Hydraulic system with active deviation correction and anti-shock and rectangular pile hole forming equipment

Abstract

The application discloses a hydraulic system with active deviation correction and anti-vibration and a rectangular pile hole forming equipment, and the hydraulic system comprises a hydraulic pump, a hydraulic oil tank, symmetrically arranged first and second oil cylinders, the first oil cylinder is connected with the hydraulic pump and the hydraulic oil tank through a first combined valve, the second oil cylinder is connected with the hydraulic pump and the hydraulic oil tank through a second combined valve, and the first combined valve and the second combined valve are used for: when the rectangular pile hole forming equipment is positioned into a hole, providing high-pressure oil to the first and second oil cylinders to actively and high-pressure extend the posture of the equipment and guide the equipment into the hole; when the equipment is drilled, providing low-pressure oil to the first and second oil cylinders to make the oil cylinders low-pressure contact wall surfaces; when the equipment is corrected, providing high-pressure oil to the oil cylinder on the overbreak side to make the oil cylinder actively and high-pressure extend, and the oil cylinder on the underbreak side is in a floating unloading state to be passively retracted; and when the rectangular pile hole forming equipment is lifted, oil is provided to make the first and second oil cylinders actively retract or passively retract after unloading.

Description

Technical Field

[0001] The present application relates to the technical field of engineering machinery, and in particular to a hydraulic system and rectangular pile drilling equipment with active deviation correction and earthquake resistance. Background Art

[0002] Rectangular anti-slip piles have a rectangular cross-section and are widely used in highway and railway projects, with high demand. For soft soil, double-wheel milling equipment is often used to excavate rectangular holes. For hard rock, manual excavation is often used, which not only requires a large number of workers and has low construction efficiency, but also poses a high risk. Double-wheel milling equipment is not suitable for hard rock. To address the shortcomings of manual excavation of piles in hard rock, a new pile excavation construction model is adopted. In the early stages, rotary drilling equipment is used for circular hole excavation, which has high construction efficiency. Later, rectangular pile drilling equipment is used to further excavate rectangular holes based on the circular holes. This construction method is not only efficient and mechanized, but also greatly improves construction site safety.

[0003] With the rapid development of my country's infrastructure construction and the extensive construction of roads and railways, the demand for rectangular anti-slip piles will become increasingly greater. Faced with harsh geological conditions, especially in mountainous areas with hard geology, the excavation mode using rotary drilling and rectangular pile drilling equipment will be widely used.

[0004] There is no relevant hydraulic control system for rectangular pile drilling equipment on the market. Referring to the hydraulic control systems of other equipment, most hydraulic shock absorbers use accumulators for shock absorption. The entire hydraulic system either has only shock absorption or only high and low pressure switching, neither of which can meet the working requirements of the rectangular pile drilling equipment.

[0005] According to the site test of the rectangular pile drilling equipment, the main problems of the rectangular pile drilling equipment in the process of downward drilling are: the whole equipment shakes greatly during the drilling process, which reduces the service life of the equipment; in order to solve this problem, six support shoe cylinders 18 are set around the equipment, as shown in the attached figure. Figure 1 , Figure 1 The figure is a top view of the rectangular pile drilling equipment 20 drilling downwards. The six support shoe cylinders 18 support the wall 19 with high pressure during the construction process, effectively reducing the overall shaking of the equipment during the drilling process. However, this also brings a problem. Since the cylinders all support the wall with high pressure, the drilling of the equipment is discontinuous, and it is necessary to rely on the mechanical structure for step-by-step drilling. Due to the short stepping distance, the cylinders need to be retracted after the stepping is completed, and the equipment is moved downward as a whole. Then, the cylinders are extended with high pressure to support the wall and continue the step-by-step drilling. This is not only inefficient, but also cumbersome to operate. Therefore, a hydraulic control system is needed that can not only reduce the overall shaking of the equipment during the drilling process, but also maintain continuous drilling by gravity during the drilling process, and at the same time ensure that the deviation can be corrected in time. Summary of the Invention

[0006] The embodiment of the present application provides a hydraulic system with active deviation correction and anti-vibration functions to solve the technical problems of existing rectangular pile drilling equipment such as shaking, low efficiency, cumbersome operation, and inability to correct deviations in a timely manner.

[0007] The technical solutions adopted in this application are as follows:

[0008] A hydraulic system with active deviation correction and anti-vibration function includes a hydraulic pump, a hydraulic oil tank, and a first oil cylinder and a second oil cylinder arranged symmetrically. The first oil cylinder is connected to the hydraulic pump and the hydraulic oil tank via a first combination valve, and the second oil cylinder is connected to the hydraulic pump and the hydraulic oil tank via a second combination valve. The first combination valve and the second combination valve are used to:

[0009] When the rectangular pile drilling equipment is positioned into the hole, high-pressure oil is supplied to the first cylinder and the second cylinder to actively extend the oil cylinder at high pressure to adjust the posture of the entire rectangular pile drilling equipment and guide the equipment into the hole; when the rectangular pile drilling equipment is drilling, low-pressure oil is supplied to the first cylinder and the second cylinder to make each cylinder contact the wall at low pressure; when the rectangular pile drilling equipment is correcting the deviation, high-pressure oil is supplied to the cylinder on the over-excavated side to make it actively extend at high pressure, and the cylinder on the under-excavated side is in a floating unloading state to achieve passive retraction; when the rectangular pile drilling equipment is lifted, oil is provided to make the first cylinder and the second cylinder actively retract or passively retract after unloading.

[0010] Furthermore, the first combination valve includes a first electromagnetic reversing valve, a third electromagnetic reversing valve, a first pressure reducing valve, a second relief valve, and a first shuttle valve, wherein:

[0011] The oil inlet a of the first solenoid reversing valve is connected to the output port of the hydraulic pump, the oil return port d is connected to the hydraulic oil tank, the working port b is connected to the oil inlet a of the third solenoid reversing valve, and the working port c of the first solenoid reversing valve is connected to the rod chamber of the first oil cylinder; the oil return port d of the third solenoid reversing valve is connected to the hydraulic oil tank, the working port b is connected to the input port a of the first pressure reducing valve, the output port b of the first pressure reducing valve is respectively connected to the input port a of the second relief valve and the input port a of the first shuttle valve, the working port c of the third solenoid reversing valve is connected to the input port b of the first shuttle valve, and the output port c of the first shuttle valve is connected to the rodless chamber of the first oil cylinder; the output port b of the second relief valve is respectively connected to the control port c of the first pressure reducing valve and the hydraulic oil tank;

[0012] The second combination valve includes a second solenoid reversing valve, a fourth solenoid reversing valve, a second pressure reducing valve, a third relief valve, and a second shuttle valve. The oil inlet a of the second solenoid reversing valve is connected to the output port of the hydraulic pump, the oil return port d is connected to the hydraulic oil tank, the working port b is connected to the oil inlet a of the fourth solenoid reversing valve, and the working port c is connected to the rod chamber of the second oil cylinder; the oil return port d of the fourth solenoid reversing valve is connected to the hydraulic oil tank, the working port b is connected to the input port a of the second pressure reducing valve, the output port b of the second pressure reducing valve is respectively connected to the input port a of the third relief valve and the input port a of the second shuttle valve, the working port c of the fourth solenoid reversing valve is connected to the input port b of the second shuttle valve, and the output port c of the second shuttle valve is connected to the rodless chamber of the second oil cylinder; the output port b of the third relief valve is respectively connected to the control port c of the second pressure reducing valve and the hydraulic oil tank.

[0013] Furthermore, it also includes a first overflow valve, which is connected to the output port of the hydraulic pump.

[0014] Furthermore, the first electromagnetic reversing valve and the second electromagnetic reversing valve are Y-type three-position four-way reversing valves.

