A stabilizer hydraulic system, a heading machine

Abstract

The application provides a stabilizer hydraulic system and a heading machine, and the stabilizer hydraulic system comprises a hydraulic pump, a three-way pressure reducing valve, a mode switching valve, a main reversing valve, a rodless cavity hydraulic flow control valve, a cylinder, a rod cavity hydraulic flow control valve, a floating valve and a propulsion main reversing valve. The application can automatically switch the working mode of the stabilizer according to the current working state of the TBM, that is, the working mode is automatically switched to the "hydraulic spring" mode during heading, and the working mode is automatically switched to the high-pressure supporting mode during step changing or shutdown. The hydraulic control mode is reliable, stable, and highly automated, and avoids relying on manual switching. The application avoids the situation that the rodless cavity of the cylinder of the stabilizer is blocked, and in combination with the three-way pressure reducing valve, the oil pressure in the rodless cavity of the cylinder does not increase but is stabilized at a low pressure when the TBM has a large negative load during the heading process, thereby solving the problems of TBM jamming, excessive heading resistance and stabilizer damage.

Description

Technical Field

[0001] This application relates to the field of hydraulic technology, and in particular, to a stabilizer hydraulic system and a tunneling machine. Background Technology

[0002] A full-face hard rock tunnel boring machine (TBM) is a heavy piece of equipment used for excavating tunnels in full-face rock formations. Its stabilizer system stabilizes and dampens the TBM shield during tunneling (the main propulsion cylinder extends slowly under high pressure, and the cutterhead rotates to break the rock), and provides high-pressure support during step changes (the main propulsion cylinder retracts rapidly to prepare for the next tunneling step) or when the machine stops. The stabilizer primarily achieves stabilization and damping, and high-pressure support, respectively, by injecting low-pressure or high-pressure hydraulic oil into the rodless chamber of the cylinder through a hydraulic system.

[0003] With the development of pumped storage power stations, tunnel construction with ultra-small turns (bending radius less than 100 meters) and steep gradients (gradient greater than 35°) is becoming increasingly common. Inclined shaft TBMs are one of the preferred solutions for achieving automated, mechanized, and unmanned construction in such tunnels. Due to the steep gradient of the inclined shaft TBM, the stabilizer must be kept under high pressure during TBM step changes and shutdowns to prevent the shield from slipping backward. The ultra-small turns during inclined shaft TBM tunneling inevitably result in a significant negative load on the stabilizer during turns and attitude adjustments. This can lead to increased pressure in the rodless chamber of the hydraulic cylinder, causing problems such as TBM jamming, excessive tunneling resistance, and stabilizer damage.

[0004] Currently, existing TBM stabilizer hydraulic systems generally require manual switching between modes, such as stabilization and damping mode and high-pressure tightening mode. Furthermore, the problem of increased pressure in the rodless chamber of the cylinder due to large loads during TBM tunneling still exists. Summary of the Invention

[0005] This application provides a stabilizer hydraulic system to solve the technical problems of existing TBM stabilizer hydraulic systems that rely on manual mode switching and experience increased pressure in the rodless chamber of the cylinder during tunneling.

[0006] The technical solution adopted in this application is as follows:

[0007] A stabilizer hydraulic system includes: a hydraulic pump, a three-way pressure reducing valve, a mode switching valve, a main directional valve, a rodless chamber hydraulic flow direction control valve, a hydraulic cylinder, a rod chamber hydraulic flow direction control valve, a floating valve, and a propulsion main directional valve, wherein:

[0008] The P port of the hydraulic pump is connected to the P port of the three-way pressure reducing valve and the P port of the mode switching valve, respectively. The A port of the three-way pressure reducing valve is connected to the T port of the mode switching valve. The A port of the mode switching valve is connected to the P port of the main directional valve and the P port of the floating valve, respectively. The T ports of the mode switching valve and the floating valve are both connected to the oil tank.

[0009] The A port of the main directional valve is connected to the V1 port of the rodless chamber hydraulic flow direction control valve and the pilot X2 port of the rod chamber hydraulic flow direction control valve, respectively. The C1 port and the pilot X1 port of the rodless chamber hydraulic flow direction control valve are connected to the rodless chamber of the cylinder and the A port of the floating valve, respectively.

