port of the logic valve 6.1), the right side force of the first logic valve 6.1 is greater than the left side force, and the right position of the first logic valve 6.1 works; the hydraulic oil with the X1 port is led to the left side of the pilot valve 5 (a left control oil port of the pilot valve 5) through the first logic valve 6.1, and the pilot valve 5 reverses the left operation; the pilot oil is led to the left side of the hydraulic control reversing valve 4 through the pilot valve 5, the hydraulic control reversing valve 4 reverses the left position to work, and the hydraulic oil of the port P is led to the port Y1 of the double-acting pressurization oil cylinder 7 through the left position of the hydraulic control reversing valve 4. And circulating, continuously changing the movement direction of the double-acting pressurizing oil cylinder 7, continuously outputting high-pressure oil, and inputting the high-pressure oil into the high-pressure oil cylinder 9 through the HP port.
Moreover, when the piston in the double-acting pressurizing cylinder 7 moves towards the right side, the high-pressure oil in the cavity M of the second high-pressure chamber reaches the high-pressure output port HP through the port HP2 via the fourth check valve 8.4, the first check valve 8.1 can prevent the high-pressure oil from entering the cavity J of the first high-pressure chamber of the double-acting pressurizing cylinder 7, the hydraulic oil in the cavity K of the first pressurizing chamber can enter the cavity J of the first high-pressure chamber of the double-acting pressurizing cylinder 7 via the port D1 via the port second check valve 8.2 and the port C1, and the cavity J of the first high-pressure chamber of the double-acting pressurizing cylinder 7 is prevented from being emptied; the third one-way valve 8.3 can prevent high-pressure oil from entering a second pressurizing cavity of the double-acting pressurizing oil cylinder 7 through a port C2; similarly, when the piston in the double-acting pressurization cylinder 7 moves to the left, the high-pressure oil in the J cavity of the first high-pressure cavity reaches the high-pressure output port HP through the HP1 port via the first check valve 8.1, the fourth check valve 8.4 can prevent the high-pressure oil from entering the M cavity of the second high-pressure cavity of the double-acting pressurization cylinder 7, the hydraulic oil in the L cavity of the second pressurization cavity can enter the M cavity of the second high-pressure cavity of the double-acting pressurization cylinder 7 via the D2 port via the third check valve 8.3 and the C2 port, so as to prevent the M cavity of the second high-pressure cavity of the double-acting pressurization cylinder 7 from being empty, and the second check valve 8.2 can prevent the high-pressure oil from entering the K cavity of the first pressurization cavity of the double-acting pressurization cylinder 7 via the C1 port.
The invention controls the movement direction of the double-acting pressurizing oil cylinder through the hydraulic control reversing valve, provides pilot oil for the hydraulic control reversing valve through the pilot valve to reverse the hydraulic control reversing valve, provides control oil for the pilot valve through the logic valve to reverse the pilot valve, does not need electric control, can automatically reverse the double-acting pressurizing oil cylinder through pure hydraulic control, realizes continuous output of high-pressure oil by a smaller device, and is convenient to realize on a construction site.
The embodiment of the deviation correcting system comprises:
the embodiment of the posture correction system of the shield machine, disclosed by the invention, has the same specific content as the posture correction system of the shield machine introduced in the embodiment of the shield machine, and the structure of the posture correction system is shown in figure 1. Since the shield machine attitude deviation rectifying system is described in detail in the shield machine embodiment, it is not described herein again.