[0015] Furthermore, the first electromagnetic reversing valve and the second electromagnetic reversing valve are H-type three-position four-way reversing valves.

[0016] Furthermore, the first combination valve includes a first electromagnetic reversing valve, a third electromagnetic reversing valve, a first pressure reducing valve, a second relief valve, a first shuttle valve, and a first hydraulically controlled one-way valve, wherein:

[0017] The oil inlet a of the third solenoid reversing valve is connected to the output port of the hydraulic pump, the oil return port d is respectively connected to the output port b of the second relief valve and the hydraulic oil tank, the working port c is connected to the input port b of the first shuttle valve, and the working port b is respectively connected to the control port c of the first hydraulically controlled one-way valve and the input port a of the first pressure reducing valve; the control port c of the first pressure reducing valve is connected to the hydraulic oil tank, the output port b is connected to the input port a of the first shuttle valve, the output port c of the first shuttle valve is connected to the oil inlet a of the first solenoid reversing valve, the oil return port d of the first solenoid reversing valve is connected to the hydraulic oil tank, the working port b is respectively connected to the input port a of the first hydraulically controlled one-way valve and the rodless chamber of the first oil cylinder, and the working port c is connected to the rod chamber of the first oil cylinder; the output port b of the first hydraulically controlled one-way valve is connected to the input port a of the second relief valve;

[0018] The second combination valve includes a second electromagnetic reversing valve, a fourth electromagnetic reversing valve, a second pressure reducing valve, a third relief valve, a second shuttle valve, and a second hydraulically controlled one-way valve, wherein:

[0019] The oil inlet a of the fourth solenoid reversing valve is connected to the output port of the hydraulic pump, the oil return port d is respectively connected to the output port b of the third relief valve and the hydraulic oil tank, the working port c is connected to the input port b of the second shuttle valve, and the working port b is respectively connected to the control port c of the second hydraulically controlled one-way valve and the input port a of the second pressure reducing valve; the control port c of the second pressure reducing valve is connected to the hydraulic oil tank, the output port b is connected to the input port a of the second shuttle valve, the output port c of the second shuttle valve is connected to the oil inlet a of the second solenoid reversing valve, the oil return port d of the second solenoid reversing valve is connected to the hydraulic oil tank, the working port b is respectively connected to the input port a of the second hydraulically controlled one-way valve and the rodless chamber of the second oil cylinder, and the working port c is connected to the rod chamber of the second oil cylinder; the output port b of the second hydraulically controlled one-way valve is connected to the input port a of the third relief valve.

[0020] Furthermore, it also includes a first overflow valve, which is connected to the output port of the hydraulic pump.

[0021] Furthermore, the first electromagnetic reversing valve and the second electromagnetic reversing valve are Y-type three-position four-way reversing valves.

[0022] Furthermore, the first electromagnetic reversing valve and the second electromagnetic reversing valve are H-type three-position four-way reversing valves.

[0023] Another preferred embodiment of the present application further provides a rectangular pile drilling device, including the hydraulic system described above.

[0024] Compared with the existing technology, this application has the following beneficial effects:

[0025] The present application provides a hydraulic system with active deviation correction and anti-vibration, comprising a hydraulic pump, a hydraulic oil tank, a symmetrically arranged first oil cylinder and a second oil cylinder, the first oil cylinder being connected to the hydraulic pump and the hydraulic oil tank through a first combination valve, and the second oil cylinder being connected to the hydraulic pump and the hydraulic oil tank through a second combination valve, the first combination valve and the second combination valve being used for: when the rectangular pile drilling equipment is positioned in a hole, high-pressure oil is supplied to the first oil cylinder and the second oil cylinder to actively extend the oil cylinder and adjust the posture of the entire rectangular pile drilling equipment to guide the equipment into the hole; when the rectangular pile drilling equipment is drilling, low-pressure oil is supplied to the first oil cylinder and the second oil cylinder to make each oil cylinder contact the wall surface at low pressure; when the rectangular pile drilling equipment is correcting deviation, high-pressure oil is supplied to the oil cylinder on the over-excavated side to make it actively extend the oil cylinder at high pressure, and the oil cylinder on the under-excavated side is in a floating unloading state to achieve passive retraction; when the rectangular pile drilling equipment is lifted, oil is provided to make the first oil cylinder and the second oil cylinder actively retract or passively retract after unloading. Therefore, the present application has the following advantages:

[0026] 1. This application applies to the hydraulic anti-seismic control of rectangular pile drilling equipment. During the downward drilling process, the hydraulic system continuously provides low pressure to keep the cylinder close to the wall. When the cylinder is squeezed due to overall equipment shaking, the cylinder can be passively retracted, and the symmetrical cylinder can be actively extended. During the drilling process, the cylinder always stays close to the wall, thereby reducing equipment shaking.

[0027] 2. This application is applicable to the control of active high-pressure deviation correction of rectangular pile drilling equipment. When drilling deviation occurs, the cylinder that needs to be adjusted can be switched to high pressure individually to adjust the equipment posture. The symmetrical cylinder is in a floating state, and the required high pressure of the deviation correction cylinder can be appropriately reduced;

[0028] 3. This application has the functions of active deviation correction and hydraulic shock resistance. Each cylinder is controlled separately, and the high and low pressure switching is not affected by other cylinders. When correcting deviation or drilling, each cylinder is close to the wall to reduce equipment shaking;

[0029] 4. When the reversing valve is in the middle position, the oil cylinder is in the unloading state. When the pipeline is damaged or the system loses pressure during the equipment construction in the well, the oil cylinder can be squeezed and easily passively retracted, so that the whole equipment can be lifted out for maintenance without getting stuck due to the oil cylinder being unable to retract.

[0030] 5. Various related hydraulic control valves are integrated into the combination valve. Each cylinder is equipped with a combination valve for control. It has high centralization, compactness and strong versatility. The valve group has high and low pressure switching and hydraulic shock resistance functions. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] The accompanying drawings, which constitute part of this application, are intended to provide a further understanding of this application. The exemplary embodiments and descriptions of this application are intended to explain this application and do not constitute an improper limitation on this application. In the accompanying drawings:

[0032] Figure 1 This is a schematic diagram of the operation of existing rectangular pile hole-forming equipment;

[0033] Figure 2 This is a schematic diagram of the principle of a hydraulic system with active deviation correction and anti-vibration function according to a preferred embodiment of the present application;

[0034] Figure 3 This is a schematic diagram of the principle of a hydraulic system with active deviation correction and anti-vibration function according to another preferred embodiment of the present application;

[0035] In the figure: 1. Hydraulic pump; 2. First relief valve; 3. First solenoid reversing valve; 4. Second solenoid reversing valve; 5. Third solenoid reversing valve; 6. First pressure reducing valve; 7. Second relief valve; 8. First shuttle valve; 9. Fourth solenoid reversing valve; 10. Second pressure reducing valve; 11. Third relief valve; 12. Second shuttle valve; 13. First oil cylinder; 14. Second oil cylinder; 15. Hydraulic oil tank; 16. First hydraulically controlled one-way valve; 17. Second hydraulically controlled one-way valve; 18. Shoe cylinder; 19. Wall; 20. Rectangular pile drilling equipment. DETAILED DESCRIPTION

[0036] It should be noted that, in the absence of conflict, the embodiments and features of the embodiments in this application can be combined with each other. The present application will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0037] Reference Figure 2 A preferred embodiment of the present application provides a hydraulic system with active deviation correction and anti-vibration properties, characterized in that it includes a hydraulic pump 1, a hydraulic oil tank 15, and a symmetrically arranged first cylinder 13 and second cylinder 14. The first cylinder 13 is connected to the hydraulic pump 1 and the hydraulic oil tank 15 via a first combination valve, and the second cylinder 14 is connected to the hydraulic pump 1 and the hydraulic oil tank 15 via a second combination valve. The first and second combination valves are used to:

[0038] When the rectangular pile drilling equipment is positioned into the hole, high-pressure oil is supplied to the first oil cylinder 13 and the second oil cylinder 14 to actively extend them at high pressure to adjust the posture of the entire rectangular pile drilling equipment and guide the equipment into the hole; when the rectangular pile drilling equipment is drilling, low-pressure oil is supplied to the first oil cylinder 13 and the second oil cylinder 14 to make each oil cylinder contact the wall at low pressure; when the rectangular pile drilling equipment is correcting the deviation, high-pressure oil is supplied to the oil cylinder on the over-excavation side to make it actively extend at high pressure, and the oil cylinder on the under-excavation side is in a floating unloading state to achieve passive retraction; when the rectangular pile drilling equipment is lifted, oil is supplied to make the first oil cylinder 13 and the second oil cylinder 14 actively retract or passively retract after unloading.