[0010] The B port of the main directional valve is connected to the V2 port of the rod chamber hydraulic flow control valve, and the C2 port of the rod chamber hydraulic flow control valve is connected to the rod chamber of the oil cylinder.

[0011] The control terminal of the floating valve is connected to the B port of the main directional valve, the electromagnet that propels the main directional valve, or the electromagnet of the mode switching valve, so that the floating valve can switch the rodless chamber hydraulic flow control valve to a unidirectional or bidirectional state according to the current working state of the B port of the main directional valve, the electromagnet that propels the main directional valve, or the mode switching valve.

[0012] The control terminal of the mode switching valve is connected to the main directional valve of the propulsion system, so that the mode switching valve can switch the operating mode according to the current working state of the main directional valve of the propulsion system.

[0013] Furthermore, the rodless chamber hydraulic flow direction control valve includes a rodless chamber balance valve, and the rod chamber hydraulic flow direction control valve includes a rod chamber balance valve.

[0014] Furthermore, the rodless chamber hydraulic flow direction control valve includes a rodless chamber hydraulic lock, and the rod chamber hydraulic flow direction control valve includes a rod chamber hydraulic lock.

[0015] Furthermore, the three-way pressure reducing valve is a fixed-position three-way pressure reducing valve that can only adjust one pressure level.

[0016] Furthermore, the three-way pressure reducing valve is an electro-proportional three-way pressure reducing valve with stepless pressure adjustment.

[0017] Furthermore, the mode switching valve is a hydraulically controlled mode switching valve, and the pilot control port X of the hydraulically controlled mode switching valve is connected to the A port of the propulsion main directional valve.

[0018] Furthermore, the mode switching valve is an electromagnetic mode switching valve. Whether the electromagnet of the electromagnetic mode switching valve is energized or not is related to the tunneling signal of the main directional valve. When the main directional valve is energized and in the tunneling state, the electromagnet of the electromagnetic mode switching valve will automatically be energized to complete the mode switching.

[0019] Furthermore, the floating valve includes a hydraulically controlled floating valve and a shuttle valve. The pilot control port X of the hydraulically controlled floating valve is connected to the port B of the shuttle valve. The port A1 of the shuttle valve is connected to the port B of the main directional valve. The port A2 of the shuttle valve is connected to the port A of the main directional valve.

[0020] Furthermore, the floating valve includes an electromagnetic floating valve. Whether the electromagnet of the electromagnetic floating valve is energized or not is related to the tunneling signal of the main directional valve and the main directional valve. When the electromagnet of the main directional valve is energized and is in the tunneling state, or when the electromagnet of the main directional valve is energized and hydraulic oil flows from the rodless chamber of the cylinder into the rod chamber and out, the electromagnetic floating valve is automatically energized and the hydraulic oil flow direction control valve is switched from a unidirectional flow state to a bidirectional flow state.

[0021] This application also provides a tunneling machine, including the aforementioned stabilizer hydraulic system.

[0022] Compared with the prior art, this application has the following advantages:

[0023] 1. This application prevents the TBM shield from sliding backward due to short-term pressure relief in the stabilizer's cylinder by setting a rodless chamber hydraulic flow control valve and a rod chamber hydraulic flow control valve in the rodless chamber and rod chamber of the stabilizer's cylinder, respectively.

[0024] 2. This application connects the control terminal of the mode switching valve to the main propulsion directional valve, and uses hydraulic control to enable the mode switching valve to switch operating modes according to the current working state of the main propulsion directional valve. This achieves the function of automatically switching the working mode of the stabilizer according to the current working state of the TBM (such as step change, shutdown, or tunneling). That is, it automatically switches to the "hydraulic spring" mode during tunneling and automatically switches to the high-pressure tensioning mode during step change or shutdown. The hydraulic control method has high reliability, stability, and automation, avoiding reliance on manual switching.

[0025] 3. In the "hydraulic spring" mode of this application, when the stabilizer retracts, the oil in the rodless chamber of the cylinder can freely flow bidirectionally through the rodless chamber to the control valve, avoiding the situation of pressure buildup in the rodless chamber of the stabilizer cylinder. At the same time, combined with the three-way pressure reducing valve, the oil pressure in the rodless chamber of the cylinder will not rise when the TBM has a large load during tunneling, but will be stabilized at a low pressure (e.g., 50 bar), thus realizing the "hydraulic spring mode". This can solve problems such as TBM jamming, excessive tunneling resistance, and stabilizer damage.