Claims (10)
1. A shield machine posture correction system is characterized by comprising a high-pressure oil cylinder, a booster oil cylinder, a first logic valve, a second logic valve, a pilot valve, a reversing valve and an oil return tank;
the boosting oil cylinder comprises a cylinder body, and a first piston, a second piston and a third piston which are assembled in the cylinder body in a sliding manner, wherein a first high-pressure cavity, a first boosting cavity, a second boosting cavity and a second high-pressure cavity are respectively formed between the cylinder body and the first piston, between the first piston and the second piston, between the second piston and the third piston and between the third piston and the cylinder body; the first piston is connected with the second piston through a first connecting rod, and the second piston is connected with the third piston through a second connecting rod; the first piston is provided with a first force application surface and is used for applying pressure to hydraulic oil in the first high-pressure cavity; the second piston is provided with a first stress surface and a second stress surface which are respectively used for being pressurized by hydraulic oil in the first pressurizing cavity and the second pressurizing cavity; the third piston is provided with a second force application surface and is used for applying pressure to the hydraulic oil in the second high-pressure cavity; the area of the first force bearing surface is larger than that of the second force application surface, and the area of the second force bearing surface is larger than that of the first force application surface; the first high-pressure cavity and the second high-pressure cavity are both connected with an oil inlet of the high-pressure oil cylinder;
the reversing valve has a left working state and a right working state; the left working state of the reversing valve is used for communicating the hydraulic pump station with the first pressurizing cavity and communicating the second pressurizing cavity with the oil return tank; the right working state is used for communicating the hydraulic pump station with the second pressurizing cavity and communicating the first pressurizing cavity with the oil return tank;
the pilot valve has a left working state and a right working state; the left working state of the pilot valve is used for communicating the hydraulic pump station with a left control oil port of the reversing valve and communicating a right control oil port of the reversing valve with an oil return tank; the right working state of the pilot valve is used for communicating a left control oil port of the reversing valve with the oil return tank and communicating an oil port of the hydraulic pump station with a right control oil port of the reversing valve;
the first logic valve comprises a first oil inlet, a first oil outlet and a third control oil port; the first oil outlet is connected to a left control oil port of the pilot valve, and the first control oil port is connected to the first pressurizing cavity; when the second piston moves to the left limit position of the second piston, the first oil inlet is connected to the second pressurizing cavity, and the first oil inlet is connected to the first pressurizing cavity in the rest state;
the second logic valve comprises a second oil inlet, a second oil outlet and a second control oil port; the second oil outlet is connected to a right control oil port of the pilot valve, and the second control oil port is connected to the second pressurizing cavity; when the second piston moves to the right limit position of the second piston, the second oil inlet is connected to the first pressurizing cavity, and the second oil inlet is connected to the second pressurizing cavity in the other states; wherein the first piston is located to the left of the second piston.
2. The shield tunneling machine attitude deviation correcting system according to claim 1, further comprising a pressure reducing valve disposed on an oil path connected to an oil port of the hydraulic pump station.
3. The shield tunneling machine attitude deviation correcting system according to claim 1, further comprising a speed regulating valve disposed on an oil path connected to an oil port of the hydraulic pump station.
4. The system of claim 1, further comprising a first check valve disposed on the oil path between the first high pressure chamber and the high pressure cylinder to allow high pressure oil to enter the high pressure cylinder only from the first high pressure chamber.
5. The system of claim 1, further comprising a fourth check valve disposed on the oil path between the second high pressure chamber and the high pressure cylinder to allow high pressure oil to enter the high pressure cylinder only from the fourth high pressure chamber.
6. The system for correcting the attitude of the shield tunneling machine according to claim 1, further comprising a second check valve disposed on the oil path between the first high-pressure chamber and the first pressurizing chamber, so that the hydraulic oil can enter the first high-pressure chamber only from the first pressurizing chamber.
7. The system for correcting the attitude of the shield tunneling machine according to claim 1, further comprising a third check valve disposed on the oil path between the second high-pressure chamber and the second pressurizing chamber, so that the hydraulic oil can only enter the second high-pressure chamber from the second pressurizing chamber.
8. The system for correcting the attitude of the shield tunneling machine according to any one of claims 1 to 7, wherein the reversing valve is a two-position four-way valve.
9. The system for correcting the attitude of the shield tunneling machine according to any one of claims 1 to 7, wherein the pilot valve is a two-position four-way valve.
10. A shield machine is characterized by comprising a shield machine body and the shield machine posture correction system according to any one of claims 1-9, wherein the shield machine body comprises a hydraulic pump station.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110068463.1A CN112814692B (en) | 2021-01-19 | 2021-01-19 | Shield machine and posture deviation rectifying system thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110068463.1A CN112814692B (en) | 2021-01-19 | 2021-01-19 | Shield machine and posture deviation rectifying system thereof |
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