[0039] This embodiment provides a hydraulic system with active deviation correction and anti-vibration, including a hydraulic pump 1, a hydraulic oil tank 15, a symmetrically arranged first oil cylinder 13 and a second oil cylinder 14, the first oil cylinder 13 is connected to the hydraulic pump 1 and the hydraulic oil tank 15 through a first combination valve, and the second oil cylinder 14 is connected to the hydraulic pump 1 and the hydraulic oil tank 15 through a second combination valve. The first combination valve and the second combination valve are used to: provide high-pressure oil to the first oil cylinder 13 and the second oil cylinder 14 when the rectangular pile drilling equipment is positioned in the hole, and actively extend the high-pressure oil. The posture of the entire rectangular pile drilling device is adjusted to guide the device into the hole in the right direction; when the rectangular pile drilling device is drilling, low-pressure oil is supplied to the first oil cylinder 13 and the second oil cylinder 14 so that each oil cylinder contacts the wall surface at low pressure; when the rectangular pile drilling device is correcting deviation, high-pressure oil is supplied to the oil cylinder on the over-excavated side so that it actively extends at high pressure, and the oil cylinder on the under-excavated side is in a floating unloading state to achieve passive retraction; when the rectangular pile drilling device is lifted, oil is supplied to cause the first oil cylinder 13 and the second oil cylinder 14 to actively retract or passively retract after unloading. Therefore, this embodiment has the following advantages:

[0040] 1. This embodiment is applicable to the hydraulic anti-seismic control of rectangular pile drilling equipment. During the downward drilling process, the hydraulic system continuously provides low pressure to keep the cylinder in contact with the wall. When the cylinder is squeezed due to overall equipment shaking, the cylinder can be passively retracted, while the symmetrical cylinder can be actively extended. During the drilling process, the cylinder always stays in contact with the wall, thereby reducing equipment shaking.

[0041] 2. This embodiment is applicable to the control of active high-pressure deviation correction for rectangular pile drilling equipment. When deviation occurs during drilling, the cylinder requiring deviation correction can be individually switched to high pressure to adjust the equipment's posture. The symmetrical cylinder is in a floating state, and the required high pressure of the deviation correction cylinder can be appropriately reduced.

[0042] 3. This embodiment has the functions of active deviation correction and hydraulic shock resistance. Each cylinder is controlled independently, and the high and low pressure switching is not affected by other cylinders. When correcting deviation or drilling, each cylinder is close to the wall surface, reducing equipment shaking.

[0043] 4. When the rectangular pile drilling equipment is correcting its deviation or lifting, the oil cylinder can be in an unloaded state. When the equipment encounters pipeline damage or system pressure loss during underground construction, the oil cylinder can be squeezed and easily passively retracted, making it easy for the entire equipment to be lifted out for maintenance, and it will not be stuck due to the oil cylinder being unable to retract;

[0044] 5. Various hydraulic control valves related to this embodiment are integrated into the combination valve. Each oil cylinder is equipped with a combination valve for control. It has high centralization, compactness and strong versatility. The valve group has high and low pressure switching and hydraulic shock resistance functions.

[0045] like Figure 2In the preferred embodiment of the present application, the first combination valve includes a first electromagnetic reversing valve 3, a third electromagnetic reversing valve 5, a first pressure reducing valve 6, a second relief valve 7, and a first shuttle valve 8, wherein:

[0046] The oil inlet a of the first solenoid reversing valve 3 is connected to the oil outlet b of the hydraulic pump 1, the oil return port d is connected to the hydraulic oil tank 15, the working port b is connected to the oil inlet a of the third solenoid reversing valve 5, and the working port c of the first solenoid reversing valve 3 is connected to the rod chamber of the first oil cylinder 13; the oil return port d of the third solenoid reversing valve 5 is connected to the hydraulic oil tank 15, the working port b is connected to the input port a of the first pressure reducing valve 6, and the output port b of the first pressure reducing valve 6 is respectively connected to the input port a of the second relief valve 7 and the input port a of the first shuttle valve 8, the working port c of the third solenoid reversing valve 5 is connected to the input port b of the first shuttle valve 8, and the output port c of the first shuttle valve 8 is connected to the rodless chamber of the first oil cylinder 13; the output port b of the second relief valve 7 is respectively connected to the control port c of the first pressure reducing valve 6 and the hydraulic oil tank 15;

[0047] The second combination valve includes a second electromagnetic reversing valve 4, a fourth electromagnetic reversing valve 9, a second pressure reducing valve 10, a third overflow valve 11, and a second shuttle valve 12. The oil inlet a of the second electromagnetic reversing valve 4 is connected to the oil outlet b of the hydraulic pump 1, the oil return port d is connected to the hydraulic oil tank 15, the working port b is connected to the oil inlet a of the fourth electromagnetic reversing valve 9, and the working port c is connected to the rod chamber of the second oil cylinder 14; the oil return port d of the fourth electromagnetic reversing valve 9 is connected to the hydraulic oil tank 15, and the working port b is connected to the rod chamber of the second oil cylinder 14. The input port a is connected, the output port b of the second pressure reducing valve 10 is respectively connected to the input port a of the third relief valve 11 and the input port a of the second shuttle valve 12, the working port c of the fourth solenoid reversing valve 9 is connected to the input port b of the second shuttle valve 12, and the output port c of the second shuttle valve 12 is connected to the rodless chamber of the second oil cylinder 14; the output port b of the third relief valve 11 is respectively connected to the control port c of the second pressure reducing valve 10 and the hydraulic oil tank 15; the first relief valve 2 is connected to the output port of the hydraulic pump 1.

[0048] In the above embodiment, the first electromagnetic reversing valve 3 and the second electromagnetic reversing valve 4 are Y-type three-position four-way reversing valves. Alternatively, the first electromagnetic reversing valve 3 and the second electromagnetic reversing valve 4 can also be H-type three-position four-way reversing valves.