[0026] In addition to the purposes, features, and advantages described above, this application has other purposes, features, and advantages. A further detailed description of this application will be provided below with reference to the figures. Attached Figure Description

[0027] The accompanying drawings, which form part of this application, are used to provide a further understanding of this application. The illustrative embodiments and descriptions of this application are used to explain this application and do not constitute an undue limitation of this application. In the drawings:

[0028] Figure 1 This is a schematic diagram of the stabilizer hydraulic system according to a preferred embodiment of this application.

[0029] Figure 2 This is a schematic diagram of the stabilizer hydraulic system according to another preferred embodiment of this application.

[0030] As shown in the figure:

[0031] 1. Hydraulic pump; 2. Fixed-position three-way pressure reducing valve; 3. Hydraulic control mode switching valve; 4. Main directional valve; 5. Rodless chamber balance valve; 6. Pressure gauge; 7. Hydraulic cylinder; 8. Rod chamber balance valve; 9. Hydraulic control floating valve; 10. Shuttle valve; 11. Propulsion main directional valve; 12. Electro-proportional three-way pressure reducing valve; 13. Solenoid mode switching valve; 14. Rodless chamber hydraulic lock; 15. Rod chamber hydraulic lock; 16. Solenoid floating valve. Detailed Implementation

[0032] The embodiments of this application are described in detail below with reference to the accompanying drawings; however, this application may be implemented in a variety of different ways as defined and covered below.

[0033] Example 1

[0034] Reference Figure 1 As shown, a preferred embodiment of this application provides a stabilizer hydraulic system, including: a hydraulic pump 1, a three-way pressure reducing valve, a mode switching valve, a main directional valve 4, a rodless chamber hydraulic flow direction control valve, a cylinder 7, a rod chamber hydraulic flow direction control valve, a floating valve, and a propulsion main directional valve 11, wherein:

[0035] The P port of the hydraulic pump 1 is connected to the P port of the three-way pressure reducing valve and the P port of the mode switching valve, respectively. The A port of the three-way pressure reducing valve is connected to the T port of the mode switching valve. The A port of the mode switching valve is connected to the P port of the main directional valve 4 and the P port of the floating valve, respectively. The T ports of the mode switching valve and the floating valve are both connected to the oil tank.

[0036] The A port of the main directional valve 4 is connected to the V1 port of the rodless chamber hydraulic flow direction control valve and the pilot X2 port of the rod chamber hydraulic flow direction control valve, respectively. The C1 port and the pilot X1 port of the rodless chamber hydraulic flow direction control valve are connected to the rodless chamber of the cylinder 7 and the A port of the floating valve, respectively.

[0037] The B port of the main directional valve 4 is connected to the V2 port of the rod chamber hydraulic flow control valve, and the C2 port of the rod chamber hydraulic flow control valve is connected to the rod chamber of the cylinder 7.

[0038] The control terminal of the floating valve is connected to the B port of the main directional valve 4, the electromagnet of the main directional valve 11, or the electromagnet of the mode switching valve, so that the floating valve can switch the rodless chamber hydraulic flow direction control valve to a unidirectional or bidirectional state according to the current working state of the B port of the main directional valve 4, the main directional valve 11, or the mode switching valve.

[0039] The control terminal of the mode switching valve is connected to the main propulsion directional valve 11, so that the mode switching valve switches the operating mode according to the current working state of the main propulsion directional valve 11.

[0040] Specifically, the rodless chamber hydraulic flow direction control valve includes a rodless chamber balance valve 5, and the rod chamber hydraulic flow direction control valve includes a rod chamber balance valve 8.

[0041] Specifically, the three-way pressure reducing valve is a fixed-position three-way pressure reducing valve 2 that can only adjust one pressure level.

[0042] Specifically, the mode switching valve is a hydraulically controlled mode switching valve 3, and the pilot control port X of the hydraulically controlled mode switching valve 3 is connected to the port A of the propulsion main directional valve 11.

[0043] Specifically, the floating valve includes a hydraulically controlled floating valve 9 and a shuttle valve 10. The pilot control port X of the hydraulically controlled floating valve 9 is connected to the port B of the shuttle valve 10. The port A1 of the shuttle valve 10 is connected to the port B of the main directional valve 4. The port A2 of the shuttle valve 10 is connected to the port A of the propulsion main directional valve 11.