[0049] Figure 2 The functions of the various parts of the hydraulic system shown in the figure are as follows:

[0050] The function of the hydraulic pump 1 shown is to provide power for the entire hydraulic control system;

[0051] The function of the first relief valve 2 is to limit the maximum pressure of the entire hydraulic system and protect the system safety;

[0052] The function of the first electromagnetic reversing valve 3 is to control the action of the first oil cylinder 13, including three actions: extension, retraction and neutral unloading of the first oil cylinder 13;

[0053] The function of the second electromagnetic reversing valve 4 is to control the action of the second oil cylinder 14, including three actions: the second oil cylinder 14 extends, retracts, and unloads in the middle position;

[0054] The function of the third electromagnetic reversing valve 5 is to switch the pressure of the rodless chamber between high and low pressure when the first oil cylinder 13 is extended. When in the normal position, the rodless chamber of the first oil cylinder 13 is in a high pressure state;

[0055] The function of the first pressure reducing valve 6 is to provide a constant low pressure to the rodless chamber of the first oil cylinder 13, while ensuring that the pressure regulation of other oil cylinders does not affect each other;

[0056] The function of the second relief valve 7 is to provide overflow safety protection for the system when the equipment shakes when the first oil cylinder 13 is under low pressure control;

[0057] The function of the first shuttle valve 8 is to select the pressure when the first oil cylinder 13 switches between high and low pressure, so that the oil circuits do not affect each other during the high and low pressure switching, and the high pressure oil channel is in the normal position;

[0058] The function of the fourth electromagnetic reversing valve 9 is to switch the pressure of the rodless chamber between high and low pressure when the second oil cylinder 14 is extended. When in the normal position, the rodless chamber of the second oil cylinder 14 is in a high pressure state;

[0059] The function of the second pressure reducing valve 10 is to provide a constant low pressure to the rodless chamber of the second oil cylinder 14, while ensuring that the pressure regulation of other oil cylinders does not affect each other;

[0060] The function of the third relief valve 11 is to provide overflow safety protection for the system when the equipment shakes when the second oil cylinder 14 is under low pressure control;

[0061] The function of the second shuttle valve 12 is to select the pressure when the second oil cylinder 14 switches between high and low pressure, so that the oil circuits do not affect each other during the high and low pressure switching, and the high pressure oil channel is in the normal position;

[0062] The first oil cylinder 13 serves as an actuator for supporting the entire device and the wall.

[0063] The second oil cylinder 14 serves as an actuator for supporting the entire device and the wall.

[0064] The hydraulic oil tank 15 is used to store hydraulic oil.

[0065] Figure 2 The control principle of the provided hydraulic system is as follows:

[0066] When the equipment is positioned into the hole: the equipment needs to adjust the posture of the entire equipment by controlling six oil cylinders. At this time, each oil cylinder uses high pressure to guide the equipment into the hole. The hydraulic pump 1 sets a high pressure, and the hydraulic pump 1 suction port a draws oil from the hydraulic oil tank 15 to provide power for the entire hydraulic system. The hydraulic pump 1's oil outlet b outputs high-pressure oil, which is connected to the input port a of the first relief valve 2. The first relief valve 2 is used to limit the maximum pressure of the entire hydraulic system and protect the hydraulic system at the same time; the hydraulic pump 1 oil outlet b is also connected to the oil inlet a of the first solenoid reversing valve 3. When the first solenoid reversing valve 3 is energized in the right position, the valve is in the right position. At this time, the oil inlet a of the first solenoid reversing valve 3 is connected to the working port b, and the working port b is connected to the a of the third solenoid reversing valve 5. At this time, the third solenoid reversing valve 5 is not energized, the valve is in the right position, and the oil inlet a of the third solenoid reversing valve 5 The port is connected with the working port c, and the working port c is connected with the input port b of the first shuttle valve 8. The first shuttle valve 8 is in the normal right position due to the action of the spring. At this time, the input port b of the first shuttle valve 8 is connected with the output port c, and the output port c is connected with the rodless cavity of the first oil cylinder 13. The rod cavity of the first oil cylinder 13 is connected with the working port c of the first electromagnetic reversing valve 3, and is connected back to the hydraulic oil tank 15 through the return oil port d of the first electromagnetic reversing valve 3, thereby forming a circuit, so that the first oil cylinder 13 is extended for posture adjustment. After the posture is adjusted, the first electromagnetic reversing valve 3 loses power; the control method of extending the posture adjustment of other oil cylinders such as the second oil cylinder 14 is similar to the control principle of the first oil cylinder 13, and will not be repeated here.

[0067] When the first cylinder 13 needs to retract and adjust its posture, the first solenoid reversing valve 3 is energized in the left position, and the valve is in the left position. The oil inlet a of the first solenoid reversing valve 3 is connected to the working port c, and the working port c is connected to the rod chamber of the first cylinder 13. The first cylinder 13 retracts, and its rodless chamber is connected to the output port c of the first shuttle valve 8. The first shuttle valve 8 is in the normal position, and its output port c is connected to the input port b, and its input port b is connected to the working port c of the third solenoid reversing valve 5. The third solenoid reversing valve 5 is de-energized and in the right position, and its working port c is connected to the oil inlet a, and the oil inlet a is connected to the working port b of the first solenoid reversing valve 3. Since the first solenoid reversing valve 3 is energized in the left position, its working port b is connected to the oil return port d, and the oil return port d is connected to the hydraulic oil tank 15, thereby forming a circuit. The control principle for retracting and adjusting the posture of other cylinders such as the second cylinder 14 is the same as that of the first cylinder 13, and will not be repeated here. It can be seen that each oil cylinder in this embodiment can be controlled individually to adjust the posture and guide it into the hole. The hydraulic system is in a high-pressure state during positioning.

[0068] When the equipment is drilling: the entire equipment is guided into the hole through the front positioning, and the symmetrical first oil cylinder 13 and the second oil cylinder 14 are taken as an example. The control method of other oil cylinders is the same. At this time, the first electromagnetic reversing valve 3 is in the right position, the third electromagnetic reversing valve 5 and the second electromagnetic reversing valve 4 are in the right position, and the fourth electromagnetic reversing valve 9 is energized at the same time. At this time, the oil inlet a of the first electromagnetic reversing valve 3 is connected to the working port b, and its working port b is connected to the oil inlet a of the third electromagnetic reversing valve 5, and the oil inlet a of the third electromagnetic reversing valve 5 is connected to the working port b, and its working port b is connected to the input port a of the first pressure reducing valve 6, and the input port a of the first pressure reducing valve 6 is connected to the output port b, and its output port b is then connected to the input port a of the first shuttle valve 8, and at the same time connected to the input port a of the second relief valve 7, and the output of the first shuttle valve 8 Port c is connected to the output port b of the second overflow valve 7, and the first pressure reducing valve 6 is set to a low pressure; at this time, the first shuttle valve 8 is in the left position, its input port a is connected to the input port c, and its output port c is connected to the rodless cavity of the first oil cylinder 13, and the first oil cylinder 13 extends out to contact the wall at low pressure, and the rod cavity of the first oil cylinder 13 is connected to the working port c of the first solenoid reversing valve 3, and the working port c of the first solenoid reversing valve 3 is connected to the return oil port d, and the return oil port d is connected back to the hydraulic oil tank 15, thereby forming a circuit; the control principle of the low-pressure extension of the second oil cylinder 14 to contact the wall is the same as the control principle of the first oil cylinder 13, and will not be repeated here.

[0069] When drilling, each oil cylinder contacts the wall at low pressure, reducing the shaking of the entire equipment and keeping the equipment stable. At the same time, due to the low-pressure contact with the wall, the entire equipment can achieve continuous downward vertical drilling by its own gravity. During drilling, due to the uneven wall surface and the shaking of the equipment, the cylinders will inevitably be squeezed. Assuming that the first cylinder 13 is squeezed and forced to retract, the rodless chamber of the first cylinder 13 is connected to the output port c of the first shuttle valve 8, which is connected to the input port a of the first relief valve 7 through the first shuttle valve 8. The set pressure of the first relief valve 7 is about 20 bar higher than the set pressure of the first pressure reducing valve 6. At this time, when the first cylinder 13 is forced to be squeezed, the first relief valve 7 overflows the excess flow back to the hydraulic oil tank 15, so that the first cylinder 13 is forced to retract due to the squeezing; at this time, the second cylinder 14 on the symmetrical surface of the first cylinder 13 will continue to extend to contact the wall due to the retraction of the first cylinder 13, and the other cylinders will follow similarly. This cycle is repeated over and over again, and each cylinder continuously extends and retracts, automatically adjusting to ensure that low-pressure contact with the wall is always achieved, ensuring that the entire equipment can achieve continuous drilling while being hydraulically anti-vibration, reducing the amount of equipment shaking, and maintaining the stability of the equipment during drilling.

[0070] When correcting the deviation of the equipment: During drilling, when the overall deviation of the equipment occurs, correction is required, such as using a laser device to ensure the verticality detection of the rectangular hole, and correcting the deviation by actively extending the cylinder at high pressure. Assuming that over-excavation occurs on the side where the first cylinder 13 is located, and under-excavation occurs on the side where the second cylinder 14 is located on the symmetrical side, these two cylinders are used as an example to illustrate the correction principle. When over-excavation occurs on the side of the first cylinder 13, the first cylinder 13 needs to be actively extended at high pressure, and the second cylinder 14 needs to be retracted. At this time, the first solenoid reversing valve 3 is energized in the right position, the third solenoid reversing valve 5 is de-energized, the second solenoid reversing valve 4 and the fourth solenoid reversing valve 9 are de-energized, and the other cylinders all maintain the state during drilling. , and the oil pump 1 outputs high pressure, and its oil outlet port b is connected to the oil inlet port a of the first solenoid reversing valve 3. The first solenoid reversing valve 3 is in the right position, and its oil inlet port a is connected to the inlet of the working port b, and the working port b is connected to the oil inlet port a of the third solenoid reversing valve 5. The third solenoid reversing valve 5 is in the right position, and its oil inlet port a is connected to the working port c, and the working port c is connected to the input port b of the first shuttle valve 8. The input port b of the first shuttle valve 8 is connected to the output port c, and its output port c is connected to the rodless cavity of the first oil cylinder 13. The first oil cylinder 13 extends out at high pressure to correct the offset. The rod cavity of the first oil cylinder 13 is connected to the working port c of the first solenoid reversing valve 3, and its working port c is connected to the oil return port d and connected to the hydraulic oil tank 15 to form a circuit; at this time, the first oil cylinder 13 is extended out at high pressure, and the second oil cylinder 14 on the symmetrical side is in a floating state. Its rodless cavity is connected to the output port c of the second shuttle valve 12, and the second shuttle valve 1 2, the output port c is connected to the input port b, the input port b of the second shuttle valve 12 is connected to the working port c of the fourth solenoid reversing valve 9, the working port c of the fourth solenoid reversing valve 9 is connected to the return oil port d, and the return oil port d is connected to the working port b of the second solenoid reversing valve 4; the rod chamber of the second oil cylinder 14 is connected to the working port c of the second solenoid reversing valve 4, and the second solenoid reversing valve 4 is in the neutral position due to no power, and its working port b, working port c, and return oil port d are connected and connected back to the hydraulic oil tank 15. At this time, the rodless chamber and the rod chamber of the second oil cylinder 14 are connected. When the first oil cylinder 13 is pushed out under high pressure, the second oil cylinder 14 is in a floating unloading state and passively retracts, reducing the high pressure required for the first oil cylinder 13 to correct the deviation. In this way, active correction of the over-excavation side is realized to ensure the verticality of the excavated rectangular hole. The other oil cylinders not involved in the correction maintain the state during drilling, so that each oil cylinder is in contact with the wall surface, and the overall shaking of the equipment is reduced while correcting the deviation. When over-digging occurs on the second oil cylinder 14 side and under-digging occurs on the first oil cylinder 13 side, the correction principle is similar. When over-digging or under-digging occurs on the other oil cylinder sides, the correction principle is similar and will not be repeated here.

[0071] When the equipment is lifted: When the hole is drilled or the equipment fails and needs to be lifted for maintenance, each cylinder needs to be actively retracted or unloaded. The first working condition: After the hole is drilled, the equipment needs to be lifted out. At this time, oil enters the rod chamber of each cylinder. Retract each cylinder. Taking the first cylinder 13 as an example, the left position of the first solenoid reversing valve 3 is energized, and the valve is in the left position. The oil inlet port a of the first solenoid reversing valve 3 is connected to the working port c, and the working port c is connected to the rod chamber of the first cylinder 13. The cylinder retracts, and its rodless chamber is connected to the output port c of the first shuttle valve 8. The first shuttle valve 8 is in the normal position, and its output port c is connected to the input port b, and the input port b is connected to the The working port c of the third electromagnetic reversing valve 5 is connected. The third electromagnetic reversing valve 5 is not energized and is in the right position. Its working port c is connected to the oil inlet a, and the oil inlet a is connected to the working port b of the first electromagnetic reversing valve 3. Since the first electromagnetic reversing valve 3 is energized in the left position, its working port b is connected to the oil return port d, and the oil return port d is connected back to the hydraulic oil tank 15, thereby forming a circuit, and the first oil cylinder 13 retracts; the operation of other oil cylinders is consistent with it. When each oil cylinder is retracted, it is convenient to quickly lift the equipment out. The second working condition: when the hydraulic pipeline is found to be damaged during drilling, the hydraulic system cannot build pressure to retract the oil cylinder. At this time, all oil cylinders are in contact with the wall. At this time, all electromagnetic reversing valves are de-energized, and each oil cylinder is in a neutral floating unloading state. When the equipment is lifted, each oil cylinder is passively retracted by actively shaking, so that the entire equipment can be smoothly lifted out for maintenance.

[0072] like Figure 3 In the preferred embodiment of the present application, the first combination valve includes a first electromagnetic reversing valve 3, a third electromagnetic reversing valve 5, a first pressure reducing valve 6, a second relief valve 7, a first shuttle valve 8, and a first hydraulically controlled one-way valve 16, wherein:

[0073] The oil inlet a of the third solenoid reversing valve 5 is connected to the oil outlet b of the hydraulic pump 1, the oil return port d is connected to the output port b of the second relief valve 7 and the hydraulic oil tank 15 respectively, the working port c is connected to the input port b of the first shuttle valve 8, and the working port b is connected to the control port c of the first hydraulically controlled one-way valve 16 and the input port a of the first pressure reducing valve 6 respectively; the control port c of the first pressure reducing valve 6 is connected to the hydraulic oil tank 15, and the output port b is connected to the output port b of the first shuttle valve 8. The inlet port a is connected, the output port c of the first shuttle valve 8 is connected to the oil inlet port a of the first solenoid reversing valve 3, the oil return port d of the first solenoid reversing valve 3 is connected to the hydraulic oil tank 15, the working port b is respectively connected to the input port a of the first hydraulically controlled one-way valve 16 and the rodless cavity of the first oil cylinder 13, and the working port c is connected to the rod cavity of the first oil cylinder 13; the output port b of the first hydraulically controlled one-way valve 16 is connected to the input port a of the second relief valve 7;

[0074] The second combination valve includes a second electromagnetic reversing valve 4, a fourth electromagnetic reversing valve 9, a second pressure reducing valve 10, a third relief valve 11, a second shuttle valve 12, and a second hydraulically controlled one-way valve 17, wherein:

[0075] The oil inlet a of the fourth solenoid reversing valve 9 is connected to the oil outlet b of the hydraulic pump 1, the oil return port d is respectively connected to the output port b of the third relief valve 11 and the hydraulic oil tank 15, the working port c is connected to the input port b of the second shuttle valve 12, and the working port b is respectively connected to the control port c of the second hydraulically controlled one-way valve 17 and the input port a of the second pressure reducing valve 10; the control port c of the second pressure reducing valve 10 is connected to the hydraulic oil tank 15, and the output port b is connected to the input port a of the second shuttle valve 12. The output port c of the second shuttle valve 12 is connected to the oil inlet a of the second solenoid reversing valve 4, the return oil port d of the second solenoid reversing valve 4 is connected to the hydraulic oil tank 15, the working port b is respectively connected to the input port a of the second hydraulically controlled one-way valve 17 and the rodless chamber of the second oil cylinder 14, and the working port c is connected to the rod chamber of the second oil cylinder 14; the output port b of the second hydraulically controlled one-way valve 17 is connected to the input port a of the third overflow valve 11; the first overflow valve 2 is connected to the output port of the hydraulic pump 1.