[0044] The specific working principle of this embodiment is as follows:

[0045] 1) High-Pressure Tensioning Mode: When the TBM is switching steps or stopping, the main directional valve 11 is in the neutral or right position, and there is no pressure oil output from port A of the main directional valve 11. At this time, there is no pilot oil pressure at port X of the hydraulic control mode switching valve 3. Under the action of the spring return force, the hydraulic control mode switching valve 3 automatically switches to the left position. At this time, the lower pressure oil output from port A of the fixed gear three-way pressure reducing valve 2 (e.g., the set pressure is 50 bar) is cut off by the hydraulic control mode switching valve 3. The high-pressure oil directly output by the hydraulic pump 1 is input from port A to port P of the main directional valve 4 through the left position of the hydraulic control mode switching valve 3. The pressure of the hydraulic pump 1 is set to a higher pressure (e.g., 300 bar). At this time, the stabilizer will automatically work under high pressure (e.g., 300 bar). When the driver presses the stabilizer extension button, the main directional valve 4 is in the left position, and the higher pressure... Oil enters the rodless chamber of cylinder 7 from port A of main directional valve 4 through rodless chamber balance valve 5. At the same time, the pressure oil from port A of main directional valve 4 is output to the pilot X2 port of rod chamber balance valve 8, opening rod chamber balance valve 8 so that the hydraulic oil in the rod chamber of cylinder 7 can smoothly return to the oil tank. At this time, there is no oil pressure at the pilot control port X of hydraulic control float valve 9, and it is in the upper position under the action of spring return force. At this time, rodless chamber balance valve 5 is in a one-way conduction state, that is, oil can only enter the rodless chamber of cylinder 7, and the oil in the rodless chamber cannot be discharged, thereby realizing the high-pressure tightening of the stabilizer. After tightening, the driver releases the stabilizer extension button. At this time, main directional valve 4 is in the neutral position, and the higher pressure oil will no longer be input into the rodless chamber of cylinder 7. However, due to the one-way conduction function of rodless chamber balance valve 5, the rodless chamber of cylinder 7 can maintain pressure to prevent the TBM shield from sliding backward.

[0046] 2) "Hydraulic Spring" Mode: When the TBM is tunneling, the main directional valve 11 is in the left position, and there is pressurized oil output from port A of the main directional valve 11. At this time, port X of the hydraulic control mode switching valve 3 will automatically switch to the right position under the action of pilot pressure oil. At this time, the higher pressure oil output from port A of the hydraulic pump 1 (e.g., 300 bar) cannot directly pass through the hydraulic control mode switching valve 3, but is reduced by the fixed-position three-way pressure reducing valve 2 and outputs a lower pressure oil (e.g., set pressure of 50 bar). This lower pressure oil is then input to port P of the main directional valve 4 through the right position of the hydraulic control mode switching valve 3. The stabilizer automatically operates at low pressure (e.g., 50 bar). When the driver presses the stabilizer extension button, the main directional valve 4 is in the left position. Lower pressure oil (e.g., 50 bar) flows from port A of the main directional valve 4 through the rodless chamber balance valve 5 into the rodless chamber of the cylinder 7. Simultaneously, the pressure oil from port A of the main directional valve 4 is output to the pilot X2 port of the rod chamber balance valve 8, opening the rod chamber balance valve 8 and allowing the oil in the rod chamber of the cylinder 7 to return smoothly to the oil tank, thereby achieving the stabilizing and shock-absorbing effect of the stabilizer. At the same time, the pressure oil propelling port A of the main directional valve 11 flows through the right side of the shuttle valve 10 into... The pilot control port X of the hydraulically controlled floating valve 9 is opened, causing the hydraulically controlled floating valve 9 to automatically switch to the lower position. The pressure oil passing through the hydraulic control mode switching valve 3 enters the pilot port X1 of the rodless chamber balance valve 5 through the hydraulically controlled floating valve 9, thus enabling the rodless chamber balance valve 5 to be bidirectionally open. That is, the oil in the rodless chamber of the cylinder 7 can freely pass through the rodless chamber balance valve 5 in both directions. At this time, the oil in the rodless chamber of the cylinder 7 can freely pass through the rodless chamber balance valve 5 in both directions, and enters the fixed position three-way pressure reducing valve 2 through the left position of the main reversing valve 4 and the right position of the hydraulic control mode valve 3. The fixed position three-way pressure reducing valve 2 has... It has a load port overflow function (when the pressure at load port A is set to a high pressure value, such as 50 bar, the channel between port A and the oil tank will be opened to release pressure), so that when the TBM has a large load during tunneling, the oil pressure in the rodless chamber of cylinder 7 will not rise but will remain stable at a low pressure (such as 50 bar), thus realizing the "hydraulic spring mode". The so-called hydraulic spring means that there is always a relatively low pressure oil in the rodless chamber of the stabilizer cylinder, which will neither decrease nor increase, so that the stabilizer is like a mechanical spring with preload. Therefore, it is referred to as a hydraulic spring in this application.

[0047] 3) Cylinder retraction: Regardless of the position of the hydraulic control mode switching valve 3, as long as the driver presses the stabilizer retraction button, the P port of the main directional valve 4 can receive high-pressure oil (e.g., 300 bar) or low-pressure oil (e.g., 50 bar). At this time, the main directional valve 4 is in the right position, and the pressure oil is input into the rod chamber of the cylinder 7 through the rod chamber balance valve 8. At the same time, the pressure oil of the main directional valve 4 enters the pilot control port X port of the hydraulic control floating valve 9 through the left side of the shuttle valve 10, so that the hydraulic control floating valve 9 is in the lower position. The pressure oil through the hydraulic control mode switching valve 3 enters the lower position of the hydraulic control floating valve 9 and enters the pilot X1 port of the rodless chamber balance valve 5, thus enabling the rodless chamber balance valve 5 to be bidirectionally open. At this time, the oil in the rodless chamber of the cylinder 7 can return to the oil tank, realizing the retraction function of the stabilizer.

[0048] As can be seen, compared with the prior art, this embodiment has the following beneficial effects:

[0049] 1. In this embodiment, by setting a rodless chamber balance valve 5 and a rod chamber balance valve 8 in the rodless chamber and rod chamber of the stabilizer's cylinder respectively, it is possible to prevent the TBM shield from slipping backward due to short-term pressure relief in the stabilizer's cylinder.

[0050] 2. In this embodiment, by connecting the pilot control port X of the hydraulic control mode switching valve 3 to the port A of the propulsion main directional valve 11, the hydraulic control mode switching valve 3 switches the operating mode according to the current working state of the propulsion main directional valve through hydraulic control. This realizes the function of automatically switching the working mode of the stabilizer according to the current working state of the TBM (such as step change, stop, or tunneling). That is, it automatically switches to the "hydraulic spring" mode during tunneling and automatically switches to the high-pressure tensioning mode when step change or stop. The hydraulic control method has high reliability, stability, and automation, avoiding reliance on manual switching.

[0051] 3. In this embodiment, the "hydraulic spring" mode and the oil in the rodless chamber of the cylinder can freely pass through the rodless chamber balance valve 5 in both directions when the stabilizer retracts, avoiding the situation of pressure buildup in the rodless chamber of the stabilizer cylinder. At the same time, combined with the fixed-position three-way pressure reducing valve 2, the oil pressure in the rodless chamber of the cylinder 7 will not rise when the TBM has a large load during tunneling, but will be stabilized at a low pressure (e.g., 50 bar), thus realizing the "hydraulic spring mode". This can solve problems such as TBM jamming, excessive tunneling resistance, and stabilizer damage.

[0052] Example 2

[0053] like Figure 2 As shown, the stabilizer hydraulic system in this embodiment differs from the embodiments described above in that:

[0054] The rodless chamber hydraulic flow control valve includes a rodless chamber hydraulic lock 14, and the rod chamber hydraulic flow control valve includes a rod chamber hydraulic lock 15.

[0055] The three-way pressure reducing valve is an electro-proportional three-way pressure reducing valve 12 with stepless pressure adjustment.

[0056] The mode switching valve is an electromagnetic mode switching valve 13. Whether the electromagnet of the electromagnetic mode switching valve 13 is energized or not is related to the tunneling signal of the main directional valve 11. When the main directional valve 11 is energized and in the tunneling state, the electromagnet of the electromagnetic mode switching valve 13 will automatically be energized to complete the mode switching.