[0076] In the above embodiment, the first electromagnetic reversing valve 3 and the second electromagnetic reversing valve 4 are Y-type three-position four-way reversing valves. Alternatively, the first electromagnetic reversing valve 3 and the second electromagnetic reversing valve 4 can also be H-type three-position four-way reversing valves.

[0077] Figure 3 The control principle of the provided hydraulic system is as follows:

[0078] When the equipment is positioned into the hole: the equipment needs to adjust the posture of the entire equipment by controlling six cylinders. At this time, each cylinder uses high pressure to guide the equipment into the hole. The hydraulic pump 1 is set to a high pressure. The oil suction port a of the hydraulic pump 1 draws oil from the hydraulic oil tank 15 to provide power for the entire hydraulic system. The oil outlet b of the hydraulic pump 1 discharges high-pressure oil, which is connected to the input port a of the first relief valve 2. The first relief valve 2 is used to limit the maximum pressure of the entire hydraulic system and protect this hydraulic system; the oil outlet b of the hydraulic pump 1 is connected to the oil inlet a of the third solenoid reversing valve 5, and the oil return port d of the third solenoid reversing valve 5 is connected to the output port b of the second relief valve 7, and is also connected back to the hydraulic oil tank 15. At this time, the third solenoid reversing valve 5 is not energized and the valve is in the right position. The oil inlet a of the third solenoid reversing valve 5 is connected to the working port c, and the working port c is then connected to the input port b of the first shuttle valve 8. Its oil return port d is connected to the working port b, and the working port b is respectively connected to the input port a of the first pressure reducing valve 6 and the control port c of the first hydraulically controlled one-way valve 16, and is connected to When the camshaft is in the right position, the oil inlet a of the first solenoid valve 3 is connected to the working port b of the first oil cylinder 13, and the working port b of the first oil cylinder 13 is connected to the working port c of the first oil cylinder 13. The rod cavity of the first oil cylinder 13 is connected to the working port c of the first oil cylinder 13, and the oil return port d of the first oil cylinder 13 is connected to the hydraulic oil tank 15, thereby forming a circuit, so that the first oil cylinder 13 is extended for adjusting the posture. After the posture is adjusted, the first solenoid valve 3 loses power. The control method of extending the posture adjustment of other oil cylinders such as the second oil cylinder 14 is similar to the control principle of the first oil cylinder 13, and will not be repeated here.

[0079] When the first oil cylinder 13 needs to retract and adjust its posture, the third electromagnetic reversing valve 5 is not energized and the valve is in the right position. The oil inlet a of the third electromagnetic reversing valve 5 is connected to the working port c, and its oil return port d is connected to the working port b. The working port b is respectively connected to the input port a of the first pressure reducing valve 6 and the control port c of the first hydraulically controlled one-way valve 16, and is also connected to the hydraulic oil tank 15. The first hydraulically controlled one-way valve 16 is in a closed state, the second relief valve 7 does not work, and the system is in a high-pressure system. The working port c of the third electromagnetic reversing valve 5 is connected to the input port b of the first shuttle valve 8, and the input port b of the first shuttle valve 8 is connected to the output port. The output port c is connected to the oil inlet a of the first electromagnetic reversing valve 3; the first electromagnetic reversing valve 3 is energized in the left position, the valve is in the left position, the oil inlet a of the first electromagnetic reversing valve 3 is connected to the working port c, the working port c is connected to the rod chamber of the first oil cylinder 13, the first oil cylinder 13 retracts, its rodless chamber is connected to the working port b of the first electromagnetic reversing valve 3, the working port b is connected to the return oil port d, and the return oil port d is connected back to the hydraulic oil tank 15, thus forming a loop. The control principle for retracting and adjusting the posture of other oil cylinders such as the second oil cylinder 14 is consistent with the control principle of the first oil cylinder 13, which will not be repeated here. It can be seen that each oil cylinder in this embodiment can be individually controlled to adjust the posture, lead into the hole, and the hydraulic system is in a high-pressure state during positioning.

[0080] When the equipment is drilling: the entire equipment is guided into the hole through the front positioning, and the symmetrical first oil cylinder 13 and second oil cylinder 14 are taken as an example. The control method of other oil cylinders is the same. At this time, the first electromagnetic reversing valve 3 is in the right position, the third electromagnetic reversing valve 5 and the second electromagnetic reversing valve 4 are in the right position, and the fourth electromagnetic reversing valve 9 is energized at the same time. At this time, the oil inlet a of the third electromagnetic reversing valve 5 is connected to the working port b, and its working port b is respectively connected to the oil inlet a of the first pressure reducing valve 6 and the control port c of the first hydraulically controlled one-way valve 16. At this time, the control port c of the first hydraulically controlled one-way valve 16 is high-pressure oil, which is in the open state. The oil outlet b of the first pressure reducing valve 6 is connected to the a of the first shuttle valve 8, and its oil drain port c is connected back to the hydraulic oil tank 15. The input port a of the first shuttle valve 8 is connected to its output port c. At this time, the pressure has become low pressure after passing through the first pressure reducing valve 6. The first shuttle valve 8 The output port c is connected with the oil inlet a of the first solenoid reversing valve 3, the oil inlet a is connected with its working port b, the working port b is connected with the rodless cavity of the first oil cylinder 13, and at the same time is connected with the oil inlet a of the first hydraulically controlled one-way valve 16, the b port of the first one-way valve 16 is connected with the oil inlet a of the second overflow valve 7, and its oil outlet b is connected back to the hydraulic oil tank 15, the rod cavity of the first oil cylinder 13 is connected with the working port c of the first solenoid reversing valve 3, the working port c is connected with the oil return port d, and the oil return port d is connected back to the hydraulic oil tank 15, thereby forming a circuit; the control principle of the low pressure extending out of the contact wall of the second oil cylinder 14 is the same as that of the first oil cylinder 13, and will not be repeated here.

[0081] When drilling, each oil cylinder contacts the wall at low pressure, which reduces the shaking of the entire equipment and keeps the equipment stable. At the same time, due to the low-pressure contact with the wall, the entire equipment can achieve continuous downward vertical drilling by its own gravity. During drilling, due to the uneven wall and the shaking of the equipment, the oil cylinder will inevitably be squeezed. Assuming that the first oil cylinder 13 is squeezed and forced to retract, the rodless cavity of the first oil cylinder 13 is connected to the oil inlet a of the first hydraulically controlled one-way valve 16. Since the first hydraulically controlled one-way valve 16 controls the oil to be high-pressure oil, it is always in an open state. Its oil inlet a is connected to the output b, and is connected to the input a of the second relief valve 7 through the first hydraulically controlled one-way valve 16. The set pressure of the second relief valve 7 is about 20 bar higher than the set pressure of the first pressure reducing valve 6. At this time, the first oil When the cylinder 13 is forced to be squeezed, the excess flow is overflowed back to the hydraulic oil tank 15 through the second overflow valve 7, so that the first cylinder 13 is forced to retract due to the squeezing; at this time, the second cylinder 14 on the symmetrical surface of the first cylinder 13 will continue to extend to contact the wall due to the retraction of the first cylinder 13, and the other cylinders will be similarly extended. This is repeated over and over again, and each cylinder continuously extends and retracts, automatically adjusting to ensure that it always contacts the wall at low pressure, ensuring that the entire equipment can perform hydraulic shock resistance while achieving continuous drilling, reducing the amount of equipment shaking, and maintaining the stability of the equipment during drilling.