[0057] The floating valve includes an electromagnetic floating valve 16. Whether the electromagnet of the electromagnetic floating valve 16 is energized or not is related to the tunneling signal of the main directional valve 11 and the main directional valve 4. When the electromagnet of the main directional valve 11 is energized and is in the tunneling state, or when the electromagnet of the main directional valve 4 is energized and hydraulic oil flows from the rodless chamber of the cylinder 7 into the rod chamber and out, the electromagnetic floating valve 16 is automatically energized to switch the flow of hydraulic oil in the rodless chamber to the control valve from a unidirectional state to a bidirectional state.

[0058] The working principle of this embodiment is roughly the same as that of the above embodiments, except that:

[0059] 1) In this embodiment, an electro-proportional three-way pressure reducing valve 12 with stepless pressure adjustment is used instead of a fixed-position three-way pressure reducing valve 2. Its oil circuit and function are the same as those in the above embodiment. The difference is that in this embodiment, the pressure output of the electro-proportional three-way pressure reducing valve 12 is changed by changing the current value. The electro-proportional three-way pressure reducing valve 12 can adjust the pressure steplessly according to the driver's wishes (e.g., 50 bar-200 bar). The initial current value is set to the current value when the output pressure is 50 bar. It has stronger adaptability and meets the pressure value needs under different working conditions. In contrast, the fixed-position three-way pressure reducing valve 2 can only adjust one pressure level (e.g., 50 bar).

[0060] 2) In this embodiment, an electromagnetic mode switching valve 13 is used instead of a hydraulic control mode switching valve 3. Its main oil circuit and function are the same as those in the above embodiment. The difference is that the electromagnetic mode switching valve 13 in this embodiment does not have a pilot control oil circuit. When energized, the electromagnetic mode switching valve 13 is in the right position and when de-energized, it is in the left position. Whether it is energized or not is related to the tunneling signal of the main directional valve 11. When the main directional valve 11 is energized and in the tunneling state, the electromagnet of the electromagnetic mode switching valve 13 will automatically be energized to complete the mode switching. That is, when the left side of the main directional valve 11 is energized and the TBM is in the tunneling state, the electromagnetic mode switching valve 13 will automatically be energized and switch to the "hydraulic spring" mode. Conversely, when the main directional valve 11 is in the middle position or the right side is energized and the TBM is in the step-changing or stopping state, the electromagnetic mode switching valve 13 will automatically be de-energized and switch to the high-pressure tensioning mode.

[0061] 3) In this embodiment, the rodless chamber hydraulic lock 14 and the rod chamber hydraulic lock 15 are used to replace the rodless chamber balance valve 5 and the rod chamber balance valve 8 in the above embodiments, respectively. Their main oil circuit and pilot oil circuit are the same as those in the above embodiments. The unidirectional conduction and conditional bidirectional conduction functions are the same as those in the above embodiments. However, the balance valve in the above embodiments also has a load port overflow function, so that when the TBM has a large negative load during tunneling, the oil pressure in the rodless chamber of the cylinder 7 will not rise but will be stabilized at a low pressure (e.g., 50 bar).

[0062] 4) In this embodiment, an electromagnetic floating valve 16 is used instead of the hydraulically controlled floating valve 9 in the above embodiment. Its main oil circuit and function are the same as those in the above embodiment. The difference is that the electromagnetic floating valve 16 in this embodiment does not have a pilot control oil circuit. When energized, the valve is in the lower position and when de-energized, it is in the upper position. Whether it is energized or not is related to the tunneling signal of the main directional valve 11 and the main directional valve 4. When the electromagnet of the main directional valve 11 is energized and is in the tunneling state, or when the electromagnet of the main directional valve 4 is energized and hydraulic oil flows from the rodless chamber of the cylinder 7 into the rod chamber and out, the electromagnetic floating valve 16 is automatically energized and switches the flow of hydraulic oil in the rodless chamber to the control valve from the unidirectional flow state to the bidirectional flow state. That is, when the left side of the main directional valve 11 is energized or the right side of the main directional valve 4 is energized, the electromagnetic floating valve 16 will automatically be energized and switch the flow of hydraulic oil in the rodless chamber to the control valve from the unidirectional flow state to the bidirectional flow state.

[0063] It is understandable that the stabilizer has more than one hydraulic cylinder 7. Generally, there are multiple hydraulic cylinders 7 grouped together according to the top, bottom, left, right and other directions. At the same time, its valve group is also grouped together, which will not be elaborated here.