[0082] When correcting the deviation of the equipment: During drilling, when the overall deviation of the equipment occurs, correction is required, such as using a laser device to ensure the verticality detection of the rectangular hole, and correcting the deviation by actively extending the cylinder at high pressure. Assuming that over-excavation occurs on the side where the first cylinder 13 is located, and under-excavation occurs on the side where the second cylinder 14 is located on the symmetrical side, these two cylinders are used as an example to illustrate the correction principle. When over-excavation occurs on the side of the first cylinder 13, the first cylinder 13 needs to be actively extended at high pressure, and the second cylinder 14 needs to be retracted. At this time, the first solenoid reversing valve 3 is energized in the right position, the third solenoid reversing valve 5 is de-energized, the second solenoid reversing valve 4 and the fourth solenoid reversing valve 9 are de-energized, and the other cylinders all maintain the state during drilling. The hydraulic pump 1 outputs high pressure, and its oil outlet port b is connected to the oil inlet port a of the third electromagnetic reversing valve 5. The d port of the third electromagnetic reversing valve 5 is connected to the output port b of the second relief valve 7, and is connected to the hydraulic oil tank 15 at the same time. At this time, the third electromagnetic reversing valve 5 is in the right position, and the oil inlet port a of the third electromagnetic reversing valve 5 is connected to the working port c, and the working port c is then connected to the input port b of the first shuttle valve 8. Its oil return port d is connected to the working port b, and the working port b is connected to the a port of the first pressure reducing valve 6 and the first hydraulic port 8 respectively. The control port c of the control check valve 16 is connected and communicated with the hydraulic oil tank 15. The first hydraulic control check valve 16 is in a closed state, the second relief valve 7 does not work, and the system is in a high-pressure system. At this time, the input port b of the first shuttle valve 8 is connected to the output port c, and the output port c is connected to the oil inlet a of the first electromagnetic reversing valve 3. At this time, the oil inlet a of the first electromagnetic reversing valve 3 is connected to the working port b, and the working port b is connected to the rodless chamber of the first oil cylinder 13. The first oil cylinder 13 extends at high pressure to correct the offset. The rod chamber of the first oil cylinder 13 is connected to the working port c of the first electromagnetic reversing valve 3, and its working port c is connected to the return oil port d and connected to the hydraulic oil tank 15, forming a circuit, so that the first oil cylinder 13 extends; at this time, the first oil cylinder 13 is stretched out with high pressure, and the second oil cylinder 14 on the symmetrical side is in a floating state, and its rodless chamber is connected to the working port b of the second electromagnetic reversing valve 4; the rod chamber of the second oil cylinder 14 is connected to the working port c of the second electromagnetic reversing valve 4, and the second electromagnetic reversing valve 4 is in the middle position due to no electricity. , its working port b, working port c, and return oil port d are connected to the hydraulic oil tank 15. At this time, the rodless cavity and the rod cavity of the second oil cylinder 14 are connected. When the first oil cylinder 13 is pushed out with high pressure, the second oil cylinder 14 is in a floating unloading state and passively retracts, reducing the high pressure required for the first oil cylinder 13 to correct the deviation. In this way, active correction of the over-excavation side is achieved to ensure the verticality of the excavated rectangular hole. The other oil cylinders that are not involved in the correction maintain the state during drilling, so that each oil cylinder is in contact with the wall surface, and the overall shaking of the equipment is reduced while correcting the deviation. When over-excavation occurs on the side of the second oil cylinder 14 and under-excavation occurs on the side of the first oil cylinder 13, the correction principle is similar. When over-excavation and under-excavation occur on the other oil cylinder sides, the correction principle is similar and will not be repeated here.

[0083] When the equipment is lifted: When the hole is drilled or the equipment fails and needs to be lifted for maintenance, each cylinder needs to be actively retracted or unloaded. The first working condition: After the hole is drilled, the equipment needs to be lifted out. At this time, oil enters the rod cavity of each cylinder. Retract each cylinder. Taking the first cylinder 13 as an example, the third solenoid reversing valve 5 is not energized, the valve is in the right position, the oil inlet port a is connected to the working port c, and its oil return port d is connected to the working port b. The working port b is respectively connected to the a port of the first pressure reducing valve 6 and the control port c of the first hydraulically controlled one-way valve 16, and is connected to the hydraulic oil tank 15. The first hydraulically controlled one-way valve 16 is in a closed state, the second overflow valve 7 does not work, and the system is in a high-pressure system; the working port c of the third solenoid reversing valve 5 is connected to the input port b of the first shuttle valve 8, the first The input port b of the shuttle valve 8 is connected with the output port c, and the output port c is connected with the oil inlet a of the first solenoid reversing valve 3; the first solenoid reversing valve 3 is energized in the left position, and the valve is in the left position, the oil inlet a of the first solenoid reversing valve 3 is connected with the working port c, and the working port c is connected with the rod cavity of the first oil cylinder 13, the first oil cylinder 13 retracts, and its rodless cavity is connected with the working port b of the first solenoid reversing valve 3, and the working port b is connected with the return oil port d, and the return oil port d is connected back to the hydraulic oil tank 15, thereby forming a loop and the first oil cylinder 13 retracts; the operation of other oil cylinders is consistent with it, and when each oil cylinder is retracted, it is convenient to lift the equipment out quickly. The second working condition: During the drilling process, it is found that the hydraulic pipeline is damaged and the hydraulic system cannot build pressure to retract the cylinder. At this time, all cylinders are in contact with the wall. At this time, all solenoid reversing valves are de-energized and each cylinder is in a neutral floating unloading state. When the equipment is lifted, the cylinders are passively retracted through active shaking, so that the entire equipment can be lifted out for maintenance smoothly.

[0084] Another preferred embodiment of the present application further provides a rectangular pile drilling device, comprising the hydraulic system described in any of the above embodiments.

[0085] The above description is only a preferred embodiment of the present application and is not intended to limit the present application. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principles of the present application should be included in the scope of protection of the present application.

Claims

1. A hydraulic system with active deviation correction and anti-vibration function, characterized in that: The invention comprises a hydraulic pump (1), a hydraulic oil tank (15), a symmetrically arranged first oil cylinder (13) and a second oil cylinder (14), wherein the first oil cylinder (13) is connected to the hydraulic pump (1) and the hydraulic oil tank (15) through a first combination valve, and the second oil cylinder (14) is connected to the hydraulic pump (1) and the hydraulic oil tank (15) through a second combination valve. The first combination valve and the second combination valve are used for: when the rectangular pile hole forming device is positioned in a hole, high-pressure oil is supplied to the first oil cylinder (13) and the second oil cylinder (14), so that the device is actively extended at high pressure to adjust the posture of the entire rectangular pile hole forming device and guide the device into the hole; when the rectangular pile hole forming device is drilling, low-pressure oil is supplied to the first oil cylinder (13) and the second oil cylinder (14), so that each oil cylinder contacts the wall surface at low pressure; when the rectangular pile hole forming device is correcting deviation, high-pressure oil is supplied to the oil cylinder on the over-excavation side so that the oil cylinder is actively extended at high pressure, and the oil cylinder on the under-excavation side is in a floating unloading state and is passively retracted; when the rectangular pile hole forming device is lifted, oil is supplied to the first oil cylinder (13) , the second oil cylinder (14) actively retracts or passively retracts after unloading; the first combination valve comprises a first electromagnetic reversing valve (3), a third electromagnetic reversing valve (5), a first pressure reducing valve (6), a second relief valve (7), and a first shuttle valve (8), wherein: The oil inlet a of the first electromagnetic reversing valve (3) is connected to the oil outlet b of the hydraulic pump (1), the oil return port d is connected to the hydraulic oil tank (15), the working port b is connected to the oil inlet a of the third electromagnetic reversing valve (5), and the working port c of the first electromagnetic reversing valve (3) is connected to the rod chamber of the first oil cylinder (13); the oil return port d of the third electromagnetic reversing valve (5) is connected to the hydraulic oil tank (15), the working port b is connected to the input port a of the first pressure reducing valve (6), and the output port b of the first pressure reducing valve (6) is connected to the oil return port d of the third electromagnetic reversing valve (5). The ports are respectively connected to the input port a of the second relief valve (7) and the input port a of the first shuttle valve (8); the working port c of the third electromagnetic reversing valve (5) is connected to the input port b of the first shuttle valve (8); the output port c of the first shuttle valve (8) is connected to the rodless chamber of the first oil cylinder (13); the output port b of the second relief valve (7) is respectively connected to the control port c of the first pressure reducing valve (6) and the hydraulic oil tank (15); the second combination valve includes the second electromagnetic reversing valve (4), the fourth electromagnetic reversing valve ( 9), a second pressure reducing valve (10), a third overflow valve (11), a second shuttle valve (12), the oil inlet a of the second electromagnetic reversing valve (4) is connected to the oil outlet b of the hydraulic pump (1), the oil return port d is connected to the hydraulic oil tank (15), the working port b is connected to the oil inlet a of the fourth electromagnetic reversing valve (9), and the working port c is connected to the rod chamber of the second oil cylinder (14); the oil return port d of the fourth electromagnetic reversing valve (9) is connected to the hydraulic oil tank (15), the working port b is connected to the oil inlet of the second pressure reducing valve (10), and the working port c is connected to the rod chamber of the second oil cylinder (14); the oil return port d of the fourth electromagnetic reversing valve (9) is connected to the hydraulic oil tank (15), and the working port b is connected to the oil inlet of the second pressure reducing valve (10). The inlet port a is connected, the output port b of the second pressure reducing valve (10) is respectively connected to the input port a of the third relief valve (11) and the input port a of the second shuttle valve (12), the working port c of the fourth electromagnetic reversing valve (9) is connected to the input port b of the second shuttle valve (12), the output port c of the second shuttle valve (12) is connected to the rodless chamber of the second oil cylinder (14); the output port b of the third relief valve (11) is respectively connected to the control port c of the second pressure reducing valve (10) and the hydraulic oil tank (15).

2. The hydraulic system with active deviation correction and anti-vibration function according to claim 1, characterized in that: It also includes a first overflow valve (2), which is connected to the output port of the hydraulic pump (1).

3. The hydraulic system with active deviation correction and anti-vibration function according to claim 1, characterized in that: The first electromagnetic reversing valve (3) and the second electromagnetic reversing valve (4) are Y-type three-position four-way reversing valves.

4. The hydraulic system with active deviation correction and anti-vibration function according to claim 1, characterized in that: The first electromagnetic reversing valve (3) and the second electromagnetic reversing valve (4) are H-type three-position four-way reversing valves.

5. A hydraulic system with active deviation correction and anti-vibration function, characterized in that: The invention comprises a hydraulic pump (1), a hydraulic oil tank (15), a symmetrically arranged first oil cylinder (13) and a second oil cylinder (14), wherein the first oil cylinder (13) is connected to the hydraulic pump (1) and the hydraulic oil tank (15) through a first combination valve, and the second oil cylinder (14) is connected to the hydraulic pump (1) and the hydraulic oil tank (15) through a second combination valve. The first combination valve and the second combination valve are used for: when the rectangular pile hole forming device is positioned in a hole, high-pressure oil is supplied to the first oil cylinder (13) and the second oil cylinder (14), so that the device is actively extended at high pressure to adjust the posture of the entire rectangular pile hole forming device and guide the device into the hole; when the rectangular pile hole forming device is drilling, low-pressure oil is supplied to the first oil cylinder (13) and the second oil cylinder (14), so that each oil cylinder contacts the wall surface at low pressure; when the rectangular pile hole forming device is correcting deviation, high-pressure oil is supplied to the oil cylinder on the over-excavation side so that the oil cylinder is actively extended at high pressure, and the oil cylinder on the under-excavation side is in a floating unloading state and is passively retracted; when the rectangular pile hole forming device is lifted, oil is supplied to the first oil cylinder (13) , the second oil cylinder (14) actively retracts or passively retracts after unloading; the first combination valve comprises a first electromagnetic reversing valve (3), a third electromagnetic reversing valve (5), a first pressure reducing valve (6), a second relief valve (7), a first shuttle valve (8), and a first hydraulically controlled one-way valve (16), wherein: The oil inlet a of the third electromagnetic reversing valve (5) is connected to the oil outlet b of the hydraulic pump (1), the oil return port d is respectively connected to the output port b of the second overflow valve (7) and the hydraulic oil tank (15), the working port c is connected to the input port b of the first shuttle valve (8), and the working port b is respectively connected to the control port c of the first hydraulically controlled one-way valve (16) and the input port a of the first pressure reducing valve (6); the control port c of the first pressure reducing valve (6) is connected to the hydraulic oil tank (15), the output port b is connected to the input port a of the first shuttle valve (8), and the output port c of the first shuttle valve (8) is connected to the The oil inlet a is connected, the oil return port d of the first electromagnetic reversing valve (3) is connected to the hydraulic oil tank (15), the working port b is respectively connected to the input port a of the first hydraulically controlled one-way valve (16) and the rodless cavity of the first oil cylinder (13), and the working port c is connected to the rod cavity of the first oil cylinder (13); the output port b of the first hydraulically controlled one-way valve (16) is connected to the input port a of the second relief valve (7); the second combination valve includes a second electromagnetic reversing valve (4), a fourth electromagnetic reversing valve (9), a second pressure reducing valve (10), a third relief valve (11), a second shuttle valve (12), and a second hydraulically controlled one-way valve (17), wherein: The oil inlet a of the fourth electromagnetic reversing valve (9) is connected to the oil outlet b of the hydraulic pump (1), the oil return port d is respectively connected to the output port b of the third overflow valve (11) and the hydraulic oil tank (15), the working port c is connected to the input port b of the second shuttle valve (12), and the working port b is respectively connected to the control port c of the second hydraulically controlled one-way valve (17) and the input port a of the second pressure reducing valve (10); the control port c of the second pressure reducing valve (10) is connected to the hydraulic oil tank (15), and the output port b is connected to the second shuttle valve (12). The output port c of the second shuttle valve (12) is connected to the oil inlet a of the second electromagnetic reversing valve (4), the oil return port d of the second electromagnetic reversing valve (4) is connected to the hydraulic oil tank (15), the working port b is respectively connected to the input port a of the second hydraulically controlled one-way valve (17) and the rodless cavity of the second oil cylinder (14), and the working port c is connected to the rod cavity of the second oil cylinder (14); the output port b of the second hydraulically controlled one-way valve (17) is connected to the input port a of the third overflow valve (11).

6. The hydraulic system with active deviation correction and anti-vibration function according to claim 5, characterized in that: It also includes a first overflow valve (2), which is connected to the output port of the hydraulic pump (1).

7. The hydraulic system with active deviation correction and anti-vibration function according to claim 5, characterized in that: The first electromagnetic reversing valve (3) and the second electromagnetic reversing valve (4) are Y-type three-position four-way reversing valves.

8. The hydraulic system with active deviation correction and anti-vibration function according to claim 5, characterized in that: The first electromagnetic reversing valve (3) and the second electromagnetic reversing valve (4) are H-type three-position four-way reversing valves.

9. A rectangular pile hole-forming device, characterized in that: Comprising the hydraulic system according to any one of claims 1 to 8.

Images