[0064] Example 3

[0065] This embodiment provides a tunneling machine, including the stabilizer hydraulic system described in Embodiment 1 or Embodiment 2 above.

[0066] The above description is merely a preferred embodiment of this application and is not intended to limit this application. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A stabilizer hydraulic system, characterized in that, include: Hydraulic pump (1), three-way pressure reducing valve, mode switching valve, first main directional valve (4), rodless chamber hydraulic flow direction control valve, cylinder (7), rod chamber hydraulic flow direction control valve, floating valve, propulsion main directional valve (11), wherein: The P port of the hydraulic pump (1) is connected to the P port of the three-way pressure reducing valve and the P port of the mode switching valve, respectively. The A port of the three-way pressure reducing valve is connected to the T port of the mode switching valve. The A port of the mode switching valve is connected to the P port of the first main directional valve (4) and the P port of the floating valve, respectively. The T ports of the first main directional valve (4) and the T ports of the floating valve are both connected to the oil tank. The A port of the main directional valve (4) is connected to the V1 port of the rodless chamber hydraulic flow direction control valve and the pilot X2 port of the rod chamber hydraulic flow direction control valve, respectively. The C1 port of the rodless chamber hydraulic flow direction control valve is connected to the rodless chamber of the cylinder (7). The pilot X1 port of the rodless chamber hydraulic flow direction control valve is connected to the A port of the floating valve. The B port of the first main directional valve (4) is connected to the V2 port of the rod chamber hydraulic flow control valve, and the C2 port of the rod chamber hydraulic flow control valve is connected to the rod chamber of the oil cylinder (7). The control end of the floating valve is connected to the B port of the first main directional valve (4), the electromagnet of the main directional valve (11) or the electromagnet of the mode switching valve, so that the floating valve can switch the rodless chamber hydraulic flow direction control valve to a unidirectional or bidirectional state according to the current working state of the B port of the first main directional valve (4), the main directional valve (11) or the mode switching valve. The control terminal of the mode switching valve is connected to the main propulsion reversing valve (11) so that the mode switching valve can switch the operation mode according to the current working state of the main propulsion reversing valve (11). When the TBM changes position or stops, the main directional valve (11) is in the neutral or right position, and the first main directional valve (4) is in the left position, allowing hydraulic oil to flow from the rodless chamber of the cylinder (7) into the rod chamber and out. At this time, the floating valve is de-energized, causing the hydraulic flow control valve in the rodless chamber to be in a one-way directional state. The A port of the three-way pressure reducing valve is cut off by the mode switching valve, and the hydraulic system is in a high-pressure tightening mode. When the TBM is tunneling, the main directional valve (11) is in the left position, the first main directional valve (4) is in the left position, and the mode switching valve automatically... When energized, the A port of the three-way pressure reducing valve is input to the P port of the first main directional valve (4) via the right position of the mode switching valve. The floating valve is automatically energized, causing the hydraulic oil in the rodless chamber to flow to the control valve from a unidirectional to a bidirectional state. The hydraulic system is in hydraulic spring mode. When the first main directional valve (4) is in the right position, causing the hydraulic oil to flow from the rod chamber of the cylinder (7) into the rodless chamber and out, the floating valve is automatically energized, causing the hydraulic oil in the rodless chamber to flow to the control valve from a unidirectional to a bidirectional state. The cylinder retracts.

2. The stabilizer hydraulic system of claim 1, wherein, The rodless chamber hydraulic flow control valve includes a rodless chamber balance valve (5), and the rod chamber hydraulic flow control valve includes a rod chamber balance valve (8).

3. The stabilizer hydraulic system of claim 1, wherein, The rodless chamber hydraulic flow control valve includes a rodless chamber hydraulic lock (14), and the rod chamber hydraulic flow control valve includes a rod chamber hydraulic lock (15).

4. The stabilizer hydraulic system according to claim 1, characterized in that, The three-way pressure reducing valve is a fixed-position three-way pressure reducing valve (2) that can only adjust one pressure level.

5. The stabilizer hydraulic system of claim 1, wherein, The three-way pressure reducing valve is an electro-proportional three-way pressure reducing valve (12) with stepless pressure adjustment.

6. A heading machine characterized by Includes the stabilizer hydraulic system as described in any one of claims 1 to 5.

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